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WO2025216335A1 - Compresseur à spirale - Google Patents

Compresseur à spirale

Info

Publication number
WO2025216335A1
WO2025216335A1 PCT/KR2024/004635 KR2024004635W WO2025216335A1 WO 2025216335 A1 WO2025216335 A1 WO 2025216335A1 KR 2024004635 W KR2024004635 W KR 2024004635W WO 2025216335 A1 WO2025216335 A1 WO 2025216335A1
Authority
WO
WIPO (PCT)
Prior art keywords
back pressure
valve
passage
pressure
scroll
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/KR2024/004635
Other languages
English (en)
Korean (ko)
Inventor
최중선
이재하
문제현
한미쁨
최세헌
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Priority to PCT/KR2024/004635 priority Critical patent/WO2025216335A1/fr
Publication of WO2025216335A1 publication Critical patent/WO2025216335A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a scroll compressor.
  • Compressors used in refrigeration cycles such as refrigerators and air conditioners compress refrigerant gas and transmit it to the condenser.
  • Air conditioners primarily use rotary or scroll compressors.
  • Scroll compressors are increasingly being used not only in air conditioners but also in compressors for water heaters, which require even higher pressure ratios.
  • a scroll compressor is classified as a sealed compressor if the drive unit (or electric unit) and the compression unit are included in one casing, and as an open type if they are provided independently. If the compression unit is located above the drive unit, it is classified as an upper compression type, and if located below, it is classified as a lower compression type. If the space where the drive unit is accommodated is suction pressure, it is classified as a low pressure type, and if it is discharge pressure, it is classified as a high pressure type.
  • the scroll compressor includes a fixed scroll having a fixed wrap and an orbiting scroll having an orbiting wrap that is engaged with the fixed wrap.
  • Scroll compressors can be classified into an orbiting back pressure type and a fixed back pressure type depending on the back pressure method.
  • the orbiting back pressure type is a method in which a back pressure space is formed on the back surface of the orbiting scroll
  • the fixed back pressure type is a method in which a back pressure space is formed on the back surface of the fixed scroll.
  • the present embodiment can be applied to a scroll compressor of an orbiting back pressure type.
  • a thrust bearing surface is formed between the orbiting scroll and the fixed scroll, so that the orbiting scroll orbits while in sliding contact with the fixed scroll.
  • a back pressure space is formed between the orbiting scroll and the main frame supporting the orbiting scroll, and the back pressure of the back pressure space presses the orbiting scroll toward the fixed scroll, thereby bringing the two scrolls into close contact and preventing leakage between the compression chambers.
  • a single back pressure passage is formed between the compression chamber and the back pressure space, which form an intermediate pressure, so that a portion of the refrigerant compressed in the compression chamber can be moved to the back pressure space, thereby forming a back pressure in the back pressure space.
  • the back pressure of the back pressure space is maintained constant regardless of the operating conditions of the compressor.
  • leakage may occur between compression chambers or friction loss due to excessive contact may occur.
  • the back pressure of the back pressure space may be lower than the required pressure, preventing the orbiting scroll from being in strong contact with the fixed scroll, which may result in leakage between compression chambers.
  • the pressure in the back pressure space may be higher than the required pressure, causing the orbiting scroll to be in excessive contact with the fixed scroll, which may increase friction loss. This may narrow the operating range of the compressor.
  • the purpose of the present invention is to provide a scroll compressor capable of suppressing leakage between compression chambers and/or friction loss on the bearing surface between scrolls.
  • Another object of the present invention is to provide a scroll compressor capable of appropriately controlling the back pressure of the back pressure space according to operating conditions.
  • Another object of the present invention is to provide a scroll compressor capable of simplifying a member for controlling the opening and closing of a back pressure passage, including a back pressure passage connecting a compression chamber and a back pressure space.
  • a scroll compressor including a casing, a main frame, an orbiting scroll, a fixed scroll, a back pressure space, a back pressure passage, and a back pressure valve
  • the casing can be provided with a discharge space.
  • the main frame can be provided inside the casing.
  • the orbiting scroll can be axially supported by the main frame.
  • the fixed scroll can be coupled to the main frame with the orbiting scroll therebetween to form a compression chamber together with the orbiting scroll.
  • the back pressure space can be provided between the main frame and the orbiting scroll.
  • the back pressure passage can be provided in the fixed scroll to communicate the back pressure space with the compression chamber.
  • the back pressure valve can selectively open and close the back pressure passage.
  • the back pressure passage can be communicated with a plurality of compression chambers having different pressures among the compression chambers. Through this, the back pressure passage can be selectively opened and closed by the back pressure valve between the compression chamber and the back pressure space, and the back pressure of the back pressure space can be appropriately varied according to the operating conditions of the compressor, thereby suppressing leakage between the compression paths and/or friction loss between scrolls. In addition, this can expand the operating range of the compressor.
  • the fixed scroll may further include a valve pressurization passage communicating between the back pressure passage and the discharge space of the casing.
  • the back pressure valve is arranged such that one side thereof faces the valve pressurization passage and can be slidably inserted within the back pressure passage according to the pressure of the discharge space.
  • the center of the valve pressure passage facing the back pressure valve may be formed to be on the same line as the center of the back pressure valve. This allows the inner diameter of the back pressure passage to be formed as small as possible, thereby minimizing the inner diameter of the back pressure valve and/or the weight of the back pressure valve, thereby improving valve responsiveness.
  • the back pressure valve may include a valve body and a connecting passage.
  • the valve body may include a plurality of opening/closing parts configured to selectively open/close the back pressure passage, and a connecting part configured to connect between the plurality of opening/closing parts.
  • the connecting passage may be selectively connected to the back pressure passage depending on the position of the valve body.
  • the connecting passage may be formed by penetrating the interior of the valve body. Through this, the connecting passage may move the corresponding compression chamber to the back pressure space depending on the position of the valve body.
  • the connecting passage may include a first passage portion and a second passage portion.
  • the first passage portion may be provided in the connecting portion.
  • the second passage portion may be provided in an opening/closing portion adjacent to the back pressure space among the plurality of opening/closing portions and may be in communication with the first passage portion. At least a portion of the second passage portion may be formed on the same line as the first passage portion along the back pressure passage.
  • the opening and closing part facing the valve pressure passage is formed in a blocked shape and can be slidably inserted into the back pressure passage.
  • the back pressure valve can uniformly receive the pressure of the refrigerant transferred from the discharge space through the valve pressure passage, while at the same time tightly sealing the two compression chambers that form the intermediate pressure and the valve pressure passage.
  • a valve support surface that restricts movement of the back pressure valve may be provided between the back pressure passage and the valve pressure passage. Through this, the back pressure valve can operate stably while its movement position is restricted by the valve support surface.
  • an elastic member may be provided on the opposite side of the valve pressurization passage with the back pressure valve in between to elastically support the back pressure valve toward the valve pressurization passage.
  • the pressure relief passage may be provided with a fixing member that supports the other end of the elastic member.
  • the fixing member may be separated from the sealing member that seals one end of the pressure relief passage. This reduces the manufacturing cost of the sealing member while ensuring the passage cross-sectional area in the valve receiving portion is as wide as possible.
  • a fixing member support surface that limits the insertion depth of the fixing member may be formed on the inner surface of the pressure passage. This allows the insertion depth of the fixing member to be limited by the fixing member support surface, simplifying the assembly process while also appropriately maintaining the elasticity of the elastic member.
  • the pressure relief passage may be provided with a fixing member that supports the second end of the elastic member.
  • the fixing member may extend from a sealing member that seals the pressure relief passage with respect to the internal space of the casing. This enhances the fastening force of the fixing member, thereby stably fixing the elastic member even when the fixed scroll overheats.
