KR20180083646A - Scroll compressor - Google Patents

Abstract

A scroll compressor according to the present invention includes: a casing; A drive motor; A rotating shaft coupled to the rotor of the driving motor to rotate together; An oil feeder provided on the rotary shaft for pumping oil stored in the casing; A frame provided to the drive motor; A first scroll provided on a side of the frame adjacent to the oil feeder on both sides in the axial direction, the first scroll having a first wrap; A second lap provided between the frame and the first scroll to form a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber in engagement with the first lap, Second scroll; An accumulator connected to the suction chamber of the compression chamber; And a check valve provided inside the accumulator for blocking fluid from flowing back in the direction of the accumulator from the compression chamber. Thus, when the compressor is stopped, the fluid discharged into the casing flows back to the compression chamber, .

Description

[0001] SCROLL COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly to a scroll compressor having a check valve for preventing reverse flow of refrigerant when the compressor is stopped.

The scroll compressor has a fixed scroll fixed to an inner space of the casing, and a fixed scroll is fixed to the fixed scroll while the orbiting scroll is engaged with the orbiting scroll of the fixed scroll and the orbiting scroll of the orbiting scroll, And forms a compression space of the pair.

In addition, the scroll compressor is widely used for refrigerant compression in an air conditioner or the like because it has a relatively high compression ratio as compared with other types of compressors, and smooth suction, compression, and discharge strokes of the refrigerant can be obtained and stable torque can be obtained. Recently, a high-efficiency scroll compressor having an eccentric load lowered and an operation speed of 180 Hz or higher has been introduced.

The scroll compressor may be divided into a low-pressure type in which the suction pipe communicates with the internal space of the casing and a high-pressure type in which the suction pipe directly communicates with the compression portion. In the case of the low-pressure type, the internal space of the casing is divided into a low-pressure suction space and a high-pressure discharge space, and in the case of a high-pressure type, the internal space of the casing forms a high-

In the scroll compressor, a discharge port is formed in the fixed scroll regardless of the low pressure type and the high pressure type, and a check valve is provided at the end of the discharge port. Accordingly, when the compressor is in operation, the compressed refrigerant opens the check valve and is discharged to the internal space of the casing forming the discharge space. On the other hand, when the compressor is stopped, the check valve is closed by the pressure of the internal space, Thereby preventing reverse rotation of the discharged refrigerant to the compression section, thereby preventing the second scroll from rotating in the reverse direction.

The scroll compressor may be divided into an upper compression type and a lower compression type according to the positions of the driving unit and the compression unit. If the compression unit is located above the driving unit, . Even in the case of the upper compression type and the lower compression type, it is generally the same to install the check valve at the end of the discharge port. For example, Korean Patent Publication No. 10-2016-0020190 discloses a lower compression scroll compressor.

However, when the check valve is provided at the discharge port of the compression unit in the above scroll compressor, it is advantageous to prevent the reverse rotation of the orbiting scroll by blocking the reverse flow of refrigerant already discharged at the time of stop of the compressor, Pressure refrigerant discharged from the compression chamber is prevented from being introduced into the compression section (precisely, the compression chamber) which is in a relatively low-pressure state, thereby causing an adverse effect of hindering the pneumatic pressure between the discharge space and the compression chamber. Accordingly, when the compressor attempts to restart, the pressure in the compression chamber overcomes the elastic force of the check valve and the pressure in the discharge space, and it takes a considerable time to discharge the compressed refrigerant while pushing the check valve. As a result, The efficiency and reliability of the compressor are deteriorated.

Further, when the check valve is installed at the discharge port of the compression unit as described above, the intermediate pressure refrigerant compressed by the compression unit at the time of stopping the compressor flows back toward the suction pipe, so that the pressure difference between the condenser and the evaporator of the refrigeration cycle may be reduced. This is because, even if the fan of the refrigeration cycle is operated for a time period during which the compressor is stopped, the latent heat of the refrigeration cycle device is low and the efficiency of the refrigeration cycle device is deteriorated.

Korean Patent Publication No. 10-2016-0020190

It is an object of the present invention to provide a scroll compressor in which the internal space of the casing and the compression section can be quickly pneumatically regressed when the refrigeration cycle apparatus is stopped.

It is another object of the present invention to provide a scroll compressor capable of increasing the efficiency of the refrigeration cycle apparatus by allowing the refrigeration cycle apparatus to perform heat exchange during the time when the compressor is stopped.

In order to achieve the object of the present invention, a scroll compressor in which the discharge side is always communicated with the inner space of the casing with respect to the compression chamber, while a check valve is provided on the suction side so that the internal space of the casing is communicated with the compression chamber when the compressor is stopped Can be provided.

Here, an accumulator assembled to a suction pipe is provided outside the casing, and the check valve is installed inside the accumulator so that the check valve can be modularized with the accumulator.

