Compressor

Abstract

To provide a compressor for compressing refrigerant while suppressing the sticking of a discharge valve to a valve retainer.SOLUTION: A swash plate compressor includes: a suction chamber into which refrigerant is sucked; a compression mechanism for compressing the refrigerant in the section chamber; a discharge chamber from which the refrigerant compressed by the compression mechanism is discharged; a reed valve-type discharge valve arranged on the exit side of a discharge hole which communicates the compression mechanism and the discharge chamber; a valve retainer 75 for, when the discharge valve is opened, restricting the opening degree thereof with the discharge valve abutting thereon; and a rubber 77 with which the surface of the valve retainer 75 is coated. A plurality of positions on the rubber 77 with which the valve retainer 75 is coated are peeled to form a peeled part 75B, so that the abutment surface of the rubber 77 which abuts on the discharge valve and with which the valve retainer 75 is coated is formed as a rough surface.SELECTED DRAWING: Figure 8

Description

[Technical Field]

[0001] The present invention relates to a compressor that compresses a refrigerant. [Background technology]

[0002] As described in JP-A-2005-508480 (Patent Document 1), a compressor that compresses a refrigerant has a reed valve-type discharge valve that opens and closes a discharge hole of a compression mechanism, and a valve retainer that limits the opening (deflection) of the discharge valve. When the discharge valve opens, the valve retainer abuts against the entire surface of the discharge valve to limit its opening, improving, for example, the closing characteristics of the discharge valve when it changes from an open state to a closed state. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Special Publication No. 2005-508480 Summary of the Invention [Problem to be solved by the invention]

[0004] However, in conventional compressors, the valve retainer covers the entire surface of the discharge valve, limiting its opening. This can cause the discharge valve to stick to the valve retainer for some reason, resulting in a delay in changing from an open state to a closed state. If a delay occurs in changing from an open state to a closed state, for example, refrigerant may flow back from the discharge chamber to the compression mechanism, potentially resulting in a decrease in performance due to re-expansion in the compression mechanism. Furthermore, because the discharge valve closes after the pressure difference between the discharge hole and the discharge chamber of the compression mechanism becomes small, for example, the discharge valve closes faster, which can increase the impact energy when it hits the valve seat, potentially leading to wear on the valve seat.

[0005] SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a compressor that prevents the discharge valve from sticking to the valve retainer. [Means for solving the problem]

[0006] The compressor has a suction chamber into which refrigerant is drawn, a compression mechanism that compresses the refrigerant in the suction chamber, a discharge chamber from which the refrigerant compressed by the compression mechanism is discharged, a reed valve-type discharge valve located on the outlet side of a discharge hole that connects the compression mechanism and the discharge chamber, a valve retainer against which the discharge valve abuts to limit the opening of the discharge valve when the discharge valve opens, and a rubber coating on the surface of the valve retainer.The rubber coating on the valve retainer that abuts against the discharge valve is formed into a rough surface. [Effects of the Invention]

[0007] According to the present invention, in a compressor that compresses a refrigerant, it is possible to suppress sticking of a discharge valve to a valve retainer. [Brief explanation of the drawings]

[0008] [Figure 1] FIG. 1 is a vertical cross-sectional view showing an example of a swash plate compressor. [Figure 2] FIG. 2 is a perspective view showing an example of a valve retainer in the first embodiment. [Figure 3] 1 is a perspective view showing a main part of an example of a valve retainer in a first embodiment. FIG. [Figure 4] FIG. 3 is a plan view showing an example of a contact surface of a valve retainer in the first embodiment. [Figure 5] FIG. 4 is a perspective view showing another example of the valve retainer in the first embodiment. [Figure 6] FIG. 10 is a perspective view showing an example of a valve retainer in a second embodiment. [Figure 7] FIG. 10 is a perspective view showing another example of the valve retainer in the second embodiment. [Figure 8] FIG. 11 is a perspective view showing an example of a valve retainer in a third embodiment. [Figure 9] FIG. 11 is a perspective view showing a first modified example of the valve retainer in the third embodiment. [Figure 10] FIG. 11 is a cross-sectional view of a main part showing a first modified example of the valve retainer in the third embodiment. [Figure 11] FIG. 11 is a perspective view showing a second modified example of the valve retainer in the third embodiment. [Figure 12] FIG. 11 is a cross-sectional view of a main part showing a second modified example of the valve retainer in the third embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. 1 shows an example of a swash plate compressor 1, which is an example of a compressor to which the present embodiment can be applied. The swash plate compressor 1 is incorporated, for example, in a refrigerant circulation circuit of an air conditioning system of a vehicle (not shown), and draws in and compresses refrigerant from the low-pressure side of the refrigerant circulation circuit, and discharges the compressed refrigerant to the high-pressure side of the refrigerant circulation circuit.

