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); the compression mechanism is used for compressing a refrigerant therein; a discharge chamber (152) through which the refrigerant compressed by the compression mechanism is discharged; a crank chamber (110) for changing the state of the compression mechanism according to the internal pressure; a capacity control valve (200) that is disposed in a pressure supply passage (156) that connects the discharge chamber (152) and the crank chamber (110), and that controls the discharge capacity of the refrigerant by changing the internal pressure of the crank chamber (110) by increasing and decreasing the flow rate of the refrigerant supplied from the discharge chamber (152) to the crank chamber (110); a filter (210) attached to the periphery of the plurality of introduction ports of the capacity control valve (200); and a direction changing member that changes the supply direction of the refrigerant supplied from the tip opening of the pressure supply passage (156) to 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, a capacity control valve is disposed in a communication path connecting a discharge chamber and a crank chamber, for example, and the capacity control valve controls the discharge capacity of the refrigerant and the lubricating oil mixed with the refrigerant by increasing or decreasing the flow rate of the refrigerant supplied from the discharge chamber to the crank chamber to change the pressure of the crank chamber. Foreign matter caused by wear and tear of a movable part built into the variable capacity compressor may be mixed into the refrigerant supplied from the discharge chamber. If the foreign matter mixed into the refrigerant flows into the interior of the capacity control valve, the drive of the valve core accommodated in the interior of the capacity control valve will be hindered, and the discharge capacity of the refrigerant may not be controlled. Therefore, as described in Japanese Patent Publication No. 2004-137922 (Patent Document 1), the following technology is proposed: In the capacity control valve, a filter is installed at the inlet port for introducing the refrigerant supplied from the discharge chamber, so that foreign matter mixed into the refrigerant is difficult to flow into the interior. Prior art literature Patent Literature

[0003] Patent Document 1: Japanese Patent Application Publication No. 2004-137922 Summary of the invention Technical problem to be solved by the invention

[0004] However, since the mesh of the filter is generally larger than the size of the foreign matter that hinders the operation of the capacity control valve, and the flow rate of the refrigerant flowing into the capacity control valve is relatively fast, the foreign matter mixed in the refrigerant will still pass through the filter and flow into the capacity control valve.

[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 for introducing refrigerant; a compression mechanism for sucking the refrigerant in the suction chamber and compressing it; a discharge chamber for discharging the refrigerant compressed by the compression mechanism; a control pressure chamber for changing the state of the compression mechanism according to the internal pressure; a cylindrical capacity control valve, which is arranged in a communication path for connecting the discharge chamber and the control pressure chamber; and a short strip-shaped and cylindrical filter, which is installed around a plurality of refrigerant inlet ports of the capacity control valve. Here, the capacity control valve controls the discharge capacity of the refrigerant by increasing or decreasing the flow rate of the refrigerant supplied from the discharge chamber to the control pressure chamber so as to change the internal pressure of the control pressure chamber. In addition, the variable capacity compressor also has a direction-changing member, which changes the supply direction of the refrigerant supplied from the front end opening of the communication path to 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 It is a front view showing a first embodiment of a direction changing member. Figure 5 It is a side view showing a first embodiment of a direction changing member. Figure 6 It is an explanatory diagram of the operation and effect of the first embodiment of the direction-changing member. Figure 7 It is a cross-sectional view of the main parts showing the second embodiment of the direction changing member. Figure 8 It is an explanatory diagram of the operation and effect of the second embodiment of the direction changing member. Fig. 9 It is a perspective view showing a third embodiment of a direction changing member. Fig.10 It is a perspective view showing a modified example of the direction changing member according to the third embodiment. Fig.11 It is a longitudinal sectional view showing a modified example of the direction changing member according to the third embodiment. Fig.12It is a cross-sectional view showing a modified example of the direction changing member according to the third embodiment. 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 gas 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 body 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. The crank chamber 110 constitutes a control pressure chamber, and the control pressure chamber changes the state of the compression mechanism composed of the cylinder bore 102A of the cylinder body 102, the piston 146 and the inclined plate 114 according to the internal pressure, and changes the discharge capacity of the refrigerant. 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 that is integrally fixed to the drive shaft 112 via a connecting rod mechanism 118.

