Variable capacity compressor

Abstract

A variable capacity compressor reduces the inflow of foreign matter into a capacity control valve that controls the discharge capacity of a refrigerant. A swash plate compressor (100), which is an example of a variable capacity compressor, is provided with: a suction chamber (150); a compression mechanism which sucks the refrigerant therein and compresses the refrigerant therein; a discharge chamber (152) through which the refrigerant compressed by the compressor is discharged; a crank chamber (110) for changing the state of the compression mechanism according to the internal pressure; and a capacity control valve (200) disposed in a pressure supply passage (156) that connects the discharge chamber (152) and the crank chamber (110). The capacity control valve (200) has a plurality of introduction ports, and controls the discharge capacity of the refrigerant by changing the internal pressure of the control pressure chamber (110) by increasing and decreasing the flow rate of the refrigerant supplied from the discharge chamber (152) to the control pressure chamber (110). In addition, the cross-sectional area of the pressure supply passage (156) that opens into the discharge chamber (152) is larger than the total cross-sectional area of the plurality of introduction ports of the capacity control valve (200).

Description

Technical Field

[0001] The present invention relates to a variable capacity compressor capable of making the discharge capacity of a refrigerant variable. Background Art

[0002] In a variable capacity compressor, as described in Japanese Patent Application Laid-Open No. 2017-31834 (Patent Document 1), a capacity control valve for controlling the discharge capacity of the refrigerant is arranged in the middle of a communication path that connects the discharge chamber to the crank chamber (control pressure chamber). The capacity control valve changes the state of a 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, thereby controlling the discharge capacity of the refrigerant. Prior art literature Patent Literature

[0003] Patent Document 1: Japanese Patent Application Publication No. 2017-31834 Summary of the invention Technical problem to be solved by the invention

[0004] However, in Patent Document 1, since the cross-sectional area of ​​the connecting path connecting the discharge chamber and the crank chamber is not optimized, especially when the flow rate of the refrigerant in the discharge chamber is relatively slow, the refrigerant is throttled by the opening of the connecting path and the flow rate increases, and foreign matter mixed with the refrigerant and the lubricating oil mixed with the refrigerant easily flows into the connecting path.

[0005] Therefore, an object of the present invention is to provide a variable capacity compressor capable of reducing the inflow of foreign matter into a capacity control valve that controls the discharge capacity of a refrigerant. Technical solutions adopted to solve technical problems

[0006] The variable capacity compressor has: a suction chamber into which refrigerant is introduced; a compression mechanism that sucks the refrigerant in the suction chamber and compresses it; 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 according to the internal pressure; and a capacity control valve that is arranged in a communication path that connects the discharge chamber with the control pressure chamber. The capacity control valve has a plurality of inlet ports, and controls the discharge capacity of the refrigerant by changing the internal pressure of the control pressure chamber by increasing or decreasing the flow rate of the refrigerant supplied from the discharge chamber to the control pressure chamber. In addition, the cross-sectional area of ​​the communication path opening to the discharge chamber is larger than the total cross-sectional area of ​​the plurality of inlet ports of the capacity control valve. Effects of the Invention

[0007] According to the present invention, in a variable capacity compressor, it is possible to reduce the inflow of foreign matter into a capacity control valve that controls the discharge capacity of refrigerant. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a longitudinal sectional view of a swash plate type compressor given as an example of a variable capacity compressor. Figure 2 It is a perspective view showing a part of the internal structure of the cylinder head. Figure 3 It is a cross-sectional view of a main part showing an example of a mounting structure of a displacement control valve. Figure 4 This is a front view showing an example of a cylinder head in which a pressure supply passage is formed. Figure 5 This is a cross-sectional view of a main part showing an example of a cylinder head in which a pressure supply passage is formed. Figure 6 It is a cross-sectional view of a main part showing a modified example of the pressure supply passage. Figure 7 It is a cross-sectional view of a main part showing a modified example of the pressure supply passage. Figure 8 This is a front view showing another example of a cylinder head in which a pressure supply passage is formed. Fig. 9 yes Figure 8 BB cross-sectional view. DETAILED DESCRIPTION

