JP6723022B2 - Variable capacity compressor - Google Patents

Description

The present invention relates to the structure of a variable capacity compressor.

For example, a reciprocating variable displacement compressor used in a vehicle air conditioning system includes a housing, and a discharge chamber, a suction chamber, a crank chamber, and a cylinder bore are formed inside the housing. A swash plate is tiltably connected to a drive shaft extending in the crank chamber, and a conversion mechanism including the swash plate converts the rotation of the drive shaft into a reciprocating motion of a piston arranged in the cylinder bore. The reciprocating motion of the piston executes the steps of sucking the refrigerant from the suction chamber into the cylinder bore, compressing the sucked refrigerant, and discharging the compressed refrigerant to the discharge chamber.

The stroke length of the piston, that is, the discharge capacity of the variable displacement compressor is variable by changing the pressure (control pressure) in the crank chamber. The variable capacity compressor is provided with a pressure supply passage (air supply passage) in which a discharge control chamber and a crank chamber are connected to each other and a capacity control valve is interposed in order to control the discharge displacement. Is provided with a pressure release passage (bleeding passage) through which a throttle is provided.
Further, the variable displacement compressor disclosed in Patent Document 1 is provided with a filter in the pressure release passage, so that foreign matter flowing from the crank chamber to the suction chamber can be captured.
When the filter is provided in the flow channel, it is necessary to select the openings so that the mesh member of the filter is not completely clogged. For example, in a variable displacement compressor, a mesh member having an opening of 100 μm to 200 μm is often used.

JP, 2011-111984, A

However, foreign matter existing in the crank chamber, which contains abrasion powder generated in the sliding portion in the variable displacement compressor, is, for example, about several μm to several tens of μm, and foreign matter of these sizes is disclosed in Patent Document 1. It cannot be captured by a conventional filter (mesh member having an opening of about 100 μm to 200 μm). The minute foreign matter in the crank chamber passes through the filter, is discharged to the discharge chamber via the suction chamber and the cylinder bore, and is mostly discharged to the external refrigerant circuit, while part is again discharged via the capacity control valve. It enters the crank chamber and circulates in the variable displacement compressor. In particular, a minute foreign substance of 20 μm or less enters the support hole for supporting the valve body of the capacity control valve interposed in the pressure supply passage, and becomes a factor that hinders the smooth operation of the valve body. There is a risk that the valve body will become stuck (locked) and become out of control.

The present invention has been made to solve such a problem, and its object is to prevent the refrigerant from flowing through the pressure release passage even if foreign matter is deposited on the filter provided in the pressure release passage. It is to provide a variable capacity compressor that ensures the discharge capacity and can execute the discharge capacity control satisfactorily.

In order to achieve the above-mentioned object, in the variable displacement compressor of the present invention, a cylinder block in which a plurality of cylinder bores are formed, a piston provided in each of the cylinder bores, and one end side of the cylinder block is closed. A front housing that forms a crank chamber in cooperation with the cylinder block; a valve plate that closes the other end side of the cylinder block; and a valve plate that sandwiches the valve plate and that faces the cylinder block. An annular discharge chamber, a suction chamber radially inside the discharge chamber, a suction passage connecting the suction port and the suction chamber, and a discharge passage connecting the discharge port and the discharge chamber And a drive shaft rotatably supported in a housing composed of the front housing, the cylinder block, and the rear housing, and a drive shaft connected to the drive shaft to rotate in synchronization with the drive shaft. A swash plate whose inclination angle is variable with respect to the drive shaft, a conversion mechanism which converts the rotation of the swash plate into a reciprocating motion of the piston, and a pressure supply passage which connects the discharge chamber and the crank chamber. A control valve disposed in the pressure supply passage, a pressure release passage communicating the crank chamber and the suction chamber, a throttle disposed in the pressure release passage, and a downstream side of the throttle. A first filter covering an opening of the pressure release passage on the suction chamber side, the variable capacity compressor compressing the refrigerant sucked into the cylinder bore from the suction chamber and discharging the compressed refrigerant to the discharge chamber. The first filter has a mesh member having a predetermined opening, bypasses the mesh member to communicate the pressure release passage with the suction chamber, and has a flow passage having a flow passage cross-sectional area larger than that of the throttle. A first bypass passage having a cross-sectional area is provided , and an opening of the first bypass passage on an inner side of the first filter is directed in a radial direction of an opening of the pressure release passage on the suction chamber side. It is characterized in that it is arranged apart from the extension of the opening of the passage .

