WO2024172177A1 - Scroll compressor - Google Patents

Abstract

A scroll compressor is disclosed. In the scroll compressor, a fixed scroll has formed therein an oil supply path which communicates between an intermediate pressure chamber and a compression chamber so as to guide some of an oil in the intermediate pressure chamber to the compression chamber, an orbiting wrap has an oil supply groove formed in the front end surface thereof to be in communication with the oil supply path, and the oil supply groove is recessed to a preset depth in the height direction of the wrap and can extend in a direction in which the wrap is formed. As such, under an abnormal driving condition such as rapid start-up, the oil can be supplied between the front end surface of the wrap and an end plate facing the front end surface through the oil supply groove provided in the front end surface of the wrap. Then, a frictional loss and/or abrasion between the front end surface of the wrap and the end plate may be reduced under the abnormal driving condition.

Description

Scroll Compressor

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor which supplies oil to a compression chamber by utilizing the difference between the internal pressure of a casing and the internal pressure of a compression chamber.

Compressors used in refrigeration cycles such as refrigerators and air conditioners compress refrigerant gas and transmit it to the condenser. Rotary compressors or scroll compressors are mainly used in air conditioners, and scroll compressors are used not only in air conditioners but also in water heater compressors that require a higher compression ratio than air conditioners.

Scroll compressors can be classified into a closed scroll compressor in which the drive unit (or electric unit) and the compression unit are provided together inside the casing, and an open scroll compressor in which the drive unit (or electric unit) is provided outside the casing and only the compression unit is provided inside the casing.

Scroll compressors can be classified into upper compression types or lower compression types depending on the location of the drive motor and the compression unit that make up the drive or electric unit. The upper compression type is a type in which the compression unit is located above the drive motor, and the lower compression type is a type in which the compression unit is located below the drive motor. This classification is based on examples in which the casing is installed in a vertical or vertical shape, and in cases in which the casing is installed horizontally, the left side can be conveniently classified as the upper side and the right side as the lower side.

Scroll compressors can be divided into low-pressure scroll compressors in which the internal space of the casing equipped with a compression section forms suction pressure, and high-pressure scroll compressors in which the internal space forms discharge pressure. Upper compression scroll compressors can be configured as low-pressure or high-pressure types, but lower compression scroll compressors are generally configured as high-pressure scroll compressors considering the location of the refrigerant suction pipe.

The high-pressure scroll compressor supplies oil from the casing to the compression chamber by utilizing the difference (hereinafter, differential pressure) between the internal pressure of the casing and the internal pressure of the compression chamber as the internal space of the casing forms the discharge pressure. Accordingly, the oil supply pump can be simplified in the high-pressure scroll compressor. Unless otherwise specified, the scroll compressor is defined as a bottom compression type and a high-pressure scroll compressor.

Patent Document 1 (Korean Patent Publication No. 10-2018-0138479) discloses a scroll compressor utilizing differential pressure. Patent Document 1 illustrates an example in which oil sucked through an oil passage of a rotating shaft is supplied to a compression chamber through an intermediate pressure chamber.

In these scroll compressors, if oil is supplied to the compression chamber before suction is completed, volume loss due to oversupply may occur. Therefore, in the oil supply structure using differential pressure, the location of the oil supply passage is set so that oil is supplied to the compression chamber after suction is completed.

However, in the case of the above conventional scroll compressor, under abnormal operating conditions such as rapid starting, the temperature of the compression section may rise up to 40 degrees higher than the high-pressure side temperature of the refrigeration cycle due to friction between the wraps. Then, the temperature of the suction-side wrap also rises rapidly, causing the suction-side wrap to be significantly deformed, which may significantly increase friction loss and/or wear between the leading edge of the suction-side wrap and the facing plate portion. If the orbiting scroll is manufactured from a material having a higher friction coefficient than the fixed scroll, the aforementioned friction loss and/or wear may increase even more, which may result in a decrease in compression efficiency and/or reliability problems.

In addition, since the conventional scroll compressor is configured to supply fuel to the compression chamber via an intermediate pressure chamber that forms back pressure for the orbiting scroll, fuel supply may not be possible in low pressure ratio operation with an operating pressure ratio of 1.3 or less. As a result, low pressure ratio operation with an operating pressure ratio of 1.3 or less may be limited, which may lower the efficiency of the scroll compressor and the air conditioner using the scroll compressor.

The purpose of the present invention is to provide a scroll compressor capable of reducing friction loss and/or wear between a leading edge of a wrap and a plate portion facing it even under abnormal operating conditions such as rapid starting.

Another object of the present invention is to provide a scroll compressor in which oil is smoothly supplied between a leading edge of a wrap and a plate portion facing it.

Another object of the present invention is to provide a scroll compressor in which oil is smoothly supplied between a suction-side wrap having relatively large thermal deformation and a plate portion facing the suction-side wrap.

Another object of the present invention is to provide a scroll compressor capable of suppressing wear of an orbiting scroll when the orbiting scroll is made of a material having a higher coefficient of thermal expansion than a fixed scroll.

Another object of the present invention is to provide a scroll compressor capable of smoothly supplying oil stored in the internal space of a casing to the compression chamber by utilizing the pressure difference between the internal space of a casing and the compression chamber while operating at a low pressure ratio of 1.3 or less.

In order to achieve the object of the present invention, a scroll compressor including a casing, a rotating shaft, an orbiting scroll, a fixed scroll, and a main frame can be provided. A certain amount of oil can be stored in the casing. The rotating shaft is provided in an internal space of the casing, and an oil passage can be formed therein. The orbiting scroll is provided with a rotating plate part to be coupled to the rotating shaft and perform an orbiting motion, and a orbiting wrap can be provided on one side of the orbiting plate part. The fixed scroll is coupled to the orbiting wrap and can be provided with a fixed wrap on one side of the fixed plate part to form a compression chamber. The main frame is provided on an opposite side of the fixed scroll with the orbiting scroll interposed therebetween and is fixed to the internal space of the casing, and can form an intermediate pressure chamber together with the orbiting scroll and the fixed scroll to pressurize the orbiting scroll toward the fixed scroll. The above fixed scroll may be provided with an oil supply passage that communicates between the intermediate pressure chamber and the compression chamber and guides a portion of the oil of the intermediate pressure chamber to the compression chamber. An oil supply groove may be formed on a front end surface of the orbiting wrap facing the fixed plate portion so as to communicate with the oil supply passage. The oil supply groove may be sunken in a lap height direction by a preset depth and may extend along the formation direction of the lap. Accordingly, even under abnormal driving conditions such as a rapid start, oil may be supplied between the front end surface of the lap and the plate portion facing it through the oil supply groove provided on the front end surface of the lap. Then, friction loss and/or wear between the front end surface of the lap and the plate portion may be reduced even under abnormal driving conditions.

For example, the oil supply groove may be formed inwardly along the formation direction of the orbital wrap from a point spaced apart from the outer end of the orbital wrap by a preset sealing length, within a range of a rotation angle of up to 300° of the rotational axis. Through this, oil may be smoothly supplied between the suction-side wrap, which has relatively large thermal deformation, and the facing plate portion, thereby reducing friction loss and/or wear in the suction-side wrap.

As another example, one end of the oil supply passage connected to the compression chamber may be formed so that at least a portion of each revolution of the orbiting scroll is positioned within the rotation radius range of the oil supply groove. Accordingly, oil flowing into the compression chamber through the oil supply passage may be continuously supplied to the oil supply groove, thereby reducing friction loss and/or wear in the suction-side wrap.

For example, the inner diameter of the fuel passage connected to the compression chamber may be formed smaller than the thickness of the lap of the rotating lap, and the width of the fuel groove may be formed smaller than or equal to the inner diameter of the fuel passage. Through this, the area of the cross-section provided on both sides of the fuel groove may be secured, thereby maintaining the sealing distance between the fuel groove and the compression chamber and/or between the compression chambers.

As another example, the above-mentioned fuel groove may be formed with the same cross-sectional area along the formation direction of the above-mentioned turning wrap. Through this, the fuel groove can be easily formed on the leading edge of the turning wrap while maintaining the leading edge area of the wrap uniform.

As another example, the oil supply grooves may be formed with different cross-sectional areas along the forming direction of the rotating wrap. This allows more oil to be supplied to areas with large thermal deformation, thereby more effectively reducing friction loss and/or wear.

For example, the above-described fueling groove may include a first fueling groove connected to the fueling passage; and a second fueling groove connected to the first fueling groove and formed on an outer side relative to the first fueling groove along the formation direction of the swirling wrap. The cross-sectional area of the second fueling groove may be formed to be larger than the cross-sectional area of the first fueling groove. Through this, more oil can be supplied to a portion with relatively large thermal deformation, such as the suction-side wrap, thereby reducing friction loss and/or wear in the suction-side wrap.

In addition, the refueling groove may include a first refueling groove connected to the refueling passage; and a second refueling groove connected to the first refueling groove and formed on an outer side of the first refueling groove along the formation direction of the orbital wrap. The cross-sectional area of the second refueling groove may be formed smaller than the cross-sectional area of the first refueling groove. Through this, the area of the leading edge in a part where thermal deformation is relatively large, such as the suction-side wrap, can be formed large, thereby ensuring reliability in the suction-side wrap.

As another example, the orbiting scroll may be formed of a material having a higher coefficient of thermal expansion than the fixed scroll. Through this, the weight of the orbiting scroll may be reduced, thereby increasing compression efficiency, while suppressing wear on the leading edge of the orbiting wrap, thereby increasing reliability of the orbiting scroll.

As another example, the oil supply passage may be formed to be separated from the intermediate pressure chamber and communicate between the oil passage and the compression chamber. Accordingly, since the internal space of the casing is directly connected to the compression chamber without passing through the intermediate pressure chamber, even when the operating pressure ratio is 1.3 or less, that is, even when the differential pressure between the internal space of the casing and the compression chamber is not large, the oil stored in the internal space of the casing can be smoothly supplied to the compression chamber.

For example, the fuel supply passage may include a first fuel supply passage and a second fuel supply passage. The first fuel supply passage is provided in the orbiting scroll, and one end may be connected to the oil passage of the rotating shaft. The second fuel supply passage is provided in the fixed scroll, and one end may be connected to the first fuel supply passage and the other end may be connected to the compression chamber. Through this, the fuel supply passage is separated from the intermediate pressure chamber, so that the internal space of the casing can be directly connected to the compression chamber without passing through the intermediate pressure chamber.