  • the back pressure passage may be formed as one.
  • the back pressure passage may include one valve receiving portion, a plurality of back pressure inlets, and one back pressure outlet portion.
  • the one valve receiving portion may be provided on the fixed scroll so that the back pressure valve may be received therein.
  • the plurality of back pressure inlets may be respectively connected to the plurality of compression chambers having different pressures at one end of the valve receiving portion, and may be selectively opened and closed by the back pressure valve.
  • the one back pressure outlet portion may be connected to the back pressure space at the other end of the valve receiving portion.
  • the plurality of back pressure inlets may be formed on the same line as the back pressure outlets based on the longitudinal direction of the valve receiving portion. This allows the inner diameter of the back pressure passage to be formed as small as possible, thereby minimizing the inner diameter of the back pressure valve and/or the weight of the back pressure valve, thereby improving valve responsiveness.
  • the back pressure passages may be formed in plurality so as to be spaced apart from each other along the circumferential direction.
  • Each of the plurality of back pressure passages may include one valve receiving portion, one back pressure inlet portion, and one back pressure outlet portion.
  • the one valve receiving portion may be provided in the fixed scroll so as to receive the back pressure valve.
  • the one back pressure inlet portion may be connected to one of the plurality of compression chambers having different pressures at one end of the valve receiving portion, and may be selectively opened and closed by the back pressure valve.
  • the one back pressure outlet portion may be connected to the back pressure space at the other end of the valve receiving portion.
  • back pressure passages are formed to be independently connected to the plurality of compression chambers, not only is the operational reliability of the back pressure valve improved, but also the back pressure of the back pressure space can be optimized by appropriately adjusting the position of the back pressure passage connected to the intermediate pressure depending on the operating conditions.
  • the scroll compressor of the present invention comprises a casing, a main frame, an orbiting scroll, a fixed scroll, a back pressure space, a back pressure passage, and a back pressure valve, wherein the back pressure valve is provided in the back pressure passage to selectively open and close the back pressure passage, and the back pressure passage can be connected to a plurality of compression chambers having different pressures among the compression chambers.
  • the back pressure passage is selectively opened and closed by the back pressure valve between the corresponding compression chambers and the back pressure space, and the back pressure of the back pressure space is appropriately varied according to the operating conditions of the compressor, so that leakage between compression paths and/or friction loss between scrolls can be suppressed.
  • the scroll compressor of the present invention further comprises a valve pressurization passage communicating between a back pressure passage and a discharge space of a casing, and the back pressure valve is arranged such that one side thereof faces the valve pressurization passage and can be slidably inserted within the back pressure passage according to the pressure of the discharge space.
  • the back pressure valve can be simplified by selectively connecting the compression chamber and the valve pressurization passage while moving according to the pressure of the refrigerant transmitted from the discharge space through the valve pressurization passage.
  • the scroll compressor of the present invention may have one back pressure passage formed therein, and may include one valve receiving portion, multiple back pressure inlets, and one back pressure outlet portion.
  • One valve receiving portion receives a back pressure valve, and the multiple back pressure inlets are connected to multiple compression chambers having different pressures at one end of the valve receiving portion and are selectively opened and closed by the back pressure valve, and one back pressure outlet portion may be connected to the back pressure space at the other end of the valve receiving portion.
  • the scroll compressor of the present invention may have a plurality of back pressure passages formed so as to be spaced apart from each other along the circumferential direction, and may each include one valve receiving portion, one back pressure inlet portion, and one back pressure outlet portion.
  • One valve receiving portion receives a back pressure valve
  • one back pressure inlet portion communicates with one of a plurality of compression chambers having different pressures at one end of the valve receiving portion and is selectively opened and closed by the back pressure valve
  • one back pressure outlet portion may communicate with the back pressure space at the other end of the valve receiving portion.
  • the back pressure passages are formed to independently communicate with a plurality of compression chambers, not only is the operational reliability of the back pressure valve improved, but also the back pressure of the back pressure space can be optimized by appropriately adjusting the position of the back pressure passages connected to the intermediate pressure depending on the operating conditions.
  • Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.
  • Figure 2 is a perspective view showing the pressure relief valve assembly according to the present embodiment disassembled from the fixed scroll.
  • Figure 3 is a perspective view showing a pressure valve assembly according to the present embodiment assembled to a fixed scroll.
  • Figure 4 is a plan view of Figure 3.
  • Fig. 5 is a cross-sectional view showing the “A” portion of Fig. 4 broken off.
  • Figure 6 is a cross-sectional view taken along the line “VI-VI” of Figure 5.
  • Fig. 7 is a cross-sectional view showing another embodiment of the blocking member in Fig. 5.
  • FIG. 8a and FIG. 8b are cross-sectional views showing the operation of the back pressure valve assembly according to the operating conditions of the compressor in FIG. 2, with FIG. 8a showing the low pressure ratio operating conditions and FIG. 8b showing the high pressure ratio operating conditions, respectively.
  • Figure 9 is a plan view of a fixed scroll shown to explain another embodiment of a pressure relief valve assembly.
  • Figure 10 is a cross-sectional view taken along the line “X-X” of Figure 9.
  • Figures 11a and 11b are cross-sectional views showing the operation of the back pressure valve assembly according to the operating conditions of the compressor in Figure 9, with Figure 11a showing the low pressure ratio operating conditions and Figure 11b showing the high pressure ratio operating conditions, respectively.
  • scroll compressors can be classified as sealed or open, depending on whether the drive motor and compression unit are installed together within the internal space of the casing.
  • This embodiment uses a sealed scroll compressor as a representative example.
  • the same principles can be applied to open scroll compressors.
  • Scroll compressors can also be categorized into fixed scroll compressors and mobile scroll compressors.
  • Fixed scroll compressors are typically used for building air conditioning, while mobile scroll compressors are used for vehicle air conditioning.
  • This embodiment uses a fixed scroll compressor as a representative example. However, the same principles can be applied to mobile scroll compressors.
  • Scroll compressors can also be categorized as low-pressure or high-pressure depending on the pressure of the refrigerant filled within the internal space of the casing.
  • a low-pressure type the internal space of the casing is filled with refrigerant at suction pressure
  • a high-pressure type the internal space of the casing is filled with refrigerant at discharge pressure.
  • This embodiment uses a high-pressure scroll compressor as a representative example. However, the same principles can be applied to low-pressure scroll compressors.
  • scroll compressors can be categorized into upper compression types and lower compression types depending on the installation location of the compression unit.
  • the compression unit In the upper compression type, the compression unit is installed above the driving motor, and in the lower compression type, the compression unit is installed below the driving motor.
  • This embodiment describes an upper compression type scroll compressor as a representative example. However, the same principles can be applied to a lower compression type scroll compressor.
  • scroll compressors can be classified into single-rotating scroll compressors and reciprocating scroll compressors depending on whether the scrolls rotate.
  • Single-rotating scroll compressors are configured such that one scroll is fixed or has limited rotational movement while the other scroll rotates, while reciprocating scroll compressors are configured such that both scrolls rotate.
  • This embodiment will be described using a single-rotating scroll compressor as a representative example. However, the same principles can be applied to reciprocating scroll compressors.
  • Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.
  • a scroll compressor according to the present embodiment has a drive motor (120) installed in the lower half of a casing (110), and a main frame (130) installed above the drive motor (120).
  • a compression unit is installed above the main frame (130).
  • the compression unit includes a fixed scroll (140) and an orbiting scroll (150), but in some cases, the main frame (130) may also be described as being included in the compression unit.
  • the casing (110) includes a cylindrical shell (111), an upper cap (112), and a lower cap (113). Accordingly, the internal space (110a) of the casing (110) can be divided into an upper space provided on the inside of the upper cap (112), an intermediate space provided on the inside of the cylindrical shell (111), and a lower space provided on the inside of the lower cap (113) based on the flow order of the refrigerant.