Further, it is preferable that the mesh member has an opening of 20 μm or less.

Further, preferably, the flow passage cross-sectional area of the first bypass passage may be set to be equal to or smaller than the minimum flow passage cross-sectional area of the region other than the throttle of the pressure release passage.

Further preferably, the first filter has an annular member that covers the periphery of the opening of the pressure release passage, and a foreign matter trap portion that is continuously provided from the annular member and that has the net member integrated therein. The first bypass path may be formed between the contact member with which the annular member abuts and the annular member.

Further, preferably, a groove is formed on a surface of the annular member that abuts the abutting member, and the groove forms the first bypass passage.

Further preferably, the first filter may be arranged in a region other than an extension region of the opening of the suction passage to the suction chamber.

Further preferably, the suction chamber further includes a second filter which covers the first filter and has a mesh member, and the first bypass path is provided between the first filter and the second filter. It is preferable that the space communicates with the inside of the first filter, and the mesh size of the mesh member of the second filter is set to be larger than the mesh size of the mesh member of the first filter.

Further, preferably, the suction passage further comprises a third filter having a mesh member, and a second bypass passage bypassing the mesh member of the third filter is provided, and the mesh member mesh of the third filter is provided. The opening may be set to be equal to or larger than the opening of the mesh member of the first filter, and the flow passage cross-sectional area of the second bypass passage may be set larger than the minimum flow passage cross-sectional area of the suction passage.

According to the variable capacity compressor of the present invention, since the first bypass passage that bypasses the mesh member and connects the pressure release passage and the suction chamber is provided, even if foreign matter is deposited on the first filter, the refrigerant is cooled. Can pass through the first bypass passage and flow into the suction chamber from the pressure release passage. Thus, the refrigerant can be discharged from the crank chamber to the suction chamber through the pressure release passage and the first bypass passage, the swash plate can be tilted, and the discharge capacity can be controlled.

Since the first bypass passage has a flow passage cross-sectional area that is equal to or larger than the flow passage cross-sectional area of the throttle of the pressure release passage, even if the mesh member of the first filter is completely closed, the minimum distance from the crank chamber to the suction chamber is reduced. The channel cross-sectional area is defined by the diaphragm. Thereby, even if the mesh member of the first filter is completely closed, the discharge volume control can be favorably executed.

It is a sectional view of a compressor concerning a 1st embodiment of the present invention. It is sectional drawing which shows the detail of the 1st filter attachment part in the compressor which concerns on 1st Embodiment. It is sectional drawing which shows the detail of the 1st filter attachment part in the compressor which concerns on 2nd Embodiment. It is sectional drawing of the compressor which concerns on 3rd Embodiment. It is sectional drawing of the compressor which concerns on 4th Embodiment.

FIG. 1 is a sectional view of a variable capacity compressor (hereinafter referred to as a compressor 100) according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view showing details of the first filter 180 mounting portion in the compressor 100 according to the first embodiment.

The compressor 100 according to the first embodiment of the present invention is used, for example, in a vehicle air conditioning system and is provided in a circulation path in which a refrigerant (for example, R134a) circulates. A compressor 100, a radiator (condenser), an expander (expansion valve), and an evaporator are sequentially inserted in the circulation path of the vehicle air conditioning system in the flow direction of the refrigerant. The compressor 100 performs a series of processes including a refrigerant suction step, a sucked refrigerant compression step, and a compressed refrigerant discharge step to circulate the refrigerant in the circulation path.

As shown in FIG. 1, the compressor 100 is a swash plate type variable displacement compressor, and has a substantially cylindrical cylinder block 101 having a plurality of cylinder bores 101 a, and a front housing 102 connected to one end of the cylinder block 101. And a rear housing 104 connected to the other end of the cylinder block 101 via a valve plate 103 (contact member).

A crank chamber 105 is defined by the cylinder block 101 and the front housing 102, and a drive shaft 106 extends vertically through the crank chamber 105. The drive shaft 106 penetrates an annular swash plate 107 arranged in the crank chamber 105, and the swash plate 107 is hinged to a rotor 108 fixed to the drive shaft 106 via a connecting portion 109. Therefore, the swash plate 107 can tilt while moving along the drive shaft 106.