[0010] The swash plate compressor 1 has a cylinder block 3 in which a plurality of cylinder bores 3A are formed, a front housing 5 joined to one axial end of the cylinder block 3, and a cylinder head 9 joined to the other axial end of the cylinder block 3 via a valve plate 7.

[0011] The cylinder block 3 and the front housing 5 form a crank chamber 11, through which a drive shaft 13 is disposed in the axial direction. A disc-shaped swash plate 15 is disposed within the crank chamber 11. A through-hole 15A is formed in the center of the swash plate 15, and the drive shaft 13 passes through the through-hole 15A. The swash plate 15 is connected via a link mechanism 19 to a disc-shaped rotor 17 that is fixed integrally to the drive shaft 13. The crank chamber 11 forms a control pressure chamber that changes the state of a compression mechanism, which includes cylinder bores 3A of the cylinder block 3, pistons 47 (described later), and the swash plate 15, in response to the internal pressure.

[0012] The link mechanism 19 includes a first arm 17A protruding from the rotor 17, a second arm 15B protruding from the swash plate 15, and a link arm 21 connecting a tip of the first arm 17A to a tip of the second arm 15B. One end of the link arm 21 is rotatably connected to the first arm 17A via a first connecting pin 23. The other end of the link arm 21 is rotatably connected to the second arm 15B via a second connecting pin 25. Therefore, the link mechanism 19 allows the swash plate 15 to rotate integrally with the drive shaft 13 and change its tilt angle along the axial direction of the drive shaft 13.

[0013] The through-hole 15A of the swash plate 15 is shaped to allow the swash plate 15 to tilt between a minimum inclination angle and a maximum inclination angle. Specifically, the through-hole 15A is formed with a minimum inclination angle limiter that contacts the outer circumferential surface of the drive shaft 13 to limit the tilt angle of the swash plate 15 in a direction that decreases the inclination angle. The through-hole 15A also has a maximum inclination angle limiter that contacts the outer circumferential surface of the drive shaft 13 to limit the tilt angle of the swash plate 15 in a direction that increases the inclination angle. Therefore, the swash plate 15 can freely tilt between the minimum inclination angle limited by the minimum inclination angle limiter and the maximum inclination angle limited by the maximum inclination angle limiter with respect to the axial direction of the drive shaft 13.

[0014] A tilt angle reducing spring 27 that urges the swash plate 15 in a direction to decrease the tilt angle and a tilt angle increasing spring 29 that urges the swash plate 15 in a direction to increase the tilt angle are disposed on the drive shaft 13 at positions across the swash plate 15. Specifically, the tilt angle reducing spring 27 is disposed between the swash plate 15 and the rotor 17, and the tilt angle increasing spring 29 is disposed between the swash plate 15 and a disk-shaped spring support member 31 fixed to or formed on the drive shaft 13.

[0015] The biasing force of the inclination angle increasing springs 29 is set to be greater than the biasing force of the inclination angle decreasing springs 27 when the inclination angle of the swash plate 15 is at the minimum inclination angle. Therefore, when the drive shaft 13 is not rotating, i.e., when the swash plate compressor 1 is stopped, the swash plate 15 is positioned at an inclination angle (>minimum inclination angle) where the biasing force of the inclination angle decreasing springs 27 and the biasing force of the inclination angle increasing springs 29 are balanced. The inclination angle where the biasing force of the inclination angle decreasing springs 27 and the biasing force of the inclination angle increasing springs 29 are balanced is set as the minimum inclination angle range that ensures compression by the pistons 47 (described later). For example, if the inclination angle when the swash plate 15 is perpendicular to the axial direction of the drive shaft 13 is 0 degrees (minimum inclination angle), the inclination angle can be set in the range of 1 to 3 degrees.

