WO2020004165A1 - Compresseur à capacité variable - Google Patents

Compresseur à capacité variable Download PDF

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Publication number
WO2020004165A1
WO2020004165A1 PCT/JP2019/024240 JP2019024240W WO2020004165A1 WO 2020004165 A1 WO2020004165 A1 WO 2020004165A1 JP 2019024240 W JP2019024240 W JP 2019024240W WO 2020004165 A1 WO2020004165 A1 WO 2020004165A1
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WO
WIPO (PCT)
Prior art keywords
valve
passage
pressure
port
chamber
Prior art date
Application number
PCT/JP2019/024240
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English (en)
Japanese (ja)
Inventor
田口　幸彦
清人 菊池
Original Assignee
サンデン・オートモーティブコンポーネント株式会社
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 サンデン・オートモーティブコンポーネント株式会社 filed Critical サンデン・オートモーティブコンポーネント株式会社
Priority to CN201980040568.7A priority Critical patent/CN112313413B/zh
Publication of WO2020004165A1 publication Critical patent/WO2020004165A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block

Definitions

  • the present invention relates to a variable displacement compressor used for, for example, an air conditioner for a vehicle.
  • variable displacement compressor which is provided with a displacement control valve and whose discharge displacement is controlled by regulating the pressure in a crank chamber
  • a first valve unit that opens and closes a supply passage and a second valve unit that opens and closes a pressure release passage are provided downstream of a control valve that controls an opening degree of a supply passage.
  • a switching valve including a spool that moves in accordance with the pressure difference between the front and rear.
  • the switching valve has a configuration in which a back pressure chamber and a valve chamber are partitioned, a pressure receiving section is provided in the back pressure chamber, and a valve section is provided in the valve chamber. For this reason, the length of the switching valve along the axial direction of the drive shaft becomes longer, and it becomes difficult to arrange the switching valve inside the variable displacement compressor. Therefore, the present invention provides a variable displacement compressor in which a switching valve can be easily arranged inside and a pressure adjustment of a control pressure chamber such as a crank chamber can be prevented from being delayed. Aim.
  • one embodiment of the present invention is to supply refrigerant in a discharge chamber to a control pressure chamber through a supply passage and discharge refrigerant in the control pressure chamber to a suction chamber through a discharge passage.
  • This is a variable displacement compressor in which the pressure in the control pressure chamber is adjusted to control the displacement.
  • the variable displacement compressor includes a control valve for adjusting the opening degree of the supply passage, a switching valve provided closer to the control pressure chamber than the control valve in the supply passage, and a control valve and a switching valve of the supply passage.
  • a throttle passage communicating the upstream supply passage and the suction chamber therebetween is included.
  • the switching valve includes a first wall surface, a second wall surface, a valve chamber, a main valve body, and a sub-valve body, and switches between a first state and a second state in conjunction with opening and closing of the control valve. .
  • a first port communicating with the upstream supply passage opens in the first wall surface.
  • the second wall surface has a second port communicating with the downstream supply passage between the switching valve and the control pressure chamber in the supply passage, and a third port communicating with the suction chamber is open. Confront each other.
  • the valve chamber is defined by a first wall surface and a second wall surface, and a peripheral wall provided between the first wall surface and the second wall surface.
  • the main valve body is housed in the valve chamber, and moves between the first wall surface and the second wall surface according to the pressure difference between the pressure in the upstream supply passage and the pressure in the downstream supply passage.
  • the sub-valve is housed in the main valve and is formed to be lighter than the main valve.
  • the first state is a state in which the first port communicates with the second port.
  • the second state is a state in which the third supply port communicates with the second port to allow the downstream supply passage to function as a part of a discharge passage for discharging the refrigerant in the control pressure chamber to the suction chamber.
  • the main valve body includes a first valve portion, a second valve portion, and an in-valve passage.
  • the first valve portion has a first end surface that opens and closes the first port by contacting or separating from the first wall surface and receives the pressure of the upstream supply passage via the first port.
  • the second valve portion opens and closes the third port by contacting or separating from the second wall surface, and has a second end surface that receives the pressure of the downstream supply passage through the second port.
  • One of the in-valve passages is open at the first end face and the other is open at the second end face.
  • the sub-valve element opens the valve passage when the pressure of the upstream supply passage becomes higher than the pressure of the downstream supply passage, and closes the valve passage when the pressure of the upstream supply passage becomes lower than the pressure of the downstream supply passage.
  • the sub-valve which is lighter than the main valve, is earlier than the main valve. Move to close the valve passage.
  • the refrigerant in the control pressure chamber is suppressed from flowing into the valve chamber via the internal passage, and the pressure in the valve chamber, the first port, and the upstream passage is quickly reduced to the pressure in the suction chamber. Therefore, a delay in the movement of the main valve body and a delay in lowering the pressure in the control pressure chamber due to the delay in the movement of the main valve body are suppressed.
  • FIG. 2 is an enlarged view of a range surrounded by a line II in FIG. 1. It is a figure showing the structure of a valve room.
  • FIG. 4 is a sectional view taken along line IV-IV of FIG. 3. It is a figure showing the structure of a valve element. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the modification of a 1st embodiment. It is a figure showing the modification of a 1st embodiment. It is a figure showing the modification of a 1st embodiment. It is a figure showing the modification of a 1st embodiment. It is a figure showing the modification of a 1st embodiment. It is a figure showing the modification of a 1st embodiment. It is
  • the first embodiment described below exemplifies a configuration for embodying the technical idea of the present invention
  • the technical idea of the present invention is based on the materials of components, their shapes, The structure, arrangement, etc. are not specified as follows.
  • the technical idea of the present invention can be variously modified within the technical scope defined by the claims described in the claims.
  • the directions “left and right” and “up and down” in the following description are simply definitions for convenience of description, and do not limit the technical idea of the present invention. Therefore, for example, if the paper is rotated 90 degrees, “left and right” and “up and down” are read interchangeably, and if the paper is rotated 180 degrees, “left” becomes “right” and “right” becomes “left”. Of course.
  • variable displacement compressor 1 includes a cylinder block 2, a front housing 3, a valve plate 4, a cylinder head 5, a drive shaft 6, a supply passage 7, a discharge passage 8, A control valve 9 and a switching valve 10 are provided.