[0009] Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the accompanying drawings. Figure 1 An example of an inclined plate compressor 100 is shown as an example of a variable capacity compressor. The inclined plate compressor 100 is installed in a refrigerant circulation circuit of an air conditioning system of a vehicle (not shown), for example, sucks in refrigerant from the low-pressure side of the refrigerant circulation circuit and compresses it, and discharges the compressed refrigerant to the high-pressure side of the refrigerant circulation circuit. In addition, the variable capacity compressor is not limited to the inclined plate compressor 100 shown in the figure, and may be a compressor well known to those skilled in the art.

[0010] The inclined plate compressor 100 includes a cylinder block 102 having a plurality of cylinder bores 102A, 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 .

[0011] A crank chamber 110 is formed by the cylinder block 102 and the front housing 104, and a drive shaft 112 is arranged in a manner that penetrates the interior of the crank chamber 110 in the axial direction. A circular plate-shaped inclined plate 114 is arranged inside the crank chamber 110. A through hole 114A is formed in the central portion of the inclined plate 114, and the drive shaft 112 penetrates the through hole 114A of the inclined plate 114. In addition, the inclined plate 114 is connected to a circular plate-shaped rotor 116 integrally fixed to the drive shaft 112 via a connecting rod mechanism 118. Here, the crank chamber 110 constitutes a control pressure chamber, and the control pressure chamber changes the state of a compression mechanism composed of a cylinder bore 102A of the cylinder block 102, a piston 146 described later, and the inclined plate 114 according to the internal pressure.

[0012] The link mechanism 118 includes: a first arm 116A, which is protruding from the rotor 116; a second arm 114B, which is protruding from the swash plate 114; and a link arm 120, which connects the front end of the first arm 116A and the front end 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 relatively rotatable. In addition, 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 relatively rotatable. Therefore, the swash plate 114 can rotate integrally with the drive shaft 112 through the link mechanism 118, and the inclination angle can be changed along the axial direction of the drive shaft 112.

[0013] The through hole 114A of the inclined plate 114 is formed into a shape that allows the inclined plate 114 to tilt within a range between a minimum tilt angle and a maximum tilt angle. Specifically, a minimum tilt angle limiting portion is formed in the through hole 114A, and the minimum tilt angle limiting portion abuts against the outer peripheral surface of the drive shaft 112 to limit the tilt angle displacement (tilt movement) of the inclined plate 114 in a direction that reduces the tilt angle. In addition, a maximum tilt angle limiting portion is formed in the through hole 114A, and the maximum tilt angle limiting portion abuts against the outer peripheral surface of the drive shaft 112 to limit the tilt movement of the inclined plate 114 in a direction that increases the tilt angle. Therefore, the inclined plate 114 can freely tilt relative to the axial direction of the drive shaft 112 between the minimum tilt angle limited by the minimum tilt angle limiting portion and the maximum tilt angle limited by the maximum tilt angle limiting portion.

[0014] An inclination angle reducing spring 126 and an inclination angle increasing spring 128 are respectively arranged at positions of the drive shaft 112 sandwiching the swash plate 114. The inclination angle reducing spring 126 applies force to the swash plate 114 in a direction to reduce the inclination angle, and the inclination angle increasing spring 128 applies force to the swash plate 114 in a direction to increase the inclination angle. Specifically, the inclination angle reducing spring 126 is arranged between the swash plate 114 and the rotor 116, and the inclination angle increasing spring 128 is arranged between the swash plate 114 and a spring support member 130 in a disk shape fixed or formed on the drive shaft 112.