[0016] One end of the drive shaft 13 passes through the cylindrical boss portion 5A of the front housing 5, extends outward, and is connected via an electromagnetic clutch 33 to a pulley 35 that is attached to the outer circumferential surface of the boss portion 5A so as to be rotatable relative to the boss portion 5A. The drive shaft 13 and rotor 17 are supported in the radial direction by bearings 37 and 39, and in the thrust direction by a bearing 41 and a thrust plate 43. The distance between the other end of the drive shaft 13 and the thrust plate 43 is adjusted by an adjustment screw 45 to provide a predetermined gap.

[0017] When the electromagnetic clutch 33 is operated while a rotational driving force from an electric motor or an engine (not shown) is being transmitted to the pulley 35, the pulley 35 and the drive shaft 13 are connected to each other, and the drive shaft 13 is rotated. When the electromagnetic clutch 33 is stopped, the pulley 35 and the drive shaft 13 are separated from each other, and the swash plate compressor 1 can be stopped.

[0018] The swash plate compressor 1 also has pistons 47 in the same number as the plurality of cylinder bores 3A formed in the cylinder block 3. Each piston 47 has a piston body 47A arranged axially movably relative to the cylinder bore 3A, and an extension portion 47B extending axially from the piston body 47A toward the inside of the crank chamber 11.

[0019] The extension 47B of the piston 47 is formed with a housing 47C that can house a pair of shoes 49 that are arranged on either side of the periphery of the swash plate 15. That is, the piston 47 is connected to the swash plate 15 via the pair of shoes 49 that are arranged on either side of the periphery of the swash plate 15. Therefore, the piston 47 reciprocates in the cylinder bore 3A of the cylinder block 3 as the swash plate 15 rotates.

[0020] The cylinder head 9 is formed with a suction chamber 51 located in the center and multiple discharge chambers 53 arranged annularly surrounding the suction chamber 51. The suction chamber 51 communicates with each cylinder bore 3A of the cylinder block 3 via a suction hole 7A and a suction valve (not shown) formed in the valve plate 7. The discharge chamber 53 communicates with each cylinder bore 3A of the cylinder block 3 via multiple discharge holes 7B formed in the valve plate 7 and a reed valve-type discharge valve 61 attached to the back surface of the valve plate 7 facing the discharge chamber 53. In addition to the discharge valve 61, a valve retainer 63 that limits the opening degree (deflection amount) of the discharge valve 61 is attached to the back surface of the valve plate 7 facing the discharge chamber 53. The discharge valve 61 and the valve retainer 63 will be described in detail later.

[0021] Here, the front housing 5, cylinder block 3, valve plate 7, cylinder head 9, etc. are fastened together by a plurality of through bolts 55, with gaskets (not shown) placed between each component as needed, to form the compressor housing.

[0022] 1, the cylinder head 9 is formed with a suction passage that connects the low-pressure side of the refrigerant circuit of the air conditioning system with the suction chamber 51, and a discharge passage that connects the high-pressure side of the refrigerant circuit of the air conditioning system with the discharge chamber 53. A check valve (not shown) that opens and closes the discharge passage is also provided in the cylinder head 9. This check valve operates in response to the pressure difference between the pressure in the discharge chamber 53 upstream of it and the pressure in the discharge passage downstream of it, closing the discharge passage when this pressure difference is smaller than a predetermined value and opening the discharge passage when this pressure difference is equal to or greater than a predetermined value.

[0023] A cylindrical displacement control valve 65 is attached to a predetermined location in the cylinder head 9 to adjust the aperture of a pressure supply passage 57 that connects the discharge chamber 53 and the crank chamber 11. By adjusting the aperture of the pressure supply passage 57, the displacement control valve 65 increases or decreases the flow rate of high-pressure refrigerant supplied from the discharge chamber 53 to the crank chamber 11, thereby changing the internal pressure of the crank chamber 11 and controlling the refrigerant discharge capacity. The refrigerant present in the crank chamber 11 flows into the suction chamber 51 through a pressure release passage 59 formed by a communicating passage 3B and a space 3C formed in the cylinder block 3 and an orifice (not shown) formed in the valve plate 7. Therefore, by changing the internal pressure of the crank chamber 11 with the displacement control valve 65, the inclination angle of the swash plate 15, i.e., the stroke of the pistons 47, is changed, thereby variably controlling the discharge capacity of the swash plate compressor 1.

