JP4247225B2 - Control valve for variable capacity compressor - Google Patents

Description

  The present invention relates to a control valve for a variable displacement compressor used in an air conditioner such as a vehicle, and more particularly to a variable displacement compressor that controls the supply of refrigerant gas in a crank chamber from a discharge pressure region as necessary. The present invention relates to a control valve for a variable displacement compressor in which a pressure sensitive part is formed on the inner upper part of a suction element of the control valve.

  Conventionally, a variable capacity compressor having a cylinder, piston, swash plate, etc. is used for compressing and discharging refrigerant gas of an automotive air conditioner as disclosed in, for example, Japanese Patent Laid-Open No. 9-268973. The variable displacement compressor includes a refrigerant gas passage that communicates the discharge pressure region and the crank chamber, and changes the inclination angle of the swash plate by adjusting the pressure in the crank chamber to thereby change the discharge capacity. What is configured to change is known. For adjusting the pressure in the crank chamber, means for supplying high-pressure compressed refrigerant gas from the discharge pressure region to the crank chamber by adjusting the opening of a control valve provided in the middle of the refrigerant gas passage is employed.

  As a control valve for the variable displacement compressor, the present applicant has previously proposed the invention of Japanese Patent Application No. 2001-108951 (filed on April 6, 2001) (see Japanese Patent Application Laid-Open No. 2002-303262). Yes.

An object of the present invention is to provide a solenoid valve having a solenoid and an attractor provided on a lower side of the plunger in the proposed control valve, and winding an exciting coil of the solenoid exciting unit inside the attractor . By incorporating a pressure sensitive part in the rotation region, the pressure sensitive part does not protrude outside the solenoid exciting part, and the solenoid exciting part can be miniaturized , thereby miniaturizing the control valve. There is something you can do.

In order to solve the above-described problems, a control valve for a variable displacement compressor according to the present invention is provided for a variable displacement compressor including a solenoid exciter and a control valve body disposed above the solenoid exciter. a control valve, wherein the solenoid excitation unit is equipped with a suction element provided on the lower side of the plunger and the plunger moves in the vertical direction, of the inner portion of the suction element, the exciting coil of the solenoid excitation part A pressure - sensitive part is built in the winding region .

Further, in the control valve for a variable displacement compressor according to a specific aspect of the present invention, the pressure sensitive part is built in an upper part of the suction element, and the pressure sensitive part further comprises: A pressure sensitive chamber is provided in the interior, and a bellows and a spring for operating the plunger are arranged in the pressure sensitive chamber.

  According to the control valve for a variable displacement compressor according to the present invention, the solenoid exciting portion includes a plunger that moves in the vertical direction and an attractor provided below the plunger, and an upper portion of the attractor. Since the pressure sensitive part is formed on the inside, the pressure sensitive part hardly protrudes outside the solenoid exciting part, and the control valve can be miniaturized by miniaturizing the solenoid exciting part.

  Hereinafter, a first embodiment of the present invention will be described with reference to FIG. 1. First, referring to FIGS. 2 to 5, a control valve for a variable capacity compressor of the prior art as a premise thereof will be described. To do. 2 and 3 show the variable displacement compressor 1 in which the control valve 100 according to the first embodiment can be provided. FIG. 2 shows a state in which the discharge passage of the variable displacement compressor 1 is opened. FIG. 3 is a longitudinal sectional view showing a state in which the discharge passage is closed.

  As shown in FIG. 2, the rear housing 3 is fixed to one end face of the cylinder block 2 of the variable capacity compressor 1 via a valve plate 2a, and the front housing 4 is fixed to the other end face. The cylinder block 2 is provided with a plurality of cylinder bores 6 at predetermined intervals in the circumferential direction around a shaft (rotating shaft) 5. Each piston 7 is slidably accommodated in the cylinder bore 6.

  A crank chamber 8 is formed in the front housing 4, and a swash plate 10 is accommodated in the crank chamber 8. On the sliding surface 10 a of the swash plate 10, a shoe 50 that supports the spherical one end portion 11 a of the connecting rod 11 so as to be capable of relative rolling is held by a retainer 53. The retainer 53 is attached to the boss portion 10 b of the swash plate 10 via the radial bearing 55 and is rotatable relative to the swash plate 10. The radial bearing 55 is secured to the boss 10b by a stopper 54 that is fixed by a screw 45. The other end 11 b of the connecting rod 11 is fixed to the piston 7. The shoe 50 includes a shoe main body 51 that supports the front end surface of the one end portion 11a of the connecting rod 11 so as to allow relative rolling, and a washer 52 that supports the rear end surface of the one end portion 11a of the connecting rod 11 so as to allow relative rolling. Has been.

