JP2004100473A - Control valve for variable capacity type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To simplify the whole structure of a control valve and exactly open and close a valve element by completely transmitting the operations of a sensing part and a solenoid energizing part to the valve element. <P>SOLUTION: This control valve 200 for variable capacity type compressor includes the valve body 220; the solenoid energizing part 130 for sliding a plunger 133 with a magnetic force; and a sensing part 145 having a sensing body 145 and a stem 232d operated by the sensing body. In this constitution, a valve section 232a which opens and closes by connecting and disconnecting with a valve hole 225 of the valve body, a plunger body section 232c fixed on the plunger, and the stem 232d are formed integrally with each other. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a control valve for a variable displacement compressor used in an air conditioner of a vehicle or the like, and particularly to a control valve for a variable displacement compressor that controls supply of refrigerant gas in a crank chamber from a discharge pressure region as needed. The present invention relates to a control valve and a means for adjusting and setting sensitivity in a pressure sensing portion and a valve body structure.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, a variable displacement compressor having a cylinder, a piston, a swash plate and the like compresses and discharges a refrigerant gas of an air conditioner for an automobile as disclosed in, for example, Japanese Patent Application Laid-Open No. 9-268973. The variable displacement compressor is provided with a refrigerant gas passage communicating 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. Then, there is known one configured to change the discharge capacity. The pressure in the crank chamber is adjusted by supplying a 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.
[0003]
[Problems to be solved by the invention]
As a control valve for the variable displacement compressor, the present applicant has previously proposed Japanese Patent Application No. 2001-108951 (filed on April 6, 2001, hereinafter referred to as "prior application invention"). The above-mentioned prior invention (described later) has various functions and effects, but the sensitivity adjustment in the pressure-sensitive portion is performed by applying a tool (driver) to a driver groove formed in the back of the adjusting screw. The means to do is adopted. However, according to the above-described means, individually adjusting many control valves with a tool requires not only a separate tool but also a lot of trouble and may not be efficient.
Therefore, an object of the present invention is to provide a control valve for a variable displacement compressor according to the prior application relating to the control valve for a variable displacement compressor, in which the sensitivity adjusting means of a pressure sensing portion constituting the control valve is simplified and easily provided. Is to do.
Another object of the present invention is to simplify the configuration of the entire control valve and to accurately open and close the valve body by reliably transmitting the operations of the pressure sensing unit and the solenoid excitation unit to the valve body.
[0004]
[Means for Solving the Problems]
Then, in order to solve the above-mentioned problems, a control valve for a variable displacement compressor according to the present invention employs the following means.
A control valve for a variable displacement compressor according to claim 1, wherein the control valve for a variable displacement compressor includes a control valve main body, a solenoid exciting section, and a pressure sensing section having a pressure sensing element. The pressure-sensitive part is a coil assembly that allows the sensitivity of the pressure-sensitive body to be adjusted by an adjusting screw that is provided so as to be adjustable with respect to a frame supporting the pressure-sensitive part, and that constitutes a solenoid excitation part. The adjusting screw is operated by engaging an engaging portion attached to the adjusting screw with the adjusting screw.
[0005]
A control valve for a variable displacement compressor according to a second aspect of the present invention is the control valve for a variable displacement compressor according to the first aspect, wherein a connector of a solenoid exciting unit is integrally formed of a synthetic resin with the coil assembly. Features.
A control valve for a variable displacement compressor according to claim 3 is the control valve for a variable displacement compressor according to claim 1 or 2, wherein a bellows is disposed as the pressure sensing element, and the pressure sensing section is disposed. The supporting frame is constituted by a suction element, and the bellows is extended and contracted by an adjusting screw provided to be able to advance and retreat with respect to the suction element.
[0006]
According to a fourth aspect of the present invention, in the control valve for a variable displacement compressor, the bellows is expanded and contracted by rotating a coil assembly or a connector with respect to the suction element. .
[0007]
A control valve for a variable displacement compressor according to claim 5, comprising a control valve main body having a valve main body, a solenoid exciting unit for sliding a plunger by magnetic force, a bellows and a stem operated by the bellows. And a control valve for a variable displacement compressor comprising: a pressure-sensitive section, wherein the sensitivity of the bellows is adjusted by an adjusting screw provided so as to be able to advance and retreat with respect to a frame supporting the pressure-sensitive section. In addition to being adjustable, an engaging portion attached to a coil assembly constituting a solenoid exciting portion is engaged with an adjusting screw so that the adjusting screw can be operated, and the frame supporting the pressure-sensitive portion is It is constituted by a suction element, and the bellows can be extended and contracted by an adjusting screw provided so as to be able to advance and retreat with respect to the suction element, and further, A valve body contacting away the valve hole of Kiben body, a plunger integral portion fixed to the plunger, characterized in that an integral and the stem.