[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] The inclination angle reducing spring 126 for urging the swash plate 114 in a direction to reduce the inclination angle and the inclination angle increasing spring 128 for urging the swash plate 114 in a direction to increase the inclination angle are arranged on the drive shaft 112 in such a manner as to sandwich the swash plate 114. 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 bearings 140 and thrust plates 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 arranged in the center and a plurality of discharge chambers 152 arranged in a ring-shaped manner to surround 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 1As shown, a suction passage 108A and a discharge passage 108B are formed in the cylinder head 108, respectively. The suction passage 108A allows the refrigerant circulation circuit on the low pressure side of the air conditioning system to communicate with the suction chamber 150, and the discharge passage 108B allows the refrigerant circulation circuit on the high pressure side of the air conditioning system to communicate 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, thereby adjusting 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 into and fixed in the control valve mounting hole 108C in the shape of a pulley step 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, and has 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 having a regulated flow rate formed at two positions separated in the axial direction on its outer peripheral surface.

[0025] In addition, a short and cylindrical filter 210 and a filter 220 are respectively installed on the outer peripheral surface of the capacity control valve 200, that is, at a position covering the plurality of inlet ports and at a position covering the plurality of outlet ports. In addition, an O-ring 230 is respectively installed on the outer peripheral surface of the capacity control valve 200, that is, at a position located between the two filters 210 and 220 and at a position located outside the two filters 210 and 220, for sealing with the inner peripheral surface of the control valve mounting hole 108C of the cylinder head 108. Therefore, by the three O-rings 230 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 108D and 108E are respectively 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. In addition, it should be noted that the two gaps 108D and 108E are not connected to each other.

[0026] In addition, the pressure supply passage 156 that connects the discharge chamber 152 of the cylinder head 108 with the gap 108D formed in the control valve mounting hole 108C extends linearly in a state where the capacity control valve 200 is fitted and fixed to the control valve mounting hole 108C, so as to open at a position facing the outer periphery of the filter 210 installed around the inlet port thereof. Therefore, the high-pressure refrigerant supplied from the discharge chamber 152 via 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. The high-pressure refrigerant supplied to the gap 108D formed around the capacity control valve 200 through the pressure supply passage 156 flows around the gap 108D formed between the filter 210 and the control valve mounting hole 108C of the cylinder head 108, and flows into the inside of the capacity control valve 200 from the plurality of inlet ports while passing through the filter material of the filter 210.

[0027] The filter 210 includes: two ring members 210A, which are fixed by being fitted in two positions separated in the axial direction of the capacity control valve 200; four rod-shaped connecting members 210B, which connect the two ring members 210A; and a filter material 210C, which is installed in a rectangular area divided by the two ring members 210A and the connecting members 210B. Here, the four connecting members 210B are respectively arranged at positions divided into four at an angle of 90 degrees around the central axis of the ring member 210A, but the number and arrangement position thereof can also be arbitrary (the same below).

[0028] 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 or the engine 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 rotates, the swash plate 114 connected to the rotor 116 via the rotor 116 and the connecting rod mechanism 118 integrated therewith also rotates. 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.

[0029] 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) installed on 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, and the lubricating oil is returned to the lower part of the crank chamber 110 through 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 through 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 in response to an operation signal from the outside, and supplies the high-pressure refrigerant of the flow rate corresponding to the operation signal to the crank chamber 110 located downstream thereof through the pressure supply passage 156. At this time, the capacity control valve 200 senses the internal pressure of the suction chamber 150 and changes the movement amount of the valve core, and automatically adjusts the internal pressure of the crank chamber 110 so that the internal pressure of the suction chamber 150 becomes constant.