  • the upper space can be defined as a discharge space (110b), the intermediate space as an oil separation space (110c), and the lower space as an oil storage space (110d), respectively.
  • the cylindrical shell (111) has a cylindrical shape with both upper and lower ends open, and a drive motor (120) is press-fitted and fixed to the lower half and a main frame (130) is press-fitted and fixed to the upper half of the inner surface of the cylindrical shell (111).
  • a refrigerant discharge pipe (116) is connected to the cylindrical shell (111) by penetrating between the drive motor (120) and the main frame (130), and a refrigerant suction pipe (115) is connected to the upper cap (112) by penetrating therethrough.
  • the refrigerant suction pipe (115) passes through the discharge space (110b) of the casing (110) and is directly connected to the suction pressure chamber (not shown) of the compression unit, which will be described later, and the refrigerant discharge pipe (116) is connected to the internal space (110a) of the casing (110).
  • the refrigerant is directly supplied to the suction chamber (or suction pressure chamber) through the refrigerant suction pipe (115), and the high-pressure refrigerant discharged to the internal space (110a) of the casing (110) passes through the oil separation space (110c) and can be discharged through the refrigerant discharge pipe (116).
  • the driving motor (120) is installed in the lower half of the oil separation space (110c) forming the high-pressure section in the internal space (110a) of the casing (110), and includes a stator (121) and a rotor (122).
  • the stator (121) is fixed to the inner wall surface of the cylindrical shell (111) by hot pressing, and the rotor (122) is rotatably provided inside the stator (121).
  • the rotation shaft (125) is press-fitted and coupled to the rotor (122).
  • the upper part of the rotation shaft (125) is rotatably inserted into a main frame (130) to be described later and supported radially, and the lower part of the rotation shaft (125) is rotatably inserted into a subframe (118) and supported radially and axially.
  • An eccentric portion (1251) is provided at the upper end of the rotary shaft (125), into which a rotary shaft insertion portion (153) of a later-described orbiting scroll (150) is rotatably inserted and coupled.
  • the eccentric portion (1251) may be inserted into and coupled to the rotary shaft insertion portion (153), or the rotary shaft insertion portion (153) may be inserted into and coupled to the eccentric portion (1251).
  • This embodiment illustrates an example in which the rotary shaft insertion portion (153) is inserted into and coupled to the eccentric portion (1251) of the rotary shaft (125).
  • An oil supply hole (1255) is formed inside the rotating shaft (125) by penetrating between the two ends of the rotating shaft (125).
  • the oil supply hole (1255) is formed by penetrating from the lower end of the rotating shaft (125) to the bottom surface of the eccentric portion (1251). Accordingly, oil stored in the oil storage space (110d) forming the oil storage space (110d) can be supplied to the inside of the eccentric portion (1251) through the oil supply hole (1255).
  • An oil pickup (126) including an oil pump is installed at the bottom of the rotating shaft (125), more precisely, at the bottom of the oil supply hole (1255).
  • the inlet of the oil pickup (126) may be installed so as to be submerged in the oil stored in the oil storage space (110d). Accordingly, the oil stored in the oil storage space (110d) can be pumped by the oil pickup (126) and sucked up through the oil supply hole (1255).
  • the main frame (130) is installed on the upper side of the driving motor (120) and is fixed by hot pressing or welding to the inner wall surface of the cylindrical shell (111).
  • the main frame (130) includes a main flange portion (131), a shaft support protrusion portion (132), and a back pressure space portion (133).
  • the upper surface of the main flange portion (131) may be formed with a scroll support surface (134) that forms a thrust bearing surface (hereinafter, a first thrust bearing surface). Accordingly, the lower surface (or back surface) of the pivot plate portion (151) described later may be slidably placed on the scroll support surface (134) and supported in the axial direction.
  • the shaft support protrusion (132) extends from the center of the main flange portion (131) toward the driving motor (120), and a shaft support hole (1321) is formed on the inside of the shaft support protrusion (132). Accordingly, the main flange portion (131) can be formed in a circular shape.
  • the back pressure space (133) is a part that forms a back pressure space (S2) together with the fixed thrust surface (142a) to be described later, and can be formed in an annular shape by being sunken to a preset depth from the edge of the scroll support surface (134).
  • the back pressure space (133) is connected to the intermediate pressure chamber of the compression chamber (V) through the back pressure passage (170) to be described later, thereby forming a back pressure that is an intermediate pressure between the suction pressure and the discharge pressure.
  • the orbiting scroll (150) is pushed upward toward the fixed scroll (140) by the pressure (back pressure) of the back pressure space (S), and the orbiting thrust surface (151a) to be described later is brought into close contact with the fixed thrust surface (142a) to form a thrust bearing surface (hereinafter, second thrust bearing surface) (B2).
  • the second thrust bearing surface (B2) will be described later in the fixed scroll (140) and/or the orbiting scroll (150).
  • the fixed scroll (140) includes a fixed plate portion (141), a fixed side wall portion (142), and a fixed wrap (143).
  • the fixed plate portion (141) is formed in a circular shape.
  • the outer surface of the fixed plate portion (141) may be in close contact with the inner surface of the upper cap (112) forming the discharge space (110b) or may be spaced apart from the inner surface of the upper cap (112).
  • the fixed plate portion (141) may be formed with the same thickness. Accordingly, the root end of the fixed wrap (143) described later may be formed with the same height throughout the entire fixed wrap (143).
  • An intake port (1411) is formed at the edge of the fixed plate (141) in the axial direction and is connected to a suction pressure chamber (not shown), and a refrigerant intake pipe (115) that penetrates the upper cap (112) of the casing (110) is inserted and connected to the intake port (1411). Accordingly, the refrigerant intake pipe (115) can pass through the discharge space (110b) of the casing (110) and be directly connected to the intake port (1411) of the fixed scroll (140).
  • a discharge port (1412) and a bypass hole (not shown) are formed in the center of the fixed plate portion (141), and a discharge valve (145) for opening and closing the discharge port (1412) and a bypass valve (not shown) for opening and closing the bypass hole may be installed on the back surface of the fixed plate portion (141). Accordingly, the refrigerant compressed in the first compression chamber (V1) and the second compression chamber (V2) is discharged from the upper side of the fixed scroll (140) to the discharge space (110b) formed in the upper cap (112).
  • the compression chamber formed between the outer surface of the rotating wrap (152) and the inner surface of the fixed wrap (143) facing it is defined as the first compression chamber (V1)
  • the compression chamber formed between the inner surface of the rotating wrap (152) and the outer surface of the fixed wrap (143) facing it is defined as the second compression chamber (V2).
  • a portion of a back pressure passage (170) is formed in the fixed plate portion (141).
  • the back pressure passage (170) is a passage for supplying refrigerant at an intermediate pressure to the back pressure space portion (133) forming the back pressure space (S2). Therefore, one end of the back pressure passage (170) is connected to the compression chamber (V) forming the intermediate pressure, and the other end of the back pressure passage (170) is connected to the back pressure space portion (133). Accordingly, the back pressure passage (170) can be formed by continuously penetrating the fixed plate portion (141) and the fixed side wall portion (142).
  • one end of the back pressure passage (170) is formed to communicate with a plurality of compression chambers (V) having different pressures, and a back pressure valve assembly (180) may be provided inside the back pressure passage (170) to selectively communicate the plurality of compression chambers (V) with the back pressure passage (170).