[0008]
A control valve for a variable displacement compressor according to a sixth aspect is the control valve for a variable displacement compressor according to the first aspect, wherein the valve body which is separated from and brought into contact with the valve hole of the valve body and the plunger are slid by magnetic force. A control valve for a variable displacement compressor including a solenoid exciting section to be operated, and a pressure sensing section having a pressure sensing element and a stem operated by the pressure sensing element, the valve being fixed to the plunger. The plunger integral part and the stem are integrated.
The control valve for a variable displacement type compressor according to claim 7 is the control valve for a variable displacement type compressor according to claim 5 or 6, wherein the valve body, the plunger integrated portion, and the stem are: It is characterized by being composed of an integral object.
[0009]
BEST MODE FOR CARRYING OUT THE INVENTION
Embodiment 1
Hereinafter, a first embodiment of the present invention will be described. First, each embodiment of a control valve for a variable displacement compressor according to the prior application will be described with reference to FIGS. FIGS. 2 and 3 show the variable displacement compressor 1 including the control valve 100 of the first embodiment. FIG. 2 shows a state where the discharge passage of the variable displacement compressor 1 is open. FIG. 3 is a longitudinal sectional view showing a state in which the discharge passage is closed.
[0010]
As shown in FIG. 2, a rear housing 3 is fixed to one end face of a cylinder block 2 of the variable displacement compressor 1 via a valve plate 2a, and a 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 a circumferential direction around a shaft (rotating shaft) 5. A piston 7 is slidably housed in each of the cylinder bores 6.
[0011]
A crank chamber 8 is formed in the front housing 4, and a swash plate 10 is housed in the crank chamber 8. A shoe 50 that supports the spherical end portion 11a of the connecting rod 11 so as to be relatively rotatable is held by a retainer 53 on the sliding surface 10a of the swash plate 10. The retainer 53 is mounted on the boss 10b of the swash plate 10 via a radial bearing 55, and is rotatable relative to the swash plate 10.
The radial bearing 55 is retained by the boss 10b by a stopper 54 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 tip end surface of the one end 11a of the connecting rod 11 so as to be relatively rollable, and a washer 52 that supports the rear end surface of the one end 11a of the connecting rod 11 so as to be relatively rollable. Have been.
[0012]
A discharge chamber 12 and a suction chamber 13 are formed in the rear housing 3. The suction chamber 13 is arranged so as to surround the discharge chamber 12. The rear housing 3 is provided with a suction port (not shown) communicating with an outlet of an evaporator (not shown). FIG. 2 shows a state where the discharge passage 39 is open, and FIG. 3 shows a state where the discharge passage 39 is closed.
A spool valve (discharge control valve) 31 is provided in the middle of a discharge passage 39 communicating the discharge chamber 12 and the discharge port 1a, and the discharge passage 39 includes a passage 39a formed in the rear housing 3, A passage 39b formed in the valve plate 2a, and the passage 39b communicates with a discharge port 1a formed in the cylinder block 2.
[0013]
A spring (biasing member) 32 is accommodated in the bottomed cylindrical spool valve 31, and one end of the spring 32 abuts on a stopper 56 fixed to the rear housing 3 by 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 via a passage 34.
[0014]
On one side (upper side) of the spool valve 31, the urging 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 equal to or less than a predetermined value, the spool valve 31 moves in the valve closing direction to shut off the discharge passage 39, and the lower side of 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.
[0015]
The discharge chamber 12 and the crank chamber 8 communicate with each other via a 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 thermal load is large, the second passage 57 is shut off by energizing the solenoid 131A of the control valve 100 so that the valve body 132 is seated, and when the thermal load is small, the energization of the solenoid 131A is stopped to shut off the valve body 132. It is released by moving away from the valve seat 125a. The operation of the control valve 100 is controlled by a computer (not shown).
[0016]
The suction chamber 13 and the crank chamber 8 communicate with each other via 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 bearing housing space 60b, a passage 60c formed in the shaft 5, a rear bearing housing space 60d formed in the cylinder block 2, and a cylinder. It is composed of a passage 58b of the block 2 and an orifice 58a of the valve plate 2a.
