JP6064123B2 - Control valve - Google Patents

Description

  The present invention relates to a control valve, and more particularly to a control valve that is provided with a main valve and a sub valve in a common body and is driven by a single solenoid.

  In general, an air conditioner for an automobile compresses the refrigerant flowing through the refrigeration cycle and discharges it as a high-temperature / high-pressure gas refrigerant, a condenser that condenses the gas refrigerant, and adiabatic expansion of the condensed liquid refrigerant. And an expansion device that converts the refrigerant into a low-temperature and low-pressure refrigerant, an evaporator that exchanges heat with the air in the vehicle interior by evaporating the refrigerant, and the like. The refrigerant evaporated in the evaporator is returned to the compressor and circulates in the refrigeration cycle.

  As this compressor, a variable capacity compressor (also simply referred to as “compressor”) capable of varying the refrigerant discharge capacity is used so that a constant cooling capacity is maintained regardless of the engine speed. In this compressor, a piston for compression is connected to a swing plate attached to a rotary shaft that is driven to rotate by an engine, and the discharge amount of the refrigerant is changed by changing the stroke of the piston by changing the angle of the swing plate. adjust. The angle of the swing plate can be continuously changed by introducing a part of the discharged refrigerant into the sealed crank chamber and changing the balance of pressure applied to both surfaces of the piston. The pressure in the crank chamber (hereinafter referred to as “crank pressure”) Pc is controlled by a variable displacement compressor control valve (also simply referred to as “control valve”) provided between the discharge chamber and the crank chamber of the compressor. The

  Such a control valve adjusts the valve opening degree by supplying current from the outside to a solenoid as a drive unit. When it is necessary to quickly exhibit the air conditioning function, such as when the air conditioner is started, the valve portion is closed by supplying a maximum current to the solenoid, for example, the crank pressure Pc is lowered and the swing plate is used as the rotating shaft. In contrast, the compressor can be operated at the maximum capacity by being tilted greatly. When the engine load on the vehicle is large, the solenoid is turned off to fully open the valve, and the crank pressure Pc is increased to make the swing plate substantially perpendicular to the rotating shaft, thereby reducing the compressor with the minimum capacity. Can be driven.

  In such a control valve, a main valve is provided in a main passage communicating the discharge chamber and the crank chamber, while a sub valve is provided in a sub passage communicating the crank chamber and the suction chamber. Some are driven by a solenoid (see, for example, Patent Document 1). According to this control valve, the opening degree of the main valve is adjusted with the sub valve closed during the steady operation of the air conditioner. Thereby, the crank pressure Pc can be controlled as described above, and the discharge capacity of the compressor can be controlled. On the other hand, when the air conditioner is started, the sub valve is opened while the main valve is closed, and thereby the crank pressure Pc is rapidly reduced, so that the compressor can be promptly shifted to the maximum capacity operation state. Moreover, since it was set as the structure which opens and closes a some valve with a single solenoid, the whole control valve can be comprised compactly.

  Such a control valve is provided with a main valve body and a sub-valve body on the same axis for driving the main valve and the sub-valve by a single solenoid, and an operating rod disposed along the axis. And a mechanism for transmitting a solenoid force to each valve body via the. A main valve hole is provided in the body of the control valve, and a sub valve hole is provided in the main valve body. That is, the auxiliary passage is provided so as to penetrate the main valve body. And the main valve is opened and closed by attaching and detaching the main valve body to the main valve seat provided at the opening end of the main valve hole, and with respect to the sub valve seat provided at the opening end of the sub valve hole. The auxiliary valve is opened and closed by attaching and detaching the auxiliary valve body. However, during the steady operation of the compressor, the auxiliary valve body is pressed against the auxiliary valve seat, and the closed state of the auxiliary valve is maintained. When the compressor is started, the solenoid force is maximized, and the auxiliary valve can be opened by further energizing the auxiliary valve body in the valve opening direction with the main valve element seated on the main valve seat.