Between the rotor 108 and the swash plate 107, a coil spring 110 that biases the swash plate 107 toward the minimum tilt angle is mounted around the drive shaft 106, while the swash plate 107 is sandwiched between the coil spring 110 and the coil spring 110. On the opposite side, that is, between the swash plate 107 and the cylinder block 101, a coil spring 111 that biases the swash plate 107 toward the maximum inclination angle is mounted around the drive shaft 106.

The drive shaft 106 penetrates through the inside of the boss portion 102 a protruding to the outside of the front housing 102, and its tip extends to the outside. A shaft sealing device 112 is inserted between the drive shaft 106 and the boss portion 102a to shut off the inside and outside of the front housing 102. The drive shaft 106 is rotatably supported by bearings 113, 114, 115 and 116 in the radial direction and the thrust direction. The drive shaft 106 is rotationally driven by transmitting a drive force from an external drive source such as an engine to the tip protruding from the boss 102a.

A piston 117 is arranged in the cylinder bore 101a, and a tail portion protruding into the crank chamber 105 is integrally formed with the piston 117. A pair of shoes 118 is arranged in the recess 117a formed in the tail portion, and the shoes 118 are in sliding contact with the outer peripheral portion of the swash plate 107 so as to be sandwiched. Therefore, the piston 117 and the swash plate 107 interlock with each other via the shoe 118, and the rotation of the drive shaft 106 causes the piston 117 to reciprocate in the cylinder bore 101a (conversion mechanism).

A suction chamber 119 and a discharge chamber 120 are defined in the rear housing 104. The discharge chamber 120 is annularly arranged inside the rear housing 104, and the suction chamber 119 is arranged radially inside the discharge chamber 120. The suction chamber 119 can communicate with the cylinder bore 101a via a suction hole 103a provided in the valve plate 103. The discharge chamber 120 communicates with the cylinder bore 101a via a discharge hole 103b provided in the valve plate 103. Between the cylinder block 101 and the rear housing 104, in order from the cylinder block 101 side, the cylinder gasket 150, the suction valve forming body 160, the valve plate 103, the discharge valve forming body 130 (contact member), the head gasket. 170 is interposed. The suction hole 103a is opened and closed by a suction valve formed in the suction valve forming body 160, and the discharge hole 103b is opened and closed by a discharge valve formed in the discharge valve forming body 130.

The front housing 102, the center gasket (not shown), the cylinder block 101, the cylinder gasket 150, the suction valve forming body 160, the discharge valve forming body 130, the head gasket 170, and the rear housing 104 are fastened together by a plurality of through bolts 140. A housing of the compressor 100 is formed.

A muffler 121 is provided outside the cylinder block 101. A muffler casing 122 that constitutes the muffler 121 is joined to a muffler base 101b that is integrally formed with the cylinder block 101 via a seal member (not shown). The muffler casing 122 and the muffler base 101b define a muffler space 123, and the muffler space 123 communicates with the discharge chamber 120 via a discharge passage 124 that penetrates the rear housing 104, the valve plate 103, and the muffler base 101b.

A discharge port 122a is formed in the muffler casing 122, and a check valve 200 is arranged in the muffler space 123 so as to block between the discharge passage 124 and the discharge port 122a. Specifically, the check valve 200 opens and closes according to the pressure difference between the pressure on the discharge passage 124 side and the pressure on the muffler space 123 side, and closes when the pressure difference is smaller than a predetermined value, while it also has a predetermined value. If it is larger, it opens.

The discharge chamber 120 can be communicated with the forward path portion of the refrigerant circulation path through the discharge passage 124, the muffler space 123, and the discharge port 122a, and this communication is interrupted by the check valve 200. On the other hand, the suction chamber 119 communicates with the return passage portion of the refrigerant circulation passage through the suction passage 104b and the suction port 104a provided in the rear housing 104.

An electromagnetically controlled displacement control valve (control valve) 300 is connected to the rear housing 104, and the displacement control valve 300 is inserted in the pressure supply passage 125. A part of the pressure supply passage 125 is formed from the rear housing 104 to the cylinder block 101 via the valve plate 103 so as to connect the discharge chamber 120 and the crank chamber 105.