Specifically, the other end of the first-grade oil passage and one end of the second-grade oil passage can be continuously connected at least partially during the rotational movement of the orbiting scroll. Through this, oil in the casing can be guided to be continuously supplied to the compression chamber without the oil passage being connected to the intermediate pressure chamber.

Specifically, the other end of the first fuel passage may be penetrated through the first thrust surface of the orbiting scroll facing the fixed scroll, and one end of the second fuel passage may be penetrated through the second thrust surface of the fixed scroll facing the orbiting scroll. Through this, the fuel passage may be formed so as to always be connected without being connected to the intermediate pressure chamber.

More specifically, at least one of the other end of the first fuel passage and one end of the second fuel passage facing it may be formed with a non-circular cross-section shape. Accordingly, even if the thrust surface is narrowed by forming a hybrid wrap or an elliptical wrap, the fuel passage can be formed so as to always be connected without being connected to the intermediate pressure chamber.

More specifically, the other end of the first-grade oil passage can be extended in a circumferential direction from the first thrust surface. One end of the second-grade oil passage can be extended in a circumferential direction from the second thrust surface. Through this, the first-grade oil passage and the second-grade oil passage are continuously connected even during the rotating motion of the orbiting scroll, so that oil stored in the internal space of the casing can be smoothly supplied to the compression chamber even during low-pressure ratio operation.

More specifically, the cross-section of one end of the second fuel passage can be formed wider than the cross-section of the other end of the first fuel passage. Accordingly, by forming the cross-section of the fuel passage larger on the thrust surface with a relatively larger free area, the first fuel passage and the second fuel passage can be continuously connected even during the orbital movement of the orbital scroll.

In addition, the first oil supply passage may include a first turning oil supply section, a second turning oil supply section, and a third turning oil supply section. The first turning oil supply section may have one end connected to the oil passage, and the other end extended toward the outer circumferential surface of the orbiting scroll. The second turning oil supply section may have one end connected to the first turning oil supply section, and the other end may be opened toward the fixed scroll. The third turning oil supply section may extend circumferentially from the other end of the second turning oil supply section facing the fixed scroll and be connected to the second oil supply passage. Through this, the first oil supply passage may be easily formed in the orbiting scroll without being connected to the intermediate pressure chamber.

Specifically, the radial width of the third turning oil refueling section may be formed to be greater than or equal to the inner diameter of the second turning oil refueling section. Through this, it may be advantageous to form the cross-sectional area of the third turning oil refueling section formed on the thrust surface as wide as possible so that the first oil refueling passage is continuously connected with the second oil refueling passage.

Specifically, the inner diameter of the second turning oil refueling part can be formed to be smaller than or equal to the inner diameter of the first turning oil refueling part. Through this, the first turning oil refueling part can be easily processed while the pressure of the oil passing through the second turning oil refueling part can be lowered, thereby increasing the oil refueling effect in low pressure ratio operation.

In addition, the second fuel passage may include a first fixed fuel section, a second fixed fuel section, a third fixed fuel section, and a fourth fixed fuel section. The first fixed fuel section may have one end opened on a side facing the orbiting scroll and communicated with the first fuel passage, and the other end may extend toward the other side of the fixed scroll. The second fixed fuel section may have one end connected to the other end of the first fixed fuel section and the other end may extend toward the compression chamber. The third fixed fuel section may have one end connected to the second fixed fuel section and the other end may open to communicate with the compression chamber. The fourth fixed fuel section may extend circumferentially from one end of the first fixed fuel section facing the orbiting scroll and communicate with the first fuel passage. Through this, a second-grade oil passage can be easily formed in the fixed scroll without being connected to the intermediate pressure chamber.

Specifically, the radial width of the fourth fixed oil supply portion may be formed to be larger than the inner diameter of the first fixed oil supply portion. Through this, the cross-sectional area of the fourth fixed oil supply portion formed on the thrust surface may be formed as wide as possible, which may be advantageous in allowing the second oil supply passage to be continuously connected with the first oil supply passage.

Specifically, the fourth fixed oil supply unit may be formed so that the cross-sectional area on the side farther from the first fixed oil supply unit is larger than the cross-sectional area on the side adjacent to the first fixed oil supply unit. Accordingly, the fourth fixed oil supply unit may be formed wider on the relatively wide side of the thrust surface of the fixed scroll, thereby making the size of the fourth fixed oil supply unit as large as possible. In addition, it may be more advantageous to ensure that the second oil supply passage is continuously connected with the first oil supply passage.

According to the scroll compressor of the present invention, a fixed scroll has an oil supply passage formed between an intermediate pressure chamber and a compression chamber to guide some of the oil of the intermediate pressure chamber to the compression chamber, and an oil supply groove formed on a front end surface of an orbiting wrap so as to communicate with the oil supply passage, and the oil supply groove can be sunken in a wrap height direction to a preset depth and extended along the formation direction of the wrap. Through this, even under abnormal operating conditions such as a rapid start, oil can be supplied between the front end surface of the wrap and the facing plate portion through the oil supply groove provided on the front end surface of the wrap. Then, friction loss and/or wear between the front end surface of the wrap and the facing plate portion can be reduced even under abnormal operating conditions.

According to the scroll compressor of the present invention, the oil supply groove can be formed inwardly along the formation direction of the orbital wrap from a point where the oil supply groove is spaced apart from the outer end of the orbital wrap by a preset sealing length, within a range of a rotation angle of up to 300° of the rotational shaft. Through this, oil can be smoothly supplied between the suction-side wrap having a relatively large thermal deformation and the facing plate portion, thereby reducing friction loss and/or wear in the suction-side wrap.

The scroll compressor according to the present invention can be formed so that at least a part of an oil supply passage communicating with a compression chamber is positioned within the rotation radius range of an oil supply groove per one revolution of the orbiting scroll. Accordingly, oil flowing into the compression chamber through the oil supply passage can be continuously supplied to the oil supply groove, thereby reducing friction loss and/or wear in the suction-side wrap.

In the scroll compressor according to the present invention, the oil supply grooves can be formed with the same cross-sectional area along the formation direction of the orbiting wrap. Through this, the oil supply grooves can be easily formed on the leading edge of the orbiting wrap while maintaining the leading edge area of the wrap uniform.

In the scroll compressor according to the present invention, the oil supply grooves can be formed with different cross-sectional areas along the formation direction of the rotating wrap. Through this, more oil can be supplied to a part with a large thermal deformation, thereby more effectively reducing friction loss and/or wear.

The scroll compressor according to the present invention can be formed so that the oil supply passage is separated from the intermediate pressure chamber and communicates between the oil passage and the compression chamber. Accordingly, since the internal space of the casing is directly connected to the compression chamber without passing through the intermediate pressure chamber, the oil stored in the internal space of the casing can be smoothly supplied to the compression chamber even when the operating pressure ratio is 1.3 or less, that is, even when the differential pressure between the internal space of the casing and the compression chamber is not large.

Figure 1 is a longitudinal cross-sectional view showing a lower compression type scroll compressor according to the present embodiment.

Figure 2 is a perspective view showing the rotating scroll and fixed scroll in Figure 1 in an exploded view.

Figure 3 is a plan view showing the rotary scroll in Figure 2.

Figure 4 is a cross-sectional view taken along line “Ⅸ-Ⅸ” of Figure 3.

Figure 5 is a plan view showing the fixed scroll in Figure 2.

Figure 6 is a cross-sectional view taken along the line “Ⅹ-Ⅹ” of Figure 5.

Figure 7 is a plan view showing the state in which the rotating scroll and the fixed scroll are combined from the fixed scroll side in this embodiment.

Figure 8 is a schematic diagram showing an enlarged view of the relationship between the third rotating refueling unit and the fourth fixed refueling unit according to the change in rotation angle in Figure 7.

Figure 9 is a plan view showing the state in which the rotating scroll and the fixed scroll are combined from the rotating scroll side in this embodiment.

Figure 10 is a schematic diagram explaining the communication relationship between the fuel passage and the fuel home in Figure 9.

Fig. 11 is a plan view of a rotating scroll shown to explain another embodiment for a refueling home.

Fig. 12 is a plan view of a pivot scroll shown to illustrate another embodiment of a refueling home.

Hereinafter, a scroll compressor according to the present invention will be described in detail based on the attached drawings. In the following description, descriptions of some components may be omitted in order to clarify the features of the present invention.

In addition, the term "upper side" used in the following description means the direction away from the support surface supporting the scroll compressor according to the embodiment of the present invention, that is, the upper side toward the drive unit (power unit or drive motor) when looking at the drive unit (power unit or drive motor) and the compression unit in the center. The term "lower side" means the direction approaching the support surface, that is, the lower side toward the compression unit when looking at the drive unit (power unit or drive motor) and the compression unit in the center.

Also, the term "axial" used in the following description means the longitudinal direction of the rotation axis. "Axial" can be understood as the up-down direction. "Radial" means the direction intersecting the rotation axis.

In addition, in the following description, the scroll compressor is explained as an example of a sealed scroll compressor in which the drive unit (electrical unit or drive motor) and the compression unit are provided in the casing. However, the same can be applied to an open compressor in which the drive unit (electrical unit or drive motor) is provided outside the casing and connected to the compression unit provided inside the casing.

In addition, the following description will be made using a lower compression type scroll compressor as an example, which is a vertical scroll compressor in which the drive unit and the compression unit are arranged in the vertical axial direction, and the compression unit is located below the drive unit (the drive unit or the drive motor). However, the same can be applied to a horizontal scroll compressor in which the drive unit (the drive unit or the drive motor) and the compression unit are arranged left and right, as well as an upper compression type scroll compressor in which the compression unit is located above the drive unit (the drive unit or the drive motor).

In addition, the following description uses as an example a high-pressure scroll compressor that is a lower compression type and in which a refrigerant suction pipe forming a suction passage is directly connected to a compression section and a refrigerant discharge pipe is connected to the internal space of the casing so that the internal space of the casing forms a discharge pressure.

Fig. 1 is a longitudinal cross-sectional view showing the interior of a lower compression type scroll compressor according to the present embodiment.