In order to achieve the object of the present invention, A driving motor provided in an inner space of the casing; A rotating shaft coupled to the rotor of the driving motor to rotate together; An oil feeder provided on the rotary shaft for pumping oil stored in the casing; A frame provided to the drive motor; A first scroll provided on a side of the frame adjacent to the oil feeder on both sides in the axial direction, the first scroll having a first wrap; A second lap provided between the frame and the first scroll to form a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber in engagement with the first lap, Second scroll; An accumulator connected to the suction chamber of the compression chamber; And a check valve provided inside the accumulator to prevent the fluid from flowing back toward the accumulator in the compression chamber.

Here, the first scroll may have a discharge port communicating between the discharge chamber and the internal space of the casing, and the discharge port may be always open to the internal space of the casing.

The first scroll may have a suction port communicating with the suction chamber, and the suction port may be directly connected to a suction pipe connected to the accumulator.

The suction port may be formed in a radial direction of the first scroll, and the suction pipe may be coupled to the side surface of the casing.

The accumulator may be installed outside the casing.

The check valve may include a valve plate fixed to an inner circumferential surface of the accumulator and having a refrigerant passage formed therein; And a valve plate disposed between one side surface of the valve plate and an inner surface of the accumulator corresponding to one side surface of the valve plate for selectively opening and closing the refrigerant passage, The refrigerant passage can be opened or closed according to a pressure difference formed between the both sides.

In order to achieve the object of the present invention, A driving motor provided in an inner space of the casing; A rotating shaft coupled to the rotor of the driving motor to rotate together; An oil feeder provided on the rotary shaft for pumping oil stored in the casing; A frame provided to the drive motor; A first scroll provided on a side of the frame adjacent to the oil feeder on both sides in the axial direction, the first scroll having a first wrap; A second lap provided between the frame and the first scroll to form a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber in engagement with the first lap, Second scroll; A discharge passage communicating with the internal space of the casing; A suction passage directly connected to the suction chamber of the compression chamber and guiding the fluid to the suction chamber; And a valve member provided in the suction passage, the valve member blocking the flow of the fluid in the direction of the suction passage from the compression chamber.

Here, the first scroll may have a discharge port communicating between the discharge chamber and the internal space of the casing, and the discharge port may be always open to the internal space of the casing.

In addition, an accumulator constituting the suction passage may be provided outside the casing, and the valve member may be provided so as to be opened and closed by a pressure difference in the accumulator.

Further, in order to achieve the object of the present invention, A driving motor provided in an inner space of the casing; A rotating shaft coupled to the rotor of the driving motor to rotate together; A first scroll provided on the casing; A second scroll that engages with the first scroll to form a compression chamber and is coupled to the rotation shaft to perform a swing motion; A suction port provided in the first scroll and guiding the refrigerant to the compression chamber; A discharge port communicating with the inner space of the casing to discharge the refrigerant compressed in the compression chamber to the inner space of the casing, the discharge port being provided in the first scroll; A discharge passage connecting the internal space of the casing and the condenser of the refrigeration cycle apparatus to guide the fluid discharged into the internal space of the casing toward the condenser; A suction duct which penetrates the casing and connects between the suction port and the evaporator of the refrigeration cycle to guide the fluid passing through the evaporator toward the compression chamber; And a check valve installed in the suction passage and blocking the back flow of the fluid.

Here, an accumulator constituting the suction passage may be provided outside the casing, and the check valve may be provided inside the accumulator.

Here, the inner space of the casing is divided into a suction space and a discharge space, and the check valve may be installed in the suction space.

The check valve includes a valve plate fixed to the accumulator and having a hole through which fluid can pass; And a valve disposed at one side of the valve plate with respect to a direction of flow of the fluid, wherein the hole of the valve plate can be opened and closed while being moved by a pressure difference.

The scroll compressor according to the present invention is installed in a suction pipe or an accumulator without providing a check valve in a discharge port so that when the refrigeration cycle apparatus including the compressor is stopped, the inner space and the compressed portion of the casing are communicated with each other, The refrigerant becomes the compression portion, and the inside of the compressor quickly becomes the pressure of the pressure, so that the compressor can be smoothly restarted.

Further, a check valve is provided on the suction side of the compression chamber to prevent high-pressure refrigerant compressed in the compression chamber from stopping in the direction of the evaporator when the compressor is stopped, so that the refrigerant smoothly flows from the condenser toward the evaporator, The refrigeration cycle device can perform heat exchange during the stopped time, thereby increasing the efficiency of the refrigeration cycle device.

1 is a system diagram showing a refrigeration cycle apparatus to which a scroll compressor according to the present invention is applied,
2 is a longitudinal sectional view showing an example of a lower compression scroll compressor according to the present invention,
Figure 3 is a cross-sectional view of the compression section of the scroll compressor according to Figure 2,
FIG. 4 is a perspective view of the scroll compressor according to FIG. 2,
FIG. 5 is a cross-sectional view of the accumulator according to FIG. 4,
6 and 7 are cross-sectional views illustrating embodiments for fixing a check valve in the accumulator according to FIG. 4,
FIG. 8A and FIG. 8B are schematic views for explaining a flow state of the refrigerant according to whether or not the scroll compressor according to FIG. 2 is operated;
9 and 10 are sectional views showing other embodiments of a scroll compressor to which a check valve according to the present invention is applied.