Therefore, the passage 58b of the cylinder block 2 and the orifice 58a of the valve plate 2a constitute a part of the first passage 58 and a part of the third passage 60.
[0017]
A female screw 61 is formed on the inner peripheral surface of the rear end of the passage 60c, and a screw 62 is screwed into the female screw 61. An orifice (first orifice) 62a is formed in the screw 62, and the passage area of the orifice 62a is equal to the passage area of the second orifice 58a in the valve plate 2a constituting a part of the first passage 58. Less than.
Accordingly, 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 significantly reduced, the refrigerant in the crank chamber 8 is sucked through the third passage 60. It is led to the chamber 13.
[0018]
The valve plate 2a is provided with a discharge port 16 for communicating the compression chamber 82 with the discharge chamber 12 and a suction port 15 for communicating the compression chamber 82 with the suction chamber 13 at predetermined intervals in the circumferential direction. ing. The discharge port 16 is opened and closed by a discharge valve 17. The discharge valve 17 is fixed to a rear housing side end surface of the valve plate 2 a together with a valve retainer 18 by bolts 19 and nuts 20. 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 2a and the cylinder block 2.
[0019]
A rear end of the shaft 5 is rotatably supported by a radial bearing (rear bearing) 24 and a thrust bearing (rear bearing) 25 housed in a rear bearing housing space 60 d of the cylinder block 2. The front end is rotatably supported by a radial bearing (front bearing) 26 housed in a front bearing housing space 60b of the front housing 4. In addition to the radial bearing 26, a shaft seal 46 is housed in the bearing housing space 60b on the front side.
[0020]
A female screw 1b is provided at the center of the cylinder block 2, and an adjust 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 end of the shaft 5.
[0021]
A thrust flange 40 for transmitting 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 33a. 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 mounted on the shaft 5 so as to slide and tilt.
[0022]
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, it is constituted. The longitudinal axis of the guide groove 10f is inclined at a predetermined angle with respect to the front surface 10c of the swash plate 10. The spherical portion 43a of the rod 43 is fitted into the guide groove 10f so as to be relatively slidable.
[0023]
Next, a control valve (hereinafter, referred to as a “control valve”) 100 for a variable displacement compressor according to the first embodiment will be described in detail. FIG. 4 is an enlarged longitudinal sectional view showing a state where the control valve 100 is incorporated in the variable displacement compressor 1, and FIG. 5 is an enlarged longitudinal sectional view showing details of the control valve of FIG.
[0024]
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 spaces 84, 85 of the rear housing 3. It is arranged in a state where airtightness is maintained.
As shown in FIG. 5, the control valve 100 includes a control valve main body 120, a solenoid exciting unit 130, and a pressure sensing unit 145. The solenoid exciting unit 130 is disposed at a central portion, and the solenoid The control valve main body 120 and the pressure sensing section 145 are arranged on both sides of the excitation section 130.
[0025]
The solenoid excitation 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 vertically by excitation of the solenoid 131A, a suction element 141, and a stem 141 138, and the plunger chamber 130 a in which the plunger 133 is disposed communicates with a suction refrigerant port 129 provided in the control valve main body 120.
The pressure sensing portion 145 is disposed below the solenoid housing 161 and includes a pressure sensing chamber 145a therein. The pressure sensing chamber 145a includes a bellows 146 that operates the plunger 133 via a stem 138 and a spring. 159.
[0026]
The control valve 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. Are 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. In the center of the stopper 124, a pressure chamber 151 having a bottomed vertical hole having a cross-sectional area equal to that of the valve hole 125 is formed in the center thereof so as to face the valve hole 125. The chamber 151 is formed as a spring storage chamber 151a, and a valve closing spring 127 for urging the valve body 132 toward the bottom surface of the valve chamber 123 is disposed at the bottom.
[0027]
The valve body 132 is a rod-shaped body including 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 132b is disposed in the valve chamber 123, and the small diameter portion 132c is connected to the crank chamber (crank chamber pressure Pc) in the valve hole. The lower portion 132d is fitted and supported in the control valve main body 120, and the lower end thereof is inserted into the plunger chamber 130a through which the refrigerant gas having the suction pressure Ps is guided, and is opposed to the plunger 133. In contact. When the plunger 133 moves up and down, the valve body 132 moves up and down, and the enlarged valve body 132b of the valve body 132 adjusts the gap between the valve seat 125a on the upper surface of the valve hole 125.