JP 2008-240580 A

  However, the control valve specifically disclosed in the cited document 1 has a structure in which one end of the operating rod and the sub-valve element are fixed in order to directly transmit the solenoid force to the sub-valve element. On the other hand, the other end of the operating rod is fixed to a solenoid plunger. That is, the auxiliary valve body, the operating rod, and the plunger are integrally provided. For this reason, every time the sub-valve is seated on the sub-valve seat when the sub-valve is opened / closed, the sub-valve seat is loaded not only with the sub-valve but also with the weight of the operating rod and plunger as an impact load. Become. As a result, wear and deformation may occur in the formation portion of the sub valve seat in the main valve body, which may hinder the sealing performance of the sub valve. Moreover, since the weight of the working part which gives an impact load to a subvalve seat becomes large, the problem of a striking sound also arises. Such a problem occurs not only in the variable displacement compressor control valve as shown in the cited document 1, but also in a control valve in which the main valve and the sub valve are driven by a single solenoid. obtain.

  The present invention has been made in view of such problems, and in a control valve that drives the main valve and the sub valve by a single solenoid, it suppresses the generation of wear and impact noise when the sub valve is closed. For the purpose.

  In order to solve the above problems, a control valve according to an aspect of the present invention includes an introduction / exit port for introducing or deriving a working fluid, an introduction port for introducing the working fluid, and a body provided with a deriving port for deriving the working fluid. An internal passage that is slidably supported by the body and that opens and closes the main valve seat by opening and closing the main valve seat formed between the introduction port and the introduction / extraction port, while communicating the introduction / extraction port and the outlet port. The formed main valve body, the sub-valve body that opens and closes the sub-valve by attaching to and detaching from the end of the internal passage or the sub-valve seat formed inside, and the one end of the body that senses the pressure to be sensed. , Provided at the other end side of the body and a pressure sensitive part that generates a driving force for driving the main valve body in the valve opening direction when the sensed pressure becomes lower than the set pressure, and according to the amount of current supplied Solenoid force to drive the main valve body in the valve closing direction. Comprising a solenoid which is interposed between the pressure sensitive portion and a solenoid, and a direct transfer possible actuation rod relative to the pressure sensing section without via any of the solenoid force of the main valve body and the sub-valve element.

  According to this aspect, the operating rod is interposed between the pressure sensing unit and the solenoid, so that the balance of the driving force in the valve opening direction and the valve closing direction of the main valve is adjusted. It is possible to transmit directly to the pressure-sensitive part without using any of the valve body and the sub-valve body. For this reason, even if the sub-valve element is seated on the sub-valve seat when the solenoid is turned off, the effect of the weight of the actuating rod and the solenoid does not substantially occur during the seating. As a result, it is possible to suppress the occurrence of wear and impact sound when the auxiliary valve is closed.

  ADVANTAGE OF THE INVENTION According to this invention, in the control valve which drives a main valve and a subvalve with a single solenoid, generation | occurrence | production and the generation | occurrence | production of an impact sound when a subvalve is closed can be suppressed.

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 operation | movement of a control valve. It is a figure showing operation | movement of a control valve. It is a partial expanded sectional view corresponding to the upper half part of the control valve concerning a 2nd embodiment. It is a partial expanded sectional view corresponding to the upper half part of the control valve concerning a 3rd embodiment. It is a partial expanded sectional view corresponding to the upper half part of the control valve concerning a 4th embodiment. It is a partial expanded sectional view corresponding to the upper half part of the control valve concerning a 5th embodiment. It is sectional drawing which shows the structure of the control valve which concerns on 6th Embodiment. It is a partial expanded sectional view corresponding to the upper half part 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 refrigerant introduced from the discharge chamber into the crank chamber so as to keep the suction pressure Ps of the compressor at a set pressure. 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 inside the body 5, a power element 6 that generates a force that opposes the solenoid force in order to adjust the opening of the main valve, and the like. It has. The power element 6 functions as a “pressure sensitive part”.

