JP2021038703A - Reciprocation type compressor - Google Patents

Abstract

To facilitate connection between a chamber and a passage portion and improve design flexibility of the passage portion in a reciprocation type compressor including the chamber with a discharge passage provided at a cylinder block and the passage portion provided at a cylinder head.SOLUTION: A discharge passage 144 of a reciprocation type compressor includes: a first chamber 162 provided at a cylinder block 101; a second chamber 170 provided at a cylinder head 104; a first communication hole 201 and a first communication groove 202 which penetrate through an interposition member IM at the radial outer side of the second chamber 170 and allow a discharge chamber 142 and the first chamber 162 to communicate with each other; a second communication hole 203 which penetrates through the interposition member IM in the second chamber 170 and allows the first chamber 162 and the second chamber 170 to communicate with each other; and a communication passage 204 which allows the second chamber 170 and the high pressure side of an external refrigerant circuit to communicate with each other.SELECTED DRAWING: Figure 2

Description

The present invention relates to a reciprocating compressor having a plurality of pistons reciprocating in the corresponding cylinder bores.

Patent Document 1 describes an example of a conventional reciprocating compressor. In the reciprocating compressor described in Patent Document 1, a chamber 30 incorporating an oil separation mechanism 40 is provided in the central region of the cylinder block 1, and is provided in the lower bottom portion of the chamber 30 and the front housing 2. The crank chamber 7 is communicated with the oil return hole 34. Further, the discharge passage is connected to an external refrigeration circuit from the discharge chamber 6 provided in the rear housing 3 corresponding to the cylinder head via the chamber 30 provided in the cylinder block 1. The reciprocating compressor described in Patent Document 1 has such a configuration, which makes it possible to reduce the oil content of the refrigerant delivered to the refrigeration circuit and reduce the pulsation of the discharge pressure. There is.

Japanese Unexamined Patent Publication No. 7-27047

In the reciprocating compressor described in Patent Document 1, the discharge passages are the first discharge passage 32 and the first discharge passage 32, which are penetrated through the fixture 31 of the discharge valve 16 and communicate with the discharge chamber 6 and the chamber 30. A second discharge passage 33, which is arranged diagonally above the discharge passage 32 and independently penetrates the discharge chamber 6 and is connected to the refrigeration circuit, is included. Here, the second discharge passage 33 is provided in the rear housing (cylinder head) 3 and needs to be connected to the chamber 30 provided in the cylinder block 1.

However, in the reciprocating compressor described in Patent Document 1, the fixture 31 through which the first discharge passage 32 is penetrated is located on the radial inner side (approximately the center) of the chamber 30, and the second discharge is performed. The connection position between the passage 33 and the chamber 30 is limited to the radial outer region of the fixture 31 and within the radial inner region of the chamber 30. Further, between the chamber 30 provided in the cylinder block 1 and the second discharge passage 33 provided in the rear housing (cylinder head) 3, a valve plate 4 to which the fixture 31 is attached and the fixture 31 provide a valve. There is a discharge valve retainer fixed to the valve plate 4 by the discharge valve 16 fixed to the plate 4 and the fixture 31. Therefore, it is not easy to connect the chamber 30 provided in the cylinder block 1 and the second discharge passage 33 provided in the rear housing (cylinder head) 3, and in the rear housing (cylinder head) 3. There is a problem that the degree of freedom in designing the second discharge passage 33 may be limited.

Therefore, according to the present invention, in a reciprocating compressor including a chamber in which the discharge passage is provided in the cylinder block and a passage portion provided in the cylinder head, the chamber and the passage portion constituting the discharge passage can be easily separated from each other. It is an object of the present invention to enable connection and to improve the degree of design freedom of the passage portion in the cylinder head.

According to one aspect of the present invention, a reciprocating compressor is provided. This reciprocating compressor is interposed between a cylinder block having a plurality of cylinder bores arranged in an annular shape, a housing member provided on one of the cylinder blocks and having a crank chamber formed therein, and the other of the cylinder blocks. A cylinder head provided via a member, a discharge chamber is formed, and a suction chamber is formed radially outside the discharge chamber, a plurality of pistons reciprocally housed in the plurality of cylinder bores, and the above. A drive shaft extending through the crank chamber and a conversion mechanism for converting the rotation of the drive shaft into reciprocating motion of the plurality of pistons, the conversion mechanism including a swash plate mounted on the drive shaft. Including. In the reciprocating compressor, the refrigerant that has flowed into the suction chamber from the low pressure side of the external refrigerant circuit through the suction passage is sucked into the corresponding cylinder bore by the reciprocating movement of each piston, compressed, and discharged to the discharge chamber. The refrigerant discharged into the discharge chamber is configured to flow out to the high pressure side of the external refrigerant circuit through the discharge passage. The discharge passages are provided in a first chamber provided on the radial inside of the plurality of cylinder bores in the cylinder block and on the radial inside of the discharge chamber in the cylinder head, and the first chamber is interposed below the intervening member. The second chamber facing the chamber, the first communication portion that penetrates the intervening member on the radial outer side of the second chamber and communicates the discharge chamber and the first chamber, and the said in the second chamber. It includes a second communication portion that penetrates the intervening member and communicates the first chamber and the second chamber, and an outlet passage that communicates the second chamber and the high pressure side of the external refrigerant circuit.

According to one aspect of the present invention, in a reciprocating compressor in which a discharge passage includes a chamber provided in a cylinder block and a passage portion provided in a cylinder head, the chamber and the passage portion can be easily connected. At the same time, it is possible to improve the degree of freedom in designing the passage portion in the cylinder head.

It is sectional drawing which shows the schematic structure of 1st Embodiment of the swash plate type variable capacity compressor which is an example of the reciprocating type compressor by this invention. It is an enlarged view of the main part of FIG. It is a figure which shows the state which looked at the discharge valve forming plate as an intervening member intervening between a cylinder block and a cylinder head in the 1st Embodiment from the cylinder head side. FIG. 5 is a cross-sectional view of a main part of the variable displacement compressor when cut with a cut surface different from that of FIG. 1 (and FIG. 2). It is a figure which shows the 1st modification of the 1st Embodiment. It is a figure which shows the 2nd modification of the said 1st Embodiment. It is a figure which shows the 3rd modification of the 1st Embodiment. It is sectional drawing of the main part of the 2nd Embodiment of the said swash plate type variable capacitance compressor. It is a figure which shows the modification of the 2nd Embodiment. It is sectional drawing of the main part of the 3rd Embodiment of the variable capacity compressor of the swash plate type. It is a figure which shows the state which looked at the discharge valve forming plate as an intervening member interposed between a cylinder block and a cylinder head in the 3rd Embodiment from the cylinder head side. It is a figure which shows the modification of the said 3rd Embodiment. It is sectional drawing of the main part of the 4th Embodiment of the said swash plate type variable capacity compressor. It is a figure which shows the modification of the 4th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
[First Embodiment]
FIG. 1 is a cross-sectional view showing a schematic configuration of a first embodiment of a swash plate type variable capacitance compressor (hereinafter, simply referred to as “variable compressor”) which is an example of a reciprocating compressor according to the present invention. 2 is an enlarged view of a main part of FIG. 1 (a cross-sectional view of a main part of the variable displacement compressor). The variable displacement compressor 100 according to the first embodiment is configured as a clutchless compressor mainly applied to an air conditioner system for vehicles. The top and bottom in FIG. 1 are the top and bottom in the vertical direction.

