KR100757507B1 - Displacement control valve for variable displacement compressor - Google Patents

Abstract

The displacement control valve adjusts the pressure in the crank chamber of the compressor which can change the compressor capacity. The suction pressure is introduced into the pressure reducing chamber of the control valve. The diaphragm operates the valve body through the rod in accordance with the suction pressure in the decompression chamber. The receiving sheet is arranged on the opposite side of the rod with the diaphragm sandwiched. A positioning convex part is provided in the receiving sheet, and a positioning concave part is formed in the upper end surface of the rod. The receiving seat and the rod hold the diaphragm so that the positioning ball covering engages with the positioning recess. Therefore, the receiving sheet is reliably positioned with respect to the diaphragm and the rod.

Diaphragm, Receiving Seat, Rod, Control Valve, Valve Body, Concave, Convex

Description

Capacity control valve for variable displacement compressors {DISPLACEMENT CONTROL VALVE FOR VARIABLE DISPLACEMENT COMPRESSOR}

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the displacement control valve of one Embodiment of this invention.

FIG. 2A is a partially enlarged cross-sectional view showing a portion of abutting portion of the receiving seat and the diaphragm in the control valve of FIG. 1.

FIG. 2B is a partially enlarged cross-sectional view showing a portion of the contact between the valve body and the rod in the control valve of FIG.

3A and 3B are partially enlarged sectional views of the capacity control valve according to another embodiment of the present invention, respectively.

4 is a sectional view showing a conventional capacity control valve.

The present invention relates to a capacity control valve for controlling the capacity of a variable displacement compressor.

The general variable displacement compressor used in the refrigerant circuit includes a crank chamber, an inclined movable tilt plate provided in the crank chamber, and a piston reciprocated by the inclined plate. The inclination angle of the inclined plate changes in accordance with the pressure (crank pressure) in the crank chamber. The piston moves in a stroke according to the inclination angle of the inclined plate. The capacity of the compressor changes with the stroke of the piston.

In order to regulate the crank pressure, the compressor is provided with a capacity control valve. This control valve is provided, for example, in the middle of a gas supply passage connecting the discharge chamber of the compressor to the crank chamber. The control valve adjusts the amount of refrigerant gas supplied from the discharge chamber to the crank chamber through the gas supply passage from the discharge chamber in accordance with the pressure (suction pressure) of the refrigerant gas sucked into the compressor from the evaporator provided in the refrigerant circuit.

4 shows an example of a conventional capacity control valve. The valve chamber 102 is provided in the lower part of the valve housing 101 of this control valve. The valve chamber 102 is connected to the discharge chamber 142 of the compressor via an upstream portion of the gas supply passage 143 formed in the compressor. The valve chamber 102 is further connected to the crank chamber 140 of the compressor via the valve hole 103 and the downstream portion of the gas supply passage 143. The spherical valve body 104 is accommodated in the valve chamber 102 and pressurized toward the valve hole 103 by the spring 105.

The pressure reduction mechanism 108 is provided in the upper part of the valve housing 101. The pressure reduction mechanism 108 has a spring chamber 110 partitioned by a resin or metal diaphragm 109 and a pressure reduction chamber 111. The pressure reduction chamber 111 is connected to the suction chamber 141 of the compression chamber via the pressure detection passage 144. The valve housing 101 is provided with a rod hole 112 having a circular cross section for forming the pressure reduction chamber 111.                         

The pressure reduction mechanism 108 is provided with the cylindrical case 115 which defines the said spring chamber 110. As shown in FIG. This cylindrical case 115 is fixed on the valve housing 101. The diaphragm 109 is held by the cylindrical case 115 and the valve housing 101.

The rod hole 112 is connected to the valve hole 103 via a communication hole 116 formed in the valve housing 101. An axially movable rod 117 is received in the rod hole 112, and the tip of the rod 117 extends through the communication hole 116 to the valve hole 103. The spring 105 in the valve chamber 102 pressurizes the valve body 104 such that the valve body 104 is pressed against the lower end surface of the rod 117.

The spring 119 disposed in the pressure reduction chamber 111 presses the diaphragm 109 upward through FIG. 4 through the rod 117.