[0028]
Then, the low-temperature suction pressure Ps guided to the plunger chamber 130a is guided to a pressure-sensitive portion 145 described later, and also 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 via an O-ring 131b of a protrusion 131a provided on a side portion 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. Is trying to cool down.
[0029]
As shown in FIG. 5, a plunger 133 for contacting and fixing the valve body 132 is disposed inside the solenoid housing 131 which is crimped to the control valve main body 120. The end is slidably supported by a pipe 136 which is in close contact with the end via an O-ring 134a.
An upper portion 138A of the stem 138 is inserted into and fixed to an accommodation hole 137 formed at a lower end portion of the plunger 133, and a lower portion 138B of the stem 138 is connected to the lower end accommodation hole from the upper end accommodation hole 142 side of the suction element 141. It is slidably supported by 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 receiving hole 142 of the suction element 141 to bias the plunger 133 in a direction away from the suction element 141 side.
[0030]
In the lower part 138B of the stem 138, the stopper 147 side of the pair of stoppers 147, 148 inside the bellows 146 disposed in the pressure-sensitive chamber 145a is attached so as to be able to freely contact with and separate from the flange 149 of the stopper 147. A spring 150 for urging the stopper 147 in a direction away from the suction element 141 is provided between the suction element 141 and the lower end housing hole 143.
[0031]
The suction pressure Ps in the pressure-sensitive chamber 145 a increases, and the displacement position of the bellows 146 is regulated by the contraction of the bellows 146 and the pair of stoppers 147, 148 abutting against each other. It is set to be smaller than the maximum fitting amount of the lower portion 138B and the stopper 147 of the bellows 146. A cord 158 capable of supplying an exciting current controlled by a control computer (not shown) is connected to the solenoid 131A (FIG. 4).
[0032]
Further, as shown in the drawing, the stopper 124 is provided with a lateral hole 153 communicating with the pressure chamber 151, and the lateral hole 153 is provided with a gap 139 formed by the stopper 124 and the control valve body 120. The pressure chamber 151 communicates with the pressure chamber 151. On the other hand, the control valve body 120 is provided with a cancel hole 155 that communicates the gap 139 with the plunger chamber 130a into which the refrigerant gas having the suction pressure Ps flows.
[0033]
Next, the operation of the variable displacement compressor 1 and the control valve 100 of the prior application will be described. The rotational power of the vehicle-mounted engine is constantly 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. Then, the swash plate 10 is rotated.
[0034]
The rotation of the swash plate 10 causes the shoe 50 to relatively rotate on the sliding surface 10 a 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 suction, compression, and discharge of the refrigerant gas are sequentially performed by the change, and the refrigerant gas having a capacity corresponding to the inclination angle of the swash plate 10 is discharged.
[0035]
First, when the heat load increases, the flow of the refrigerant gas from the discharge chamber 12 into the crank chamber 8 is prevented, 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 decreases. When the total force generated on the rear surface of the piston 7 is smaller than the total force generated on the front surface (top surface) of the piston 7, the inclination angle of the swash plate 10 increases.
[0036]
Here, the pressure in the discharge chamber 12 increases, 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 becomes: 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 to open the discharge passage 39 (FIG. 2). The refrigerant gas in the discharge chamber 12 flows out of the discharge port 1a to the condenser 88. When the inclination angle of the swash plate 10 is changed from the minimum to the 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 discharged. Since the air flows into the suction chamber through one passage 58, the pressure in the crank chamber 8 decreases.
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.
[0037]
As described above, when the heat load increases and the solenoid 131A of the control valve 100 is excited, the plunger 133 is retracted toward the suction element 141, and the valve body 132 that is in contact with the plunger 133 becomes the valve hole 125. In the closing direction, and the inflow of the crank chamber 8 is blocked.
On the other hand, the low-temperature refrigerant gas is guided from the passage 80 side communicating with the suction chamber 13 to the pressure-sensitive part 145 via the suction refrigerant port 129 of the control valve body 120 and the plunger chamber 130a, and the bellows of the pressure-sensitive part 145 146 is displaced based on the pressure of the refrigerant gas, which is the suction pressure Ps of the suction chamber 13, and the displacement is transmitted to the valve body 132 via 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 attraction force of the solenoid 131A, the urging force of the bellows 146, and the urging forces of the valve closing spring 127 and the valve opening spring 144. You.
