WO2024070420A1 - Compresseur à cylindrée variable - Google Patents

Compresseur à cylindrée variable Download PDF

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Publication number
WO2024070420A1
WO2024070420A1 PCT/JP2023/031302 JP2023031302W WO2024070420A1 WO 2024070420 A1 WO2024070420 A1 WO 2024070420A1 JP 2023031302 W JP2023031302 W JP 2023031302W WO 2024070420 A1 WO2024070420 A1 WO 2024070420A1
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WO
WIPO (PCT)
Prior art keywords
control valve
chamber
refrigerant
discharge
pressure
Prior art date
Application number
PCT/JP2023/031302
Other languages
English (en)
Japanese (ja)
Inventor
正俊 士反
順也 佐藤
淑恵 松嵜
Original Assignee
サンデン株式会社
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 サンデン株式会社 filed Critical サンデン株式会社
Publication of WO2024070420A1 publication Critical patent/WO2024070420A1/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
    • F04B27/10—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 having stationary cylinders
    • F04B27/12—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 having stationary cylinders having plural sets of cylinders or pistons
    • 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 that can change the refrigerant discharge capacity.
  • a capacity control valve that controls the refrigerant discharge capacity is disposed in the middle of a communication passage that connects the discharge chamber and the crank chamber (control pressure chamber).
  • the capacity control valve controls the refrigerant discharge capacity by changing the state of the compression mechanism that compresses the refrigerant by increasing or decreasing the flow rate of the refrigerant supplied from the discharge chamber to the crank chamber to change the internal pressure of the crank chamber.
  • Patent Document 1 the cross-sectional area of the communication passage that connects the discharge chamber and the crank chamber is not optimized, and therefore, particularly in situations where the flow rate of the refrigerant in the discharge chamber is relatively slow, the refrigerant is constricted by the opening of the communication passage, increasing the flow rate, and foreign matter contained in the refrigerant and the lubricating oil mixed with the refrigerant is more likely to flow into the communication passage.
  • the present invention aims to provide a variable displacement compressor that can reduce the inflow of foreign matter into the displacement control valve that controls the refrigerant discharge capacity.
  • a variable displacement compressor has a suction chamber into which refrigerant is introduced, a compression mechanism that draws in and compresses the refrigerant in the suction chamber, a discharge chamber from which the refrigerant compressed by the compression mechanism is discharged, a control pressure chamber that changes the state of the compression mechanism depending on the internal pressure, and a capacity control valve arranged in a communication passage that communicates between the discharge chamber and the control pressure chamber.
  • the capacity control valve has multiple inlet ports, and by increasing or decreasing the flow rate of refrigerant supplied from the discharge chamber to the control pressure chamber, it changes the internal pressure of the control pressure chamber and controls the discharge capacity of the refrigerant.
  • the cross-sectional area of the communication passage that opens into the discharge chamber is larger than the total cross-sectional area of the multiple inlet ports of the capacity control valve.
  • the present invention makes it possible to reduce the inflow of foreign matter into the capacity control valve that controls the refrigerant discharge capacity in a variable capacity compressor.
  • FIG. 1 is a vertical sectional view of a swash plate compressor which is an example of a variable displacement compressor.
  • FIG. 2 is a perspective view showing an example of an internal structure of a cylinder head.
  • 1 is a cross-sectional view showing an example of a mounting structure for a displacement control valve;
  • FIG. 2 is a front view showing an example of a cylinder head in which a pressure supply passage is formed.
  • 1 is a cross-sectional view showing a main portion of an example of a cylinder head in which a pressure supply passage is formed.
  • 13 is a cross-sectional view of a main portion showing a modified example of a pressure supply passage.
  • FIG. 13 is a cross-sectional view of a main portion showing a modified example of a pressure supply passage.
  • FIG. FIG. 11 is a front view showing another example of a cylinder head in which a pressure supply passage is formed. This is a cross-sectional view taken along line BB in FIG.
  • FIG. 1 shows an example of a swash plate compressor 100, which is an example of a variable displacement compressor.