  • the back pressure valve assembly (180) may be formed to selectively open and close the back pressure passage (170) depending on the pressure of the refrigerant discharged to the discharge space (110b). Accordingly, depending on the operating conditions of the compressor, it is possible to appropriately close the fixed scroll (140) and the orbiting scroll (150) to suppress leakage between the compression chambers (V) and/or friction loss at the second thrust bearing surface (B2). Through this, the operating range of the compressor can be expanded.
  • the back pressure passage (170) will be described later together with the back pressure valve assembly (180).
  • the fixed side-wall portion (142) can extend in an annular shape from the edge of the fixed plate portion (141) toward the main frame (130). Accordingly, the fixed side-wall portion (142) can be bolted so that its lower surface is in close contact with the upper surface of the main frame (130), i.e., the upper surface of the main flange portion (131).
  • the thrust bearing surface of the fixed side wall portion (142), i.e., the fixed thrust surface (142a), may be penetrated by the other end of the back pressure passage (170) to be described later, and a back pressure connection groove (142b) may be formed radially long at the other end of the back pressure passage (170) to guide the refrigerant moving through the back pressure passage (170) to the back pressure space (S).
  • the back pressure connection groove (142b) may extend outside the turning radius of the turning plate portion (151). Accordingly, when the turning scroll (150) is turned, the back pressure connection groove (142b) is always connected to the back pressure space (S), and the refrigerant in the compression chamber (Vm1) (Vm2) can continuously move to the back pressure space (S).
  • the fixed wrap (143) extends from the lower surface of the fixed plate portion (141) toward the orbiting scroll (150).
  • the fixed wrap (143) may be formed in various shapes, such as an involute.
  • the fixed wrap (143) may be formed in a logarithmic spiral or may be formed in a plurality of circular arc curves.
  • the fixed wrap (143) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In this embodiment, an example in which the wrap heights of the fixed wrap (143) are the same is shown.
  • the rotary scroll (150) may include a rotary plate portion (151), a rotary wrap (152), and a rotary shaft insert portion (153).
  • the pivot plate (151) is formed in a disc shape and is axially supported by the main frame (130) so as to pivot between the main frame (130) and the fixed scroll (140).
  • the lower surface of the pivot plate (151) forms a first thrust bearing surface (B1) together with the scroll support surface (134) of the main frame (130)
  • the upper surface of the pivot plate (151) forms a pivot thrust surface (151a) that forms a second thrust bearing surface (B2) together with the fixed thrust surface (142a) of the fixed side wall (142).
  • the upper surface of the pivot plate (151) facing the fixed thrust surface (142a) is defined as the pivot thrust surface (151a) and described.
  • An oil supply passage (155) is formed inside the turning plate (151).
  • One end of the oil supply passage (155) penetrates the lower surface of the turning plate (151) and is connected to the oil passage (1255) of the rotating shaft (125), and the other end of the oil supply passage (155) penetrates the upper surface of the turning plate (151), i.e., the turning thrust surface (151a). Accordingly, a portion of the oil sucked through the turning shaft (125) is supplied to the second thrust bearing surface (B2) to lubricate the second thrust bearing surface (B2).
  • the orbiting wrap (152) extends from the upper surface (compression surface) of the orbiting plate (151) toward the fixed scroll (140). Accordingly, the orbiting wrap (152) can be interlocked with the fixed wrap (143) to form two pairs of compression chambers (V1) (V2).
  • the orbital wrap (152) can be formed in various shapes, such as an involute, to correspond to the fixed wrap (143).
  • the orbital wrap (152) can be formed in a logarithmic spiral or in a plurality of circular arc curves.
  • the turning wrap (152) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In this embodiment, an example is shown in which the wrap height of the turning wrap (152) is the same along the wrap formation direction.
  • the rotary shaft insertion portion (153) can extend from the geometric center of the orbiting scroll (150) toward the eccentric portion (1251) of the rotary shaft (125).
  • the rotary shaft insertion portion (153) can be rotatably inserted into the eccentric portion (1251) of the rotary shaft (125). Accordingly, the orbiting scroll (150) is rotated by the eccentric portion (1251) of the rotary shaft (125) and the rotary shaft insertion portion (153).
  • the unexplained symbol 160 in the drawing is Oldham Ring.
  • the scroll compressor according to the above embodiment operates as follows.
  • the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually narrows as the orbiting scroll (150) moves from the suction port (or suction pressure chamber) (1411) toward the discharge port (or discharge pressure chamber) (1412) while performing the orbiting motion.
  • the refrigerant is introduced into the first compression chamber (V1) and the second compression chamber (V2) through the refrigerant suction pipe (115) and the suction port (1411) of the fixed scroll (140), and the refrigerant is compressed while moving toward the final compression chamber by the orbiting scroll (150).
  • the refrigerant is discharged from the final compression chamber to the discharge space (110b) of the casing (110) through the discharge port (1412) of the fixed scroll (140), and the refrigerant moves to the oil separation space (110c) or/and the oil storage space (110d) of the casing (110) through the discharge passage (not shown) provided in the fixed scroll (140) and the main frame (130).
  • the refrigerant circulates through the oil separation space (110c) of the casing (110), and the oil is separated from the refrigerant.
  • the refrigerant from which the oil has been separated is discharged to the outside of the casing (110) through the refrigerant discharge pipe (116), while the oil separated from the refrigerant moves to the oil storage space (110d) of the casing (110) and is stored therein, and then is supplied to the compression unit through the oil pickup (126) and the oil supply hole (1255) of the rotating shaft (125), repeating a series of processes.
  • the orbiting scroll (150) may be pushed toward the main frame (130). Then, as the orbiting scroll (150) separates from the fixed scroll (140), leakage may occur between the compression chambers (V). This may occur more significantly under high pressure ratio operating conditions.
  • a back pressure passage (170) that connects the compression chamber (Vm1) (Vm2) forming the intermediate pressure to the back pressure space (S) may be provided.
  • a portion of the refrigerant forming the intermediate pressure moves to the back pressure space (S) through the back pressure passage (170) and pressurizes the orbiting scroll (150) toward the fixed scroll (140), thereby suppressing the orbiting scroll (150) from being pushed by the pressure of the compression chamber (V).
  • the back pressure passage (170) is connected to one compression chamber (intermediate pressure chamber) (V), it may not be possible to form an appropriate back pressure for the operating conditions of the compressor. Therefore, in the present embodiment, the back pressure of the back pressure space (S) can be formed to vary in response to the operating conditions of the compressor. Through this, in low pressure ratio operation, the back pressure for the orbiting scroll (150) is relatively high, effectively suppressing leakage between the compression chambers (V1) (V2), and in high pressure ratio operation, the back pressure for the orbiting scroll (150) is relatively low, effectively reducing friction loss at the second thrust bearing surface (B2) formed between the two scrolls (140) (150). Through this, the operating range of the compressor can be expanded.
  • FIG. 2 is a perspective view showing the back pressure valve assembly according to the present embodiment disassembled from the fixed scroll
  • FIG. 3 is a perspective view showing the back pressure valve assembly according to the present embodiment assembled to the fixed scroll
  • FIG. 4 is a plan view of FIG. 3
  • FIG. 5 is a cross-sectional view showing part “A” of FIG. 4 broken off
  • FIG. 6 is a cross-sectional view taken along line “VI-VI” of FIG. 5
  • FIG. 7 is a cross-sectional view showing another embodiment of the fixed member in FIG. 5.
  • the fixed scroll (140) may be provided with the back pressure passage (170), back pressure valve assembly (180), and valve pressurization passage (190) described above.