[0030] When high-pressure refrigerant is supplied to the crank chamber 110, the internal pressure of the crank chamber 110 rises and the tilting angle of the swash plate 114 decreases. When the tilting angle of the swash plate 114 decreases, the stroke of the piston 146 connected to the swash plate 114 via the connecting rod mechanism 118 decreases, and the discharge capacity of the swash plate type compressor 100 also decreases. In addition, the flow rate of the high-pressure refrigerant discharged from the compression chamber to the discharge chamber 152 decreases, 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 decreases.

[0031] By the way, in order to Figure 2 and Figure 3 It is understood that the high-pressure refrigerant supplied from the discharge chamber 152 to the capacity control valve 200 via 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. At this time, since the flow rate of the high-pressure refrigerant directly colliding with the outer peripheral surface of the filter 210 is relatively fast, foreign matter mixed in the refrigerant may pass through the mesh of the filter material 210C of the filter 210 and flow into the interior from the inlet port of the capacity control valve 200. When foreign matter flows into the interior of the capacity control valve 200, for example, an obstacle is generated in the movement of the valve core and it does not move normally, so that the discharge capacity of the inclined plate type compressor 100 may not be changed.

[0032] Therefore, in the present embodiment, a direction-changing member is installed at a predetermined position of the inclined plate type compressor 100 to reduce the flow rate of the refrigerant supplied to the capacity control valve 200, and the direction-changing member changes the supply direction of the refrigerant supplied from the front end opening of the pressure supply passage 156 that connects the discharge chamber 152 and the capacity control valve 200 to the outer peripheral surface of the capacity control valve 200. In addition, by reducing the flow rate of the refrigerant supplied to the capacity control valve 200, the situation that foreign matter mixed in the refrigerant passes through the mesh of the filter 210 and flows into the inside is reduced, thereby suppressing the situation where the discharge capacity of the inclined plate type compressor 100 cannot be changed. The following is a detailed description of the direction-changing member.

[0033] <<First embodiment>> Figure 5 and Figure 6 A first embodiment of a direction-changing member is shown. In the first embodiment, the direction-changing member is a blocking member 210D installed in a portion of the outer periphery of the filter 210 facing the front end opening of the pressure supply passage 156 that communicates the discharge chamber 152 with the capacity control valve 200. Specifically, a portion of the outer peripheral surface of the filter 210 installed around the inlet port of the capacity control valve 200, for example, a portion facing the front end opening of the pressure supply passage 156, that is, a rectangular region defined by two ring members 210A and two connecting members 210B, is installed with a thin plate arc-shaped blocking member 210D that prevents high-pressure refrigerant and lubricating oil containing foreign matter from passing through, instead of the filter material 210C.

[0034] In this way, Figure 7 As shown, the high-pressure refrigerant and lubricating oil containing foreign matter supplied from the front end opening of the pressure supply passage 156 to the capacity control valve 200 initially collide with the blocking member 210D of the filter 210, and the foreign matter and the lubricating oil are captured by the member. In addition, the high-pressure refrigerant is dispersed to the surroundings on the surface, and its flow rate decreases. The high-pressure refrigerant after the flow rate decreases flows into the interior of the capacity control valve 200 while passing through the annular gap 108D formed in the cylinder head 108. At this time, the flow rate of the high-pressure refrigerant decreases, so the foreign matter mixed therein is easily captured by the filter material 210C of the filter 210, thereby reducing the foreign matter flowing into the interior of the capacity control valve 200. Therefore, the foreign matter flowing into the interior of the capacity control valve 200 decreases, so the situation that the movement of the valve core is hindered by the foreign matter is reduced, and the possibility of not being able to change the discharge capacity of the inclined plate type compressor 100 is reduced.

