JP4493480B2 - Capacity control valve of variable capacity swash plate compressor - Google Patents

Description

The present invention relates to a capacity control valve for a variable capacity swash plate compressor.

A valve shaft insertion hole is formed in one end wall, an inlet hole is formed in the peripheral wall, and a valve chamber is formed in the other end wall, and the valve shaft insertion hole is slidably inserted into the valve shaft insertion hole. A variable capacity swash plate type having a valve body having a valve shaft that reciprocates in the valve chamber to open and close the valve hole, and a valve body driving means, the inlet hole communicating with the discharge chamber, and the valve hole communicating with the crank chamber A capacity control valve of a compressor is disclosed in Patent Document 1.
JP-A-9-268973

In the capacity control valve of Document 1, minute foreign matter inside the compressor, abrasion powder, minute foreign matter on the external refrigeration circuit side, etc. contained in a minute amount in the gas flowing into the valve chamber from the inlet hole, the valve shaft insertion hole peripheral wall and the valve shaft In the gap between the two, the smooth reciprocation of the valve shaft is hindered, and the capacity control function may be hindered.
The present invention has been made in view of the above problems, and is a cylindrical valve in which a valve shaft insertion hole is formed in one end wall, an inlet hole is formed in a peripheral wall, and a valve hole is formed in the other end wall. A valve body that has a valve shaft that is slidably inserted into the valve shaft insertion hole and that reciprocates in the valve chamber to open and close the valve hole, and a valve body drive means. The inlet hole communicates with the discharge chamber. The valve hole is a capacity control valve of a variable capacity swash plate compressor that communicates with the crank chamber, and a capacity control valve that suppresses the entry of foreign matter into the gap between the valve shaft insertion hole peripheral wall and the valve shaft. The purpose is to provide.

In order to solve the above problems, in the present invention, a cylindrical valve chamber in which a valve shaft insertion hole is formed in one end wall, an inlet hole is formed in a peripheral wall, and a valve hole is formed in the other end wall A valve body having a valve shaft slidably inserted into the valve shaft insertion hole and reciprocating in the valve chamber to open and close the valve hole, and a valve body drive means, and the inlet hole communicates with the discharge chamber The valve hole is a capacity control valve of a variable capacity swash plate compressor communicating with the crank chamber, and the valve chamber is formed in a cylindrical shape that is concentric with the valve shaft insertion hole and has a larger diameter than the valve shaft insertion hole. holes are directed in a direction perpendicular to the central axis of valve chamber, and offset from the central axis of valve chamber radially, imaginary line extending the central axis of inlet holes in the valve chamber does not intersect the valve shaft to provide a displacement control valve of a variable displacement swash plate type compressor according to claim which are arranged so as.

In the displacement control valve of the variable displacement swash plate compressor according to the present invention, the valve chamber is formed concentrically with the valve shaft insertion hole and has a larger diameter than the valve shaft insertion hole, and the valve chamber inlet hole is formed in the valve chamber. An imaginary line that is directed perpendicular to the central axis and that is radially offset from the central axis of the valve chamber and extends the central axis of the inlet hole into the valve chamber is disposed so as not to intersect the valve shaft. Therefore, the gas flowing into the valve chamber from the inlet hole swirls in the valve chamber, and the foreign matter receiving the centrifugal force moves toward the valve chamber peripheral wall. Since the valve shaft insertion hole is formed at the center of the valve chamber end wall, the possibility that foreign matter exists near the valve shaft insertion hole is reduced. As a result, the entry of foreign matter into the gap between the valve shaft insertion hole peripheral wall and the valve shaft is suppressed.
When the valve chamber has a cylindrical shape, the generation of a swirling flow in the valve chamber is promoted, and the suppression of foreign matter intrusion into the gap between the valve shaft insertion hole peripheral wall and the valve shaft is promoted.

In a preferred embodiment of the present invention, a plurality of inlet holes are formed in the circumferential wall of the valve chamber at intervals in the circumferential direction.
A plurality of inlet holes are formed in the circumferential wall of the valve chamber at intervals in the circumferential direction, thereby facilitating the formation of a swirling flow in the valve chamber, and a gap between the circumferential wall of the valve shaft insertion hole and the valve shaft Suppression of foreign matter intrusion into the body is promoted.

