JP6747813B2 - Compressor - Google Patents

Description

The present invention relates to a compressor that compresses and discharges a fluid such as a refrigerant, and particularly relates to a compressor that can reduce pressure pulsation of the fluid.

An example of this type of compressor is described in Patent Document 1. In the compressor described in Patent Document 1, an expansion type discharge muffler is provided on the discharge passage of the refrigerant gas, and a check valve is provided on the discharge passage on the upstream side of the discharge muffler.

JP, 11-315785, A

However, the expansion type discharge muffler generally requires an expansion space having a relatively large volume. Therefore, the compressor described in Patent Document 1 is inevitably large in size as a whole, and there is a possibility that the compressor cannot be installed in the installation space especially when the installation space is limited.

Therefore, it is an object of the present invention to provide a compressor capable of reducing pressure pulsation of fluid while suppressing an increase in size.

According to one aspect of the present invention, a compressor that compresses and discharges a fluid includes a valve accommodating chamber that constitutes a part of a discharge passage that guides the compressed fluid to the outside, and an opening end that opens to the valve accommodating chamber. And a check valve that is housed in the valve housing chamber and that prevents the reverse flow of the fluid in the discharge passage. The check valve cooperates with the valve accommodating chamber to form a passage portion having a passage area smaller than an opening area of the opening end of the cavity chamber, and the formed passage portion discharges the cavity chamber. The passage portion is formed to communicate with a passage, and the passage portion is formed between a portion on the outer surface of the check valve on the cavity chamber side and a corresponding portion on the inner wall surface of the valve accommodating chamber facing the portion . ..

In the compressor, the hollow chamber constitutes a Helmholtz resonator having the passage portion as an opening. Therefore, the pressure pulsation of the fluid in the discharge passage (discharge pulsation) is reduced. Further, since the volume of the cavity chamber can be smaller than that of the expansion type discharge muffler, it is possible to suppress the increase in size of the compressor as a whole.

It is a sectional view showing an internal structure of a compressor concerning a 1st embodiment of the present invention. It is a principal part figure which shows the structure of the valve storage chamber and cavity which were formed in the cylinder head of the said compressor. It is a partial cross section figure which shows the structure of the check valve accommodated in the said valve accommodating chamber. It is a principal part figure showing the state where the above-mentioned check valve was stored in the above-mentioned valve storage room. It is a principal part sectional drawing of the compressor which concerns on 2nd Embodiment of this invention. It is a principal part sectional drawing of the compressor which concerns on 3rd Embodiment of this invention. It is explanatory drawing for demonstrating the other state by which the said check valve was accommodated in the said valve accommodating chamber.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. The compressor according to the embodiment is configured as a clutchless variable displacement compressor, is used in, for example, an air conditioner (air conditioner system) mounted on a vehicle, and is a refrigerant (refrigerant) flowing through a refrigerant pipe (not shown) of the air conditioner system. Gas) is compressed and discharged. However, the present invention is not limited to this, and the compressor can also compress and discharge a fluid other than the refrigerant.

[First Embodiment]
FIG. 1 is a sectional view showing the internal structure of a compressor 100 according to the first embodiment of the present invention. The compressor 100 is formed to have a substantially columnar appearance. The state shown in FIG. 1 is the installed state of the compressor 100, and the arrow A indicates the vertical direction (vertical direction) and the arrow B indicates the front-back direction (horizontal direction).

As shown in FIG. 1, a compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101a, and a front housing 102 arranged on one end side (front side) in the horizontal direction (front-rear direction) of the cylinder block 101. And a cylinder head 104 arranged on the other end side (rear side) of the cylinder block 101 in the horizontal direction (front-back direction) with the valve plate 103 interposed therebetween. Then, the cylinder block 101, the front housing 102, the valve plate 103, and the cylinder head 104 are fastened with a plurality of through bolts 105 to form a housing of the compressor 100 (hereinafter referred to as a “compressor housing”). Here, although not shown, gaskets are respectively provided between the front housing 102 and the cylinder block 101, between the cylinder block 101 and the valve plate 103, and between the valve plate 103 and the cylinder head 104. It is arranged. Further, in the present embodiment, the cylinder block 101, the front housing 102, and the cylinder head 104 are manufactured by casting, although not particularly limited thereto.

The compressor 100 has a crank chamber 140 formed by the cylinder block 101 and the front housing 102, and a drive shaft 110 that penetrates the crank chamber 140 and extends in the horizontal direction (front-rear direction).

In the crank chamber 140, a swash plate 111 and a rotor 112 are attached to the drive shaft 110 at intervals. The swash plate 111 has a variable inclination angle (inclination angle) with respect to the axis of the drive shaft 110, and the rotor 112 is fixed to the drive shaft 110. The swash plate 111 is connected to the rotor 112 via the link mechanism 120 and is configured to rotate together with the drive shaft 110 and the rotor 112.