  Ports 12, 14, and 16 are provided on the side of the body 5 from the upper end side. 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. The upper end opening of the body 5 is sealed by the end member 13, and the lower end of the body 5 is connected to the upper end of the solenoid 3. In the body 5, a main passage that communicates the port 12 and the port 14 and a sub passage that communicates 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 main valve hole 18 is provided in the main passage, and a main valve seat 20 is formed on the tapered surface of the lower end opening edge.

  The port 14 introduces a refrigerant having a discharge pressure Pd from the discharge chamber. The port 12 guides the refrigerant having the crank pressure Pc via the main valve toward the crank chamber during steady operation of the compressor, and introduces the refrigerant having the crank pressure Pc discharged from the crank chamber when the compressor is started. The refrigerant introduced at this time is guided to the auxiliary valve. A working chamber 22 is formed between the port 12 and the main valve hole 18 to be filled with the crank pressure Pc. The power element 6 is disposed in the working chamber 22. The port 16 introduces the refrigerant having the suction pressure Ps during the steady operation of the compressor, and guides the refrigerant having the suction pressure Ps via the sub valve toward the suction chamber when starting the compressor.

  A guide hole 24 is formed coaxially with the main valve hole 18 between the port 14 and the port 16. A valve chamber 26 is formed between the guide hole 24 and the port 14, and a pressure chamber 28 is formed between the guide hole 24 and the port 16. A cylindrical main valve body 30 is slidably inserted into the guide hole 24. The main valve body 30 opens and closes the main valve by being attached to and detached from the main valve seat 20 from the valve chamber 26 side, and adjusts the flow rate of refrigerant flowing from the discharge chamber to the crank chamber. On the other hand, a sub valve hole 32 is provided inside the main valve body 30, and a sub valve seat 34 is formed at the upper end opening of the sub valve hole 32. A lower portion of the main valve body 30 extends to the pressure chamber 28, and a communication hole 35 is provided near the lower end of the main valve body 30 to communicate the inside and the outside. In the working chamber 22, a stepped disk-like subvalve element 36 is disposed. The auxiliary valve body 36 is disposed opposite to the main valve body 30 in the axial direction, and opens and closes the auxiliary valve by being attached to and detached from the auxiliary valve seat 34.

  Further, an elongated operating rod 38 is provided along the axis of the body 5. The upper end portion of the operating rod 38 is connected to the power element 6 so as to be operatively connectable, and the lower end portion is connected to a plunger 50 described later of the solenoid 3 so as to be operatively connectable. The upper half of the actuating rod 38 penetrates the main valve body 30 and the sub-valve element 36, and supports the sub-valve element 36 from below at the step provided near the upper end thereof. A spring receiving member 40 is provided at an intermediate portion of the operating rod 38. Between the main valve body 30 and the spring receiving member 40, a spring 42 (functioning as a "first urging member", "elastic body") that urges the main valve body 30 in the valve closing direction of the main valve. It is intervened. On the other hand, between the power element 6 and the sub-valve element 36, the sub-valve element 36 is urged in the valve closing direction and the main valve element 30 is urged in the valve opening direction. 44 (functioning as “second urging member” and “elastic body”) is interposed.

  The sub-valve body 36 is not fixed to the operating rod 38, and is supported from below while being loosely fitted with a predetermined clearance. On the other hand, the lower end portion of the actuating rod 38 is not fixed to the plunger 50 and is supported from below while being loosely fitted with a predetermined clearance. That is, the actuating rod 38 is interposed between the power element 6 and the plunger 50, but is not fixed to either. However, since the upper end portion of the operating rod 38 is inserted into a recess provided in the power element 6 and the lower end portion of the operating rod 38 is inserted into a recess provided in the plunger 50, the operating rod 38 is connected to the power element 6 and the power element 6. The plunger 50 does not fall off.

