JP2003148338A - Control valve for variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a control valve for a variable displacement compressor capable of preventing leakage of refrigerant gas to a crankcase when the valve is fully closed. SOLUTION: This control valve for the variable displacement compressor has a first passage 38 extending in the moving direction of a valve element 32, and second passages 37a and 37b extending in the right-angled direction to the moving direction of the valve element 32. Virtual lines 11 and 12 contacting with inner peripheral surfaces 37c and 37d of the passages 37a and 37b in parallel to the axes O1 and O2 of the second passages 37a and 37b, and most distant in the radial direction from the axis O3 of the first passage 38, are matched with a tangent of an inner peripheral surface 38a of the first passage 38 to generate a turning flow in a flow of the refrigerant gas flowing in the first passage 38 from the second passages 37a and 37b.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control valve for a variable displacement compressor that controls the supply of refrigerant gas from a discharge chamber to a crank chamber.

[0002]

2. Description of the Related Art FIG. 8 is an enlarged vertical sectional view showing a conventional control valve for a variable displacement compressor.

The control valve for the variable displacement compressor is a bellows 581, a valve body 532 connected to the bellows 581 via a plunger 570 and a rod 574, and a holder fitted in a solenoid housing 535 for accommodating the plunger 570. 531 and. The valve body 532 opens and closes the air supply passage that connects the discharge chamber and the crank chamber (not shown) of the variable displacement compressor by the expansion and contraction operation of the bellows 581. A valve body 532 is constituted by the valve rod 534 and the valve body 533.

The holder 531 has a first passage 538 and a second passage 538.
537a, 537b of the first passage 5 are formed.
38 communicates with the crank chamber, and the second passages 537a, 537b communicate with the discharge chamber. A valve body 533, a coil spring 539, and a valve rod 534 are housed in the first passage 538. The coil spring 539 biases the valve body 532 in the valve closing direction.

A first passage 538 and a second passage 537a,
537b constitutes a part of the air supply passage.

The first passage 538 extends in the moving direction of the valve body 532, the valve rod 534 is slidably supported in the first passage 538, and the valve body 533 moves integrally with the valve rod 534.

The port 531a communicates with a suction chamber (not shown), and a low pressure (suction pressure P
The refrigerant gas of s) is introduced around the bellows 581.

The suction pressure Ps is high, the bellows 581 contracts, and the valve body 532 moves in the valve closing direction to move the first passage 538.
And when the second passages 537a and 537b are cut off,
The pressure in the crank chamber (control pressure Pc) decreases, the inclination of a swash plate (not shown) increases, the piston stroke amount increases, and the discharge capacity increases.

On the other hand, the suction pressure Ps is low, the bellows 581 expands, the valve body 532 moves in the valve opening direction, and the first
When the passage 538 and the second passages 537a and 537b communicate with each other, high-pressure refrigerant gas is guided to the crank chamber.

As a result, the pressure in the crank chamber rises, the inclination of the swash plate decreases, the piston stroke amount decreases, and the discharge capacity decreases.

FIG. 9 is a sectional view taken along the line IX-IX in FIG.

The second passages 537a and 537b are provided with the valve rod 53.
4 (valve body 532) extends in a direction perpendicular to the moving direction. The second passage 537a and the second passage 537b are located on a straight line with the valve rod 534 interposed therebetween.

The second passages 537a and 537b always communicate with the discharge chamber, and the high-pressure refrigerant gas is introduced from the discharge chamber into the first passage 538 through the second passages 537a and 537b.

[0014]

FIG. 10 is a partially enlarged view for explaining the flow of the refrigerant gas. However, the coil spring 539
Is omitted.

In FIG. 10, white arrows indicate the flow of the refrigerant gas.

The refrigerant gas flowing from the second passages 537a and 537b into the first passage 538 collides with the valve rod 534, and
Flows downward as indicated by the arrow in FIG.

By the way, the refrigerant gas contains not only the refrigerant gas but also abrasion powder generated inside the compressor.