Referring to FIG. 1, a high-pressure, bottom-compression scroll compressor (hereinafter, abbreviated as a scroll compressor) according to the present embodiment is provided with a driving motor (120) forming an electric part in the upper half of a casing (110), and a main frame (130), an orbiting scroll (140), a fixed scroll (150), and a discharge cover (160) are provided on the lower side of the driving motor (120). As described above, the driving motor (120) typically forms an electric part, and the main frame (130), the orbiting scroll (140), the fixed scroll (150), and the discharge cover (160) form a compression part (C).

The drive motor (120) forming the electric part is coupled to the upper end of the rotation shaft (125) described later, and the compression part (C) is coupled to the lower end of the rotation shaft (125). Accordingly, the compressor (10) forms the lower compression structure described above, and the compression part (C) is connected to the drive motor (120) by the rotation shaft (125) and operates by the rotational force of the drive motor (120). Accordingly, the drive motor (120) can be understood as a drive part that drives the compression part (C), and thus, the drive motor may be described hereinafter as an electric part or a drive part.

Referring to FIG. 1, the casing (110) according to the present embodiment may include a cylindrical shell (111), an upper shell (112), and a lower shell (113). The cylindrical shell (111) has a cylindrical shape with upper and lower ends open, the upper shell (112) is coupled to cover the opened upper end of the cylindrical shell (111), and the lower shell (113) is coupled to cover the opened lower end of the cylindrical shell (111). Accordingly, the internal space (110a) of the casing (110) is sealed, and the internal space (110a) of the sealed casing (110) is divided into a lower space (S1) and an upper space (S2) based on the driving motor (120).

The lower space (S1) is a space formed at the lower side of the driving motor (120), and the lower space (S1) can be divided into a storage space (S11) and a discharge space (S12) based on the compression section (C).

The upper space (S2) is a space formed above the driving motor (120) and forms an oil separation space where oil is separated from the refrigerant discharged from the compression section (C). A refrigerant discharge pipe (116), which will be described later, is connected to the upper space (S2).

The aforementioned driving motor (120) and main frame (130) are inserted and fixed inside the cylindrical shell (111). An oil recovery passage (not shown) may be formed on the outer surface of the driving motor (120) and the outer surface of the main frame (130) at a preset interval from the inner surface of the cylindrical shell (111).

A refrigerant suction pipe (115) is connected by penetrating the side of the cylindrical shell (111). Accordingly, the refrigerant suction pipe (115) is connected by penetrating the cylindrical shell (111) forming the casing (110) in the radial direction.

The upper part of the upper shell (112) is connected by penetrating the inner end of the refrigerant discharge pipe (116) to the inner space (110a) of the casing (110), specifically, the upper space (S2) formed on the upper side of the driving motor (120).

One end of an oil circulation pipe (not shown) may be radially connected to the lower half of the lower shell (113). The oil circulation pipe is open at both ends, and the other end of the oil circulation pipe may be connected to the refrigerant suction pipe (115). An oil circulation valve (not shown) may be installed in the middle of the oil circulation pipe.

Referring to FIG. 1, the driving motor (120) according to the present embodiment includes a stator (121) and a rotor (122). The stator (121) is inserted and fixed into the inner surface of a cylindrical shell (111), and the rotor (122) is rotatably provided inside the stator (121).

The stator (121) includes a stator core (1211) and a stator coil (1212).

The stator core (1211) is formed in an annular or hollow cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot pressing.

The stator coil (1212) is wound around the stator core (1211) and is electrically connected to an external power source through a power cable (not shown) that penetrates the casing (110). An insulator (1213), which is an insulating material, is inserted between the stator core (1211) and the stator coil (1212).

The rotor (122) includes a rotor core (1221) and a permanent magnet (1222).

The rotor core (1221) is rotatably inserted into the stator core (1211) at a predetermined gap (not shown). Permanent magnets (1222) are embedded in the rotor core (1221) at a predetermined gap along the circumference.

A balance weight (123) may be coupled to the lower end of the rotor core (1221). However, the balance weight (123) may also be coupled to the rotation shaft (125). This embodiment shows an example in which the balance weight (123) is coupled to the rotation shaft (125). The balance weights (123) are installed at the lower end and upper end of the rotor, respectively, and the two are installed symmetrically to each other.

A rotation shaft (125) is coupled to the center of the rotor core (1221). The upper part of the rotation shaft (125) is press-fitted and coupled to the rotor (122), and the lower part of the rotation shaft (125) is rotatably inserted into the main frame (130) and supported in the radial direction.

The main frame (130) is provided with a main bearing (not shown) made of a bushing bearing to support the lower end of the rotation shaft (125). Accordingly, the lower end of the rotation shaft (125) inserted into the main frame (130) can rotate smoothly inside the main frame (130).

The rotating shaft (125) transmits the rotational power of the driving motor (120) to the orbiting scroll (140) forming the compression section (C). Accordingly, the orbiting scroll (140) eccentrically coupled to the rotating shaft (125) rotates relative to the fixed scroll (150).

An oil passage (126) is formed inside the rotating shaft (125) to guide oil stored in the oil storage space (S11) of the casing (110) to the sliding part, and an oil pickup (127) can be coupled to the lower end of the oil passage (126) to pump the oil filled in the oil storage space (S11). Accordingly, the oil filled in the oil storage space (S11) can be supplied to each sliding part while being sucked along the rotating shaft (125) through the oil pickup (127) and the oil passage (126) when the rotating shaft (125) rotates.

The oil passage (126) includes a first oil passage (1261) formed in an axial or inclined direction inside the rotating shaft (125) and a second oil passage (1262) penetrating from the first oil passage (1261) toward the outer surface of the rotating shaft (125).

The first oil passage (1261) may be formed by excavating a groove from the lower end of the rotation shaft (125) to approximately the lower end or middle height of the stator (121), or around the upper end of the main bearing section (133) described later, as the compression section (C) is located lower than the driving motor (120). Of course, in some cases, the first oil passage (1261) may be formed by axially penetrating the rotation shaft (125).

A plurality of second oil passages (1262) are provided to communicate with each of the sliding parts, and a plurality of second oil passages (1262) can be formed at preset intervals along the axial direction to correspond to each of the sliding parts.

The compression unit (C) according to the present embodiment includes a main frame (130), a rotating scroll (140), and a fixed scroll (150). For example, the fixed scroll (150) may be provided on the lower side of the main frame (130), and the rotating scroll (140) may be axially supported by the fixed scroll (150) and may be provided so as to be rotatable between the main frame (130) and the fixed scroll (150).

Referring to FIG. 1, the main frame (130) according to the present embodiment includes a frame plate part (131), a frame side wall part (132), and a main bearing part (133). The frame plate part (131) is installed on the lower side of the driving motor (120). A main shaft hole (1331) forming a main bearing part (133), which will be described later, is formed axially through the center of the frame plate part (131). The frame side wall part (132) extends in a cylindrical shape from the lower edge of the frame plate part (131) and is fixed to the inner surface of a cylindrical shell (111) by hot pressing or welding. The main bearing part (133) is provided with a main shaft hole (1331) so that a rotation shaft (125) can be rotatably inserted therein, and supports the rotation shaft (125) in the radial direction.

Referring to FIG. 1, the orbiting scroll (140) according to the present embodiment includes a orbiting plate portion (141), an orbiting wrap (142), and a rotating shaft coupling portion (143). The orbiting scroll (140) may be formed of a material that is lighter than a fixed scroll (150) described below, for example, a material having a thermal expansion coefficient greater than that of the fixed scroll (150).

The pivot plate (141) is formed in a circular shape and is accommodated between the frame pivot plate (131) and the fixed pivot plate (151) described later. The upper surface of the pivot plate (141) can be axially supported on the main frame (130) with a back pressure sealing member (not shown) interposed therebetween.

On one side of the pivot plate (141), that is, on the upper edge of the pivot plate (141) facing the main frame (130), a pivot-side keyway (1411) is formed that is sunken from the outer surface to a preset depth. The pivot-side keyway (1411) is formed long in the radial direction, and a pivot-side key (not shown) of an old ring (170) that prevents rotation of the pivot scroll (140) is slidably inserted therein. The depth of the pivot-side keyway (1411) can be formed to be approximately half the thickness of the pivot plate (141). Accordingly, when the first-grade fuel passage (1911) described later is formed on the same axis as the turning-side keyway (1411), the inner diameter of the first-grade fuel passage (1911) must be formed too small or the thickness of the turning plate (141) must be formed too thick, which may be inappropriate.

In addition, an intermediate pressure chamber (Sm) can be formed on the outer surface of the pivot plate (141) facing the edge of the pivot plate (141), that is, the frame pivot plate (131) and the frame side wall (132), together with the frame pivot plate (131), the frame side wall (132), and the fixed side wall (152) to be described later. The intermediate pressure chamber (Sm) is communicated with the compression chamber (V) through the intermediate pressure passage (180) to be described later to form an intermediate pressure (back pressure). Accordingly, the pivot plate (141) receives the back pressure of the intermediate pressure chamber (Sm) and is axially supported toward the fixed scroll (150), so that leakage between the compression chambers (V) can be suppressed. The intermediate pressure chamber (Sm) and the intermediate pressure passage (180) will be described again later together with the fixed scroll (150).

Meanwhile, a first fuel passage (191) is formed inside the pivot plate (141). The first fuel passage (191) forms a part of a fuel passage (190) to be described later, and may be formed by penetrating the inside of the pivot plate (141). For example, one end of the first fuel passage (191) may be opened to the inner surface of the pivot plate (141) or to the upper surface facing the frame plate (131) and communicated with the oil passage (126), and the other end of the first fuel passage (191) may be opened to the lower surface of the pivot plate (141), that is, the thrust surface (hereinafter, first thrust surface) (140a) of the pivot scroll (140), and may be directly connected to the second fuel passage (192) to be described later. Accordingly, the first oil passage (191) can be connected to the second oil passage (192) without passing through the intermediate pressure chamber (Sm). Then, a portion of the oil sucked from the internal space (110a) of the casing (110) through the oil passage (126) of the rotating shaft (125) can move directly to the second oil passage (192) through the first oil passage (191) and then be supplied to the compression chamber (V) through the second oil passage (192). The first oil passage (191) will be described later together with the second oil passage (192) forming another portion of the oil passage (190).

The pivoting wrap (142) extends from the lower surface of the pivoting plate (141) toward the fixed plate (151) to be described later, and is interlocked with the fixed wrap (154) to be described later to form the first compression chamber (V1) and the second compression chamber (V2) described above.

