JP6175630B2 - Control valve - Google Patents

Description

  The present invention relates to a control valve that controls a flow of fluid.

  An automobile air conditioner is generally configured by arranging a compressor, a condenser, an evaporator, and the like in a refrigerant circulation passage. Various control valves are provided for switching the refrigerant circulation passage and adjusting the refrigerant flow rate. As such a control valve, there is one in which a refrigerant introduction port is provided on a side portion of the body (see, for example, Patent Document 1).

  Such a control valve has a shaft that is slidably supported by the body, and a valve body is provided at one end of the shaft. The shaft is driven in the axial direction by an actuator provided integrally with the body to operate the valve body in the opening / closing direction of the valve portion. When the valve is opened, the refrigerant is introduced toward the side of the shaft, and most of the refrigerant is guided in one direction along the outer periphery of the shaft and passes through the valve hole.

  However, a part of the refrigerant also flows into the sliding portion between the shaft and the body in the other direction, which may prevent smooth sliding of the shaft. That is, in such an air conditioner, foreign matter such as metal powder may be contained in the refrigerant discharged from the compressor. This occurs due to wear around the piston of the compressor. When this foreign matter flows into the sliding portion of the control valve, the sliding of the shaft and the smooth operation of the valve body may be hindered by the biting of the foreign matter. Therefore, in the configuration described in Patent Document 1, a method is adopted in which a labyrinth structure is provided in the sliding portion between the shaft and the body to suppress the inflow of the refrigerant into the sliding portion.

JP-A-11-287354

  However, although such a labyrinth structure can suppress the flow of the refrigerant in the sliding portion between the shaft and the body, it is not necessarily sufficient to restrict the inflow of foreign matter to the sliding portion inlet itself. In addition, there is a problem that foreign matter flowing along the wall surface of the shaft easily collides directly with the attaching / detaching portion of the valve body to the valve seat. Such a problem is not limited to an air conditioner for automobiles, but can occur in an apparatus equipped with a control valve.

  An object of the present invention is to provide a control valve capable of effectively suppressing entry of a foreign substance contained in a fluid into a sliding portion.

  In order to solve the above problems, a control valve according to an aspect of the present invention is formed so that a valve hole and a guide hole communicate with each other in an axial direction through an intermediate pressure chamber, and introduces a fluid into the intermediate pressure chamber. An intermediate pressure chamber is formed in a body formed with a lead-out port for leading the fluid that has passed through the valve hole, and a valve seat provided at the opening end of the valve hole. A valve body that opens and closes the valve part by attaching and detaching from the side, a valve drive body in which the valve body is integrally provided and slidably supported in the guide hole, and driving in the opening and closing direction of the valve part with respect to the valve drive body An actuator capable of applying a force. The valve driver has a stepped portion for receiving foreign matter entering from the introduction port on the outer peripheral surface of the portion located in the intermediate pressure chamber. A wall surface facing the guide hole side in the stepped portion has a portion located on the valve hole side with respect to the introduction port.

  According to this aspect, a sufficiently large step portion is provided on the outer surface of the valve driver facing the introduction port. For this reason, even if foreign matter is contained in the fluid introduced through the introduction port, the foreign matter can be once received by the step portion of the valve driver and then guided to the valve hole. That is, by providing the step portion on the outer peripheral surface of the valve drive body, it is possible to prevent foreign matter from being directly guided to the sliding portion between the valve drive body and the guide hole. This is because the foreign matter has a certain amount of mass, so that it is easy to go straight from the introduction port toward the outer peripheral surface of the valve driving body, and this is caught at the step portion and decelerated. The foreign matter thus decelerated is sucked to the valve hole side and discharged. As a result, it is possible to effectively suppress the entry of foreign matter contained in the fluid into the sliding portion. Further, it is possible to make it difficult for the foreign matter flowing along the wall surface of the shaft to directly collide with the attaching / detaching portion of the valve body to the valve seat.

  According to the present invention, it is possible to provide a control valve that can effectively suppress the entry of foreign matter contained in a fluid into a sliding portion, and that makes it difficult for the foreign matter to directly collide with the attachment / detachment portion of the valve body to the valve seat. Can do.

It is sectional drawing which shows the structure of the control valve which concerns on 1st Embodiment. It is a partial expanded sectional view corresponding to the upper half part of FIG. It is a figure showing a foreign material discharge | emission promotion structure and its effect. It is a partial expanded sectional view showing the foreign matter discharge promotion structure of the control valve concerning a modification. It is a partial expanded sectional view showing the foreign matter discharge promotion structure of the control valve concerning a modification. It is a partial expanded sectional view showing the foreign matter discharge promotion structure of the control valve concerning a modification. It is a partial expanded sectional view showing the foreign matter discharge promotion structure of the control valve concerning a modification. It is sectional drawing which shows the structure of the control valve which concerns on 2nd Embodiment. It is a figure showing a foreign material discharge | emission promotion structure, and is the I section enlarged view of FIG.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, for the sake of convenience, the positional relationship between the structures may be expressed as upper and lower with reference to the illustrated state.

[First Embodiment]
FIG. 1 is a cross-sectional view illustrating a configuration of a control valve according to the first embodiment.
The control valve 1 is configured as an electromagnetic valve that controls the discharge capacity of a variable capacity compressor (not shown) (simply referred to as “compressor”) installed in the refrigeration cycle of the automotive air conditioner. This compressor compresses the refrigerant flowing through the refrigeration cycle and discharges it as a high-temperature and high-pressure gas refrigerant. The gas refrigerant is condensed in a condenser (external heat exchanger) and further adiabatically expanded by an expansion device to become a low temperature / low pressure mist refrigerant. The low-temperature and low-pressure refrigerant evaporates in the evaporator, and the passenger compartment air is cooled by the latent heat of vaporization. The refrigerant evaporated in the evaporator is returned again to the compressor and circulates in the refrigeration cycle. The compressor has a rotating shaft that is rotationally driven by an automobile engine, and a compression piston is connected to a swing plate attached to the rotating shaft. The refrigerant discharge amount is adjusted by changing the stroke of the piston by changing the angle of the swing plate. The control valve 1 controls the flow rate of the refrigerant introduced from the discharge chamber of the compressor into the crank chamber, thereby changing the angle of the swing plate, and thus the discharge capacity of the compressor.

  The control valve 1 is configured as a so-called Ps sensing valve that controls the flow rate of the refrigerant introduced from the discharge chamber into the crank chamber so as to keep the suction pressure Ps (corresponding to “sensed pressure”) of the compressor at a set pressure. Yes. The control valve 1 is configured by integrally assembling a valve body 2 and a solenoid 3. The valve body 2 is a main valve that opens and closes a refrigerant passage for introducing a part of the discharged refrigerant into the crank chamber when the compressor is in operation, and a so-called bleed valve that releases the refrigerant in the crank chamber to the suction chamber when the compressor is started. Including a functioning secondary valve. The solenoid 3 controls the flow rate of the refrigerant introduced into the crank chamber by driving the main valve in the opening / closing direction to adjust the opening degree. The valve body 2 includes a stepped cylindrical body 5, a main valve and a sub valve provided in the body 5, a power element 6 that generates a force that opposes the solenoid force to adjust the opening of the main valve, and the like. I have. The power element 6 functions as a “pressure sensitive part”.

