KR20030071457A - Control valve for compressors and manufacturing method thereof - Google Patents

Abstract

The present invention provides a control valve of a reversible displacement compressor with high accuracy and relatively low cost. The control valve according to the present invention includes a pressure sensing unit having a metal diaphragm for machining at a relatively low cost. The diaphragm is supported between the flanges. After the pressure leak test, the pressure sensor is attached to the control valve. The control valve portion has a fastening piece and a positioning surface. The flange is in contact with the positioning surface and fixed by the fastening piece. The positioning surface is formed such that the gap between the diaphragm and the top of the valve chamber becomes a predetermined value.

Description

CONTROL VALVE AND MANUFACTURING METHOD OF A REVERSIBLE CAPACITY COMPRESSOR

The present invention relates to a control valve for controlling the discharge amount of a reversible displacement compressor for an automotive air conditioner. In particular, the present invention relates to an improvement of a pressure sensor for detecting a suction pressure of a compressor.

Japanese Patent Laid-Open No. 9-268973 describes a conventional control valve 1 for a variable displacement compressor. The control valve 1 is disposed in the refrigerant gas passage connecting the discharge pressure region and the crank chamber of the compressor. The control valve 1 changes the discharge capacity of the compressor by adjusting the pressure of the crank chamber. According to FIG. 8, the control valve 1 includes a main body 21 accommodating the valve body 23 and a pressure sensing unit 10 connected to the main body 21. The pressure sensing unit 10 includes a case 13 and a metal bellows 11 accommodated in the pressure sensing member or the case. The bellows 11 is connected to the upper and lower allowances 15a and 15b which are arranged to face each other. The pressure sensing chamber is installed in the bellows 11. The bellows 11 changes according to the suction pressure Ps of the compressor and detects the suction pressure Ps. The lower allowance 15b is joined to the transfer rod 22. The lower stake 15b and the transfer rod 22 transmit the change of the bellows 11 to the valve body 23.

The adjuster 18 is fitted to the upper opening of the case 13. The adjuster 18 adjusts the bonding force of the bellows 11. More specifically, the distance between the upper and lower allowances 15a and 15b or the length of the bellows 11 vary depending on the position of the adjuster 18. The change in the longitudinal direction or the elastic load of the bellows affects the control valve 1 characteristic (valve opening pressure). The conventional control valve 1 controls the characteristics of the control valve 1 by adjusting the position of the adjuster 18.

Since the machining cost of the bellows 11 is relatively expensive, the bellows presents a difficulty in lowering the manufacturing cost of the control valve 1.

In addition, in order to operate the above-mentioned conventional control valve 1 stably, it is preferable to maintain the pressure sensing chamber in a vacuum. However, the bellows 11 is soldered to the upper and lower sugars 15a and 15b, and volatile substances such as fluid generated by the soldering may flow into the pressure sensing chamber. Moreover, air bubbles or cavities generated by the solder cause a slow leak and change the degree of vacuum in the pressure sensing chamber. If the pressure inside the pressure sensing chamber changes, the accuracy of the control valve 1 is reduced. Instead of soldering, the bellows 11 can use the lazar to join the upper and lower sugars 15a and 15b. However, since the cost of the Raza welding apparatus is quite expensive, the manufacturing cost of the control valve 1 is increased, which is a problem.

An object of the present invention is to solve the above problems and to provide a control valve of high accuracy and relatively low cost.

1 is a cross-sectional view showing a control valve of a first embodiment according to the present invention.

2 is a sectional view showing a part of a control valve of a second embodiment according to the present invention.

3 is a sectional view showing a control valve of a third embodiment according to the present invention.

4 is a sectional view showing a control valve of a fourth embodiment according to the present invention.

5 is a sectional view showing a control valve of a fifth embodiment according to the present invention.

6 is a sectional view showing a control valve of a sixth embodiment according to the present invention.

7 is a cross-sectional view of a reversible displacement compressor with the control valve of FIG. 1.

8 is a cross-sectional view showing a conventional control valve.

Explanation of symbols on the main parts of the drawings

1: control valve 10: pressure sensing unit

11: bellows 18: adjuster

110: pressure detection unit 111: diaphragm

114: suture 116: pressure sensing spring

120: control valve 123: valve body

125: valve ball 127: valve chamber

132: suction element 134: plunger

135: solenoid spring 136: plunger sleeve

137: adjuster 139: solenoid seal

In order to achieve the above object, an embodiment of the present invention provides a control valve of a reversible displacement compressor. The reversible capacity compressor is connected to a crank chamber in a refrigerant gas suction passage through which refrigerant gas can flow even at a considerably low pressure, a discharge pressure region in which refrigerant gas compressed to a considerable pressure flows, a crank chamber connected to a cam, and a discharge pressure region. It includes a supply passage. The control valve includes a body connected to the valve body for opening and closing the valve groove connected to the supply passage and a pressure sensing unit fixed to the body to sense the pressure of the suction passage. The pressure sensing unit has a diaphragm and a first flange which move in accordance with the pressure of the suction passage, a second case having a first case which cooperates with the diaphragm to define the pressure sensing chamber and a second flange which cooperates with the first flange to support the diaphragm. Include the case.