[0024] Next, the operation of the swash plate compressor 1 will be described. When the electromagnetic clutch 33 is activated while a rotational driving force from an electric motor, an engine, or the like is being transmitted to the pulley 35, the pulley 35 and the drive shaft 13 are connected via the electromagnetic clutch 33, and the drive shaft 13 begins to rotate. When the drive shaft 13 starts to rotate, the rotor 17, which is integrated with the drive shaft 13, and the swash plate 15, which is connected to the rotor 17 via the link mechanism 19, also begin to rotate. While the swash plate compressor 1 is stopped, as described above, the swash plate 15 is in the minimum inclination range that ensures compression by the pistons 47. Therefore, the pistons 47 connected to the swash plate 15 reciprocate within the cylinder bores 3A of the cylinder block 3. When the pistons 47 move toward the front (the swash plate 15 side in FIG. 1 ), the volume of the compression chamber defined by the pistons 47, the cylinder bores 3A, and the valve plate 7 increases, creating a negative pressure. Low-pressure refrigerant is introduced into the suction chamber 51 from the low-pressure side of the refrigerant circuit via the suction passage. The low-pressure refrigerant introduced into the suction chamber 51 is sucked into the compression chamber through the suction hole 7A and the suction valve formed in the valve plate 7. When the piston 47 moves to the rear side (toward the cylinder head 9 in FIG. 1), the volume of the compression chamber decreases and the pressure becomes positive, and the high-pressure refrigerant present in the compression chamber is discharged into the discharge chamber 53 through the discharge hole 7B and the discharge valve 61 formed in the valve plate 7.

[0025] Most or all of the high-pressure refrigerant discharged into the discharge chamber 53 is separated into lubricating oil and high-pressure refrigerant by an oil separator (not shown) attached to the cylinder head 9. The high-pressure refrigerant separated by the oil separator is discharged to the high-pressure side of the refrigerant circuit via a discharge passage. The lubricating oil separated by the oil separator is returned to the bottom of the crank chamber 11 via a lubricating oil passage (not shown). In addition, some of the high-pressure refrigerant discharged into the discharge chamber 53 is supplied to the displacement control valve 65 via a pressure supply passage 57 that connects the discharge chamber 53 and the crank chamber 11. The high-pressure refrigerant supplied to the displacement control valve 65 passes through filters (not shown) arranged around multiple inlet ports of the displacement control valve 65 to capture foreign matter, and then flows into the interior of the displacement control valve 65 through the multiple inlet ports.

[0026] The capacity control valve 65 adjusts the flow rate of high-pressure refrigerant flowing in through multiple inlet ports by increasing or decreasing the opening of internal passages in response to an external actuation signal, while discharging high-pressure refrigerant from multiple discharge ports. At this time, the capacity control valve 65 senses the internal pressure of the suction chamber 51 and changes the lift amount of the valve disc to automatically adjust the internal pressure of the crank chamber 11 so that the internal pressure of the suction chamber 51 remains constant. After foreign matter is trapped in filters (not shown) arranged around the multiple discharge ports, the high-pressure refrigerant discharged from the multiple discharge ports flows into the pressure supply passage 57 located downstream of the capacity control valve 65 and is supplied to the crank chamber 11.

[0027] When the supply of high-pressure refrigerant to the crank chamber 11 is cut off, the internal pressure of the crank chamber 11 decreases, increasing the inclination angle of the swash plate 15. As the inclination angle of the swash plate 15 increases, the stroke of the pistons 47 connected to the swash plate 15 via the link mechanism 19 increases, and the discharge capacity from the compression chambers also increases. As a result, the flow rate of high-pressure refrigerant discharged from the compression chambers to the discharge chamber 53 increases, and the flow rate of high-pressure refrigerant discharged from the swash plate compressor 1 to the high-pressure side of the refrigerant circulation circuit also increases.

[0028] As described above, the discharge valve 61, which opens and closes the discharge hole 7B formed in the valve plate 7, has its opening limited by the valve retainer 63. That is, when the pressure difference between the internal pressure of the compression chamber and the internal pressure of the discharge chamber 53 exceeds a predetermined pressure difference, the discharge valve 61 opens and its entire surface abuts against the valve retainer 63, thereby limiting its opening. When the pressure difference between the internal pressure of the compression chamber and the internal pressure of the discharge chamber 53 falls below a predetermined pressure difference, the discharge valve 61 changes from its open state, in which its opening is limited, to a closed state due to its own elasticity. At this time, if the discharge valve 61 is stuck to the valve retainer 63 for some reason, it will not immediately change from the open state to the closed state even when the pressure difference between the internal pressure of the compression chamber and the internal pressure of the discharge chamber 53 falls below the predetermined pressure difference, resulting in a delay in closing the discharge valve 61. If there is a delay in closing the discharge valve 61, high-pressure refrigerant will flow back from the discharge chamber 53 to the compression chamber, resulting in a decrease in performance, or the collision energy when the discharge valve 61 seats on the valve seat of the valve plate 7 will increase, resulting in increased wear and vibration of the valve seat.