Hereinafter, a scroll compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.

FIG. 1 is a schematic view showing a refrigeration cycle apparatus to which a scroll compressor according to the present invention is applied, FIG. 2 is a longitudinal sectional view showing an example of a lower compression scroll compressor according to the present invention, FIG. 3 is a cross- FIG. 4 is a perspective view showing the accumulator in a scroll compressor according to FIG. 2, and FIG. 5 is a cross-sectional view of the accumulator according to FIG.

1, the refrigeration cycle apparatus to which the scroll compressor according to the present embodiment is applied includes a compressor 1, a condenser 2 and a condensing fan 2a, an inflator 3, an evaporator 4, 4a may constitute a closed loop.

The compressor 1 is provided with a driving unit 20 for generating a rotational force and a drive motor for driving the driving unit 20 in the inner space 10a of the casing 10 forming the discharge space. And a compression unit 30 for compressing the refrigerant.

The casing 10 includes a cylindrical shell 11 constituting a hermetically sealed container, an upper shell 12 covering the upper portion of the cylindrical shell 11 and constituting a hermetically sealed container together with the lower shell of the cylindrical shell 11, And a lower shell 13 which forms the oil storage space 1b.

The refrigerant suction pipe 15 penetrates to the side surface of the cylindrical shell 11 and directly communicates with the suction chamber of the compression unit 30. The upper shell 12 is communicated with the inner space 10a of the casing 10 A refrigerant discharge pipe 16 may be installed. The refrigerant discharge pipe 16 corresponds to a passage through which the compressed refrigerant discharged from the compression unit 30 to the inner space 10a of the casing 10 is discharged to the outside, A separator (not shown) may be connected to the refrigerant discharge pipe 16.

A stator 21 constituting a power transmitting portion 20 is fixed to an upper portion of the casing 10 and a stator 21 is formed inside the stator 21 together with the stator 21 to form a transmission portion 20, The rotor 22 which rotates by the action can be rotatably installed.

The stator 21 is formed with a plurality of slots (not shown) along the circumferential direction on its inner circumferential surface so that the coils 25 are wound. The outer circumferential surface of the stator 21 is cut into a D- The oil return passageway 211 can be formed so that the oil passes between the oil return passageway 211 and the oil return passageway.

The main frame 31 constituting the compression unit 30 may be fixedly coupled to the inner circumferential surface of the casing 10 at a predetermined distance below the stator 21. The outer circumferential surface of the main frame 31 may be heat-shrunk or welded and fixedly coupled to the inner circumferential surface of the cylindrical shell 11.

A first sidewall portion 311 is formed at an edge of the main frame 31 and a second sidewall portion 311 for supporting a main bearing portion 231 of a rotation shaft 23, A portion 312 may be formed. The first bearing water hole 312a may be formed in the first bearing part through the axial direction so that the main bearing part 231 of the rotary shaft 23 is rotatably inserted and supported in the radial direction.

(Hereinafter, referred to as a first scroll) 32, which is eccentrically coupled to the rotation shaft 23 (hereinafter, abbreviated as second scroll 33) is provided on the bottom surface of the main frame 31 The first scroll 32 may be fixedly coupled to the main frame 31, but may also be movably coupled in the axial direction.

The first scroll 32 has a fixed plate portion 321 (hereinafter referred to as a first fixed plate portion) formed in a substantially circular plate shape. The edge portion of the first fixed plate portion 321 is formed with a bottom edge of the main frame 31 A scroll side wall portion (hereinafter referred to as a second side wall portion) 322 may be formed.

A fixed lap (hereinafter abbreviated as a first lap) (hereinafter referred to as a second lap) 332, which is engaged with the orbiting lap 332 (hereinafter referred to as a second lap) 323 may be formed. The compression chamber V is formed between the first hard plate portion 321 and the first lap 323 and between the second lap 332 and the second hard plate portion 331 to be described later, An intermediate pressure chamber, and a discharge chamber may be continuously formed.

The compression chamber V includes a first compression chamber V1 formed between the inner surface of the first wrap 323 and the outer surface of the second wrap 332, And a second compression chamber (V2) formed between the inner surfaces of the second wrap (332).

3, the first compression chamber V1 is formed between two contact points P11 and P12 which are formed by the inner surface of the first wrap 323 and the outer surface of the second wrap 332 coming into contact with each other, When the angle between the center O of the eccentric portion and the two lines connecting the two contact points P11 and P12 is a large angle, the angle α is set to at least <360 ° before the start of the discharge. The second compression chamber V2 is formed between the two contact points P21 and P22 which are generated by the contact between the outer surface of the first wrap 323 and the inner surface of the second wrap 332. [

Therefore, in the first compression chamber (V1), as compared with the second compression chamber (V2), the refrigerant is first sucked and the compression path is relatively long, but the second lap (332) V1 is formed to be relatively lower than that of the second compression chamber V2. In the second compression chamber V2, as compared with the first compression chamber V1, the refrigerant is sucked later and the compression path is relatively short. However, since the second lap 332 is formed with non-forming, The compression ratio of the first compression chamber V2 is relatively higher than that of the first compression chamber V1.