Another embodiment is a control valve of a reversible displacement compressor including a suction passage through which refrigerant flows at a relatively low pressure, a discharge pressure region through which refrigerant gas compressed at a relatively high pressure flows, a crank chamber accommodating a cam, and a discharge pressure region Provides a supply passage to the crankcase. The control valve includes a pressure sensing unit for sensing the pressure in the suction passage. The pressure sensing unit includes a first membrane defining a pressure sensing chamber in cooperation with the diaphragm and having a diaphragm that moves in accordance with the pressure of the suction passage, and a second flange having a second flange which cooperates with the first flange to support the diaphragm. We include 2 cases. In addition, the control valve includes a body for receiving the valve body for opening and closing the valve hole connected to the supply passage and positioning the diaphragm by contact with the second case, and includes a positioning surface formed on the body.

Another embodiment of the present invention provides a method for producing a control valve of a reversible capacity compressor. The control valve includes a body for adjusting the valve body for changing the opening degree of the valve groove and a pressure sensing unit attached to the body to sense the pressure of the compressor. The method comprises: generating a positioning surface of the body at a position coinciding with a predetermined distance from the valve groove, adjusting a pair of donors for supporting both ends of the pressure sensing spring and the pressure sensing spring, and having a first flange; In the first case, the connecting member inside the second case having the second flange is adjusted, and the first case and the second case are fixed by clamping the diaphragm between the first flange and the second flange, and the diaphragm and the first case And setting the pressure in the pressure sensing chamber defined by the predetermined value, and attaching the pressure sensing unit to the body by bringing the second case into contact with the position surface of the body.

Hereinafter, exemplary embodiments of the present invention will be described with reference to the accompanying drawings. In addition, this embodiment is not intended to limit the scope of the present invention, but is presented by way of example only.

The control valve 1a according to the first embodiment of the present invention will be described with reference to the drawings.

As shown in FIG. 7, the control valve 1a is mounted to the rear housing member of the reversible capacity compressor 200. The compressor 200 enters into the refrigerant circuit 400 as a component. The compressor 200 compresses the refrigerant gas and supplies the refrigerant gas to the refrigerant circuit 400 from the discharge chambers 212a and 212b. After the compressed refrigerant gas is expanded in the refrigerant circuit 400, the refrigerant gas is recirculated to the suction passage 215 installed in the rear housing member 210. Thus, even at a relatively low pressure, the refrigerant gas flows in the suction passage 215.

The crank chamber 231 of the compressor 200 is inclined and fluidly supported in the axial direction of the drive shaft 250, the rotation support 251 fixed to the drive shaft 250, the drive shaft 250 is rotated by the pulley 201 The inclined plate 240 or cam plate is accommodated. The support arm 252 of the rotating support 251 supports the guide pin 241 of the inclined plate 240. The inclined plate 240 is connected by a pair of gods 242. The piston 260 reciprocates in the cylinder bore when the inclined plate rotates.

The stroke of the piston 260 changes according to the inclination angle of the inclined plate 240. The inclination angle of the inclined plate 240 changes in relation to the pressure of the crank chamber 231 (crank chamber pressure Pc). The blocking body 270 is pressed in the inclined plate direction and moves in the accommodation hole 222 according to the inclination angle of the inclined plate 240.

The suction chambers 211a and 211b and the discharge chambers 212a and 212b are formed in the rear housing member 210. When the piston 260 moves, the refrigerant gas flows from the suction chambers 211a and 211b to the cylinder bore 221 through the suction port 213. The refrigerant gas compressed by the piston 260 is discharged to the discharge chambers 212a and 212b through the discharge port 214. That is, the discharge chambers 212a and 212b form discharge pressure regions in which the refrigerant gas flows at a relatively high pressure (discharge pressure Pd).

The suction passage 215 is connected to the receiving hole 222, and is also connected to the suction chamber 211b by the through hole 216. When the inclined plate 240 moves the block 270 toward the rear housing member 210, the block closes the through hole 216. The discharge chamber 212b and the crank chamber 231 are connected to each other by the supply passages 218 and 219. The control valve 1a changes the opening degree of the supply passages 218 and 219.