  A discharge chamber 12 and a suction chamber 13 are formed in the rear housing 3. The suction chamber 13 is disposed so as to surround the discharge chamber 12. The rear housing 3 is provided with a suction port (not shown) that leads to an outlet of an evaporator (not shown). FIG. 2 shows a state in which the discharge passage 39 is opened, and FIG. 3 shows a state in which the discharge passage 39 is closed. A spool valve (discharge control valve) 31 is provided in the middle of the discharge passage 39 that connects the discharge chamber 12 and the discharge port 1a. The discharge passage 39 includes a passage 39a formed in the rear housing 3, The passage 39b is formed in the valve plate 2a, and the passage 39b communicates with the discharge port 1a formed in the cylinder block 2.

  A spring (biasing member) 32 is accommodated in the bottomed cylindrical spool valve 31, and one end of the spring 32 abuts against a stopper 56 fixed to the rear housing 3 with a cap 59. The end is in contact with the bottom surface of the spool valve 31. An internal space 33 of the spool valve 31 communicates with the crank chamber 8 through a passage 34.

  On one side (upper side) of the spool valve 31, the biasing force of the spring 32 and the pressure of the crank chamber 8 act in the valve closing direction (the direction in which the valve opening decreases). On the other hand, when the spool valve 31 is opened, the discharge port 1a and the discharge chamber 12 communicate with each other via the discharge passage 39 (see FIG. 2). The pressure of the discharge port 1a and the pressure of the discharge chamber 12 act in the valve opening direction (the direction in which the valve opening increases). However, when the pressure difference between the crank chamber 8 and the discharge port 1a becomes a predetermined value or less, the spool valve 31 moves in the valve closing direction to block the discharge passage 39, and the discharge chamber 39 is located below the spool valve 31. Only 12 pressures act in the valve opening direction. That is, the pressure of the discharge port 1a does not act on the lower side of the spool valve 31.

  The discharge chamber 12 and the crank chamber 8 communicate with each other via the second passage 57. In the middle of the passage 57, a control valve 100 of the present embodiment, which will be described in detail later, is provided below the center position of the compressor 1. When the heat load is large, the second passage 57 is blocked by the valve element 132 being seated by energization of the solenoid 131A of the control valve 100, and when the heat load is small, the valve element 132 is blocked by energization of the solenoid 131A. It is released by leaving the valve seat 125a. The operation of the control valve 100 is controlled by a computer (not shown).

  The suction chamber 13 and the crank chamber 8 communicate with each other through a first passage 58. The passage 58 includes an orifice (second orifice) 58 a formed in the valve plate 2 a, a passage 58 b formed in the cylinder block 2, and a hole formed in a ring (annular body) 9 fixed to the shaft 5. 58c. The suction chamber 13 and the crank chamber 8 communicate with each other via a third passage 60. The passage 60 includes a passage 60a formed in the front housing 4, a front-side bearing housing space 60b, a passage 60c formed in the shaft 5, a rear-side bearing housing space 60d formed in the cylinder block 2, and a cylinder. It is comprised by the channel | path 58b of the block 2, and the orifice 58a of the valve plate 2a. Therefore, the passage 58 b of the cylinder block 2 and the orifice 58 a of the valve plate 2 a constitute a part of the first passage 58 and a part of the third passage 60.

  A female screw 61 is formed on the inner peripheral surface of the rear end portion of the passage 60c, and a screw 62 is screwed into the female screw 61. An orifice (first orifice) 62 a is formed in the screw 62, and the passage area of the orifice 62 a is the passage area of the second orifice 58 a in the valve plate 2 a constituting a part of the first passage 58. Smaller than. Accordingly, the refrigerant in the crank chamber 8 is sucked through the third passage 60 only when the boss portion 10b of the swash plate 10 substantially closes the hole 58c of the ring 9 and the passage sectional area of the first passage 58 is greatly reduced. Guided to chamber 13.