  • the back pressure passage (170) is a passage that connects a plurality of compression chambers (more precisely, intermediate pressure chambers having an intermediate pressure between the suction pressure and the discharge pressure) (Vm1)(Vm2) having different intermediate pressures to the back pressure space (S)
  • the back pressure valve assembly (180) is a valve that selectively opens and closes the back pressure passage (170) to connect any one of the plurality of compression chambers (Vm1)(Vm2) to the back pressure space (S)
  • the valve pressurization passage (190) is a passage that selectively opens and closes the back pressure valve assembly (180) according to the pressure of the discharge space (110b).
  • the back pressure passage (170) can be opened and closed selectively by the back pressure valve assembly (180) to selectively open and close the corresponding compression chamber (Vm1) (Vm2) and the back pressure space (S), so that the back pressure of the back pressure space (S) can be appropriately varied according to the operating conditions of the compressor.
  • the back pressure passage (170) may include one valve receiving portion (171), a plurality of back pressure inlets (172), and one back pressure outlet portion (173).
  • the valve receiving portion (171) is a space in which the back pressure valve assembly (180) is received
  • the back pressure inlet portion (172) is one end of the back pressure passage (170) that is connected to the compression chamber (Vm1) (Vm2) forming the intermediate pressure chamber
  • the back pressure outlet portion (173) is the other end of the back pressure passage (170) that is connected to the back pressure space (S).
  • the back pressure passage (170) may be formed such that the back pressure inlets (172) and the back pressure outlet portions (173) are connected to each of the two ends of the valve receiving portion (171) with the valve receiving portion (171) interposed therebetween.
  • the valve receiving portion (171) may be formed in a smooth pipe shape with a single inner diameter, or may be formed in a multi-stage shape with multiple inner diameters. This embodiment illustrates an example in which the inner circumference of the valve receiving portion (171) is formed in a multi-stage shape with multiple inner diameters, since the position of the back pressure valve assembly (180) must be appropriately controlled within the valve receiving portion (171).
  • valve receiving portion (171) may be formed to be recessed by a preset length from the outer surface of the fixed plate portion (141) toward the discharge port (1412).
  • one end of the valve receiving portion (171) forming the end toward the discharge port (1412) is connected to the discharge space (110b) through a valve pressure passage (190) to be described later, and the other end of the valve receiving portion (171) forming the end toward the outer surface of the fixed plate portion (141) may be sealed using a separate blocking member (175).
  • a valve support surface (171a) and/or a fixed member support surface (171b) may be formed on the inner surface of the valve receiving portion (171).
  • the valve support surface (171a) is a surface that restricts movement of the back pressure valve (181) toward the discharge port (1412)
  • the fixed member support surface (171b) is a surface that restricts the fixing position of the fixed member (183) that fixes the other end of the elastic member (182).
  • the valve support surface (171a) and the fixed member support surface (171b) may be formed in sequence from the end of the valve receiving portion (171) toward the outer surface.
  • the pressure relief valve (181) can move stably because its movement position is limited by the valve support surface (171a), and the insertion depth of the fixed member (183) is limited by the fixed member support surface (171b), simplifying the assembly process while maintaining the elasticity of the elastic member (182) appropriately.
  • valve support surface (171a) and the fixed member support surface (171b) may be formed to have different inner diameters, but may be formed so that the inner diameters increase in the order of the valve support surface (171a) and the fixed member support surface (171b). Accordingly, the valve support surface (171a) and the fixed member support surface (171b) may be processed from the outer circumferential surface of the fixed plate portion (141) toward the discharge port (1412), so that each support surface (171a) (171b) may be easily formed.
  • the fixed member support surface (171b) may be formed in a circular shape like the valve support surface (171a), or may be formed in an arc shape.
  • This embodiment illustrates an example in which each support surface (171a) (171b) is formed in a circular shape. Accordingly, each support surface (171a) (171b) can stably support the back pressure valve (181), the elastic member (182), and the fixed member (183).
  • valve support surface (171a) may be formed on the inner surface of the valve receiving portion (171).
  • a valve support surface (171a) that restricts the movement of the back pressure valve (181) may be formed in a stepwise manner between the back pressure passage (170) and the valve pressure passage (190). Accordingly, the inner surface of the valve receiving portion is simplified and can be easily processed.
  • the back pressure inlet (172) can be connected to a plurality of compression chambers (Vm1) (Vm2) that form an intermediate pressure at one end of the valve receiving portion (171).
  • the back pressure inlet (172) penetrates through one side of the fixed plate portion (141) that forms the compression chambers (Vm1) (Vm2) in the valve receiving portion (171), and the back pressure inlet (172) can be formed to be connected to a plurality of compression chambers (Vm1) (Vm2) that form different intermediate pressures.
  • the plurality of back pressure inlets (172) can be selectively connected to one end of the valve receiving portion (171) depending on the position of the back pressure valve (181) to be described later.
  • the back pressure inlet (172) may include a first inlet (172a) and a second inlet (172b).
  • the first inlet (172a) may be connected to a compression chamber (or first intermediate pressure chamber) (Vm1) having a relatively high intermediate pressure
  • the second inlet (172b) may be connected to a compression chamber (or second intermediate pressure chamber) (Vm2) having a relatively low intermediate pressure
  • the inlet of the back pressure passage (170) may be connected to two compression chambers (Vm1) (Vm2) having different intermediate pressures, respectively.
  • the first inlet (172a) and the second inlet (172b) may be formed on the same line along the longitudinal direction of the valve receiving portion (171).
  • the first inlet (172a) and the second inlet (172b) may be formed on the same line in the radial direction with the back pressure outlet portion (173). Accordingly, by forming the inner diameter of the valve receiving portion (171) as small as possible, the inner diameter of the back pressure valve assembly (180) and/or the weight of the back pressure valve assembly (180) may be reduced to a minimum, thereby improving valve responsiveness.
  • the first inlet (172a) and the second inlet (172b) may be formed to have a cross-sectional area smaller than that of the valve receiving portion (171), but may be formed to have the same cross-sectional area.
  • the first inlet (172a) and the second inlet (172b) may be formed to have a circular shape smaller than or equal to the thickness of the swirl wrap (152), but may be formed to have the same shape and/or inner diameter for both inlets (172a) (172b).
  • first inlet (172a) and the second inlet (172b) may be formed to have the same shape, so that they can be easily processed, but they may be connected to compression chambers (Vm1) (Vm2) having different pressures, so that the back pressures of the back pressure space (S) can be formed differently.
  • the back pressure outlet (173) can be passed through one side of the fixed plate portion (141) facing the back pressure space portion (133) of the main frame (130) from the other end of the valve receiving portion (171).
  • the back pressure outlet portion (173) can be formed by passing through one side of the fixed plate portion (141) between the fixed member support surface (171b) and the blocking member (175). Accordingly, the back pressure outlet portion (173) can selectively connect the back pressure passage (170) to the back pressure space (S) depending on the position of the back pressure valve (181) described later.
  • the back pressure outlet portion (173) can be formed on the same line as the first inlet portion (172a) and the second inlet portion (172b) forming the back pressure inlet portion (172) based on the longitudinal direction of the valve receiving portion (171). Accordingly, the inner diameter of the valve receiving portion (171) can be minimized, thereby reducing the weight of the back pressure valve assembly (180).
  • the cross-sectional area of the back pressure outlet (173) may be formed to be the same as the cross-sectional area of the back pressure inlet (172).
  • the inner diameter of the back pressure outlet (173) may be formed to be the same as the inner diameter of the first inlet (172a) and/or the inner diameter of the second inlet (172b). Accordingly, the refrigerant discharged to the valve receiving portion (171) through the back pressure inlet (172) can quickly move to the back pressure space (S) through the back pressure outlet (173) without a pressure drop.
  • the back pressure valve assembly (180) can be inserted into the valve receiving portion (171) of the back pressure passage (170).