The turning wrap (142) can be formed in an involute shape. However, the turning wrap (142) can be formed in various shapes other than an involute together with the fixed wrap (154). For example, the turning wrap (142) has a shape in which a plurality of arcs having different diameters and origins are connected, and the outermost curve can be formed in an approximately elliptical shape having a major axis and a minor axis. The fixed wrap (154) can also be formed in the same manner. Hereinafter, this can be explained by defining it as a hybrid wrap shape.

The inner end of the pivoting wrap (142) is formed in the central portion of the pivoting plate (141), and a rotation shaft coupling portion (143) is formed axially through the central portion of the pivoting plate (141). Accordingly, the discharge port (1511) described later is formed in the center of the pivoting scroll (140), that is, at an eccentric position from the rotation shaft coupling portion (143).

A refueling groove (195) communicating with a second refueling passage (192) to be described later may be formed on the leading edge of the turning wrap (142). The refueling groove (195) may be sunken along the axial direction of the turning wrap (142) to a preset depth and may extend along the formation direction of the turning wrap (142) (or the compression direction of the compression chamber). Accordingly, a portion of the oil supplied to the compression chamber (V) through the refueling passage (190) flows into the refueling groove (195), and the oil spreads along the refueling groove (195) to lubricate the space between the leading edge (142a) of the turning wrap (142) and one side of the fixed plate portion (151) facing it. The refueling groove (195) will be described later together with the refueling passage (190).

A rotary shaft (125) is rotatably inserted and connected to the rotary shaft coupling part (143). Accordingly, the outer circumference of the rotary shaft coupling part (143) is connected to the rotary wrap (142) to form a first compression chamber (V1) together with the fixed wrap (154) during the compression process.

The rotary shaft coupling portion (143) is formed at a height that overlaps the rotary wrap (142) on the same plane. That is, the rotary shaft coupling portion (143) is positioned at a height that overlaps the eccentric portion (1251) of the rotary shaft (125) on the same plane as the rotary wrap (142). Accordingly, the repulsive force and the compressive force of the refrigerant are applied on the same plane based on the rotary plate portion (141) and cancel each other out, thereby suppressing the tilting of the rotary scroll (140) due to the action of the compressive force and the repulsive force.

Referring to FIG. 1, a fixed scroll (150) according to the present embodiment includes a fixed plate portion (151), a fixed side wall portion (152), a sub-bearing portion (153), and a fixed wrap (154).

The fixed plate part (151) is formed in a disc shape and is arranged at a preset interval on the lower side of the frame plate part (131). A sub-axis hole (1531) forming a sub-bearing part (153) is formed through the center of the fixed plate part (151) in the vertical direction. A discharge port (1511) is formed around the sub-axis hole (1531) to communicate with the first compression chamber (V1) and the second compression chamber (V2) described below, respectively, through which the compressed refrigerant is discharged to the muffler space (160a) of the discharge cover (160).

The discharge port (1511) is formed at an eccentric position from the center of the fixed plate portion (151). In other words, as the sub-axis hole (1531) is formed at the center of the fixed plate portion (151), the discharge port (1511) is formed at an eccentric position from the sub-axis hole (1531).

The fixed side wall portion (152) extends upward and downward from the upper edge of the fixed plate portion (151) and is joined to the frame side wall portion (132) of the main frame (130). A suction port (1521) is formed in the fixed side wall portion (152) that penetrates the fixed side wall portion (152) in the radial direction. As described above, an end of a refrigerant suction pipe (115) that penetrates the cylindrical shell (111) is inserted and joined to the suction port (1521).

In addition, an intermediate pressure passage (180) and a second fuel passage (192) are formed on one side of the suction port (1521). In other words, an intermediate pressure passage (180) and a second fuel passage (192) are formed on one side of the circumference of the suction port (1521). Accordingly, the intermediate pressure passage (180) and the second fuel passage (192) can each be connected to compression chambers (V) having different pressures by penetrating the interior of the fixed side wall portion (152) without interfering with the suction port (1521).

The intermediate pressure passage (180) may be connected at one end to the compression chamber (V) and at the other end directly connected to the intermediate pressure chamber (Sm) to be described later. For example, one end of the intermediate pressure passage (180) may be connected to a compression chamber (V) that forms an intermediate pressure between the suction pressure and the discharge pressure among the compression chambers (V), and the other end of the intermediate pressure passage (180) may be formed by penetrating the axial side surface of the fixed side wall portion (152) that continuously penetrates the fixed plate portion (151) and the fixed side wall portion (152) to form the intermediate pressure chamber (Sm) to be described later, that is, penetrating the thrust surface (hereinafter, referred to as the second thrust surface (150a)) of the fixed scroll (150). Accordingly, the intermediate pressure chamber (Sm) may form an appropriate back pressure depending on the pressure of the compression chamber (V) connected to the intermediate pressure chamber (Sm).

However, one end of the intermediate pressure passage (180) may be connected to a compression chamber (V) having a higher pressure than the pressure of the compression chamber (V) to which the other end of the fuel passage (190) described later, that is, the other end of the third fixed fuel supply part (1923) forming the outlet of the fuel passage (190) is connected. Accordingly, the intermediate pressure chamber (Sm) can form a back pressure sufficient to support the orbiting scroll (140) toward the fixed scroll (150), thereby stably sealing between the orbiting scroll (140) and the fixed scroll (150).

In addition, the other end of the intermediate pressure passage (180) is formed so that at least a portion thereof is located outside the turning radius range of the turning plate member (141) based on the rotation angle of the orbiting scroll (140). For example, an intermediate pressure groove (180a) extending radially from the second thrust surface (150a) is formed at the other end of the intermediate pressure passage (180), and the intermediate pressure groove (180a) may be formed so as to be located outside the turning radius range of the turning plate member (141) at least at one point in time based on the rotation angle of the orbiting scroll (140). Accordingly, one end of the intermediate pressure passage (180) may be continuously connected to the compression chamber (V), while the other end of the intermediate pressure passage (180) may be continuously or/and temporarily connected to the intermediate pressure chamber (Sm). Then, the pressure of the intermediate pressure chamber (Sm) can be varied according to the pressure of the compression chamber (V) as explained above, and an appropriate back pressure can be formed.

Meanwhile, the second fuel passage (192) forms another part of the fuel passage (190) and may be formed inside the fixed scroll (150) separately from the intermediate pressure passage (180) described above. For example, one end of the second fuel passage (192) may be opened to the upper surface of the fixed side wall portion (152), i.e., the second thrust surface (150a) of the fixed scroll (150), so as to be connected to the intermediate pressure chamber (Sm), and the other end of the second fuel passage (192) may be opened to the upper surface of the fixed plate portion (151) so as to be connected to the compression chamber (V). In other words, one end of the second fuel passage (192) is connected to the other end of the first fuel passage (191), and the other end of the second fuel passage (192) can be formed to be connected to the rotation angle immediately after the compression chamber (V) is completed with respect to the rotation angle of the rotary shaft (125). Accordingly, the second fuel passage (192) can be directly connected to the first fuel passage (191) without going through the intermediate pressure chamber (Sm). Then, as described above, a portion of the oil sucked from the internal space (110a) of the casing (110) through the oil passage (126) of the rotary shaft (125) can move directly to the second fuel passage (192) through the first fuel passage (191), and then be supplied to the compression chamber (V) through the second fuel passage (192). The second fuel route (192) will be described later together with the first fuel route (191), which forms another part of the fuel route (190).

A cylindrical sub-axis hole (1531) penetrates axially through the center of the sub-bearing portion (153) to support the lower end of the rotation shaft (125) in the radial direction.

The fixed wrap (154) is formed to extend axially from the upper surface of the fixed plate member (151) toward the orbiting scroll (140). The fixed wrap (154) is interlocked with the orbiting wrap (142) to be described later to form a compression chamber (V). The compression chamber (V) includes a first compression chamber (V1) formed between the inner surface of the fixed wrap (154) and the outer surface of the orbiting wrap (142), and a second compression chamber (V2) formed between the outer surface of the fixed wrap (154) and the inner surface of the orbiting wrap (142).

Since the fixed wrap (154) is formed to correspond to the shape of the pivot wrap (144) described above, the description of the fixed wrap (154) is replaced with the description of the pivot wrap (142).

The unexplained symbol 1512 in the drawing is a bypass hole.

The scroll compressor according to the present embodiment as described above operates as follows.

That is, when power is applied to the driving motor (120), rotational force is generated in the rotor (122) and the rotation shaft (125), causing them to rotate, and the orbiting scroll (140) eccentrically coupled to the rotation shaft (125) performs a rotational movement with respect to the fixed scroll (150) by the Oldham ring (170).

Then, the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually decreases from the outside of each compression chamber (V1)(V2) toward the center. Then, the refrigerant is sucked into the first compression chamber (V1) and the second compression chamber (V2) through the refrigerant suction pipe (115).

Then, the refrigerant is compressed while moving along the movement path of each compression chamber (V1)(V2), and the compressed refrigerant is discharged into the muffler space (160a) of the discharge cover (160) through the discharge port (1511) connected to the compression chamber.

Then, the refrigerant is discharged through the discharge hole (not shown) provided in the fixed scroll (150) and the main frame (130) into the discharge space (S12) between the main frame (130) and the drive motor (120), passes through the drive motor (120), and moves to the upper space (S2) of the casing (110) formed on the upper side of the drive motor (120). The refrigerant is separated into refrigerant and oil in the upper space (S2), and the refrigerant is discharged to the outside of the casing (110) through the refrigerant discharge pipe (116), while the oil separated from the refrigerant is recovered to the oil storage space (S11) of the casing (110) through the oil recovery passage (not shown) described above. This oil is supplied to each of the sliding parts and compression chambers (V) through the oil path (126) of the rotating shaft (125) and then returned to the oil storage space (S11) of the casing (110), repeating a series of processes.

Meanwhile, when the orbiting wrap and the fixed wrap are formed in the conventional involute shape, a relatively large free area is left outside the outermost wrap of the orbiting wrap and the fixed wrap where no compression chamber is formed. In other words, in the conventional involute wrap, the areas of the first thrust surface and the second thrust surface are formed widely. Therefore, in the conventional involute wrap, a circular groove can be formed widely on one side of the orbiting scroll or the fixed scroll so that the fuel passages of both scrolls, that is, the fuel passages connecting the internal space of the casing and the compression chamber, are continuously connected.