  The valve plate 2a is provided with a discharge port 16 for communicating the compression chamber 82 and the discharge chamber 12, and a suction port 15 for communicating the compression chamber 82 and the suction chamber 13, respectively, at predetermined intervals in the circumferential direction. ing. The discharge port 16 is opened and closed by a discharge valve 17, and the discharge valve 17 is fixed to a rear housing side end surface of the valve plate 2a by a bolt 19 and a nut 20 together with a valve presser 18. On the other hand, the suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is disposed between the valve plate 2 a and the cylinder block 2.

  The rear side end portion of the shaft 5 is rotatably supported by a radial bearing (rear side bearing) 24 and a thrust bearing (rear side bearing) 25 housed in the rear side bearing housing space 60 d of the cylinder block 2. The front side end is rotatably supported by a radial bearing (front side bearing) 26 accommodated in the front side bearing accommodation space 60b of the front housing 4. In addition to the radial bearing 26, a shaft seal 46 is accommodated in the bearing housing space 60b on the front side.

  A female screw 1b is provided at the center of the cylinder block 2, and an adjusting nut 83 is screwed into the female screw 1b. By tightening the adjustment nut 83, a preload is applied to the shaft 5 via the thrust bearing 25. A pulley (not shown) is fixed to the front side end of the shaft 5.

  A thrust flange 40 for transmitting the rotation of the shaft 5 to the swash plate 10 is fixed to the shaft 5, and the thrust flange 40 is supported on the inner wall surface of the front housing 4 via a thrust bearing 33 a. The thrust flange 40 and the swash plate 10 are connected via a hinge mechanism 41, and the swash plate 10 can be inclined with respect to a virtual plane perpendicular to the shaft 5. The swash plate 10 is attached to the shaft 5 so as to be slidable and tiltable.

  The hinge mechanism 41 includes a bracket 10e provided on the front surface 10c of the swash plate 10, a linear guide groove 10f provided on the bracket 10e, and a rod 43 screwed to the swash plate side surface 40a of the thrust flange 40. And is composed of. The longitudinal axis of the guide groove 10 f is inclined at a predetermined angle with respect to the front surface 10 c of the swash plate 10. The spherical portion 43a of the rod 43 is fitted in the guide groove 10f so as to be relatively slidable.

  Next, FIG. 4 is a longitudinal sectional view showing a state in which a control valve for a variable displacement compressor (hereinafter referred to as “control valve”) 100 is incorporated in the variable displacement compressor 1, and FIG. It is a longitudinal cross-sectional view which shows the detail of a control valve.

  The control valve 100 shown in FIG. 4 is provided on the rear housing 3 side of the variable displacement compressor 1 shown in FIGS. 2 and 3, and O-rings 121 a, 121 b, 131 b are provided in the spaces 84, 85 of the rear housing 3. It is arrange | positioned in the state which maintained airtightness. As shown in FIG. 5, the control valve 100 is formed of a control valve main body 120, a solenoid exciting part 130, and a pressure sensing part 145, and the solenoid exciting part 130 is disposed at the center, and the solenoid The control valve main body 120 and the pressure sensitive part 145 are arranged on both sides of the exciting part 130.

  The solenoid exciting unit 130 includes a solenoid housing 131 on the outer periphery thereof. Inside the solenoid housing 131, a solenoid 131A, a plunger 133 that moves up and down by the excitation of the solenoid 131A, an attractor 141, and a stem 138, and the plunger chamber 130a in which the plunger 133 is disposed communicates with an intake refrigerant port 129 provided in the control valve main body 120. The pressure-sensitive portion 145 is disposed below the solenoid housing 161 and includes a pressure-sensitive chamber 145a. The pressure-sensitive chamber 145a includes a bellows 146 that operates the plunger 133 via a stem 138 and the like, and a spring. 159.

  The control valve main body 120 includes a valve chamber 123, and a valve body 132 that is opened and closed by the plunger 133 is disposed in the valve chamber 123. The valve chamber 123 has a refrigerant gas having a high discharge pressure Pd. Is guided through the passage 81 and the discharge refrigerant port 126. A valve hole 125 communicating with the crank chamber refrigerant port 128 is formed in the bottom surface of the valve chamber 123, and a space above the valve chamber 123 is closed by a stopper 124. The stopper 124 is formed with a bottomed vertical hole pressure chamber 151 having a cross-sectional area equal to the valve hole 125 at the center thereof, and further, the pressure of the bottomed vertical hole. The chamber 151 is formed as a spring storage chamber 151 a, and a valve closing spring 127 that urges the valve body 132 toward the bottom surface of the valve chamber 123 is disposed at the bottom of the chamber 151.