[0029] Therefore, as in the first to third embodiments described below, the structure of the valve retainer 63 that limits the opening degree of the discharge valve 61 is devised to prevent the discharge valve 61 from sticking to the valve retainer 63.

[0030] <<First Embodiment>> As shown in FIG. 2 , the valve retainer 63 is fixed concentrically to the back surface of the valve plate 7 facing the discharge chamber 53 by bolts (not shown). The valve retainer 63 includes a disk-shaped fixing portion 63A fixed to the back surface of the valve plate 7 and multiple extension portions 63B extending from the periphery of the fixing portion 63A toward each of the discharge holes 7B in the valve plate 7. Each extension portion 63B is made of a material having the same plate thickness as the fixing portion 63A, and its tip portion is formed in a shape that follows the tip portion of the discharge valve 61 located on the outlet side of the discharge hole 7B. Each extension portion 63B is formed in a curved shape that gradually moves away from the back surface of the valve plate 7 in a side view. Here, the curved shape of the extension portion 63B can be a shape that follows the shape of the back surface of the discharge valve 61 facing the discharge chamber 53 when the discharge valve 61 is opened to a predetermined opening degree.

[0031] 3, a non-contact portion 63C that avoids contact with the discharge valve 61 is formed on at least a part of the edge of the contact surface of the valve retainer 63 that contacts the discharge valve 61, in other words, on at least a part of the edge of the contact surface that contacts the discharge valve 61 on the front surface of the extended portion 63B facing the discharge valve 61. Specifically, the non-contact portion 63C is formed in a shape where a corner located on the edge of the contact surface of the valve retainer 63 is cut out. Therefore, as shown in FIG. 4, the extended portion 63B of the valve retainer 63 has the non-contact portion 63C that does not contact the edge of the discharge valve 61. Note that the hatched area in FIG. 4 indicates the area where the valve retainer 63 contacts the discharge valve 61.

[0032] In this way, the following effects can be achieved. In an open state in which the discharge valve 61 abuts against the valve retainer 63, it is considered that the edge of the discharge valve 61 is particularly likely to stick to the valve retainer 63. Therefore, by forming a non-abutment portion 63C on at least a portion of the edge of the abutment surface of the valve retainer 63 that abuts against the discharge valve 61, direct abutment with the edge of the discharge valve 61 is avoided, and the discharge valve 61 is more likely to separate from the valve retainer 63. Therefore, sticking of the discharge valve 61 to the valve retainer 63 can be suppressed. Furthermore, there is no delay in the change of the discharge valve 61 from the open state to the closed state, and it is possible to avoid, for example, a decrease in performance due to refrigerant backflow from the discharge chamber 53 to the compression mechanism and re-expansion in the compression mechanism. Furthermore, because the discharge valve 61 closes when the pressure difference between the compression chamber and the discharge chamber 53 is large, the elastic force of the discharge valve 61 returning to the closed state is weakened by the internal pressure of the compression chamber, preventing the discharge valve 61 from closing more quickly than necessary. Therefore, the collision energy when the discharge valve 61 abuts against the valve seat is reduced, which prevents the valve seat from being worn more easily and prevents increased vibration and noise.

[0033] As shown in Fig. 5, the valve retainer 63 may be integrated with a metal gasket 67 disposed between the valve plate 7 and the cylinder head 9. In the following description, to avoid confusion with the valve retainer 63 shown in Figs. 2 to 4, it will be referred to as a "valve retainer 69" (different reference numerals will be used for the valve retainers in other embodiments as well).