[0015] Here, the force of the inclination angle increasing spring 128 is set to be larger than the force of the inclination angle decreasing spring 126 when the inclination angle of the swash plate 114 is the minimum inclination angle. Therefore, when the drive shaft 112 does not rotate, that is, when the swash plate type compressor 100 stops, the swash plate 114 is located at a position of an inclination angle (> the minimum inclination angle) at which the force of the inclination angle decreasing spring 126 and the force of the inclination angle increasing spring 128 are balanced. The inclination angle at which the force of the inclination angle decreasing spring 126 and the force of the inclination angle increasing spring 128 are balanced is set to a minimum inclination angle range in which a compression action by the piston 146 described later is ensured. For example, if the inclination angle of the swash plate 114 when it is orthogonal to the axial direction of the drive shaft 112 is set to 0 degrees (the minimum inclination angle), it can be set to a range of 1 to 3 degrees.

[0016] One end of the drive shaft passes through the cylindrical sleeve portion 104A of the front housing 104 and extends to the outside thereof, and is connected to a pulley 134 that is relatively rotatably fitted to the outer peripheral surface of the sleeve portion 104A via an electromagnetic clutch 132. In addition, the drive shaft 112 and the rotor 116 are supported in the radial direction by bearings 136 and 138, and in the thrust direction by a bearing 140 and a thrust plate 142. In addition, the interval between the other end of the drive shaft 112 and the thrust plate 142 is adjusted by an adjustment screw 144 to have a predetermined gap.

[0017] In addition, when the electromagnetic clutch 132 is operated while the rotational driving force from the electric motor or the engine (not shown) is being transmitted to the pulley 134, the pulley 134 is connected to the drive shaft 112 and the drive shaft 112 is driven to rotate. In addition, when the electromagnetic clutch 132 is stopped, the pulley 134 is disengaged from the drive shaft 112, so that the inclined plate type compressor 100 can be stopped.

[0018] Furthermore, the inclined plate compressor 100 has the same number of pistons 146 as the plurality of cylinder bores 102A formed in the cylinder block 102. Each piston 146 has a piston body 146A configured to be movable in the axial direction relative to the cylinder bore 102A, and a protruding portion 146B protruding from the piston body 146A toward the inside of the crank chamber 110 in the axial direction.

[0019] The extended portion 146B of the piston 146 is provided with a housing portion 146C capable of housing a pair of shoe portions 148 disposed near the peripheral portion sandwiching the swash plate 114. That is, the piston 146 is connected to the swash plate 114 via the pair of shoe portions 148 disposed near the peripheral portion sandwiching the swash plate 114. Therefore, the piston 146 reciprocates in the cylinder bore 102A of the cylinder block 102 by the rotation of the swash plate 114.

[0020] like Figure 2 As shown, the cylinder head 108 is respectively formed with a suction chamber 150 disposed in the center and a discharge chamber 152 disposed in a manner of annularly surrounding the suction chamber 150. The suction chamber 150 is communicated with each cylinder bore 102A of the cylinder block 102 via a suction hole 106A formed in the valve plate 106 and a suction valve (not shown). The discharge chamber 152 is communicated with each cylinder bore 102A of the cylinder block 102 via a plurality of discharge holes 106B formed in the valve plate 106 and a discharge valve (not shown).

[0021] Here, the front housing 104 , the cylinder block 102 , the valve plate 106 , the cylinder head 108 , etc. are fastened to each other by a plurality of through bolts 154 with gaskets (not shown) disposed between the respective members as necessary to form a compressor housing.

[0022] like Figure 1 As shown, a suction passage 108A and a discharge passage 108B are formed in the cylinder head 108, respectively. The suction passage 108A connects the low-pressure side of the circulating refrigerant loop of the air-conditioning system with the suction chamber 150, and the discharge passage 108B connects the high-pressure side of the refrigerant circulation loop of the air-conditioning system with the discharge chamber 152. In addition, a check valve (not shown) for opening and closing the discharge passage 108B is arranged in the cylinder head 108. The check valve operates in response to the pressure difference between the pressure of the discharge chamber 152 upstream and the pressure of the discharge passage 108B downstream, and cuts off the discharge passage 108B when the pressure difference is less than a specified value, and opens the discharge passage 108B when the pressure difference is greater than a specified value.