In a preferred embodiment of the present invention, the inlet hole is directed tangential to the peripheral wall of the valve chamber.
As the inlet hole is directed tangentially to the peripheral wall of the valve chamber, the generation of a swirling flow in the valve chamber is promoted, and the entry of foreign matter into the gap between the peripheral wall of the valve shaft insertion hole and the valve shaft is suppressed. Is promoted.

In a preferred aspect of the present invention, the valve chamber has a truncated cone shape that is convex toward the other end wall.
Since the valve chamber has a convex truncated cone shape toward the other end wall, the gas flow from the inlet hole to the valve hole when the valve hole is opened becomes smooth. As a result, foreign matter discharge performance is improved.

In a preferred aspect of the present invention, a cylinder surrounding the valve shaft insertion hole extends from the one end wall toward the other end wall, and the tip of the cylinder has the other end rather than the inlet hole. Located on the wall side.
The cylinder surrounding the valve shaft insertion hole extends from the one end wall toward the other end wall, and the tip of the cylinder is positioned closer to the other end wall than the inlet hole. The gas that has flowed into the valve chamber flows through an annular gap between the cylinder and the valve chamber peripheral wall. As a result, the formation of the swirling flow is promoted, and the possibility that the swirling flow directly touches the valve shaft insertion hole is reduced, and the suppression of foreign matter intrusion into the gap between the valve shaft insertion hole peripheral wall and the valve shaft is promoted. The

In the displacement control valve of the variable displacement swash plate compressor according to the present invention, the valve chamber is formed concentrically with the valve shaft insertion hole and has a larger diameter than the valve shaft insertion hole, and the valve chamber inlet hole is formed in the valve chamber. An imaginary line that is directed perpendicular to the central axis and that is radially offset from the central axis of the valve chamber and extends the central axis of the inlet hole into the valve chamber is disposed so as not to intersect the valve shaft. Therefore, the gas flowing into the valve chamber from the inlet hole swirls in the valve chamber, and the foreign matter receiving the centrifugal force moves toward the valve chamber peripheral wall. Since the valve shaft insertion hole is formed at the center of the valve chamber end wall, the possibility that foreign matter exists near the valve shaft insertion hole is reduced. As a result, the entry of foreign matter into the gap between the valve shaft insertion hole peripheral wall and the valve shaft is suppressed.
When the valve chamber has a cylindrical shape, the generation of a swirling flow in the valve chamber is promoted, and the suppression of foreign matter intrusion into the gap between the valve shaft insertion hole peripheral wall and the valve shaft is promoted.

A discharge capacity control valve of a variable capacity swash plate compressor according to an embodiment of the present invention will be described.

As shown in FIG. 1, the variable capacity swash plate compressor A includes a main shaft 10, a rotor 11 fixed to the main shaft 10, and a swash plate 12 supported on the main shaft 10 so that the tilt angle is variable. The swash plate 12 is connected to the rotor 11 via a link mechanism 13 that allows the tilt angle of the swash plate 12 to vary, and rotates in synchronization with the rotor 11 and thus the main shaft 10.
A piston 15 is moored to the swash plate 12 via a pair of shoes 14 that are in sliding contact with the peripheral edge of the swash plate 12. The piston 15 is inserted into a cylinder bore 16 a formed in the cylinder block 16.
A plurality of pistons 15 are arranged at intervals in the circumferential direction.

A dish-shaped front housing 18 is provided that forms a crank chamber 17 that accommodates the main shaft 10, the rotor 11, and the swash plate 12 in cooperation with the cylinder block 16. The main shaft 10 extends outside through the front housing 18. A shaft sealing member 19 for sealing the front housing penetrating portion of the main shaft 10 is disposed.
A pulley 20 fixed to the tip of the main shaft 10 is connected to a vehicle engine (not shown) via a belt (not shown).