  A port 12 is provided at the upper end opening of the body 5, and a port 14 is provided at the side. The lower end opening of the body 5 communicates with a port 16 provided in a core 42 (described later) of the solenoid 3. The port 12 functions as a “crank chamber communication port” communicating with the crank chamber, the port 14 functions as a “discharge chamber communication port” communicating with the discharge chamber, and the port 16 is a “suction chamber communication port” communicating with the suction chamber. Function as. In the body 5, a main passage for communicating the port 12 and the port 14 and a sub-passage for communicating the port 12 and the port 16 are formed. A main valve is provided in the main passage, and a sub valve is provided in the sub passage. A part of the body 5 constituting the main passage is provided with a valve hole 18 (main valve hole), and a valve seat 20 (main valve seat) is formed on the tapered surface of the lower end opening.

  The port 14 functions as an “introduction port” for introducing the refrigerant having the discharge pressure Pd from the discharge chamber. The port 12 functions as a “derivation port” for deriving the refrigerant having the crank pressure Pc via the main valve toward the crank chamber during steady operation of the compressor, while the crank pressure discharged from the crank chamber when the compressor is started up. It functions as an “introduction port” for introducing the refrigerant of Pc. The refrigerant introduced at this time is guided to the auxiliary valve. That is, the port 12 functions as an “introduction / exit port” for introducing or deriving the refrigerant having the crank pressure Pc. The port 16 functions as an “introduction port” that introduces the refrigerant having the suction pressure Ps during the steady operation of the compressor, and at the time of starting the compressor, the refrigerant having the suction pressure Ps via the auxiliary valve is led out toward the suction chamber. Functions as a “derived port”. That is, the port 16 functions as an “introduction / exit port” for introducing or deriving the refrigerant having the suction pressure Ps.

  An attachment hole 22 is provided in the center of the partition wall at the upper end of the body 5 in the axial direction, and a plurality of communication holes 23 are provided around the attachment hole 22. A stepped columnar support member 27 is press-fitted into the mounting hole 22 so that the upper end thereof is supported. The support member 27 extends downward in the axial direction inside the body 5 and supports the upper end portion of the power element 6 from above. The communication hole 23 allows the port 12 and the valve hole 18 to communicate with each other.

  A valve chamber 24 (functioning as an “intermediate pressure chamber”) is provided on the opposite side of the valve hole 18 from the port 12. The valve chamber 24 is formed of an annular space and communicates with the port 14 in the radial direction. A guide hole 26 is formed coaxially with the valve hole 18 on the opposite side of the valve chamber 24 from the valve hole 18. A working chamber 28 is formed on the opposite side of the guide hole 26 from the valve chamber 24, and communicates with the port 16.

  An annular strainer 15 is attached to the port 14. The strainer 15 includes a filter for suppressing entry of dust and the like into the body 5. On the other hand, a bottomed cylindrical strainer 13 is attached to the port 12. The strainer 13 includes a filter for suppressing entry of dust and the like into the body 5.

  The body 5 is provided with a stepped cylindrical valve driver 30. The valve driver 30 has an internal passage 35 extending in the axial direction. The internal passage 35 communicates with the port 12 through the valve hole 18 and the mounting hole 22. The valve drive body 30 is configured by joining a stepped cylindrical first member 31 and a bottomed stepped cylindrical second member 32 in the axial direction. The upper part of the first member 31 is reduced in diameter, and the lower part is press-fitted into the upper part of the second member 32. A valve body 33 (main valve body) is integrally provided at the distal end portion of the first member 31. The valve body 33 is attached to and detached from the valve seat 20 to open and close the main valve, and adjusts the flow rate of refrigerant flowing from the discharge chamber to the crank chamber. In the present embodiment, a configuration is adopted in which the valve body 33 is seated on or removed from the valve seat 20 to open and close the main valve, but a mode of a spool valve in which the main valve body is inserted into and removed from the main valve hole is employed. May be.

  The second member 32 has a lower half with a reduced diameter, and has a valve hole 34 (sub-valve hole) formed of a plurality of circular holes at the bottom. A valve seat 36 (sub valve seat) is formed around the valve hole 34 in the second member 32. Inside the valve drive body 30, the power element 6 and the valve body 38 (sub-valve body) are coaxially arranged vertically. The valve body 38 has a bottomed cylindrical shape, is attached to and detached from the valve seat 36, opens and closes the auxiliary valve, and allows or blocks the relief of the refrigerant from the crank chamber to the suction chamber. The power element 6 includes a bellows 8, and applies a force that opposes the solenoid force by the displacement of the bellows 8 through the valve body 38 to the valve drive body 30 and then the valve body 33.

  Between the valve body 38 and the power element 6, a spring 39 (functioning as an “urging member”) that urges the valve element 38 and the power element 6 in a direction to separate them is interposed. Further, a spring 40 (functioning as an “urging member”) that biases the valve driving body 30 in the valve closing direction of the main valve is interposed between the valve driving body 30 and the solenoid 3 (core 42). ing.

  On the other hand, the solenoid 3 includes a stepped cylindrical core 42, a bottomed cylindrical sleeve 44 assembled so as to seal the lower end opening of the core 42, and the sleeve 42 accommodated in the axial direction of the core 42. A cylindrical plunger 46 disposed opposite to the core 42, a cylindrical bobbin 48 extrapolated to the core 42 and the sleeve 44, an electromagnetic coil 50 wound around the bobbin 48 to generate a magnetic circuit by energization, and an electromagnetic coil A cylindrical case 52 provided so as to cover 50 from the outside and also functioning as a yoke, and an end member 54 provided so as to seal the lower end opening of the case 52 are provided. In the present embodiment, the body 5, the core 42, the case 52, and the end member 54 form the body of the entire control valve 1.

  The valve body 2 and the solenoid 3 are fixed by press-fitting the lower end of the body 5 into the upper end opening of the core 42. The diameter of the upper half of the core 42 is enlarged, and the working chamber 28 for satisfying the suction pressure Ps is formed between the core 42 and the body 5. The port 16 is provided near the joint between the core 42 and the body 5. On the other hand, a long operating rod 58 is inserted through the center of the core 42 in the axial direction.

  The lower end of the operating rod 58 is loosely fitted to the upper half of the plunger 46, and the operating rod 58 and the plunger 46 are connected coaxially. A spring 64 (functioning as an “urging member”) is interposed between the plunger 46 and the sleeve 44. The spring 64 biases the plunger 46 upward, whereby the plunger 46 and the operating rod 58 are held together.

  A ring-shaped engaging member 59 (functioning as an “engaging portion”) is fitted to the operating rod 58. The actuating rod 58 can be operatively connected to the valve drive body 30 via the engaging member 59 and can be operatively connected to the power element 6 via the valve body 38. The actuating rod 58 appropriately transmits a solenoid force, which is a suction force between the core 42 and the plunger 46, to the valve driving body 30 and then to the valve body 33 via the engaging member 59.