[0023] A cylindrical capacity control valve 200 is mounted at a predetermined position of the cylinder head 108. The capacity control valve 200 adjusts the opening of the pressure supply passage 156 that communicates the discharge chamber 152 with 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 the high-pressure refrigerant supplied from the discharge chamber 152 to the crank chamber 110, and changes the internal pressure of the crank chamber 110 to control the discharge capacity of the refrigerant. In addition, the refrigerant in the crank chamber 110 flows into the suction chamber 150 through the communication path 102B and the space 102C formed in the cylinder body 102 and the pressure relief passage 158 formed by the throttle hole 106C formed in the valve plate 106. Therefore, by changing the pressure of the crank chamber 110 using the capacity control valve 200, the inclination angle of the swash plate 114, that is, the stroke of the piston 146 can be changed, and the discharge capacity of the swash plate type compressor 100 can be variably controlled. Here, the pressure supply passage 156 is cited as an example of the communication path.

[0024] like Figure 3 As shown, the capacity control valve 200 is fitted and fixed to the control valve mounting hole 108C with a stepped shape formed from the side of the cylinder head 108 to the inside. The capacity control valve 200 is an electromagnetic control valve that adjusts the opening of the pressure supply passage 156 according to an input signal from the outside. In addition, a plurality of inlet ports (not shown) for introducing the high-pressure refrigerant supplied from the discharge chamber 152 into the inside and a plurality of discharge ports (not shown) for discharging the high-pressure refrigerant whose flow rate has been adjusted according to the change in the opening of the pressure supply passage 156 are formed at two positions separated in the axial direction on the outer peripheral surface of the capacity control valve 200. Here, the plurality of inlet ports and the plurality of outlet ports are respectively arranged at respective positions equally divided around the central axis of the capacity control valve 200, for example.

[0025] In addition, strip-shaped and cylindrical filters 210 and 220 are respectively installed on the outer peripheral surface of the capacity control valve 200, that is, at the position covering the plurality of inlet ports and at the position covering the plurality of outlet ports. In addition, O-rings 230 for sealing the inner peripheral surface of the control valve mounting hole 108C of the cylinder head 108 are respectively installed on the outer peripheral surface of the capacity control valve 200, that is, at the position located between the two filters 210 and 220 and at the positions located on the two outer sides of the axial direction of the two filters 210 and 220. Therefore, by the three O-rings installed on the outer peripheral surface of the capacity control valve 200, at least the inlet port and the outlet port can be separated in an airtight state. In addition, in the cylinder head 108, annular gaps (spaces) for high-pressure refrigerant to flow are formed around the outer peripheral surfaces of the two filters 210 and 220 installed on the outer peripheral surface of the capacity control valve 200.

[0026] In addition, the pressure supply passage 156 located upstream of the capacity control valve 200 extends straightly in a state where the capacity control valve 200 is fitted into the control valve mounting hole 108C and fixed, so as to open at a position facing the outer peripheral surface of the filter 210 installed around the inlet port of the capacity control valve 200. Therefore, the high-pressure refrigerant supplied from the discharge chamber 152 through the pressure supply passage 156 directly collides with the outer peripheral surface of the filter 210 installed around the inlet port of the capacity control valve 200. In addition, the high-pressure refrigerant supplied to the outer peripheral surface of the filter 210 flows through the filter material of the filter 210 while flowing in the annular gap formed around the filter 210 and flows into the inside of the capacity control valve 200 from the plurality of inlet ports. Subsequently, the high-pressure refrigerant discharged from the plurality of discharge ports of the capacity control valve 200 flows into the gap through the filter 220 installed around the plurality of discharge ports, flows through the gap, enters the pressure supply passage 156 located downstream of the capacity control valve 200, and is supplied to the crank chamber 110.