  The valve body 132 is a rod-shaped body composed of an upper part 132a, an enlarged valve body part 132b, a small diameter part 132c, and a lower part 132d. The upper part 132a and the lower part 132d have the same cross-sectional area as the valve hole 125. 132a is fitted and supported by a stopper 124 having a pressure chamber 151, the enlarged valve body portion 132b is disposed in the valve chamber 123, and the small diameter portion 132c is formed in the crank chamber (crank chamber pressure Pc) in the valve hole. Opposing to the communicating crank chamber refrigerant port 128, the lower portion 132d is fitted and supported in the control valve main body 120, and the lower end portion thereof is inserted into the plunger chamber 130a into which the refrigerant gas having the suction pressure Ps is guided to the plunger 133. Touching. When the plunger 133 moves up and down, the valve body 132 moves up and down, and the enlarged valve body portion 132b of the valve body 132 adjusts a gap between the valve seat 125a on the upper surface of the valve hole 125.

  Then, the low-temperature suction pressure Ps guided to the plunger chamber 130a is guided into a pressure sensing portion 145 described later, and is also guided to a suction pressure introduction space 85 between the rear housing 3 and the solenoid housing 131 (FIG. 3). ). The suction pressure introduction space 85 is sealed through an O-ring 131b of a protrusion 131a provided on the side of the solenoid housing 131, and the entire side surface of the solenoid housing 131 is cooled by a low-temperature refrigerant gas from the suction chamber 13 side. The cooling is aimed at.

  As shown in FIG. 5, a plunger 133 that contacts and fixes the valve body 132 is disposed inside the solenoid housing 131 that is caulked and coupled to the control valve body 120, and the plunger 133 is connected to the control valve body 120. It is slidably supported by a pipe 136 that is in close contact with the end portion via an O-ring 134a. The upper portion 138A of the stem 138 is inserted and fixed in the accommodation hole 137 formed in the lower end portion of the plunger 133, and the lower portion 138B of the stem 138 is inserted into the lower end portion accommodation hole from the upper end accommodation hole 142 side of the suction element 141. It is slidably supported with respect to the suction element 141 in a state of protruding toward the 143 side. A valve opening spring 144 is provided between the plunger 133 and the upper end accommodation hole 142 of the suction element 141 to bias the plunger 133 in a direction away from the suction element 141 side.

  Further, the stopper 147 side of the pair of stoppers 147 and 148 in the bellows 146 disposed in the pressure sensing chamber 145a is detachably attached to the lower portion 138B of the stem 138, and the flange 149 of the stopper 147 is connected to the flange 149. A spring 150 is provided between the lower end receiving hole 143 on the suction element 141 side and biases the stopper 147 away from the suction element 141 side.

  The suction pressure Ps in the pressure sensing chamber 145a is increased and the pair of stoppers 147 and 148 are brought into contact with each other due to the contraction of the bellows 146, whereby the displacement position of the bellows 146 is regulated. It is set to be smaller than the maximum fitting amount between the lower portion 138B and the stopper 147 of the bellows 146. The solenoid 131A is connected to a cord 158 that can supply an exciting current controlled by a control computer (not shown) (FIG. 4).

  Further, as shown in the figure, the stopper 124 is provided with a lateral hole 153 communicating with the pressure chamber 151, and the lateral hole 153 is formed by the gap 139 formed by the stopper 124 and the control valve main body 120, and the The pressure chamber 151 communicates with the pressure chamber 151. On the other hand, the control valve main body 120 is provided with a cancel hole 155 that communicates the gap portion 139 and the plunger chamber 130a into which the refrigerant gas having the suction pressure Ps flows.

  Next, the operation of the variable displacement compressor 1 and the control valve 100 will be described. The rotational power of the in-vehicle engine is always transmitted from the pulley (not shown) to the shaft 5 via a belt (not shown), and the rotational force of the shaft 5 is transmitted to the swash plate 10 via the thrust flange 40 and the hinge mechanism 41. The swash plate 10 is rotated.