  On the other hand, the power element 6 includes a bellows 45 that is displaced by sensing the crank pressure Pc, and generates a force that opposes the solenoid force by the displacement of the bellows 45. This counter force is also transmitted to the main valve body 30 via the actuating rod 38 and the auxiliary valve body 36. When the auxiliary valve body 36 is seated on the auxiliary valve seat 34 and closes the auxiliary valve, the relief of the refrigerant from the crank chamber to the suction chamber is blocked. Further, when the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and opens the auxiliary valve, the refrigerant is allowed to be relieved from the crank chamber to the suction chamber.

  On the other hand, the solenoid 3 includes a stepped cylindrical core 46, a bottomed cylindrical sleeve 48 assembled so as to seal the lower end opening of the core 46, and the sleeve 46 accommodated in the axial direction of the core 46. A cylindrical plunger 50 disposed opposite to the core 46, a cylindrical bobbin 52 extrapolated to the core 46 and the sleeve 48, an electromagnetic coil 54 wound around the bobbin 52 and generating a magnetic circuit by energization, and an electromagnetic coil A cylindrical case 56 provided so as to cover 54 from the outside and also functioning as a yoke, and an end member 58 provided so as to seal the lower end opening of the case 56 are provided. In the present embodiment, the body 5, the core 46, the case 56, and the end member 58 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 46. The diameter of the upper half of the core 46 is expanded, and a pressure chamber 28 for satisfying the suction pressure Ps is formed between the core 46 and the body 5. The operating rod 38 is inserted so as to penetrate the center of the core 46 in the axial direction. When the lower end portion of the operating rod 38 is inserted into the upper half of the plunger 50, the operating rod 38 and the plunger 50 are connected coaxially. The operating rod 38 is supported from below by the plunger 50 and is configured to be operatively connected to the main valve body 30, the sub-valve body 36 and the power element 6. The actuating rod 38 transmits a solenoid force, which is a suction force between the core 46 and the plunger 50, on the one hand directly to the sub-valve body 36 and on the other hand to the main valve body 30 via the spring 42. The actuating rod 38 also transmits to the plunger 50 a reaction force due to the expansion and contraction of the power element 6, that is, a force that opposes the solenoid force. In the present embodiment, the urging force of the spring 44 is transmitted to the operating rod 38 via the sub-valve body 36, thereby pressing the operating rod 38 against the plunger 50, so that the operating rod 38 and the plunger 50 are connected. Is maintained stably.

  A ring-shaped shaft support member 60 is press-fitted into the upper end portion of the core 46, and the operating rod 38 is supported by the shaft support member 60 so as to be slidable in the axial direction. A communication groove (not shown) parallel to the axis is formed at a predetermined location on the outer peripheral surface of the shaft support member 60. The suction pressure Ps introduced / extracted from the port 16 is also guided to the inside of the sleeve 48 through the communication groove, the communication passage 62 formed by the gap between the operating rod 38 and the core 46.

  The communication path 62 functions as an orifice for making the inside of the sleeve 48 an oil damper chamber. That is, in the present embodiment, in the manufacturing process of the control valve 1, oil of the same type as that contained in the refrigerant is lubricated in the sleeve 48 in advance 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 48. With such a configuration, the sleeve 48 can function as an oil damper chamber, and minute vibrations of the plunger 50 disposed in the sleeve 48 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 48. 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 44 functions as an off-spring that urges the core 46 and the plunger 50 in a direction to separate them from each other. The spring load of the spring 44 is set larger than the spring load of the spring 42.

  The sleeve 48 is made of a nonmagnetic material. Plural communicating grooves 66 parallel to the axis are provided on the side surface of the plunger 50, and plural communicating grooves 68 extending in the radial direction and communicating between the inside and the outside are provided on the lower end surface of the plunger 50. With such a configuration, the suction pressure Ps is guided to the back pressure chamber 70 through the gap between the plunger 50 and the sleeve 48 even when the plunger 50 is located at the bottom dead center as shown in the figure.