[0027] Here, the operation of the swash plate type compressor 100 will be described. If the electromagnetic clutch 132 is operated while the rotational driving force of the electric motor, engine, etc. is transmitted to the pulley 134, the pulley 134 and the drive shaft 112 are connected via the electromagnetic clutch 132, so that the drive shaft 112 starts to rotate. When the drive shaft 112 starts to rotate, the swash plate 114 connected to the rotor 116 also starts to rotate via the rotor 116 and the connecting rod mechanism 118 integrated therewith. During the stop process of the swash plate type compressor 100, as described above, the swash plate 114 is within the minimum inclination angle range that ensures the compression action achieved by the piston 146. Therefore, the piston 146 connected to the swash plate 114 reciprocates in the cylinder bore 102A of the cylinder body 102. When the piston 146 moves toward Figure 1 When the piston 146 moves to the left (front side), the volume of the compression chamber divided by the piston 146 and the cylinder bore 102A increases and becomes negative pressure, and the low-pressure refrigerant introduced from the low-pressure side of the refrigerant circulation circuit to the suction chamber 150 through the suction passage 108A passes through the suction hole 106A formed in the valve plate 106 and the suction valve and is sucked into the compression chamber. Figure 1 When it moves to the right (rear side), the volume of the compression chamber decreases and becomes a positive pressure. The high-pressure refrigerant in the compression chamber passes through the discharge hole 106B formed on the valve plate 106 and the discharge valve and is discharged to the discharge chamber 152.

[0028] Most or all of the high-pressure refrigerant discharged to the discharge chamber 152 is separated into lubricating oil and high-pressure refrigerant by an oil separator (not shown) mounted on the cylinder head 108, and the high-pressure refrigerant is discharged to the high-pressure side of the refrigerant circulation circuit via the discharge passage 108B, and the lubricating oil is returned to the lower part of the crank chamber 110 via the lubricating oil passage (not shown). In addition, a part of the high-pressure refrigerant discharged to the discharge chamber 152 is supplied to the capacity control valve 200 via the 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 while passing through the filter 210 to capture foreign matter, and then flows into the inside of the capacity control valve 200 from a plurality of inlet ports.

[0029] The capacity control valve 200 increases or decreases the opening of the internal passage in response to an operation signal from the outside, thereby adjusting the flow rate of the high-pressure refrigerant flowing in from the multiple inlet ports and 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 to change the movement amount of the valve core, and automatically adjusts the internal pressure of the crank chamber 110 in such a way that the internal pressure of the suction chamber 150 becomes constant. In addition, the high-pressure refrigerant discharged from the multiple discharge ports flows through the annular gap formed around the filter 220 after foreign matter is captured by the filter 220 installed around the multiple discharge ports, and flows into the pressure supply passage 156 located downstream of the capacity control valve 200, and is supplied to the crank chamber 110.

[0030] When the supply of high-pressure refrigerant to the crank chamber 110 is cut off, the internal pressure of the crank chamber 110 decreases, and the inclination angle of the swash plate 114 increases. When the inclination angle of the swash plate 114 increases, the stroke of the piston 146 connected to the swash plate 114 via the connecting rod mechanism 118 increases, and the discharge capacity from the compression chamber also increases. In addition, the flow rate of the high-pressure refrigerant discharged from the compression chamber to the discharge chamber 152 increases, and as a result, the flow rate of the high-pressure refrigerant discharged from the swash plate type compressor 100 to the high-pressure side of the refrigerant circulation circuit also increases.