A cylinder head 23 that forms a suction chamber 21 and a discharge chamber 22 is disposed. The suction chamber 21 is connected to an evaporator (not shown) of the in-vehicle air conditioner via a suction port (not shown). The discharge chamber 22 is connected to a condenser (not shown) of the in-vehicle air conditioner via a discharge port (not shown).
A valve plate 24 having a suction hole and a discharge hole communicating with the bore 16a is disposed between the cylinder block 16 and the cylinder head 23. A discharge valve and a suction valve are mounted on the valve plate 24.
The crank chamber 17 and the suction chamber 21 communicate with each other through an orifice hole 24 a formed in the valve plate 24.

The front housing 18, the cylinder block 16, the valve plate 24, and the cylinder head 23 are integrally fastened by a plurality of through bolts 25 that are spaced apart from each other along a circumference around the main shaft 10.

A capacity control valve B for controlling the discharge capacity of the variable capacity swash plate compressor A is fitted and fixed in a recess 26 formed in the cylinder head 23 adjacent to the discharge chamber 22.
As shown in FIG. 2, the capacity control valve B is disposed in the pressure sensing chamber 201, the inside is evacuated, a spring is disposed, and a feeling of receiving the internal pressure of the suction chamber 21 (hereinafter referred to as suction pressure). A bellows 202 functioning as a pressure member, a pressure-sensitive rod 204 having one end abutting on the bellows 202 and slidably supported on the valve casing 203, and a pressure-sensitive rod 204 are integrally formed. The opening 203a is opened and closed, and the discharge chamber 22 and the crank chamber 17 reach from the discharge chamber 22 to the crank chamber 17 through the communication passage 27, the inlet hole 203b, the valve chamber 205, the valve hole 203a, the outlet hole 203c, and the communication passage 28. A valve body 206 that opens and closes the communication path between the valve body 206, a fixed iron core 207 that slidably supports the valve shaft 206 a of the valve body 206, and one end abutting against one end of the valve shaft 206 a, 207 A solenoid rod 209 having a central portion inserted in a non-contact manner and a plunger 208 fixed to the other end, a spring 210 for urging the plunger 208 in the valve closing direction, and an outer peripheral portion of the plunger 208 slidable. A non-magnetic tube 212 supported and fixed to the solenoid housing 211 and an electromagnetic coil 213 surrounding the tube 212 and fixed to the solenoid housing 211 are provided.

As shown in FIGS. 2 and 3 (a), the valve chamber 205 is formed in a cylindrical shape, and a valve shaft insertion hole 207b through which the valve shaft 206a is slidably inserted into a fixed iron core 207 forming one end wall. The inlet hole 203b is formed in the peripheral wall, and the valve hole 203a is formed in the other end wall. The inlet hole 203 b communicates with the discharge chamber 22 through the communication passage 27, and the valve hole 203 a communicates with the crank chamber 17 through the outlet hole 203 c and the communication passage 28. The valve shaft insertion hole 207 b and the valve hole 203 a extend concentrically with the central axis X of the valve chamber 205. The valve body 206 reciprocates in the extending direction of the central axis X in the valve chamber 205 to open and close the valve hole 203a.
As shown in FIGS. 2 and 3 (a), the inlet hole 203 b is oriented in a direction orthogonal to the central axis X of the valve chamber 205 and is offset from the central axis X of the valve chamber 205 in the radial direction. ing.

The bellows 202 is supported at its lower end by a bellows guide 214, and the bellows guide 214 is slidably supported by a pressure setting member 215 that forms the lower end of the pressure sensitive chamber 201. Between the pressure setting member 215 and the bellows guide 214, a spring 216 for biasing the bellows 202 in the valve opening direction is disposed. The amount of press-fitting of the pressure setting member 215 into the peripheral wall of the pressure-sensitive chamber 201 is adjusted, and the control characteristic of the capacity control valve B is adjusted.

The pressure sensing chamber 201 communicates with the internal hole 207a of the fixed iron core 207 through the pressure guiding passage 203d. Accordingly, the one end of the valve shaft 206a facing the inner hole 207a of the fixed iron core, the fixed iron core 207, the plunger 208, and the spring 210 receive the suction pressure.
In order to prevent the biasing force in the valve closing direction due to the discharge pressure from acting on the valve body 206, the sectional area of the valve shaft 206a is set slightly larger than the area of the valve hole 203a.
The refrigerant leaks from the valve chamber 205 side to the inner hole 207a of the fixed iron core through a gap between the valve shaft 206a and the peripheral wall of the valve shaft insertion hole 207b. Since it is discharged to the suction chamber 21 via the pressure sensitive chamber 201, it does not affect the pressure of the internal hole 207a of the fixed iron core.
The electromagnetic force generated by the electromagnetic coil 213 acts on one end of the valve shaft 206a via the plunger 208 and the solenoid rod 209, and urges the valve body 206 in the valve closing direction.