  A pair of connection terminals 72 connected to the electromagnetic coil 54 extend from the bobbin 52, and extend through the end members 58 to the outside. For convenience of explanation, only one of the pair is displayed in the figure. The end member 58 is attached so as to seal the entire structure in the solenoid 3 included in the case 56 from below. The end member 58 is formed by molding (injection molding) of a resin material having corrosion resistance, and the resin material is also filled in the gap between the case 56 and the electromagnetic coil 54. In this way, the resin material fills the gap between the case 56 and the electromagnetic coil 54 so that the heat generated in the electromagnetic coil 54 can be easily transferred to the case 56 and the heat dissipation performance is enhanced. The end portion of the connection terminal 72 is drawn out from the end member 58 and is 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 labyrinth seal 74 composed of a plurality of annular grooves for suppressing the flow of the refrigerant is provided on the sliding surface of the main valve body 30 with the guide hole 24. The lower end opening of the main valve body 30 has a slightly reduced inner diameter, and the lower end surface of the reduced diameter portion can be appropriately engaged and connected to the operating rod 38 (acting as an “engaged portion”). Configure. The actuating rod 38 has a stepped columnar shape whose diameter gradually decreases upward, and an engaging portion 78 is constituted by a first step provided near the actuating surface 76. Further, a support portion 80 (functioning as a “pressing portion”) is configured by the second step provided in the vicinity of the sub valve seat 34.

  A through hole in the axial direction is formed in the center of the sub-valve body 36, and the upper end portion of the operating rod 38 is penetrated. The sub-valve body 36 is formed so that the center of the lower end surface thereof is flat, and is supported from below so as to abut the support portion 80. The sub-valve element 36 has a tapered shape whose cross section increases outwardly from the center of the lower end surface, and is attached to and detached from the sub-valve seat 34 at the tapered surface. In the state where the sub-valve element 36 is seated on the sub-valve seat 34 as shown in the drawing, the position of each step is set so that the engaging portion 78 is separated from the operating surface 76 with a predetermined interval L. Has been. The predetermined interval L functions as so-called “play”.

  When the solenoid force is increased, the actuating rod 38 is displaced relative to the main valve body 30 against the biasing force of the spring 42, thereby lifting the sub valve body 36 from the sub valve seat 34 and opening the sub valve. Can do. Further, the solenoid force can be directly transmitted to the main valve body 30 in a state where the engaging portion 78 and the operation surface 76 are engaged (contacted), and the main valve body can be transmitted with a force larger than the urging force of the spring 42. 30 can be pressed in the valve closing direction of the main valve. This configuration can function as an unlocking mechanism (interlocking mechanism) that releases the main valve body 30 when the main valve body 30 is locked by the foreign matter being caught in the sliding portion between the main valve body 30 and the guide hole 24. it can. In this embodiment, the main valve body 30 is provided with an operating surface 76 as an “engaged portion”, and the engaging portion 78 of the operating rod 38 comes into surface contact with the operating surface 76 and presses it. However, the contact state between the engaging portion 78 and the engaged portion is not limited to surface contact, and may be line contact or point contact, and it is only necessary that the solenoid force can be directly transmitted to the main valve body 30 by the engagement of both.

  A retaining ring 82 is fitted in an intermediate portion of the operating rod 38, and a spring receiving member 40 is provided so that the downward movement is restricted by the retaining ring 82. The power element 6 has an upper end opening of the bellows 45 closed by a first stopper 84 (corresponding to a “base member”) and a lower end opening closed by a second stopper 86 (corresponding to a “base member”). It is configured. The inside of the bellows 45 is a sealed reference pressure chamber S, and a spring 88 that biases the bellows 45 in the extending direction is interposed between the first stopper 84 and the second stopper 86. The reference pressure chamber S is in a vacuum state in this embodiment. The first stopper 84 is integrally formed with the end member 13. Therefore, the first stopper 84 is fixed to the body 5.