  • the swash plate compressor 100 is incorporated, for example, in a refrigerant circulation circuit of an air conditioning system of a vehicle (not shown), and draws in and compresses a refrigerant from a low pressure side of the refrigerant circulation circuit, and discharges the compressed refrigerant to the high pressure side of the refrigerant circulation circuit.
  • the variable displacement compressor is not limited to the illustrated swash plate compressor 100, and may be a compressor well known to those skilled in the art.
  • the swash plate compressor 100 has a cylinder block 102 in which multiple cylinder bores 102A are formed, a front housing 104 joined to one axial end of the cylinder block 102, and a cylinder head 108 joined to the other axial end of the cylinder block 102 via a valve plate 106.
  • the cylinder block 102 and the front housing 104 form a crank chamber 110, and a drive shaft 112 is arranged so as to penetrate the interior of the crank chamber 110 in the axial direction.
  • a disk-shaped swash plate 114 is arranged inside the crank chamber 110.
  • a through hole 114A is formed in the center of the swash plate 114, and the drive shaft 112 penetrates the through hole 114A of the swash plate 114.
  • the swash plate 114 is also connected to a disk-shaped rotor 116 fixed integrally to the drive shaft 112 via a link mechanism 118.
  • the crank chamber 110 forms a control pressure chamber that changes the state of the compression mechanism, which is composed of the cylinder bore 102A of the cylinder block 102, the piston 146 described later, and the swash plate 114, depending on the internal pressure.
  • the link mechanism 118 includes a first arm 116A protruding from the rotor 116, a second arm 114B protruding from the swash plate 114, and a link arm 120 connecting the tip of the first arm 116A to the tip of the second arm 114B.
  • One end of the link arm 120 is connected to the first arm 116A via a first connecting pin 122 so as to be rotatable relative to the first arm 116A.
  • the other end of the link arm 120 is connected to the second arm 114B via a second connecting pin 124 so as to be rotatable relative to the second arm 114B. Therefore, the link mechanism 118 allows the swash plate 114 to rotate integrally with the drive shaft 112 and change the inclination angle along the axial direction of the drive shaft 112.
  • the through hole 114A of the swash plate 114 is formed in a shape that allows the swash plate 114 to tilt in a range between the minimum and maximum tilt angles.
  • the through hole 114A is formed with a minimum tilt angle regulating portion that abuts against the outer peripheral surface of the drive shaft 112 to regulate the tilt angle displacement (tilting) of the swash plate 114 in a direction that reduces the tilt angle.
  • the through hole 114A is also formed with a maximum tilt angle regulating portion that abuts against the outer peripheral surface of the drive shaft 112 to regulate the tilt of the swash plate 114 in a direction that increases the tilt angle. Therefore, the swash plate 114 can freely tilt in the axial direction of the drive shaft 112 between the minimum tilt angle regulated by the minimum tilt angle regulating portion and the maximum tilt angle regulated by the maximum tilt angle regulating portion.
  • a tilt angle reducing spring 126 that urges the swash plate 114 in a direction that reduces the tilt angle and a tilt angle increasing spring 128 that urges the swash plate 114 in a direction that increases the tilt angle are respectively arranged on either side of the swash plate 114 of the drive shaft 112.
  • the tilt angle reducing spring 126 is arranged between the swash plate 114 and the rotor 116
  • the tilt angle increasing spring 128 is arranged between the swash plate 114 and a disk-shaped spring support member 130 that is fixed or formed on the drive shaft 112.
  • the biasing force of the tilt angle increasing spring 128 is set to be greater than the biasing force of the tilt angle decreasing spring 126 when the tilt angle of the swash plate 114 is at the minimum tilt angle. Therefore, when the drive shaft 112 is not rotating, i.e., when the swash plate compressor 100 is stopped, the swash plate 114 is positioned at a tilt angle (>minimum tilt angle) where the biasing force of the tilt angle decreasing spring 126 and the biasing force of the tilt angle increasing spring 128 are balanced.
  • the tilt angle where the biasing force of the tilt angle decreasing spring 126 and the biasing force of the tilt angle increasing spring 128 are balanced is set as the minimum tilt angle range where the compression action of the piston 146 described later is ensured. For example, if the tilt angle when the swash plate 114 is perpendicular to the axial direction of the drive shaft 112 is 0 degrees (minimum tilt angle), it can be set in the range of 1 to 3 degrees.