Since the density of the abrasion powder is larger than the density of the refrigerant gas and the inertia force is large, the valve rod 534 together with the refrigerant gas.
When it collides with the second passage 5, the abrasion powder falls without being diffused in the circumferential direction of the first passage 538, and the second passage 5 shown by a chain line in FIG.
It is easy to concentrate and adhere to the outer peripheral surface of the valve main body 533, the seat portion 538b of the first passage 538, and the like, which are located in the vicinity of 37a and 537b.

Therefore, even when the valve is fully closed, the valve body 53
There is a problem that a gap is created between the outer peripheral surface of No. 3 and the seat portion 538b of the first passage 538, and the refrigerant gas leaks to the crank chamber through this gap.

The present invention has been made in view of such circumstances, and an object thereof is to provide a control valve for a variable displacement compressor capable of preventing leakage of refrigerant gas when the valve is fully closed. .

[0021]

In order to solve the above-mentioned problems, a control valve for a variable displacement compressor according to a first aspect of the present invention is an air supply passage for connecting a discharge chamber and a crank chamber of the variable displacement compressor. And a valve body that opens and closes the air supply passage, and first and second passages that form a part of the air supply passage, the first passage extending in a moving direction of the valve body, A second passage extends in a direction substantially perpendicular to a moving direction of the valve body, the valve body is movably supported in the first passage, and refrigerant gas in the discharge chamber passes through the air supply passage to In a control valve for a variable displacement compressor fed into a crank chamber, a swirling flow generating means for swirling the refrigerant gas around the valve body when the refrigerant gas in the second passage flows into the first passage. It is characterized by having.

When the refrigerant gas flows from the second passage into the first passage, the swirling flow generating means causes a swirling flow in the refrigerant gas. As a result, the refrigerant gas flows in the first passage while swirling.

The 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 the swirl flow generating means is the central axis of the second passage. An imaginary line that is parallel to the inner peripheral surface of the passage and is farthest from the central axis of the first passage in the radial direction is substantially aligned with the tangent line of the inner peripheral surface of the first passage. Is characterized by.

A swirling flow can be generated in the first passage by forming the second passage so that the imaginary line substantially coincides with the tangent line of the inner peripheral surface of the first passage.

A variable displacement compressor control valve according to a third aspect of the present invention is the variable displacement compressor control valve according to the first aspect, wherein the swirl flow generating means serves as the outer peripheral surface of the valve body or the It is characterized in that a spiral groove is formed on the inner peripheral surface of the first passage.

When the refrigerant gas flows into the first passage from the second passage, the refrigerant gas flows along the spiral groove formed on the outer peripheral surface of the valve body or the inner peripheral surface of the first passage, A swirl flow is generated on the outer peripheral surface of the valve body or the inner peripheral surface of the first passage. As a result, the refrigerant gas flows downward while swirling in the first passage. At this time, since the abrasion powder also moves with the swirling flow, it is possible to prevent the abrasion powder from diffusing in the circumferential direction and concentrating and attaching the abrasion powder to the outer peripheral surface of the valve body or a part of the seat portion.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a vertical sectional view of a variable displacement type swash plate compressor having a variable displacement compressor control valve according to a first embodiment of the present invention.

A rear head 3 is arranged on one end surface of a cylinder block 1 of this variable displacement type swash plate compressor via a valve plate 2, and a front head 4 is arranged on the other end surface thereof.

Front head 4, cylinder block 1,
The valve plate 2 and the rear head 3 are integrally coupled in the axial direction with through bolts 29.

A piston 7 is slidably inserted in a cylinder bore 6 formed in the cylinder block 1.

The front head 4 has a swash plate 10 which will be described later.
A crank chamber 8 for accommodating the thrust flange 40 and the like is formed.

The rear head 3 has a suction chamber 13 and a discharge chamber 12
And are formed.

The discharge chamber 12 is located around the suction chamber 13. The low-pressure refrigerant gas supplied to the compression chamber 22 is accumulated in the suction chamber 13.

One end of the shaft 5 is rotatably supported by the front head 4 via a radial bearing 26, and the other end of the shaft 5 is a thrust bearing 24 and a radial bearing 25.
It is rotatably supported by the cylinder block 1 via.

The thrust flange 40 is fixed to the shaft 5 and rotates integrally with the shaft 5.