  • the upper side in FIG. 1 is the upper side in the vertical direction.
  • the lower part in FIG. 1 is the lower part in the vertical direction.
  • variable displacement compressor 1 is configured as a clutchless variable displacement compressor applied to an air conditioner system (air conditioner system) for a vehicle (vehicle).
  • air conditioner system air conditioner system
  • vehicle vehicle
  • the cylinder block 2, the front housing 3, the valve plate 4, and the cylinder head 5 are fastened by through bolts 11 via a gasket (not shown) to form a housing of the variable displacement compressor 1.
  • a plurality of cylinder bores 21 and one center bore 22 are formed in the cylinder block 2.
  • the plurality of cylinder bores 21 are arranged annularly.
  • a piston 23 is housed inside the cylinder bore 21.
  • the center bore 22 is arranged radially inside the plurality of annularly arranged cylinder bores 21 at the center, and is a space penetrating the cylinder block 2.
  • the front housing 3 closes one end side (the left side in FIG. 1) of the cylinder block 2.
  • the front housing 3 forms a crank chamber 30 together with the cylinder block 2.
  • the crank chamber 30 is a space formed by the front housing 3 and the cylinder block 2, and has a swash plate 31 disposed therein.
  • the drive shaft 6 is disposed inside the crank chamber 30 so that the axial direction thereof is horizontal.
  • the swash plate 31 is formed in an annular shape and surrounds the drive shaft 6 from the radial direction.
  • the swash plate 31 is connected to a rotor 32 fixed to the drive shaft 6 via a link mechanism 33, and rotates together with the drive shaft 6.
  • the swash plate 31 can change the inclination angle (inclination angle) with respect to the axis of the drive shaft 6.
  • the link mechanism 33 includes a first arm 33a, a second arm 33b, and a link arm 33c.
  • the first arm 33a protrudes from a surface of the rotor 32 facing the swash plate 31.
  • the second arm 33b protrudes from a surface of the swash plate 31 facing the rotor 32.
  • One end of the link arm 33c is rotatably connected to the first arm 33a via a first connection pin 33d.
  • the other end of the link arm 33c is rotatably connected to the second arm 33b via a second connection pin 33e.
  • the swash plate 31 is formed with a through hole 34 in such a shape that the swash plate 31 can be tilted within a range of the maximum tilt angle and the minimum tilt angle.
  • the through-hole 34 is formed with a minimum inclination restricting portion (not shown) that contacts the drive shaft 6.
  • the minimum inclination restricting unit can displace the swash plate 31 by approximately 0 [°]. It is formed to be possible. Further, when the inclination angle of the swash plate 31 is maximized, the swash plate 31 comes into contact with the rotor 32 and the increase of the inclination angle is restricted.
  • an inclination-reducing spring 35 that urges the swash plate 31 in the direction of decreasing the inclination until the swash plate 31 has the minimum inclination.
  • a tilt-increase spring 37 that urges the swash plate 31 in a direction to increase the tilt angle is mounted.
  • the urging force of the inclination increasing spring 37 at the minimum inclination is set to be larger than the urging force of the inclination decreasing spring 35. Therefore, when the drive shaft 6 is not rotating, the inclination angle of the swash plate 31 is an angle at which the urging force of the inclination decreasing spring 35 and the urging force of the inclination increasing spring 37 are balanced.
  • the outer peripheral portion of the swash plate 31 is accommodated in an inner space formed at an end of the piston 23 protruding toward the crank chamber 30.
  • the swash plate 31 is configured to interlock with the piston 23 via the pair of shoes 38. Accordingly, the rotation of the swash plate 31 accompanying the rotation of the drive shaft 6 causes each piston 23 to reciprocate inside the accommodated cylinder bore 21. That is, the swash plate 31 and the shoe 38 form a reciprocating motion converting unit that converts the rotation of the drive shaft 6 into the reciprocating motion of the piston 23.
  • valve plate 4 The valve plate 4 is provided between the cylinder block 2 and the cylinder head 5. One surface of the valve plate 4 closes the other end side (the right side in FIG. 1) of the cylinder block 2 so that each cylinder bore 21 is closed. It is closed. Further, a discharge hole 41 and a suction hole 42 are formed in the valve plate 4. The discharge hole 41 and the suction hole 42 communicate with the respective cylinder bores 21.
  • the cylinder head 5 is arranged to face the cylinder block 2 with the valve plate 4 interposed therebetween. That is, the cylinder head 5 is provided on the other end side of the cylinder block 2 via the valve plate 4. Further, the cylinder head 5 is formed with a suction chamber 51 and a discharge chamber 52 partitioned inside the cylinder head 5. The suction chamber 51 and the discharge chamber 52 are closed by the other surface of the valve plate 4.
  • the suction chamber 51 is disposed at the center of the cylinder head 5 when viewed from the axial direction of the drive shaft 6.
  • the suction chamber 51 is connected to a suction side external refrigerant circuit of the air conditioner system via a suction port 53 and a suction passage 54, and a low pressure side refrigerant (refrigerant gas) from the suction side external refrigerant circuit. Inhalation.
  • the suction chamber 51 communicates with each cylinder bore 21 via a suction hole 42 provided in the valve plate 4 and a suction valve (not shown).
  • the discharge chamber 52 is disposed at a position surrounding the suction chamber 51 in a ring shape when viewed from the axial direction of the drive shaft 6.
  • the discharge chamber 52 communicates with each cylinder bore 21 via a discharge valve (not shown) and a discharge hole 41 provided in the valve plate 4.
  • the low-pressure side refrigerant sucked into the suction chamber 51 from the suction side external refrigerant circuit is sucked into the cylinder bore 21 containing the piston 23 by the reciprocating motion of the piston 23.
  • the reciprocating motion of the piston 23 causes the piston 23 to be compressed to a high pressure and discharged to the discharge chamber 52. That is, the cylinder bore 21 and the piston 23 form a compression unit that compresses the refrigerant drawn into the suction chamber 51.
  • the discharge chamber 52 is connected to a discharge-side external refrigerant circuit of the air conditioning system via a discharge passage 55 and a discharge port 56.
  • the refrigerant discharged into the discharge chamber 52 and compressed by the compression unit is discharged as a high-pressure refrigerant (refrigerant gas) to the external refrigerant circuit on the discharge side via the discharge passage 55 and the discharge port 56.