The variable displacement compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101a arranged in an annular shape, a front housing 102 provided on one of the cylinder blocks 101 (left side in FIG. 1), and the other of the cylinder blocks 101 (FIG. 1). It has a cylinder head 104 provided via a valve plate 103 (on the right side in 1). The cylinder block 101, the front housing 102, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 105 to form a compressor housing. Further, in the compressor housing, a crank chamber 140 is formed by the cylinder block 101 and the front housing 102.

Here, a center gasket (not shown) is interposed between the cylinder block 101 and the front housing 102. Further, as shown in FIG. 2, in addition to the valve plate 103, a cylinder gasket (not shown), a suction valve forming plate 150, a discharge valve forming plate 151, and a retainer are formed between the cylinder block 101 and the cylinder head 104. A plate 152 and a head gasket (not shown) are interposed. However, in this embodiment, the retainer forming plate 152 and the head gasket are integrally formed.

In the following description, members interposed between the cylinder block 101 and the cylinder head 104, that is, members such as the valve plate 103, the suction valve forming plate 150, the discharge valve forming plate 151, and the retainer forming plate 152 are generically referred to. Then, it is called "intervening member IM".

Returning to FIG. 1, the variable displacement compressor 100 has a drive shaft 110 extending horizontally through the crank chamber 140. A swash plate 111 is attached to the intermediate portion of the drive shaft 110 in the axial direction. The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120, and rotates together with the drive shaft 110. Further, the swash plate 111 is configured so that the angle with respect to the plane orthogonal to the axis O of the drive shaft 110 (hereinafter referred to as "tilt angle of the swash plate 111") can be changed.

The link mechanism 120 rotates with respect to the first arm 112a projecting from the rotor 112, the second arm 111a projecting from the swash plate 111, and one end side with respect to the first arm 112a via the first connecting pin 121. Includes a link arm 123 that is movably connected and whose other end is rotatably connected to the second arm 111a via a second connecting pin 122.

The swash plate 111 is formed with a shaft insertion hole 111b through which the drive shaft 110 is inserted. The shaft insertion hole 111b is formed so that the swash plate 111 can be tilted within a range of a maximum tilt angle and a minimum tilt angle. A minimum tilt angle regulating portion is formed in the shaft insertion hole 111b. When the tilt angle of the swash plate 111 when the swash plate 111 is orthogonal to the drive shaft 110 is set to the minimum tilt angle (= 0 °), the tilt angle of the swash plate 111 is approximately 0 ° in the minimum tilt angle regulating portion of the shaft insertion hole 111b. Then, it comes into contact with the drive shaft 110 and restricts further tilting of the swash plate 111. Further, when the tilt angle of the swash plate 111 reaches the maximum tilt angle, the swash plate 111 comes into contact with the rotor 112 and further tilting is restricted.

The drive shaft 110 includes a tilt angle reducing spring 114 that urges the swash plate 111 in a direction that reduces the tilt angle of the swash plate 111, and a tilt angle increasing spring 115 that urges the swash plate 111 in a direction that increases the tilt angle of the swash plate 111. And are installed. The tilt angle reducing spring 114 is arranged between the swash plate 111 and the rotor 112, and the tilt angle increasing spring 115 is mounted between the swash plate 111 and the spring support member 116 fixed to the drive shaft 110.

When the tilt angle of the swash plate 111 is the minimum tilt angle, the urging force of the tilt angle increasing spring 115 is set to be larger than the urging force of the tilt angle decreasing spring 114. Further, when the drive shaft 110 is not rotating, the swash plate 111 is positioned at an inclination angle in which the urging force of the tilt angle decreasing spring 114 and the urging force of the tilt angle increasing spring 115 are balanced.

One end side (the left end side in FIG. 1) of the drive shaft 110 penetrates the protruding portion 102a of the front housing 102 and extends to the outside of the front housing 102. A power transmission device (not shown) is connected to the one end of the drive shaft 110. The drive shaft 110 rotates in synchronization with the rotation of the power transmission device by transmitting the power from the external drive source to the power transmission device. Further, a shaft sealing device 130 is provided between the drive shaft 110 and the protruding portion 102a.

The other end side (right end side in FIG. 1) of the drive shaft 110 is inserted through the center bore 101b formed in the cylinder block 101. The center bore 101b is formed inside the plurality of cylinder bores 101a in the radial direction, and penetrates the cylinder block 101 in the horizontal direction. Specifically, the center bore 101b extends from one end surface (end surface on the front housing 102 side) to the other end surface (end surface on the cylinder head 104 side) of the cylinder block 101 at the radial center portion of the cylinder block 101. It penetrates.

In the present embodiment, the center bore 101b has the first bore 101b1 and the second from the other end surface (the end surface on the cylinder head 104 side) of the cylinder block 101 toward the one end surface (the end surface on the front housing 102 side). It has a bore 101b2, a third bore 101b3, a fourth bore 101b4, and a fifth bore 101b5 in this order.

The first bore 101b1 is open to the other end surface of the cylinder block 101. The second bore 101b2 is formed to have a smaller diameter than the first bore 101b1. The third bore 101b3 is formed to have a smaller diameter than the second bore 101b2. The fourth bore 101b4 is formed to have a smaller diameter than the third bore 101b3. The fifth bore 101b5 is formed to have a diameter larger than that of the first bore 101b1 and is open to the one end surface of the cylinder block 101, that is, in the crank chamber 140.

The connecting body of the drive shaft 110 and the rotor 112 is supported by the first bearing 131 provided in the front housing 102 and the second bearing 132 provided in the cylinder block 101 in the radial direction, and is supported by the front housing 102 in the thrust direction. It is supported by a third bearing 133 provided and a thrust plate 134 provided in the cylinder block 101. The gap between the other end (right end in FIG. 1) of the drive shaft 110 and the thrust plate 134 is adjusted to an appropriate value by the adjusting screw 135.

In the present embodiment, the first bearing 131 is mounted inside the shaft sealing device 130 (crank chamber 140 side) in the protruding portion 102a of the front housing 102, and the second bearing 132 is the center bore 101b of the cylinder block 101. It is attached to the fourth bore 101b4 of the above. Further, the third bearing 133 is arranged between the inner surface of the front housing 102 and the rotor 112, and the thrust plate 134 and the adjusting screw 135 are mounted on the third bore 101b3 of the center bore 101b of the cylinder block 101. ing.

A bottomed cylindrical partition member 161 is attached to the first bore 101b1. The partition member 161 is positioned by being press-fitted into the first bore 101b1 from the bottom surface side, and the bottom surface abuts on the annular stepped surface 101b6 between the first bore 101b1 and the second bore 101b2. The inside of the first bore 101b1 is partitioned from the other inside of the center bore 101b (that is, the inside of the second to fifth bores 101b2 to 101b5) by the partition member 161 and is located inside the plurality of cylinder bores 101a in the radial direction. Further, it constitutes a first chamber 162 located at the radial center portion of the cylinder block 101.