The swash plate 10 is slidably and slidably attached to the shaft 5 via a hinge ball 9. The swash plate 10 is connected to the thrust flange 40 by the link mechanism 41 and rotates integrally with the rotation of the thrust flange 40.

The peripheral edge of the swash plate 10 and one end of the piston 7 are connected via shoes 60 and 61.

One pair of shoes 6 for one piston 7
0 and 61 are arranged so as to sandwich the swash plate 10, and the shoe 6
0 and 61 relatively rotate on the sliding surfaces 10a and 10b of the swash plate 10 as the shaft 5 rotates. By the rotation of the swash plate 10, the piston 7 linearly reciprocates in the cylinder bore 6.

The valve plate 2 is provided with a discharge port 16 for connecting the compression chamber 22 and the discharge chamber 12 and a suction port 15 for connecting the compression chamber 22 and the suction chamber 13 at regular intervals along the circumferential direction. It is provided every other time.

The discharge chamber 12 and the crank chamber 8 are connected to the air supply passage 3
It communicates via a. A variable displacement compressor control valve (hereinafter referred to as a control valve) 30, which will be described later, is provided in the middle of the air supply passage 3a, and the pressure of the crank chamber 8 is adjusted by the control valve 30. The air supply passage 3a includes a passage 3b, chambers 3c, 3
d, passage 3e, port 3f and passage 3g.

As described above, the thrust flange 40 and the swash plate 10 are connected via the link mechanism 41, and the swash plate 10 can be tilted with respect to the plane perpendicular to the shaft 5.

A winding spring 47 is mounted between the thrust flange 40 and the hinge ball 9, and the swash plate 10 is urged toward the rear head 3 by the urging force of the winding spring 47.

FIG. 2 is an enlarged view of the control valve for the variable displacement compressor of FIG. However, the vertical direction of the control valve 30 is reversed.

The control valve 30 has an O-ring 50 in a valve accommodating hole 50 (see FIG. 1) of the rear head 3 of the variable displacement type swash plate compressor.
It is provided via a, 50b, 50c.

The control valve 30 includes a first passage 38 and second passages 37a and 37b which form a part of the air supply passage 3a.
A valve body 32 for opening and closing the air supply passage 3a, and a valve body 3
2, a holder 31 for accommodating 2 and a solenoid housing 35
It has and.

The first passage 38 extends in the moving direction of the valve body 32 (vertical direction in FIG. 2). Second passage 37a, 37
b always communicates with the discharge chamber 12, and the second passage 37
High pressure (discharge pressure Pd) from the discharge chamber 12 via a and 37b
Of the refrigerant gas is introduced into the first passage 38.

The valve body 32 is composed of a valve body 33 and a valve rod 34.

The valve rod 34 has a small diameter portion 34a and a large diameter portion 34b. The large diameter portion 34b contacts the plunger 70 and is slidably supported in the first passage 38.
The small diameter portion 34a is formed integrally with the valve body 33. The valve body 33 and the valve rod 34 may be separate bodies.

First passage 38 and second passages 37a, 3
7b is formed in the holder 31, the first passage 38 communicates with the crank chamber 8, and the second passages 37a, 37b communicate with the discharge chamber. Each of the passages 38, 37a, 37b is a linear passage having a circular cross section. In the first passage 38, in addition to the valve rod 34, a valve body 33 and a coil spring 39 for urging the valve body 32 in the valve closing direction are housed.

Further, the holder 31 is provided with a port 31a communicating with the suction chamber 13, and a low-pressure (suction pressure Ps) refrigerant gas is guided from the suction chamber 13 to the pressure-sensitive chamber 80 through the port 31a.

The holder 31 is provided at one end of the solenoid housing 35. A plunger 70 that drives the valve element 32 is housed inside the solenoid housing 35. The plunger 70 is slidably supported by a flanged pipe 72 that is in close contact with the holder 31 via an O-ring 71.

One end of the stem 74 is inserted into the accommodation hole 73 formed at one end of the plunger 70.
The other end of the stem 73 is accommodated in the accommodation hole 76a of the stopper 76 through the center hole 75a of the suction element 75. The suction element 75 is fixed to one end of a holder 79 arranged in the solenoid housing 35.