On the other hand, the suction chamber 119 communicates with the crank chamber 105 via the pressure release passage 127. The pressure release passage 127 is composed of a gap between the drive shaft 106 and the bearings 115 and 116, a space 128, and a fixed orifice 160 a (throttle) formed in the valve plate 103.

Further, the suction chamber 119 is connected to the capacity control valve 300 independently of the pressure supply passage 125 through a pressure sensitive passage 126 formed in the rear housing 104. The capacity control valve 300 adjusts the opening degree of the pressure supply passage 125 that connects the discharge chamber 120 and the crank chamber 105, and controls the amount of refrigerant (discharge gas) introduced from the discharge chamber 120 to the crank chamber 105.

The fixed orifice 160a is a portion that defines the minimum value of the flow passage cross-sectional area of the pressure release passage 127, and the diameter of the fixed orifice 160a is such that blow-by gas that leaks to the crank chamber 105 side when the piston 117 compresses the gas is discharged. It has the minimum necessary and sufficient diameter.

Therefore, the discharge volume is controlled by adjusting the discharge gas introduction amount to the crank chamber 105 by the capacity control valve 300 to change the pressure of the crank chamber 105 and changing the inclination angle of the swash plate 107, that is, the stroke of the piston 117. can do. The capacity control valve 300 is an externally controlled capacity control valve that operates according to an external signal. The capacity control valve 300 senses the pressure in the suction chamber 119 through the pressure-sensitive passage 126 and adjusts the amount of electricity supplied to the solenoid of the capacity control valve 300. By doing so, the discharge capacity is controlled so that the pressure in the suction chamber 119 becomes a predetermined value, and when the energization is turned off, the valve body is forcibly opened to minimize the discharge capacity.

The opening of the suction passage 104b on the suction chamber 119 side is arranged outside the region (extension region) near the extension line of the opening 161 of the pressure release passage 127 on the suction chamber 119 side.

Further, the suction chamber 119 is provided with a first filter 180 so as to cover the opening 161 of the pressure release passage 127. Foreign matter contained in the refrigerant flowing from the crank chamber 105 through the pressure release passage 127 and into the suction chamber 119 is captured by the first filter 180.

The first filter 180 has an annular plate-shaped opening member (annular member) 181 arranged around the opening 161 on the suction chamber 119 side of the pressure release passage 127, and has a cylindrical shape by being integrated with the opening member 181. And a foreign matter capturing unit 182. The foreign matter catching portion 182 has a cylindrical case 183 having one end opening and a plurality of opening portions on the side surface and an opening portion on the other end, and a net member 184 and a case 183 attached to the opening portion on the side surface of the case 183. Is formed of a net member 185 attached to the opening at the other end. Both the case 183 and the net members 184, 185 are made of resin or the like, and the openings of the net members 184, 185 are set to 20 μm or less (for example, 10 μm). The opening member 181 has an inner edge portion connected to one end of the case 183 over the entire circumference thereof, and an outer peripheral portion thereof projects radially outward from the case 183 to form a flange.

The head gasket 170 is formed with an insertion hole having a diameter larger than that of the case 183 and smaller than the outer peripheral diameter of the opening member 181. The edge portion of the insertion hole in the head gasket 170 is slightly smaller than the thickness of the opening member 181, and is bent and protrudes toward the suction chamber 119. Then, the first filter 180 is arranged so as to cover the opening 161 of the fixed orifice 160a, and the flange that is the edge of the opening member 181 is sandwiched between the discharge valve forming body 130 and the edge of the insertion hole of the head gasket 170. By fastening the housing with the through bolt 140, the opening member 181 is in close contact with the discharge valve forming body 130, and the first filter 180 covers the opening 161 and is fixed to the valve plate 103 via the discharge valve forming body 130. To be done.
The discharge valve forming body 130 corresponds to the contact member of the present invention with which the opening member 181 contacts. The opening member 181 may have a structure in which the opening member 181 is brought into contact with and fixed to the valve plate 103. In this case, the valve plate 103 corresponds to the contact member of the present invention.