Hereinafter, the control valve 1a will be described with reference to FIG. 1.

The control valve 1a includes a pressure sensing unit 110, a control valve unit 120, and a solenoid unit 130.

The pressure sensing unit 110 includes an upper case (first case) 113 having an upper flange 113b and a lower case (second case) 112 having a lower flange 112b. The pressure sensing member or the diaphragm 111 is provided between the lower flange 112b and the upper flange 113b. The diaphragm 111 and the upper case 113 define the pressure sensing chamber 119. The pressure sensing chamber 119 is maintained at a predetermined reference pressure (preferably almost vacuum). The sugar 115b is positioned on the diaphragm 111. The spring holder 115a includes a hollow tube portion 115c extending along the axis of the spring holder 115a. The pressure sensing spring 116 and the spring holder 115a supported by the sugar 115b press the sugar 115b toward the diaphragm 111. The upper case 113 includes a normal hole 113a or a pressure setting hole. The suture 114 seals the top hole 113a. The top hole 113a is circular, and the suture 114 is preferably spherical.

The connecting member or the pressure sensing shaft 117 is received in the lower case 112 in contact with the lower side of the diaphragm. The lower case 112 includes a connection protrusion 112c accommodated in the connection hole 121b of the body 121. It is formed in the suction pressure lower case 112 for introducing the hole (112a). When the control valve 1a is installed in the compressor 200, the pressure sensing unit 110 is exposed to the suction passage 215 of the compressor 200. Thus, the suction pressure Ps acts on the chamber 119a provided below the diaphragm 111 through the suction pressure introduction hole 112a. When the suction pressure Ps is relatively high, the diaphragm 111 moves upward in response to the pressure of the pressure sensing spring 116. On the contrary, when the suction pressure Ps is relatively low, the diaphragm 111 moves downward by the pressure and pressure difference of the pressure sensing spring 116. In other words, the diaphragm 111 changes in accordance with the suction pressure Ps.

The process of manufacturing the pressure sensing unit 110 will now be described. First, the spring holder 115a, the pressure sensing spring 116, and the sugar 115b are assembled together and accommodated in the upper case 113. The pressure sensing shaft 117 is accommodated in the lower case 112.

The diaphragm 111 is supported between the lower flange 112b and the upper flange 113b. In this state, the upper case 113 and the lower case 112 are integrated. Preferably, the cases 112 and 113 are connected to each other by sealing the outer periphery of the cases 112 and 113 by using plasma welding, laser welding, and beam welding.

Thereafter, the pressure sensing unit 110 is arranged in the atmosphere at a predetermined reference pressure. For example, the pressure sensing unit 110 is disposed in the pressure chamber at a predetermined pressure. The pressure in the pressure sensing chamber 119 is slowly equilibrated with the pressure in the pressure chamber by the top hole 113a and the hollow cavity 115c, and the pressure inside the pressure sensing chamber 119 is set to the reference pressure. In this state, the suture 114 closes the top hole 113a. The pressure sensing chamber 119 is sealed by welding the sealing body 114 to the upper case 113. After the coupling, a pressure leak test of the pressure sensing unit 110 is performed.

In the first embodiment, the pressure leakage test of the pressure sensing unit 110 is executed before the control valve 1a is manufactured. Moreover, although it is preferable that the pressure sensing chamber 119 is pressure-sensitive to almost vacuum, the gas of the reference pressure is filled in the pressure sensing chamber 119. In addition, the pressure sensing unit 110 may be assembled under a reduced pressure atmosphere.

The control valve unit 120 will be described below.

The valve hole 125 and the valve chamber 127 are formed in the body 121 of the control valve unit 120. The valve chamber 127 includes a valve body. The valve body 123 includes a cross section 123a corresponding to the top of the valve chamber 127. The body 121 includes a discharge pressure introduction port 127a disposed perpendicular to the axis of the body 121 and connected to the valve chamber 127. Referring to FIG. 7, the discharge pressure introduction port 127a is connected to the discharge chamber 212b of the compressor 200 by the supply passage 218. Thus, the discharge pressure Pd is introduced into the valve chamber 127 by the discharge pressure introduction port 127a. The body 121 includes a crank pressure introduction port 125a connected to the valve hole 125. The crank pressure introduction port 125a is connected to the crank chamber 231 of the compressor 200 by the supply passage 219.