  On the other hand, a fitting groove 90 having a predetermined depth along the axial direction is provided in the center of the lower surface of the second stopper 86, and the upper end of the operating rod 38 is detachably connected. The fitting groove 90 comes into contact with the upper end surface of the operating rod 38 at the flat bottom surface 92. Since the fitting groove 90 has a tapered shape in which the inner diameter is increased downward from the bottom surface 92, the upper end portion of the operating rod 38 does not slide with respect to the fitting groove 90. The actuating rod 38 can be displaced integrally with the power element 6 with its upper end face engaged with the second stopper 86, and is relatively displaced with the power element 6 with its upper end face spaced from the second stopper 86. It is possible.

  Since the spring 88 biases the first stopper 84 and the second stopper 86 in a direction in which the first stopper 84 and the second stopper 86 are separated from each other, the bellows 45 responds to a differential pressure between the crank pressure Pc of the working chamber 22 and the reference pressure of the reference pressure chamber S. It expands or contracts in the axial direction (the opening and closing direction of the main valve and sub valve). However, even if the differential pressure increases, if the bellows 45 contracts by a predetermined amount, the front end surfaces of the first stopper 84 and the second stopper 86 come into contact with each other and are locked, so that the contraction is restricted.

  In the above configuration, the main valve body 30 and the main 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 auxiliary valve body 36 and the auxiliary valve seat 34 constitute an auxiliary valve, and the opening and closing of the auxiliary valve permits 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 of the bellows 45, the effective pressure receiving diameter B of the main valve body 30 in the main valve, and the effective pressure receiving diameter C of the sliding portion of the main valve body 30 are set equal. For this reason, in the state where the main valve 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 main valve body 30 is substantially canceled. As a result, the main valve body 30 opens and closes based on the suction pressure Ps received in the pressure chamber 28 in the control state of the main valve. That is, the control valve 1 functions as a so-called Ps sensing valve.

  In such a configuration, when the control valve 1 is in a stable control state, the main valve operates autonomously so that the suction pressure Ps of the pressure chamber 28 becomes the predetermined set pressure Pset. This set pressure Pset is basically adjusted in advance by the spring load of the springs 42, 44, 88, and is set as a pressure value that can prevent freezing of the evaporator from the relationship between the temperature in the evaporator and the suction pressure Ps. The The set pressure Pset can be changed by changing the supply current (set current) to the solenoid 3. In this embodiment, the set load of the spring can be finely adjusted by readjusting the press-fitting amount of the end member 13 with the assembly of the control valve 1 substantially completed, and the set pressure Pset is accurately adjusted. be able to.

Next, the operation of the control valve will be described.
3 and 4 are diagrams showing the operation of the control valve, and correspond to FIG. FIG. 2 which has already been described shows the minimum capacity operation state of the control valve. FIG. 3 shows a state when the bleed function of the control valve is operated. FIG. 4 shows a relatively stable control state. In the following, description will be given based on FIG. 1 and with reference to FIGS.

  When the solenoid 3 is not energized in the control valve 1, that is, when the automotive air conditioner is not operating, no suction force acts between the core 46 and the plunger 50. On the other hand, the suction pressure Ps is relatively high. For this reason, as shown in FIG. 2, the urging force of the spring 44 is transmitted to the main valve body 30 via the sub-valve body 36 in a state where the bellows 45 is contracted. As a result, the main valve body 30 is separated from the main valve seat 20 and the main valve is fully opened. At this time, since the auxiliary valve body 36 is seated on the auxiliary valve seat 34, the auxiliary valve is closed. The power element 6 does not substantially function.