  As the swash plate 10 rotates, the shoe 50 rotates relative to the sliding surface 10a of the swash plate 10 and is converted into a linear reciprocating motion of the piston 7. As a result, the volume of the compression chamber 82 in the cylinder bore 6 changes. The refrigerant gas is sequentially sucked, compressed, and discharged by the change, and the refrigerant gas having a capacity corresponding to the inclination angle of the swash plate 10 is discharged.

  First, when the heat load increases, the refrigerant gas is prevented from flowing from the discharge chamber 12 to the crank chamber 8, the pressure in the crank chamber 8 is low, and the force generated on the rear surface of the piston 7 during the compression stroke is reduced. When the total force generated on the rear surface of the piston 7 is less than the total force generated on the front surface (top surface) of the piston 7, the inclination angle of the swash plate 10 is increased.

  Here, the pressure in the discharge chamber 12 becomes high, the pressure difference between the discharge chamber 12 and the crank chamber 8 becomes a predetermined value or more, and the pressure of the refrigerant gas in the discharge chamber 12 acting on the lower side of the spool valve 31 is When the combined pressure of the refrigerant gas pressure in the crank chamber 8 acting on the upper side of the spool valve 31 and the urging force of the spring 32 is overcome, the spool valve 31 moves in the valve opening direction and the discharge passage 39 opens (FIG. 2). The refrigerant gas in the discharge chamber 12 flows out from the discharge port 1a to the condenser 88. When the inclination angle of the swash plate 10 is from minimum to maximum, the boss portion 10b of the swash plate 10 is separated from the hole 58c of the ring 9, the first passage 58 is fully opened, and the refrigerant gas in the crank chamber 8 is Since the air flows into the suction chamber via the one passage 58, a pressure drop in the crank chamber 8 occurs. Further, when the passage area of the first passage 58 is maximized, the refrigerant gas hardly flows from the third passage 60 to the suction chamber 13.

  As described above, when the heat load increases and the solenoid 131A of the control valve 100 is excited, the plunger 133 is drawn to the attractor 141 side, and the valve body 132 that is in contact with the plunger 133 has the valve hole 125. Is moved in the closing direction, and the inflow of the crank chamber 8 is prevented. On the other hand, the low-temperature refrigerant gas is led from the side of the passage 80 communicating with the suction chamber 13 to the pressure sensing part 145 through the suction refrigerant port 129 and the plunger chamber 130a of the control valve body 120, and the bellows of the pressure sensing part 145 146 is displaced based on the pressure of the refrigerant gas that is the suction pressure Ps of the suction chamber 13, and the displacement is transmitted to the valve body 132 through the stem 138 and the plunger 133. That is, the opening position of the valve body 132 with respect to the valve hole 125 is determined by the attractive force of the solenoid 131A, the urging force of the bellows 146, and the urging force of the valve closing spring 127 and the valve opening spring 144. The

  When the pressure in the pressure sensing chamber 145a (suction pressure Ps) increases, the bellows 146 contracts, which coincides with the direction in which the plunger 133 is sucked by the solenoid 131A. The movement of 132 follows, and the opening degree of the valve hole 125 decreases. As a result, the amount of high-pressure refrigerant gas introduced from the discharge chamber 12 into the valve chamber 123 decreases (the crank chamber pressure Pc decreases), and the inclination angle of the swash plate 10 increases (FIG. 2). Further, when the pressure in the pressure sensing chamber 145a is lowered, the bellows 146 is extended by the restoring force of the spring 159 and the bellows 146 itself, and the valve element 132 moves in a direction to increase the opening degree of the valve hole 125. The amount of high-pressure refrigerant gas introduced into the valve chamber 123 increases (the crank chamber pressure Pc increases), and the inclination angle of the swash plate 10 in the state of FIG. 2 decreases.

  On the other hand, when the heat load is reduced, the high-pressure refrigerant gas flows out from the discharge chamber 12 to the crank chamber 8, and the pressure in the crank chamber 8 increases. Then, the force generated on the rear surface of the piston 7 during the compression stroke is increased, and the sum of the forces generated on the rear surface of the piston 7 exceeds the sum of the forces generated on the front surface of the piston 7, whereby the inclination angle of the swash plate 10 is increased. Becomes smaller.