  • a discharge check valve 57 is arranged between the discharge chamber 52 and the discharge passage 55.
  • the discharge check valve 57 operates in response to a pressure difference between the discharge chamber 52 (upstream) and the discharge passage 55 (downstream).
  • the discharge check valve 57 shuts off the space between the discharge chamber 52 and the discharge passage 55, and the refrigerant flows from the discharge passage 55 to the discharge chamber 52. Prevent movement.
  • the discharge check valve 57 makes the discharge chamber 52 and the discharge passage 55 communicate with each other. Therefore, the high-pressure side refrigerant discharged from the discharge chamber 52 to the discharge-side external refrigerant circuit through the discharge passage 55 and the discharge port 56 is prevented from flowing backward by the discharge check valve 57.
  • the drive shaft 6 is disposed inside the front housing 3 and the cylinder block 2, and both ends are rotatably supported by the front housing 3 and the cylinder block 2. One end of the drive shaft 6 is inserted into the center bore 22. A first slide bearing 61 is arranged between the drive shaft 6 and the center bore 22. An end surface of the drive shaft 6 on the side facing the valve plate 4 is supported by an annular thrust plate 62. The contact state (gap) between the drive shaft 6 and the thrust plate 62 is adjusted by the attachment state of the adjustment screw 63 to the cylinder block 2.
  • the adjusting screw 63 is formed in an annular shape, and has a male screw (not shown) formed on an outer diameter surface.
  • the adjusting screw 63 is disposed inside the center bore 22 at a position closer to the valve plate 4 than the drive shaft 6 by fitting a male screw to the female screw of the center bore 22.
  • the gap portion of the adjustment screw 63 is formed in a hexagonal shape.
  • the adjusting screw 63 is formed with a screw-side passage 63 a that allows a surface of the adjusting screw 63 facing the drive shaft 6 to communicate with an outer diameter surface of the adjusting screw 63.
  • the screw-side passage 63a is formed in a shape in which a part of a surface of the adjusting screw 63 facing the drive shaft 6 is cut away when viewed from the axial direction of the drive shaft 6. Therefore, a portion of the surface of the adjusting screw 63 facing the drive shaft 6 where the screw side passage 63 a is not formed is in contact with the thrust plate 62.
  • a part of the other end of the drive shaft 6 projects outside the front housing 3 and is connected to a power transmission device (not shown).
  • the power transmission device is connected to a driving force generating source (not shown) such as an engine via a belt. Therefore, when the driving force generated by the driving force generation source is transmitted to the power transmission device, the drive shaft 6 can rotate in synchronization with the rotation of the power transmission device.
  • a second sliding bearing 64 and a shaft sealing device 65 are arranged between the drive shaft 6 and the front housing 3.
  • the second sliding bearing 64 supports the drive shaft 6 rotatably in the radial direction. Further, a load in the thrust direction toward the other end of the drive shaft 6 is supported by a thrust bearing 66 via the rotor 32.
  • the connected body formed by the drive shaft 6 and the rotor 32 is supported by the first sliding bearing 61 and the second sliding bearing 64 so as to be rotatable in the radial direction, and the thrust plate 62 and the thrust bearing 66 provide thrust. It is supported so that it can rotate in the direction.
  • the shaft sealing device 65 blocks the inside of the crank chamber 30 from the external space. Note that lubricating oil (not shown) is sealed inside the variable capacity compressor 1 and the oil is stirred when the drive shaft 6 rotates. When the refrigerant moves inside the variable displacement compressor 1, oil moves together with the refrigerant, and the inside of the variable displacement compressor 1 is lubricated.
  • the supply passage 7 is a passage that supplies the refrigerant in the discharge chamber 52 to the crank chamber 30.
  • the supply passage 7 has a head-side supply passage forming portion 71, a plate-side supply passage forming portion 72, and an in-shaft passage 81, as shown in FIG.
  • the head-side supply passage forming portion 71 is a passage formed in the cylinder head 5 in the supply passage 7, and a portion of the supply passage 7 for discharging the refrigerant supplied from the discharge chamber 52 and a plate-side supply passage formation portion.
  • the section 72 is communicated with the section 72.
  • the plate-side supply passage forming portion 72 is a portion of the supply passage 7 formed in the valve plate 4, and communicates the head-side supply passage forming portion 71 with the valve chamber 100.
  • a throttle passage 74 that connects the plate-side supply passage forming portion 72 of the supply passage 7 with the suction chamber 51 is formed. A detailed description of the valve chamber 100 will be described later.
  • the throttle passage 74 includes the upstream supply passage (the head-side supply passage forming portion 71 and the plate-side supply passage forming portion 72) between the control valve 9 and the switching valve 10 in the supply passage 7, and the suction chamber. It is a passage communicating with 51.
  • the shaft passage 81 is a passage formed in the drive shaft 6 in the supply passage 7. One end of the in-shaft passage 81 is open to the side surface of the drive shaft 6, and communicates with the crank chamber 30 via the oil introduction passage 39. The other end of the in-shaft passage 81 is open at the end face of the drive shaft 6 on the side facing the valve plate 4. Therefore, the shaft passage 81 communicates the crank chamber 30 with the valve chamber 100.
  • the oil introduction passage 39 is formed in the front housing 3 at a position vertically above the drive shaft 6 when the variable displacement compressor 1 is mounted on the vehicle, and accommodates the crank chamber 30 and the shaft sealing device 65. It is a passage that communicates with the accommodation space 67, which is a space that performs the operation. An opening of the oil introduction passage 39 that opens into the housing space 67 is formed closer to the crank chamber 30 than the shaft sealing device 65 along the axial direction of the drive shaft 6.
  • the discharge passage 8 is a passage for discharging the refrigerant in the crank chamber 30 to the suction chamber 51.
  • the discharge passage 8 has a first discharge passage 8a and a second discharge passage 8b.
  • the first discharge passage 8a has an in-shaft passage 81, a block-side discharge passage forming portion 82, and a plate-side discharge passage forming portion 83.
  • the in-shaft passage 81 is a passage formed in the drive shaft 6 in the discharge passage 8.
  • the block-side discharge passage forming portion 82 is a passage formed in the cylinder block 2 of the discharge passage 8, and includes an expansion portion 82a and a discharge portion 82b.