[0034] A portion of the gasket 67 facing the discharge valve 61 arranged on the back surface of the valve plate 7 bulges in a direction away from the valve plate 7, thereby forming a valve retainer 69 integrally therewith. The front surface of the valve retainer 69 facing the discharge valve 61 can be shaped to conform to the back surface of the discharge valve 61 facing the discharge chamber 53 when the discharge valve 61 is open to a predetermined degree. The valve retainer 69 integrated with the gasket 67 is also formed with at least one through-hole 69A through which high-pressure refrigerant passes, so that the high-pressure refrigerant discharged from the discharge hole 7B of the valve plate 7 via the discharge valve 61 can be discharged to the discharge chamber 53. In the example shown in FIG. 5 , the through-holes 69A of the valve retainer 69 are arranged at a position facing the tip of the discharge valve 61 and on both sides in the direction in which the discharge valve 61 extends, but this is not limited to this.

[0035] At least a part of the edge of the contact surface of the valve retainer 69 that contacts the discharge valve 61 is formed with a non-contact portion 69B that avoids contact with the discharge valve 61. Specifically, the edge of the contact surface of the valve retainer 69, located on both sides in a direction perpendicular to the extension direction of the discharge valve 61, is further bulged in a direction away from the valve plate 7 to form the non-contact portion 69B. The non-contact portion 69B starts from the edge of the through hole 69A facing the tip end of the discharge valve 61 and extends along the edge of the discharge valve 61 to at least the base end of the contact surface. In this way, the valve retainer 69 has the non-contact portion 69B that does not contact the edge of the discharge valve 61.

[0036] 2 to 4, by forming a non-contact portion 69B on at least a part of the edge of the contact surface of the valve retainer 69 that contacts the discharge valve 61, direct contact with the edge of the discharge valve 61 is avoided, and the discharge valve 61 can be easily separated from the valve retainer 69. This makes it possible to prevent the discharge valve 61 from sticking to the valve retainer 69. Note that other actions and effects are the same as those of the first embodiment shown in FIGS. 2 to 4, and therefore detailed description thereof will be omitted. Please refer to the description of the first embodiment if necessary (the same applies hereinafter).

[0037] <<Second embodiment>> As shown in FIG. 6 , the valve retainer 71 is concentrically fixed to the back surface of the valve plate 7 facing the discharge chamber 53 by bolts (not shown), similar to the valve retainer 63 of the first embodiment shown in FIG. 2 . The valve retainer 71 includes a disk-shaped fixing portion 71A fixed to the back surface of the valve plate 7 and multiple extension portions 71B extending from the periphery of the fixing portion 71A toward each of the discharge holes 7B in the valve plate 7. Each extension portion 71B is made of a material having the same plate thickness as the fixing portion 71A, and its tip portion is formed in a shape that follows the tip portion of the discharge valve 61 disposed on the outlet side of the discharge hole 7B. Each extension portion 71B is formed in a curved shape that gradually moves away from the back surface of the valve plate 7 in a side view. Here, the curved shape of the extension portion 71B can be a shape that follows the shape of the back surface of the discharge valve 61 facing the discharge chamber 53 when the discharge valve 61 is opened to a predetermined opening degree.

[0038] The contact surface of the valve retainer 71 that contacts the discharge valve 61 is configured to reduce the contact area with the discharge valve 61. Specifically, at least one hole 71C penetrating the plate surface is formed at the tip of the extension portion 71B of the valve retainer 71, at the location that contacts the tip of the discharge valve 61. In the example shown in the figure, one hole 71C is formed at the tip of the extension portion 71B, but the number of hole 71C may be multiple. Therefore, the extension portion 71B of the valve retainer 71 has at least one hole 71C penetrating the plate surface.

[0039] In this way, by forming at least one hole 71C on the contact surface of the valve retainer 71 that contacts the discharge valve 61, the contact area with the discharge valve 61 at that location is smaller than in a valve retainer 71 that does not have the hole 71C, making it easier for the discharge valve 61 to separate from the valve retainer 71. Therefore, it is possible to prevent the discharge valve 61 from sticking to the valve retainer 71. Furthermore, with this configuration, the internal pressure of the discharge chamber 53 acts on the back surface of the discharge valve 61 via the at least one hole 71C, so it is possible to support the elastic force when the discharge valve 61 separates from the valve retainer 71.

[0040] Instead of the at least one hole 71C, at least one recess (not shown) recessed by a predetermined dimension from (not penetrating) the front surface facing the discharge valve 61 may be formed at the tip of the extension portion 71B of the valve retainer 71. This configuration also provides the same effects as the valve retainer 71 shown in FIG. 6, except for the effect of the internal pressure of the discharge chamber 53 acting on the back surface of the discharge valve 61.