The spring chamber 110 is provided with an adjustment spring (125). The adjustment spring 125 presses the diaphragm 109 downward through FIG. 4 via the receiving seat 126. The adjuster 127 is screwed to the cylindrical case 115 so as to be axially movable. The adjusting body 127 receives the adjusting spring 125 through the receiving seat 128. According to the axial position of the adjuster 127 with respect to the cylindrical case 115, the force which the adjustment spring 125 presses the diaphragm 109 changes.

The suction pressure Ps is introduced into the decompression chamber 111 from the suction chamber 141 through the check passage 144. The diaphragm 109 is displaced in accordance with the suction pressure Ps in the decompression chamber 111. The displacement of the diaphragm 109 is transmitted to the valve body 104 via the rod 117. Therefore, the valve body 104 is operated by the diaphragm 109 so as to adjust the opening degree of the valve hole 103 in accordance with the suction pressure Ps in the decompression chamber 111. According to the opening degree of the valve hole 103, the amount of the refrigerant gas supplied from the discharge chamber 142 to the crank chamber 140 through the gas supply passage 143 is adjusted. The crank pressure Pc changes in accordance with the amount of the refrigerant gas supplied to the crank chamber 140, and the inclination angle of the inclined plate of the compressor is also changed accordingly. As a result, the capacity of the compressor is adjusted so that the suction pressure Ps converges to a predetermined target value (target suction pressure).

The pressing force of the adjustment spring 125 reflects the target suction pressure. At the time of manufacture of the control valve, by adjusting the axial position of the adjuster 127 with respect to the cylindrical case 115, the pressing force of the adjustment spring 125, ie, the target suction pressure, is determined. The control valve is operated so that the suction pressure Ps converges to the target suction pressure set by the adjuster 127.

The lower end of the adjustment spring 125 is fitted to the fitting convex portion 126 formed on the upper surface of the receiving sheet 126 so as to be positioned with respect to the receiving sheet 126. The upper end of the adjustment spring 125 is likewise fitted to the receiving seat 128 such that it is positioned with respect to the receiving seat 128. The receiving sheet 128 also has a recess 128a that is engaged with the engaging projection 127a formed on the lower surface of the adjuster 127. By engaging the engaging projection 127a and the recessed portion 128a, the receiving sheet 128 is positioned relative to the adjuster 127.

However, the receiving seat 126 is only pressed against the diaphragm 109 by the adjustment spring 125. Therefore, the position of the receiving sheet 126 is shifted with respect to the diaphragm 109 by the movement of the diaphragm 109 according to the pressure fluctuations in the pressure reduction chamber 111. As a result, the receiving sheet 126 or the adjustment spring 125 contacts the inner wall of the cylindrical case 115, and a sliding resistance is generated.

In addition, the valve body 104 is only pressed against the bottom surface of the rod 114 by the spring 105. Therefore, the position of the valve body 104 shifts with respect to the rod 117 by the movement of the rod 117 by the pressure change in the pressure reduction chamber 111. As a result, the valve body 104 comes into contact with the inner wall of the valve housing 101 defining the valve chamber 102, and a sliding resistance is generated.

The sliding resistance deteriorates the movement of the diaphragm 109 due to pressure fluctuations in the pressure reducing chamber 111, thereby lowering the response and accuracy of the flow rate control by the control valve. As a result, the capacity of the compressor is not well controlled. In addition, the sliding resistance causes the occurrence of noise in the operation of the control valve and at the same time reduces the durability of the control valve.

Accordingly, it is an object of the present invention to provide a capacity control valve that operates well and is excellent in durability.