  On the other hand, a driving force (also referred to as “pressure-sensitive driving force”) due to the expansion / contraction operation of the power element 6 is transmitted to the operating rod 58 via the valve body 38 and is loaded so as to oppose the solenoid force. That is, in the control state of the main valve, the force adjusted by the solenoid force and the pressure-sensitive driving force acts on the valve body 33, and the opening degree of the main valve is appropriately controlled. When the main valve is closed, the operating rod 58 is displaced relative to the valve drive body 30 in accordance with the magnitude of the solenoid force, and the valve body 38 is pushed up to open the sub valve. As a result, the bleed function is exhibited.

  A ring-shaped shaft support member 60 is press-fitted into the upper end portion of the core 42, and the operating rod 58 is supported by the shaft support member 60 so as to be slidable in the axial direction. A communication groove parallel to the axis is formed at a predetermined location on the outer peripheral surface of the shaft support member 60. Therefore, when the main valve is controlled, the suction pressure Ps of the working chamber 28 is guided to the inside of the sleeve 44 through the communication groove 62 and the communication passage 62 formed by the gap between the operation rod 58 and the core 42.

  The communication path 62 functions as an orifice for making the inside of the sleeve 44 an oil damper chamber. That is, in the present embodiment, in the manufacturing process of the control valve 1, the same kind of oil as that contained in the refrigerant is previously put in the sleeve 44 for lubricating the compressor. In the present embodiment, the communication groove provided in the shaft support member 60 functions as a throttle passage that resists oil entering and exiting the sleeve 44. With such a configuration, the sleeve 44 can function as an oil damper chamber, and minute vibrations of the plunger 46 disposed in the sleeve 44 are suppressed. As a result, the generation of noise due to such minute vibration is prevented or suppressed. In the modified example, the communication path 62 may function as a throttle path that resists oil entering and exiting the sleeve 44. That is, at least one of the communication groove and the communication path 62 provided in the shaft support member 60 may function as a throttle path. The spring 39 functions as an off-spring that biases the plunger 46 away from the core 42 via the valve body 38 and the operating rod 58.

  The sleeve 44 is made of a nonmagnetic material. Plural communication grooves parallel to the axis are provided on the side surface of the plunger 46, and a plurality of communication grooves extending in the radial direction and communicating between the inside and the outside are provided on the lower end surface of the plunger 46 (both shown in the same figure). Not appear). With such a configuration, the suction pressure Ps or the crank pressure Pc is guided to the back pressure chamber 70 through the gap between the plunger 46 and the sleeve 44.

  A pair of connection terminals 72 connected to the electromagnetic coil 50 extend from the bobbin 48 and extend through the end members 54 to the outside. For convenience of explanation, only one of the pair is displayed in the figure. The end member 54 is attached so as to seal the entire structure in the solenoid 3 included in the case 52 from below. The end member 54 is formed by molding (injection molding) a resin material having corrosion resistance, and the resin material is also filled in the gap between the case 52 and the electromagnetic coil 50. In this way, the resin material fills the gap between the case 52 and the electromagnetic coil 50 so that the heat generated in the electromagnetic coil 50 can be easily transferred to the case 52 and the heat dissipation performance is enhanced. The end portion of the connection terminal 72 is drawn out from the end member 54 and connected to an external power source (not shown).

FIG. 2 is a partially enlarged cross-sectional view corresponding to the upper half of FIG.
A valve hole 18 and a guide hole 26 are coaxially provided in the axially intermediate portion of the body 5. The support member 27 extends downward in the axial direction in a manner that it is supported in a cantilevered manner on the upper end portion of the body 5. The inner diameter of the body 5 is expanded at the position of the working chamber 28. The lower portion of the body 5 is slightly reduced in diameter to form a guide hole 74.

  The first member 31 of the valve drive body 30 is slidably supported in the guide hole 26, and the upper end portion thereof constitutes the valve body 33. The sliding surface of the first member 31 is provided with a labyrinth seal 84 composed of a plurality of annular grooves for suppressing the circulation of the refrigerant. On the outer peripheral surface of the lower part of the first member 31, a sliding part 86 projects in an annular shape. The first member 31 is slidably supported by the guide hole 74 through the sliding portion 86. That is, the valve drive body 30 is supported at two points by the body 5 in such a manner that one end side is slidably supported by the guide hole 26 and the other end side is slidably supported by the guide hole 74. The center of gravity as a unit combining the valve drive body 30, the valve body 38, and the power element 6 is configured to be positioned between the two support portions.

  A circular boss-shaped valve seat 88 projects from the center of the upper surface of the core 42, and the lower end of the second member 32 is attached to and detached from the inner and outer sides of the valve drive body 30. The communication state is blocked or released. That is, the lower end portion of the valve drive body 30 and the upper end surface of the core 42 constitute a “shut-off valve portion”. The bottom portion of the second member 32 functions as an “engaged portion” that can be appropriately engaged and connected to the operating rod 58. The operating rod 58 passes through an insertion hole and a valve body 38 provided at the bottom center of the second member 32, and an upper end portion thereof guides the power element 6 in the axial direction.

  The valve body 38 is disposed between the power element 6 and the operating rod 58. The valve body 38 has a bottomed cylindrical shape, an insertion hole 91 is formed at the center of the bottom, and a plurality of communication holes 93 for allowing the refrigerant to pass therethrough are formed around the insertion hole 91. The upper end portion of the valve body 38 is attached to and detached from the lower surface of the power element 6 to block or allow the communication state between the internal passage 35 of the valve driver 30 and the internal passage 37 of the valve body 38. That is, an “open / close valve portion” is constituted by the upper end portion of the valve body 38 and the lower surface of the power element 6.

  The upper end portion of the operating rod 58 is inserted into the insertion hole 91 so as to be relatively displaceable. In a control state of the main valve in which the solenoid 3 is turned on, an engaging portion 94 (functioning as a “first engaging portion”) provided on the upper portion of the operating rod 58 engages with the lower surface of the valve body 38. . Further, the urging force of the springs 39 and 40 urges the valve drive body 30 and the valve body 38 in a direction in which they abut against each other. Thereby, the operating rod 58, the valve body 38, and the valve drive body 30 can be displaced integrally.

  The power element 6 includes a pair of base members 97 and 98 and a bellows 8. The base members 97 and 98 are formed into a bottomed cylindrical shape by press-molding a metal material, and have a flange portion 100 extending outward in the radial direction at an opening end portion thereof. In the bellows 8, the upper end opening of the bellows-like main body is hermetically welded to the flange portion 100 of the base member 97, and the lower end opening is hermetically welded to the flange portion 100 of the base member 98. Thereby, the upper and lower ends of the base member 98 are closed. The base members 97 and 98 have respective main bodies extending inward of the bellows 8, and their bottoms are arranged close to each other.