  • the back pressure valve assembly (180) can be formed as a type of piston valve that moves to a position to selectively open and close the first inlet portion (172a) and the second inlet portion (172b) by the pressure difference between the two ends. Accordingly, the back pressure valve (181) can be inserted into the interior of the fixed scroll (140) to suppress interference with surrounding members.
  • the back pressure valve assembly (180) may include a back pressure valve (181), an elastic member (182), and a fixing member (183).
  • the back pressure valve (181) is a member that substantially opens and closes the back pressure passage (170)
  • the elastic member (182) is a member that supports the back pressure valve (181) toward the discharge space (110b)
  • the fixing member (183) is a member that fixes an end of the elastic member (182). Accordingly, the back pressure valve assembly (180) is inserted into the valve receiving portion (171) of the back pressure passage (170) and can selectively open and close the back pressure passage (170) while moving according to the pressure difference between the discharge space (110b) and the back pressure space (S).
  • the back pressure valve (181) may include a valve body (1811) and a connecting passage (1812).
  • the valve body (1811) is a part that is slidably inserted into the back pressure passage (170) to open and close the back pressure inlet (172), and the connecting passage (1812) is a part that is selectively connected to the back pressure passage (170) depending on the position of the valve body (1811).
  • the valve body (1811) may include a plurality of opening/closing portions (1811a) (1811b) and a connecting portion (1811c).
  • the valve body (1811) may have a plurality of opening/closing portions (1811a) (1811b) extending radially from both ends of the connecting portion (1811c). Accordingly, not only can the valve body (1811) be easily manufactured, but also valve reliability can be improved.
  • the plurality of openings (1811a) (1811b) may be formed as a single body by extending in a flange shape from both ends of the connecting portion (1811c).
  • the plurality of openings (1811a) (1811b) may be formed such that their outer diameters are almost identical to the inner diameter of the valve receiving portion (171). Accordingly, the plurality of openings (1811a) (1811b) may be in sliding contact with the valve receiving portion (171) to tightly open and close the first inlet portion (172a) and/or the second inlet portion (172b).
  • the plurality of openings (1811a) (1811b) may include a first opening (1811a) and a second opening (1811b), and the gap between the first opening (1811a) and the second opening may be formed to be smaller than or equal to the gap between the first inlet (172a) and the second inlet (172b) of the back pressure inlet (172). Accordingly, the first inlet (172a) may be selectively opened and closed by the first opening (1811a), and the second inlet (172b) may be selectively opened and closed by the second opening.
  • the first opening/closing portion (1811a) may be formed at a position facing the valve pressure passage (190), and the second opening/closing portion may be formed at a position adjacent to the back pressure space (S). Accordingly, the first opening/closing portion (1811a) may form a pressurized portion pressurized by the pressure of the discharge space (110b), and the second opening/closing portion (1811b) may form a part of the connecting passage (1812).
  • the first opening/closing portion (1811a) is formed in a closed disc shape so that it can slidably contact the valve receiving portion (171). Accordingly, the first opening/closing portion (1811a) uniformly receives the pressure of the refrigerant transmitted from the discharge space (110b) through the valve pressure passage (190), and at the same time, tightly seals between the compression chambers (Vm1) (Vm2) forming an intermediate pressure and the valve pressure passage (discharge space) (190).
  • the second opening/closing portion (1811b) may be formed with a second passage portion (1812b) that opens to communicate between its two sides.
  • the second opening/closing portion (1811b) may be formed in a circular shape, and at least one second passage portion (1812b) may be formed along the circumference.
  • the second passage portion (1812b) is formed in a hole shape, but in some cases, it may be formed in a groove or a die-cut shape that is sunken into the outer surface of the second opening/closing portion (1812b).
  • the connecting portion (1811c) may be formed in a rod shape to connect the centers of the two opening/closing portions (1811a) (1811b) to each other.
  • the outer diameter of the connecting portion (1811c) may be formed to be smaller than the outer diameters of the two opening/closing portions (1811a) (1811b).
  • a first passage portion (1812a) forming a part of the connecting passage (1812) may be formed along the outer circumference of the connecting portion (1811c).
  • the outer diameter of the connecting portion (1811c) may be formed smaller than the virtual circle connecting the centers of the second passage portions (1812b). Accordingly, at least a portion of the first passage portion (1812a) may be connected in a straight line to the second passage portion (1812b).
  • the connecting portion (1811c) may be formed as a rectangle when projected longitudinally.
  • the connecting portion (1811c) may be cut in a die-cut shape on the outer surface of the valve body (1811) or may be formed by being recessed at a predetermined interval along the circumference. In these cases, the die-cut portion or the recessed portion may form the first passage portion (1812a).
  • the connecting passage (1812) may include a first passage portion (1812a) and a second passage portion (1812b).
  • the first passage portion (1812a) may be formed in the connecting portion (1811c) of the valve body (1811), and the second passage portion (1812b) may be formed in the second opening/closing portion (1811b) of the valve body (1811).
  • the first passage portion (1812a) may be formed along the outer circumferential surface of the connecting portion (1811c) formed to be smaller than the outer diameter of the second opening/closing portion (1811b), and the second passage portion (1812b) may be formed to penetrate the second opening/closing portion (1811b) but communicate with the first passage portion (1812a).
  • the connecting passage (1812) is formed to penetrate the interior of the valve body (1811), so that the corresponding compression chamber (Vm1) (Vm2) can be quickly moved to the back pressure space (S) depending on the position of the valve body (1811).
  • the elastic member (182) is made of a compression coil spring and can elastically support the end of the back pressure space (S) side of the back pressure valve (181).
  • one end of the elastic member (182) facing the discharge space (110b) may be in contact with the second opening/closing part (1811b) of the back pressure valve (181), and the other end of the elastic member (182) facing the back pressure space (S) may be supported by a fixing member (183) inserted into the valve receiving part (171).
  • the back pressure valve (181) is elastically supported toward the discharge space (110b) by the elastic member (182) inside the valve receiving part (171), so that a plurality of back pressure inlets (172a)(172b) can be selectively opened and closed depending on the pressure of the discharge space (110b).
  • the elastic member (182) may be formed so as not to interfere with the second passage (1812b) of the second opening/closing portion (1811b) described above, or so as to interfere with it as little as possible.
  • the inner diameter of the elastic member (182) may be formed to be larger than the inner diameter of the virtual circle connecting the centers of the second passages (1812b), or the outer diameter of the elastic member (182) may be formed to be smaller than the inner diameter of the virtual circle described above. Accordingly, the connection passage (1812) connected to the pressure relief passage (170) can be minimized from being covered by the elastic member (182).
  • an example in which the inner diameter of the elastic member (182) is formed to be larger than the inner diameter of the virtual circle described above is illustrated.
  • the fixing member (183) can be separated from the blocking member (175) and separately fixed to the valve receiving portion (171).
  • the fixing member (183) can be manufactured as a separate member from the blocking member (175) that seals the valve receiving portion (171) on the outer surface of the fixed plate portion (141) and assembled to the valve receiving portion (171). Accordingly, the manufacturing cost for the blocking member (175) can be reduced while ensuring the passage cross-sectional area in the valve receiving portion (171) as wide as possible.
  • the fixing member (183) may be formed in a ring shape and inserted into and fixed in the valve receiving portion (171).
  • the fixing member (183) may be formed in an annular shape and press-fitted or formed as a C-ring and fixed elastically. This embodiment illustrates an example in which the annular fixing member (183) is fixed by heat-fitting.
  • the inner surface of the valve receiving portion (171) may be formed in a smooth pipe shape or may be formed to be sunken into a fixing member insertion groove (not shown).
  • the processing of the valve receiving portion (171) can be simplified, while in the latter case, the insertion depth and/or fixing strength for the fixing member (183) can be increased.