[0031] Incidentally, regarding the cross-sectional area of ​​the pressure supply passage 156 located upstream of the capacity control valve 200, if the flow rate of the high-pressure refrigerant supplied from the discharge chamber 152 to the capacity control valve 200 is not optimized in consideration of the flow rate of the high-pressure refrigerant supplied from the discharge chamber 152 and is not optimized, the following inconvenience may occur, especially 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, if the state of the high-pressure refrigerant flowing from the discharge chamber 152 into the pressure supply passage 156 is considered, the flow rate of the high-pressure refrigerant flowing from the discharge chamber 152 into the pressure supply passage 156 increases because the inlet to the pressure supply passage 156 functions as a throttle. When the flow rate of the high-pressure refrigerant flowing into the pressure supply passage 156 increases, for example, the high-pressure refrigerant before the lubricating oil is separated by the oil separator easily flows into the pressure supply passage 156, and as a result, foreign matter mixed in the lubricating oil contained in the high-pressure refrigerant also easily flows into the pressure supply passage 156. Most of the foreign matter flowing into the pressure supply passage 156 can be captured by the filter 210 of the capacity control valve 200, but because the size of the foreign matter is smaller than the mesh size of the filter 210, there is a possibility that the foreign matter will flow into the interior of the capacity control valve 200 and hinder the movement of the valve core, making it impossible to control the discharge capacity of the refrigerant.

[0032] Therefore, in this embodiment, if Figure 4 and Figure 5 As shown in FIG. 1 , the cross-sectional area of ​​the pressure supply passage 156 opening to the discharge chamber 152 is formed to be larger than the total cross-sectional area of ​​the plurality of introduction ports of the capacity control valve 200. That is, the total cross-sectional area of ​​the plurality of introduction ports of the capacity control valve 200 is obtained, and the cross-sectional area of ​​the pressure supply passage 156 opening to the discharge chamber 152 is obtained to be larger than the total cross-sectional area. In short, the cross-sectional area of ​​the pressure supply passage 156 located upstream of the capacity control valve 200 is obtained. Furthermore, using a drill bit suitable for the cross-sectional area obtained in the above manner, the pressure supply passage 156 having the same cross-sectional area over the entire length of the portion located upstream of the capacity control valve 200 is formed.

[0033] In this case, since the cross-sectional area of ​​the pressure supply passage 156 located upstream of the capacity control valve 200 is larger than the total cross-sectional area of ​​the plurality of inlet ports, the throttling function at the entrance of the pressure supply passage 156 is weakened, and the flow rate of the high-pressure refrigerant flowing from the discharge chamber 152 into the pressure supply passage 156 is reduced. When the flow rate of the high-pressure refrigerant flowing into the pressure supply passage 156 is reduced, for example, the high-pressure refrigerant before the lubricating oil is separated by the oil separator is difficult 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 is also difficult to flow into the pressure supply passage 156. In addition, since the foreign matter flowing into the pressure supply passage 156 is reduced, the foreign matter flowing into the inside of the capacity control valve 200 is also reduced, and the movement of the valve core of the capacity control valve 200 is not easily blocked by the foreign matter, so that the discharge capacity of the refrigerant cannot be controlled.

[0034] <<First Modification>> If the cross-sectional area of ​​the pressure supply passage 156 located upstream of the capacity control valve 200 is formed uniformly over the entire length, the pressure supply passage 156 may interfere with the O-rings 230 disposed on both sides of the filter 210 of the capacity control valve 200 in the axial direction on the capacity control valve 200 side. Figure 6 and Figure 7 As shown in FIG. 1 , the cross-sectional area of ​​the pressure supply passage 156 decreases midway from the discharge chamber 152 to the capacity control valve 200. Specifically, Figure 6 In the first modified example shown, the cross-sectional area of ​​the pressure supply passage 156 is reduced near the capacity control valve 200. Figure 7 In the first modified example shown, the cross-sectional area of ​​the pressure supply passage 156 becomes smaller in the middle portion from the discharge chamber 152 to the displacement control valve 200 .

[0035] In this way, interference between the pressure supply passage 156 and the O-ring 230 can be avoided, for example, the range of the pressure supply passage 156 can be expanded, and the direction in which the pressure supply passage 156 extends can be optimized. In addition, since the cross-sectional area of ​​the pressure supply passage 156 is reduced midway from the discharge chamber 152 to the capacity control valve 200, the flow rate of the high-pressure refrigerant increases, but since the absolute amount of foreign matter flowing into the pressure supply passage 156 is reduced, it does not have a great influence.