Housing hole 73 of plunger 70 and suction element 75
A winding spring 77 for urging the plunger 70 in the direction of separating from the suction element 75 side is housed between and.

The stopper 76 is provided on the movable end side of the bellows 81 arranged in the pressure sensitive chamber 80. Bellows 8
A stopper 82 is provided on the fixed end side of the stopper 1.
A winding spring 83 is arranged between the 6 and the stopper 82,
The stopper 76 is biased toward the suction element 75 side by the spring force. The stopper 82 is fixed to a cap 84 screwed into the holder 79.

A winding spring 78 is arranged between the stopper 76 and the suction element 75 to urge the stopper 76 in a direction away from the suction element 75.

Next, the operation of the control valve 30 will be described.

The solenoid 35A of the control valve 30 is supplied with a predetermined current obtained by the control logic on the vehicle side. In this state, the plunger 70 turns the winding spring 7
7 is attracted to the suction element 75 side against the spring force of 7, and the valve element 32
Also, due to the spring force of the coil spring 39, it moves together with the plunger 70 in the valve closing direction.

On the other hand, low pressure refrigerant gas is introduced from the suction chamber 13 to the pressure sensing chamber 80 through the port 31a. Inhalation chamber 13
The bellows 81 in the pressure-sensitive chamber 80 expands and contracts based on the pressure of the refrigerant gas from, and the expansion and contraction action acts on the valve element 32 via the plunger 70. The opening degree of the valve element 32 at this time is determined by the suction force of the solenoid 35A and the spring force of the coil springs 83 and 77.

When the pressure of the refrigerant gas from the suction chamber 13 (suction pressure Ps) becomes lower than the pressure determined by a predetermined current, the bellows 81 expands due to the restoring force of the coil spring 83 and the bellows 81 itself, and the valve element 32 becomes The air supply passage 3a (the first passage 38 and the second passages 37a, 37b) is moved in the opening direction.

As a result, the flow rate of the high-pressure refrigerant gas guided from the discharge chamber 12 to the crank chamber 8 increases, so that the pressure in the crank chamber 8 rises and the stroke becomes smaller. Since the suction pressure rises as the stroke becomes smaller, the stroke is controlled so that the suction pressure becomes constant.

When the current is increased, the valve body 32 moves in the closing direction, so the air supply passage 3a cannot be opened unless the suction pressure becomes lower. That is, the stroke is controlled so as to maintain a lower suction pressure.

When the supply of current to the solenoid 35A of the control valve 30 is stopped, the plunger 70 moves in the direction away from the suction element 75 by the spring force of the winding spring 77, so that the bellows 81 expands and the valve body 32 is opened. The air supply passage 3a is moved in the opening direction regardless of the suction pressure and the discharge pressure. Therefore, the air supply passage 3a is opened and the crank chamber 8
The pressure rises and the swash plate 10 shifts to the minimum angle.

FIG. 3 is a sectional view taken along line III-III in FIG.

The second passages 37a and 37b are always in the discharge chamber 1
2 and the high-pressure refrigerant gas flows from the discharge chamber 12 into the first passage 38 through the second passages 37a and 37b.

The second passages 37a and 37b extend in a direction perpendicular to the moving direction of the valve rod 34 (valve element 32) (left-right direction in FIG. 3).

Central axes O1, of the second passages 37a, 37b
Inner peripheral surface 3 of the passages 37a, 37b parallel to O2
7c, 37d, and the central axis O of the first passage 38
The virtual lines I1 and I2 farthest from the radial direction 3 are aligned with the tangent line of the inner peripheral surface 38a of the first passage 38. Second
The central axis O1 of the passage 37a does not coincide with the central axis O2 of the second passage 37b.

That is, the second passage 37a and the second passage 37b are located symmetrically with respect to the central axis O3 of the first passage 38, and the central axis O1 of the second passage 37a and the second passage 37a. The central axis O2 of 37b is not located on a straight line.

Next, the operation of the variable capacity type swash plate compressor will be described.

When the rotational power of the engine (not shown) is transmitted to the shaft 5, the rotational force of the shaft 5 is transmitted from the thrust flange 40 to the swash plate 10 via the link mechanism 41, and the swash plate 10 rotates.