A piston 136 is housed in each cylinder bore 101a so as to be reciprocating. That is, the variable displacement compressor 100 has a plurality of pistons 136, each of which is housed in one of the plurality of cylinder bores 101a so as to be reciprocating. Each piston 136 has a protruding portion 136a protruding into the crank chamber 140. An accommodating portion is formed in the protruding portion 136a, and the outer edge portion of the swash plate 111 and its vicinity are accommodated in the accommodating portion via a pair of shoes 137. Each piston 136 reciprocates in the corresponding cylinder bore 101a by rotating the swash plate 111 with the rotation of the drive shaft 110. That is, the rotation of the drive shaft 110 is converted into the reciprocating motion of each piston 136 by the conversion mechanism including the swash plate 111 and the pair of shoes 137.

The cylinder head 104 is provided with a suction chamber 141 and a discharge chamber 142. The suction chamber 141 and the discharge chamber 142 are formed in a substantially annular shape on the end surface of the cylinder head 104 on the cylinder block 101 side. In the present embodiment, the suction chamber 141 is formed in the radial outer region of the cylinder head 104, and the discharge chamber 142 is formed in the radial inner region of the cylinder head 104 with respect to the suction chamber 141. In other words, the suction chamber 141 is provided so as to surround the discharge chamber 142.

As shown in FIG. 2, the suction chamber 141 communicates with each cylinder bore 101a through a plurality of suction holes 103a formed in the valve plate 103 corresponding to the plurality of cylinder bores 101a (that is, the same number as the silin bores 101a). ing. Each suction hole 103a is opened and closed by a corresponding suction valve (reed valve) 150a provided on the suction valve forming plate 150. That is, the suction valve forming plate 150 is formed with the same number of suction valves 150a as the suction holes 103a (and the cylinder bore 101a).

The discharge chamber 142 communicates with each cylinder bore 101a through a plurality of discharge holes 103b formed in the valve plate 103 corresponding to the plurality of cylinder bores 101a (that is, the same number as the cylindrical bores 101a). Each discharge hole 103b is opened and closed by a corresponding discharge valve (reed valve) 151a provided on the discharge valve forming plate 151. That is, the discharge valve forming plate 151 is formed with the same number of discharge valves 151a as the discharge holes 103b (and the cylinder bore 101a). Further, the opening degree (maximum opening degree) of each discharge valve 151a is regulated by the corresponding retainer 152a provided on the retainer forming plate 152.

In the present embodiment, the cylinder block 101 has seven cylinder bores 101a arranged in an annular shape, and the suction valve forming plate 150 has seven suction valves extending radially from the valve support portion on the center side thereof. 150a is provided, the discharge valve forming plate 151 is provided with seven discharge valves 151a extending radially from the valve support portion on the center side thereof, and the retainer forming plate 152 is provided with any one of the seven discharge valves 151a. Seven retainers 152a corresponding to the above are provided.

The suction chamber 141 communicates with the low pressure side of the refrigerant circuit (external refrigerant circuit) of the air conditioner system via the suction passage 143 formed in the cylinder head 104. The discharge chamber 142 communicates with the high pressure side of the refrigerant circuit of the air conditioner system via the discharge passage 144.

A refrigerant (that is, a low-pressure refrigerant) flows into the suction chamber 141 from the low-pressure side of the refrigerant circuit of the air conditioner system through the suction passage 143. The refrigerant that has flowed into the suction chamber 141 is sucked into the corresponding cylinder bore 101a by the reciprocating movement of each piston 136, compressed, and discharged to the discharge chamber 142. The refrigerant discharged into the discharge chamber 142 (that is, the high-pressure refrigerant) flows out to the high-pressure side of the refrigerant circuit of the air conditioner system through the discharge passage 144. The discharge passage 144 will be described in detail later.

Further, the variable displacement compressor 100 has a supply passage 145 for supplying the refrigerant of the discharge chamber 142 to the crank chamber 140, and a discharge passage 146 for discharging the refrigerant of the crank chamber 140 to the suction chamber 141. (Indicated by the broken line in FIG. 1). In the present embodiment, the supply passage 145 is arranged below the axis O of the drive shaft 110, and the discharge passage 146 is arranged above the axis O of the drive shaft 110.

The supply passage 145 is formed as a passage connecting the discharge chamber 142 and the crank chamber 140. A control valve 300 is provided in the middle of the supply passage 145.

The control valve 300 is attached to the cylinder head 104. In the valve body of the control valve 300, a refrigerant inlet portion into which the refrigerant from the discharge chamber 142 flows in, a refrigerant outlet portion from which the refrigerant flowing in from the refrigerant inlet portion flows out, and a pressure Ps in the suction chamber 141 are introduced. A pressure inlet and a pressure inlet are provided. Further, the control valve 300 has a valve body that opens and closes the valve hole, a pressure sensitive unit that gives an urging force in the valve opening direction to the valve body in response to the pressure Ps of the suction chamber 141, and a coil energization amount. It has a solenoid unit that applies an urging force to the valve body in the valve closing direction. The refrigerant inlet portion, the refrigerant outlet portion, and the valve hole form a part of the supply passage 145. The control valve 300 adjusts the opening degree of the supply passage 145 (more specifically, the valve hole) so that the pressure Ps of the suction chamber 141 becomes the pressure (set pressure) corresponding to the energization amount of the coil. It is configured in. The supply passage 145 will be described in detail later.

The discharge passage 146 is formed as a passage connecting the crank chamber 140 and the suction chamber 141. A throttle is provided in the discharge passage 146. The discharge passage 146 will be described in detail later.

When the control valve 300 increases the opening degree of the supply passage 145 (opens), the amount of the refrigerant (high pressure refrigerant) in the discharge chamber 142 supplied to the crank chamber 140 is the amount of the refrigerant discharged from the crank chamber 140 to the suction chamber 141. More than quantity. Therefore, the pressure in the crank chamber 140 increases. When the pressure in the crank chamber 140 increases, the tilt angle of the swash plate 111 decreases. As a result, the stroke of the piston 136 is reduced, and the discharge capacity of the variable displacement compressor 100 is reduced.

On the other hand, when the control valve 300 reduces (closes) the opening degree of the supply passage 145, the amount of refrigerant in the discharge chamber 142 supplied to the crank chamber 140 is larger than the amount of refrigerant discharged from the crank chamber 140 to the suction chamber 141. Will also decrease. Therefore, the pressure in the crank chamber 140 is reduced. When the pressure in the crank chamber 140 decreases, the tilt angle of the swash plate 111 increases. As a result, the stroke of the piston 136 increases and the discharge capacity of the variable displacement compressor 100 increases.

In this way, the variable displacement compressor 100 changes the pressure of the crank chamber 140 by adjusting the opening degree of the supply passage 145, that is, the amount of the refrigerant supplied from the discharge chamber 142 to the crank chamber 140 by the control valve 300. As a result, the tilt angle of the swash plate 111 is changed to control the stroke amount (discharge capacity) of the piston 136.