  The lower end portion of the support member 27 is press-fitted into the main body of the base member 97. On the other hand, the upper end portion of the operating rod 58 is loosely fitted into the main body of the base member 98. That is, the diameter of the upper portion of the operating rod 58 is reduced from the engagement portion 94, and the reduced diameter portion 99 passes through the insertion hole 91 and is partially inserted into the base member 98. However, the insertion amount of the actuating rod 58 is regulated by the engagement portion 94 that is the base end of the reduced diameter portion 99 being locked to the lower surface of the valve body 38. The transverse section of the reduced diameter portion 99 is a D-shaped section, and is configured to release the pressure inside the base member 98. The operating rod 58 can be displaced integrally with the power element 6 in a state where the engaging portion 94 is locked to the valve body 38. Further, in the state where the valve driving body 30 and the valve body 38 are pressed against each other as shown in the drawing, the operating rod 58 can be displaced integrally with the valve driving body 30 via the valve body 38.

  The inside of the bellows 8 is a sealed reference pressure chamber S. A spring 104 that biases the bellows 8 in the extending direction is interposed between the base member 97 and the base member 98. The reference pressure chamber S is in a vacuum state in this embodiment. The bellows 8 expands or contracts in the axial direction (opening / closing direction of the valve portion) according to the differential pressure between the crank pressure Pc inside the valve driver 30 and the reference pressure in the reference pressure chamber S. However, even if the differential pressure increases, if the bellows 8 contracts by a predetermined amount, the base member 97 and the base member 98 come into contact with each other and are locked, so that the contraction is restricted.

  The valve body 38 is supported between the power element 6 and the operating rod 58 with the upper end portion of the operating rod 58 as an axis, but is not fixed to either the power element 6 or the operating rod 58.

  A concave groove is provided slightly below the engaging portion 94 of the operating rod 58, and a ring-shaped engaging member 59 (functioning as a “second engaging portion”) is fitted thereto. Therefore, when the operating rod 58 is further displaced relative to the valve driver 30 after the auxiliary valve is opened, the engaging member 59 is engaged with the bottom of the valve driver 30 (second member 32). As a result, the solenoid force can be directly transmitted to the valve driving body 30, and the valve driving body 30 can be pressed in the valve closing direction of the main valve. This configuration should be used when the valve driver 30 is locked due to foreign matter biting into the sliding part between the valve driver 30 and the guide hole 26 or the sliding part between the valve driver 30 and the guide hole 74. , Functions as a lock release mechanism (interlocking mechanism, pressing mechanism) for releasing it.

  In the above configuration, the valve body 33 and the valve seat 20 constitute a main valve, and the flow rate of the refrigerant introduced from the discharge chamber to the crank chamber is adjusted by the opening of the main valve. Further, the valve body 38 and the valve seat 36 constitute a sub-valve, and the opening and closing of the sub-valve allows or blocks the refrigerant from the crank chamber to the suction chamber. That is, the control valve 1 also functions as a three-way valve that switches the flow of the refrigerant by opening one of the main valve and the sub valve.

  In the present embodiment, the effective pressure receiving diameter A (seal part diameter) of the main valve of the valve drive body 30, the effective pressure receiving diameter B (seal part diameter) of the sliding part of the valve drive body 30, and the effective pressure receiving diameter C of the bellows 8. , Effective pressure receiving diameter D (seal part diameter) in the sub-valve of the valve body 38, effective pressure receiving diameter E (seal part diameter) in the shut-off valve part of the valve driver 30, and effective pressure receiving diameter F in the on-off valve part of the valve body 38 (Seal diameter) is set equal. For this reason, in the state where the valve drive body 30 and the power element 6 are operatively connected, the influence of the discharge pressure Pd and the crank pressure Pc acting on the valve body 33 is cancelled. The power element 6 receives only the suction pressure Ps in its effective pressure receiving area. As a result, in the control state of the main valve, the valve body 33 opens and closes based on the suction pressure Ps received in the working chamber 28. That is, the control valve 1 functions as a so-called Ps sensing valve.

  In the present embodiment, the state in which the engaging portion 94 of the operating rod 58 and the valve body 38 are always in contact with each other by the urging force of the springs 39 and 64 is maintained. On the other hand, the shape and size of the mechanism is such that the distance between the engagement member 59 of the actuating rod 58 and the bottom surface of the valve driver 30 is a predetermined value L in the closed state of the sub-valve with the solenoid 3 turned off. Is set. When the control valve 1 is activated, the solenoid force in the valve closing direction of the main valve and the valve opening direction of the auxiliary valve can be transmitted to the valve body 38 by energizing the solenoid 3. As a result, the valve body 33 can be seated on the valve seat 20 to close the main valve, and the valve body 38 can be lifted from the valve seat 36 to open the auxiliary valve. That is, the control valve 1 has a “forced valve opening mechanism” for forcibly opening the auxiliary valve using the driving force of the solenoid 3.

  In the above configuration, when the control valve 1 is in a stable control state, the main valve operates autonomously so that the suction pressure Ps in the working chamber 28 becomes a predetermined set pressure Pset. This set pressure Pset is basically adjusted in advance by the spring load of the springs 39, 40, 64 and 104 and the load of the bellows 8, and the evaporator is frozen based on the relationship between the temperature in the evaporator and the suction pressure Ps. It is set as a pressure value that can be prevented. The set pressure Pset can be changed by changing the supply current (set current) to the solenoid 3. In this embodiment, by adjusting the press-fitting amount of the support member 27 in a state where the assembly of the control valve 1 is almost completed, the set load of the spring can be finely adjusted, and the set pressure Pset is accurately adjusted. Can do.

Next, the operation of the control valve 1 will be described.
When the solenoid 3 is not energized in the control valve 1, that is, when the air conditioner is not operating, no suction force acts between the core 42 and the plunger 46. For this reason, the valve body 38 is displaced downward by the urging force of the spring 39 and presses the valve drive body 30 downward. As a result, the valve element 33 is separated from the valve seat 20 and the main valve is fully opened. At this time, the valve body 38 is seated on the valve seat 36, the auxiliary valve is closed, the lower end portion of the valve driver 30 is seated on the valve seat 88, and the shut-off valve portion is closed. For this reason, the refrigerant introduced into the port 14 from the discharge chamber of the compressor passes through the fully opened main valve and flows from the port 12 to the crank chamber. On the other hand, the relief of the crank pressure Pc is cut off. Therefore, the crank pressure Pc is increased and the compressor is operated at the minimum capacity. At this time, the power element 6 does not substantially function.

  On the other hand, the valve body 38 is separated from the power element 6 by the biasing force of the spring 39, and the internal passage 37 of the valve body 38 is opened. That is, the on-off valve portion is opened with the shut-off valve portion closed. As a result, the crank pressure Pc is filled in the internal passage 35 of the valve drive body 30 and the internal passage 37 of the valve body 38, and the influence of the refrigerant pressure acting on the valve drive body 30 and the valve body 38 is cancelled. Since the differential pressure (Pc−Ps) does not act on each valve body, when the solenoid 3 is energized next time, the valve drive body 30 and thus the valve body 33 can be driven in the valve closing direction with a small solenoid force.