[0036] <<Second Modification>> Due to the layout of the cylinder head 108 of the variable capacity compressor 100, it is sometimes difficult to change the cross-sectional area of ​​the pressure supply passage 156 located upstream of the capacity control valve 200. In this case, Figure 8 and Fig. 9As shown, a plurality of (two in the example shown) pressure supply passages 156 are formed upstream of the capacity control valve 200, and the total cross-sectional area of ​​the pressure supply passages 156 opening to the discharge chamber 152 is larger than the total cross-sectional area of ​​the plurality of inlet ports of the capacity control valve 200. In the example shown in the figure, in consideration of the layout of the cylinder head 108, the pressure supply passages 156 are formed so as to extend obliquely toward the capacity control valve 200 from two positions separated by a predetermined distance from the discharge chamber 152 formed in the cylinder head 108.

[0037] In this way, even if the cross-sectional area of ​​the pressure supply passage 156 cannot be changed due to the layout of the cylinder head 108, by forming a plurality of pressure supply passages 156 located upstream of the capacity control valve 200, the total cross-sectional area of ​​the plurality of pressure supply passages 156 opening to the discharge chamber 152 can be made larger than the total cross-sectional area of ​​the plurality of introduction ports of the capacity control valve 200. Therefore, even if the cylinder head 108 has a diverse layout, the total cross-sectional area of ​​the plurality of pressure supply passages 156 opening to the discharge chamber 152 can be made larger than the total cross-sectional area of ​​the plurality of introduction ports of the capacity control valve 200.

[0038] In addition, it should be easy for those skilled in the art to understand that, for the technical ideas of the various above-mentioned embodiments, new embodiments can be generated by omitting some of them, or appropriately combining some of them with each other, or replacing some of them with known technologies.

[0039] As an example, the connecting rod mechanism 118 connecting the rotor 116 and the inclined plate 114 is not limited to the structure described above, and may be a well-known connecting rod mechanism. In addition, the inclined plate type compressor 100 may not necessarily have the pulley 134 that transmits the rotational driving force of the electric motor or the engine and the electromagnetic clutch 132 that connects the pulley 134 and the drive shaft 112. (Explanation of symbols)

[0040] 100 Inclined plate compressor (variable capacity compressor); 102A cylinder bore (compression mechanism); 110 crank chamber (control pressure chamber); 114 inclined plate (compression mechanism); 146 piston (compression mechanism); 150 suction chamber; 152 discharge chamber; 156 pressure supply passage (communication path); 200 capacity control valve.

Claims

1. A variable capacity compressor, characterized in that: have: A suction chamber, wherein the refrigerant is introduced into the suction chamber; a compression mechanism that sucks the refrigerant in the suction chamber and compresses it; 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 according to an internal pressure; as well as a capacity control valve having a plurality of inlet ports, the capacity control valve being disposed in a communication path connecting the discharge chamber and the control pressure chamber, and controlling the discharge capacity of the refrigerant by changing the internal pressure of the control pressure chamber by increasing or decreasing the flow rate of the refrigerant supplied from the discharge chamber to the control pressure chamber, The cross-sectional area of ​​the communication path opening to the discharge chamber is larger than the total cross-sectional area of ​​the plurality of introduction ports of the capacity control valve.

2. The variable capacity compressor according to claim 1, characterized in that: The cross-sectional area of ​​the communication path decreases midway from the discharge chamber toward the capacity control valve.

3. The variable capacity compressor according to claim 1, characterized in that: By forming a plurality of the communication paths upstream of the capacity control valve, a total cross-sectional area of ​​the plurality of communication paths opening to the discharge chamber is made larger than a total cross-sectional area of ​​a plurality of introduction ports of the capacity control valve.

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