Further, the crank chamber 140 is filled with lubricating oil. The lubricating oil is agitated and turned into mist by rotating the swash plate 111 mainly with the rotation of the drive shaft 110, and moves in the variable displacement compressor 100 together with the refrigerant. Specifically, the mist-ized lubricating oil circulates together with the refrigerant in the internal circulation path formed by the crank chamber 140, the discharge passage 146, the suction chamber 141, the cylinder bore 101a, the discharge chamber 142, and the supply passage 145. Lubricates the inside of the variable displacement compressor 100.

Next, the discharge passage 144, the supply passage 145, and the discharge passage 146 will be described in detail with reference to FIGS. 2 to 4. FIG. 3 is a view showing a state in which the discharge valve forming plate 151 is viewed from the cylinder head 104 side, and FIG. 4 is a variable displacement compressor 100 when cut at a cutting surface different from that of FIG. 1 (and FIG. 2). It is a cross-sectional view of a main part of.

(Discharge passage 144)
As shown in FIG. 2, in the cylinder head 104, a columnar second chamber 170 is formed inside the discharge chamber 142 in the radial direction. The second chamber 170 is formed in the radial center portion of the cylinder head 104, and faces the first chamber 162 provided in the cylinder block 101 with the intervening member IM interposed therebetween. In the present embodiment, the second chamber 170 has a diameter smaller than the diameter of the first chamber 162 (first bore 101b1). In other words, the cross-sectional area perpendicular to the axis O of the drive shaft 110 of the first chamber 162 (first bore 101b1) is larger than the cross-sectional area perpendicular to the axis O of the drive shaft 110 of the second chamber 170. However, the volume of the first chamber 162 does not necessarily have to be larger than the volume of the second chamber 170, and may be larger or smaller than the volume of the second chamber 170.

Further, as shown in FIGS. 2 and 3, the discharge chamber 142 corresponds to a plurality of (five here) first communication holes 201 and a plurality of first communication holes 201 penetrating the intervening member IM. It communicates with the first chamber 162 via a plurality of (five in this case) first communication grooves 202 formed in the cylinder block 101. Here, the cross-sectional area of the first chamber 162 is larger than the total cross-sectional area of the passage formed by the plurality of first communication holes 201 and the plurality of first communication grooves 202, and the first chamber 162 has a plurality of first chambers 162. It constitutes an expansion space whose diameter is expanded with respect to the one communication hole 201 and the plurality of first communication grooves 202.

In the present embodiment, as described above, the discharge valve forming plate 151 is provided with seven discharge valves 151a in a radial pattern, and each first communication hole 201 is provided in the first chamber 162 (and the second chamber 170). It is provided between the discharge valves 151a that are radially outside and adjacent to each other (see FIG. 3). This means that when the intervening member IM is viewed from the cylinder head 104 side, each first communication hole 201 is provided between the adjacent retainers 152a. That is, in the present embodiment, the first communication hole 201 penetrates the valve plate 103 and the suction valve forming plate 150 as the intervening member IM. The alternate long and short dash line in FIG. 3 indicates the second chamber 170.

Each first communication groove 202 is formed in the other end surface (end surface on the cylinder head 104 side) of the cylinder block 101, and communicates the corresponding first communication hole 201 with the first chamber 162. Specifically, each first communication groove 202 extends radially outward from the peripheral edge of the opening of the first bore 101b1 (corresponding to the outer circumference of the first chamber 162) and exceeds the corresponding first communication hole 201. It has reached the position where it was. The depth of each first communication groove 202 becomes shallower as the distance from the peripheral edge of the opening of the first bore 101b1 increases (see FIG. 2).

The second chamber 170 is discharged by abutting the tip surface of the annular forming wall 104a integrally formed with the cylinder head 104 to form the second chamber 170 with the flat surface 152b at the central portion in the radial direction of the retainer forming plate 152. It is partitioned from room 142. Therefore, the annular forming wall 104a partitions the second chamber 170 from the discharge chamber 142, and is a flat surface 152b at the central portion in the radial direction of the retainer forming plate 152, and presses and holds the base end side of each retainer 152a. ing. It is desirable that the central axis of the annular forming wall substantially coincides with the central axis of the retainer forming plate 152 and the discharge valve forming plate 151, that is, the axis O of the drive shaft.

The second chamber 170 passes the intervening member IM through the second communication hole 203 penetrating the intervening member IM in the second chamber 170, and further, at the radial center portion of the first chamber 162 and the second chamber 170. It communicates with the first chamber 162 through the second communication hole 203 that penetrates. In the present embodiment, the second communication hole 203 penetrates the valve plate 103 as the intervening member IM, the suction valve forming plate 150, the discharge valve forming plate 151, and the retainer forming plate 152. The cross-sectional area of the second chamber 170 is larger than the cross-sectional area of the second communication hole 203, and the second chamber 170 constitutes an expansion space whose diameter is expanded with respect to the second communication hole 203.

Further, the second chamber 170 communicates with the high pressure side of the refrigerant circuit of the air conditioner system via a communication passage 204 extending in the radial direction in the cylinder head 104 (see FIG. 2). Here, the communication passage 204 extends upward, but the present invention is not limited to this. The communication passage 204 may be formed so as to extend in any radial direction, as long as one end thereof is connected to the second chamber 170.

Therefore, the discharge chamber 142 has a first passage composed of a plurality of first communication holes 201, a plurality of first communication grooves 202, a first chamber 162, a second communication hole 203, a second chamber 170, and a communication passage 204. The refrigerant that communicates with the high pressure side of the refrigerant circuit of the air conditioner system and is discharged to the discharge chamber 142 flows out to the high pressure side of the refrigerant circuit of the air conditioner system through the first passage. That is, in the present embodiment, the discharge passage 144 is formed by the first passage. Further, the plurality of first communication holes 201 and the plurality of first communication grooves 202 correspond to the "first communication portion" of the present invention, and the second communication hole 203 corresponds to the "second communication portion" of the present invention. The communication passage 204 corresponds to the "exit passage" of the present invention.

Here, in the present embodiment, the first chamber 162, the second communication hole 203, and the second chamber 170 are on the axis O of the drive shaft 110 (it does not have to be strictly on the axis O, but may be substantially on the axis O. It is located in the chamber. In other words, the center line of the first chamber 162, the center line of the second communication hole 203, and the center line of the second chamber 170 substantially coincide with the axis O of the drive shaft 110.

(Supply passage 145)
As shown in FIG. 4, in the present embodiment, the supply passage 145 includes a first connection path 211 and a second connection path 212 formed in the cylinder head 104, a control valve 300 provided in the cylinder head 104, and the like. It is composed of a first through hole 213 that penetrates the intervening member IM and a third connection path 214 formed in the cylinder block 101. The first connection path 211 connects the discharge chamber 142 and the refrigerant inlet portion of the control valve 300, and the second connection path 212 connects the refrigerant outlet portion of the control valve 300 and the first through hole 213. The third connecting path 214 connects the first through hole 213 and the crank chamber 140. Further, as shown in FIG. 3, the first through hole 213 is provided between the adjacent discharge valves 151a as in the first communication hole 201. That is, in the present embodiment, the first through hole 213 forming a part of the supply passage 145 is the valve plate 103 as the intervening member IM and the valve plate 103 as the intervening member IM, similarly to the first communication hole 201 forming a part of the discharge passage 144. It penetrates the suction valve forming plate 150. The first through hole 213 corresponds to the "through hole for supply passage" of the present invention.