  Here, the pressure difference between the discharge chamber 12 and the crank chamber 8 becomes a predetermined value or less, and the resultant force of the pressure of the crank chamber 8 acting on the upper side of the spool valve 31 and the urging force of the spring 32 is When the pressure of the refrigerant gas in the discharge chamber 12 acting on the lower side is overcome, the spool valve 31 moves in the valve closing direction to block the discharge passage 39 (FIG. 3), and the refrigerant from the discharge port 1a to the condenser 88 Gas outflow is blocked. When the inclination angle of the swash plate 10 is minimum to maximum, the boss portion 10b of the swash plate 10 substantially closes the hole 58c of the ring 9, and the passage sectional area of the first passage 58 is greatly reduced. Since the refrigerant gas in the chamber 8 flows to the suction chamber 13 through the third passage 60, an excessive pressure rise in the crank chamber 8 is suppressed, and the refrigerant gas can be circulated in the compressor 1.

  That is, in this case, the refrigerant gas returns to the suction chamber 13 again through the suction chamber 13, the compression chamber 82, the discharge chamber 12, the second passage 57, the crank chamber 8, and the third passage 60. In the present embodiment, a structure is adopted in which the pressure of the crank chamber 8 is applied to one of the spool valves 31 as a discharge control valve and the pressure of the discharge chamber 12 is applied to the other of the spool valves 31, and the spool valve 31 is closed. A spring 32 having a relatively small spring force biased in the valve direction is used. When the thermal load is reduced and the pressure in the discharge chamber 12 gradually decreases, the minimum piston stroke (extremely low load) is obtained. The spool valve 31 is kept open until the passage area of the first passage 58 is reduced.

  Thus, when the heat load is reduced and the solenoid 131A is demagnetized, the suction to the plunger 133 disappears, and the plunger 133 is separated from the attractor 141 side by the biasing force of the valve opening spring 144. The valve body 132 moves in a direction to open the valve hole 125 of the control valve main body 120, and the inflow into the crank chamber 8 is promoted.

  Here, when the pressure in the pressure-sensitive portion 145 increases, the bellows 146 contracts and the opening of the valve body 132 decreases, but the lower portion 138B of the stem 138 is in contact with the stopper 147 of the bellows 146. Since it is detachably attached, the displacement of the bellows 146 does not affect the valve body 132.

  As described above, the control valve 100 includes the solenoid exciter 130 having the plunger 133 that moves in the vertical direction by the excitation of the solenoid 131A in the center, and the stem 138 and the like below the solenoid exciter 130. It is formed by a pressure sensing part 145 having a bellows 146 interlocked with the plunger 133 and a control valve body 120 having a valve chamber 123 having a valve body 132 etc. interlocking with the plunger 133 on the upper side of the solenoid housing 131. Therefore, the pressure sensing chamber 145a and the solenoid 131A are disposed close to each other, the action point due to the suction of the solenoid 131A approaches the action point due to the bellows 146, and the valve body 132 and stem 138 constituting the operating rod are closed. The backlash when moving to can be minimized.

  Next, a control valve according to a first embodiment of the present invention will be described with reference to FIG. In the first embodiment of the present invention shown in FIG. 1, members having the same reference numerals as those shown in FIGS. 2 to 5 have the same configuration.

  In the control valve for the variable displacement compressor according to this embodiment, a pipe holder 170 is attached to the outer periphery of a pipe 136 having a flange 136a attached in the stator 131B of the solenoid exciting part 130. The control valve main body 120 is attached via the above. Further, the solenoid housing 161 constituting the solenoid exciting unit 130 is fitted on the pipe holder 170. In this case, preferably, as shown in FIG. 1, the pipe holder 170 may be configured as an integral body including a cylindrical portion 171 serving as a portion attached to the pipe 136 and a flange-shaped flange portion 172.

  With this configuration, the value of the moment of inertia of the pipe holder 170 becomes extremely large. As a result, even if the pipe holder 170 has a relatively small shape, it can be a strong reinforcing member for the pipe 136. Further, since the flange-shaped flange portion 172 is formed, the control valve main body 120 and the solenoid housing 161 can be easily positioned with respect to each other and can be easily mounted. The integrated body is disposed along the outer periphery of the pipe 136, and the end of the solenoid housing 161 is press-fitted or caulked to the outer periphery of the cylindrical portion 171, and the control valve main body 120 is attached to the flange portion 172. Is to be worn.

  By the above means, the solenoid exciting part 130 and the control valve main body 120 are directly connected via the pipe holder 170, so that the pipe holder 170 receives vibration stress such as bending and twisting applied to the pipe 136. Thus, the load applied to the pipe 136 is extremely small.