Further, in the present embodiment, the bypass passage 186 (first bypass passage) that connects the inside and the outside of the first filter 180 is provided. The bypass passage 186 has a groove extending in the radial direction provided on the contact surface of the opening member 181 with respect to the discharge valve forming body 130, and a notch portion (not shown) formed at the edge of the insertion hole of the head gasket 170. It is composed by. By fixing the first filter 180 to the valve plate 103, a bypass passage 186 extending in the radial direction is formed between the opening member 181 and the discharge valve forming body 130.

The opening 186a of the bypass passage 186 inside the first filter 180 is arranged apart from the extension line of the opening 161 of the pressure release passage 127 on the suction chamber 119 side, and is opened in a direction perpendicular to the extension line. ing.

Further, the minimum flow passage cross-sectional area of the bypass passage 186 is set to be larger than the flow passage cross-sectional area of the fixed orifice 160a, which is the minimum flow passage cross-sectional area of the pressure release passage 127, and the pressure release passage in a portion other than the fixed orifice 160a. It is set smaller than the flow passage cross-sectional area 127.

With the above configuration, in the compressor 100 according to the first embodiment, the first filter 180 is provided so as to cover the opening 161 on the suction chamber 119 side of the pressure release passage 127. It is possible to suppress entry of a minute foreign substance from 105 into the suction chamber 119 via the pressure release passage 127. Since the openings of the mesh members 184, 185 of the first filter 180 are, for example, 20 μm or less, it is possible to suppress the movement of minute foreign matter generated in the sliding portion or the like in the crank chamber 105 to the suction chamber 119 and suck the suction. It is possible to prevent the valve element from sticking to the capacity control valve 300 from the chamber 119 via the cylinder bore 101a and the discharge chamber 120 and causing foreign matter to flow.

In addition, in the present embodiment, since the bypass passage 186 that bypasses the mesh members 184 and 185 of the first filter 180 and connects the pressure release passage 127 and the suction chamber 119 is provided, the first filter 180 has foreign matter. Even if the gas is accumulated and clogging occurs, the refrigerant can be allowed to flow from the crank chamber 105 to the suction chamber 119 via the pressure release passage 127 and the bypass passage 186. Accordingly, even if the mesh members 184 and 185 of the first filter 180 are blocked by the foreign matter, the refrigerant can be discharged from the crank chamber 105 through the pressure release passage 127, and the discharge capacity can be controlled.

In particular, in the present embodiment, the flow passage cross-sectional area of the bypass passage 186 is set to be larger than the fixed orifice 160a which is the minimum value of the flow passage cross-sectional area of the pressure release passage 127. Even if all the refrigerant discharged from the pressure release passage 127 to the suction chamber 119 passes through the bypass passage 186, the minimum flow passage cross-sectional area in the flow passage from the crank chamber 105 to the suction chamber 119 has a fixed orifice. 160a. As a result, even if the first filter 180 is blocked by the accumulation of foreign matter, the function of the fixed orifice 160a is ensured, and the discharge flow rate of the refrigerant from the crank chamber 105 to the suction chamber 119 via the pressure release passage 127 becomes excessive. Without being restricted, it is possible to prevent a decrease in the response accuracy of the discharge volume control, and it is possible to favorably execute the discharge volume control.

Further, since the flow passage cross-sectional area of the bypass passage 186 is set smaller than the flow passage cross-sectional area of the pressure release passage 127 other than the fixed orifice 160a, the foreign matter flows into the suction chamber 119 through the bypass passage 186. Can be suppressed.

Further, the opening 186a of the bypass passage 186 inside the first filter 180 is arranged apart from the extension line of the opening 161 on the suction chamber 119 side of the pressure release passage 127, and is oriented in the direction perpendicular to the extension line. Since it is open, the refrigerant discharged from the opening 161 of the pressure release passage 127 does not directly go to the opening 186a of the bypass passage 186, and the foreign matter mixed in the refrigerant is prevented from flowing into the bypass passage 186. You can As a result, it is possible to suppress deterioration of the collection performance of the first filter 180 due to the provision of the bypass passage 186.