[0041] As shown in FIG. 7, the valve retainer 73 may be integrated with the metal gasket 67 disposed between the valve plate 7 and the cylinder head 9, similar to the first embodiment shown in FIG.

[0042] A portion of the gasket 67 facing the discharge valve 61 arranged on the back surface of the valve plate 7 bulges in a direction away from the valve plate 7, thereby forming a valve retainer 73 integrally therewith. The front surface of the valve retainer 73 facing the discharge valve 61 can be shaped to conform to the back surface of the discharge valve 61 facing the discharge chamber 53 when the discharge valve 61 is open to a predetermined degree. The valve retainer 73 integrated with the gasket 67 is also formed with a through-hole 73A through which high-pressure refrigerant passes, so that the high-pressure refrigerant discharged from the discharge hole 7B of the valve plate 7 via the discharge valve 61 can be discharged to the discharge chamber 53. In the example shown in FIG. 6 , the through-holes 73A of the valve retainer 73 are arranged at a position facing the tip of the discharge valve 61 and on both sides in the direction in which the discharge valve 61 extends, but this is not limited to this.

[0043] At least one hole 73B is formed in the contact surface of the valve retainer 73 that contacts the discharge valve 61, reducing the contact area with the discharge valve 61. Instead of forming at least one hole 73B in the contact surface of the valve retainer 73, at least one protrusion (not shown) extending in a direction away from the valve plate 7 may be formed in the contact surface of the valve retainer 73.

[0044] 6, the contact area between the valve retainer 73 and the discharge valve 61 is reduced at a portion where at least one hole 73B or protrusion is formed, making it easier for the discharge valve 61 to separate from the valve retainer 73. This makes it possible to prevent the discharge valve 61 from sticking to the valve retainer 73. Furthermore, in a configuration where at least one hole 73B is formed in the valve retainer 73, the internal pressure of the discharge chamber 53 acts on the back surface of the discharge valve 61 via this at least one hole 73B, making it possible to support the elastic force when the discharge valve 61 separates from the valve retainer 73. Note that other functions and effects are similar to those of the first embodiment shown in FIG. 6, and therefore detailed description thereof will be omitted.

[0045] In the first and second embodiments, rubber may be coated on the front and back surfaces of the valve retainers 63, 69, 71, and 73. This improves the airtightness between the discharge valve 61 and the valve retainer, and absorbs the collision energy when the discharge valve 61 closes, reducing vibration and noise.

[0046] <<Third Embodiment>> As shown in Fig. 8, the valve retainer 75 is integrated with a metal gasket 67 arranged between the valve plate 7 and the cylinder head 9, similar to the valve retainer 69 of the first embodiment shown in Fig. 5. The valve retainer 75 is integrally formed by expanding a portion of the gasket 67 facing the discharge valve 61 arranged on the back surface of the valve plate 7 in a direction away from the valve plate 7. The front surface of the valve retainer 75 facing the discharge valve 61 can be shaped to conform to the back surface of the discharge valve 61 facing the discharge chamber 53 when the discharge valve 61 is open to a predetermined degree. Furthermore, the valve retainer 75 integrated with the gasket 67 is formed with a through-hole 75A through which high-pressure refrigerant passes so that the high-pressure refrigerant discharged from the discharge hole 7B of the valve plate 7 via the discharge valve 61 can be discharged into the discharge chamber 53. In the example shown in FIG. 8, the through holes 75A of the valve retainer 75 are arranged at a position facing the tip end of the discharge valve 61 and on both sides in the direction in which the discharge valve 61 extends, but this is not limitative.

[0047] Furthermore, the front and back surfaces of the valve retainer 75 are coated with rubber 77. Coating the front surface of the valve retainer 75 with rubber 77 improves the airtightness between the discharge valve 61 and the valve retainer 75, and absorbs the collision energy when the discharge valve 61 closes, thereby reducing vibration and noise.

[0048] In the valve retainer 75, of the rubber 77 coated on the front surface of the valve retainer 75, at least the rubber 77 on the contact surface with which the discharge valve 61 contacts is peeled off at multiple locations to form peeled portions 75B, making the contact surface rough. In this way, as with the second embodiment shown in Fig. 5, the contact area between the valve retainer 75 and the discharge valve 61 is reduced, making it easier for the discharge valve 61 to separate from the valve retainer 75. Therefore, it is possible to prevent the discharge valve 61 from sticking to the valve retainer 75.