The valve body 123 is connected to the pressure sensing shaft 117 by the pressure sensing rod 122. The pressure sensing rod 122 slides into the guide hole 121a. The pressure sensing rod 122 has an upper rod portion 122a having a diameter substantially the same as the inner diameter of the guide hole 121a, and a lower rod portion having a relatively small diameter formed between the valve body 123 and the upper rod portion 122a. 122b is provided. The lower rod part 122b allows the refrigerant gas to flow in the valve hole 125. The body 121 includes a connection groove 121b for receiving the connection protrusion 112c of the pressure sensing unit 110, a positioning surface 120b for supporting the flange of the lower case 112, and a pressure sensing unit 110. It includes a coupling piece (120a) for fixing. The positioning surface 120b is formed so that the space C between the diaphragm 111 and the top of the valve chamber 127 becomes a predetermined value. Coupling piece (120a) strengthens the coupling between the pressure sensing unit 110 and the control valve unit (120). The coupling piece 120a is engaged with the flange of the upper case 113 in a state where the flange of the lower case 112 is in contact with the positioning surface 120b. In this state, it is preferable that the lower end of the connection protrusion 112c is spaced apart from the bottom surface of the control groove 120b of the connection groove 121b.

The positioning surface 120b will be described below. The deformation of the diaphragm 111 is related to the valve opening pressure of the control valve 1a. Further, the repulsive force of the diaphragm 111 changes into a curved shape rather than a straight line according to the deformation degree of the diaphragm 111. Therefore, it is necessary to accurately adjust the initial degree of change of the diaphragm 111. In the first embodiment, when the pressure sensing unit 110 is coupled to the control valve unit 120, the interval between the top 125b and the positioning surface 120b is selected so that the diaphragm 111 is disposed at a predetermined position. do.

Hereinafter, the solenoid part will be described.

The solenoid portion 130 coupled to the body 121 has an adjuster fixed to a plunger sleeve having a lower opening, a movable core or a plunger 134, and a plunger sleeve 136. 137, and a fixed iron core or suction element 132 suitable for the upper opening of the plunger sleeve 136. Plunger sleeve 136, adjuster 137 and suction element 132 define solenoid chamber 139. The cylindrical coil 131 is disposed around the suction element 132 and the plunger 134. The coil 131 is connected to a driving circuit 184 that supplies an exciting current to the coil according to a command of the controller 183.

The solenoid rod guide 132b connecting the solenoid chamber 139 and the valve chamber 127 is disposed on the suction material 132. The solenoid rod 133 is integrally formed with the valve body 123 and moves in the axial direction from the solenoid rod guide 132b. The pressure of the solenoid spring 135 allows the lower end of the solenoid guide rod 133 to be adjacent to correspond to the plunger. Therefore, the plunger 134, the solenoid rod 133, and the valve body 123 move integrally.

The communication port 132a is formed at one side of the suction element 132. When the control valve 1a is installed in the compressor 200, a space 28 connected to the crank introduction port 125a is formed between the body 121 and the compressor (shown in FIG. 7). The solenoid chamber 139 is connected to the crank pressure introduction port 125a by the communication hole 132a of the suction element 132 and the communication hole 126 formed in the body and the space 28. The pressure of the solenoid chamber 139 is equal to the pressure of the valve hole 125. Plunger 134 includes a plunger hole 134a associated with the cavity. This allows the refrigerant gas to flow between the space above the plunger 134 and the space below the plunger 134.

Plunger 134 moves in plunger sleeve 136. The cavity is formed in the bottom of the plunger 134. A solenoid spring 135 that pushes the plunger 134 upward is disposed between the cavity of the plunger 134 and the adjuster 137. The adjuster 137 adjusts the pressing force (the degree of compression of the solenoid spring 135) of the solenoid spring 135.

Hereinafter, the adjustment of the solenoid spring 135 will be described.

First, the control valve 1a is arranged in the atmosphere of a predetermined reference pressure. For example, the control valve 1a is disposed inside the pressure sensing chamber. A tool (not shown) for moving the adjuster 137 is inserted through the adjusting hole 138 of the plunger sleeve 136. When the test suction pressure Ps and the test discharge pressure Pd are applied to the suction pressure introduction hole 112a and the discharge pressure introduction port 125a, respectively, the pressure of the crank pressure introduction port 125a is measured. The position of the adjuster 137 is adjusted by the tool so that the measurement reaches a predetermined value. The plunger sleeve 136 is then fastened to secure the adjuster 137 in the proper position. After the tool is removed from the adjusting hole 138, the adjusting hole 138 is closed by welding the suture 137b to the plunger sleeve 136. The adjustment of the solenoid spring 135 pressing force sets the characteristic of the control valve 1a as mentioned above.

After this, the operation of the control valve 1a will be described.