Due to the rotation of the swash plate 10, the shoes 60, 61 relatively rotate on the sliding surfaces 10a, 10b of the swash plate 10, and the rotational force from the swash plate 10 is converted into a linear reciprocating motion of the piston 7.

The piston 7 reciprocates in the cylinder bore 6, and the volume of the compression chamber 22 in the cylinder bore 6 changes.
Due to this volume change, the refrigerant gas is sequentially sucked, compressed, and discharged, and the refrigerant gas having a volume corresponding to the tilt angle of the swash plate 10 is discharged.

At the time of suction, the suction valve opens, and low-pressure refrigerant gas is sent from the suction chamber 13 to the compression chamber 22 in the cylinder bore 6 through the suction port 15.

At the time of discharge, the discharge valve is opened, and high-pressure refrigerant gas is discharged from the compression chamber 22 to the discharge chamber 12 through the discharge port 16.

When the heat load decreases, the energization of the solenoid 35A of the control valve 30 is stopped and the plunger 70 moves in the valve opening direction. The valve rod 34 moves integrally with the plunger 70, and the valve body 33 is pushed by the valve rod 34 to move.

As a result, the discharge chamber 1 is supplied through the air supply passage 3a.
High-pressure refrigerant gas is sent from 2 to the crank chamber 8, the pressure in the crank chamber 8 (control pressure Pc) increases, and the swash plate 10
The inclination angle of becomes smaller.

At this time, the refrigerant gas flows along the outer peripheral surface of the valve rod 34, and a swirling flow is generated in the first passage 38.

At the same time, the wear particles contained in the refrigerant gas swirl along with the flow of the refrigerant gas and diffuse in the circumferential direction, so that the wear particles are attached to the outer peripheral surface of the valve body 32 and the seat portion 3 of the first passage 38.
It does not adhere to only a part of 8b or the like. Further, since the abrasion powder passes through the outer peripheral surface of the valve body 32 and the seat portion 38b while swirling, the abrasion powder attached to the seat portion 38b and the like can be reduced.

When the heat load increases, the solenoid 70A of the control valve 30 is energized to move the plunger 70 in the valve closing direction. The valve rod 34 moves integrally with the plunger 70, and the valve body 33 is moved by the spring force of the coil spring 39.
Follow 4 and move.

As a result, the discharge chamber 1 is supplied through the air supply passage 3a.
The high-pressure refrigerant gas is no longer fed from 2 to the crank chamber 8, the pressure in the crank chamber 8 becomes low, and the inclination angle of the swash plate 10 becomes large.

At this time, since the abrasion powder does not concentrate and adhere to the outer peripheral surface of the valve body 32 and a part of the seat portion 38b of the first passage 38, the outer peripheral surface of the valve body 32 and the first wear passage are prevented. Passage 3
No gap is formed between the sheet No. 8 and the seat portion 38b.

According to this first embodiment, the first passage 3
The refrigerant gas guided to 8 flows while swirling, but at that time, it smoothly flows without forming a vortex.

Further, the abrasion powder contained in the refrigerant gas diffuses in the circumferential direction due to the swirling of the refrigerant gas, and adheres to the outer peripheral surface of the valve body 32 and a part of the seat portion 38b of the first passage 38 and the like. Therefore, there is no gap between the outer peripheral surface of the valve element 32 and the seat portion 38b of the first passage 38 when the valve is fully closed, and the leakage of the refrigerant gas into the crank chamber 8 can be prevented. .

Further, since the passage resistance of the control valve 30 becomes small, the flow rate when the valve is fully opened can be increased. In a clutchless compressor that discontinuously increases the valve opening when not energized to internally circulate the refrigerant gas, the smaller the passage resistance of the control valve 30, the more the torque can be reduced.

FIG. 4 is a diagram showing a first modification of the control valve for a variable displacement compressor according to the first embodiment of the present invention.
The same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

In this first modification, the second passage 37a,
The passage 37 is parallel to the central axes O1 and O2 of 37b.
a, 37b in contact with the inner peripheral surfaces 37c, 37d, and
Virtual lines I1 and I2 farthest from the central axis O3 of the passage 38 of the first passage 38 are tangents T of the inner peripheral surface 38a of the first passage 38
1 and T2, which is different from the first embodiment.