In order to achieve the above object, the present invention provides a control valve for a variable displacement compressor. The control valve adjusts the pressure in the crank chamber of the compressor, which can change the capacity of the compressor. The compressor includes a suction pressure region that receives suction pressure, a discharge pressure region that receives discharge pressure, and a gas supply passage that connects the crank chamber to the discharge pressure region. The control valve is a pressure reducing mechanism having a valve housing provided in the middle of the gas supply passage, an opening degree of the gas supply passage, a valve body provided in the valve housing, a decompression chamber, and a diaphragm. A suction pressure of the pressure region is introduced into the pressure reduction chamber, and the diaphragm is capable of transmitting a displacement of the diaphragm to the valve body and a rod extending into the valve housing, the diaphragm displacing in accordance with the suction pressure in the pressure reduction chamber; A receiving sheet disposed on an opposite side of the rod by inserting a diaphragm, pressurizing means for pressing the receiving sheet and rod toward the diaphragm so that the diaphragm is held by the receiving sheet and the rod, and the receiving sheet and the rod Installed between the receiving seat and the rod through the diaphragm Uneven engagement means for engaging is provided.

Another control valve provided by the present invention includes a valve housing provided in the middle of a gas supply passage, an opening degree of the gas supply passage, and a valve body provided in the valve housing, a pressure reducing chamber and a pressure reducing member. As the mechanism, a suction pressure of the suction pressure region is introduced into the pressure reduction chamber, and the pressure reduction member can transmit a pressure reduction mechanism that is displaced according to the suction pressure in the pressure reduction chamber, and a displacement of the pressure reduction member to the valve body. A rod extending inwardly, pressurizing means capable of pressing the valve body against the rod, and forcing the valve body toward the rod, and provided between the valve body and the rod, and hanging the valve body and the rod from each other. And an uneven engagement means for fitting.

(Embodiment of invention)

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of this invention is described according to FIGS. 1-2B. The displacement control valve shown in FIG. 1 is mounted in a variable displacement compressor in which a refrigerant circuit is assembled. Further, although the detailed configuration of the variable displacement compressor is not particularly shown, the compressor has a crank chamber 40 which receives the crank pressure Pc, and a suction chamber (suction pressure region) 41 which receives the suction pressure Ps. ) And a discharge chamber (discharge pressure region) 42 that receives the discharge pressure Pd. The crank chamber 40 is provided with an inclined plate that can move inclined. When the drive shaft of the compressor rotates, the piston is reciprocated by the inclined plate. The piston sucks the refrigerant gas introduced into the suction chamber 41 from the evaporator provided in the refrigerant circuit into the cylinder bore. The piston further compresses the refrigerant gas in the cylinder bore and discharges the compressed refrigerant gas into the discharge chamber 42. The compressed refrigerant gas in the discharge chamber 42 is sent out to the refrigerant circuit.

The compressor also includes a gas supply passage 43 for connecting the discharge chamber 42 to the crank chamber 40. The control valve is provided in the middle of the gas supply passage 43. The control valve is a refrigerant supplied from the discharge chamber 42 to the crank chamber 40 through the gas supply passage 43 in accordance with the suction pressure Ps introduced from the suction chamber 41 through the check passage 44. Adjust the amount of gas.

The valve chamber 2 is provided in the lower part of the valve housing 1 of the said control valve. The valve chamber 2 is connected to the discharge chamber 42 via an upstream portion of the gas supply passage 43. The valve housing 1 has a valve hole 3 opening in the valve chamber 2 and a port 30 communicating with the valve hole 3. The valve hole 3 is connected to the crank chamber 40 via the downstream of the port 30 and the gas supply passage 43. The valve chamber 2, the valve hole 3 and the port 30 are internal passages provided in the valve housing 1 to form part of the gas supply passage 43. The spherical valve body 4 is accommodated in the valve chamber 2. The spring 5 is disposed in the valve chamber 2 and presses the valve body 4 toward the valve hole 3. In the valve chamber 2, a spring support 6 supporting the spring 5 is provided. The spring bearing 6 has a gas flow hole 6a which communicates the valve chamber 2 with the upstream portion of the gas supply passage 43. A filter 7 is attached to the inlet of this gas flow hole 6a.

The pressure reduction mechanism 8 is provided in the upper part of the valve housing 1. The pressure reduction mechanism 8 has a spring chamber 10, a pressure reduction chamber 11, and a diaphragm 9 as a pressure reduction member for partitioning the chambers 10 and 11. The diaphragm 9 consists of a resin material or a metal material, for example. The valve housing 1 is provided with a rod hole 12 having a circular cross section for forming the decompression chamber 11. The rod hole 12 extends along the axial direction of the valve housing 1 and is open upward in FIG. 1. In the upper end surface of the valve housing 1, an annular groove 13 is formed so as to be located around the opening of the rod hole 12. The seal ring 14 is attached to the annular groove 13. The diaphragm 9 is arranged on the valve housing 1 through the seal ring 14 to close the opening of the rod hole 12.