When the air conditioner switch 180 is operated and the temperature of the cabin sensed by the temperature sensor 181 exceeds the target temperature set by the temperature setter 182, the controller 183 commands the excitation of the coil. The driving circuit 184 supplies the exciting current to the coil 131 in response to the exciting command. When excited, the coil 131 allows the magnetic circuit member, which is the suction element 132 and the plunger 134, to form a magnetic circuit. The suction force is generated between the suction element 132 and the plunger 134 according to the degree of the excitation current. The plunger 134 is sucked by the suction element 132 and presses the valve body 123 to the upper side of the solenoid rod 133. The diaphragm 111 is moved in accordance with the change of the suction pressure Ps introduced by the suction pressure introduction hole 112a. The pressure sensing rod 122 transfers the movement of the diaphragm 111 to the valve body. Therefore, the opening degree of the control valve 1a (the opening degree of the valve hole 125) is determined by the balance between the pressing force of the solenoid portion 130 and the pressing force of the pressure sensing unit 110.

When the cooling load is large, the difference between the temperature sensed by the temperature sensor 181 and the set temperature set by the temperature setter 182 is large. When the sensed temperature is high, the controller 183 gradually raises the level of the excitation current directed to the drive circuit. In this case, the attraction force between the suction element 132 and the plunger 134 increases. This increases the force that reduces the opening of the valve hole 125. Therefore, the valve body 123 is moved to the open position or the closed position by the relatively low suction pressure Ps. In other words, when the excitation current is relatively high, the control valve 1a acts to maintain the suction pressure Ps at a relatively low level.

When the opening degree regulated by the valve body 123 is small, the refrigerant gas flowing through the supply passage 218 from the discharge chamber 212b to the crank chamber 231 is reduced. Meanwhile, the refrigerant gas flows from the crank chamber 231 to the suction chamber 211b through the line 220 and the pressure sensing port 223. Thus, the crankcase pressure Pc decreases. When the cooling load is large, the difference between the crank seal pressure Pc and the suction pressure Ps of the cylinder bore 221 is small. Thus, the inclination angle of the inclination plate 240 is large.

When the valve body 123 completely closes the valve hole 125, the supply passage 219 is blocked. Thus, the high pressure refrigerant gas inside the discharge chamber 212B is not supplied to the crank chamber 231. This makes the crank chamber pressure Pc completely equal to the pressure Ps of the suction chamber 211a. Thus, the inclination angle of the inclination plate 240 is maximized. The maximum inclination angle of the inclined plate is limited by the proximity between the regulation protrusion 251a of the rotary support 251 and the inclined plate 240. So the position is maximized.

On the contrary, when the difference between the temperature sensed by the temperature sensor 181 and the set temperature set by the temperature setter 182 is small, the cooling load is small. In this case, as the sensed temperature is gradually lowered, the controller 183 gradually reduces the degree of excitation current directed to the drive circuit 184. When the degree of the excitation current is relatively low, the suction force between the suction element 132 and the plunger 134 is weak. This reduces the force acting in the direction of reducing the opening degree regulated by the valve body 123. Thus, the valve body 123 is moved to the open position or the closed position by the relatively high suction pressure Ps. That is, by reducing the current degree, the control valve 1a is operated while maintaining the suction pressure Ps to a relatively high degree.

When the opening degree regulated by the valve body 123 is large, the flow of the refrigerant gas from the discharge chamber 212a to the crank chamber 231 is increased, and the crank chamber pressure Pc is increased. If the cooling load is small, the suction pressure Ps of the cylinder bore 221 is low. The difference between the pressure Pc of the crank chamber and the suction pressure Ps of the cylinder bore 221 is large. Therefore, the inclination angle of the inclination plate 240 is small.

If the temperature sensed by the temperature sensor 104 is lower than or equal to the set temperature, the controller 183 sends a command to the drive circuit 184 to remove the magnetization of the coil. When the excitation current provided to the coil 131 is removed, the suction force between the suction element 132 and the plunger 134 is removed. The valve body 123 moves to the position where the valve hole 125 is opened to the maximum. This provides a large amount of high pressure refrigerant gas from the discharge chamber 212b to the crank chamber 231 through the supply passage 219. The crankcase pressure Pc rises. In this state, the inclination angle of the inclined plate 240 gradually decreases.

Moreover, when the air conditioner switch 180 is turned off, the controller 183 instructs the driving circuit unit 184 to remove the magnetization of the coil. Also in this case, the inclination angle of the inclined plate 240 gradually decreases.