  • the fixed member (183) may extend from the blocking member (175).
  • the fixed member (183) may extend long from the blocking member (175) toward the elastic member (182). Accordingly, the fastening force of the fixed member (183) is improved, so that the elastic member (182) can be stably fixed even if the fixed scroll (140) is overheated.
  • valve pressure passage (190) may be formed to communicate with the discharge space (110b) on the opposite side of the pressure passage (more precisely, the valve receiving portion) (170) with the pressure valve (181) as the center.
  • the valve pressure passage (190) may be formed such that one side of the pressure valve (181) slidably inserted into the valve receiving portion (171) faces it.
  • the back pressure valve (181) moves to a position (hereinafter, first position) where the first inlet (172a) is opened and the second inlet (172b) is blocked, or conversely, to a position (hereinafter, second position) where the first inlet (172a) is blocked and the second inlet (172b) is opened.
  • valve pressurization passage (190) may be opened toward the back surface of the fixed plate portion (141) forming the discharge space (110b), and the other end of the valve pressurization passage (190) may be opened toward the valve receiving portion (171) described above. Accordingly, a portion of the refrigerant discharged to the discharge space (110b) through the discharge port (1412) moves to the valve receiving portion (171) forming the back pressure passage (170) through the valve pressurization passage (190) and pressurizes the first opening/closing portion (1811a) of the back pressure valve (181).
  • the center of the valve pressurization passage (190) may be formed to be positioned on the same line as the center of the valve receiving portion (171).
  • the center of the valve pressurization passage (190) facing the valve receiving portion (171) may be formed to be positioned on the same line as the center of the first opening/closing portion (1811a) facing the valve pressurization passage (190). Accordingly, the pressure of the refrigerant transmitted through the valve pressurization passage (190) uniformly pressurizes the back pressure valve (181), so that the back pressure valve (181) can operate quickly and stably.
  • one end of the valve pressure passage (190) may be formed by penetrating the inner surface of the discharge port (1412). In this case, since the valve pressure passage (190) is formed in a straight line, the number of processing steps for the valve pressure passage (190) can be reduced, thereby lowering the manufacturing cost.
  • a back pressure passage (170) that connects the compression chamber and the back pressure space (S) is connected to a plurality of compression chambers (Vm1) (Vm2) having different pressures, and a back pressure valve (181) that moves according to the pressure of the discharge space (110b) and selectively connects a plurality of compression chambers (Vm1) (Vm2) having different pressures to the back pressure space (S) may be provided inside the back pressure passage (170). Accordingly, the position of the back pressure valve (181) can be changed in accordance with the operating conditions of the compressor, and the back pressure of the back pressure space (S) can be appropriately controlled. Through this, leakage between compression chambers in low pressure ratio operation and/or friction loss between scrolls in high pressure ratio operation can be suppressed, thereby expanding the operating range of the compressor.
  • FIG. 8a and FIG. 8b are cross-sectional views showing the operation of the back pressure valve assembly according to the operating conditions of the compressor in FIG. 2, with FIG. 8a showing the low pressure ratio operating conditions and FIG. 8b showing the high pressure ratio operating conditions, respectively.
  • the pressure in the discharge space (110b) decreases.
  • the refrigerant with relatively low pressure is delivered to the back pressure valve (181) through the valve pressurization passage (190).
  • the back pressure valve (181) is pushed by the elastic force of the elastic member (182) to maintain the initial position, i.e., the first position.
  • the first opening/closing part (1811a) opens the first inlet part (172a), while the second opening/closing part (1811b) blocks the second inlet part (172b).
  • the refrigerant in the compression chamber (Vm1) with relatively high intermediate pressure is delivered to the back pressure space (S) through the first inlet part (172a), the connecting passage (1812), the valve receiving part (171), and the back pressure outlet part (173).
  • the back pressure space (S) forms a relatively high first back pressure and strongly presses the orbiting scroll (150) toward the fixed scroll (140).
  • the orbiting scroll (150) is pressed relatively strongly against the fixed scroll (140), effectively preventing leakage between compression chambers.
  • the refrigerant in the compression chamber (Vm2) with relatively low intermediate pressure is delivered to the back pressure space (S) through the second inlet part (172b), the connecting passage (1812), the valve receiving part (171), and the back pressure outlet part (173).
  • the back pressure space (S) forms a relatively low second back pressure and slightly presses the orbiting scroll (150) toward the fixed scroll (140).
  • the orbiting scroll (150) is relatively weakly pressed against the fixed scroll (140), so that frictional loss between the scrolls can be effectively suppressed.
  • multiple compression chambers having different pressures are collectively connected to one pressure passage, but in some cases, multiple compression chambers having different pressures may be independently connected to multiple pressure passages.
  • FIG. 9 is a plan view of a fixed scroll shown to explain another embodiment of a back pressure valve assembly
  • FIG. 10 is a cross-sectional view taken along line “X-X” of FIG. 9.
  • a scroll compressor according to the present embodiment is provided with a back pressure passage (170) that connects a plurality of compression chambers (Vm1) (Vm2) having different pressures in a fixed scroll (140) to a back pressure space (S), and a back pressure valve assembly (180) that selectively opens and closes the back pressure passage (170) is provided in the back pressure passage (170), and a valve pressure passage (190) that is connected to a discharge space (110b) of a casing (110) can be connected to one end of the back pressure passage (170).
  • the pressure of the discharge space (110b) varies depending on the operating conditions of the compressor, and the position of the back pressure valve assembly (180) facing the valve pressure passage (190) connected to the discharge space (110b) moves to the first position and the second position, so that the back pressure of the back pressure space (S) can be appropriately varied.
  • the back pressure passage (170) is divided into a plurality of back pressure passages (170a)(170b), and each back pressure valve assembly (180a)(180b) is provided in each back pressure passage (170a)(170b), and each valve pressure passage (190a)(190b) can be connected to the opposite side of each back pressure passage (170a)(170b) with each back pressure valve assembly (180a)(180b) therebetween.
  • a plurality of compression chambers (Vm1) (Vm2) having different pressures are independently connected to the back pressure space (S) by respective back pressure passages (170a) (170b), and each back pressure passage (170a) (170b) is provided with a respective back pressure valve assembly (180a) (180b) that selectively opens and closes the respective back pressure passages (170a) (170b), and each valve pressure passage (190a) (190b) for opening and closing the respective back pressure valve assemblies (180a) (180b) can be independently connected to one end of each back pressure passage (170a) (170b) facing each back pressure valve assembly (180a) (180b).
  • the back pressure passage (170) may include a first back pressure passage (170a) and a second back pressure passage (170b).
  • the first back pressure passage (170a) and the second back pressure passage (170b) may be formed symmetrically on the same line, or in some cases, may be formed symmetrically on different lines.
  • the present embodiment shows an example in which the first back pressure passage (170a) and the second back pressure passage (170b) are formed symmetrically at a position where they intersect each other.
  • first back pressure passage (170a) and the second back pressure passage (170b) are formed in an empty space of the fixed scroll (140) while avoiding a bypass hole (not shown), etc., and the processing of the first back pressure passage (170a) and the second back pressure passage (170b) can be uniform, thereby reducing the manufacturing cost. Since these first pressure passages (170a) and second pressure passages (170b) are formed almost identically to the pressure passages (170) in the embodiment of FIG. 6 described above, the description thereof will be replaced with the description of the embodiment described above.
  • the back pressure valve assembly (180) may include a first back pressure valve assembly (180a) and a second back pressure valve assembly (180b).
  • the first back pressure valve assembly (180a) and the second back pressure valve assembly (180b) may be formed with the same shape, or in some cases, may be formed with different shapes.