In the discharge capacity control valve B, when the internal pressure of the suction chamber 21 (hereinafter referred to as suction pressure) is equal to or lower than a predetermined value, the bellows 202 extends and the valve body 206 is resisted against the electromagnetic force generated by the electromagnetic coil 213. Push in the valve opening direction to open the valve hole 203a. The internal pressure of the discharge chamber 22 (hereinafter referred to as discharge pressure) is introduced into the crank chamber 17 and the internal pressure of the crank chamber (hereinafter referred to as crank chamber pressure) increases, the inclination angle of the swash plate 12 decreases, and the discharge capacity of the compressor A Decrease. As a result, the refrigerant gas circulation amount in the external refrigeration circuit decreases, and the suction pressure increases. When the suction pressure exceeds a predetermined value, the bellows 202 contracts, the electromagnetic force generated by the electromagnetic coil 213 pushes the valve body 206 in the valve closing direction, and closes the valve hole 203a. As a result, the introduction of the discharge pressure into the crank chamber 17 is stopped. As the refrigerant gas in the crank chamber flows into the suction chamber 21 through the orifice hole 24a, the crank chamber pressure decreases, the inclination angle of the swash plate 12 increases, and the discharge capacity of the compressor A increases. As a result, the amount of refrigerant gas circulating in the external refrigeration circuit increases and the suction pressure decreases. Opening and closing of the valve hole 203a is repeated, the suction pressure is maintained at a predetermined value, and the comfort of the vehicle air conditioning is maintained.
The operating point of the internal control valve formed by the bellows 202, the pressure sensitive rod 204, and the valve body 206 is uniquely determined by the energization amount to the electromagnetic coil 213.

In the capacity control valve B, the inlet hole 203b is directed in a direction orthogonal to the central axis X of the valve chamber 205 and is offset from the central axis X of the valve chamber 205 in the radial direction. The refrigerant gas that has flowed into the valve chamber 205 from the hole 203b rotates in the valve chamber 205 as indicated by an arrow in FIG. The minute foreign matter inside the compressor, the abrasion powder, and the minute foreign matter on the external refrigeration circuit side contained in a minute amount in the refrigerant gas are moved toward the peripheral wall of the valve chamber 205 under the centrifugal force. Since the valve shaft insertion hole 207b is formed at the center of the end wall of the valve chamber, the possibility that foreign matter exists in the vicinity of the valve shaft insertion hole 207b decreases, and the valve shaft insertion hole 207b has a peripheral wall between the valve shaft 206a and the valve shaft 206a. Intrusion of foreign matter into the gap is suppressed.
Since the valve chamber 205 has a cylindrical shape, the formation of a swirling flow of the refrigerant gas is promoted, and the suppression of foreign matter intrusion into the gap between the valve shaft insertion hole 207b and the valve shaft 206a is promoted.

As shown in FIG. 3B, the inlet hole 203 b may be directed tangential to the peripheral wall of the valve chamber 205. Since the inlet hole 203b is directed tangentially to the peripheral wall of the valve chamber 205, the generation of the refrigerant gas swirling flow in the valve chamber 205 is promoted, and the gap between the peripheral wall of the valve shaft insertion hole 207b and the valve shaft 206a is promoted. Suppression of entry of foreign matter into the gap is promoted.

Instead of forming a pair of inlet holes 203b as shown in FIG. 3 (a), a single inlet hole 203b may be formed as shown in FIG. 3 (c), and spaced apart from each other in the circumferential direction. Three or more inlet holes 203b may be formed apart.
By forming a plurality of inlet holes 203b spaced apart from each other in the circumferential direction, the generation of a swirling flow of refrigerant gas in the valve chamber 205 is promoted, and a gap between the peripheral wall of the valve shaft insertion hole 207b and the valve shaft 206a. Suppression of foreign matter intrusion into the body is promoted.