  On the other hand, when a control current is supplied to the solenoid 3 such as when the air conditioner is activated, the operating rod 58 is driven by the solenoid force. This solenoid force is transmitted to the valve driving body 30 and then to the valve body 33 through the operating rod 58 and the valve body 38. As a result, the valve body 33 is seated on the valve seat 20 to close the main valve, and the valve body 38 is separated from the valve seat 36 together with the closing of the main valve to open the auxiliary valve. However, since the displacement of the operating rod 58 is restricted by the engagement member 59 being locked to the valve drive body 30, the lift amount of the valve body 38 (that is, the opening degree of the sub-valve) is set to the predetermined value L. Match. At the time of start-up, the suction pressure Ps and the crank pressure Pc are normally relatively high, so that the bellows 8 maintains the contracted state and the sub-valve is opened.

  That is, when the starting current is supplied to the solenoid 3, the main valve is closed to restrict the introduction of the refrigerant discharged into the crank chamber, and at the same time, the sub valve is immediately opened to quickly relieve the refrigerant in the crank chamber to the suction chamber. As a result, the compressor can be started quickly. Further, even when the suction pressure Ps is low and the bellows 8 is extended, for example, when the vehicle is placed in a low temperature environment, the auxiliary valve can be opened by supplying a large current to the solenoid 3. And the compressor can be started quickly.

  When the current value supplied to the solenoid 3 is in the control state set to a predetermined value, the bellows 8 is extended because the suction pressure Ps and the crank pressure Pc are relatively low, and the valve body 38 is moved to the valve seat 36. Sit down and close the secondary valve. On the other hand, the valve element 33 operates in such a state that the sub-valve is closed to adjust the opening degree of the main valve. At this time, the valve element 33 operates in accordance with the force in the valve opening direction by the springs 39, 64, 104, the force in the valve closing direction by the spring 40, the solenoid force in the valve closing direction by the solenoid 3, and the suction pressure Ps. It stops at the valve lift position where the force against the solenoid force by the power element 6 is balanced.

  For example, when the refrigeration load increases and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 8 is reduced, so that the valve element 33 is displaced relatively upward (in the valve closing direction). As a result, the valve opening of the main valve decreases, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps changes in a decreasing direction. Conversely, when the refrigeration load is reduced and the suction pressure Ps is lower than the set pressure Pset, the bellows 8 expands. As a result, the urging force by the power element 6 acts in a direction opposite to the solenoid force. As a result, the force in the valve closing direction on the valve element 33 is reduced, the valve opening of the main valve is increased, and the compressor operates to reduce the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset.

  When such steady control is being performed, the load on the engine increases, and when it is desired to reduce the load on the air conditioner, the solenoid 3 in the control valve 1 is switched from on to off. Then, since a suction force does not act between the core 42 and the plunger 46, the bellows 8 is extended, the urging force of the spring 39 separates the valve element 33 from the valve seat 20, and the main valve is fully opened. At this time, since the valve body 38 is seated on the valve seat 36, the auxiliary valve is closed. At this time, the refrigerant having the discharge pressure Pd introduced from the discharge chamber of the compressor to the port 14 passes through the fully opened main valve and flows from the port 12 to the crank chamber. Therefore, the crank pressure Pc is increased and the compressor is operated at the minimum capacity.

Next, the foreign matter discharge promoting structure in the present embodiment will be described.
In the present embodiment, when foreign matter is contained in the refrigerant introduced from the port 14, it is possible to effectively prevent the foreign matter from entering the gap between the valve driver 30 and the guide hole 26, and to remove the foreign matter as a main component. A foreign matter discharge promoting structure that can discharge along the passage is provided. The details will be described below. FIG. 3 is a diagram illustrating a foreign matter discharge promoting structure and its function and effect. (A) is the G section enlarged view of FIG. (B) shows the foreign matter discharge promoting effect of the present embodiment, and (C) shows the foreign matter discharge structure and the operation of the comparative example. In FIG. 3A, for convenience, the boundary between the port 14 and the valve chamber 24 is indicated by a broken line.

  As shown in FIG. 3A, in the present embodiment, a recess 110 having a predetermined depth is provided on the outer peripheral surface of the valve driver 30 located in the valve chamber 24. The concave portion 110 functions as a “step portion” for receiving a foreign matter that has entered from the port 14. The recess 110 has a bottom surface 112 parallel to the axis of the valve driver 30. The wall surface 114 on one end side (the guide hole 26 side) of the bottom surface 112 is perpendicular to the bottom surface 112, and the wall surface 116 on the other end side (valve hole 18 side) of the bottom surface 112 is an obtuse angle (about approximately 150 degrees). The wall surface 114 faces the valve hole 18 and is located closer to the guide hole 26 than the port 14. The wall surface 116 is a tapered surface whose outer diameter gradually increases toward the valve hole 18 side.

  On the other hand, the valve seat 20 has a tapered surface whose inner diameter gradually decreases toward the valve hole 18 side, and the peripheral portion of the valve body 33 is seated in a line contact manner to close the main valve (valve portion). The angle and position of the taper surface are set so that a virtual extension line (refer to a two-dot chain line) along the taper surface of the wall surface 116 is displaced from the attaching / detaching portion of the valve element 33. That is, as shown in the drawing, the intersection point a between the extension line of the wall surface 116 and the valve seat 20 is configured to deviate from the attachment / detachment point b of the valve element 33 in the valve seat 20. Thereby, it is difficult for the foreign matter flowing along the wall surface 116 to directly collide with the attaching / detaching portion of the valve element 33.

  Further, the wall surface 118 on one end side (the guide hole 26 side) of the valve chamber 24 is configured to be positioned on the guide hole 26 side with respect to the recess 110. That is, the wall surface 114 of the recess 110 is configured to be positioned between the wall surface 118 of the valve chamber 24 and the port 14. As a result, the foreign matter that has entered from the port 14 is easily caught by the recess 110. That is, when a foreign substance enters from the port 14, the foreign substance has a certain amount of mass, and thus is considered to travel substantially straight along the port 14. The foreign object that has been traveling straight is received by the concave portion 110 and dammed by the wall surface 114, so that it is difficult to move toward the gap between the valve driver 30 and the guide hole 26. In particular, by positioning the wall surface 114 closer to the guide hole 26 than the port 14, the recess 110 is configured closer to the guide hole 26 so that the foreign object can be caught by the recess 110 even if it deviates from the straight direction. In addition, the wall surface 118 is positioned closer to the guide hole 26 than the wall surface 114 to secure the distance between the recess 110 and the guide hole 26, and the foreign matter hardly reaches the gap between the valve drive body 30 and the guide hole 26. Has been.

  With this configuration, as shown in FIG. 3B, most of the foreign matter W that has entered from the port 14 is directly guided to the valve hole 18 along the main passage (see the dotted line) or hits the recess 110. After that, it is guided along the bottom surface 112 to the valve hole 18 (refer to the alternate long and short dash line) or is guided to the valve hole 18 after being caught by the recess 110 (refer to the two-dot chain line). That is, by providing the recess 110 on the outer peripheral surface of the valve drive body 30, it is possible to suppress the foreign matter W from being directly guided to the sliding portion between the valve drive body 30 and the guide hole 26. The foreign matter W caught by the recess 110 is discharged to the valve hole 18 side by the suction force due to the differential pressure across the main valve (valve part).