  • the expansion portion 82a is a passage formed between the cylinder bore 21 and the center bore 22 in the cylinder block 2, and communicates the in-shaft passage 81 with the discharge portion 82b. That is, the expansion portion 82a of the discharge passage 8 is provided at a position closer to the crank chamber 30 than the valve chamber 100, communicates with the third port P3, and has a larger flow path cross-sectional area than the third port P3. .
  • the description of the third port P3 will be described later.
  • the discharge portion 82b is a passage formed in the cylinder block 2 at a position farther from the crank chamber 30 than the expansion portion 82a, and communicates the expansion portion 82a with the plate-side discharge passage formation portion 83.
  • the discharge portion 82b of the discharge passage 8 is disposed outside the valve chamber 100 in the radial direction (radial direction of the drive shaft 6) as viewed from the axial direction of the drive shaft 6, and the expansion portion 82a and the suction chamber 51 And the cross-sectional area of the flow passage is smaller than that of the expansion portion 82a.
  • the block-side discharge passage forming portion 82 is formed, for example, by closing an opening of the extension portion 82 a on the crank chamber 30 side of the center bore 22 with a closing member 84.
  • the plate-side discharge passage forming portion 83 is an opening formed in the valve plate 4 in the discharge passage 8, and connects the discharge portion 82b and the suction chamber 51 to each other.
  • the first discharge passage 8a is a passage for discharging the refrigerant in the crank chamber 30 to the suction chamber 51 via the second port P2, the valve chamber 100, and the third port P3 in this order.
  • the second discharge passage 8b includes a throttle 84a formed in the closing member 84.
  • the throttle 84a is a passage that allows the crank chamber 30 to communicate with the extension 82a.
  • the inner diameter of the throttle 84a is smaller than the inner diameter of the discharge portion 82b.
  • the second discharge passage 8b is a passage through which the refrigerant in the crank chamber 30 is discharged to the suction chamber 51 via the throttle 84a that constantly connects the crank chamber 30 to the suction chamber 51.
  • the path for discharging the refrigerant from the third port P3 to the suction chamber 51 in the first discharge passage 8a is such that the refrigerant is discharged from the throttle 84a to the suction chamber 51 in the second discharge passage 8b before reaching the suction chamber 51. Merging with the path to be.
  • the control valve 9 connects the discharge chamber 52 and the crank chamber 30 inside the cylinder head 5, and is arranged in the middle of the supply passage 7 (between both ends). Further, the control valve 9 can adjust and change the opening degree (cross-sectional area) of the supply passage 7. By controlling the opening of the supply passage 7 by the control valve 9, it is possible to control the amount of refrigerant introduced from the discharge chamber 52 to the crank chamber 30. Therefore, by controlling the opening of the supply passage 7 by the control valve 9 to change the pressure of the crank chamber 30 and change the inclination angle of the swash plate 31, the stroke of the piston 23 can be changed. . When the stroke of the piston 23 is changed, the discharge capacity (flow rate of the discharged refrigerant) of the variable displacement compressor 1 can be variably controlled.
  • the control valve 9 can control the suction pressure to an optimum value according to the external environment.
  • the air conditioner is not operating, that is, when the variable displacement compressor 1 is not operating, the supply passage 7 is forcibly opened by not energizing the solenoid built in the control valve 9, The discharge capacity of the variable displacement compressor 1 is controlled to a minimum.
  • the refrigerant in the discharge chamber 52 is supplied to the control pressure chamber (crank chamber 30) via the supply passage 7, and the refrigerant in the crank chamber 30 is supplied to the suction chamber via the discharge passage 8.
  • the pressure in the crank chamber 30 is adjusted, and the discharge capacity is controlled.
  • the switching valve 10 is provided on the control pressure chamber (crank chamber 30) side of the control valve 9 in the supply passage 7, and includes a valve chamber 100, a main valve body 110, and a sub-valve.
  • the body 120 is provided.
  • the valve chamber 100 is formed by a part of the center bore 22 on the side closer to the valve plate 4.
  • the valve chamber 100 is a space formed between the valve plate 4 and the other end surface of the drive shaft 6 inside the center bore 22 as shown in FIG.
  • the other end face of the drive shaft 6 is an end face on the side facing the valve plate 4.
  • valve chamber 100 is defined by a first wall surface 101, a second wall surface 102, and a peripheral wall surface 103, and communicates with the other end of the axial passage 81. Further, a passage is formed between the valve chamber 100 and the in-shaft passage 81 by a gap part of the thrust plate 62 and a gap part of the adjustment screw 63.
  • the inner diameter of the gap portion of the thrust plate 62 is larger than the inner diameter of the axial passage 81.
  • the inner diameter of the gap of the adjusting screw 63 is larger than the inner diameter of the gap of the thrust plate 62.
  • the first wall surface 101 is a wall surface on which the first port P ⁇ b> 1 opens, and constitutes a wall surface of the valve chamber 100 on the side close to the valve plate 4.
  • the suction valve forming plate 104 is a plate-shaped member arranged between the cylinder block 2 and the valve plate 4.
  • the first port P ⁇ b> 1 is an opening that allows a region between the control valve 9 and the valve plate 4 in the supply passage 7 to communicate with the center bore 22. That is, the first port P1 communicates with the upstream supply passage.
  • the second wall surface 102 is a wall surface where the second port P2 and the third port P3 are open, and is a wall surface facing the first wall surface 101 in the axial direction of the drive shaft 6. Therefore, the valve chamber 100 is partitioned by the first wall surface 101 and the second wall surface 102, and the peripheral wall 103 provided between the first wall surface 101 and the second wall surface 102.
  • the second port P ⁇ b> 2 is an opening that allows the gap of the adjustment screw 63 to communicate with the valve chamber 100. That is, the second port P2 is an opening that allows the crank chamber 30 to communicate with the valve chamber 100 via the in-shaft passage 81.
  • the second port P2 communicates with the downstream supply passage in the supply passage 7 between the switching valve 10 and the control pressure chamber (the crank chamber 30).
  • the second port P ⁇ b> 2 includes a region of the center bore 22 where the drive shaft 6 is arranged, when viewed from the axial direction of the drive shaft 6.