[0038]
When the pressure (suction pressure Ps) in the pressure-sensitive chamber 145a increases, the bellows 146 contracts, which coincides with the suction direction of the plunger 133 by the solenoid 131A. The movement of the valve hole 132 follows, and the opening degree of the valve hole 125 decreases. As a result, the amount of high-pressure refrigerant gas guided 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).
When the pressure in the pressure sensing chamber 145a decreases, the bellows 146 expands due to the restoring force of the spring 159 and the bellows 146 itself, and the valve body 132 moves in a direction to increase the opening degree of the valve hole 125. The amount of the high-pressure refrigerant gas guided 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.
[0039]
On the other hand, when the heat load is reduced, the high-pressure refrigerant gas flows out of the discharge chamber 12 into the crank chamber 8, and the pressure in the crank chamber 8 increases. The force generated on the rear surface of the piston 7 during the compression stroke increases, and the total force generated on the rear surface of the piston 7 exceeds the total force generated on the front surface of the piston 7. Becomes smaller.
[0040]
Here, the pressure difference between the discharge chamber 12 and the crank chamber 8 becomes equal to or less than a predetermined value, 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 flows from the discharge port 1 a to the condenser 88. Gas outflow is prevented.
When the inclination angle of the swash plate 10 is reduced from the maximum to the minimum, the boss portion 10b of the swash plate 10 substantially closes the hole 58c of the ring 9 and greatly reduces the passage cross-sectional area of the first passage 58. Since the refrigerant gas in the chamber 8 flows into the suction chamber 13 through the third passage 60, an excessive increase in the pressure in the crank chamber 8 is suppressed, and the refrigerant gas can be circulated in the compressor 1.
[0041]
That is, in this case, the refrigerant gas returns to the suction chamber 13 again via 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 in which the pressure of the crank chamber 8 is applied to one of the spool valves 31 serving as the 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. The spring 32 having a relatively small spring force that is urged in the valve direction is used. When the heat load is reduced and the pressure in the discharge chamber 12 gradually decreases, the minimum piston stroke (extremely low load) is obtained, and the swash plate 10 is used. The spool valve 31 is kept open until the pressure decreases the passage area of the first passage 58.
[0042]
As described above, 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 suction element 141 by the urging 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 body 120, and the inflow into the crank chamber 8 is promoted.
[0043]
Here, when the pressure in the pressure sensing 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 moves with respect to the stopper 147 of the bellows 146. The bellows 146 does not affect the valve body 132 because the bellows 146 is attached so as to be able to freely contact and separate.
[0044]
As described above, the control valve 100 according to the present embodiment includes a solenoid exciting unit 130 having a plunger 133 that moves in the vertical direction when the solenoid 131A is excited in the center, and a stem 138 and the like below the solenoid exciting unit 130. A pressure-sensitive portion 145 provided with a bellows 146 interlocked with the plunger 133 through the control valve body 120 having a valve chamber 123 provided above the solenoid housing 131 with a valve body 132 interlocked with the plunger 133. Therefore, the pressure sensing chamber 145a and the solenoid 131A are disposed close to each other, and the point of action of the suction of the solenoid 131A and the point of action of the bellows 146 are close to each other, so that the valve body 132 and the stem 138 constituting the operating rod are formed. It is possible to minimize backlash during movement in the valve closing direction.
[0045]
FIG. 6 is a longitudinal sectional view showing details of a second embodiment of the control valve of the invention of the prior application. The present embodiment is characterized mainly by the structure of the suction element and the pressure-sensitive portion, and this point will be described in detail below.
The suction element 141 of the control valve 100 for a variable displacement compressor according to the present embodiment includes a cylindrical portion 141b engaged with the inside of the solenoid exciting portion 130 and a lid press-fitted at an upper end of the cylindrical portion 141b. The pressure sensor 145 includes a portion 141c and an adjusting screw 157 that is engaged below the cylindrical portion 141b.
[0046]
That is, the cylindrical portion 141b is engaged with the adjusting screw 157 from below, while the stopper 148, the spring 159, the bellows 146, the flange 149 of the stopper, and the spring 150 are loaded from above. Then, the lid 141c is press-fitted at the upper end of the cylindrical portion 141b. Since the joint between the tubular portion 141b and the pipe 136 is TIG-welded, and the pressure-sensitive chamber 145a is formed inside the suction element 141, the control valve 100 can be made compact by shortening in the longitudinal axis direction. Can be planned. The bellows is expanded and contracted by the adjusting screw 157.