Further, the first filter 180 is arranged in a region other than the extension region of the opening of the suction passage 104b to the suction chamber 119, and the foreign matter is trapped in the net member 185 of the first filter 180, especially at the bottom. Therefore, when the refrigerant flows from the suction passage 104b into the suction chamber 119, the flow of the refrigerant from the suction passage 104b prevents foreign matters from being separated from the mesh member 185 of the first filter 180 and flowing into the bypass passage 186. Can be suppressed. In this way, by setting the opening position of the suction passage 104b, it is possible to prevent foreign matter from flowing into the bypass passage 186 and passing through the first filter 180.

Further, in the present embodiment, since the bypass passage 186 is formed by forming a groove on the contact surface of the opening member 181 with which the discharge valve forming body 130 abuts, the bypass passage 186 can be easily formed.

FIG. 3 is a cross-sectional view showing details of the first filter 180 mounting portion in the compressor 100 according to the second embodiment.

As shown in FIG. 3, in the second embodiment, the opening member 181 in the first embodiment is not provided with a groove, and the contact surface of the discharge valve forming body 130 of the valve plate 103 is provided in the radial direction of the opening member 181. A groove extending to the first filter 180 is provided, and the groove forms a bypass passage 186 that connects the inside and the outside of the first filter 180. Accordingly, also in the second embodiment, the bypass passage 186 can be easily formed by forming the groove as in the first embodiment.

FIG. 4 is a cross-sectional view of the compressor 100 according to the third embodiment.
As shown in FIG. 4, in the compressor 100 of the third embodiment, in addition to the compressor 100 of the first embodiment or the second embodiment, foreign matter that further enters the suction chamber 119 from the suction passage 104b. The suction chamber 119 is provided with a second filter 190 for capturing the gas.

The second filter 190 has a tubular shape and both ends are open ends, and the valve plate 103 and the suction chamber 119 are arranged so that the peripheral surface on which the mesh member is arranged covers the radial direction of the first filter. It is located between the end wall. The open end on the one end side of the second filter 190 is fitted into the hole in the end wall of the suction chamber 119 to which the suction passage 104b is connected, and the open end on the other end side is the head gasket 170 opened by the bypass passage 186. The head gasket 170 is abutted at a portion radially outside the edge of the insertion hole.
Therefore, the refrigerant flowing through the pressure release passage 127 flows into the second filter 190 together with the refrigerant flowing through the suction passage 104b.
The opening size of the second filter 190 is set larger than that of the first filter 180. For example, the opening is set to about 100 μm to 200 μm.

Therefore, in the third embodiment, even if the first filter 180 is completely clogged and the foreign matter passes from the crank chamber 105 through the bypass passage 186, the second filter 190 removes the relatively large foreign matter. Can be captured. As a result, in the compressor 100 of the third embodiment, when the first filter 180 is completely clogged, the foreign matter that flows out from the crank chamber 105 can be captured more effectively than the compressor 100 of the first embodiment. Can be improved.

FIG. 5 is a sectional view of the compressor 100 according to the fourth embodiment.
As shown in FIG. 5, in the compressor 100 of the fourth embodiment, in addition to the compressor 100 of the first embodiment or the second embodiment, a third filter 195 that captures foreign matter is further sucked. It is provided in the passage 104b. The third filter 195 is a filter that uses a mesh member like the first filter 180, and the mesh opening of the mesh member is set to be the same as the mesh opening of the mesh member of the first filter 180. .. Further, the third filter 195 also includes a bypass passage 196 (second bypass passage) formed in a radial direction perpendicular to the extending direction of the suction passage 104b. The flow passage cross-sectional area of the bypass passage 196 is set to be equal to or larger than the minimum flow passage cross-sectional area of the suction passage 104b.

As a result, in the compressor 100 of the third embodiment, it is possible to suppress the inflow of minute foreign matter from the suction port 104a into the suction chamber 119, and further suppress the control failure of the capacity control valve 300 due to the inflow of foreign matter. You can Even if the third filter 195 is blocked due to the accumulation of foreign matter, the bypass passage 196 allows the refrigerant to flow, and the compressor 100 can ensure the discharge of the refrigerant. Since the bypass passage 196 is formed in the radial direction perpendicular to the extending direction of the suction passage 104b, when foreign matter is not deposited on the third filter 195, the foreign matter is sucked through the bypass passage 196. The flow into the chamber 119 can be suppressed.

The invention of the present application is not limited to the above-described embodiment, and various detailed structures in the above-described embodiment can be appropriately changed. Further, in the above embodiment, the present invention is applied to the compressor of the vehicle air conditioning system, but the present invention can be widely applied to compressors for other purposes.