As described above, the control valve 1a operates in conjunction with the exciting current of the coil 131. That is, the control valve 1a changes the set value of the suction pressure Ps according to the exciting current. When the excitation current is high, the valve hole 125 opens at a relatively low suction pressure Ps. When the excitation current is low, the valve hole 125 opens at a relatively high suction pressure Ps. The compressor 200 maintains the suction pressure at the set value by changing the discharge amount.

The control valve 1a of the first embodiment has the following advantages.

The control valve 1a is provided with a diaphragm 111 which is manufactured at a lower cost than the conventional bellows 11. This reduces the production cost of the control valve 1a.

The junction between the positioning surface 120b and the lower flange sets the distance C between the diaphragm 111 and the valve hole 125 (normal 125b) to a predetermined value. The initial deformation degree (spring load) of the diaphragm 111 matches the design value. This makes it easy to set the characteristics of the control valve 1a and improves the accuracy of the control valve 1a.

The positioning surface 120b and the top 125b are formed in the body 121. Thus, the pressure sensing unit 110 and the control valve unit 120 are attached to set the interval C between the diaphragm 111 and the top 125b to a predetermined value. Thus, the accuracy of the control valve 1a is improved.

The top hole 113a is circular and the suture 114 is spherical. The suture 114 securely closes the normal hole. The sealing body 114 is welded with the upper case in a state covering the top hole 113a, so that the flux from the pressure sensing chamber 119 is prevented. Moreover, the sealing body 114 and the top hole 113a are easy to machine, and the production cost of the control valve 1a is reduced.

Since the lower case 112 is provided with the suction pressure introduction hole 112a, the suction pressure Ps certainly acts on the pressure sensing chamber 119 (horizontal membrane 111). Moreover, the suction pressure inlet 112a is easy to machine, so that the production cost of the control valve 1a is reduced.

Even when the suction pressure Ps is extremely high, the lower end of the spring support 115a is in contact with the sugar 115b to prevent the diaphragm 111 from changing excessively. Thus, breakage of the diaphragm 111 is prevented.

The hollow tube portion 115c is disposed in the space surrounded by the pressure sensing spring 116, so that the hollow tube portion 115c reduces the inclination of the pressure sensing spring 116. Thus, the contact between the sugar 115b and the upper case 113 is prevented. The diaphragm 111 is not affected by the frictional resistance that would otherwise occur between the sugar 115 and the upper case, and is accurately deformed according to the change in the suction pressure.

The control valves of the second to fifth embodiments of the present invention are described below.

Hereinafter will be described focusing on the differences between the embodiments compared to the control valve (1a) of FIG.

(Second embodiment)

Fig. 2 is a sectional view showing a part of the control valve 1b of the second embodiment of the present invention. The control valve part 120 does not include the positioning surface 120b and the coupling part 120a of FIG. Instead, the bottom of the connecting groove 121b functions as a positioning surface. More specifically, the size of the depth of the connection groove 121b and the length of the connection protrusion 112c is a predetermined value between the diaphragm and the valve port 125 (normal 125b), or the pressure sensing unit 110. When the lower end of the connection protrusion of the contact with the bottom surface of the connection groove 121b is selected so that the initial deformation of the diaphragm 111 is a design value.

The connection protrusion 112C is fixed to the connection groove 21b by, for example, applying a pressure to the contact groove 121b by applying pressure to the connection groove 121b or screwing the protrusion 112c into the contact groove 121b by screwing. .

(Third embodiment)

Fig. 3 is a sectional view showing the control valve 1c of the third embodiment of the present invention. The control valve 1c has an adjuster 137 installed in the solenoid part 130. The adjuster 137 includes a fastener 137a and an O-ring 152 formed on the side of the adjuster 137. The position of the adjuster 137 is adjusted to have the designed characteristics with the control valve 1c. The plunger sleeve 136 is sealed so that the plunger sleeve portion 136 can be engaged with the fastener 137a. This secures the adjuster 137 to the plunger sleeve 136. O-ring 152 attached to adjuster 137 seals the space between plunger sleeve 136 and adjuster 137.

(Example 4)

4 is a sectional view showing the control valve 1d of the fourth embodiment of the present invention. The control valve 1d includes an adjuster 137 installed in the solenoid portion 130. The adjuster 137 includes an engagement portion 137c and an O-ring 152 formed at the side of the adjuster 137. The adjuster 137 is fixed to the lower opening of the plunger sleeve 136 by screwing. The position of the adjuster 137 is adjusted so that the control valve 1d has the designed characteristic. The O-ring seals the space between the plunger sleeve 136 and the adjuster 137.