The pressure reduction mechanism 8 further has a cylindrical case 15 defining the spring chamber 10. This cylindrical case 15 is fixed on the valve housing 1. The diaphragm 9 is sandwiched and supported by the cylindrical case 15 and the valve housing 1.

An adjustment spring 25 is provided in the spring chamber 10. The adjustment spring 25 presses the diaphragm 9 downward through the receiving seat 26. The cylindrical body 15 is screwed so that the adjuster 27 is axially movable. The adjuster 27 receives and holds the adjustment spring 25 through the receiving seat 28. By adjusting the axial position of the adjuster 27 with respect to the cylindrical case 15, the force which the adjustment spring 25 presses the diaphragm 9 changes.

The cylindrical fitting convex part 26a is formed in the upper surface of the receiving sheet 26. The lower end of the adjustment spring 25 is fitted to the fitting convex portion 26a so as to be positioned with respect to the receiving seat 26. The upper end of the adjustment spring 25 is likewise fitted to the receiving seat 28 so as to be positioned with respect to the receiving seat 28. In addition, the receiving sheet 28 has a recess 28a that is engaged with the cylindrical engaging projection 27a formed on the lower surface of the adjuster 27. By engaging the engaging projection 27a and the recessed portion 28a, the receiving sheet 28 is positioned relative to the adjuster 27.

The rod hole 12 includes a large diameter portion 12a positioned near the opening of the rod hole 12, a middle diameter portion 12b positioned in an axial middle portion of the rod hole 12, and a rod hole ( It has the small diameter part 12c located in the deep inner part of 12). The valve housing 1 has a partition 16 provided between the small diameter portion 12c and the valve hole 3. The partition 16 has a communication hole 16a which communicates the small diameter part 12c with the valve hole 3.

The rod 17 communicates with the rod hole 12, the communication hole 16a and the valve hole 3 so as to be axially movable with respect to the valve housing 1. The rod 17 has a large diameter portion 17a and a small diameter portion 17b. The large diameter portion 17a is inserted through the large diameter portion 12a and the middle diameter portion 12b of the rod hole 12. The diameter of the large diameter portion 17a of the rod 17 is approximately equal to or slightly smaller than the diameter of the middle diameter portion 12b of the rod hole 12. The pressure reduction chamber 11 is formed between the large diameter portion 17a of the rod 17 and the large diameter portion 12a of the rod hole 12.

An annular groove 17c and an elongated groove 17d are formed on the outer circumferential surface of the large diameter portion 17a of the rod 17. The elongate groove 17d extends along the axis of the rod 17 so as to communicate the decompression chamber 11 with the annular groove 17c. The annular groove 17c is connected to the pressure detecting passage 44 via a port 18 formed in the valve housing 1. Therefore, the suction pressure Ps of the suction chamber 41 is introduce | transduced into the pressure reduction chamber 11 through the pressure detection path 44, the port 18, the annular groove 17c, and the elongate groove 17d.

The spring 19 is arranged in the decompression chamber 11. The upper end of the spring 19 is engaged with the flange of the upper end of the rod 17. The lower end of the spring 19 is engaged with the stepped portion between the large diameter portion 12a and the middle diameter portion 12b of the rod hole 12. The spring 19 presses the diaphragm 9 upward through FIG. 1 through a rod 17. Moreover, this spring 19 and the said adjustment spring 25 diaphragm the receiving seat 16 and the rod 17, respectively, so that the diaphragm 9 may be supported by the receiving seat 26 and the rod 17. A pressing means for pressurizing toward (9) is configured.

The small diameter portion 17b of the rod 17 extends downward from the lower end of the large diameter portion 17a toward the valve hole 3 through the communication hole 16a. The spring 5 as the pressurizing means provided in the valve chamber 2 pressurizes the valve body 4 so as to press the valve body 4 to the lower end of the small diameter portion 17b.