The link mechanism 120 includes a first arm 112a protruding from the rotor 112, a second arm 111a protruding from the swash plate 111, and one end of which is rotated with respect to the first arm 112a via the first connecting pin 121. The link arm 123 is movably connected and has the other end rotatably connected to the second arm 111a via the second connecting pin 122.

The swash plate 111 has a through hole 111b into which the drive shaft 110 is inserted. The through hole 111b is formed so that the swash plate 111 can change its tilt angle within a range between the maximum tilt angle and the minimum tilt angle. In the present embodiment, the through hole 111b is provided with a minimum tilt angle restricting portion that restricts the minimum tilt angle of the swash plate 111 by coming into contact with the drive shaft 110. The minimum tilt angle restricting portion is formed so that the tilt angle of the swash plate 111 can be changed to approximately 0° when the tilt angle of the swash plate 111 when the swash plate 111 is orthogonal to the axis of the drive shaft 110 is 0°. ing. On the other hand, the maximum inclination angle of the swash plate 111 is regulated when a predetermined portion of the swash plate 111 contacts the rotor 112.

Further, on the drive shaft 110, an inclination reducing spring 114 for urging the swash plate 111 toward the minimum inclination angle and an inclination increasing spring 115 for urging the swash plate 111 in a direction to increase the inclination angle of the swash plate 111. It is installed by sandwiching it. Specifically, the tilt angle decreasing spring 114 is arranged between the rotor 112 and the swash plate 111, and the tilt angle increasing spring 115 is arranged between the swash plate 111 and the spring support member 116 provided on the drive shaft 110. Has been done. Here, at the minimum tilt angle, the biasing force of the tilt angle increasing spring 115 is set to be larger than the biasing force of the tilt angle reducing spring 114, and when the drive shaft 110 is not rotating, the swash plate 111 causes the tilt angle reducing spring 114 to rotate. Is maintained at an inclination angle (>the minimum inclination angle) that balances the urging force of the inclination angle increasing spring 115 with the urging force of the inclination increasing spring 115.

One end (front end) of the drive shaft 110 extends through the boss portion 102a of the front housing 102 to the outside of the front housing 102 and is connected to a power transmission device (not shown). Further, a gap between the drive shaft 110 and the shaft hole of the boss portion 102a through which the drive shaft 110 penetrates is sealed by a shaft sealing device 130, whereby the inside of the crank chamber 140 is shut off from the outside.

The coupling body between the drive shaft 110 and the rotor 112 is supported by bearings 131 and 132 in the radial direction, and is supported by bearings 133 and a thrust plate 134 in the thrust direction. The gap between the contact portion of the drive shaft 110 with the thrust plate 134 and the thrust plate 134 is adjusted to a predetermined gap by the adjusting screw 135. Then, power from an external drive source (for example, the engine of the vehicle) is transmitted to the drive shaft 110 via the power transmission device, whereby the drive shaft 110 is rotated.

In the cylinder block 101, a plurality of cylinder bores 101a are annularly arranged so as to surround the drive shaft 110, and a piston 136 is slidably arranged in each cylinder bore 101a. Each piston 136 has a protrusion 136a that protrudes into the crank chamber 140, and the outer peripheral edge of the swash plate 111 is housed in the inner space of the protrusion 136a. The swash plate 111 and the piston 136 are configured to interlock with each other via a pair of shoes 137. For example, when the swash plate 111 rotates in accordance with the rotation of the drive shaft 110 (and the rotor 112), the rotation of the swash plate 111 is converted into the reciprocating motion of the piston 136 by the pair of shoes 137, so that the piston 136 moves inside the cylinder bore 101a. It is designed to reciprocate.

A discharge chamber forming portion 141a and a suction chamber forming portion 142a are formed in a recess on the end surface of the cylinder head 104 on the valve plate 103 side. The discharge chamber forming portion 141a is formed in a substantially central portion of the end surface of the cylinder head 104 on the valve plate 103 side, and forms the discharge chamber 141 together with the valve plate 103. The compressed refrigerant is discharged into the discharge chamber 141. The suction chamber forming portion 142a is formed so as to surround the discharge chamber forming portion 141a in a ring shape, and forms the suction chamber 142 together with the valve plate 103. The refrigerant before compression is sucked into the suction chamber 142. That is, in the compressor 100 according to the present embodiment, the discharge chamber 141 is provided substantially at the center in the cross section (here, the cross section cut along the vertical plane) orthogonal to the drive shaft 110 (in other words, the extension of the drive shaft 110). A suction chamber 142 is provided so as to surround the discharge chamber 141.