A suction port 324 through which the refrigerant suction pipe 15 communicates with the suction chamber is formed at one side of the second side wall portion 322. A refrigerant compressed and communicated with the discharge chamber is formed at the center of the first hard plate portion 321 A discharge port 325 to be discharged can be formed. The discharge port 325 may be formed so as to communicate with both the first compression chamber V1 and the second compression chamber V2 but may be provided so as to be able to communicate independently with the respective compression chambers V1 and V2 And a plurality of them may be formed.

A second bearing portion 326 for supporting the sub bearing portion 232 of the rotation shaft 23 to be described later is formed at the center of the hard plate portion 321 of the first scroll 32. The second bearing bearing portion 326, The second bearing hole 326a may be formed to penetrate in the axial direction and support the sub bearing portion 232 in the radial direction.

A thrust bearing portion 327 for axially supporting the rotary shaft 23 is formed between the first hard plate portion 321 of the first scroll 32 and the bottom surface of the eccentric portion 233 of the rotary shaft 23 .

On the other hand, a discharge cover 34 for receiving the refrigerant discharged from the compression chamber V and guiding the refrigerant to a refrigerant passage to be described later may be coupled to the lower portion of the first scroll 32. The discharge cover 34 has a refrigerant passage P _G for guiding the refrigerant discharged from the compression chamber V to the internal space 10a of the casing 10 while the internal space 341 accommodates the discharge port 325, As shown in FIG.

Here, the refrigerant passage P _{G is} formed at a position between the second sidewall portion 322 of the first scroll 32 and the inner wall of the main frame 31 on the inner side of the flow dividing portion 40, The first sidewall portion 311 may be formed to penetrate through the second sidewall portion 322 and the second sidewall portion 322 may be continuously formed on the outer circumferential surface of the first frame 311.

On the other hand, the second scroll (33) can be installed to be pivotable between the main frame (31) and the first scroll (32). An ore ring 35 is provided between the upper surface of the second scroll 33 and the corresponding bottom surface of the main frame 31 to prevent the second scroll 33 from rotating. A sealing member 36 for forming a back pressure chamber Bs may be provided. Therefore, the back pressure chamber Bs is a space formed by the main frame 31, the first scroll 32 and the second scroll 33 at the outside of the sealing member 36 with the sealing member 36 as a center The back pressure chamber Bs communicates with the intermediate compression chamber V by a back pressure hole (not shown) provided in the first scroll 32 and is filled with refrigerant at an intermediate pressure, thereby forming an intermediate pressure. However, since the space formed inside the sealing member 36 is filled with high-pressure oil, this space can also serve as a back-pressure chamber.

The second scroll (33) may be formed in a substantially disc shape as the swash plate portion (hereinafter referred to as the second hard plate portion) 331. A back pressure chamber Bs may be formed on the upper surface of the second hard plate 331 and a second lap 332 may be formed on the bottom surface of the second hard plate 331 to engage with the first lap 323 to form a compression chamber.

The shaft portion 333 may be formed on the central portion of the second hard plate portion 331 in the axial direction so that the eccentric portion 233 of the rotary shaft 23 is rotatably inserted into the shaft portion 233 to be described later.

The rotation axis coupling portion 333 may extend from the second wrap 332 to form the inner end of the second wrap 332. The rotation axis connecting portion 333 is formed to have a height that overlaps the second wraps 332 on the same plane so that the eccentric portion 233 of the rotation axis 23 is overlapped on the same plane as the second wraps 332 As shown in FIG. As a result, the repulsive force and the compressive force of the refrigerant are canceled each other while being applied to the same plane with reference to the second longitudinal plate portion, so that the inclination of the second scroll 33 due to the action of the compressive force and the repulsive force can be prevented.

The outer circumferential portion of the rotary shaft coupling portion 333 is connected to the second wrap 332 to form the compression chamber V together with the first wrap 323 during the compression process. The second wrap 332 may be formed in an involute shape with the first wrap 323, but may be formed in various other shapes. For example, the second wrap 332 and the first wrap 323 may have a shape in which a plurality of arcs having different diameters and origin points are connected, and the outermost curve is formed in a substantially elliptical shape having a long axis and a short axis .

A protrusion 328 is formed near the inner end (suction end or start end) of the first wrap 323 so as to protrude toward the outer peripheral portion of the rotation shaft coupling portion 333. The protrusion 328 is formed to protrude from the protrusion 328 The contact portion 328a can be formed. That is, the inner end of the first wrap 323 may be formed to have a larger thickness than the other portions. Thus, the lap strength at the inner end portion, which receives the greatest compressive force among the first laps 323, is improved, and the durability can be improved.