[0047]
Further, 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 the refrigerant having the suction pressure Ps into the pressure-sensitive portion 145 in the longitudinal direction of the outer surface thereof. A slit 133a is provided. Further, 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 formed through the slit 133a of the plunger 133 and the stem 140. The refrigerant having the suction pressure Ps therein is introduced into the pressure sensing portion 145 or the like.
[0048]
Further, unlike the first embodiment described above, the control valve main body 120 and the solenoid exciter 130 of the present embodiment are caulked and connected on the control valve main body 120 side via a pipe 136 and a spacer 156. Note that a seal is provided between the control valve main body 120 and the solenoid excitation unit 130 by a packing 134b.
[0049]
By the way, in the embodiment shown in FIG. 6, the sensitivity adjustment in the pressure sensing portion is performed by applying a tool (driver) to a driver groove 157b formed in the adjusting screw 157 and rotating the adjusting screw 157. However, according to the above means, individually adjusting many control valves with a tool requires not only a separate tool but also a lot of trouble and is not efficient. Therefore, the following embodiment is provided in order to simplify and facilitate the sensitivity adjusting means of the pressure-sensitive portion constituting the control valve.
[0050]
The control valve according to the first embodiment of the present invention is particularly shown in FIGS. 1 (A) and 1 (B) and FIGS. 7 (A), 7 (B) and 7 (C). 1 that are the same as those shown in FIG. 6 represent the same members.
In the control valve according to the second aspect of the present invention, the pressure-sensitive portion 145 is provided with an adjusting screw 157 that can be advanced and retracted with respect to a frame supporting the pressure-sensitive portion 145, that is, the suction element 141. By 157, the sensitivity can be adjusted by expanding and contracting the pressure-sensitive body, that is, the bellows 146. Further, the adjusting screw 157 is engaged with an engaging portion 181 attached to the coil assembly 180 constituting the solenoid exciting portion 130.
[0051]
In the above configuration, the control valve rotates the adjusting screw 157 by rotating the coil assembly 180 with respect to the suction element 141, and causes the bellows 146 to expand and contract. The connector 182 is integrally formed (molded) of the coil assembly 180 with a synthetic resin.
[0052]
In addition, since the coil assembly 180 and the connector 182 hermetically seal the solenoid exciting unit 130 together with the solenoid housing 161, the embodiment of the present invention is also desirable from the viewpoint of sealing properties such as waterproof and airtightness of the solenoid exciting unit 130. Things.
The present invention can be applied to other pressure-sensitive bodies that do not use bellows. Needless to say, the present invention can be applied to a case where the frame supporting the pressure-sensitive portion 145 is not the suction element 141 but another frame.
[0053]
Embodiment 2
By the way, in the first embodiment, various improvements have been made to simplify and facilitate the sensitivity adjusting means of the pressure sensing part constituting the control valve for the variable displacement compressor. That is, since the vertical movement of the valve body 132 is transmitted as the vertical movement of the valve body 132 via the stem 138 and the plunger 133 which are independent members separate from the valve body 132, the pressure-sensitive part 145 and the solenoid excitation part The operation of 130 may not be reliably transmitted to the valve body 132, and the reliability of the opening and closing operation of the valve body 132 may be reduced.
[0054]
Therefore, in the second embodiment, it is an object to ensure that the operations of the pressure sensing unit 145 and the solenoid excitation unit 130 in the first embodiment are transmitted to the valve body, and the stem 138 which is a component of the first embodiment is used. , Plunger 133 and valve body 132 are integrated into a single body, simplifying the configuration of the entire control valve, and reliably transmitting the operation of the pressure sensing section 145 and the solenoid exciting section 130 to the valve body, and The purpose is to make the opening / closing operation accurate.
[0055]
Next, a second embodiment will be described in detail with reference to FIG. In the second embodiment, the same reference numerals as in FIG. 1 denote parts having the same configuration as in the first embodiment, and a description thereof will be omitted.
The control valve 200 according to the second embodiment includes a valve body 220, a solenoid exciting unit 130 that slides the plunger 133 by magnetic force, a pressure sensing unit 145 including a pressure sensing body (bellows) 146, and the solenoid exciting unit 130. A valve element 232 operated by the pressure sensing part 145. The valve body 232 includes a valve portion 232a that is separated from and connected to the valve body 232 to open and close the valve hole 225, a small-diameter portion 232e located in the valve hole 225, a plunger integrated portion 232c fixed to the plunger 133, and a stem 232d. , And is composed of an integral object.