The valve plate 103 has suction holes 103a and discharge holes 103b corresponding to the plurality of cylinder bores 101a. The suction chamber 142 is configured to communicate with each cylinder bore 101a through each suction hole 103a, and the discharge chamber 141 is configured to communicate with each cylinder bore 101a through each discharge hole 103b. Each suction hole 103a is opened and closed by a suction valve (not shown), and each discharge hole 103b is opened and closed by a discharge valve (not shown). The suction valve is, for example, a reed valve, and is configured to open the suction hole 103a when the pressure inside the cylinder bore 101a becomes lower than the pressure inside the suction chamber 142. The discharge valve is, for example, a reed valve, and is configured to open the discharge hole 103b when the pressure inside the cylinder bore 101a becomes higher than the pressure inside the discharge chamber 141. The reference numeral 160 indicates a component (retainer) that regulates the maximum opening of the discharge valve.

A suction passage (not shown) and a discharge passage 143 are formed in the cylinder head 104. The suction passage is formed so as to connect a low pressure side refrigerant pipe (not shown) of the air conditioner system to the suction chamber 142, and a discharge passage 143 is formed to communicate with a high pressure side refrigerant pipe (not shown) of the air conditioner system. It is formed so as to communicate with 141. In the present embodiment, the discharge passage 143 is composed of a valve accommodating chamber 144 that accommodates a check valve 200 (described later) and a downstream passage 145 that is downstream of the valve accommodating chamber 144. The valve accommodating chamber 144 is located on the extension line of the drive shaft 110, and the downstream passage portion 145 extends in the vertical direction when the compressor 100 is installed, and the lower end thereof is connected to the valve accommodating chamber 144. There is.

Refrigerant of the air conditioner system (refrigerant before compression) is guided from the low pressure side refrigerant pipe to the suction chamber 142 via the suction passage. In the compressor 100, each piston 136 reciprocates in the cylinder bore 101a as the drive shaft 110 rotates, and the reciprocating motion of the piston 136 sucks the refrigerant in the suction chamber 142 into the cylinder bore 101a from the suction hole 103a. Then, the compressed refrigerant (compressed refrigerant) is discharged into the discharge chamber 141 from the discharge hole 103b. The compressed refrigerant discharged into the discharge chamber 141 is guided to the high pressure side refrigerant pipe through the discharge passage 143. Here, in the present embodiment, the check valve 200 accommodated in the valve accommodating chamber 144 causes the reverse flow of the refrigerant in the discharge passage 143, that is, the refrigerant flows from the high pressure side refrigerant pipe side toward the discharge chamber 141. Are prevented. The configuration of the valve accommodating chamber 144 forming a part of the discharge passage 143 and the check valve 200 accommodated in the valve accommodating chamber 144 will be described later.

Further, in the present embodiment, the cylinder head 104 has a cavity chamber 146 formed adjacent to the valve accommodating chamber 144. The cavity chamber 146 is located on the extension line of the drive shaft 110, like the valve accommodating chamber 144. That is, the valve accommodating chamber 144 and the cavity chamber 146 are formed side by side in the horizontal direction (front-back direction). The configuration of the cavity chamber 146 will be described later.

Further, the cylinder head 104 is provided with a control valve 300. The control valve 300 adjusts the opening amount of the pressure supply passage 147 that connects the discharge chamber 141 and the crank chamber 140 to adjust the amount of refrigerant (the compressed refrigerant) introduced from the discharge chamber 141 to the crank chamber 140. Is configured to control. Further, the refrigerant in the crank chamber 140 flows into the suction chamber 142 via a pressure release passage 148 that connects the crank chamber 140 and the suction chamber 142, and the pressure release passage 148 is provided with an orifice 148a. Has been. Therefore, the compressor 100 adjusts the opening degree of the pressure supply passage 147 by the control valve 300, so that the pressure in the crank chamber 140, or more specifically, the differential pressure between the pressure in the crank chamber 140 and the pressure in the suction chamber 142. It is possible to change the inclination angle of the swash plate 111, that is, the stroke amount of the piston 136, thereby changing the discharge capacity.

Next, with reference to FIGS. 2-4, the valve accommodating chamber 144 and the cavity chamber 146 formed in the cylinder head 104, and the check valve 200 accommodated in the valve accommodating chamber 144 will be described. FIG. 2 is a main part view showing the configuration of the valve storage chamber 144 and the cavity chamber 146, FIG. 3 is a partial cross-sectional view showing the configuration of the check valve 200, and FIG. It is a principal part figure (equivalent to the principal part enlarged view of FIG. 1) which shows the state in which the check valve 200 was accommodated.