  On the other hand, when a control current is supplied to the electromagnetic coil 54 of the solenoid 3 at the time of starting the air conditioner for automobiles, as shown in FIG. 3, the operating rod 38 is driven by the solenoid force. This solenoid force is transmitted to the main valve body 30 via the spring 42 on the one hand and directly to the sub-valve body 36 via the operating rod 38 on the other hand. As a result, the main valve body 30 is seated on the main valve seat 20 to close the main valve, and the sub-valve body 36 is separated from the sub-valve seat 34 together with the closing of the main valve to open the sub-valve. However, since the displacement of the actuating rod 38 is restricted when the engaging portion 78 is locked to the actuating surface 76, the lift amount of the sub-valve element 36 (that is, the opening degree of the sub-valve) is shown in FIG. It coincides with the predetermined interval L. On the other hand, normally, since the suction pressure Ps is relatively high at the time of startup, the bellows 45 maintains the contracted state and the open state of the auxiliary valve is maintained. 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 45 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 a control state set to a predetermined value, as shown in FIG. 4, the suction pressure Ps is relatively low, so that the bellows 45 expands and the sub-valve element 36 It sits on the auxiliary valve seat 34 and closes the auxiliary valve. On the other hand, the main valve body 30 operates in such a state that the sub-valve is closed so as to adjust the opening degree of the main valve. At this time, the main valve body 30 operates in accordance with the force in the valve opening direction by the spring 44, the force in the valve closing direction by the spring 42, the solenoid force in the valve closing direction by the solenoid 3, and the suction pressure Ps. Stops at the valve lift position where the force against the solenoid force due to 6 is balanced.

  For example, when the refrigeration load increases and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 45 is reduced, so that the main valve body 30 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 45 extends. 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 main valve body 30 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 the suction force does not act between the core 46 and the plunger 50, the bellows 45 extends, the main valve body 30 is separated from the main valve seat 20 by the urging force of the spring 44, and the main valve is fully opened. Become. At this time, since the auxiliary valve body 36 is seated on the auxiliary valve seat 34, 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.

  In particular, when the solenoid 3 is switched from on to off in this way, the foreign matter that has entered with the refrigerant from the port 14 slides between the main valve body 30 and the guide hole 24 in accordance with the valve opening operation of the main valve body 30. It becomes easy to be drawn into. Immediately after the solenoid 3 is turned off, the differential pressure (Pd-Ps) between the port 14 and the port 16 is relatively large, and the main valve body 30 slides foreign matter accumulated at the high-pressure side opening end of the guide hole 24. This is because it operates in the direction of drawing into the part. Then, when the main valve body 30 is about to be displaced in the valve closing direction by switching the solenoid 3 from OFF to ON again, there is a possibility that a lock due to the biting of the foreign matter may occur. In this embodiment, even when such a lock occurs, an interlocking mechanism (lock release mechanism) that can release the lock is provided.

  The sub-valve element 36 operates in accordance with the valve closing force by the spring 44, the valve opening force by the spring 42, the valve opening solenoid force by the solenoid 3, and the suction pressure Ps. The opening / closing state is determined by the balance with the force against the solenoid force generated by the above, and the balance is set so that the sub valve is closed when the suction pressure Ps value is lower than a predetermined value except at the time of starting. For this reason, the setting value (valve opening setting value) of the suction pressure Ps when the auxiliary valve is opened can be changed according to the current value supplied to the solenoid 3. That is, according to the interlocking mechanism of the present embodiment, the valve opening set value of the sub valve can be changed by the supply current to the solenoid 3, and the lock of the main valve body 30 is released by the solenoid force. Can do.

  That is, the discharge refrigerant introduced from the port 14 may contain foreign matters such as metal powder, and the foreign matters enter the sliding portion between the main valve body 30 and the guide hole 24 to smoothly move the main valve body 30. There is a concern that the operation of the main valve body 30 may be locked in the worst case. Since there is a relatively large differential pressure (Pd-Ps) between the port 14 and the port 16, foreign matter entering from the port 14 is easily attracted to the opening of the guide hole 24, and the compressor is switched from on to off. This is because, when the main valve body 30 is largely displaced toward the fully open state, the foreign matter is easily drawn into the sliding portion.