(Discharge passage 146)
As shown in FIG. 4, in the present embodiment, the discharge passage 146 is formed in the fourth connection path 221 formed in the cylinder block 101, the second through hole 222 penetrating the intervening member IM, and the cylinder head 104. It is composed of a fifth connecting path 223 and the like. The fourth connection path 221 connects the crank chamber 140 and the second through hole 222, and the fifth connection path 223 connects the second through hole 222 and the suction chamber 141. Further, as shown in FIG. 3, the second through hole 222 is provided between the adjacent discharge valves 151a like the first communication hole 201 and the first through hole 213. That is, in the present embodiment, the second through hole 222 that forms a part of the discharge passage 146 is the first through hole 201 that forms a part of the discharge passage 144 and the first through hole that forms a part of the supply passage 145. Similar to the hole 213, it penetrates the valve plate 103 as the intervening member IM and the suction valve forming plate 150. Here, although not shown in the figure, the throttle is a cylinder block 101 (end of the fourth connecting path 221), an intervening member IM (valve plate 103 and / or a suction valve forming plate 150), or a cylinder. It may be provided at the head 104 (the end of the fifth connection path 223). The second through hole 222 corresponds to the "through hole for discharge passage" of the present invention.

Here, in the present embodiment, the five first communication holes 201 forming a part of the discharge passage 144, the first through hole 213 forming a part of the supply passage 145, and a part of the discharge passage 146 are formed. When the intervening member IM is viewed from the cylinder head 104 side, the second through hole 222 is arranged (arranged in an annular shape) on the same circle at intervals from each other (see FIG. 3).

As described above, in the variable displacement compressor 100 according to the present embodiment, the discharge passages 144 are the first chamber 162 provided inside the plurality of cylinder bores 101a in the cylinder block 101 in the radial direction, and the discharge chamber in the cylinder head 104. A second chamber 170, which is provided inside the 142 in the radial direction and faces the intervening member IM, is included. Here, the first chamber 162 passes through the first communication hole 201 and the cylinder block 101 formed in the first communication hole 201 and the cylinder block 101 that penetrate the intervening member IM on the radial outer side of the first chamber 162 and the second chamber 170. It communicates with the discharge chamber 142, and the first chamber 162 and the second chamber 170 communicate with each other through the second communication hole 203 penetrating the intervening member IM in the first chamber 162 and the second chamber 170. There is. Further, the second chamber 170 communicates with the high pressure side of the refrigerant circuit of the air conditioner system via a communication passage 204 extending in the radial direction in the cylinder head 104.

As described above, in the present embodiment, the first communication hole 201 for communicating the discharge chamber 142 and the first chamber 162 is arranged on the radial outer side of the second chamber 170, and the first chamber 162 and the second chamber 162 are arranged. A second communication hole 203 for communicating with the 170 is arranged in the second chamber 170 and in the first chamber 162. Therefore, as compared with the prior art, the first chamber 162 provided in the cylinder block 101 and the discharge chamber 142 provided in the cylinder head 104 are connected to each other, and the first chamber 162 provided in the cylinder block 101 and the cylinder are connected. It is easy to connect the second chamber 170 and the communication passage 204, which are passage portions provided in the head 104. Further, since the communication passage 204 may be provided so as to simply connect to the second chamber 170, the degree of freedom in designing the passage portion provided in the cylinder head 104 is also improved.

In particular, in the present embodiment, in the second chamber 170, the tip surface of the annular forming wall 104a integrally formed with the cylinder head 104 to form the second chamber 170 is the radial center portion of the retainer forming plate 152. It is partitioned from the discharge chamber 142 by abutting on the flat surface 152b. Therefore, the second chamber 170 can be easily partitioned from the discharge chamber 142 with a simple structure. Further, since the annular forming wall 104a abuts on the flat surface 152b at the central portion in the radial direction of the retainer forming plate 152, it also has a function of pressing and holding the base end side of each retainer 152a and each discharge valve 151a. ..

Further, in the above-described embodiment, the discharge chamber 142 and the first chamber 162 are formed in the first communication portion (the first communication hole 201 penetrating the intervening member IM and the cylinder block 101) on the radial outer side of the second chamber 170. It communicates through a plurality of first communication grooves 202). Specifically, the first communication portion (first communication hole 201) penetrates the valve plate 103 and the suction valve forming plate 150 between the adjacent discharge valves 151a. Therefore, the discharge chamber 142 and the first chamber 162 can be easily connected.

Here, in the above-described embodiment, since a plurality of (five) first communication holes 201 can be arranged at intervals on the same circle between adjacent discharge valves 151a (see FIG. 3), the variable capacitance can be arranged. One or more first communication holes 201 (and one or more first communication holes 201) depending on the installation conditions of the variable displacement compressor 100, such as when the compressor 100 is installed while being rotated around the axis O of the drive shaft 110. The 1-communication groove 202) can be provided at an appropriate position to allow the discharge chamber 142 and the first chamber 162 to communicate with each other. Further, by adjusting the number of the first communication holes 201 (and the first communication groove 202), the passage cross-sectional area (cross-sectional area of the first passage portion) between the discharge chamber 142 and the first chamber 162 is adjusted. It is also possible.

Further, in the present embodiment, the inside of the first bore 101b1 of the center bore 101b is a partition member mounted on the first bore 101b1 so as to abut the annular stepped surface 101b6 between the first bore 101b1 and the second bore 101b2. It is separated from the other interior of the center bore 101b by 161. The inside of the first bore 101b1 constitutes the first chamber 162. Therefore, it is possible to easily form the first chamber 162 by using the center bore 101b. Since the partition member 161 is pressed against the stepped surface 101b6 by the force of the discharge pressure, the displacement of the partition member 161 is effectively prevented.

Further, the first chamber 162 constitutes an expansion space whose diameter is expanded with respect to the first communication portion (first communication hole 201 and first communication groove 202), and the second chamber 170 is a second communication portion (first communication groove 202). It constitutes an expansion space whose diameter is expanded with respect to the two communication holes 203). Therefore, the first chamber 162 and the second chamber 170 function as two muffler chambers for reducing the pulsation of the discharge pressure. That is, the discharge passage 144 has two muffler chambers. Therefore, the pulsation of the discharge pressure can be effectively reduced.

In the above-described embodiment, the first chamber 162 is formed by using the center bore 101b penetrating the cylinder block 101. However, the present invention is not limited to this, and the first chamber 162 may be formed by a recess or the like formed on the other end surface (end surface on the cylinder head 104 side) of the cylinder block 101.