As shown in FIG. 2, in the installed state of the compressor 100, the valve accommodating chamber 144 that constitutes a part of the discharge passage 143 has the compressed refrigerant on one side (front side) in the horizontal direction (front-rear direction). Has an inflow port 144a into which the compressed refrigerant flows from the inflow port 144a into the valve housing chamber 144, and an outflow port 144b from which the compressed refrigerant flows out. In the present embodiment, the inflow port 144a of the valve accommodating chamber 144 is open to the discharge chamber 141 (discharging chamber forming part 141a), and the outflow port 144b of the valve accommodating chamber 144 is provided at the lower end of the downstream passage part 145. It opens at the corresponding position. That is, the valve accommodating chamber 144 communicates with the discharge chamber 141 via the inflow port 144a, and communicates with the downstream passage portion 145 via the outflow port 144b.

The cavity chamber 146 is formed as a cylindrical space extending in the horizontal direction (front-back direction). One end (front side end) of the cavity chamber 146 is an opening end 146a that opens to the wall surface on the other side (rear side) in the horizontal direction (front-back direction) of the valve storage chamber 144, and the other end of the cavity chamber 146. (Rear side end) is a closed end. Specifically, the open end 146 a of the cavity chamber 146 is open at a position facing the inflow port 144 a of the valve storage chamber 144 across the indoor space of the valve storage chamber 144, and the open end 146 a of the cavity chamber 146 is opened. The opening area is smaller than the opening area of the inflow port 144a of the valve accommodating chamber 144.

In the present embodiment, the check valve 200 closes the discharge passage 143 by blocking the communication between the inflow port 144a and the outflow port 144b of the valve housing chamber 144, thereby preventing the reverse flow of the refrigerant in the discharge passage 143. Is configured to.

As shown in FIG. 3, the check valve 200 includes a first housing member 201, a second housing member 202, a valve body 203, and a compression coil spring (biasing member) 204. The first housing member 201 and the second housing member 202 form a housing of the check valve 200 (hereinafter referred to as “valve housing”). Specifically, in the present embodiment, the second housing member 202 is formed into a bottomed tubular shape, and the first housing member 201 is fitted and attached to the open end of the second housing member 202, whereby the valve body 203 Further, the valve housing having the accommodation space 205 of the compression coil spring 204 therein is formed.

An inlet hole 201a is formed through the first housing member 201. Specifically, one end of the inlet hole 201a is opened to the end surface of the first housing member 201 on the accommodation space 205 side, and the other end of the inlet hole 201a is different from the accommodation space 205 side of the first housing member 201. It opens on the opposite end face. A valve seat 201b is formed on the end surface of the first housing member 201 on the accommodation space 205 side, with which the valve element 203 accommodated in the accommodation space 205 comes into contact with and separates from the valve seat 201b. On the other hand, a plurality of outlet holes 202a are formed in the peripheral wall of the second housing member 202, and pressure introducing holes 202b are formed in the bottom wall (closed end wall) of the second housing member 202. The accommodation space 205 inside the valve housing communicates with the outside through the inlet hole 201a, the plurality of outlet holes 202a, and the pressure introducing hole 202b.

The valve body 203 is provided slidably in the accommodation space 205. The compression coil spring 204 is disposed between the valve body 203 and the inner bottom surface of the second housing member 202, and biases the valve body 203 toward the valve seat 201b. When the valve body 203 is seated on the valve seat 201b, that is, when the end surface of the valve body 203 on the first housing member 201 side is in contact with the valve seat 201b, the inlet hole 201a and the plurality of outlet holes 201a are provided. When it is separated from the valve seat 201b by blocking the communication with 202a, that is, when the end surface of the valve body 203 on the side of the first housing member 201 is separated from the valve seat 201b, the plurality of inlet holes 201a and a plurality of inlet holes 201a are formed. It is configured to communicate with the outlet hole 202a.

As shown in FIG. 4, the check valve 200 includes the valve housing (here, the first housing member 201) with the O-ring 206 mounted on the outer peripheral surface thereof so that the first housing member 201 is disposed in the discharge chamber. It is accommodated in the valve accommodating chamber 144 so as to be positioned on the side of 141 (discharging chamber forming portion 141a), and is positioned and fixed by, for example, a retaining ring 207.

When the check valve 200 is housed in the valve accommodating chamber 144, the compressed refrigerant that has flowed from the discharge chamber 141 into the valve accommodating chamber 144 via the inflow port 144a receives the valve of the check valve 200 from the inlet hole 201a. It comes to flow into the housing, that is, the accommodation space 205. Further, in the valve accommodating chamber 144, a communication space 149 is formed around the plurality of outlet holes 202a of the check valve 200 so as to communicate with the downstream passage portion 145 via the outflow port 144b. The formed communication space 149 becomes the downstream side of the check valve 200 in the discharge passage 143 together with the downstream passage portion 145. In addition, an opening of the cavity chamber 146 is provided between a portion 208 on the cavity chamber 146 side on the outer surface (of the valve housing) of the check valve 200 and a corresponding portion 144c on the inner wall surface of the valve accommodating chamber 144 facing this. A passage portion 150 having a smaller passage area than the opening area of the opening end 146a of the cavity 146 is formed so as to surround the end 146a. Then, the cavity chamber 146 communicates with the communication space 149 (that is, the downstream side of the discharge passage 143) via the formed passage portion 150. That is, when the check valve 200 is accommodated in the valve accommodating chamber 144, the check valve 200 cooperates with the valve accommodating chamber 144 to form the passage portion 150, and the cavity chamber 146 to the discharge passage 143 via the formed passage portion 150. It is configured to communicate.