  • the third port P3 is an opening that allows the expansion portion 82a to communicate with the valve chamber 100. That is, the third port P3 is an opening that allows the valve chamber 100 and the suction chamber 51 to communicate with each other.
  • the third port P ⁇ b> 3 is disposed outside the area of the center bore 22 where the drive shaft 6 is disposed, when viewed from the axial direction of the drive shaft 6.
  • the peripheral wall surface 103 is a wall surface that connects the first wall surface 101 and the second wall surface 102, and is formed in an annular shape when viewed from the axial direction of the drive shaft 6.
  • the main valve body 110 is formed in a disk shape and is housed in the valve chamber 100.
  • the valve chamber 100 is located between the end face of the adjustment screw 63 and the valve plate 4. Can be formed using the space in the center bore 22.
  • the valve chamber 100 uses the existing configuration of the variable capacity compressor 1 instead of the space formed as a dedicated storage chamber for disposing the switching valve 10 inside the variable capacity compressor 1. It is a configuration that can be formed.
  • the main valve body 110 As a material for forming the main valve body 110, for example, a metal material or a resin material can be used. In the first embodiment, a case where the main valve body 110 is formed using a metal material will be described as an example.
  • the thickness direction of the main valve body 110 is parallel to the axial direction of the drive shaft 6.
  • the main valve body 110 includes a large-diameter portion 110a, a small-diameter portion 110b, and a protruding portion 110c.
  • the large diameter portion 110a is located closer to the drive shaft 6 than the small diameter portion 110b.
  • the outer diameter of the large diameter portion 110a is smaller than the inner diameter of the peripheral wall surface 103.
  • a second concave portion 112a is formed on a second pressure receiving surface 112 which is a surface facing the drive shaft 6.
  • the bottom surface of the second concave portion 112a faces the axial passage 81 when viewed from the axial direction of the drive shaft 6.
  • a part of the second pressure receiving surface 112 where the second concave portion 112a is not formed faces the third port P3 when viewed from the axial direction of the drive shaft 6. Therefore, the second pressure receiving surface 112 is a surface facing the second port P2 and the third port P3.
  • the second pressure receiving surface 112 contacts or separates from the second wall surface 102 to open and close the third port P3, and forms a second end surface that receives the pressure of the downstream supply passage via the second port P2. . That is, main valve body 110 includes a second valve portion having a second end surface (second pressure receiving surface 112).
  • the small diameter portion 110b is continuous with the large diameter portion 110a, and is disposed closer to the valve plate 4 than the large diameter portion 110a.
  • the outer diameter of the small diameter portion 110b is smaller than the outer diameter of the large diameter portion 110a.
  • the center of the circle formed by the small diameter portion 110b and the center of the circle formed by the large diameter portion 110a overlap when viewed from the axial direction of the drive shaft 6.
  • a first concave portion 111a is formed on a first pressure receiving surface 111 which is a surface facing the valve plate 4.
  • the bottom surface of the first recess 111a faces the first port P1 when viewed from the axial direction of the drive shaft 6. Therefore, the first pressure receiving surface 111 is a surface facing the first port P1.
  • the first pressure receiving surface 111 contacts or separates from the first wall surface 101 to open and close the first port P1, and forms a first end surface that receives the pressure of the upstream supply passage via the first port P1.
  • main valve element 110 includes a first valve portion having a first end surface (first pressure receiving surface 111). Further, when the first end surface (the first pressure receiving surface 111) abuts on the first wall surface 101, the main valve body 110 switches the first pressure receiving surface 111 that receives the pressure of the upstream supply passage from the first port P1. Including.
  • the protruding portion 110c protrudes from the first concave portion 111a along the axial direction of the drive shaft 6, and is arranged inside a gap portion of the adjustment screw 63.
  • the main valve body 110 has an in-valve passage 113 that allows the first pressure receiving surface 111 and the second pressure receiving surface 112 to communicate with each other.
  • the in-valve passage 113 is a passage that connects the region of the first concave portion 111a and the region of the second concave portion 112a.
  • the inner diameter increases in three stages from the first concave portion 111a to the second concave portion 112a. That is, the in-valve passage 113 is a passage having one opening on the first end surface (first pressure receiving surface 111) and the other opening on the second end surface (second pressure receiving surface 112).
  • the first pressure receiving surface 111 is formed radially outward of the valve passage 113 from one opening of the valve passage 113.
  • the axis (center axis) of one opening of the valve passage 113 is offset from the axis (center axis) of the first port P1 in the radial direction of the valve passage 113. That is, the axis of the first port P ⁇ b> 1 is provided to be offset in the radial direction of the valve passage 113 from the axis of one opening of the valve passage 113.
  • a cap 114 formed using, for example, a resin material is attached to a portion where the inner diameter of the valve passage 113 is the largest.
  • the cap 114 is formed in a cylindrical shape, and has a cap internal passage 114 a penetrating the center of the cap 114 when viewed from the axial direction of the drive shaft 6.
  • the inner diameter of the cap 114 is a portion between the portion where the inner diameter of the in-valve passage 113 is the largest and the portion where the inner diameter is the smallest. And the same inner diameter.
  • the height of the end surface of the cap 114 in the direction along the axial direction of the drive shaft 6 is set to a height at which the cap 114 is flush with the first pressure receiving surface 111.
  • the opening (opening to the cap 114) of the first pressure receiving surface 111 of the in-valve passage 113 is arranged at a position that does not overlap with the first port P1 when viewed from the axial direction of the drive shaft 6.
  • the sub-valve element 120 includes a small-diameter portion 121, a valve portion 122, a large-diameter portion 123, and an internal passage 124.
  • the small-diameter portion 121 is formed in a columnar shape, and is arranged in a portion where the inner diameter of the in-valve passage 113 is minimum.
  • the axial direction of the small diameter portion 121 is parallel to the axial direction of the drive shaft 6.
  • the valve portion 122 is formed in a columnar shape, and is arranged at an intermediate inner diameter portion of the in-valve passage 113. One end of the valve portion 122 faces the in-cap passage 114 a when viewed from the axial direction of the drive shaft 6.
  • the large-diameter portion 123 is formed in a cylindrical shape having a larger diameter than the small-diameter portion 121 and the valve portion 122, and connects the small-diameter portion 121 and the valve portion 122.
  • the large-diameter portion 123 is disposed at an intermediate inner diameter portion of the in-valve passage 113.