However, when the outermost lap is extended without empty space, such as in the hybrid lap shape or elliptical lap shape described above, the free area between the first thrust surface and the second thrust surface becomes narrow. As a result, it is not easy to form the fuel supply passages on both sides to be continuously connected. Considering this, in the past, in the case of the hybrid lap shape, as in Patent Document 1, the fuel supply passages on both sides were formed to be continuously connected via the intermediate pressure chamber. This can secure the stroke volume to the maximum extent and increase the volumetric efficiency, but the pressure difference between the internal space of the casing and the compression chamber increases, which is disadvantageous for low-pressure ratio operation.

In other words, if the fuel supply passage passes through the intermediate pressure chamber, the pressure of the intermediate pressure chamber, i.e. the back pressure, must be maintained at an appropriate pressure. Accordingly, in the low pressure ratio operation where the operating pressure ratio is 1.3 or less, the pressure difference between the pressure of the internal space of the casing and the compression chamber is not formed, and fuel supply by differential pressure does not occur smoothly. As a result, low pressure ratio operation may become impossible in scroll compressors and air conditioners using the same.

Accordingly, in this embodiment, non-circular oil supply portions are formed in each of the orbiting scroll and the fixed scroll, so that the oil supply passage of the orbiting scroll and the oil supply passage of the fixed scroll are continuously connected. Accordingly, the oil supply passage can directly connect the internal space of the casing and the compression chamber without passing through the intermediate pressure chamber, so that oil supply using differential pressure can be possible even at a low pressure ratio of 1.3 or less, or even 1.1 or less.

FIG. 2 is a perspective view showing the orbiting scroll and the fixed scroll in FIG. 1 in an exploded manner, FIG. 3 is a plan view showing the orbiting scroll in FIG. 2, FIG. 4 is a cross-sectional view taken along line "Ⅸ-Ⅸ" of FIG. 3, FIG. 5 is a plan view showing the fixed scroll in FIG. 2, and FIG. 6 is a cross-sectional view taken along line "Ⅹ-Ⅹ" of FIG. 5.

Referring to FIGS. 1 and 2, the orbiting scroll (140) according to the present embodiment is provided with a first fuel passage (191) forming a part of the fuel passage (190), and the fixed scroll (150) is provided with a second fuel passage (192) forming another part of the fuel passage (190). The first fuel passage (191) and the second fuel passage (192) are connected to each other to form a single fuel passage (190). Accordingly, a part of the oil sucked along the oil passage (126) of the rotating shaft (125) in the internal space (110a) of the casing (110) can be supplied to the compression chamber (V) through the fuel passage (190).

Referring to FIGS. 2, 3, and 4, the first refueling channel (191) includes a first turning refueling unit (1911), a second turning refueling unit (1912), and a third turning refueling unit (1913). The first turning refueling unit (1911) may be understood as an inlet of the first refueling channel (191), the third turning refueling unit (1913) may be understood as an outlet of the first refueling channel (191), and the second turning refueling unit (1912) may be understood as a connecting portion connecting the inlet and outlet of the first refueling channel (191). However, the other end of the second turning refueling unit (1912), which will be described later, may also be understood as an outlet of the first refueling channel (191) together with the third turning refueling unit (1913).

The first turning oil supply portion (1911) may be formed to be sunken in from the inside of the turning plate portion (141) toward the outer surface by a preset depth. One end of the first turning oil supply portion (1911) may extend from the inner surface of the turning plate portion (141), that is, the inner surface of the rotation shaft coupling portion (143), toward the outer surface, or a groove may be formed on the upper surface of the inner surface side of the turning plate portion (141) facing the frame plate portion (131) and may extend from the groove toward the outer surface of the turning plate portion (141). Hereinafter, an example in which the first turning oil supply portion (1911) extends from the upper surface of the inner surface side of the turning plate portion (141) toward the outer surface is illustrated, but for convenience, it will be described as extending from the inner surface of the first turning oil supply portion (1911) toward the outer surface.

Specifically, one end of the first orbital oil supply unit (1911) is opened to the inner surface (more precisely, the upper surface on the inner surface) of the orbital scroll (140), and the other end of the first orbital oil supply unit (1911) may extend laterally (for convenience, this may be understood as the radial direction) toward the outer surface of the orbital scroll (140). However, one end of the first orbital oil supply unit (1911) is formed by penetrating the inner surface of the orbital scroll (140) so as to be connected to the oil path (126) of the rotation shaft (125), whereas the other end of the first orbital oil supply unit (1911) may be closed using a separate stopper member (not shown) even if it penetrates the outer surface of the orbital scroll (140). Accordingly, the other end of the first turning refueling unit (1911) is not connected to the intermediate pressure chamber (Sm) and can be blocked from the intermediate pressure chamber (Sm).

In addition, the first turning oil supply unit (1911) may be formed at a position where it does not axially interfere with the turning-side keyway (1411) of the old ring (170) provided on one side of the turning plate (141) when projected in the axial direction, that is, at a predetermined interval on one side of the circumferential direction of the turning-side keyway (1411). Accordingly, by suppressing interference between the first turning oil supply unit (1911) and the turning-side keyway (1411), the thickness of the turning plate (141) may be maintained thin, while the first turning oil supply unit (1911) may be formed in the middle of the turning plate (141).

In addition, the inner diameter (D11) of the first turning oil refueling part (1911) can be formed larger than the inner diameter (D12) of the second turning oil refueling part (1912) to be described later. Accordingly, the length of the first turning oil refueling part (1911) can be formed longer than the length of the second turning oil refueling part (1912) while being easily processed.

Although not shown in the drawing, a pressure reducing member (not shown) may be inserted into the interior of the first turning oil refueling unit (1911). In this case, the inner diameter (D11) of the first turning oil refueling unit (1911) may be formed wide while increasing the pressure reducing effect in the first turning oil refueling unit (1911), thereby lowering the pressure of the oil flowing into the compression chamber (V) to an appropriate pressure.

The second turning refueling unit (1912) can be formed by being connected to the first turning refueling unit (1911) and penetrating longitudinally toward the fixed scroll (150).

Specifically, one end of the second turning oil supply unit (1912) is connected to the first turning oil supply unit (1911), and the other end of the second turning oil supply unit (1912) may extend axially toward and penetrate the fixed scroll (150). For example, one end of the second turning oil supply unit (1912) may be connected to the first turning oil supply unit (1911), and the other end of the second turning oil supply unit (1912) may penetrate the lower surface of the turning plate unit (141) forming the thrust surface (i.e., the first thrust surface) (140a) of the turning scroll (140). Accordingly, the second turning oil supply unit (1912) may be opened to the first thrust surface (140a) at a position that does not overlap the compression chamber (V).

In addition, the inner diameter (D12) of the second turning oil refueling unit (1912) may be formed smaller than the inner diameter (D11) of the first turning oil refueling unit (1911) as described above. In other words, the length of the second turning oil refueling unit (1912) may be formed shorter than the length of the first turning oil refueling unit (1911), but the inner diameter (D12) of the second turning oil refueling unit (1912) may be formed smaller than the inner diameter (D11) of the first turning oil refueling unit (1911). Accordingly, the depressurization effect in the second turning oil refueling unit (1912) may be increased to lower the oil pressure flowing into the compression chamber (V) to an appropriate pressure.

Referring to FIGS. 2 and 3, the third turning oil supply unit (1913) is connected to the second turning oil supply unit (1912) and can extend laterally from the first thrust surface (140a), which is the lower surface of the turning plate (141).

Specifically, the third turning oil supply unit (1913) may be extended circumferentially from the other end of the second turning oil supply unit (1912) facing the fixed scroll (150). In other words, the third turning oil supply unit (1913) may be formed in a non-circular cross-sectional shape when projected in the axial direction, but may be formed as a groove that is sunken to a preset depth in the lower surface of the turning plate portion (141) forming the first thrust surface (140a). For example, one end of the third turning oil supply unit (1913) may be connected to the other end of the second turning oil supply unit (1912), and the other end of the third turning oil supply unit (1913) may be extended circumferentially so as to be connected to the third fixed oil supply unit (1923) of the second oil supply passage (192) to be described later.

In addition, the third turning oil supply unit (1913) may be extended to a position where it axially overlaps the turning-side keyway (1511) when projected in the axial direction. However, the third turning oil supply unit (1913) may be formed to a depth that does not communicate with the turning-side keyway (1511). Accordingly, the third turning oil supply unit (1913) may be extended to a position as close as possible to the second oil supply passage (192) described later, while suppressing the first oil supply passage (191) from communicating with the intermediate pressure chamber (Sm) through the turning-side keyway (1511).

In addition, the width (D13) of the third turning oil refueling part (1913) may be formed to be smaller than or equal to the inner diameter (D12) of the second turning oil refueling part (1912). In other words, the third turning oil refueling part (1913) may be formed to have the same width (D13) between both ends, but smaller than or equal to the inner diameter (D12) of the second turning oil refueling part (1912). This embodiment illustrates an example in which the width (D13) of the third turning oil refueling part (1913) is formed to be the same as the inner diameter (D12) of the second turning oil refueling part (1912). Accordingly, while securing the oil refueling passage (190) in the relatively narrow first thrust surface (140a) of the orbiting scroll (140), it is possible to secure the sealing distance between the oil refueling passage (190) and the outer surface of the orbiting plate (141).

Meanwhile, referring to FIGS. 2, 5, and 6, the second refueling passage (192) includes a first fixed refueling unit (1921), a second fixed refueling unit (1922), a third fixed refueling unit (1923), and a fourth fixed refueling unit (1924). The first fixed refueling unit (1921) and the fourth fixed refueling unit (1924) can be understood as connecting the inlet of the second refueling passage (192), the third fixed refueling unit (1923) can be understood as connecting the outlet of the second refueling passage (192), and the second fixed refueling unit (1922) can be understood as connecting the inlet and outlet of the second refueling passage (192).

The first fixed refueling portion (1921) can be formed to be recessed in the fixed side wall portion (152) to a preset depth in the longitudinal direction.