  • One end of the drive shaft 112 passes through the cylindrical boss portion 104A of the front housing 104 and extends to the outside, and is connected via an electromagnetic clutch 132 to a pulley 134 that is fitted to the outer circumferential surface of the boss portion 104A so as to be capable of relative rotation.
  • the drive shaft 112 and rotor 116 are supported in the radial direction by bearings 136 and 138, and in the thrust direction by bearing 140 and thrust plate 142.
  • the distance between the other end of the drive shaft 112 and the thrust plate 142 is adjusted by an adjustment screw 144 so as to leave a predetermined gap.
  • the electromagnetic clutch 132 When the electromagnetic clutch 132 is operated while the rotational driving force from the electric motor or engine (not shown) is being transmitted to the pulley 134, the pulley 134 and the drive shaft 112 are connected, and the drive shaft 112 is rotated. When the electromagnetic clutch 132 is stopped, the pulley 134 and the drive shaft 112 are separated, and the swash plate compressor 100 can be stopped.
  • the swash plate compressor 100 also has the same number of pistons 146 as the number of cylinder bores 102A formed in the cylinder block 102.
  • Each piston 146 has a piston body 146A arranged so as to be movable in the axial direction relative to the cylinder bore 102A, and an extension portion 146B extending axially from the piston body 146A toward the inside of the crank chamber 110.
  • the extension 146B of the piston 146 is formed with a housing portion 146C capable of housing a pair of shoes 148 arranged on either side of the periphery of the swash plate 114. That is, the piston 146 is connected to the swash plate 114 via a pair of shoes 148 arranged on either side of the periphery of the swash plate 114. Therefore, the piston 146 reciprocates in the cylinder bore 102A of the cylinder block 102 as the swash plate 114 rotates.
  • the cylinder head 108 is formed with a suction chamber 150 located in the center and a discharge chamber 152 arranged to surround the suction chamber 150 in an annular shape.
  • the suction chamber 150 communicates with each cylinder bore 102A of the cylinder block 102 via a suction hole 106A and a suction valve (not shown) formed in the valve plate 106.
  • the discharge chamber 152 communicates with each cylinder bore 102A of the cylinder block 102 via a plurality of discharge holes 106B and a discharge valve (not shown) formed in the valve plate 106.
  • the front housing 104, cylinder block 102, valve plate 106, and cylinder head 108 are fastened together by a number of through bolts 154, with gaskets (not shown) placed between each component as necessary, to form the compressor housing.
  • the cylinder head 108 is formed with a suction passage 108A that connects the low pressure side of the refrigerant circulation circuit of the air conditioning system with the suction chamber 150, and a discharge passage 108B that connects the high pressure side of the refrigerant circulation circuit of the air conditioning system with the discharge chamber 152.
  • the cylinder head 108 is also provided with a check valve (not shown) that opens and closes the discharge passage 108B. This check valve operates in response to the pressure difference between the pressure in the discharge chamber 152 upstream and the pressure in the discharge passage 108B downstream, closing the discharge passage 108B when this pressure difference is less than a predetermined value and opening the discharge passage 108B when this pressure difference is equal to or greater than the predetermined value.
  • a cylindrical capacity control valve 200 is attached to a predetermined location of the cylinder head 108 to adjust the opening of the pressure supply passage 156 that connects the discharge chamber 152 and the crank chamber 110.
  • the capacity control valve 200 adjusts the opening of the pressure supply passage 156 to increase or decrease the flow rate of high-pressure refrigerant supplied from the discharge chamber 152 to the crank chamber 110, thereby changing the internal pressure of the crank chamber 110 and controlling the discharge capacity of the refrigerant.
  • the refrigerant present inside the crank chamber 110 flows into the suction chamber 150 through the communication passage 102B and space 102C formed in the cylinder block 102, and the pressure release passage 158 formed by the orifice 106C formed in the valve plate 106.
  • the pressure supply passage 156 is an example of a communication passage.