A concave portion 335 is formed in the outer peripheral portion of the rotation axis coupling portion 333 facing the inner end of the first wrap 323 to engage with the projection 328 of the first wrap 323. At one side of the recess 335, an increasing portion 335a is formed on the upstream side along the forming direction of the compression chamber V to increase the thickness from the inner peripheral portion to the outer peripheral portion of the rotary shaft engaging portion 333. This shortens the length of the first compression chamber (V1) immediately before discharge and consequently makes it possible to increase the compression ratio of the first compression chamber (V1).

The other side of the concave portion 335 is formed with an arc surface 335b having an arc shape. The diameter of the arc surface 335b is determined by the thickness of the inner end of the first wrap 323 and the radius of turn of the second wrap 332. Increasing the thickness of the inner end of the first wrap 323 increases the diameter of the arc surface 335b ) Becomes larger. As a result, the thickness of the second wrap around the arc surface 335b can be increased to ensure durability, and the compression path can be made longer, so that the compression ratio of the second compression chamber V2 can be increased accordingly.

The upper portion of the rotary shaft 23 is press-fitted to the center of the rotor 22 while the lower portion thereof is coupled to the compression portion 30 and can be supported in a radial direction. Thus, the rotary shaft 23 transmits the rotational force of the electromotive unit 20 to the second scroll 33 of the compression unit 30. Then, the second scroll 33 eccentrically connected to the rotary shaft 23 rotates relative to the first scroll 32.

A main bearing portion 231 is formed on the lower half portion of the rotary shaft 23 so as to be inserted into the first bearing hole 312a of the main frame 31 and radially supported. The sub bearing portion 232 may be formed to be inserted into the second bearing hole 326a of the bearing 32 and radially supported. The eccentric portion 233 may be formed between the main bearing portion 231 and the sub bearing portion 232 so as to be inserted into the rotation axis engaging portion 333 of the second scroll 33 and coupled therewith.

The main bearing portion 231 and the sub bearing portion 232 are coaxially formed so as to have the same axial center and the eccentric portion 233 is formed in a radial direction with respect to the main bearing portion 231 or the sub bearing portion 232 It can be formed eccentrically. The sub bearing portion 232 may be formed eccentrically with respect to the main bearing portion 231.

The eccentric part 233 is formed so as to be smaller in outer diameter than the outer diameter of the main bearing part 231 and larger than the outer diameter of the sub bearing part 232 so that the rotary shaft 23 is rotatably coupled to the respective bearing holes 312a, It may be advantageous to pass through the portion 333. However, when the eccentric portion 233 is formed integrally with the rotary shaft 23 but using a separate bearing, the outer diameter of the sub-bearing portion 232 is not formed to be smaller than the outer diameter of the eccentric portion 233, (23) can be inserted and coupled.

In addition, the bearing portion and the oil supply passage 234 for supplying oil to the eccentric portion may be formed inside the rotary shaft 23, respectively. The oil supply passage 234 is formed at the lower end or middle height of the stator 21 at the lower end of the rotary shaft 23 or at the lower end or middle height of the main bearing portion 231 as the compression portion 30 is positioned below the transmission portion 20. [ And may be formed as a grooving to a height higher than the top.

An oil feeder 60 for pumping the oil filled in the oil storage space 10b may be coupled to the lower end of the rotary shaft 23, that is, the lower end of the sub bearing portion 232. The oil feeder 60 includes an oil supply pipe 61 inserted and joined to the oil supply passage 234 of the rotary shaft 23 and an oil suction member such as a propeller Not shown). The oil supply pipe 61 may be installed so as to be submerged in the oil storage space 10b through the discharge cover 34. [

Here, the oil supply hole and / or the oil supply groove may be formed between each bearing portion and the eccentric portion or between the respective bearing portions so that oil absorbed through the oil supply passage is supplied to the outer peripheral surfaces of the bearing portion and the eccentric portion. Therefore, the oil taken up in the upper direction of the main bearing portion 231 along the oil supply passage 234, the oil supply hole (not shown) and the oil supply groove (not shown) of the rotary shaft 23 is supplied to the main frame 31 And then flows out from the bearing surface at the upper end of the first bearing portion 312 and flows down to the upper surface of the main frame 31 along the first bearing portion 312. The outer peripheral surface of the main frame 31 home) and through the oil passage (P _O) are formed in a row on the outer circumferential surface of the first scroll 32, which is recovered as a low dielectric space (10b).

The oil discharged to the inner space 10a of the casing 10 together with the refrigerant in the compression chamber V is separated from the refrigerant in the upper space of the casing 10 and flows through the passage 10 formed in the outer peripheral surface of the transmission portion 20, and through the oil passage (P _O) is formed on the outer peripheral surface of the compression unit 30 and is recovered as a low dielectric space (10b).

On the other hand, an accumulator 70 for sorting the liquid refrigerant from the refrigerant sucked in the direction of the compressor in the evaporator 4 of the refrigeration cycle apparatus is provided in the middle of the refrigerant suction pipe 15, that is, outside the casing 10.