[0035] <<Second embodiment>> Figure 8 A second embodiment of a direction-changing member is shown. In the second embodiment, the direction-changing member is a cylindrical member 210E having a tapered outer peripheral surface and mounted around the filter 210 of the capacity control valve 200. Specifically, the cylindrical member 210E having a truncated cone-shaped (conical shape with the head cut off) outer peripheral surface is mounted on the outer periphery of the filter 210 mounted around the inlet port of the capacity control valve 200. Here, the cylindrical member 210E is formed so as to be fixed by fitting to the outer peripheral surface of the capacity control valve 200 via its small diameter portion, and a gap of a predetermined interval is formed between its large diameter portion and the outer peripheral surface of the filter 210.

[0036] In this way, Fig. 9As shown, the high-pressure refrigerant supplied from the front end opening of the pressure supply passage 156 to the capacity control valve 200 initially collides with the tapered outer peripheral surface of the cylindrical member 210E installed on the outer periphery of the filter 210. Foreign matter in the high-pressure refrigerant colliding with the outer peripheral surface of the cylindrical member 210E is captured by the member together with the lubricating oil. In addition, the refrigerant is dispersed toward the direction of the small diameter portion due to the tapered outer peripheral surface, so that the flow rate of the refrigerant decreases, and the refrigerant flows from the large diameter portion of the cylindrical member 210E to the filter 210 while passing around the gap 108D. Then, the high-pressure refrigerant after the flow rate decreases passes through the filter material 210C of the filter 210 and flows into the interior of the capacity control valve 200. At this time, the flow rate of the high-pressure refrigerant decreases, so that the foreign matter mixed in it is easily captured by the filter material 210C of the filter 210, thereby reducing the foreign matter flowing into the interior of the capacity control valve 200. In addition, other functions and effects are the same as those of the first embodiment, and therefore, the description thereof is omitted for the purpose of avoiding duplication. If necessary, please refer to the description of the first embodiment (the same below).

[0037] <<Third Embodiment>> Fig.10 A third embodiment of a direction-changing member is shown. In the third embodiment, the deflection member is a ring member 210F having a ring shape installed in the middle of the axial direction of the filter 210. Specifically, a ring member 210F having a diameter smaller than the diameter of the ring member 210A is arranged in the middle of the two ring members 210A of the filter 210. In addition, the connecting member 210B of the filter 210 connects the two ring members 210A with the ring member 210F located in their middle. In addition, the filter material 210C of the filter 210 is respectively installed in the rectangular area divided by the ring member 210A located on the outside of the axial direction, the ring member 210F located in the middle of the two ring members 210A, and the connecting member 210B. Therefore, the filter material 210C of the filter 210 is configured to be a V-shaped spaced gradually larger toward the periphery when viewed from the side of the filter 210. Furthermore, the axis of the pressure supply passage 156 formed in the cylinder head 108 is formed so as to pass through the middle portion of the outer peripheral surface of the ring member 210F of the filter 210. Alternatively, instead of changing the shape of the pressure supply passage 156, the position of the capacity control valve 200 relative to the cylinder head 108 may be changed so that the high-pressure refrigerant supplied from the pressure supply passage 156 collides with the outer peripheral surface of the ring member 210F.

[0038] If so, the high-pressure refrigerant supplied from the front end opening of the pressure supply passage 156 to the capacity control valve 200 initially collides with the outer peripheral surface of the ring member 210F arranged in the middle part of the two ring members 210A of the filter 210. Foreign matter in the high-pressure refrigerant that collides with the outer peripheral surface of the ring member 210F is captured by the member together with the lubricating oil. In addition, it rebounds and disperses in the outer peripheral surface of the ring member 210F, so that the flow rate of the refrigerant decreases, and a part of it passes through the filter material 210C and flows into the capacity control valve 200, and most of it passes through the filter material 210C while passing around the gap 108D and flows into the capacity control valve 200. At this time, the flow rate of the high-pressure refrigerant decreases, so that the foreign matter mixed in it is easily captured by the filter material 210C of the filter 210, thereby reducing the foreign matter flowing into the interior of the capacity control valve 200.