As shown in Fig. 2B, a mortar-shaped inclined surface 16b is formed at a corner around the upper edge of the communication hole 16a, that is, the upper surface of the partition 16 and the communication hole 16a. Formed. This inclined surface 16b gradually becomes a small diameter as it goes from the rod hole 12 toward the valve hole 3.

In the small diameter portion 12c of the rod hole 12, a bush 21 having a substantially cylindrical shape is press-fitted. The bush 21 has an insertion through hole 21a that allows passage of the small diameter portion 17b of the rod 17. The bush 21 also has a tapered surface 21b corresponding to the inclined surface 16b.

A donut plate-shaped annular seal plate 22 is sandwiched and held between the bush 21 and the partition wall 16. The seal plate 22 has an insertion hole 22a that allows passage of the small diameter portion 17b of the rod 17. The seal plate 22 is made of an elastic resin material and has a substantially flat plate shape before being attached to the control valve. When the seal plate 22 is held by the inclined surface 16b of the partition 16 and the tapered surface 21b of the bush 21, the seal plate 22 is tapered along their surfaces 16b and 21b. Is bent. In the state where the rod 17 is assembled to the control valve, the inner circumferential edge of the seal plate 22 comes into close contact with the small diameter portion 17b by the elastic force of the seal plate 22.

As shown in FIG. 1, between the receiving sheet 26 and the rod 17, a first unevenness for engaging the receiving sheet 26 and the rod 17 with each other through the diaphragm 9 is engaged. Alignment means E1 is provided. Specifically, as shown in FIG. 2A, a positioning convex portion 26b is provided on the lower surface of the receiving sheet 26, that is, the end face of the receiving sheet 26 facing the diaphragm 9. This positioning convex part 26b is arrange | positioned on the shaft center of the receiving sheet 26. As shown in FIG. On the other hand, the positioning concave portion 17e corresponding to the positioning convex portion 26b is formed on the upper end surface of the rod 17, that is, the end face of the rod 17 facing the diaphragm 9. This positioning recessed portion 17e is disposed on the shaft center of the rod 17.

The receiving sheet 16 and the rod 17 hold the diaphragm 9 so that the positioning convex portion 26b is engaged with the positioning recess 17e. In the diaphragm 9, the deformed portion 9a corresponding to the positioning convex portion 26b and the positioning concave portion 17e is formed in advance. In addition, a flat diaphragm 9 having no deformation portion 9a is prepared, and the diaphragm 9 is sandwiched and held by the receiving seat 26 and the rod 17 when the control valve is assembled. The portion of the diaphragm 9 corresponding to the positioning convex portion 26b and the positioning concave portion 17e may be deformed.

The outer surface of the positioning convex portion 26b has a substantially spherical shape and is connected to the lower surface of the receiving sheet 26 in a smooth curved surface. The positioning concave portion 17e has a shape corresponding to the positioning convex portion 26b. That is, the positioning concave portion 17e has a substantially spherical shape and is connected to the top surface of the rod 17 with a smooth curved surface. Therefore, there is no possibility that the diaphragm 9 fitted and held by the positioning convex part 26b and the positioning recessed part 17e may be damaged.

As shown in FIG. 1, between the valve body 4 and the rod 17, a second uneven engagement means E2 for engaging the valve body 4 and the rod 17 with each other is provided. have. Specifically, as shown in FIG. 2B, the valve body 4 has a conical positioning convex portion 4a at a portion facing the lower surface of the rod 17. On the other hand, on the lower end surface of the rod 17, a conical positioning recess 17f engaging with the positioning convex portion 4a is formed.

Next, the operation of the control valve configured as described above will be described.

The suction pressure Ps of the suction chamber 41 is introduced into the decompression chamber 11 through the check passage 44. The diaphragm 9 is displaced according to the suction pressure Ps in the decompression chamber 11. The displacement of the diaphragm 9 is transmitted to the valve body 4 via the rod 17. Therefore, the valve body 4 is operated by the diaphragm 9 to adjust the opening degree of the valve hole 3 in accordance with the suction pressure Ps in the pressure reduction chamber 11. According to the opening degree of the valve hole 3, the amount of the refrigerant gas supplied from the discharge chamber 42 to the crank chamber 40 through the gas supply passage 43 is adjusted.