In this modification, the virtual lines I1 and I2 are displaced radially inward from the inner peripheral surface of the first passage 38. The “substantially matching” in claim 2 of the claims is a concept including such a degree of deviation.

The second passages 37a and 37b do not have to be parallel to each other.
It is also possible to form 7b obliquely downward.

According to this first modification, the same effects as those of the first embodiment are obtained, and the imaginary lines I1 and I2 are exactly aligned with the tangents T1 and T2 of the inner peripheral surface 38a of the first passage 38. The second passages 37a and 37b are not required to be provided.
Can be easily formed.

FIG. 5 is a diagram showing a second modification of the control valve for a variable displacement compressor according to the first embodiment of the present invention.
The same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

In this second modification, the second passage 37a,
The passage 37 is parallel to the central axes O1 and O2 of 37b.
a, 37b in contact with the inner peripheral surfaces 37c, 37d, and
Virtual lines I1 and I2 farthest from the central axis O3 of the passage 38 of the first passage 38 are tangents T of the inner peripheral surface 38a of the first passage 38
1 and T2, which is different from the first embodiment.

In this modified example, the virtual lines I1 and I2 are displaced outward in the radial direction. The “substantially matching” in claim 2 of the claims is a concept including such a degree of deviation.

According to this second modification, the same effect as that of the first modification can be obtained.

FIG. 6 is a partially enlarged sectional view of a control valve for a variable displacement compressor according to a second embodiment of the present invention, and the portions common to those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted. Omit it.

In the second embodiment, the second passage 137a,
This is different from the first embodiment in that the central axes of 137b coincide with each other, and a spiral groove 134c is formed on the outer peripheral surface of the small diameter portion 134a of the valve rod 134.

The refrigerant gas flowing into the first passage 38 from the second passages 137a and 137b flows along the spiral groove 134c of the small diameter portion 134a, and a swirling flow is generated. As a result, the refrigerant gas smoothly flows through the valve hole 38c. At this time, the rotation of the refrigerant gas causes diffusion of wear powder contained in the refrigerant gas, which prevents the wear powder from unevenly adhering to the outer peripheral surface of the valve body 132 or the seat portion 38b of the first passage 38. it can.

According to the second embodiment, the same effect as that of the first embodiment can be obtained.

FIG. 7 is a partially enlarged sectional view of a control valve for a variable displacement compressor according to a modification of the second embodiment of the present invention, and the portions common to the first embodiment are designated by the same reference numerals. The description is omitted.

In this modification, the second passages 137a and 137 are used.
This is different from the first embodiment in that the central axes of b are coincident with each other and a spiral groove 138a is formed on the inner peripheral surface of the first passage 138.

The refrigerant gas flowing from the second passages 137a and 137b into the first passage 138 flows along the spiral groove 138a of the first passage 138 to generate a swirling flow. As a result, the refrigerant gas smoothly flows through the valve hole 138c. At this time, the swirling of the refrigerant gas causes the wear powder contained in the flow of the refrigerant gas to diffuse, so that the wear powder is released from the valve body 3
It is possible to prevent non-uniform adhesion to the outer peripheral surface of No. 2 or the seat portion 138b of the first passage 138.

According to this modification, the same effect as that of the first embodiment can be obtained.

The number of the second passages may be two as in the above embodiment, but may be one or three or more.

In the above embodiment, the second passage 37
Although the a, 37b and the second passages 137a, 137b are communicated with the discharge chamber 12 and the first passage 38 is communicated with the crank chamber 8, the second passages 37a, 37b and the second passage 1 are connected.
Alternatively, 37a and 137b may communicate with the crank chamber 8 and the first passage 38 may communicate with the discharge chamber 12.

Further, the swirling flow generating means is not limited to those of the above-mentioned respective embodiments and respective modified examples, and any means for swirling the refrigerant gas around the valve body may be used.

In each of the above embodiments, the control valve 30 is applied to the variable displacement swash plate type compressor in which the swash plate 10 rotates integrally with the shaft 5, but the swash plate is integrated with the shaft. The present invention can be applied to an oscillating plate compressor that does not rotate but merely oscillates, and can also be applied to various other variable displacement compressors.