  • the large-diameter portion 123 faces a portion where the inner diameter of the in-valve passage 113 is the smallest when viewed from the axial direction of the drive shaft 6. Therefore, a portion where the inner diameter of the in-valve passage 113 is the smallest forms a departure restricting portion 125 that restricts the departure of the sub-valve body 120 from the in-valve passage 113.
  • the small-diameter portion 121 and the large-diameter portion 123 form a support portion that supports the valve portion 122.
  • the internal passage 124 is a passage that allows an end surface of the small diameter portion 121 facing the drive shaft 6 to communicate with a side surface of the valve portion 122.
  • a case will be described in which a plurality of end portions of the internal passage 124 that open to the side surface of the valve portion 122 are formed at intervals.
  • the end of the internal passage 124 that opens at the end surface of the small-diameter portion 121 facing the drive shaft 6 faces the shaft passage 81.
  • one end of the sub-valve body 120 is disposed in an opening that opens to the first pressure receiving surface 111 of the in-valve passage 113.
  • the other end of the sub-valve 120 faces the axial passage 81.
  • a material forming the sub-valve body 120 for example, a metal material or a resin material can be used, but in order to make the sub-valve body 120 lighter than the main valve body 110, It is preferable to use a resin material as the material to be formed.
  • the sub-valve 120 is formed of a resin material, for example, a polyphenylene sulfide resin, a nylon (polyamide) resin, or the like can be used as the resin material.
  • the sub-valve body 120 is lighter than the main valve body 110, is arranged so as to be movable inside the valve passage 113, and is housed in the main valve body 110.
  • variable displacement compressor 1 An example of the operation performed by the variable displacement compressor 1 of the first embodiment and the operation will be described with reference to FIGS. 1 to 5 and FIGS. 6 to 8.
  • the rotation of the drive shaft 6 is converted into reciprocating motion of the piston 23, and compresses the refrigerant supplied inside the cylinder bore 21.
  • the stroke of the piston 23 changes by controlling the opening of the supply passage 7 by the control valve 9.
  • the switching chamber 10 including the main valve body 110 and the sub-valve body 120 is housed in the valve chamber 100.
  • the main valve body 110 has a first pressure receiving surface 111, a second pressure receiving surface 112, and a valve passage 113 that connects the first pressure receiving surface 111 and the second pressure receiving surface 112. Further, the sub-valve body 120 is lighter than the main valve body 110 and is movably disposed inside the in-valve passage 113.
  • the control valve 9 When controlling the opening degree of the supply passage 7, when the control valve 9 opens the supply passage 7, the control valve 9 moves to the valve chamber 100 through the first port P ⁇ b> 1 which is applied to the first pressure receiving surface 111 including the first concave portion 111 a. The pressure of the flowing refrigerant increases. For this reason, the main valve body 110 is pushed by the pressure of the refrigerant moving to the valve chamber 100 through the first port P1. Then, the main valve body 110 moves in a direction away from the valve plate 4.
  • the first pressure receiving surface 111 is separated from the first wall surface 101, and the second pressure receiving surface 112 including the second concave portion 112a is in contact with the second wall surface 102. Also, almost at the same time when the second pressure receiving surface 112 contacts the second wall surface 102, the sub-valve 120 moves in a direction away from the end surface of the cap 114.
  • the flow of the refrigerant is indicated by broken arrows.
  • the third port P3 is closed by the main valve body 110, so that the crank chamber 30 and the suction chamber 51 are connected only to the throttle 84a provided in the second discharge passage 8b. Communicate through. Thereby, the opening degree of the discharge passage 8 is minimized.
  • the control valve 9 opens the supply passage 7
  • the pressure of the refrigerant moving to the valve chamber 100 through the first port P 1 is increased by the control valve 9.
  • the pressure becomes higher than the pressure of the refrigerant moving to the second wall 102 the refrigerant contacts the second wall surface 102.
  • the suction chamber 51 of the crank chamber 30 is communicated only with the throttle 84a, and the opening of the discharge passage 8 is set to the minimum opening larger than zero.
  • the first pressure receiving surface 111 is separated from the first wall surface 101
  • the refrigerant flows into the valve passage 113 and presses one end wall of the sub-valve body 120, so that the sub-valve body 120 opens the valve passage 113.
  • the refrigerant is supplied to the second port P2 via the internal passage 124.
  • the refrigerant supplied to the second port P2 is supplied to the crank chamber 30 via the shaft passage 81.
  • the sub-valve element 120 moves by being pressed by the flow of the refrigerant moving from the in-shaft passage 81 to the in-valve passage 113 via the inner passage 124. As a result, the sub-valve element 120 comes into contact with the inner end face of the cap 114 to close the cap passage 114a and close the valve passage 113.
  • the second port P2 and the third port P3 communicate with each other via the main valve body 110 and the second wall surface 102 in the valve chamber 100.
  • the first port P1 is cut off from the second port P2 and the third port P3.
  • the first discharge passage 8a and the second discharge passage 8b communicate with each other, so that the opening degree of the discharge passage 8 is maximized.
  • the first end surface the first pressure receiving surface 111 comes into contact with the first wall surface 101, communication between the first port P ⁇ b> 1 and the valve passage 113 is cut off.
  • the distance between the first port P1 and the first pressure receiving surface 111 when the first pressure receiving surface 111 contacts the first wall surface 101 is smaller than the opening diameter of the first port P1.
  • a space SP whose diameter is also increased is provided on at least one of the first pressure receiving surface 111 and the first wall surface 101. That is, when the control valve 9 closes the supply passage 7, the pressure of the refrigerant moving to the valve chamber 100 through the first port P 1 is reduced by the control valve 9, and the pressure of the refrigerant passing through the second port P 2 is increased. When the pressure becomes lower than the pressure of the refrigerant moving to, the in-valve passage 113 is closed.
  • the main valve body 110 having the valve passage 113 closed by the sub-valve body 120 receives the pressure of the refrigerant moving to the valve chamber 100 through the first port P1 and passing through the second port P2 to the valve chamber 100.
  • the pressure becomes lower than the pressure of the moving refrigerant, the refrigerant separates from the second wall surface 102.
  • the opening of the discharge passage 8 is maximized by setting the interval between the main valve body 110 and the second wall surface 102 to the maximum value.