Here, in the present embodiment, the corresponding portion 144c on the inner wall surface of the valve accommodating chamber 144 is subjected to machining such as cutting so that the passage portion 150 having a desired passage area is formed. That is, although the cylinder head 104 is manufactured by casting, the corresponding portion 144c on the inner wall surface of the valve housing chamber 144 is formed as a machined surface (for example, a cut surface).

As described above, in the present embodiment, the inflow port 144a of the valve accommodating chamber 144 is open to the discharge chamber forming portion 141a that is recessed in the end surface of the cylinder head 104 on the valve plate 103 side. The opening end 146a of the cavity chamber 146 is opened at a position facing the inflow port 144a of the valve accommodation chamber 144 with the indoor space of the valve accommodation chamber 144 interposed therebetween, and the opening area of the opening end 146a of the cavity chamber 146 is It is smaller than the opening area of the inflow port 144a of the valve accommodating chamber 144. When the inside of the valve accommodating chamber 144 is viewed from the discharge chamber forming portion 141a side through the inflow port 144a, the corresponding portion 144c on the inner wall surface of the valve accommodating chamber 144 comes to be located inside the inflow port 144a. There is. Therefore, in the cylinder head 104, for example, a tool or the like is introduced from the discharge chamber forming portion 141a side into the valve housing chamber 144 via the inflow port 144a, and the corresponding portion 144c on the inner wall surface of the valve housing chamber 144 is machined. Can be applied.

In the check valve 200, the valve body 203 is biased toward the valve seat 201b by the compression coil spring 204 as described above. The pressure on the upstream side of the check valve 200 in the discharge passage 143 acts on the end surface of the valve body 203 on the first housing member 201 side via the inlet hole 201a, and the valve body 203 on the first housing member 201 side. The pressure on the downstream side of the check valve 200 in the discharge passage 143 acts on the end surface on the opposite side to the passage surface 150 and the pressure introduction hole 202b. Therefore, the valve body 203 moves in the accommodation space 205 according to the pressure difference between the upstream pressure and the downstream pressure of the discharge passage 143. When the differential pressure is less than or equal to a predetermined value, the one end surface of the valve body 203 contacts the valve seat 201b by the urging force of the compression coil spring 204, and the valve body 203 has the inlet hole 201a and the plurality of outlet holes 202a. Cut off communication with. Thereby, the communication between the inflow port 144a and the outflow port 144b of the valve accommodating chamber 144 is also blocked, and the discharge passage 143 is closed. On the other hand, when the differential pressure is larger than the predetermined value, the valve body 203 moves against the biasing force of the compression coil spring 204, and the valve body 203 connects the inlet hole 201a and the plurality of outlet holes 202a. Let Accordingly, the inflow port 144a and the outflow port 144b of the valve accommodating chamber 144 also communicate with each other, and the discharge passage 143 is opened.

As described above, in the present embodiment, the compressor 100 is housed in the valve accommodating chamber 144 forming a part of the discharge passage 143, the cavity chamber 146 adjacent to the valve accommodating chamber 144, and the valve accommodating chamber 144. And a check valve 200 that prevents the reverse flow of the refrigerant in the discharge passage 143. Specifically, a valve accommodating chamber 144 and a cavity chamber 146 are formed in the cylinder head 104 that constitutes a part of the compressor housing, and the cavity chamber 146 has an open end 146a that opens into the valve accommodating chamber 144 at one end. It is formed as a cylindrical space having the other end as a closed end. When the check valve 200 is housed in the valve accommodating chamber 144, the cavity chamber 146 communicates with the discharge passage 143 via the passage portion 150 formed by the check valve 200 and the valve accommodating chamber 144. Is configured. Therefore, the cavity chamber 146 constitutes a Helmholtz resonator having the passage portion 150 as an opening (in other words, a resonance chamber of the Helmholtz resonator), and the pressure pulsation of the refrigerant in the discharge passage 143 is effective by the Helmholtz resonator. Be reduced. Further, since the volume of the cavity chamber 146 forming (the resonance chamber of) the Helmholtz resonance is smaller than that of, for example, an expansion type muffler, the overall size of the compressor 100 is suppressed from increasing.