[0049] To roughen the contact surface of the rubber 77 coated on the valve retainer 75, instead of peeling off the rubber 77 at multiple locations, the rubber 77 may be recessed into a cone shape at multiple locations to form recesses 75C, as shown in FIG. 9 . Specifically, a pin-shaped tool, for example, is pressed against the contact surface of the rubber 77-coated valve retainer 75 to form through-holes of approximately 0.3 mm. In this case, as shown in FIG. 10 , recesses 75C whose diameter gradually decreases from the front surface to the rear surface are formed in the plate surface of the valve retainer 75. Since the rubber 77 is coated on the front surface of the valve retainer 75, the inner surface of the recesses 75C is covered with the rubber 77. In this case, it does not matter whether the tip of the recesses 75C is open or closed. Note that the operation and effect of this configuration are similar to those of the third embodiment shown in FIG. 8 , and therefore a detailed description thereof will be omitted.

[0050] Furthermore, to roughen the contact surface of the rubber 77 coated on the valve retainer 75, recesses 75D may be formed in a triangular pyramid shape at multiple locations, as shown in FIG. 11 . In other words, the recesses 75D may be formed in a triangular pyramid shape similar to the teeth of a grater. Specifically, a triangular pyramid-shaped tool is pressed against the contact surface of the rubber 77-coated valve retainer 75 to form through-holes. In this case, the plate surface of the valve retainer 75 is formed with triangular pyramid-shaped recesses 75D whose cross-sectional area gradually decreases from the front surface to the rear surface. Since the front surface of the valve retainer 75 is coated with rubber 77, the inner surface of the recesses 75D is covered with the rubber 77. In this case, it does not matter whether the tip of the recesses 75D is open or closed. This configuration can also achieve the same functions and effects as the valve retainer 75 shown in FIGS. 9 and 10.

[0051] In the third embodiment, the above configuration may be applied not only to the valve retainer 75 integrated with the gasket 67, but also to the valve retainer 63 of the first embodiment as shown in FIG. 2, so as to obtain the desired effects.

[0052] Furthermore, a person skilled in the art will easily understand that new embodiments can be created by omitting parts of the technical ideas of the various above-mentioned embodiments, appropriately combining parts of the ideas with each other, or replacing parts of the ideas with well-known technology.

[0053] For example, the compressor is not limited to the swash plate compressor 1, but may be any of various types of compressors such as a diaphragm compressor, a screw compressor, a scroll compressor, a rotary compressor, a slide vane compressor, etc. The compressor may further include an electric motor and a drive circuit for driving the electric motor. [Explanation of symbols]

[0054] REFERENCE SIGNS LIST 1... swash plate compressor (compressor), 3... cylinder block (compression mechanism), 3A... cylinder bore (compression mechanism), 7... valve plate, 7B... discharge hole, 15... swash plate (compression mechanism), 47... piston (compression mechanism), 51... suction chamber, 53... discharge chamber, 61... discharge valve, 67... gasket, 75... valve retainer, 75B... peeled portion, 75C... recess, 75D... recess, 77... rubber

Claims

1. a suction chamber into which a refrigerant is drawn; a compression mechanism that compresses the refrigerant in the suction chamber; a discharge chamber into which the refrigerant compressed by the compression mechanism is discharged; a reed valve-type discharge valve arranged on an outlet side of a discharge hole that communicates between the compression mechanism and the discharge chamber; a valve retainer that, when the discharge valve is opened, comes into contact with the discharge valve to limit an opening degree of the discharge valve; a rubber coating on a surface of the valve retainer; having The contact surface of the rubber coated on the valve retainer that contacts the discharge valve is formed into a rough surface. Compressor.

2. The rough surface of the contact surface is formed by peeling off the rubber at multiple locations. The compressor according to claim 1.

3. The rough surface of the abutment surface is formed by recessing a plurality of portions of the valve retainer. The compressor according to claim 1.

4. The valve retainer is formed in a conical shape at multiple locations. The compressor according to claim 3.

5. The valve retainer is formed in a triangular pyramid shape at a plurality of locations. The compressor according to claim 3.

6. The valve retainer is integrated with a gasket. The compressor according to claim 1.

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