(Example 5)

5 is a sectional view showing a control valve 1e of a fifth embodiment of the present invention. The control valve 1e has an adjuster 137 installed in the solenoid part 130. The plunger sleeve 136 includes a large diameter portion 136a positioned around the plunger 134 and a small diameter portion 136b positioned below the large diameter portion 136a. The position of the adjuster 137d is adjusted so that the control valve 1d has a design characteristic. The adjuster 137d is welded to the small diameter portion 136b at the adjusted position. The space between the plunger sleeve 136 and the adjuster 137d is sealed by welding.

(Example 6)

Fig. 6 is a sectional view showing the control valve 1f of the sixth embodiment of the present invention. In the sixth embodiment, the plunger sleeve 136 has a closed bottom. The adjuster 137e is formed in the pressure sensing unit 110. More specifically, the adjuster 137e is fastened to the upper case 113. The adjuster 137e includes a fastener 137f formed on the side of the adjuster 137e and a hollow tube portion 137g extending along the axis of the adjuster 137e. Like the spring support 115a of FIG. 1, the adjuster 137e supports the upper end of the pressure sensing spring 116. The characteristics of the control valve are regulated as follows.

The tool is inserted through the top hole 113a and adjusts the position of the adjuster 137e so that the control valve 1f has the designed characteristic. A portion of the upper case 113 is fastened to the fastening groove 137f by sealing the upper case. This locks the adjuster in the adjusted position. The length or pressing force of the pressure sensing spring 116 is adjusted to regulate the characteristics of the control valve 1f. Thereafter, the suture 114 is welded to the upper case 113 by the process described by the first embodiment. This seals the pressure sensing chamber 119. In the sixth embodiment, the stationary hole 113a functions as a pressure setting hole and an adjustment hole.

The control valves 1b to 1f of the second to sixth embodiments have the same advantages as those of the first embodiment.

Although the embodiments of the present invention have been described with reference to the drawings, the present invention is not limited to the above and may be modified in the same form or within the scope of the claims.

Conventional control valves of compressors have used bellows. Since the machining cost of the bellows 11 is expensive, it is difficult to reduce the manufacturing price of the control valve 1.

In addition, in order to operate the above-mentioned conventional control valve 1 stably, it is preferable to maintain the pressure sensing chamber in a vacuum. However, the bellows 11 is soldered to the upper and lower sugars 15a and 15b, and volatile substances such as fluid generated by the soldering may flow into the pressure sensing chamber. Moreover, air bubbles or cavities generated by the solder cause a slow leak and change the degree of vacuum in the pressure sensing chamber. If the pressure inside the pressure sensing chamber changes, the accuracy of the control valve 1 is reduced. Instead of soldering, the bellows 11 can use the lazar to join the upper and lower sugars 15a and 15b. However, since the cost of the Raza welding apparatus is quite expensive, the manufacturing cost of the control valve 1 is increased, which is a problem. The present invention solves the above problems, it is possible to provide a control valve having a high accuracy and a relatively low price.

Claims (22)