Here, in the compressor 100, the passage portion 150 corresponds to a predetermined portion on the outer surface of the check valve 200 (the valve housing thereof) on the cavity chamber 146 side and an inner wall surface of the valve accommodating chamber 144 facing the predetermined portion. It is formed between the part 144c. Therefore, by appropriately adjusting the predetermined portion on the outer surface of the check valve 200 and/or the corresponding portion 144c on the inner wall surface of the valve housing chamber 144, the passage area of the passage portion 150, that is, the Helmholtz resonator. It is possible to change the resonance frequency. Therefore, it is relatively easy to deal with individual variations of the compressor 100. In particular, in the above-described embodiment, the corresponding portion 144c on the inner wall surface of the valve storage chamber 144 is formed as a machined surface. Therefore, while the check valve 200 and the cavity chamber 146 are left as they are, the corresponding portion 144c on the inner wall surface of the valve accommodating chamber 144 is subjected to desired machining, so that the Helmholtz resonator suitable for each compressor 100 can be obtained. Can be formed, which is convenient.

Further, in the installed state of the compressor 100, the cavity chamber 146 has an opening end 146a that opens to the wall surface on the other side (rear side) in the horizontal direction (front-rear direction) of the valve accommodating chamber 144, and the horizontal direction (front-rear direction). The passage portion 150 is formed around the open end 146 a of the cavity chamber 146. Therefore, even if oil or the like enters the cavity 146, the oil or the like is discharged from the lowermost portion of the passage portion 150 and the vicinity thereof. Thereby, the volume change of the cavity chamber 146 is suppressed, and the effect of reducing the pressure pulsation of the refrigerant in the discharge passage 143 is stably obtained.

Further, the check valve 200 opens and closes the discharge passage 143 by moving the valve body 203 according to the pressure difference between the upstream pressure and the downstream pressure in the discharge passage 143. Then, the upstream side pressure in the discharge passage 143 acts on one end surface (the end surface on the side of the first housing member 201) of the valve body 203 via the inlet hole 201a, and the other end surface of the valve body 203 (the first housing member 201). The downstream side pressure in the discharge passage 143 acts on the end surface on the side opposite to the side) via the passage portion 150 and the pressure introduction hole 202b. Therefore, the downstream pressure after the pulsation is absorbed by the Helmholtz resonator acts on the other end surface of the valve body 203, and the operation of the check valve 200 (valve body 203) is stabilized. Can be achieved.

[Second Embodiment]
FIG. 5 is a sectional view of essential parts of a compressor 500 according to the second embodiment of the present invention. Like the compressor 100 according to the first embodiment, the compressor 500 according to the second embodiment is also configured as a clutchless variable displacement compressor, and compresses and discharges a fluid such as a refrigerant. Note that, in FIG. 5, elements having the same functions as those of the compressor 100 according to the first embodiment are denoted by the same reference numerals or omitted. The main differences between the compressor 100 according to the first embodiment and the compressor 500 according to the second embodiment are as follows.

In the compressor 100 according to the first embodiment and the compressor 500 according to the second embodiment, the dispositions of the discharge chamber 141 and the suction chamber 142 are reversed. That is, in the compressor 100 according to the first embodiment, the discharge chamber 141 is provided at substantially the center of the cross section orthogonal to the drive shaft 110, and the suction chamber 142 is provided so as to surround the discharge chamber 141. On the other hand, in the compressor 500 according to the second embodiment, the suction chamber 142 is provided substantially in the center in the cross section orthogonal to the drive shaft 110, and the discharge chamber 141 is provided so as to surround the suction chamber 142. ..

Further, in the compressor 100 according to the first embodiment, the downstream passage portion 145 is formed in the cylinder head 104 together with the valve storage chamber 144. On the other hand, in the compressor 500 according to the second embodiment, the valve accommodating chamber 144 is formed in the cylinder head 104, but the downstream passage portion 145 is formed in the cylinder head 104. 145a and a cylinder block side passage portion 145b formed in the cylinder block 101.

Also in the compressor 500 according to the second embodiment, when the check valve 200 is housed in the valve accommodating chamber 144, the cavity chamber 146 is opened by the check valve 200 and the valve accommodating chamber 144. It is configured to communicate with the discharge passage constituted by the valve accommodating chamber 144 and the downstream side passage portion 145 via the passage portion 150 formed around the. Also in the compressor 500 according to the second embodiment, the same effect as that of the compressor 100 according to the first embodiment can be obtained.

[Third Embodiment]
FIG. 6 is a sectional view of essential parts of a compressor 700 according to the third embodiment of the present invention. Like the compressors 100 and 500 according to the first and second embodiments, the compressor 700 according to the third embodiment is also configured as a clutchless variable displacement compressor and compresses and discharges a fluid such as a refrigerant. Note that, in FIG. 6, elements having the same functions as those of the compressor 100 according to the first embodiment are designated by the same reference numerals or omitted. The main differences between the compressors 100, 500 according to the first and second embodiments and the compressor 700 according to the third embodiment are as follows.