Specifically, one end of the first fixed oil supply portion (1921) is opened to the thrust surface (i.e., the second thrust surface) (150a) of the fixed scroll (150) facing the thrust surface (140a) of the orbiting scroll (140), and the other end of the first fixed oil supply portion (1921) may extend longitudinally (which may be conveniently understood as the axial direction) toward the lower surface of the fixed side wall portion (152) opposite the other side of the fixed scroll (150), i.e., the second thrust surface (150a). However, the first fixed oil supply portion (1921) may also be formed as a groove having a preset depth along the axial direction in the second thrust surface (150a), or may penetrate the fixed side wall portion (152) but cover the lower surface using a separate plug. This embodiment shows an example in which the first fixed oil supply part (1921) is sunken into the second thrust surface (150a) to a preset depth.

In addition, one end of the first fixed oil supply unit (1921) may be formed at a position that is always covered by the lower surface of the turning plate unit (141), that is, the first thrust surface (140a). For example, one end of the first fixed oil supply unit (1921) may be formed within the turning trajectory range of the turning plate unit (141). Accordingly, one end of the first fixed oil supply unit (1921) is formed at a position that axially overlaps the turning plate unit (141) during the turning movement of the turning plate unit (141), and thus may not be connected to the intermediate pressure chamber (Sm) like the other end of the first turning oil supply unit (1911) described above, but may be blocked from the intermediate pressure chamber (Sm).

In addition, the inner diameter (D21) of the first fixed oil supply unit (1921) may be formed smaller than the width (D24) of the fourth fixed oil supply unit (1924) to be described later. Accordingly, not only can the first fixed oil supply unit (1921) be formed on the fixed side wall unit (152) without interfering with surrounding components such as a bypass hole (1512) for variable capacity, but also the pressure reduction effect in the first fixed oil supply unit (1921) can be increased to reduce the pressure of the oil flowing into the compression chamber (V) to an appropriate pressure.

Although not shown in the drawing, a pressure reducing member (not shown) may be inserted into the interior of the first fixed oil supply unit (1921). In this case, the inner diameter (D21) of the first fixed oil supply unit (1921) may be formed as wide as possible within a range that does not interfere with surrounding components, while increasing the pressure reducing effect in the first fixed oil supply unit (1921) so that the pressure of the oil flowing into the compression chamber (V) can be reduced to an appropriate pressure.

The second fixed refueling unit (1922) can be formed to be connected to the first fixed refueling unit (1921) and recessed in the horizontal direction to a preset depth.

Specifically, one end of the second fixed oil supply unit (1922) is connected to the first fixed oil supply unit (1921), and the other end of the second fixed oil supply unit (1922) may extend transversely (which may be conveniently understood as a radial direction) toward the compression chamber (V). For example, one end of the second fixed oil supply unit (1922) may penetrate the outer surface of the fixed scroll (150), and the other end of the second fixed oil supply unit (1922) may extend to a preset depth by continuously groove-dig the fixed side wall unit (152) and the fixed plate unit (151). In this case, one end of the second fixed oil supply unit (1922) may be sealed using a separate stopper member (not shown), and the other end of the second fixed oil supply unit (1922) may be formed in a blocked shape by groove-digng up to the middle of the fixed plate unit (151). Accordingly, both ends of the second fixed refueling unit (1922) can be formed in a blocked shape.

In addition, the second fixed oil supply unit (1922) may be formed transversely, but may be formed in a direction that is inclined obliquely with respect to the axis center (O). Accordingly, the second oil supply passage (192) including the second fixed oil supply unit (1922) may be connected to the compression chamber (V) by avoiding the bypass hole (1512) penetrating the fixed plate part (151) as well as the fastening hole (1522) penetrating the fixed side wall part (152).

In addition, the inner diameter of the second fixed oil supply unit (1922) can be formed smaller than the width (D24) of the fourth fixed oil supply unit (1924) to be described later. Accordingly, the second fixed oil supply unit (1922) can be formed on the fixed side wall unit (152) without interfering with surrounding components such as a bypass hole (1512) for variable capacity, and the pressure of the oil flowing into the compression chamber (V) can be reduced to an appropriate pressure by increasing the pressure reduction effect in the first fixed oil supply unit (1921).

Although not shown in the drawing, a pressure reducing member (not shown) may be inserted into the interior of the second fixed oil supply unit (1922). In this case, the inner diameter of the second fixed oil supply unit (1922) may be formed as wide as possible within a range that does not interfere with surrounding components, while increasing the pressure reducing effect in the second fixed oil supply unit (1922) to reduce the pressure of the oil flowing into the compression chamber (V) to an appropriate pressure.

The third fixed oil supply unit (1923) can be formed by longitudinally penetrating the interior of the fixed plate unit (151) so as to be connected to the second fixed oil supply unit (1922) and to the compression chamber (V).

Specifically, one end of the third fixed oil supply unit (1923) is connected to the other end of the second fixed oil supply unit (1922), and the other end of the third fixed oil supply unit (1923) can be connected to the compression chamber (V) by penetrating the upper surface of the fixed plate part (151) forming the compression chamber (V). Accordingly, the second oil supply passage (192) can connect between the first oil supply passage (191) connected to the oil passage (126) of the rotating shaft (125) and the compression chamber (V).

The other end of the third fixed fuel supply section (1923) forming the exit of the second fuel supply passage (192) may be connected to the compression chamber (V) as described above, but may be formed to be connected to the compression chamber (V) as soon as possible after suction is completed and compression is initiated, that is, immediately after the suction completion angle or/and the compression start angle, for example, within a range of 10° to 20° after the suction completion angle or/and the compression start angle (α). Accordingly, even in low-pressure ratio operation where the pressure ratio is 1.1 or less, the oil stored in the oil storage space (S11) of the casing (110) can be smoothly introduced into the compression chamber (V).

However, the other end of the third fixed oil supply unit (1923) may be connected to a compression chamber (V) having a lower pressure than the pressure of the compression chamber (V) to which one end of the intermediate pressure passage (180) forming the entrance of the intermediate pressure passage (180) is connected as described above. Accordingly, a large pressure difference is generated between the internal space (110a) of the casing (110) and the compression chamber (V), so that even in low pressure ratio operation, the oil stored in the internal space (110a) of the casing (110) can be smoothly supplied to the compression chamber (V).

In addition, the other end of the third fixed oil supply unit (1923) is formed in the center between the outermost fixed wrap (154) and the fixed wrap (154) radially facing the outermost fixed wrap, and the inner diameter (D23) of the third fixed oil supply unit (1923) can be formed smaller than the wrap thickness of the orbiting wrap (142). Accordingly, when the orbiting wrap (142) rotates, the other end of the third fixed oil supply unit (1923) is alternately connected to the compression chambers (V) on both sides, so that oil can be evenly supplied to the compression chambers (V) on both sides.

In addition, the inner diameter (D23) of the third fixed oil supply unit (1923) can be formed smaller than the width (D24) of the fourth fixed oil supply unit (1924) to be described later. Accordingly, not only can the second fixed oil supply unit (1922) be formed on the fixed side wall unit (152) without interfering with surrounding components such as a bypass hole (1512) for variable capacity, but also the pressure reduction effect in the first fixed oil supply unit (1921) can be increased to reduce the pressure of the oil flowing into the compression chamber to an appropriate pressure.

Referring to FIGS. 2 and 5, the fourth fixed oil supply unit (1924) may be connected to one end of the first fixed oil supply unit (1921) and formed on the second thrust surface (150a) of the fixed scroll (150).

Specifically, the fourth fixed oil supply unit (1924) may be formed as a groove having a preset depth in the second thrust surface (150a) forming the upper surface of the fixed side wall portion (152) and communicating with one end of the first fixed oil supply unit (1921) facing the orbiting scroll (140). Accordingly, the fourth fixed oil supply unit (1924) may be communicated with the third orbiting oil supply unit (1913) forming the first oil supply passage (191).

In addition, the fourth fixed oil supply portion (1924) may be formed to have a non-circular cross-sectional shape when projected in the axial direction, but the width (D24) of the fourth fixed oil supply portion (1924) may be formed to be larger than the inner diameter (D21) of the first fixed oil supply portion (1921). For example, the fourth fixed oil supply portion (1924) may be extended along the fixed wrap (154) in a first transverse direction that is approximately similar to the forming direction (or circumferential direction) of the fixed wrap (154), and a length (second transverse length) (L22) in a second transverse direction that is approximately orthogonal to the first transverse direction may be formed to be shorter than the first transverse length (L21) but larger than the inner diameter (D21) of the first fixed oil supply portion (1921). Accordingly, the width (or cross-sectional area) (D24) of the fourth fixed refueling unit (1924) is formed to be larger than the inner diameter (or cross-sectional area) (D21) of the first fixed refueling unit (1921), so that the second refueling passage (192) including the fourth fixed refueling unit (1924) can be continuously and uninterruptedly connected to the first refueling passage (191) including the third rotating refueling unit (1913).

In addition, the fourth fixed oil supply unit (1924) may be formed to have a larger cross-sectional area on the side farther from the first fixed oil supply unit (1921) than on the side adjacent to the first fixed oil supply unit (1921). Accordingly, the fourth fixed oil supply unit (1924) may be formed wider on the relatively wider side of the second thrust surface (150a) of the fixed scroll (150), thereby making the size of the fourth fixed oil supply unit (1924) as large as possible. In addition, this may be more advantageous in ensuring that the second oil supply passage (192) is continuously connected to the first oil supply passage (191).

In addition, the width (D24) of the fourth fixed refueling unit (1924) may be formed to be larger than the width (D13) of the third rotating refueling unit (1913) forming the first refueling passage (191). In other words, the second thrust surface (150a) of the fixed scroll (150) may be formed to have a relatively larger clearance area considering the sealing distance than the first thrust surface (140a) of the orbiting scroll (140). Accordingly, the width (D24) of the fourth fixed refueling unit (1924) may be formed to be larger than the width of the third rotating refueling unit (1913). Accordingly, even if the width (D13) of the third turning oil supply unit (1913) provided on the first thrust surface (140a) of the turning plate (141) is formed smaller than the inner diameter (D11) of the first turning oil supply unit (1911), the width (D24) of the fourth fixed oil supply unit (1924) is formed larger than the width (D13) of the third turning oil supply unit (1913), so that the third turning oil supply unit (1913) can be continuously connected with the fourth fixed oil supply unit (1924) without interruption.

FIG. 7 is a plan view showing the state in which the rotating scroll and the fixed scroll are combined from the fixed scroll side in this embodiment, and FIG. 8 is a schematic diagram showing the relationship between the third rotating oil supply unit and the fourth fixed oil supply unit according to the change in the rotation angle in FIG. 7 in an enlarged manner.