  • the main valve body 110 moves in a direction away from the drive shaft 6.
  • the main valve body 110 moves in a direction away from the valve plate 4.
  • the outer peripheral surface of the large diameter portion 110a forms a guide surface when the main valve body 110 moves inside the valve chamber 100. Therefore, the main valve body 110 accommodated in the valve chamber 100 moves between the first wall surface 101 and the second wall surface 102 according to the pressure difference between the pressure in the upstream supply passage and the pressure in the downstream supply passage. I do.
  • the sub-valve 120 opens the valve passage 113 when the pressure in the upstream supply passage becomes higher than the pressure in the downstream supply passage, and opens the valve passage when the pressure in the upstream supply passage becomes lower than the pressure in the downstream supply passage. It operates to close 113. That is, the switching chamber 10 including the valve chamber 100 and the main valve body 110 and the sub-valve body 120 changes the opening degree of the discharge passage 8 according to the pressure change of the supply passage 7. Therefore, the switching valve 10 switches between the first state and the second state in conjunction with the opening and closing of the control valve 9.
  • the first state is a state in which the first port P1 communicates with the second port P2.
  • the second state is a downstream supply passage as a part of the discharge passage 8 for connecting the third port P3 and the second port P2 and discharging the refrigerant in the control pressure chamber (crank chamber 30) to the suction chamber 51.
  • Function a downstream supply passage as a part of the discharge passage 8 for connecting the third port P3 and the second port P2 and discharging the refrigerant in the control pressure chamber (crank chamber 30) to the suction chamber 51.
  • the switching valve 10 switches between the first state and the second state in conjunction with the opening and closing of the control valve 9.
  • the main valve body 110 included in the switching valve 10 moves between the first wall surface 101 and the second wall surface 102 according to the pressure difference between the pressure in the upstream supply passage and the pressure in the downstream supply passage. I do.
  • the sub-valve body 120 included in the switching valve 10 opens the valve passage 113, and the pressure in the upstream supply passage becomes lower than the pressure in the downstream supply passage. When it becomes lower, it operates to close the valve passage 113.
  • the control valve 9 closes the supply passage 7 and the pressure at the first port P1 becomes lower than the pressure at the second port P2, the sub-valve element 120, which is lighter than the main valve body 110, precedes the main valve body 110.
  • the variable displacement compressor 1 capable of suppressing the delay of the movement of the main valve body 110 and the delay of the decrease in the pressure of the crank chamber 30 due to the delay of the movement of the main valve body 110. It becomes.
  • the axial length of the switching valve 10 can be reduced. It becomes possible. This eliminates the need to provide a dedicated storage chamber for disposing the switching valve 10 inside the variable displacement compressor 1, thereby facilitating the disposition of the switching valve inside the variable displacement compressor 1. As a result, it is possible to provide the variable displacement compressor 1 capable of suppressing an increase in the size of the drive shaft 6 in the axial direction.
  • the first pressure receiving surface 111 receives the pressure of the upstream supply passage from the first port P1 when the first end surface (the first pressure receiving surface 111) abuts on the first wall surface 101. including.
  • the first pressure receiving surface 111 is formed radially outward of the valve passage 113 from one opening of the valve passage 113.
  • a space SP whose diameter is larger than the opening diameter of the first port P1 is formed. It is provided on at least one of the first pressure receiving surface 111 and the first wall surface 101. As a result, the force due to the refrigerant pressure acting on the first pressure receiving surface 111 increases, and the main valve body 110 can be efficiently moved in a direction away from the valve plate 4.
  • the axis of the first port P1 is provided to be offset in the radial direction of the valve passage 113 from the axis of one opening of the valve passage 113.
  • the main valve body 110 includes a first concave portion 111a which is a concave portion formed on the first pressure receiving surface 111, and a bottom surface of the first concave portion 111a faces the first port P1.
  • first concave portion 111a which is a concave portion formed on the first pressure receiving surface 111
  • a bottom surface of the first concave portion 111a faces the first port P1.
  • the pressure of the refrigerant passing through the first port P1 and moving to the valve chamber 100 can be efficiently received by the first concave portion 111a, and the main valve body 110 is efficiently moved away from the valve plate 4. It becomes possible to move it.
  • the pressure receiving surface that receives the pressure of the refrigerant moving to the valve chamber 100 through the first port P1 can be clearly divided into the first pressure receiving surface 111.
  • the main valve element 110 includes a deviation restricting portion 125 that restricts deviation of the sub-valve element 120 from the in-valve passage 113.
  • the configuration of the switching valve 10 can be a configuration in which the sub-valve body 120 is built in the main valve body 110, and the assemblability of the variable displacement compressor 1 can be improved.
  • the discharge passage 8 has a first discharge passage 8a and a second discharge passage 8b.
  • the path for discharging the refrigerant from the third port P3 to the suction chamber 51 in the first discharge passage 8a is connected to the refrigerant from the throttle 84a to the suction chamber 51 in the second discharge passage 8b before reaching the suction chamber 51. Merging with the path for discharging the water. As a result, the formation of the discharge passage 8 is facilitated.
  • the opening that opens in the first pressure receiving surface 111 of the in-valve passage 113 is disposed at a position that does not overlap with the first port P1 when viewed from the axial direction of the drive shaft 6. It is not limited to. That is, for example, as shown in FIG. 9, a configuration is such that the opening that opens in the first pressure receiving surface 111 of the in-valve passage 113 faces the first port P ⁇ b> 1 when viewed from the axial direction of the drive shaft 6. Is also good.
  • the switching valve 10 is arranged only inside the cylinder block 2, but the invention is not limited to this. That is, for example, as shown in FIG. 10, a part of the main valve body 110 may be arranged inside the cylinder head 5.
  • a part of the discharge passage 8 is formed by the in-shaft passage 81 formed inside the drive shaft 6.
  • the invention is not limited to this. May not be formed.
  • a part of the discharge passage 8 is formed, for example, by a gap formed between the drive shaft 6 and the first sliding bearing 61 (a gap secured for rotating the drive shaft 6). Is also good.
  • one end of the in-shaft passage 81 is configured to communicate with the crank chamber 30 via the oil introduction passage 39.
  • One end may be in direct communication with the crank chamber 30.