  • the capacity control valve 200 is fitted and fixed in a stepped control valve mounting hole 108C formed from the side of the cylinder head 108 toward the inside.
  • the capacity control valve 200 is an electromagnetic control valve that adjusts the opening of the pressure supply passage 156 in response to an input signal from the outside.
  • At two positions spaced apart in the axial direction on the outer circumferential surface of the capacity control valve 200 there are formed a plurality of inlet ports (not shown) that introduce high-pressure refrigerant supplied from the discharge chamber 152 into the interior, and a plurality of outlet ports (not shown) that discharge high-pressure refrigerant whose flow rate is adjusted in response to changes in the opening of the pressure supply passage 156.
  • the plurality of inlet ports and the plurality of outlet ports are arranged, for example, at each position that divides equally around the central axis of the capacity control valve 200.
  • short cylindrical filters 210 and 220 are attached to the outer peripheral surface of the capacity control valve 200 at positions covering the inlet ports and at positions covering the outlet ports.
  • O-rings 230 that seal with the inner peripheral surface of the control valve mounting hole 108C of the cylinder head 108 are attached to the outer peripheral surface of the capacity control valve 200 at the positions between the two filters 210 and 220 and at the positions on both axially outer sides of the two filters 210 and 220. Therefore, the three O-rings attached to the outer peripheral surface of the capacity control valve 200 can separate at least the inlet port and the outlet port in an airtight state.
  • annular gaps (spaces) through which high-pressure refrigerant flows are formed around the outer peripheral surfaces of the two filters 210 and 220 attached to the outer peripheral surface of the capacity control valve 200 in the cylinder head 108.
  • the pressure supply passage 156 located upstream of the displacement control valve 200 extends linearly so as to open at a position facing the outer circumferential surface of the filter 210 attached around the inlet port of the displacement control valve 200 when the displacement control valve 200 is fitted and fixed in the control valve mounting hole 108C. Therefore, the high-pressure refrigerant supplied from the discharge chamber 152 through the pressure supply passage 156 directly hits the outer circumferential surface of the filter 210 attached around the inlet port of the displacement control valve 200.
  • the high-pressure refrigerant supplied to the outer circumferential surface of the filter 210 flows through the annular gap formed around the filter 210, passes through the filter material of the filter 210, and flows into the inside of the displacement control valve 200 from the multiple inlet ports.
  • the high-pressure refrigerant discharged from the multiple discharge ports of the displacement control valve 200 passes through the filter 220 attached around the multiple discharge ports and flows into the gap, flows through the gap, enters the pressure supply passage 156 located downstream of the displacement control valve 200, and is supplied to the crank chamber 110.
  • the operation of the swash plate compressor 100 will be described.
  • the electromagnetic clutch 132 When the electromagnetic clutch 132 is operated while a rotational driving force of an electric motor, an engine, or the like is being transmitted to the pulley 134, the pulley 134 and the drive shaft 112 are connected via the electromagnetic clutch 132, and the drive shaft 112 starts to rotate.
  • the drive shaft 112 starts to rotate, the swash plate 114 connected to the rotor 116 via the rotor 116 and the link mechanism 118, which are integrated with the drive shaft 112, also starts to rotate.
  • the swash plate 114 When the swash plate compressor 100 is stopped, as described above, the swash plate 114 is in the minimum inclination angle range where the compression action of the pistons 146 is ensured, so that the pistons 146 connected to the swash plate 114 reciprocate within the cylinder bores 102A of the cylinder block 102. 1 (toward the front), the volume of the compression chamber defined by the piston 146 and the cylinder bore 102A increases and becomes negative pressure, and low-pressure refrigerant introduced into the suction chamber 150 from the low-pressure side of the refrigerant circuit through the suction passage 108A is sucked into the compression chamber through the suction hole 106A and the suction valve formed in the valve plate 106.
  • the majority or all of the high-pressure refrigerant discharged into the discharge chamber 152 is separated into lubricating oil and high-pressure refrigerant by an oil separator (not shown) attached to the cylinder head 108, and the high-pressure refrigerant is discharged to the high-pressure side of the refrigerant circulation circuit through the discharge passage 108B, while the lubricating oil is returned to the lower part of the crank chamber 110 through a lubricating oil passage (not shown).