The accumulator 70 is provided with a housing portion 71 in a cylindrical shape having an inner diameter larger than the inner diameter of the refrigerant suction pipe 15 and a cap portion 72 for sealing the housing portion 71 at one end of the housing portion 71 ) Are combined. Of course, the accumulator 70 may be formed as a single body having a small inner diameter. However, in this case, since it is difficult to install a check valve 80 to be described later inside the accumulator 70, at least one of the housing portions 71 is opened so that the cap portion 72 ). &Lt; / RTI &gt;

A check valve 80 is provided at the lower end of the housing part 71 to prevent the refrigerant from flowing backward from the compressor 1 to the evaporator 4 side. The check valve 80 includes a valve plate 81 formed with a coolant passage hole 811 and fixed to the accumulator 70 and a valve plate 82 for selectively opening and closing the coolant passage hole 811, ).

The valve plate 81 can be press-fitted or welded to the inner circumferential surface of the housing portion 71 and fixed. However, any structure is possible as long as the valve plate 81 is fixed to the housing part 71 of the accumulator 70 like a projection and a groove. The housing portion 71 of the accumulator 70 is pressed and fixed in the direction of the inner circumferential surface so as not to push the valve plate 81 against the suction pressure or the discharge pressure of the refrigerant, The protruding portion 711 may be formed to support the rear surface of the valve plate 81.

A restriction protrusion 712 may be formed at a lower end of the housing part 71 with a space through which the valve plate 82 can move from the front surface of the valve plate 81. The restricting protrusion 712 may be formed by pressing the housing portion 71 of the accumulator 70 in the direction of the inner circumferential surface as in the case of the fixing protrusion 711 in advance, but a separate ring member 83 may be press- It may be fixed. Alternatively, as shown in FIG. 7, the cap portion 72 may be inserted into the housing portion 71 so that the end of the cap portion 72 serves as a kind of restriction protrusion.

The valve plate 82 is formed as an annular plate so that when the valve plate 82 is separated from the valve plate 81, the inner hole 821 of the valve plate 82 is connected to the refrigerant passage 811 of the valve plate 81, .

The scroll compressor according to this embodiment operates as follows.

That is, when power is applied to the driving unit 20, a rotating force is generated in the rotor 22 and the rotating shaft 23 and rotates. As the rotating shaft 23 rotates, The scroll 33 is pivoted by the oillering 35.

8A, the refrigerant passing through the condenser 2 and the evaporator 4 of the refrigerating cycle apparatus passes through the check valve 80 of the accumulator 70 and flows through the refrigerant suction pipe 15 to the compression chamber V &Lt; / RTI &gt; The refrigerant is compressed as the volume of the compression chamber (V) decreases by the swing motion of the second scroll (33) and is discharged to the inner space of the discharge cover (34) through the discharge port (325).

The refrigerant discharged into the internal space 341 of the discharge cover 34 is circulated through the internal space 341 of the discharge cover 34 and flows into the discharge space of the main frame 31 and the stator 21 after the noise is reduced. And the refrigerant moves to the upper space of the transmission portion 20 through the gap between the stator 21 and the rotor 22. [

After the oil is separated from the refrigerant in the upper space of the transmission portion 20, the refrigerant is discharged to the outside of the casing 10 through the refrigerant discharge pipe 16, while the oil flows from the inner peripheral surface of the casing 10 to the stator 21 and the inner circumferential surface of the casing 10 and the outer circumferential surface of the compression section 30 through the flow path between the inner circumferential surface of the casing 10 and the outer circumferential surface of the compression section 30.

At this time, when the operation of the refrigeration cycle apparatus is stopped, the compressor 1 is also turned off, and the compression load in the compression chamber V is removed. However, even if the pressure load in the compression chamber is removed, the refrigerant discharged from the compressor 1 to the refrigeration cycle is relatively discharged from the condenser 2, which is relatively high in pressure due to the pressure difference between the suction side and the discharge shaft, And moves toward the evaporator 4 which forms a low pressure.

Therefore, when the condensing fan 2a and the evaporation fan 4a of the refrigeration cycle apparatus are operated in a state where the compressor 1 is stopped, that is, the compression load of the compression unit 30 is removed, the refrigerant is moved The heat exchange can be continued using the latent heat during the cooling cycle, thereby increasing the efficiency of the refrigeration cycle apparatus.

However, when the check valve is provided in the discharge port 325 in the high-pressure scroll compressor in which the compression chamber V is communicated with the internal space 10a of the casing 10, Pressure refrigerant is prevented from flowing into the compression chamber (V) by the check valve when the compressor is stopped. Then, even when the difference in pressure between the suction pressure (pressure in the compression chamber) Ps and the discharge pressure (pressure in the space inside the casing) Pd is small, it is not possible to restart and the time required for pneumatic pressure must be prolonged. However, when the required period of the pneumatic pressure is prolonged, the oil leakage increases, so that it may not be possible to increase the pneumatic pressure time in practice.