As shown in FIG. 4, the valve chamber 205 may be formed in a convex truncated cone shape toward the end wall where the valve hole 203a is formed. When the valve hole 203a is opened, the refrigerant gas flows smoothly from the inlet hole 203b to the valve hole 203a, and foreign matter discharge performance is improved.

As shown in FIGS. 5 and 6, a cylindrical body 207c that surrounds the valve shaft insertion hole 207b from the end of the fixed iron core 207 that forms one end wall of the valve chamber 205 is connected to the valve chamber 205 in which the valve hole 203a is formed. The other end wall may be extended toward the other end wall, and the tip of the cylinder 207c may be positioned closer to the other end wall than the inlet hole 203b.
A cylindrical body 207c surrounding the valve shaft insertion hole 207b extends from the end of the fixed iron core 207 forming one end wall of the valve chamber 205 toward the other end wall of the valve chamber 205 in which the valve hole 203a is formed. Since the tip of the cylinder 207c is located on the other end wall side of the inlet hole 203b, the refrigerant gas that has flowed into the valve chamber 205 from the inlet hole 203b flows between the cylinder 207c and the peripheral wall of the valve chamber 205. It will flow through the annular gap between them. As a result, the formation of the swirling flow is promoted, and the possibility that the swirling flow directly touches the valve shaft insertion hole 207b is reduced, and the entry of foreign matter into the gap between the peripheral wall of the valve shaft insertion hole 207b and the valve shaft 206a is suppressed. Is promoted.

The present invention can be widely used for a capacity control valve of a variable capacity swash plate compressor.

It is sectional drawing of a variable capacity | capacitance swash plate type compressor provided with the capacity | capacitance control valve based on the Example of this invention. It is sectional drawing of the capacity | capacitance control valve which concerns on the Example of this invention. It is the III-III arrow line view of FIG. It is a fragmentary sectional view of the capacity control valve concerning other examples of the present invention. It is a fragmentary sectional view of the capacity control valve concerning other examples of the present invention. It is VI-VI arrow line view of FIG.

Explanation of symbols

A Variable displacement swash plate compressor B Capacity control valve X Central axis 21 of valve chamber Suction chamber 22 Discharge chamber 202 Bellows 203a Valve hole 203b Inlet hole 203c Outlet hole 205 Valve chamber 206 Valve body 206a Valve shaft 207b Valve shaft insertion hole 213 Electromagnetic coil

Claims (5)

A valve shaft insertion hole is formed in one end wall, an inlet hole is formed in the peripheral wall, and a valve chamber is formed in the other end wall, and the valve shaft insertion hole is slidably inserted into the valve shaft insertion hole. A variable capacity swash plate type having a valve body having a valve shaft that reciprocates in the valve chamber to open and close the valve hole, and a valve body driving means, the inlet hole communicating with the discharge chamber, and the valve hole communicating with the crank chamber A capacity control valve for a compressor, wherein the valve chamber is formed in a cylindrical shape concentric with the valve shaft insertion hole and larger in diameter than the valve shaft insertion hole, and the inlet hole is orthogonal to the central axis of the valve chamber. variable that directed are, and offset from the central axis of the valve chamber in the radial direction, a virtual line obtained by extending the central axis of the inlet port in the valve chamber, characterized in that it is arranged so as not to intersect the valve shaft Capacity control valve for capacity swash plate compressor. 2. The capacity control valve for a variable capacity swash plate compressor according to claim 1, wherein a plurality of inlet holes are formed in the circumferential wall of the valve chamber at intervals in the circumferential direction. 3. The capacity control valve for a variable capacity swash plate compressor according to claim 1, wherein the inlet hole is directed tangential to the peripheral wall of the valve chamber. The capacity control valve for a variable capacity swash plate compressor according to any one of claims 1 to 3 , wherein the valve chamber has a frustoconical shape convex toward the other end wall. A cylinder surrounding the valve shaft insertion hole extends from the one end wall toward the other end wall, and the tip of the cylinder is positioned on the other end wall side of the inlet hole. The capacity control valve for a variable capacity swash plate compressor according to any one of claims 1 to 4 , wherein

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