  • a portion of the high-pressure refrigerant discharged into the discharge chamber 152 is supplied to the capacity control valve 200 through a pressure supply passage 156 that connects the discharge chamber 152 and the crank chamber 110.
  • the high-pressure refrigerant supplied to the capacity control valve 200 flows through the annular gap formed around the filter 210, passes through the filter 210, and foreign matter is captured, and then flows into the inside of the capacity control valve 200 from multiple inlet ports.
  • the capacity control valve 200 adjusts the flow rate of the high-pressure refrigerant flowing in from the multiple inlet ports by increasing or decreasing the opening of the internal passage in response to an external actuation signal, while discharging the high-pressure refrigerant from the multiple discharge ports. At this time, the capacity control valve 200 senses the internal pressure of the suction chamber 150 and changes the lift amount of the valve body to automatically adjust the internal pressure of the crank chamber 110 so that the internal pressure of the suction chamber 150 is constant.
  • the high-pressure refrigerant discharged from the multiple discharge ports flows through the annular gap formed around the filter 220, flows into the pressure supply passage 156 located downstream of the capacity control valve 200, and is supplied to the crank chamber 110.
  • the cross-sectional area of the pressure supply passage 156 located upstream of the displacement control valve 200 is not optimized taking into account the flow rate of the high-pressure refrigerant supplied from the discharge chamber 152 to the displacement control valve 200, the following problems may occur, particularly when the flow rate of the high-pressure refrigerant in the discharge chamber 152 is relatively slow. That is, when the flow rate of the high-pressure refrigerant in the discharge chamber 152 is relatively slow, the inlet to the pressure supply passage 156 functions as a throttle, and the flow rate of the high-pressure refrigerant flowing from the discharge chamber 152 to the pressure supply passage 156 increases.
  • the high-pressure refrigerant before the lubricating oil is separated by the oil separator becomes more likely to flow into the pressure supply passage 156, and as a result, foreign matter mixed in the lubricating oil contained in the high-pressure refrigerant also becomes more likely to flow into the pressure supply passage 156.
  • Most of the foreign matter that flows into the pressure supply passage 156 can be captured by the filter 210 of the displacement control valve 200, but because the size of the foreign matter is smaller than the mesh size of the filter 210, it may flow into the inside of the displacement control valve 200 and impede the operation of the valve body, making it impossible to control the refrigerant discharge capacity.
  • the cross-sectional area of the pressure supply passage 156 opening into the discharge chamber 152 is formed to be larger than the total cross-sectional area of the multiple inlet ports of the displacement control valve 200. That is, the total cross-sectional area of the multiple inlet ports of the displacement control valve 200 is calculated, and the cross-sectional area of the pressure supply passage 156 opening into the discharge chamber 152, in other words the cross-sectional area of the pressure supply passage 156 located upstream of the displacement control valve 200, is calculated so as to be larger than this total cross-sectional area. Then, using a drill that matches the cross-sectional area thus calculated, the pressure supply passage 156 is formed so that the portion located upstream of the displacement control valve 200 has a uniform cross-sectional area throughout its entire length.
  • the cross-sectional area of the pressure supply passage 156 located upstream of the capacity control valve 200 becomes larger than the total cross-sectional area of the multiple inlet ports, so the throttling function at the inlet to the pressure supply passage 156 is weakened, and the flow rate of the high-pressure refrigerant flowing from the discharge chamber 152 to the pressure supply passage 156 decreases.
  • the flow rate of the high-pressure refrigerant flowing into the pressure supply passage 156 decreases, for example, the high-pressure refrigerant before the lubricating oil is separated by the oil separator becomes less likely to flow into the pressure supply passage 156, and as a result, foreign matter mixed in the lubricating oil contained in the high-pressure refrigerant also becomes less likely to flow into the pressure supply passage 156. And since the amount of foreign matter flowing into the pressure supply passage 156 is reduced, the amount of foreign matter flowing into the capacity control valve 200 is also reduced, and the movement of the valve body of the capacity control valve 200 is less likely to be hindered by foreign matter, which makes it possible to suppress the inability to control the discharge capacity of the refrigerant.