Therefore, the time required for the pneumatic pressure should be as short as possible, and the compressor can not reach the pneumatic pressure required for restarting, so that the compressor can not be restarted even if the refrigeration cycle device is operated again. In addition, if the time required for the pneumatic pressure is shortened, the latent heat in the differential pressure section can not be used, and the energy efficiency may be lowered accordingly.

8B, a check valve is not provided in the discharge port 325 for communicating between the compression chamber V and the internal space 10a of the casing 10, The check valve 80 is provided in the middle of the refrigerant suction pipe 15 connected to the suction side of the accumulator 70 or more precisely in the accumulator 70 so that the high pressure refrigerant discharged into the inner space 10a of the casing 10 It is possible to flow back to the compression chamber V through the discharge port 325 when the compressor 1 is stopped.

Accordingly, even if the compressor 1 is stopped, the refrigerant in the inner space 10a of the casing 10, which forms a relatively high pressure region, flows backward through the discharge port 325 and flows into the compression chamber V, So that the pressure of the inside space of the casing 10 and the pressure of the compression chamber V coincide with each other to be minimized and the refrigerant suction pipe 15 is connected to the suction side of the compression chamber V It is possible to smoothly restart the operation of the so-called high-pressure scroll compressor in which the discharge side of the compression chamber (V) communicates directly with the internal space (10a) of the casing (10).

If the refrigerant discharged into the internal space 10a of the casing 10 flows back into the compression chamber V, the second scroll 33 may rotate in the reverse direction and load may be generated in the transmission portion 20. However, The check valve 80 is installed in the refrigerant suction pipe 15 or the accumulator 70 adjacent to the casing 10 so that the amount of the refrigerant flowing back from the casing 10 to the compression chamber V is limited to a minimum . Accordingly, it is possible to minimize the increase in the load due to the reverse flow of the refrigerant through the compressor (1).

In addition, as the check valve 80 prevents the refrigerant from flowing backward from the internal space 10a of the casing 10 toward the compression chamber, that is, from the condenser 2 to the compressor 1 and the evaporator 4, The refrigerant remaining in the inner space 10a of the compressor 10 continuously moves in the direction of the evaporator 4 from the condenser 2 even when the compressor stops.

Therefore, even when the refrigeration cycle apparatus including the compressor 1 is stopped, the evaporation fan 4a and the condensing fan 2a of the refrigeration cycle apparatus can be operated to sufficiently utilize the latent heat of the refrigeration cycle apparatus, .

As in the present embodiment, the check valve 80 is installed in the accumulator 70 provided outside the casing 10, so that the check valve 80 can be easily installed. In addition, when the check valve (80) is installed in the accumulator (70), the accumulator (70) can be modularized and the check valve (80) can be installed more easily.

When the check valve 80 is provided in the accumulator 70 as in the present embodiment, since the inner diameter of the accumulator 70 is formed to be larger than the inner diameter of the refrigerant suction pipe 15, the size of the check valve 80 And may be formed to have a size larger than or equal to the inner diameter of the refrigerant suction pipe (15). Accordingly, it is possible to minimize the increase in the flow resistance of the refrigerant by the check valve (80) during normal operation of the compressor.

On the other hand, the check valve may be provided at the inlet of the first scroll. However, in this case, the flow resistance may increase or a separate member may be required depending on the shape of the suction port. For example, when the suction port is formed in the radial direction of the first scroll, the height of the first scroll is determined according to the height of the first wrap, so that there may be a restriction to enlarge the inner diameter of the suction port. This limits the size of the check valve, which can eventually increase the flow resistance due to the check valve. On the other hand, when the suction port is formed in the axial direction, the opening / closing direction of the check valve is in a direction intersecting with the flow direction of the refrigerant, so that another elastic member is further required to close the check valve in the opened state. Therefore, in this case, the number of parts can be increased and the structure can be complicated as compared with the embodiment.

In the above embodiment, the low compression type and high pressure type scroll compressors have been described. However, the present invention is not limited to the low compression type and high pressure type scroll compressors. For example, it can be applied to a low compression scroll compressor as well as a low compression scroll compressor.

However, since the suction pipe is connected to the inner space of the casing in the case of a low pressure scroll compressor, the accumulator may not be provided outside the casing 10 as shown in FIG. 9, Can be installed at the end of the suction pipe (9) inside the casing (10).

Accordingly, when the compressor is stopped, the refrigerant in the discharge space (D) flows back into the compression chamber, but can not be blocked by the check valve (80) through the suction pipe (15) and toward the evaporator. The basic structure and operation effects of the present invention are similar to those of the above-described embodiments, and thus a detailed description thereof will be omitted.

While the lower compression scroll compressor has been described in the above embodiments, it is not necessarily applied to the lower compression scroll compressor. For example, the same can be applied to a so-called upper compression scroll compressor in which the compression section is located on the opposite side of the oil feeder with respect to the transmission section.