100 compressor (variable capacity compressor)
101 cylinder block 102 front housing 103 valve plate (contact member)
104 Rear Housing 106 Drive Shaft 107 Swash Plate 117 Piston 125 Pressure Supply Passage 127 Pressure Release Passage 130 Discharge Valve Forming Body (Abutting Member)
160a Fixed orifice (throttle)
180 First filter 181 Opening member (annular member)
182 foreign matter capturing section 184, 185 mesh member 186 bypass path (first bypass path)
190 Second filter 195 Third filter 196 Bypass path (second bypass path)
300 capacity control valve (control valve)

Claims (8)

A cylinder block in which a plurality of cylinder bores are formed;
Pistons respectively arranged in the cylinder bores,
A front housing that closes one end side of the cylinder block and forms a crank chamber in cooperation with the cylinder block;
A valve plate for closing the other end of the cylinder block,
A discharge chamber, which is disposed so as to face the cylinder block with the valve plate sandwiched therebetween, and is annularly disposed inside, a suction chamber disposed radially inside the discharge chamber, a suction port, and the suction chamber. And a rear housing having a discharge passage connecting the discharge chamber and a suction passage connecting the discharge chamber,
A drive shaft rotatably supported in a housing composed of the front housing, the cylinder block, and the rear housing;
A swash plate that is connected to the drive shaft, rotates in synchronization with the drive shaft, and has a variable inclination angle with respect to the drive shaft;
A conversion mechanism that converts the rotation of the swash plate into the reciprocating motion of the piston,
A pressure supply passage communicating the discharge chamber and the crank chamber,
A control valve disposed in the pressure supply passage,
A pressure release passage that connects the crank chamber and the suction chamber,
A throttle disposed in the pressure release passage,
A first filter which is provided on the downstream side of the throttle and covers an opening of the pressure release passage on the suction chamber side,
A variable capacity compressor for compressing the refrigerant sucked from the suction chamber into the cylinder bore and discharging the refrigerant to the discharge chamber,
The first filter has a mesh member with a predetermined opening,
A first bypass passage that bypasses the mesh member and connects the pressure release passage and the suction chamber to each other, and has a flow passage cross-sectional area equal to or larger than the flow passage cross-sectional area of the throttle ;
The opening of the first bypass passage on the inner side of the first filter faces the radial direction of the opening of the pressure release passage on the suction chamber side and is arranged apart from the extension line of the opening of the pressure release passage. variable capacity compressor, characterized in that that. The variable capacity compressor according to claim 1, wherein the mesh member has an opening of 20 μm or less. 3. The variable capacity according to claim 1, wherein a flow passage cross-sectional area of the first bypass passage is set to be equal to or smaller than a minimum flow passage cross-sectional area of a region of the pressure release passage other than the throttle. Compressor. The first filter has an annular member that covers the periphery of the opening of the pressure release passage, and a foreign matter capturing portion that is continuous from the annular member and that has the net member integrated therewith.
4. The variable according to any one of claims 1 to 3 , wherein the first bypass passage is formed between an abutting member with which the annular member abuts and the annular member. Capacity compressor. The variable displacement compressor according to claim 4 , wherein a groove is formed in a surface of the annular member that is in contact with the contact member, and the groove forms the first bypass path. The first filter includes a variable displacement compressor according to any one of claims 1 5, characterized in that arranged in the non-extended area of the opening into the suction chamber of the suction passage. The suction chamber further includes a second filter that covers the first filter and has a mesh member,
The first bypass path connects the space between the first filter and the second filter with the inside of the first filter,
The mesh of the second filter of the mesh member is variable according to any one of claims 1 6, characterized in that it is set larger than the mesh of the mesh member of the first filter Capacity compressor. The suction passage further includes a third filter having a mesh member,
Providing a second bypass path that bypasses the mesh member of the third filter;
The mesh size of the mesh member of the third filter is set to be equal to or larger than the mesh size of the mesh member of the first filter,
The flow path cross-sectional area of the second bypass passage, the variable displacement compressor according to any one of claims 1 7, characterized in that it is set larger than the minimum flow path cross-sectional area of the suction passage ..

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