  • the cross-sectional area of the pressure supply passage 156 located upstream of the displacement control valve 200 is made uniform over the entire length, the pressure supply passage 156 may interfere with O-rings 230 arranged on both axial sides of the filter 210 of the displacement control valve 200 on the displacement control valve 200 side.
  • the cross-sectional area of the pressure supply passage 156 is made smaller on the way from the discharge chamber 152 to the displacement control valve 200.
  • the cross-sectional area of the pressure supply passage 156 is made smaller in the vicinity of the displacement control valve 200.
  • the cross-sectional area of the pressure supply passage 156 is made smaller in an intermediate portion from the discharge chamber 152 to the displacement control valve 200.
  • the cross-sectional area of the pressure supply passage 156 decreases on the way from the discharge chamber 152 to the capacity control valve 200, increasing the flow rate of the high-pressure refrigerant, but this does not have a significant effect because the absolute amount of foreign matter flowing into the pressure supply passage 156 is reduced.
  • the pressure supply passages 156 are formed so as to extend obliquely from two positions, spaced a predetermined distance apart, of the discharge chamber 152 formed in the cylinder head 108 to the displacement control valve 200.
  • the total cross-sectional area of the multiple pressure supply passages 156 opening into the discharge chamber 152 becomes larger than the total cross-sectional area of the multiple inlet ports of the displacement control valve 200. Therefore, even in cylinder heads 108 with various layouts, the total cross-sectional area of the multiple pressure supply passages 156 opening into the discharge chamber 152 can be made larger than the total cross-sectional area of the multiple inlet ports of the displacement control valve 200.
  • the link mechanism 118 connecting the rotor 116 and the swash plate 114 is not limited to the configuration described above, and may be a well-known link mechanism.
  • the swash plate compressor 100 does not necessarily have to have a pulley 134 to which the rotational driving force of an electric motor or an engine is transmitted, and an electromagnetic clutch 132 connecting the pulley 134 and the drive shaft 112.

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

Abstract

Ce compresseur à cylindrée variable réduit l'entrée de substances étrangères dans une soupape de commande de capacité qui commande la capacité d'évacuation d'un fluide frigorigène. Un compresseur à came plate (100), à titre d'exemple du compresseur à cylindrée variable, comprend : une chambre d'aspiration (150) ; un mécanisme de compression qui aspire et comprime un fluide frigorigène dans la chambre d'aspiration (150) ; une chambre d'évacuation (152) vers laquelle le fluide frigorigène comprimé par le mécanisme de compression est évacué ; une chambre de vilebrequin (110) qui change l'état du mécanisme de compression en fonction de la pression interne ; et une soupape de commande de capacité (200) disposée dans un trajet d'alimentation en pression (156) qui relie la chambre d'évacuation (152) et la chambre de vilebrequin (110). La soupape de commande de capacité (200) a une pluralité d'orifices d'introduction et augmente/diminue le débit du fluide frigorigène fourni par la chambre d'évacuation (152) à la chambre de vilebrequin (110) pour modifier la pression interne de la chambre de vilebrequin (110), ce qui permet de commander la capacité d'évacuation du fluide frigorigène. En outre, la surface de section transversale du trajet d'alimentation en pression (156) ouverte dans la chambre d'évacuation (152) est plus grande que la surface de section transversale totale de la pluralité d'orifices d'introduction de la soupape de commande de capacité (200).
PCT/JP2023/031302 2022-09-26 2023-08-29 Compresseur à cylindrée variable WO2024070420A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022-152351 2022-09-26
JP2022152351A JP2024046961A (ja) 2022-09-26 2022-09-26 可変容量圧縮機

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WO2024070420A1 true WO2024070420A1 (fr) 2024-04-04

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000265960A (ja) * 1999-03-15 2000-09-26 Toyota Autom Loom Works Ltd 流体機械

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000265960A (ja) * 1999-03-15 2000-09-26 Toyota Autom Loom Works Ltd 流体機械

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