For example, when the cooling load applied to the refrigerant circuit decreases, the pressure of the refrigerant gas introduced into the suction chamber 41 from the evaporator, that is, the suction pressure Ps decreases. Then, the diaphragm 9 displaces so that the valve body 4 may move below FIG. 1, and the opening degree of the valve hole 3 becomes large. Therefore, the amount of refrigerant gas supplied from the discharge chamber 42 to the crank chamber 40 increases, and the crank pressure Pc rises. As a result, the inclination angle of the inclined plate of the compressor is reduced, and the capacity of the compressor is reduced.

Conversely, when the cooling load on the refrigerant circuit increases, the suction pressure Ps rises. Then, the diaphragm 9 will displace so that the valve body 4 may move upward in FIG. 1, and the opening degree of the valve hole 3 will become small. Therefore, the amount of refrigerant gas supplied from the discharge chamber 42 to the crank chamber 40 decreases, and the crank pressure Pc decreases. As a result, the inclination angle of the inclined plate of the compressor is increased, and the capacity of the compressor is increased.

The pressing force of the adjustment spring 25 reflects the target value (target suction pressure) of the suction pressure Ps. At the time of manufacture of the control valve, by adjusting the axial position of the adjuster 27 with respect to the cylindrical case 15, the pressing force of the adjustment spring 25, ie, the target suction pressure, is determined. The control valve controls the capacity of the compressor so that the actual suction pressure Ps converges to the target suction pressure set by the adjuster 27.

As shown in FIG. 1, a stepped portion 15b that is in contact with the receiving sheet 26 is formed on an inner surface of the cylindrical case 15. The receiving sheet 26 is prevented from moving upward more by contacting the stepped portion 15a. Therefore, even if the suction pressure Ps rises excessively, excessive deformation of the diaphragm 9 is prevented by the step part 15a receiving the receiving seat 26.

This embodiment has the following advantages.                     

The receiving sheet 26 and the rod 17 hold the diaphragm 9 so that the positioning convex portion 26b engages with the positioning concave portion 17e. Therefore, the receiving sheet 26 is reliably positioned with respect to the diaphragm 9 and the rod 17, and there is no position shift with respect to these members 9 and 17. FIG. That is, the receiving seat 26 does not displace in the direction orthogonal to the axial direction of the control valve with respect to the diaphragm 9 and the rod 17. Therefore, there is no possibility that the receiving seat 26 and the adjustment spring 25 come into contact with the inner wall of the cylindrical case 15, and the control valve works well according to the pressure fluctuations in the pressure reducing chamber 11.

Furthermore, since the positioning convex portion 4a of the valve body 4 engages with the positioning concave portion 17f of the rod 17, the valve body 4 is reliably positioned with respect to the rod 17. It is determined and no positional shift occurs with respect to the rod 17. That is, the valve body 4 does not displace with respect to the rod 17 in the direction orthogonal to the axial direction of the control valve. Therefore, there is no possibility that the valve body 4 may contact the inner wall of the valve housing 1 defining the valve chamber 2, and the control valve operates well according to the pressure in the decompression chamber 11.

As a result of this, in the present embodiment, the responsiveness and precision of the flow rate control by the control valve are improved, and the capacity of the compressor is controlled well. In addition, during operation of the control valve, no noise is generated and the durability of the control valve is improved.

Embodiment of this invention is not limited to said thing, You may change suitably as follows in the range which does not deviate from the meaning of this invention.

As shown in Fig. 3A, in contrast to Fig. 2A, a positioning concave portion 26c is formed in the receiving sheet 26, and a positioning convex portion 17g corresponding to the positioning concave portion 26c is formed. The rod 17 may be formed. That is, any structure may be adopted as long as it is a fastening means capable of preventing the displacement of the receiving seat 26 with respect to the diaphragm 9 and the rod 17.