  On the other hand, in the comparative example shown in FIG. 3C, the stepped portion that catches the foreign matter W is not provided in the valve drive body 130, so that a part of the foreign matter W that has entered from the port 14 is separated from the valve drive body 130. It becomes easy to be guided to the sliding portion with the guide hole 26. As a result, the foreign matter W is caught in the sliding portion, and the smooth operation of the valve drive body 130 and thus the valve body 33 is likely to be hindered. In other words, according to the present embodiment, such a problem can be solved.

  The wall surface 118 of the valve chamber 24 is positioned closer to the guide hole 26 than the recess 110, so that foreign matter can be easily removed by the solenoid force. That is, even if foreign matter W is present in the sliding portion between the valve drive body 30 and the guide hole 26, the operation rod 58 is energized by energizing the solenoid 3 (or increasing the energization amount to the solenoid 3). Operates in the direction of discharging the foreign matter W with respect to the guide hole 26. For this reason, in the unlikely event that the foreign object W is locked, the solenoid force can be effectively used for unlocking.

(Modification)
4 to 7 are partially enlarged cross-sectional views showing the foreign matter discharge promoting structure of the control valve according to the modification. The control valve of each modification differs from the above embodiment in the configuration of the stepped portion formed in the valve driver. For this reason, below, it demonstrates centering on difference with the said embodiment. In addition, in each figure, about the component substantially the same as the said embodiment, the same code | symbol is attached | subjected. In each figure, the boundary between the port and the valve chamber is indicated by a broken line for convenience.

  4A, in the valve driver 230, the wall surface 216 of the recess 210 on the valve hole 18 side is not a tapered surface but is perpendicular to the bottom surface 112. In the modification shown in FIG. Even in such a configuration, the foreign matter that has entered from the port 14 is caught by the recess 210, decelerated, and discharged to the valve hole 18 side. For this reason, the foreign matter discharge promotion effect can be obtained. However, it goes without saying that the discharge promoting effect is higher when the tapered surface is used as in the above embodiment.

  In the modification shown in FIG. 4B, the stepped portion 310 provided at the tip of the valve driver 330 does not have a wall surface on the valve hole 18 side, and a wall surface on one end side (the guide hole 26 side). Only 118 is provided. Even with such a configuration, foreign matters entering from the port 14 toward the guide hole 26 can be blocked by the wall surface 118 and guided to the valve hole 18 side along the bottom surface 312. For this reason, the foreign matter discharge promotion effect can be obtained. However, in this configuration, there is a difference between the effective pressure receiving diameter in the valve portion of the valve driving body 330 and the effective pressure receiving diameter in the sliding portion of the valve driving body 330. For this reason, when the pressure cancellation function is important, the configuration of the above embodiment is preferable.

  In the modification shown in FIG. 5A, in the valve driver 430, a concave portion 410 having a cross-sectional shape such that the wall surface 116 on the valve hole 18 side and the wall surface 114 on the guide hole 26 side are directly connected to each other. Is formed. Even in such a configuration, the foreign matter that has entered from the port 14 is caught and decelerated by the concave portion 410, and is guided to the valve hole 18 side by the tapered surface of the wall surface 116. For this reason, the foreign matter discharge promotion effect can be obtained. However, since the volume of the recessed part 410 is small, the capacity | capacitance which can catch a foreign material is small. For this reason, when the quantity of the foreign material contained in a refrigerant | coolant is anticipated much, the structure of the said embodiment is more preferable.

  In the modification shown in FIG. 5B, the recess 510 formed in the valve drive body 530 has a shape that is obtained by inverting the recess 410 in FIG. 5A in the axial direction. That is, the wall surface 516 on the valve hole 18 side is perpendicular to the axis, and the wall surface 514 on the guide hole 26 side is a tapered surface. Even in such a configuration, the foreign matter that has entered from the port 14 is caught by the recess 510 and decelerated, and is guided to the valve hole 18 side by the differential pressure across the main valve. For this reason, the foreign matter discharge promotion effect can be obtained. However, since the tapered surface of the wall surface 514 has a shape that easily guides foreign matter to the guide hole 26 side, it is considered that the discharge promoting function is inferior to the concave portion 410 of FIG.

  In the modification shown in FIG. 6A, in the valve drive body 630, the wall surface 614 of the recess 610 on the guide hole 26 side is not perpendicular to the bottom surface 112, but forms a slightly acute angle. The wall surface 614 is located closer to the guide hole 26 than the port 14 as a whole, but the tip thereof is located substantially on the extension of the open end of the port 14. Even in such a configuration, the foreign matter that has entered from the port 14 is caught by the recess 610 and decelerated, and is discharged to the valve hole 18 side along the tapered surface of the wall surface 116.

  Further, the portion of the valve chamber 624 located closer to the guide hole 26 than the port 14 is reduced in diameter, and the gap between the inner peripheral surface of the small diameter portion 625 and the outer peripheral surface of the valve driver 630 is reduced. A wall surface 618 on one end side (the guide hole 26 side) of the valve chamber 624 is located closer to the guide hole 26 than the recess 610, but its area is small. This makes it easier for foreign matter that enters along the port 14 to be guided to the recess 610 beyond the gap, and to be difficult to be guided to the sliding portion between the valve driver 630 and the guide hole 26. With such a configuration, the effect of promoting foreign matter discharge is enhanced as a whole.

  In the modification shown in FIG. 6B, the inside of the port 714 has a step shape. That is, by providing the partition wall 715 so as to block the lower half portion of the port 714, the refrigerant flow introduced into the port 714 is directed upward, that is, toward the valve hole 18 side. With such a configuration, it is easy to guide foreign matter directly to the valve hole 18.

  In the modification shown in FIG. 7, the stepped portion of the valve driver 830 is formed by assembling two members. FIG. 7B is an enlarged view of a portion H in FIG. That is, as shown in FIG. 7A, the first member 831 constituting the valve driver 830 is configured by press-fitting a cylindrical valve forming member 834 into the upper end portion of the stepped cylindrical main body 832. ing. The valve forming member 834 is assembled so that its lower half is inserted into the upper end of the main body 832.

  As shown in FIG. 7B, the main body 832 and the valve forming member 834 form a recess 820 that opens upward in the axial direction (the valve hole 18 side) on one end side (the guide hole 26 side) of the recess 810. As a result, the structure easily captures foreign matter. Although this structure is similar to the structure shown in FIG. 6, it is easier to process by comprising two members. That is, as shown in FIG. 6, when performing processing that makes the wall surface 614 an acute angle with respect to the bottom surface 112, it is necessary to use a tool having a special shape. In this regard, as shown in FIG. 7, the structure in which the main body 832 and the valve forming member 834 are separately processed and assembled has an advantage that it can be processed using a normal tool.

[Second Embodiment]
FIG. 8 is a cross-sectional view showing the configuration of the control valve according to the second embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 201 is configured by integrally assembling a valve main body 202 and a solenoid 203. The valve body 202 includes a stepped cylindrical body 205, a valve portion provided inside the body 205, and the like. The body 205 is provided with a port 12 (crank chamber communication port), a port 14 (discharge chamber communication port), and a port 16 (suction chamber communication port) from the upper end side.