  • the height of the cap 114 is set to a height at which the cap 114 is flush with the first pressure receiving surface 111, but the present invention is not limited to this. That is, for example, as shown in FIG. 11, the height of the cap 114 may be set to a height at which the cap 114 is closer to the second recess 112a than the first pressure receiving surface 111.
  • the configuration of the first end surface is formed on the outer peripheral side of the in-valve passage 113, and is disposed on the inner peripheral side of the first end surface with respect to the contact surface that contacts the first wall surface 101.
  • an opening hole forming surface in which one opening of the in-valve passage 113 is formed is provided.
  • the first port P1 and the valve passage 113 communicate with each other via a gap formed between the opening hole forming surface and the first wall surface 101. Communicate with each other.
  • the cap 114 and the main valve body 110 are integrally formed of resin, there is a possibility that the cap 114 protrudes from the first pressure receiving surface 111 of the main valve body 110 due to dimensional tolerance.
  • the cap 114 protrudes from the first pressure receiving surface 111 of the main valve body 110, the cap 114 contacts the first wall surface 101, and a gap is formed between the main valve body 110 and the first wall surface 101. Therefore, the refrigerant from the first port P1 leaks through the third port P3.
  • a minute gap (throttle) is provided between the cap 114 and the first wall surface 101. . Therefore, it is possible to suppress the refrigerant from the first port P1 from leaking through the third port P3.
  • the throttle passage 74 is formed as a passage communicating the upstream supply passage between the control valve 9 and the switching valve 10 and the suction chamber 51 in the supply passage 7.
  • the present invention is not limited to this. That is, for example, as shown in FIG. 12, the throttle passage 74 is opposed to the first end surface (the first pressure receiving surface 111) of the first wall surface 101 and is opened at a position different from the first port P1. It may be formed.
  • the throttle passage 74 is formed by a hole formed in the suction valve forming plate 104 and a groove formed in the valve plate 4.
  • the groove formed in the valve plate 4 is formed in a shape that allows the hole formed in the suction valve forming plate 104 to communicate with the plate-side discharge passage forming portion 83.
  • SYMBOLS 1 Variable capacity compressor, 2 ... Cylinder block, 3 ... Front housing, 4 ... Valve plate, 4a ... Depression, 5 ... Cylinder head, 6 ... Drive shaft, 7 ... Supply passage, 8 ... Discharge passage, 8a ...
  • second concave portion 11 ... passage in valve, 114 ... cap, 114a ... passage in cap, 120 ... sub-valve, 121 ... small diameter part, 122 ... valve part, 123 ... large diameter part, 124 ... internal passage, 125 ... deviation control part, P1 ... First port, P2 ... second port, P3 ... third port, SP ... space

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

Le problème décrit par la présente invention consiste à fournir un compresseur à capacité variable qui facilite l'agencement d'une soupape de commutation à l'intérieur du compresseur à capacité variable et permet d'éviter un retard dans la régulation de pression d'une chambre à pression contrôlée telle qu'un carter de moteur. La solution selon l'invention porte sur une soupape de commutation (10) disposée davantage du côté d'un carter de moteur (30) qu'une soupape de commande (9) dans un canal d'alimentation (7) qui comprend : une chambre de soupape (100) ; un élément de soupape principal (110) qui est reçu dans la chambre de soupape (100) et se déplace entre une première surface de paroi et une seconde surface de paroi en fonction d'une différence de pression entre la pression d'un canal d'alimentation côté amont du canal d'alimentation (7), qui se trouve entre la soupape de commande (9) et la soupape de commutation (10) et la pression d'un canal d'alimentation côté aval du canal d'alimentation (7), qui se trouve entre la soupape de commutation (10) et le carter de moteur (30) ; et un élément de soupape secondaire (120) qui est reçu dans l'élément de soupape principal (110) et qui est formé pour être plus léger que l'élément de soupape principal. L'élément de soupape secondaire (120) fonctionne de manière à ouvrir un canal intra-soupape (113) lorsque la pression du canal d'alimentation côté amont devient supérieure à la pression du canal d'alimentation côté aval et à fermer le canal intra-soupape (113) lorsque la pression du canal d'alimentation côté amont devient inférieure à la pression du canal d'alimentation côté aval.
PCT/JP2019/024240 2018-06-27 2019-06-19 Compresseur à capacité variable WO2020004165A1 (fr)

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JP2018121637A JP7048177B2 (ja) 2018-06-27 2018-06-27 可変容量圧縮機
JP2018-121637 2018-06-27

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WO2020004165A1 true WO2020004165A1 (fr) 2020-01-02

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Citations (3)

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Publication number Priority date Publication date Assignee Title
JPH05231309A (ja) * 1992-02-20 1993-09-07 Toyota Autom Loom Works Ltd ピストン型圧縮機における潤滑構造
JP2002048059A (ja) * 2000-05-24 2002-02-15 Sanden Corp 容量可変型斜板式圧縮機
KR20140100133A (ko) * 2013-02-05 2014-08-14 한라비스테온공조 주식회사 가변 용량형 사판식 압축기

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3088536B2 (ja) * 1991-12-26 2000-09-18 サンデン株式会社 可変容量型揺動式圧縮機
JP3733633B2 (ja) * 1996-02-01 2006-01-11 株式会社豊田自動織機 可変容量圧縮機
JPH11287181A (ja) * 1998-04-02 1999-10-19 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP3891099B2 (ja) * 2001-11-12 2007-03-07 株式会社豊田自動織機 ピストン式圧縮機
JP6495634B2 (ja) * 2014-12-02 2019-04-03 サンデンホールディングス株式会社 可変容量圧縮機
JP6723148B2 (ja) 2016-12-01 2020-07-15 サンデン・オートモーティブコンポーネント株式会社 可変容量圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05231309A (ja) * 1992-02-20 1993-09-07 Toyota Autom Loom Works Ltd ピストン型圧縮機における潤滑構造
JP2002048059A (ja) * 2000-05-24 2002-02-15 Sanden Corp 容量可変型斜板式圧縮機
KR20140100133A (ko) * 2013-02-05 2014-08-14 한라비스테온공조 주식회사 가변 용량형 사판식 압축기

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JP2020002836A (ja) 2020-01-09
CN112313413B (zh) 2022-07-29
JP7048177B2 (ja) 2022-04-05

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