A suction passage through which the refrigerant flows at low pressure; A discharge pressure region through which the refrigerant compressed at high pressure flows; A crank chamber to accommodate the cam 240; In the control valve of the reversible displacement compressor including a supply passage connecting the crank chamber and the discharge pressure region, A body accommodating a valve body for opening and closing a valve hole connected to a supply passage; A first case which senses the pressure of the suction passage and is fastened to the body, and has a diaphragm 111 and a first flange 113b which is changed according to the pressure of the suction passage, and defines a pressure sensing chamber together with the diaphragm; A pressure sensing unit including a second case having a second flange supporting the diaphragm in cooperation with the first flange; Control valve of the reversible displacement compressor comprising a. The method of claim 1, The first case is provided with a pressure setting hole for setting the pressure sensing chamber to a predetermined reference pressure, The control valve is a control valve of the reversible displacement compressor further comprises a sealing body for sealing the pressure setting hole. The method of claim 1, The body of the control valve of the reversible displacement compressor, characterized in that it comprises a positioning surface for determining the position of the diaphragm in contact with the second case. The method of claim 3, wherein The positioning surface is a control valve of the reversible displacement compressor, characterized in that formed so that the interval C between the diaphragm and the valve construction is determined to a predetermined value. The method of claim 3, wherein The body is a control valve of the reversible displacement compressor characterized in that it comprises a fastening piece for fixing the pressure sensing unit. The method of claim 5, The positioning surface is in contact with the second flange, The fastening piece is a control valve of the reversible displacement compressor, characterized in that fastened with the first flange. The method of claim 1, The diaphragm includes a first side surface in contact with the pressure sensing chamber and a second side surface opposite to the first side surface; The pressure sensing unit includes a pressure sensing spring for pressing the diaphragm toward the valve body and a pair of donors for supporting both ends of the pressure sensing spring; The control valve of the reversible displacement compressor, characterized in that the pressure sensing spring and the sugars are arranged in the pressure sensing chamber. The method of claim 7, wherein The second case has a control valve of the reversible displacement compressor, characterized in that the suction pressure introduction hole for applying the pressure of the suction passage on the second side of the diaphragm. The method of claim 1, The outer diameter of the first flange is welded with the outer diameter of the second flange control valve of the compressor. A reversible passage including a suction passage through which a low pressure refrigerant gas can flow, a discharge pressure zone through which a refrigerant gas compressed at high pressure can flow, and a supply passage connecting a crank chamber accommodating a cam, a discharge pressure chamber, and a discharge pressure region In the control valve of the displacement compressor, Pressure of the suction passage including a diaphragm which changes according to the pressure of the suction passage, a first case having a first flange and defining a pressure sensing chamber together with the diaphragm, and a second flange supporting the diaphragm together with the first flange. Pressure sensing unit for detecting; A control valve for a reversible displacement compressor including a body for receiving a valve body for opening and closing the valve hole connected to the supply passage, the body including a positioning surface formed on the body for determining the position of the diaphragm by contact with the second case. The method of claim 10, The positioning surface is a control valve of a reversible displacement compressor, characterized in that the gap between the diaphragm and the valve construction is formed to a predetermined value. The method of claim 10, Control valve of the reversible displacement compressor characterized in that the fastening piece is fixed to the pressure sensing unit formed on the body. The method of claim 12, The positioning surface is in contact with the second flange, The fastening piece is a control valve of the reversible displacement compressor, characterized in that fastened with the first flange. The method of claim 10, The control valve further includes a solenoid portion fixed to the body; The solenoid part adjusts the coil, a movable iron core for moving the valve body when the coil is excited, a spring for pressing the movable iron core toward the pressure sensing unit, a plunger sleeve engaged with the movable iron core, and a pressing force of the spring. A control valve of a reversible displacement compressor characterized by including a adjuster attached to the plunger sleeve and varying the characteristics of the control valve. The method of claim 14, The adjuster is sealed to the plunger sleeve and the control valve of the reversible displacement compressor, characterized in that fixed to the plunger sleeve. The method of claim 15, The plunger sleeve has an adjusting hole; The position of the adjuster is controlled by an adjustment hole; The solenoid portion includes a suture to close the control hole; And the seal is welded to the plunger sleeve after the adjuster is fixed to the plunger sleeve. The method of claim 14, The adjuster is a control valve of a reversible displacement compressor, characterized in that fixed to the plunger sleeve by welding. The method of claim 14, The adjuster is a control valve of a reversible displacement compressor, characterized in that the adjuster having a spring for changing the position of the adjuster in relation to the plunger sleeve. The method of claim 10, The pressure sensing unit presses the diaphragm against the diaphragm in the direction of the valve body, and the contacting diaphragm supports the one end of the pressure sensing spring, and supports the other end of the pressure sensing spring to adjust the pressure of the pressure sensing spring. Including an adjuster; The pressure sensing spring, the gold, and the adjuster is a control valve of the reversible displacement compressor, characterized in that arranged in the pressure sensing chamber. The method of claim 15, The first case has a pressure setting port, The position of the adjuster is adjusted by the pressure setting port, The pressure sensing unit further includes a seal for closing the pressure setting port, The sealing body is a control valve of the reversible displacement compressor, characterized in that the adjuster is fixed to the first case and then welded to the first case. In the manufacturing method of the control valve of the reversible displacement compressor comprising a body for receiving a valve body for changing the opening of the valve hole, and a pressure sensing unit for sensing the pressure of the compressor attached to the body, Forming a positioning surface on the body at a position coinciding with a predetermined distance from the valve hole; Receiving a pair of sugar and pressure sensing springs supporting both ends of the pressure sensing spring in the first case having the first flange; Receiving a connecting member in the second case having the second flange; Clamping the diaphragm between the first flange and the second flange to secure the first case and the second case; Setting a pressure in the pressure sensing chamber defined by the diaphragm and the first case to a predetermined pressure; And attaching the pressure sensing unit to the body by bringing the second case into contact with the positioning surface of the body. The method of claim 21, The first case includes a pressure setting hole, The pressure setting step includes the steps of depressurizing the pressure sensing chamber by the pressure setting hole, closing the pressure setting hole by the sealing body, and welding the sealing body with the first case. Method of manufacturing a control valve of a compressor.