  A valve hole 18 and a guide hole 226 are provided coaxially along the axis of the body 205. A valve seat 20 (main valve seat) is formed at the upper end opening end of the valve hole 18. And the elongate valve drive body 250 is arrange | positioned so that the body 205 may be penetrated to an axial direction.

  The valve drive body 250 has a stepped columnar shape, is slidably supported in the guide hole 226, an upper end portion thereof penetrates the valve hole 18, and a valve body 33 (main valve body) is integrally formed at the distal end portion thereof. Is provided. The valve element 33 is attached to and detached from the valve seat 20 from the port 12 side to open and close the main valve (valve part). The valve driver 250 is provided with an internal passage 35 penetrating in the axial direction. A lower end portion of the valve driver 250 forms a valve body 38 (sub valve body).

  A spring receiver 234 is screwed into the upper end opening of the body 205, and a spring 236 (which urges the valve body 33 in the valve closing direction of the main valve) between the spring receiver 234 and the valve drive body 250. Functioning as "biasing member"). The load of the spring 236 can be adjusted by the screwing amount of the spring receiver 234 into the body 205.

  The valve body 202 and the solenoid 203 are connected via a cylindrical connection member 238 made of a magnetic material. That is, the lower end portion of the body 205 is press-fitted into the upper end portion of the connection member 238, and the upper end portion of the case 52 of the solenoid 203 is press-fitted into the lower end portion of the connection member 238. A port 16 is provided at a lower end side portion of the body 205, and a working chamber 28 is formed in a space surrounded by the valve body 202 and the solenoid 203.

  On the other hand, the solenoid 203 includes a case 52, a cylindrical sleeve 244 inserted into the case 52, a core 242 fixed to the lower end portion of the sleeve 244, and a plunger 246 disposed to face the core 242 in the axial direction. The bobbin 48, the electromagnetic coil 50, and an end member 254 provided to seal the lower end opening of the case 52 are provided. In the present embodiment, the body 205, the core 242, the case 52, and the end member 254 form the body of the entire control valve 201.

  The plunger 246 is composed of two plungers that are divided with a thin film diaphragm 265 interposed therebetween. One of the plungers 266 is disposed inside the sleeve 244, and the other second plunger 268 is connected to the body 205 and the connection member. 238 and the space surrounded by 238. The diaphragm 265 seals the upper end opening of the sleeve 244 and forms a reference pressure chamber inside the sleeve 244. In this embodiment, the reference pressure chamber is filled with the atmosphere, but may be in a vacuum state. The diaphragm 265 is a pressure-sensitive member having flexibility, and is configured by stacking a plurality of polyimide films. The diaphragm 265 senses the suction pressure Ps on the side surface opposite to the reference pressure chamber, and displaces the outer peripheral edge of the suction pressure Ps as a fulcrum, thereby giving a driving force in the valve opening direction or the valve closing direction to the plunger 246. . In the modification, a metal diaphragm may be adopted as the diaphragm 265.

  A concave portion 270 is formed at the center of the upper surface of the second plunger 268, and the lower end surface of the valve driver 250 is supported by a flat surface at the center thereof so as to be able to contact and separate. That is, the center of the upper surface of the second plunger 268 forms a valve seat 36 (sub valve seat), and the valve body 38 is attached to and detached from the valve seat 36 to open and close the sub valve. A communication hole 271 for communicating the inside and the outside of the recess 270 is provided on the side of the second plunger 268.

  A flange portion 272 extending outward in the radial direction is provided at the upper end portion of the second plunger 268 so that the lower surface of the flange portion 272 corresponds to the upper surface of the connection member 238. Thus, an axial suction force is generated between the flange portion 272 and the connection member 238 when the solenoid 203 is energized, so that the valve body 38 can move quickly in the valve closing direction. The second plunger 268 is biased upward by a spring 274 (corresponding to a “biasing member”) interposed between the second plunger 268 and a step formed in the connection member 238. The spring 274 has a larger spring force than the spring 236 that biases the valve body 38.

  A flange portion 276 extending outward in the radial direction is provided at the upper end opening of the sleeve 244, and the diaphragm 265 is fixed so that the outer peripheral edge portion of the diaphragm 265 is sandwiched between the connecting member 238 and the flange portion 276. . An annular plate 278 is press-fitted into the lower end portion of the connecting member 238 so as to sandwich the diaphragm 265 and the flange portion 276 therebetween. In other words, the sleeve 244 is fixed to the connection member 238 and consequently to the body 205 by press-fitting the plate 278. An O-ring 280 for sealing is interposed between the lower end surface of the connecting member 238 and the diaphragm 265.

  The sleeve 244 and the core 242 are joined in the axial direction by press-fitting and caulking. A first plunger 266 is disposed inside the sleeve 244 so as to be movable back and forth in the axial direction. The first plunger 266 is press-fitted into one end of a shaft 258 that extends in the axial direction around the center of the core 242. The shaft 258 is positioned so that the axial position of one end thereof overlaps the axial position of the sliding portion 267 with the sleeve 244 in the first plunger 266.

  The other end of the shaft 258 is supported by a bearing member 290 screwed into the lower end portion of the core 242. A retaining ring 292 is fitted in the middle of the shaft 258, and a spring receiver 294 is provided so that upward movement is restricted by the retaining ring 292. A spring 275 that biases the first plunger 266 in a direction away from the core 242 via the shaft 258 is interposed between the spring receiver 294 and the bearing member 290. The load of the spring 275 can be adjusted by changing the screwing amount of the bearing member 290 into the core 242.

Next, the operation of the control valve 201 will be described.
In the control valve 201, when the solenoid 203 is not energized, no suction force acts between the core 242 and the plunger 246. Further, since the suction pressure Ps is high, the first plunger 266 that contacts the diaphragm 265 is displaced downward against the load of the spring 275. On the other hand, since the second plunger 268 is biased upward by the spring 274 so as to be separated from the first plunger 266, the valve body 33 is biased to its fully open position via the valve driver 250. At this time, the contact state between the valve driver 250 and the second plunger 268, that is, the closed state of the auxiliary valve is maintained. The refrigerant having the discharge pressure Pd introduced into the port 14 from the discharge chamber of the compressor passes through the fully opened valve portion and flows from the port 12 to the crank chamber. Therefore, the crank pressure Pc increases and the compressor operates at the minimum capacity.

  On the other hand, when the control current is supplied to the solenoid 203 as when the automobile air conditioner is started, the first plunger 266 moves the second plunger 268 against the urging force of the spring 274 via the diaphragm 265. Suction. For this reason, the second plunger 268 contacts the diaphragm 265 and moves downward, and accordingly, the valve element 33 is pushed down by the spring 236 and is seated on the valve seat 20, and the main valve is closed. At this time, the valve driver 250 is separated from the second plunger 268. That is, the auxiliary valve opens and the bleed function is exhibited.