Referring to FIG. 7, as described above, since the first oil passage (191) is directly connected to the second oil passage (192) without passing through the intermediate pressure chamber (Sm), oil stored in the oil storage space (S11) of the casing (110) is directly supplied to the compression chamber (V) through the first oil passage (191) and the second oil passage (192).

At this time, the third turning oil supply part (1913) forming part of the first oil supply passage (191) is formed on the first thrust surface (140a) of the turning scroll (140), and thus, when the turning plate part (141) turns, it performs a turning movement with respect to the fourth fixed oil supply part (1924) forming part of the second oil supply passage (192). Accordingly, the third turning oil supply part (1913) and the fourth fixed oil supply part (1924) may be spaced apart from each other depending on their shape or formation position.

However, as explained above, the third turning refueling part (1913) is elongated in the circumferential direction, and the fourth fixed refueling part (1924) is formed to be elongated in the circumferential direction like the third turning refueling part (1913) and also wide in the radial direction, and is formed at a position overlapping the third turning refueling part (1913) in the axial direction. Then, even if the third turning refueling part (1913) performs a turning movement, at least a part of the third turning refueling part (1913) is located within the formation range of the fourth fixed refueling part (1924).

Then, as shown in FIG. 8, the third rotating oil supply unit (1913) and the fourth fixed oil supply unit (1924) are continuously connected without interruption. Then, the oil stored in the oil storage space (S11) of the casing (110) can be directly supplied to the compression chambers (V1) (V2) on both sides through the oil supply passage (190) that alternately communicates with the compression chambers (V1) (V2) on both sides without passing through the intermediate pressure chamber (Sm). Then, even in the low pressure ratio operation where the pressure difference between the internal space (110a) of the casing (110) and the pressure of the compression chamber (V) is 1.3 or less, or even 1.1 or less, compression chamber oil supply using the differential pressure can be made possible. Through this, low pressure ratio operation is made possible in a scroll compressor equipped with a hybrid wrap and an air conditioner applying the same, and the efficiency of the scroll compressor and the air conditioner can be increased accordingly.

Meanwhile, as explained above, in the case of a scroll compressor using a differential pressure oil supply method, the temperature of the suction-side wrap rapidly increases under abnormal operating conditions such as a rapid start, which may cause excessive thermal expansion of the suction-side swirl wrap having a relatively large coefficient of thermal expansion. Due to this thermal expansion, friction loss and/or wear between the leading edge of the swirl wrap and the fixed plate portion facing it may significantly increase, which may lower the compression efficiency and reliability.

Accordingly, in this embodiment, a fuel groove communicating with a fuel passage is formed on the suction-side leading edge of the turning wrap so that some of the oil supplied to the compression chamber through the fuel passage is supplied to the suction-side leading edge of the turning wrap. Accordingly, oil is continuously supplied between the suction-side leading edge of the turning wrap and the fixed plate portion facing it, so that damage to the suction-side leading edge of the turning wrap can be suppressed even under abnormal operating conditions such as rapid starting.

FIG. 9 is a plan view showing the state in which the orbiting scroll and the fixed scroll are combined from the orbiting scroll side in this embodiment, and FIG. 10 is a schematic diagram explaining the communication relationship between the fuel passage and the fuel groove in FIG. 9.

Referring again to FIGS. 1 and 2, the refueling groove (195) according to the present embodiment may be formed to be sunken to a preset depth in the direction of the wrap height into the leading edge surface (142a) of the pivot wrap (142) facing the fixed plate portion (151). For example, the depth of the refueling groove (195) may be formed to be less than half of the wrap height. Accordingly, the reduction in wrap rigidity due to the refueling groove (195) may be suppressed.

The refueling groove (195) may be formed to be in communication with the second refueling passage (192). For example, the refueling groove (195) may be formed to be in communication periodically and/or continuously with the third fixed refueling portion (1923) forming the outlet of the second refueling passage (192). In this embodiment, an example in which the refueling groove (195) is in communication periodically with the third fixed refueling portion (1923) is illustrated. In other words, as shown in FIG. 9, the inner diameter (D23) of the third fixed refueling portion (1923) may be formed to be smaller than the wrap thickness (T1) of the turning wrap (142), and the width (D5) of the refueling groove (195) may be formed to be smaller than or equal to the inner diameter (D23) of the third fixed refueling portion (1923). Accordingly, not only is it possible to prevent the third fixed refueling unit (1923) from being simultaneously connected to both compression chambers (V1) (V2), but also to prevent damage to the refueling lap (142) by ensuring the width (D6) of the side end faces (142a1) of the refueling lap (142) located on both sides in the width direction of the refueling groove (195) as wide as possible.

In addition, the refueling groove (195) may be extended along the formation direction of the turning wrap (142), but may be formed within a range including the suction completion angle based on the rotation angle of the rotation axis (125) at the outer end (suction end) of the turning wrap (142). In other words, as shown in FIGS. 9 and 10, the oil supply groove (195) is formed in an arc shape when projected in the axial direction, but the first stage (195a) is spaced apart from the outer end of the orbiting wrap (142) by a sealing length (L5), and the second stage (195b) is formed at a position that is approximately 300° from the outer end (suction end) of the orbiting wrap (142), for example, approximately 270° so as to be positioned on the same axis as the third fixed oil supply unit (1923) when the orbiting scroll (140) and the fixed scroll (150) are aligned, in other words, one end of the third fixed oil supply unit (1923) that is connected to the compression chamber (V) is positioned within the range of the orbiting radius of the oil supply groove (195). Accordingly, the oil supply home (195) is connected to the second oil supply passage (192) at least once per rotation of the orbiting scroll (140), that is, per rotation of the rotation shaft (125), during the orbiting movement of the orbiting scroll (140), so that some of the oil supplied to the compression chamber (V) through the oil supply passage (190) can flow into the oil supply home (195).

In addition, the oil refueling groove (195) may be formed with the same cross-sectional area along the formation direction of the turning wrap (142). In other words, the oil refueling groove (195) may be formed to have the same width (D5) and/or depth (not shown) along the shape direction of the turning wrap (142). Accordingly, the oil refueling groove (195) may be easily formed while maintaining the amount of oil accommodated in the oil refueling groove (195) uniformly.

In addition, the refueling groove (195) may be formed to be symmetrical in the width direction with respect to the center line of the turning wrap (142). In other words, the widths (D6) of the side end faces (142a1) of the turning wrap (142) on both sides may be formed to be the same with respect to the refueling groove (195). Accordingly, the friction loss and/or wear of the end face (142a) of the turning wrap (142) may be further reduced, and the reliability may be further increased.

In the case where a fuel groove (195) is formed on the suction side end face (or outer end face) (142a) of the turning wrap (142) to communicate with the second fuel passage (192), as described above, a portion of the oil supplied to the compression chamber (V) through the fuel passage (190) can flow into the fuel groove (195).

Then, the oil spreads along the formation direction of the oil supply groove (195) and lubricates the space between the suction-side front end face (142a) of the rotating wrap (142) made of a material with a relatively high coefficient of thermal expansion and one side of the fixed plate part (151) facing it.

Then, even if the temperature of the compression section (C) rises significantly due to friction between the laps under abnormal driving conditions such as rapid starting, and the suction-side lap deformation of the turning lap (142) increases significantly, the friction loss and/or wear between the suction-side leading edge surface (142a) of the turning lap (142) and one side of the fixed plate portion (151) facing it can be reduced.

In this way, when the orbiting scroll is manufactured from a material having a larger coefficient of thermal expansion than that of the fixed scroll, even when abnormal operating conditions such as rapid starting occur, friction loss and/or wear between the suction-side leading edge of the orbiting scroll and the fixed plate portion can be suppressed, thereby improving the compression efficiency and/or reliability of the scroll compressor in which the orbiting scroll is manufactured from a material having a larger coefficient of thermal expansion than that of the fixed scroll.

Meanwhile, there are other examples of refueling homes as follows.

That is, in the above-described embodiment, the cross-sectional area of the fuel groove is formed equally along the formation direction of the swirl wrap, but in some cases, the cross-sectional area of the fuel groove may be formed differently along the formation direction of the swirl wrap.

Fig. 11 is a plan view of a rotating scroll shown to explain another embodiment of a refueling home.

Referring to Fig. 11, the basic configuration and the resulting operational effects of the fuel passage and fuel home (195) according to the present embodiment are similar to those of the embodiment of Fig. 9 described above, and therefore, the description thereof will be replaced with the description of the embodiment of Fig. 9.

However, the refueling groove (195) according to the present embodiment may include a first refueling groove (1951) and a second refueling groove (1952). The first refueling groove (1951) is a part directly connected to the exit of the second refueling passage (192), for example, the third fixed refueling part (1923), and the second refueling groove (1952) is a part indirectly connected to the third fixed refueling part (1923) through the first refueling groove (1951). Accordingly, the first refueling groove (1951) and the second refueling groove (1952) may be formed to be connected to each other.

The first refueling groove (1951) is formed in an arc shape, and may be formed to have a first cross-sectional area that is the same along the formation direction of the turning wrap (142). Accordingly, in the section where the first refueling groove (1951) is formed, the width (D6) of the side end face (142a1) of the turning wrap (142) excluding the first refueling groove (1951) is maintained uniformly, thereby reducing friction loss and/or wear on the end face (142a) of the turning wrap (142) and increasing reliability.

In this case, the first refueling groove (1951) may be formed to be symmetrical in the width direction with respect to the center line of the turning wrap (142). Accordingly, the widths of the two side end faces (142a1) of the turning wrap (142) centered on the first refueling groove (1951) are formed to be the same, thereby further reducing friction loss and/or wear on the end face (142a) of the turning wrap (142) and further increasing reliability.

The second refueling groove (1952) is formed in an arc shape, but may be formed to have the same second cross-sectional area along the formation direction of the turning wrap (142). In other words, the second refueling groove (1952) may be formed to have the same depth as the first refueling groove (1951), but the width (D52) of the second refueling groove (1952) may be formed to be larger than the width (D51) of the first refueling groove (1951). Accordingly, the amount of oil stored in the second refueling groove (1952) becomes greater than the amount of oil stored in the first refueling groove (1951). In this way, in the section where the second refueling groove (1952) is formed, the width (D6) of the side edge (142a1) of the turning lap (142) excluding the second refueling groove (1952) is maintained uniformly, thereby reducing friction loss and/or wear on the edge (142a) of the turning lap (142) and increasing reliability.