[0039] Figure 11 to Figure 1 3 shows a modification of the filter 210 having a ring member 210F. The filter 210 includes: two first cylindrical members 210G, which are arranged at two positions separated in the axial direction; a second cylindrical member 210H, which is arranged between the two first cylindrical members 210G; two disc members 210I, which block the end faces of the two first cylindrical members 210G facing outward; and a connecting member 210J, which connects the end faces of the first cylindrical member 210G facing inward and the second cylindrical member 210H at multiple locations. The first cylindrical member 210G has an inner diameter larger than the outer peripheral surface forming the introduction port of the capacity control valve 200. The second cylindrical member 210H has an inner diameter larger than the outer peripheral surface forming the introduction port of the capacity control valve 200, and has an outer diameter smaller than the inner diameter of the first cylindrical member 210G. In addition, the disc member 210I has a thin disc shape, and is formed with a through hole TH for being fitted and fixed with the outer peripheral surface of the capacity control valve 200 in its central part. In addition, the connecting member 210J is provided with four in the present embodiment, and is configured at an angle of 90 degrees around the axis of the filter 210 respectively. In addition, in the rectangular area divided by the first cylindrical member 210G, the second cylindrical member 210H and the connecting member 210J, a filter material 210K for capturing foreign matter mixed into the refrigerant is installed. In the filter 210, when observed from its side, the filter material 210K is configured on a face parallel to the disc member 210I. Here, the second cylindrical member 210H is cited as an example of a ring member.

[0040] If so, the high-pressure refrigerant supplied from the front end opening of the pressure supply passage 156 to the capacity control valve 200 initially collides with the outer peripheral surface of the second cylindrical member 210H arranged in the middle part of the two first cylindrical members 210G of the filter 210. Foreign matter in the high-pressure refrigerant that collides with the outer peripheral surface of the second cylindrical member 210H is captured by the member together with the lubricating oil. In addition, it rebounds and disperses in the outer peripheral surface of the second cylindrical member 210H, so that the flow rate of the refrigerant decreases, and flows in the annular space (equivalent to the gap 108D) divided by the inner peripheral surface of the control valve mounting hole 108C formed in the cylinder head 108, the first cylindrical member 210G, the second cylindrical member 210H and the filter material 210K. In addition, the high-pressure refrigerant flowing in the annular space passes through the filter material 210K and flows into the capacity control valve 200. At this time, the flow rate of the high-pressure refrigerant decreases, so foreign matter mixed in the refrigerant is easily captured by the filter material 210C of the filter 210, thereby reducing the amount of foreign matter flowing into the capacity control valve 200. In addition, when the filter 210 is used, since a space equivalent to the gap 108D is formed by the filter 210, it is not necessary to form the gap 108D in the cylinder head 108.

[0041] 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.

[0042] 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)

[0043] 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; 210 filters; 210D blocking component (direction changing component); 210E cylindrical member (direction-changing member); 210F ring member (direction-changing member); 210H: second cylindrical member (direction-changing member).

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; a cylindrical capacity control valve, the capacity control valve being disposed in a communication path that connects 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; a short strip-shaped and cylindrical filter, the filter being installed around a plurality of refrigerant inlet ports of the capacity control valve; as well as A direction changing member changes a supply direction of the refrigerant supplied from the front end opening of the communication path to the capacity control valve.

2. The variable capacity compressor according to claim 1, characterized in that: The direction changing member is provided on the capacity control valve.

3. The variable capacity compressor according to claim 2, characterized in that: The direction-changing member is attached to a portion of the outer circumference of the filter facing the front end opening of the communication path, and is an arc-shaped blocking member against which the refrigerant supplied from the front end opening collides.

4. The variable capacity compressor according to claim 2, characterized in that: The direction-changing member is a cylindrical member that is attached to the periphery of the filter of the capacity control valve and has a tapered outer peripheral surface against which the refrigerant supplied from the front end opening of the communication path collides.

5. The variable capacity compressor according to claim 2, characterized in that: The direction-changing member is a ring member attached to an axially intermediate portion of the filter and against which the refrigerant supplied from the front end opening of the communication path collides.

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