  When the suction pressure Ps in the suction chamber becomes sufficiently low in this way, the diaphragm 265 senses the suction pressure Ps and is displaced upward, and the second plunger 268 contacts the valve driver 250. At this time, if the control current supplied to the solenoid 203 is reduced in accordance with the set temperature of the air conditioning, the second plunger 268 and the first plunger 266 are integrated in the adsorbed state, and the force by the suction pressure Ps and the spring 236 are integrated. , 274, 275 and the attraction force of the solenoid 203 move upward to a position where the resultant force balances. As a result, the valve element 33 is pushed up by the second plunger 268 and is separated from the valve seat 20 and set to a predetermined opening degree. Therefore, the refrigerant having the discharge pressure Pd is controlled to a flow rate corresponding to the opening degree and introduced into the crank chamber, and the compressor shifts to an operation with a capacity corresponding to the control current.

  When the control current supplied to the electromagnetic coil 50 of the solenoid 3 is constant, the diaphragm 265 senses the suction pressure Ps and controls the valve opening. For example, when the refrigeration load is increased and the suction pressure Ps is increased, the valve body 38 is displaced downward together with the valve driver 250, the second plunger 268, the diaphragm 265, and the first plunger 266. The valve opening decreases and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps decreases and approaches the set pressure. Conversely, when the refrigeration load decreases and the suction pressure Ps decreases, the valve body 38 is displaced upward to increase the valve opening, so that the compressor operates to reduce the discharge capacity. As a result, the suction pressure Ps increases and approaches the set pressure. In this way, the control valve 201 controls the discharge capacity of the compressor so that the suction pressure Ps becomes the set pressure Pset set by the solenoid 203.

Next, the foreign matter discharge promoting structure in the present embodiment will be described.
FIG. 9 is a diagram illustrating the foreign matter discharge promoting structure, and is an enlarged view of a portion I in FIG. 8. Also in the present embodiment, a step portion 910 is provided on the outer peripheral surface of the valve driver 250. The step portion 910 constitutes a reduced diameter portion at the top of the valve driver 250. In this embodiment, since the valve body 33 is disposed on the opposite side of the port 14 with respect to the valve hole 18, the stepped portion 910 is not in the valve chamber but in the intermediate pressure chamber 924 between the port 14 and the valve hole 18. Provided.

  A wall surface 918 on one end side (the guide hole 26 side) of the intermediate pressure chamber 924 is configured to be positioned closer to the guide hole 26 than the stepped portion 910. That is, the wall surface 114 of the step portion 910 is configured to be positioned between the wall surface 918 of the intermediate pressure chamber 924 and the port 14. As a result, the foreign matter that has entered from the port 14 is caught by the step portion 910, and the discharge to the valve hole 18 is promoted. The outer peripheral edge of the wall surface 114 has an edge shape and is configured such that foreign matter is less likely to enter.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to specific embodiments, and various modifications can be made within the scope of the technical idea of the present invention. Absent.

  In the said embodiment, the example which forms a level | step-difference part by making a part of outer periphery of a valve drive body small diameter was shown. In the modified example, a convex portion protruding radially outward is provided in part on the outer periphery of the valve drive body, the outer peripheral surface on the valve hole side of the convex portion of the valve drive body, and the valve hole side of the convex portion. It is good also as a structure which can catch a foreign material by the level | step-difference part formed with a wall surface.

  In the above embodiment, a hollow structure driving body is exemplified as the valve driving body. In a modified example, the valve driver may be a solid structure. For example, a solid shaft irrelevant to the bleed function may be used as a valve drive body, and a stepped portion (concave portion) may be provided on the outer peripheral surface thereof. The foreign matter discharge promoting structure may be applied to a control valve that does not have a bleed function.

  In the said embodiment, the example which applies a foreign material discharge | emission promotion structure to the solenoid valve which uses a solenoid as an actuator was shown. In a modified example, the same foreign matter discharge promoting structure may be applied to a control valve having an electric motor such as a stepping motor as an actuator. Moreover, in the said embodiment, the example which applies a foreign material discharge | emission promotion structure to the control valve for variable capacity compressors was shown. In a modification, you may apply to the other control valve provided in a refrigerating cycle. Or you may apply to the other control valve which controls not only a refrigerating cycle but the flow of a fluid.

  In addition, this invention is not limited to the said embodiment and modification, A component can be deform | transformed and embodied in the range which does not deviate from a summary. Various inventions may be formed by appropriately combining a plurality of constituent elements disclosed in the above embodiments and modifications. Moreover, you may delete some components from all the components shown by the said embodiment and modification.

  1 control valve, 2 valve body, 3 solenoid, 5 body, 6 power element, 8 bellows, 12, 14, 16 port, 18 valve hole, 20 valve seat, 24 valve chamber, 26 guide hole, 28 working chamber, 30 valve Drive body, 33 Valve body, 34 Valve hole, 35 Internal passage, 36 Valve seat, 37 Internal passage, 38 Valve body, 58 Actuation rod, 94 Engagement portion, 110 Recess, 112 Bottom surface, 114, 116, 118 Wall surface, 130 Valve driver, 201 control valve, 202 valve body, 203 solenoid, 205 body, 210 recess, 216 wall surface, 226 guide hole, 230, 250 valve driver, 265 diaphragm, 310 stepped portion, 312 bottom surface, 316 wall surface, 330 valve Driver, 410 recess, 430 valve driver, 510 concave portion, 514 wall surface, 530 valve driving body, 610 concave portion, 614, 618 wall surface, 624 valve chamber, 625 small diameter portion, 630 valve driving body, 714 port, 715 partition wall, 810, 820 concave portion, 830 valve driving body, 910 step Part, 918 wall surface, 924 intermediate pressure chamber.

Claims (4)

The valve hole and the guide hole are formed so as to communicate with each other in the axial direction through the intermediate pressure chamber, and an introduction port for introducing a fluid into the intermediate pressure chamber is formed to open to the side, and the valve hole A body formed with a derivation port for deriving the fluid that has passed through,
A valve body that opens and closes the valve portion by attaching to and detaching from the intermediate pressure chamber side to a valve seat provided at the opening end of the valve hole;
A valve drive body provided integrally with the valve body and slidably supported in the guide hole;
An actuator capable of applying a driving force in the opening / closing direction of the valve unit to the valve driver;
With
On the outer peripheral surface of the portion located in the intermediate pressure chamber in the valve drive body, has a stepped portion for receiving foreign matter that has entered from the introduction port,
The control valve characterized in that a wall surface facing the guide hole side in the step portion has a portion located on the valve hole side with respect to the introduction port.   2. The control valve according to claim 1, wherein a wall surface facing the guide hole side in the intermediate pressure chamber has a portion located closer to the valve hole side than the stepped portion.   3. The control valve according to claim 1, wherein an imaginary extension line along a wall surface facing the guide hole side in the stepped portion is deviated from an attaching / detaching portion of the valve body to the valve seat. Control for variable capacity compressor that changes the discharge capacity of the variable capacity compressor that compresses the refrigerant introduced into the suction chamber and discharges it from the discharge chamber by adjusting the flow rate of the refrigerant introduced from the discharge chamber into the crank chamber Configured as a valve,
The body includes a discharge chamber communication port that communicates with the discharge chamber as the introduction port, a crank chamber communication port that communicates with the crank chamber as the lead-out port, and a suction chamber communication port that communicates with the suction chamber. The control valve according to any one of claims 1 to 3.

Images