[0106]

As described above, according to the control valve for a variable displacement compressor of the first aspect of the present invention, the flow of the refrigerant gas in the first passage becomes smooth and the wear contained in the refrigerant gas. The powder is not diffused by the swirling flow and is not concentrated and attached to a part of the valve body or the seat part.Therefore, when the valve is fully closed, a gap is less likely to occur between the valve body and the seat part, and the refrigerant gas Leakage from the first passage to the crank chamber through the gap can be prevented.

According to the control valve for a variable displacement compressor of the second aspect of the invention, the virtual line farthest from the central axis of the first passage in the radial direction is set in the tangential direction of the inner peripheral surface of the first passage. The second passage can be easily formed without the need for exact matching.

According to the control valve for a variable displacement compressor of the third aspect of the present invention, the flow of the refrigerant in the first passage becomes smooth, and the abrasion powder contained in the refrigerant gas diffuses by the swirling flow, Since it is not concentrated and adhered to a part of the valve body or the seat portion, a gap is less likely to be formed between the valve body and the seat portion when the valve is fully closed, and the refrigerant gas passes through the gap to the first passage. Can be prevented from leaking into the crank chamber.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a variable displacement compressor equipped with a variable displacement compressor control valve according to a first embodiment of the present invention.

FIG. 2 is an enlarged view of the control valve for the variable displacement compressor of FIG.

FIG. 3 is a sectional view taken along the line III-III in FIG.

FIG. 4 is a diagram showing a first modification of the variable displacement compressor control valve according to the first embodiment of the present invention.

FIG. 5 is a diagram showing a second modification of the control valve for the variable displacement compressor according to the first embodiment of the present invention.

FIG. 6 is a partially enlarged sectional view of a control valve for a variable displacement compressor according to a second embodiment of the present invention.

FIG. 7 is a partially enlarged cross-sectional view of a control valve for a variable displacement compressor according to a modification of the second embodiment of the present invention.

FIG. 8 is an enlarged vertical sectional view showing a conventional control valve for a variable displacement compressor.

9 is a sectional view taken along line IX-IX in FIG.

FIG. 10 is a partially enlarged view illustrating the flow of refrigerant gas.

[Explanation of symbols]

3a Air supply passage 8 crank chambers 12 Discharge chamber 32 valve 31 holder 37a, 37b, 137a, 137b Second passage 36a Inner peripheral surface of first passage 37c, 37d Inner peripheral surface of second passage 38 First passage 134c Helical groove formed on the outer peripheral surface of the valve body 136a Spiral groove formed on the inner peripheral surface of the first passage I1, I2 virtual line T1, T2 tangent

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hidehiro Andachi             39, Higashihara, Chiyo-ji, Konan-cho, Osato-gun, Saitama Prefecture               Zexel Valeo Climate Co., Ltd.             In control F-term (reference) 3H051 AA01 BB10 CC11 CC17 FF15                 3H076 AA06 BB10 CC84

Claims (3)

[Claims] 1. A supply air passage that connects a discharge chamber and a crank chamber of a variable displacement compressor, a valve body that opens and closes the air supply passage, and first and first portions that form part of the supply air passage. Two passages, the first passage extending in the moving direction of the valve body,
Passage extends substantially at right angles to the moving direction of the valve body, the valve body is movably supported in the first passage, and the refrigerant gas in the discharge chamber passes through the air supply passage and the crank chamber. A control valve for a variable displacement compressor, which is sent to a flow path, comprises swirling flow generation means for swirling the refrigerant gas around the valve body when the refrigerant gas in the second passage flows into the first passage. A control valve for a variable displacement compressor, which is characterized in that 2. The swirling flow generating means is parallel to the central axis of the second passage and is in contact with the inner peripheral surface of the passage,
The variable displacement compressor according to claim 1, wherein the virtual line farthest from the central axis of the first passage in the radial direction substantially coincides with the tangent line of the inner peripheral surface of the first passage. Control valve. 3. The variable displacement compression compressor according to claim 1, wherein a spiral groove is formed on the outer peripheral surface of the valve body or the inner peripheral surface of the first passage as the swirling flow generating means. Control valve for machine.