  • This embodiment illustrates an example in which the first back pressure valve assembly (180a) and the second back pressure valve assembly (180b) are formed with the same shape. Accordingly, the manufacturing and/or assembly of the back pressure valve assemblies (180a) (180b) can be standardized, thereby reducing the manufacturing cost. Since these first back pressure valve assembly (180a) and second back pressure valve assembly (180b) are formed in the same manner as the back pressure valve assembly (180) in the embodiment of FIG. 6 described above, the description thereof will be replaced with the description of the embodiment described above.
  • the valve pressurization passage (190) may include a first valve pressurization passage (190a) and a second valve pressurization passage (190b).
  • the first valve pressurization passage (190a) and the second valve pressurization passage (190b) may be formed to be independently connected to each of the back pressure passages (170a) (170b), and in some cases, a single valve pressurization passage (not shown) may be formed to be connected in parallel to a plurality of back pressure passages (170a) (170b).
  • This embodiment illustrates an example in which the first valve pressurization passage (190a) and the second valve pressurization passage (190b) are formed independently.
  • first valve pressurized passage (190a) and the second valve pressurized passage (190b) can be appropriately formed in the empty space of the fixed scroll (140) while avoiding bypass holes, etc., and the manufacturing cost can be reduced by uniformizing the processing of the first valve pressurized passage (190a) and the second valve pressurized passage (190b). Since these first valve pressurized passage (190a) and the second valve pressurized passage (190b) are formed almost identically to the valve pressurized passage (190) in the embodiment of FIG. 6 described above, the description thereof will be replaced with the description of the embodiment described above.
  • the back pressure of the back pressure space (S) can be appropriately controlled according to the operating conditions of the compressor.
  • back pressure passages (170a)(170b) are formed to independently communicate with multiple compression chambers (Vm1)(Vm2), not only is the operational reliability of the back pressure valve (181a)(181b) improved, but also the back pressure of the back pressure space (S) can be optimized by appropriately adjusting the position of the back pressure passages (170a)(170b) that communicate with the intermediate pressure depending on the operating conditions.
  • FIG. 11a and FIG. 11b are cross-sectional views showing the operation of the back pressure valve assembly according to the operating conditions of the compressor in FIG. 9, with FIG. 11a showing the low pressure ratio operating conditions and FIG. 11b showing the high pressure ratio operating conditions, respectively.
  • the pressure in the discharge space (110b) decreases.
  • the refrigerant with relatively low pressure is delivered to the first back pressure valve (181a) and the second back pressure valve (181b) through the first valve pressurization passage (190a) and the second valve pressurization passage (190b).
  • the first back pressure valve (181a) and the second back pressure valve (181b) are pushed by the elastic force of the first elastic member (182a) and the second elastic member (182b) to maintain their first positions, respectively.
  • the first opening/closing part (1811a1) of the first back pressure valve (181a) opens the first back pressure inlet part (1721) of the first back pressure passage (170a), while the second opening/closing part (1811b2) of the second back pressure valve (181b) blocks the second back pressure inlet part (1722) of the second back pressure passage (170b).
  • the refrigerant in the compression chamber (P1) having a relatively high intermediate pressure is transferred to the back pressure space (S) through the first back pressure inlet part (1721), the first connection passage (1813a), the first valve receiving part (1711), and the first back pressure outlet part (1731).
  • the back pressure space (S) strongly presses the orbiting scroll (150) toward the fixed scroll (140) while forming a relatively high first back pressure. Then, the orbiting scroll (150) can be tightly pressed against the fixed scroll (140) to effectively prevent leakage between compression chambers.
  • the first opening/closing part (1811a1) of the first back pressure valve (181a) blocks the first back pressure inlet part (1721) of the first back pressure passage (170a), while the second opening/closing part (1811b2) of the second back pressure valve (181b) opens the second back pressure inlet part (1722) of the second back pressure passage (170b).
  • the refrigerant in the compression chamber (Vm2) having a relatively low intermediate pressure is transferred to the back pressure space (S) through the second back pressure inlet part (1722), the second connection passage (1813b), the second valve receiving part (1712), and the second back pressure outlet (1732).
  • the back pressure space (S) forms a relatively low second back pressure while slightly pressurizing the orbiting scroll (150) toward the fixed scroll (140). Then, the rotating scroll (150) can be relatively weakly pressed against the fixed scroll (140), effectively suppressing friction loss between the scrolls. This allows the operating range of the compressor to be expanded.
  • the back pressure passage may be formed to communicate with three or more compression chambers.
  • one back pressure passage may have three or more back pressure inlets, or three or more back pressure passages may be formed independently.
  • the back pressure of the back pressure space can be adjusted in a more diverse manner depending on the operating conditions of the compressor, thereby more effectively suppressing leakage between compression chambers and/or friction loss between scrolls. This allows the operating range of the compressor to be expanded.
  • the focus has been on a high-pressure scroll compressor in which the driving motor is provided in the discharge space, but the same can be applied to a low-pressure scroll compressor in which the driving motor is provided in the suction space but the discharge space is provided on the discharge side of the compression section.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

La présente invention divulgue un compresseur à spirale. Le compresseur à spirale comprend un carter, un cadre principal, une spirale orbitale, une spirale fixe, un espace de contre-pression, un passage de contre-pression et une soupape de contre-pression, la soupape de contre-pression étant disposée dans le passage de contre-pression de façon à ouvrir/fermer sélectivement le passage de contre-pression, et le passage de contre-pression pouvant être en communication avec une pluralité de chambres de compression ayant des pressions différentes parmi des chambres de compression. Ainsi, dans le passage de contre-pression, une chambre de compression correspondante et l'espace de contre-pression sont sélectivement ouverts/fermés par la soupape de contre-pression, et par conséquent, la contre-pression de l'espace de contre-pression est variable de manière appropriée en fonction de l'état d'entraînement du compresseur, et une fuite entre les chambres de compression et/ou une perte de frottement entre les spirales peuvent être limitées. De plus, la zone opérationnelle du compresseur peut être étendue.
PCT/KR2024/004635 2024-04-08 2024-04-08 Compresseur à spirale Pending WO2025216335A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/KR2024/004635 WO2025216335A1 (fr) 2024-04-08 2024-04-08 Compresseur à spirale

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2024/004635 WO2025216335A1 (fr) 2024-04-08 2024-04-08 Compresseur à spirale

Publications (1)

Publication Number Publication Date
WO2025216335A1 true WO2025216335A1 (fr) 2025-10-16

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WO (1) WO2025216335A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05340363A (ja) * 1992-06-09 1993-12-21 Hitachi Ltd スクロール圧縮機
JPH10325396A (ja) * 1997-05-27 1998-12-08 Mitsubishi Heavy Ind Ltd スクロール圧縮機及びその背圧制御弁
KR102072154B1 (ko) * 2018-09-19 2020-01-31 엘지전자 주식회사 스크롤 압축기
KR20210123446A (ko) * 2020-04-02 2021-10-14 두원중공업(주) 스크롤 압축기
KR20220030345A (ko) * 2020-08-27 2022-03-11 두원중공업(주) 스크롤 압축기의 배압제어 밸브

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05340363A (ja) * 1992-06-09 1993-12-21 Hitachi Ltd スクロール圧縮機
JPH10325396A (ja) * 1997-05-27 1998-12-08 Mitsubishi Heavy Ind Ltd スクロール圧縮機及びその背圧制御弁
KR102072154B1 (ko) * 2018-09-19 2020-01-31 엘지전자 주식회사 스크롤 압축기
KR20210123446A (ko) * 2020-04-02 2021-10-14 두원중공업(주) 스크롤 압축기
KR20220030345A (ko) * 2020-08-27 2022-03-11 두원중공업(주) 스크롤 압축기의 배압제어 밸브

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