As shown in Fig. 3B, in contrast to Fig. 2B, the positioning concave portion 4b is formed in the valve body 4, and the positioning convex portion 17h corresponding to the positioning concave portion 4b is formed. The rod 17 may be formed. That is, any structure may be adopted as long as it is an engagement means capable of preventing the positional shift between the valve body 4 and the rod 17.

The shape and size of the positioning convex portion 26b of the receiving sheet 26 and the positioning concave portion 17e of the rod 17 are not limited to those shown in the drawings, and may be appropriately changed. However, it is necessary to set the shape of the positioning convex part 26b and the positioning recessed part 17e to the shape which does not damage the diaphragm 9.

Similarly, the shape and size of the positioning convex portion 4a of the valve body 4 and the positioning concave portion 17f of the rod 17 are not limited to those shown in the figure, but may be appropriately changed.

Among the first uneven fastening means E1 provided between the receiving seat 26 and the rod 17, and the second uneven fastening means E2 provided between the valve body 4 and the rod 17, Only one uneven engagement means may be employed. Even in this manner, a good capacity control operation is achieved as compared with the conventional control valve. When only the second uneven engagement means E2 is employed, other than the diaphragm 9, for example, a bellows may be used as the pressure reducing member.

Conversely to FIG. 1, the valve hole 3 is connected to the discharge chamber 42 through the upstream portion of the gas supply passage 43, and the valve chamber 2 is connected to the crank chamber through the downstream portion of the gas supply passage 43. 40 may be connected.

Claims (10)

As a control valve for a variable displacement compressor, the control valve adjusts the pressure in the crank chamber of the compressor, which can change the capacity of the compressor, and the compressor includes: a suction pressure region receiving suction pressure, a discharge pressure region receiving discharge pressure; And a gas supply passage connecting the crank chamber to the discharge pressure region, wherein the control valve A valve housing provided in the middle of the gas supply passage; An opening of the gas supply passage can be adjusted, and a valve body installed in the valve housing; A decompression mechanism having a decompression chamber and a diaphragm, wherein a suction pressure of the suction pressure region is introduced into the decompression chamber, and the diaphragm includes a decompression mechanism displaced in accordance with the suction pressure in the decompression chamber; A rod capable of transmitting a displacement of the diaphragm to the valve body and extending in the valve housing; A receiving sheet disposed on an opposite side of the rod by inserting the diaphragm; Pressing means for pressing the receiving sheet and the rod toward the diaphragm, respectively, so that the diaphragm is held by the receiving sheet and the rod; Uneven fastening means provided between the receiving sheet and the rod to engage the receiving sheet and the rod with each other through the diaphragm. Control valve for a variable displacement compressor characterized in that it comprises a. The control valve for a variable displacement compressor according to claim 1, wherein the uneven engagement means includes a convex portion formed in the receiving seat and a concave portion formed in the rod so as to correspond to the convex portion. 3. The receiving sheet according to claim 2, wherein the receiving sheet has an opposite surface facing the diaphragm, and the convex portion is spherical in shape and is formed on the opposite surface so as to be smoothly connected to the opposite surface of the receiving sheet. The rod has an opposing face opposing the diaphragm, and the concave portion forms a spherical shape and is formed on the opposing face so as to be smoothly connected to the opposing face of the rod. Control valve. The control valve for a variable displacement compressor according to claim 1, wherein the uneven engagement means includes a recess formed in the receiving seat and a convex portion formed in the rod so as to correspond to the recess. 5. The receiving sheet according to claim 4, wherein the receiving sheet has an opposing surface facing the diaphragm, and the recess is formed on the opposing surface so as to form a spherical shape and to be smoothly connected to the opposing surface of the receiving sheet. The rod has an opposing face opposing the diaphragm, and the convex portion forms a spherical shape and is formed on the opposing face so as to be smoothly connected to the opposing face of the rod. Control valve for 6. The control valve for a variable displacement compressor according to any one of claims 1 to 5, wherein the diaphragm is provided with a deformation portion corresponding to the uneven engagement means in advance. 6. The valve body according to any one of claims 1 to 5, wherein the valve body is pressed against the rod by a spring, and a second uneven engagement means for engaging the valve body and the rod with each other is provided between the valve body and the rod. Control valve for a variable displacement compressor characterized in that it is installed. delete delete delete

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