In this case, the compression method is not limited to the high-pressure type, and can be applied to the upper compression scroll compressor while being low-pressure. 10, the internal space of the casing 10 is divided into a suction space S and a discharge space D. The check valve 80 is connected to the suction space S in the suction space S And may be installed at the end of the suction pipe 15 that communicates with each other.

Accordingly, when the compressor is stopped, the refrigerant in the discharge space (D) flows back into the compression chamber, but can not be blocked by the check valve (80) through the suction pipe (15) and toward the evaporator. The basic constitution and operation effects of such a low-pressure scroll compressor are also similar to those of the above-described embodiments, and thus a detailed description thereof will be omitted.

1: compressor 2: condenser
4: evaporator 10: casing
10a: internal space of the casing 20:
30: Compression portion 32: 1st scroll
325: discharge port 70: accumulator
71: housing part 711:
712: limiting protrusion 72: cap portion
80: Check valve 81: Valve plate
811: refrigerant passage 82: valve plate

Claims (13)

A casing in which oil is stored in the internal space;
A driving motor provided in an inner space of the casing;
A rotating shaft coupled to the rotor of the driving motor to rotate together;
An oil feeder provided on the rotary shaft for pumping oil stored in the casing;
A frame provided to the drive motor;
A first scroll provided on a side of the frame adjacent to the oil feeder on both sides in the axial direction, the first scroll having a first wrap;
A second lap provided between the frame and the first scroll to form a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber in engagement with the first lap, Second scroll;
An accumulator connected to the suction chamber of the compression chamber; And
And a check valve provided inside the accumulator to prevent the fluid from flowing back toward the accumulator in the compression chamber. The method according to claim 1,
A discharge port for communicating between the discharge chamber and the internal space of the casing is formed in the first scroll,
And the discharge port is always open to the internal space of the casing. 3. The method of claim 2,
An inlet port communicating with the suction chamber is formed in the first scroll,
And the suction port is directly connected to a suction pipe connected to the accumulator. The method of claim 3,
Wherein the suction port is formed in a radial direction of the first scroll, and the suction pipe is coupled to a side surface of the casing. The method according to claim 1,
And the accumulator is installed outside the casing. 6. The check valve according to claim 5,
A valve plate fixed to an inner circumferential surface of the accumulator and having a refrigerant through-hole; And
And a valve plate provided between one side of the valve plate and an inner side surface of the accumulator corresponding to one side of the valve plate to selectively open and close the refrigerant passage,
Wherein the valve plate opens / closes the refrigerant passage according to a pressure difference formed between both sides of the valve plate. A casing in which oil is stored in the internal space;
A driving motor provided in an inner space of the casing;
A rotating shaft coupled to the rotor of the driving motor to rotate together;
An oil feeder provided on the rotary shaft for pumping oil stored in the casing;
A frame provided to the drive motor;
A first scroll provided on a side of the frame adjacent to the oil feeder on both sides in the axial direction, the first scroll having a first wrap;
A second lap provided between the frame and the first scroll to form a compression chamber formed of a suction chamber, an intermediate pressure chamber, and a discharge chamber in engagement with the first lap, Second scroll;
A discharge passage communicating with the internal space of the casing;
A suction passage directly connected to the suction chamber of the compression chamber and guiding the fluid to the suction chamber; And
And a valve member provided in the suction passage and blocking a flow of the fluid in the direction of the suction passage from the compression chamber. 8. The method of claim 7,
A discharge port for communicating between the discharge chamber and the internal space of the casing is formed in the first scroll,
And the discharge port is always open to the internal space of the casing. 8. The method of claim 7,
An accumulator constituting the suction passage is provided outside the casing,
Wherein the valve member is configured to be opened and closed by a pressure difference within the accumulator. Casing;
A driving motor provided in an inner space of the casing;
A rotating shaft coupled to the rotor of the driving motor to rotate together;
A first scroll provided on the casing;
A second scroll that engages with the first scroll to form a compression chamber and is coupled to the rotation shaft to perform a swing motion;
A suction port provided in the first scroll and guiding the refrigerant to the compression chamber;
A discharge port communicating with the inner space of the casing to discharge the refrigerant compressed in the compression chamber to the inner space of the casing, the discharge port being provided in the first scroll;
A discharge passage connecting the internal space of the casing and the condenser of the refrigeration cycle apparatus to guide the fluid discharged into the internal space of the casing toward the condenser;
A suction duct which penetrates the casing and connects between the suction port and the evaporator of the refrigeration cycle to guide the fluid passing through the evaporator toward the compression chamber; And
And a check valve installed in the suction passage to block reverse flow of the fluid. 11. The method of claim 10,
An accumulator constituting the suction passage is provided outside the casing,
And the check valve is provided inside the accumulator. 11. The method of claim 10,
Wherein an inner space of the casing is divided into a suction space and a discharge space, and the check valve is installed in the suction space. 13. The method according to claim 11 or 12,
The check valve
A valve plate having a hole through which fluid can pass; And
Wherein the valve plate is provided at one side of the valve plate with respect to a flow direction of the fluid, and the hole of the valve plate is opened and closed while being moved by a pressure difference.

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