Further, the discharge chamber 142 and the first chamber 162 communicate with each other only through a plurality of first communication holes 201'that are radially outside the second chamber 170 and penetrate the intervening member IM in the first chamber 162. It may be configured to do so. In this case, for example, as shown in FIG. 5 corresponding to FIG. 3, a plurality of (five) first communication holes 201'form a part of the supply passage 145, and the first through hole 213 and the discharge passage. It suffices to be arranged radially inside the second through hole 222 that forms a part of the 146, and the plurality of first communication grooves 202 may be omitted. Of course, the discharge chamber 142 and the first chamber 162 may communicate with each other through one or more first communication holes 201'.

Further, as shown in FIG. 6, the second communication hole 203 and the second chamber 170 are formed to have substantially the same diameter, and one muffler chamber is formed by the first chamber 162, the second communication hole 203, and the second chamber 170. May be configured to form.

Further, as shown in FIG. 7, a discharge check valve 230 forming a part of the discharge passage 144 may be arranged in the second chamber 170. In this case, the discharge check valve 230 has, for example, a flange portion 231 and the peripheral edge portion of the flange portion 231 is in contact with the intervening member IM (here, the retainer forming plate 152) with the flange surface 231a in contact with the intervening member IM. It can be sandwiched and held by the cylinder block 101 and the cylinder head 104 via the cylinder block 101. In this way, when the variable displacement compressor 100 is stopped, the refrigerant does not flow from the second chamber 170 side to the first chamber 162 side through the second communication hole 203 (that is, the backflow of the refrigerant). Will be done. Since the discharge check valve 230 is arranged adjacent to the intervening member IM in the second chamber 170, the variable displacement compressor 100 is increased in size by providing the discharge check valve 230 (particularly). Axial dimensions increase) are also suppressed.

[Second Embodiment]
Next, a second embodiment of the variable displacement compressor will be described. FIG. 8 is a cross-sectional view of a main part of the second embodiment of the variable displacement compressor. The difference between the first embodiment and the second embodiment is that in the first embodiment, the first chamber 162 and the second chamber 170 communicate with each other through the second communication hole 203 formed in the intervening member IM. On the other hand (see FIG. 2), in the second embodiment, the first chamber 162 and the second chamber 170 communicate with each other via the inner space 240a of the tubular member 240 attached to the intervening member IM. Yes (see Figure 8). Other than that, it is basically the same as that of the first embodiment.

Here, in FIG. 8, the tubular member 240 is attached to the intervening member IM so as to project into the first chamber 162 and the second chamber 170. However, it is not limited to this. The tubular member 240 may be attached to the intervening member IM so as to project into the first chamber 162 and / or the second chamber 170.

The same effect as that of the first embodiment can be obtained by the second embodiment. Further, according to the second embodiment, by adjusting the amount of protrusion of the tubular member 240 into the first chamber 162 and / or the amount of protrusion of the tubular member 240 into the second chamber 170, the first chamber It is also possible to adjust the pulsation damping characteristics of the discharge pressure in 162 and / or the second chamber 170. Although not particularly limited, a spring pin press-fitted into the press-fitting hole formed in the intervening member IM (mainly the valve plate 103) can be used as the tubular member 240. In this case, the spring pin as the tubular member 240 is also used for positioning when fixing at least one of the suction valve forming plate 150, the discharge valve forming plate 151, and the retainer forming plate 152 to the valve plate 103. obtain.

In the second embodiment, the inner space 240a of the tubular member 240 corresponds to the "second communication portion" of the present invention. Further, among the modified examples of the first embodiment, those applicable to the second embodiment can also be modified examples of the second embodiment. For example, as shown in FIG. 9, the discharge check valve 230 may be arranged in the second chamber 170 also in the second embodiment. In this case, the tubular member 240 protrudes only into the first chamber 162, and the discharge check valve 230 has a flange surface 231a as an intervening member as in the case of the modified example of the first embodiment (see FIG. 7). The peripheral edge of the flange portion 231 can be sandwiched and held by the cylinder block 101 and the cylinder head 104 via the intervening member IM in a state of being in contact with the IM (retainer forming plate 152). The tubular member 240 may be integrated with the discharge check valve 230. In this case, the tubular member 240 is inserted with a minute gap between the tubular member 240 and the insertion hole penetrating the intervening member IM.

[Third Embodiment]
Next, a third embodiment of the variable displacement compressor will be described. FIG. 10 is a cross-sectional view of a main part of the variable capacitance compressor according to the third embodiment, and FIG. 11 is a view showing a state in which the discharge valve forming plate 151 is viewed from the cylinder head 104 side in the third embodiment (FIG. 3). The figure corresponding to). The main difference between the second embodiment and the third embodiment is that in the third embodiment, the first chamber 162, which forms a part of the discharge passage 144, also functions as an oil separation chamber. In this case, in the variable displacement compressor, the upper space in the first chamber 162 and the discharge chamber 142 are communicated with each other, and the first chamber 162 and the second chamber 170 are communicated with each other via the inner space 240a of the tubular member 240. And, the lower space in the first chamber 162 and the suction chamber 141 having a lower pressure than that of the first chamber 162 are communicated with each other.

Specifically, in the third embodiment, the variable displacement compressor provides an oil return passage 147 for returning the lubricating oil separated from the discharged refrigerant in the first chamber 162 functioning as the oil separation chamber to the suction chamber 141. Have more. The oil return passage 147 is formed as a passage connecting the lower space in the first chamber 162 and the suction chamber 141.

The discharged refrigerant flowing from the discharge chamber 142 into the first chamber 162 mainly collides with the partition member 161, whereby the lubricating oil contained therein is separated from the discharged refrigerant. The separated lubricating oil moves downward by gravity and is returned to the suction chamber 141 via the oil return passage 147. Further, the discharged refrigerant after the lubricating oil is separated passes through the inner space 240a of the tubular member 240, the second chamber 170, and the communication passage 204, and flows out to the high pressure side of the refrigerant circuit of the air conditioner system.

Here, in the third embodiment, the discharge passage 146 (second through hole 222) is provided on the lower side as compared with the first embodiment and the second embodiment (see FIGS. 3 and 11), and the cylinder. The shape member 240 is attached to the intervening member IM so as to project into at least the first chamber 162 of the first chamber 162 and the second chamber 170.

In the present embodiment, as shown in FIG. 10, the oil return passage 147 is provided in the second communication groove 251 formed in the cylinder block 101, the third through hole 252 penetrating the intervening member IM, and the cylinder head 104. It is composed of a sixth connecting path 253 formed, an oil storage chamber 254 formed in the cylinder head 104, and a throttle 255 formed in the cylinder head 104.

Here, as shown in FIG. 11, the third through hole 252 is provided between the adjacent discharge valves 151a like the first communication hole 201 and the like forming a part of the discharge passage 144, and is interposed. It penetrates the valve plate 103 as the member IM and the suction valve forming plate 150. Further, the second communication groove 251 is formed on the other end surface (end surface on the cylinder head 104 side) of the cylinder block 101, like the first communication groove 202 forming a part of the discharge passage 144, and is the first. The lower space in the chamber 162 communicates with the third through hole 252. The sixth connection path 253 communicates the third through hole 252 and the oil storage chamber 254, and the throttle 255 communicates the oil storage chamber 254 and the suction chamber 141.