[0056]
The valve portion 232a is located in a valve chamber 223 formed at the upper end of the valve body 220, and opens and closes a valve hole 225 of a valve seat 225a formed at a lower portion of the valve chamber 223 from an upper side. Note that the valve chamber 223 communicates with the crank chamber 8. When the plunger 133 is attracted to the suction element 141 (moves downward) by the magnetic force of the solenoid excitation unit 130, the valve part 232a comes into contact with the valve hole 225 from the upper surface thereof and is closed.
[0057]
The operation of the second embodiment is basically the same as that of the first embodiment, except that the valve body 232 includes a valve portion 232a, a small-diameter portion 232e, a plunger integrated portion 232c fixed to the plunger 133, Since it is constituted as an integral body composed of the stem 232d, the operation from the solenoid exciting unit 130 and the pressure sensing element 146 is directly transmitted to the valve unit 232a, so that the opening and closing of the valve unit 232a is smooth and accurate. .
[0058]
Further, since a member corresponding to the valve-closing spring 127 of the first embodiment and a configuration corresponding to the receiving portion of the valve-closing spring 127 are not required for the valve body 220, the overall configuration is simplified and the movable member is provided. Therefore, troubles are reduced, and maintenance of the control valve 100 as a whole becomes easy.
[0059]
【The invention's effect】
As can be understood from the above description, according to the control valve for the variable displacement type cotton wool press according to the present invention, the adjusting screw is rotated by rotating the coil assembly with respect to the suction element, and the bellows is rotated. Can be adjusted to adjust the pressure sensitivity. In addition, since the connector is formed integrally with the coil assembly, the adjusting screw can be easily rotated, and the sealing performance of the coil portion is improved, so that there is less fear of corrosion.
Further, not only the followability of the valve body to the plunger and the pressure sensing portion is improved, but also the valve closing spring and the spring receiving of the valve closing spring are not required, and the configuration is simplified.
[Brief description of the drawings]
FIG. 1 is a vertical sectional view (A) and a detailed view (B) of a main part of a control valve according to an embodiment of the present invention.
FIG. 2 is a longitudinal sectional view showing a state in which a discharge passage of the variable displacement compressor according to the invention of the prior application of the invention is opened.
FIG. 3 is a longitudinal sectional view showing a state in which a discharge passage of the variable displacement compressor of FIG. 2 is closed.
FIG. 4 is an enlarged longitudinal sectional view of a control valve for the variable displacement compressor of FIG. 2;
FIG. 5 is an enlarged longitudinal sectional view of another example of the embodiment of FIG. 4;
FIG. 6 is an explanatory view of a main part of the control valve of FIG. 1 before (A) and after assembling (B).
FIG. 7 is a front view (A), a side view (B), and a bottom view (C) of the control valve shown in FIG. 1;
FIG. 8 is an enlarged vertical sectional view of the second embodiment.
[Explanation of symbols]
Ps ··· Suction pressure Pc ··· Crank chamber pressure Pd ··· Discharge pressure
1 .... variable capacity compressor 1a ... discharge port 1b ... female screw
2. Cylinder block 2a Valve plate
3. Rear housing 4. Front housing
5. Shaft (rotary axis) 6. Cylinder bore
7, piston 8, crank chamber 9, ring (annular body) 10, swash plate 10a, sliding surface 10b, boss
10c front face 10e bracket 10f straight guide groove
11. Connecting rod 11a One end 11b Other end
12. Discharge chamber 13. Suction chamber 15. Suction port
16. Discharge port 17 Discharge valve 18 Valve retainer
19 Bolt 20 Nut 21 Inlet valve
24 · · · radial bearing (rear bearing) 25 · · · thrust bearing (rear bearing)
26 .. Radial bearings (front side bearings)
31 Spool valve (discharge control valve) 32 Spring (biasing member)
33 internal space 33a thrust bearing 34 passage
39 discharge passage 39a passage 39b passage
40 thrust flange 40a swash plate side surface 41 hinge mechanism
43 ... Rod 43a ... Spherical part 45 ... Screw
46 ・ ・ Shaft seal 50 ・ ・ Shoe 51 ・ ・ Shoe body
52 ・ ・ Washer 53 ・ ・ Retainer 54 ・ ・ Stopper
55 radial bearing 56 stopper 59 cap
57 second passage 58 first passage
58a orifice (second orifice) 58b passage
58c ... hole 59 ... cap
60 third passage 60a passage 60b front bearing housing space
60c passage 60d rear bearing accommodation space
61 ... female screw 62 ... screw
62a orifice (first orifice)