In this case, the cross-sectional area of the second refueling groove (1952) is formed to be larger than that of the first refueling groove (1951), but the second refueling groove (1952) can be formed to be expanded by the same width in both width directions with respect to the first refueling groove (1951). Accordingly, while the second refueling groove (1952) is expanded larger than the first refueling groove (1951), the width (D6) of the side end faces (142a1) of the turning wrap (142) is formed to be the same with respect to the second refueling groove (1952), thereby further reducing friction loss and/or wear with respect to the end face (142a) of the turning wrap (142) and further increasing reliability.

As described above, when the cross-sectional area of the second fuel groove (1952) is formed to be larger than that of the first fuel groove (1951), the amount of fuel supplied to a portion with relatively large wrap deformation is expanded, thereby further reducing friction loss and/or wear between the leading edge (142a) of the turning wrap (142) and the fixed plate portion (151) facing it, and further increasing reliability.

Although not shown in the drawing, the width (D52) of the second oil refueling groove (1952) and the width (D51) of the first oil refueling groove (1951) may be formed to be the same, and the depth of the second oil refueling groove (1952) may be formed to be deeper than the depth of the first oil refueling groove (1951). Accordingly, while the amount of oil in the second oil refueling groove (1952) is stored to be greater than the amount of oil in the first oil refueling groove (1951), the width of both end faces in the section where the second oil refueling groove (1952) is formed may be formed to be the same as the width of both side end faces (142a1) in the section where the first oil refueling groove (1951) is formed. Through this, the lubrication effect in the second oil refueling groove (1952) can be increased, while also increasing the reliability of the turning wrap (142).

Meanwhile, there is another example of a refueling home as follows.

That is, in the embodiment of Fig. 10 described above, the cross-sectional area of the second fuel groove is formed to be larger than that of the second fuel groove, but in some cases, the cross-sectional area of the second fuel groove may be formed to be smaller than that of the second fuel groove.

Fig. 12 is a plan view of a pivot scroll shown to illustrate another embodiment of a refueling home.

Referring to Fig. 12, the basic configuration and the resulting operational effects of the fuel passage (190) and the fuel groove (195) according to the present embodiment are similar to those of the embodiments of Fig. 9 and Fig. 11 described above, and therefore, the description of the embodiments of Fig. 9 and Fig. 11 will be replaced. In particular, the cross-sectional area of the fuel groove (195) according to the present embodiment may be formed differently along the formation direction of the rotating wrap (142), as in the embodiment of Fig. 11.

However, the refueling groove (195) according to the present embodiment may include a first refueling groove (1951) and a second refueling groove (1952), but the cross-sectional area of the second refueling groove (1952) may be formed smaller than the cross-sectional area of the first refueling groove (1951). For example, the width (D52) of the second refueling groove (1952) may be formed smaller than the width (D51) of the first refueling groove (1951). Accordingly, the width (D6) of the side surface (142a1) of the turning wrap (142) excluding the second refueling groove (1952) in the section where the second refueling groove (1952) is formed may be formed larger than the width (D5) of the side surface (142a1) of the turning wrap (142) excluding the first refueling groove (1951) in the section where the first refueling groove (1951) is formed.

As described above, when the cross-sectional area of the second oil refueling groove (1952) is formed smaller than that of the first oil refueling groove (1951), the side edge section (142a1) of the turning wrap (142) can be smoothly lubricated through the second oil refueling groove (1952) in the section where the second oil refueling groove (1952) is formed, while the reliability of the turning wrap (142) in the section where the thermal deformation is relatively greater can be increased.

Although not shown in the drawing, the width (D52) of the second fuel groove (1952) and the width (D51) of the first fuel groove (1951) may be formed to be the same, and the depth of the second fuel groove (1952) may be formed shallower than the depth of the first fuel groove (1951). Accordingly, the cross-sectional height of the section where the second fuel groove (1952) is formed may be formed lower than the cross-sectional height of the section where the first fuel groove (1951) is formed, and the lap strength of the section where the second fuel groove (1952) is formed may be improved compared to the lap strength of the section where the first fuel groove (1951) is formed. Through this, the lubrication effect in the second fuel groove (1952) where relatively large thermal deformation occurs may be secured, while the reliability of the swirl lap (142) may be improved.

Claims (22)

A casing in which a certain amount of oil is stored; A rotating shaft provided in the internal space of the above casing and having an oil passage formed therein; A turning scroll having a turning plate part coupled to the above-mentioned rotating shaft to perform a turning motion, and a turning wrap provided on one side of the turning plate part; A fixed scroll having a fixed wrap provided on one side of the fixed plate part to be connected to the above-mentioned rotating wrap to form a compression chamber; and A main frame is provided on the opposite side of the fixed scroll with the orbiting scroll in between and is fixed to the internal space of the casing, and forms an intermediate pressure chamber together with the orbiting scroll and the fixed scroll to pressurize the orbiting scroll toward the fixed scroll. In the above fixed scroll, an oil supply passage is formed to connect the intermediate pressure chamber and the compression chamber and guide a portion of the oil in the intermediate pressure chamber to the compression chamber. A fuel groove is formed on the front end of the above-mentioned rotating wrap facing the above-mentioned fixed plate part to communicate with the above-mentioned fuel passage. The above refueling home is, A scroll compressor that is sunk to a preset depth along the wrap height direction and extends along the wrap formation direction. In the first paragraph, The above refueling home is, A scroll compressor in which the rotation angle of the rotation axis is formed within a range of up to 300° inwardly along the formation direction of the rotation wrap from a point spaced apart from the outer end of the rotation wrap by a preset sealing length. In the first paragraph, One end of the fuel supply passage connected to the compression chamber is, A scroll compressor in which at least a portion of each rotation of the above-described orbiting scroll is formed within the rotation radius range of the above-described fuel receptacle. In the third paragraph, The inner diameter of the fuel passage connected to the compression chamber is formed smaller than the thickness of the rotating wrap. A scroll compressor in which the width of the above-mentioned fuel groove is formed to be smaller than or equal to the inner diameter of the above-mentioned fuel passage. In the first paragraph, The above refueling home is, A scroll compressor formed with the same cross-sectional area along the formation direction of the above-mentioned rotating wrap. In the first paragraph, The above refueling home is, A scroll compressor formed with different cross-sectional areas along the formation direction of the above-mentioned rotating wrap. In Article 6, The above refueling home is, A first refueling home connected to the above refueling passage; and It includes a second refueling groove that is connected to the first refueling groove and formed on the outer side of the first refueling groove along the formation direction of the turning wrap. A scroll compressor in which the cross-sectional area of the second oil refueling groove is formed larger than the cross-sectional area of the first oil refueling groove. In Article 6, The above refueling home is, A first refueling home connected to the above refueling passage; and It includes a second refueling groove that is connected to the first refueling groove and formed on the outer side of the first refueling groove along the formation direction of the turning wrap. A scroll compressor in which the cross-sectional area of the second oil refueling groove is formed smaller than the cross-sectional area of the first oil refueling groove. In any one of claims 1 to 8, A scroll compressor in which the above-mentioned orbiting scroll is formed of a material having a larger coefficient of thermal expansion than that of the above-mentioned fixed scroll. In Article 9, The above refueling route is, A scroll compressor formed so as to be separated from the intermediate pressure chamber and to communicate between the oil passage and the compression chamber. In Article 10, The above refueling route is, A first-grade oil passage provided in the above-mentioned rotary scroll, one end of which is connected to the oil passage of the above-mentioned rotary shaft; and A scroll compressor including a second grade oil passage provided on the above fixed scroll, one end of which is connected to the first grade oil passage and the other end of which is connected to the compression chamber. In Article 11, The other end of the above first-class oil distribution channel and one end of the above second-class oil distribution channel, A scroll compressor in which at least a portion of the above-mentioned orbiting scroll is continuously connected during the orbiting motion. In Article 11, The other end of the above first-grade oil passage penetrates the first thrust surface of the above-mentioned orbiting scroll facing the above-mentioned fixed scroll, A scroll compressor in which one end of the second fuel passage penetrates the second thrust surface of the fixed scroll facing the orbiting scroll. In Article 13, A scroll compressor in which at least one of the other end of the first-grade oil passage and one end of the second-grade oil passage facing it is formed with a non-circular cross-sectional shape. In Article 14, The other end of the above first-grade oil passage extends along the circumferential direction from the above first thrust surface, A scroll compressor in which one end of the second fuel passage extends along the circumferential direction from the second thrust surface. In Article 15, A scroll compressor in which the cross-section of one end of the second-grade oil passage is formed wider than the cross-section of the other end of the first-grade oil passage. In Article 11, The above first-class distribution route is: A first rotary oil supply section, one end of which is connected to the above oil path and the other end of which extends toward the outer surface of the above rotary scroll; A second rotary refueling section, one end of which is connected to the first rotary refueling section and the other end is opened toward the fixed scroll; and A scroll compressor including a third rotary oil supply section extending circumferentially from the other end of the second rotary oil supply section facing the fixed scroll and communicating with the second oil supply passage. In Article 17, The radial width of the third turning refueling section is A scroll compressor having an inner diameter greater than or equal to the inner diameter of the second rotating oil supply section. In Article 18, The inner diameter of the above second turning oil refueling part is A scroll compressor having an inner diameter smaller than or equal to the inner diameter of the first turning oil supply section. In Article 11, The above second-class oil distribution route is: A first fixed fuel section is opened at a side facing the above-mentioned rotary scroll and connected to the above-mentioned first fuel passage, and the other end extends toward the other side of the above-mentioned fixed scroll; A second fixed oil supply unit, the other end of which is connected to the other end of the first fixed oil supply unit and the other end extends toward the compression chamber; A third fixed oil supply unit, which is connected to the second fixed oil supply unit at one end and is opened to be connected to the compression chamber at the other end; and A scroll compressor including a fourth fixed oil supply unit extending circumferentially from one end of the first fixed oil supply unit facing the above-described rotating scroll and communicating with the first oil supply passage. In Article 20, The radial width of the above fourth fixed oil supply section is A scroll compressor formed to have a larger inner diameter than the first fixed oil supply portion. In Article 20, The above 4th fixed fuel supply unit is, A scroll compressor in which a cross-sectional area on the side farther from the first fixed oil supply portion is formed larger than a cross-sectional area on the side adjacent to the first fixed oil supply portion.

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