The same effect as that of the first embodiment can be obtained in the third embodiment. Further, according to the third embodiment, the lubricating oil contained in the discharged refrigerant is separated in the first chamber 162 forming a part of the discharge passage 144, and the separated lubricating oil is passed through the oil return passage 147 to the suction chamber. It is returned to 141. Therefore, it is possible to effectively prevent the lubricating oil from being discharged from the variable displacement compressor to the refrigerant circuit of the air conditioner system. Further, the first chamber 162 and the second chamber 170 communicate with each other via the inner space 240a of the tubular member 240 attached to the intervening member IM, and the tubular member 240 projects into the first chamber 162. Therefore, the lubricating oil separated in the first chamber 162 is further suppressed from flowing out to the second chamber 170.

As shown in FIG. 12, the partition member 161 may have a cylindrical portion 161a extending toward the intervening member IM. The cylindrical portion 161a accommodates a protruding portion of the tubular member 240 into the first chamber 162, and its tip surface is in contact with the intervening member IM (here, the suction valve forming plate 150). The inside of the first chamber 162 by the cylindrical portion 161a includes a first space S1 communicating with the second chamber 170 via the inner space 240a of the tubular member 240, and an annular second space S2 surrounding the first space S1. It is partitioned into. The upper side of the second space S2 communicates with the discharge chamber 142 through one or more first communication grooves 202 and one or more first communication holes 201, and the lower side of the second space S2 communicates with the second communication groove 251 and. It communicates with the suction chamber 141 via an oil return passage 147 including a third through hole 252. Further, on the side surface near the tip of the cylindrical portion 161a, a plurality of openings 161b communicating the first space S1 and the second space S2 are provided at intervals in the circumferential direction.

In this way, the discharged refrigerant flows from the discharge chamber 142 into the second space S2 through the first communication hole 201 and the first communication groove 202, and the discharged refrigerant flowing into the second space S2 is the partition member 161. It also collides and / or contacts the outer peripheral surface of the cylindrical portion 161a. Therefore, the separation of the lubricating oil from the discharged refrigerant in the first chamber 162 is promoted. That is, the cylindrical portion 161a of the partition member 161 has an oil separation promoting function. In addition, most of the lubricating oil separated from the discharged refrigerant moves downward along the outer peripheral surface of the cylindrical portion 161a, and the discharged refrigerant after the lubricating oil is separated is the opening 161b formed in the cylindrical portion 161a. After flowing into the first space S1 via the above, the oil flows out to the high pressure side of the refrigerant circuit of the air conditioner system through the inner space 240a of the tubular member 240, the second chamber 170, and the communication passage 204. Therefore, it is possible to more effectively prevent the lubricating oil from being discharged from the variable displacement compressor to the refrigerant circuit of the air conditioner system. The cylindrical portion 161a also has a function of reducing the pulsation of the discharge pressure.

Further, although not shown, the lower space (or the lower side of the second space S2) in the first chamber 162 and the crank chamber 140 are communicated with each other via the control valve 300 to form the supply passage 145. You may. In this way, when the control valve 300 opens the supply passage 145, the lubricating oil separated from the discharge refrigerant in the first chamber 162 and moved downward can be supplied to the crank chamber 140 together with the refrigerant in the discharge chamber 142 (return). Can be). That is, in this case, the supply passage 145 also functions as an oil return passage.

Of the modified examples of the first embodiment, those applicable to the third embodiment can also be modified examples of the third embodiment.

[Fourth Embodiment]
Next, a fourth embodiment of the variable displacement compressor will be described. FIG. 13 is a cross-sectional view of a main part of the fourth embodiment of the variable displacement compressor. The main difference between the first embodiment and the fourth embodiment is that in the first embodiment, the retainer forming plate 152 and the head gasket are integrally formed, whereas in the fourth embodiment, the retainer forming plate is formed integrally. The 152 and the head gasket are formed separately. In this case, the retainer forming plate 152 needs to be integrated with another intervening member IM by a fastening member or the like. Further, since the retainer forming plate 152 is arranged from the second chamber 170 to the discharge chamber 142, it is necessary to partition the discharge chamber 142 and the second chamber 170 after the retainer forming plate 152 is arranged.

In the present embodiment, as shown in FIG. 13, the retainer forming plate 152 is a fastening member 261 (here, mainly bolts 261a and nuts 261b) located at the radial center of the first chamber 162 and the second chamber 170. ), In particular, the suction valve forming plate 150, the valve plate 103, and the discharge valve forming plate 151 are integrated with the other intervening member IM.

Further, a fitting hole 262 that is concentric with the second chamber 170 and has a diameter larger than that of the second chamber 170 is formed on the end surface of the cylinder head 104 on the cylinder block 101 side. In other words, the fitting hole 262 and the second chamber 170 are formed as one stepped bottom hole that opens on the end surface of the cylinder head 104 on the cylinder block 101 side. A cylindrical ring body 263 is press-fitted into the fitting hole 262, and one end surface of the ring body 263 protruding from the fitting hole 262 hits the flat surface 152b at the center of the retainer forming plate 152 in the radial direction. The discharge chamber 142 and the second chamber 170 are separated by contact with each other. That is, in the present embodiment, the ring body 263, which is separate from the cylinder head 104, corresponds to the "annular forming wall" of the present invention.

In this case, the ring body 263 is temporarily press-fitted into the fitting hole 262 so that one end face of the ring body 263 sufficiently protrudes from the end face of the cylinder head 104 on the cylinder block 101 side, and the cylinder block 101 and the cylinder head When the 104 and the like are fastened by the through bolt 105 (see FIG. 1), the retainer forming plate 152 presses the one end face, whereby the final press-fitting position of the ring body 263 with respect to the fitting hole 262 is determined. It is preferable that the cylinder is assembled in such a manner. In this way, the discharge chamber 142 and the second chamber 170 can be reliably partitioned without creating a gap between the retainer forming plate 152 and the one end surface of the ring body 263.

Further, the first chamber 162 and the second chamber 170 communicate with each other through one or more fourth through holes 264 penetrating the intervening member IM on the radial outer side of the bolt 261a. Therefore, in the present embodiment, one or more fourth through holes 264 correspond to the "second communication portion" of the present invention and form a part of the discharge passage 144. However, the present invention is not limited to this, and the first chamber 162 and the second chamber 170 may communicate with each other through a bolt through hole (not shown) that penetrates the bolt 261a in the axial direction.

The same effect as that of the first embodiment can be obtained by the fourth embodiment. Further, among the modified examples of the first embodiment, those applicable to the fourth embodiment can also be modified examples of the fourth embodiment. For example, as shown in FIG. 14, the discharge check valve 230 may be arranged in the second chamber 170 also in the fourth embodiment.