80, 81 ... passage 82 ... compression chamber 83 ... adjustment nut
84, 85 space (inlet pressure introduction space) 88 condenser
100 ... control valve (for variable displacement compressor)
120... Control valve body 121a, 121b... O-ring
123: valve chamber 124: stopper 125: valve hole
125a valve seat 126 discharge refrigerant port 127 valve closing spring
127 ・ ・ Valve closing spring 128 ・ ・ Crank chamber refrigerant port
129 ·· Suction refrigerant port
130 ... solenoid exciting unit 130a ... plunger chamber
131 ・ ・ solenoid housing 131A ・ ・ solenoid
131a ··· Projection 131b ··· O-ring
132: valve element 132a: upper part 132b: enlarged valve element
132c-small diameter part 132d-lower part
133: plunger 133a: slit 133f: refrigerant outlet hole
134a O-ring 134b Packing 136 Pipe
137 ··· Accommodation hole
138 ··· stem 138A · · · upper 138B · · · lower
139 ··· Void 140 ··· Stem
141 ... suction element 141b ... tubular part 141c ... lid part
142 ··· Upper end accommodation hole 143 ··· Lower end accommodation hole 144 ··· Valve opening spring
145: Pressure-sensitive part 145a: Pressure-sensitive chamber 146: Bellows
147, 148 Stopper 149 Flange 150 Spring
151: pressure chamber 151a: spring storage chamber 153: horizontal hole
155 ··· Cancel hole 156 ··· Spacer
157 ・ ・ Adjusting screw
157a Screw part 157b Driver groove
158 Code 159 Spring 161 Solenoid housing 180 Coil assembly 181 Engagement part 182 Connector
200 control valve (Example 2)
220 ・ ・ ・ Valve body
223: Valve chamber 225: Valve hole 225a: Valve seat
232: valve element 232a: valve section 232b: valve stem section
232c ・ ・ Plunger integrated part 232d ・ ・ Stem
232e small diameter part

Claims (7)

In a control valve for a variable displacement compressor including a control valve body, a solenoid exciting unit, and a pressure sensing unit having a pressure sensing body,
The pressure-sensitive part is a coil assembly that allows the sensitivity of the pressure-sensitive body to be adjusted by an adjusting screw that is provided so as to be adjustable with respect to a frame supporting the pressure-sensitive part, and that constitutes a solenoid excitation part. A control valve for a variable displacement compressor, characterized in that an engaging portion attached to (1) is engaged with an adjusting screw to operate the adjusting screw. 2. The control valve for a variable displacement compressor according to claim 1, wherein a connector of a solenoid exciting unit is integrally formed with the coil assembly by a synthetic resin. A bellows is arranged as the pressure-sensitive body, and a frame supporting the pressure-sensitive portion is constituted by a suction element, and the bellows is expanded and contracted by an adjusting screw provided to be able to advance and retreat with respect to the suction element. The control valve for a variable displacement compressor according to claim 1 or 2, wherein: The control valve for a variable displacement compressor according to claim 3, wherein the bellows is extended or contracted by rotating a coil assembly or a connector with respect to the suction element. A control valve for a variable displacement compressor including a control valve main body having a valve main body, a solenoid exciting part for sliding a plunger by magnetic force, and a pressure sensitive part having a bellows and a stem operated by the bellows. ,
The pressure-sensitive part is provided with a coil assembly that constitutes a solenoid excitation part, while adjusting the sensitivity of the bellows by an adjusting screw that is provided so as to be able to advance and retreat with respect to a frame supporting the pressure-sensitive part. The engaging portion is engaged with the adjusting screw so that the adjusting screw can be operated, and the frame supporting the pressure-sensitive portion is constituted by a suction element, and is provided so as to be able to advance and retreat with respect to the suction element. The bellows can be extended and contracted by the adjusting screw provided, and furthermore, a valve body which is separated from and brought into contact with the valve hole of the valve body, a plunger integrated portion fixed to the plunger, and the stem are integrated. Control valve for variable displacement compressor. A variable displacement type including: a valve body that is separated from and brought into contact with a valve hole of a valve body; a solenoid exciting unit that slides a plunger by a magnetic force; 2. The control valve for a variable displacement compressor according to claim 1, wherein the valve body, a plunger integral part fixed to the plunger, and the stem are integrated in the control valve for the compressor. 7. The control valve for a variable displacement compressor according to claim 5, wherein the valve body, the plunger integrated portion, and the stem are integrally formed.

Images