In the compressors 100 and 500 according to the first and second embodiments, the compressor housing includes a cylinder block 101, a front housing 102, a valve plate 103, and a cylinder head 104. On the other hand, in the compressor 700 according to the third embodiment, the compression is performed by the cylinder block 101, the front housing 102, the valve plate 103, the cylinder head 104, and the upper addition member 701 fixedly attached to the upper portion of the cylinder block 101. A machine housing is configured.

Further, in the compressors 100 and 500 according to the first and second embodiments, the valve accommodating chamber 144 and the cavity chamber 146 are formed in the cylinder head 104. On the other hand, in the compressor 700 according to the third embodiment, the cavity chamber 146 is formed in the upper addition member 701, and the valve accommodation chamber 144 is configured such that the upper addition member 701 is attached to the upper portion of the cylinder block 101. That is, it is formed by the cylinder block 101 and the upper addition member 701. In addition, in the compressor 700 according to the third embodiment, the valve accommodating chamber 144 and the cavity chamber 146 may be formed in the upper addition member 701.

Furthermore, in the compressors 100 and 500 according to the first and second embodiments, the valve storage chamber 144 and the cavity chamber 146 are arranged side by side in the horizontal direction. The valve accommodating chamber 144 has an inflow port 144a on one side (front side) in the horizontal direction (front-rear direction) and an outflow port 144b on the upper side. Further, the cavity chamber 146 is formed as a columnar space extending in the horizontal direction (front-rear direction), and the opening end 146 a of the cavity chamber 146 has the other side (rear side) of the valve accommodating chamber 144 in the horizontal direction (front-rear direction). There is an opening on the wall of. On the other hand, in the compressor 700 according to the third embodiment, the valve storage chamber 144 and the cavity chamber 146 are arranged side by side in the vertical direction. Further, the valve accommodating chamber 144 has an inflow port 144a in the lower part which is one side in the vertical direction and an outflow port 144b in the side part (front side). The cavity chamber 146 is formed as a columnar space extending in the up-down direction, and the opening end 146a of the cavity chamber 146 is open to the wall surface of the valve accommodating chamber 144 on the other side in the up-down direction.

Also in the compressor 700 according to the third embodiment, when the check valve 200 is housed in the valve housing chamber 144, the cavity chamber 146 is opened by the check valve 200 and the valve housing chamber 144. It is configured to communicate with the discharge passage 143 via the passage portion 150 formed around the. Also in the compressor 700 according to the third embodiment, the same effects as those of the compressors 100 and 500 according to the first and second embodiments can be obtained. In particular, in the compressor 700 according to the third embodiment, the cavity chamber 146 has an open end 146a that opens to the upper wall surface of the valve accommodating chamber 144 and is formed as a columnar space extending in the vertical direction. Therefore, oil or the like rarely enters the cavity chamber 146, and even if oil or the like intrudes into the cavity chamber 146, it is easily discharged from the passage portion 150 formed around the opening end 146a of the cavity chamber 146. obtain. Therefore, the volume change of the cavity chamber 146 is further suppressed, and the effect of reducing the pressure pulsation of the refrigerant in the discharge passage 143 is stably obtained.

In addition, in each of the above-described embodiments, the corresponding portion 144c on the inner wall surface of the valve storage chamber 144 is formed as a machined surface (for example, a cut surface). However, it is not limited to this. The corresponding portion 144c on the inner wall surface of the valve accommodating chamber 144 may remain in the state at the time of manufacturing the cylinder head 104, that is, the casting surface.

Further, in each of the above-described embodiments, the cavity chamber 146 is formed as a space having a smaller cross-sectional area than the valve accommodating chamber 144, and the opening end 146 a of the cavity chamber 146 is open to the wall surface of the valve accommodating chamber 144. In other words, the valve accommodating chamber 144 and the cavity chamber 146 are clearly defined. Specifically, in the first embodiment (FIG. 1) and the second embodiment (FIG. 5), the cross-sectional area of the cavity chamber 146 cut along the vertical plane is the valve accommodation chamber 144 (or the cavity thereof cut along the vertical plane). The cross-sectional area of the cavity 146 is smaller than the cross-sectional area of the space on the chamber 146 side), and in the third embodiment (FIG. 6), the cross-sectional area of the cavity chamber 146 cut along the horizontal plane is smaller than the cross-sectional area of the valve accommodating chamber 144 cut along the horizontal plane. There is. However, it is not limited to this. The cross-sectional area of the hollow chamber 146 and the cross-sectional area of the valve accommodating chamber 144 (or the space on the side of the hollow chamber 146) may be the same. In this case, the valve accommodating chamber 144 and the cavity chamber 146 are integrated, but the space accommodating the entire check valve 200 is the valve accommodating chamber 144, and the remaining space is the cavity chamber 146. For example, as schematically shown in FIGS. 7A and 7B, a space that accommodates the entire check valve 200 and is located on the left side of the broken line in the drawing is the valve storage chamber 144, which is larger than the broken line. The space on the right side can be the cavity 146.