In this case, the discharge check valve 230 may be arranged in the second chamber 170 using a dedicated check valve housing 265. For example, the check valve housing 265 is formed in a stepped cylindrical shape with a stepwise reduction in diameter, and has a large diameter portion 265a, a medium diameter portion 265b, and a small diameter portion 265c. A discharge check valve 230 is attached to the outer peripheral surface of the small diameter portion 265c of the check valve housing 265. A mounting hole 266 that is concentric with the second chamber 170 and has a diameter larger than that of the second chamber 170 is formed on the end surface of the cylinder head 104 on the cylinder block 101 side. Then, the discharge check valve 230 is arranged in the second chamber 170, and the large diameter of the check valve housing 265 is in a state where the end surface of the check valve housing 265 on the large diameter portion 265a side is in contact with the retainer forming plate 152. The portion 265a is mounted in the mounting hole 266. Here, an O-ring 267 is mounted on the outer peripheral surface of the medium-diameter portion 265b of the check valve housing 265, and the O-ring 267 is between the outer peripheral surface of the medium-diameter portion 265b and the inner peripheral surface of the mounting hole 266. The check valve housing 265 is held by being crushed.

As a result, the discharge check valve 230 is arranged in the second chamber 170, and the discharge chamber 142 and the second chamber 170 are partitioned. When the discharge check valve 230 is closed, a force acts on the check valve housing 265 in the direction of being removed from the mounting hole 266, but the force is received by the retainer forming plate 152, so that the reverse is reversed. A check valve member or the like for the check valve housing 265 is not required. As with the ring body 263, the large diameter portion 265a of the check valve housing 265 may be press-fitted into the mounting hole 266.

Although the embodiments of the present invention and modified examples thereof have been described above, the present invention is not limited to the above-described embodiments and modified examples thereof, and further modifications and modifications are made based on the technical idea of the present invention. Of course it is possible.

Although the compressor of each of the above-described embodiments is a swash plate type clutchless variable capacitance compressor, it may be a variable capacitance compressor equipped with an electromagnetic clutch. Further, the present invention can be widely applied to various reciprocating compressors such as a swing plate type variable displacement compressor and a fixed capacitance compression.

100 ... Variable capacity compressor (reciprocating compressor), 101 ... Cylinder block, 101a ... Cylinder bore, 101b ... Center bore, 102 ... Front housing (housing member), 103 ... Valve plate (intervening member), 104 ... Cylinder head , 104a ... annular forming wall, 110 ... drive shaft, 111 ... check plate, 136 ... piston, 140 ... crank chamber, 141 ... suction chamber, 142 ... discharge chamber, 143 ... suction passage, 144 ... discharge passage, 145 ... supply Passage, 146 ... Discharge passage, 147 ... Oil return passage, 150 ... Suction valve forming plate (intervening member), 151 ... Discharge valve forming plate, 152 ... Retainer forming plate, 152b ... Flat surface of retainer forming plate, 161 ... Partition member , 162 ... 1st chamber, 170 ... 2nd chamber, 201, 201'... 1st communication hole (1st communication part), 202 ... 1st communication groove (1st communication part), 203 ... 2nd communication hole (1st communication part) 2 communication part), 204 ... communication passage, 230 ... discharge check valve, 240 ... tubular member, 240a ... inner space (second communication part), 300 ... control valve

Claims (8)

A cylinder block with a plurality of cylinder bores arranged in an annular shape,
A front housing provided on one side of the cylinder block and forming a crank chamber in cooperation with the cylinder block.
A cylinder head provided on the other side of the cylinder block via an intervening member, and a suction chamber is formed in a region on the outer side in the radial direction and a discharge chamber is formed on the inner side in the radial direction of the suction chamber.
A plurality of pistons housed in the plurality of cylinder bores so as to be reciprocating,
A drive shaft extending through the crank chamber and
A conversion mechanism that converts the rotation of the drive shaft into the reciprocating motion of the plurality of pistons, and the conversion mechanism including a swash plate mounted on the drive shaft.
Including
The refrigerant that has flowed into the suction chamber from the low pressure side of the external refrigerant circuit through the suction passage is sucked into the corresponding cylinder bore by the reciprocating motion of each piston, compressed and discharged to the discharge chamber, and then discharged to the discharge chamber. A reciprocating compressor configured so that the refrigerant flows out to the high pressure side of the external refrigerant circuit through the discharge passage.
The discharge passage
A first chamber provided inside the plurality of cylinder bores in the cylinder block in the radial direction, and
A second chamber provided inside the discharge chamber in the cylinder head in the radial direction and facing the first chamber with the intervening member interposed therebetween.
A first communication portion that penetrates the intervening member on the radial outer side of the second chamber and communicates the discharge chamber and the first chamber.
A second communication portion that penetrates the intervening member in the second chamber and communicates the first chamber and the second chamber.
An outlet passage connecting the second chamber and the high-pressure side of the external refrigerant circuit,
Including reciprocating compressor. The second chamber is defined by claim 1, wherein the tip surface of the annular forming wall forming the second chamber is in contact with the end surface of the intervening member on the cylinder head side to be partitioned from the discharge chamber. Reciprocating compressor. The intervening member
A valve plate having a plurality of suction holes for communicating the plurality of cylinder bores and the discharge chamber, and a plurality of discharge holes for communicating the plurality of cylinder bores and the suction chamber.
A suction valve forming plate on which a plurality of suction valves that open and close the corresponding suction holes are formed,
A discharge valve forming plate in which a plurality of discharge valves for opening and closing the corresponding discharge holes are formed, and
A retainer forming plate on which a plurality of retainers are formed, each of which regulates the maximum opening degree of the discharge valve corresponding to the discharge valve.
Including
The reciprocating compressor according to claim 2, wherein the tip surface of the annular forming wall is in contact with a flat surface at the central portion in the radial direction of the retainer forming plate. The first communication portion penetrates the valve plate and the suction valve forming plate between the adjacent discharge valves.
The reciprocating compressor according to claim 3. The intervening member is provided with a plurality of through holes that are arranged in an annular shape and that penetrate the valve plate and the suction valve forming plate between the discharge valves that are adjacent to each other.
At least one of the plurality of through holes constitutes the first communication portion.
The reciprocating compressor according to claim 4. The cylinder block has a center bore that penetrates from one end face of the cylinder block to the other end face and a part of the drive shaft is inserted into the one side of the plurality of cylinder bores in the radial direction. Have and
The center bore includes a first bore that opens to the other end face of the cylinder block and a second bore that is adjacent to the first bore and has a smaller diameter than the first bore.
The inside of the first bore is partitioned from the other interior of the center bore by a partition member attached to the first bore so as to abut the annular step surface between the first bore and the second bore. And
The inside of the first bore constitutes the first chamber.
The reciprocating compressor according to any one of claims 1 to 5. The first chamber constitutes an expansion space whose diameter is expanded with respect to the first communication portion, and the second chamber constitutes an expansion space whose diameter is expanded with respect to the second communication portion. The reciprocating compressor according to any one of 1 to 6. The second chamber according to any one of claims 1 to 7, wherein a discharge check valve for preventing the refrigerant from flowing from the second chamber side to the first chamber side is arranged in the second chamber. Reciprocating compressor.