Furthermore, in the control valve for the variable displacement compressor, the pressure sensitive part 145 is formed on the inner upper part of the suction element 141 provided on the lower side of the plunger 133, so that the pressure sensitive part is a solenoid exciting part. The control valve can be reduced in size by reducing the size of the solenoid exciting unit 130 without projecting to the outside of the 130.
FIG. 6 is a longitudinal sectional view showing details of the control valve according to the second embodiment of the present invention. The attracting element 141 of the control valve 100 includes a cylindrical portion 141b that is engaged with the inside of the solenoid exciting portion 130, a lid portion 141c that is press-fitted at the upper end of the cylindrical portion 141b, and the cylindrical portion 141b. It is comprised from the adjusting screw 157 engaged by the lower side, and the pressure sensitive part 145 is provided in the inner side enclosed with these.

That is, the cylindrical portion 141b is engaged with the adjusting screw 157 from the lower side, while the stopper 148, the spring 159, the bellows 146, the stopper flange 149, and the spring 150 are loaded from the upper side. Then, the lid portion 141c is press-fitted at the upper end of the cylindrical portion 141b. The junction between the cylindrical portion 141b and the pipe 136 is TIG welded, pressure sensitive chamber 145a is, of the inner portion of the suction element 141, since it is incorporated in the winding region of the excitation coil of the solenoid excitation part 130, The control valve 100 can be made compact by shortening the longitudinal axis direction. Note that the adjustment of the bellows 146 can be adjusted by the adjusting screw 157.

  In addition, the plunger 133 of the present embodiment is provided with a refrigerant vent hole 133f in the longitudinal direction of the inside thereof, and introduces a refrigerant having a suction pressure Ps into the pressure-sensitive portion 145 in the longitudinal direction of the outer surface thereof. A slit 133a is provided. Furthermore, the stem 140 used in the control valve 100 of the present embodiment has a substantially half-moon shaped cross section, and the plunger chamber 130a is inserted through the slit 133a and the stem 140 of the plunger 133. The refrigerant having the suction pressure Ps inside is introduced into the pressure sensing unit 145.

Further, in the control valve 100 of the present invention, the pressure sensitive part 145 is formed on the inner upper part of the suction element 141 provided on the lower side of the plunger 133, so that the pressure sensitive part is outside the solenoid exciting part 130. The control valve can be downsized by reducing the size of the solenoid exciting unit 130.
Furthermore, unlike the first embodiment described above, the control valve main body 120 and the solenoid excitation unit 130 of the present embodiment are coupled by caulking the control valve main body 120 side via a pipe 136 and a spacer 156. A seal 134b is used between the control valve main body 120 and the solenoid exciting part 130.

The principal part longitudinal cross-sectional view (A) and principal part detail drawing of the control valve of 1st embodiment of this invention. FIG. 2 is a longitudinal sectional view showing a state in which a discharge passage of a variable displacement compressor that is a prior art and is a premise of the first embodiment of FIG. 1 is opened. FIG. 3 is a longitudinal sectional view showing a state where a discharge passage of the variable displacement compressor of FIG. 2 is closed. FIG. 3 is an enlarged longitudinal sectional view of a control valve for a variable displacement compressor in FIG. 2. FIG. 5 is a detailed longitudinal sectional view of the control valve of FIG. 4. The expanded longitudinal cross-sectional view of the control valve of 2nd embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 Control valve for variable capacity compressors 120 Control valve body 130 Solenoid excitation part 133 Plunger 141 Suction element 145 Pressure sensing part 145a Pressure sensing chamber 146 Bellows 159 Spring

Claims (3)

A control valve for a variable capacity compressor, comprising a solenoid excitation part and a control valve body arranged above the solenoid excitation part,
The solenoid exciting part includes a plunger that moves in the vertical direction and an attractor provided on the lower side of the plunger,
The inner part of the suction element, the control valve for a variable capacity compressor, wherein a pressure sensing portion is built into the winding region of the excitation coil of the solenoid excitation part. 2. The control valve for a variable displacement compressor according to claim 1, wherein the pressure sensitive part is built in an upper portion of the suction element.   3. The variable according to claim 1, wherein the pressure-sensitive portion includes a pressure-sensitive chamber therein, and a bellows and a spring for operating the plunger are disposed in the pressure-sensitive chamber. Control valve for capacity compressor.

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