Although the embodiment of the present invention and the modified example thereof have been described above, the present invention is not limited to the above-described embodiment and the modified example, and further modifications and changes can be made based on the technical idea of the present invention. Is.

100, 500, 700... Compressor 101... Cylinder block (housing member)
104... Cylinder head (housing member)
141... Discharge chamber 143... Discharge passage 144... Valve accommodating chamber 144a... Inlet of valve accommodating chamber 144b... Outlet of valve accommodating chamber 146... Cavity chamber 146a... Open end of cavity chamber 150... Passage 200... Check valve 201 ...First housing member (valve housing)
201a... Inlet hole 202... Second housing member (valve housing)
202a... Outlet hole 202b... Pressure introducing hole 203... Valve body 204... Compression coil spring (biasing member)

Claims (9)

A compressor that compresses and discharges fluid,
A valve accommodating chamber forming a part of the discharge passage for guiding the compressed fluid to the outside,
A cavity chamber having an open end opening to the valve storage chamber,
A check valve that is housed in the valve housing chamber to prevent a backflow of fluid in the discharge passage,
Including,
The check valve cooperates with the valve accommodating chamber to form a passage portion having a passage area smaller than an opening area of the opening end of the cavity chamber, and the formed passage portion causes the cavity chamber to serve as the discharge passage. Configured to communicate ,
The passage portion is formed between a portion on the cavity chamber side on the outer surface of the check valve and a corresponding portion on the inner wall surface of the valve accommodating chamber facing the cavity portion .
Compressor. The compressor according to claim 1, wherein the valve accommodating chamber and the cavity chamber are formed in a housing member that constitutes a part of a housing of the compressor. The compressor according to claim 1 or 2 , wherein the corresponding portion on the inner wall surface of the valve accommodating chamber is formed as a machined surface. The valve accommodating chamber has an inlet for the compressed fluid on one side in the first direction, and the compressed fluid flowing from the inlet on the one side in the second direction intersecting the first direction. Has an outlet of
The open end of the cavity chamber is opened to a wall surface on the other side in the first direction of the valve storage chamber so as to face the inflow port of the valve storage chamber,
The check valve is configured to prevent the reverse flow of the fluid in the discharge passage by blocking the communication between the inflow port and the outflow port of the valve storage chamber,
The passage portion is formed so as to surround a periphery of the open end of the cavity chamber,
The compressor according to any one of claims 1-3. In the installed state of the compressor, the valve accommodating chamber has the inflow port on one side in the horizontal direction and the outflow port on the upper side, and the open end of the cavity chamber is horizontal to the valve accommodating chamber. The compressor according to claim 4 , which is open on a wall surface on the other side in the direction. The valve accommodating chamber and the cavity chamber are formed in one housing member, and a discharge chamber forming portion that forms a discharge chamber for discharging the compressed fluid is formed on one end surface of the one housing member. A recess is formed,
The inflow port of the valve accommodating chamber is open to the discharge chamber forming portion,
When the valve accommodating chamber is viewed from the discharge chamber forming portion side through the inflow port of the valve accommodating chamber, the corresponding portion on the inner wall surface of the valve accommodating chamber is inside the inflow port of the valve accommodating chamber. Is located in the
The compressor according to claim 5 . In the installed state of the compressor, the valve accommodating chamber has the inflow port at the lower part in the vertical direction and the outflow port at the side part, and the opening end of the cavity chamber is at the upper part of the valve accommodating chamber. The compressor according to claim 4 , which has an opening on a wall surface of the compressor. The check valve is
A valve housing in which an inlet hole into which the compressed fluid flows in, an outlet hole into which the compressed fluid flowing from the inlet hole flows out, and a pressure introducing hole are formed,
A valve element housed in the valve housing, in which one end face is subjected to upstream pressure of the discharge passage through the inlet hole and the other end face is subjected to downstream pressure of the discharge passage through the pressure introduction hole. When,
A biasing member that is housed in the valve housing and biases the valve body in a direction that blocks communication between the inlet hole and the outlet hole;
Including,
When the differential pressure between the upstream side pressure and the downstream side pressure acting on the valve body becomes equal to or less than a predetermined value, the valve body blocks the communication between the inlet hole and the outlet hole to block the discharge passage. , Thereby preventing the reverse flow of the fluid in the discharge passage,
The compressor according to any one of claims 1-7. In the check valve,
The pressure introducing hole communicates with a downstream side of the discharge passage via the passage portion,
The other end surface of the valve body is configured such that the downstream pressure of the discharge passage acts through the passage portion and the pressure introduction hole.
The compressor according to claim 8 .