  In this way, when foreign matter accumulates and adheres to the sliding portion when the main valve is fully opened, the foreign matter is caught between the main valve body 30 and the guide hole 24 when the compressor is turned on again. There is a possibility that the operation of the valve body 30 may be locked. In this case, in the configuration in which the spring 42 is urged only in the valve closing direction, a driving force for pushing out the foreign matter and moving the main valve body 30 in the valve closing direction may not be obtained. Then, even if the auxiliary valve can be opened, it is difficult to start the compressor because the opening of the main valve is larger.

  Therefore, in this embodiment, the lock is released by directly transmitting the solenoid force to the main valve body 30 via the engaging portion 78 of the operating rod 38. Also, with such a configuration, it is possible to release the lock by applying a larger load by supplying a current exceeding the maximum current supplied during steady control. That is, when the foreign matter is caught between the main valve body 30 and the guide hole 24 and the operation of the main valve body 30 is locked, the actuating rod 38 is driven in the valve closing direction by the solenoid force. At this time, if the sub-valve should normally be kept closed, the main valve body 30 is locked. Therefore, the operating rod 38 is displaced relative to the main valve body 30, and the sub-valve body 36 is moved. The secondary valve seat 34 is lifted. That is, the auxiliary valve is opened before the main valve is closed. However, here, the actuating rod 38 is driven as it is, the engaging portion 78 is abutted against the actuating surface 76, and the solenoid force is directly applied to the main valve body 30.

  Thereby, not only the urging force of the spring 42 but also a large solenoid force is directly applied to the main valve body 30. At this time, the spring 42 is also compressed, so that the main valve body 30 is pressed with an urging force larger than the set load set for steady control. As a result, the main valve body 30 is unlocked by the foreign matter caught in the sliding portion, and the foreign matter can be pushed out in the process of operating the main valve body 30 in the valve closing direction. The foreign matter pushed out at this time floats in the valve chamber 26. On the other hand, the main valve can be closed because the lock of the main valve body 30 has been released. When the lock is released in the process of operating the main valve body 30 in the closing direction of the main valve in this way, the engaging portion 78 is separated from the operating surface 76 by the urging force of the spring 42, and the auxiliary valve is temporarily moved. Closed state.

  Then, by further driving the operating rod 38 after the main valve is closed, the auxiliary valve can be opened as it is, and the refrigerant can escape from the crank chamber to the suction chamber. Thus, when the compressor is started and the main valve is opened, the refrigerant can be supplied from the discharge chamber to the crank chamber. At this time, the floating foreign matter can be discharged together with the refrigerant through the main valve. Note that, depending on the state of foreign matter sticking to the main valve body 30, there may be a case where the lock by the foreign matter can be broken, but not all of the stuck foreign matter can be peeled off. However, since the lock can be released in this way, the function of the control valve 1 can be ensured. Further, it can be expected that the remaining foreign matter is gradually removed in the process of repeatedly turning the solenoid 3 on and off.

  As described above, in the present embodiment, the operating rod 38 is interposed between the power element 6 and the plunger 50, so that the driving force in the valve opening direction and the valve closing direction is balanced. Adjusted. In such a configuration, since the actuating rod 38 passes through the main valve body 30 and the sub valve body 36 and is connected to the power element 6, the solenoid force does not pass through either the main valve body 30 or the sub valve body 36. Direct transmission to the power element 6 is possible. On the other hand, the auxiliary valve body 36 is not fixed to the operating rod 38 by press fitting or the like, and is supported from below while being loosely fitted to the operating rod 38. For this reason, the auxiliary valve body 36 is configured to receive the force in the valve opening direction of the auxiliary valve via the operating rod 38, but not the force in the valve closing direction. For this reason, even if the sub-valve body 36 is seated on the sub-valve seat 34 by the biasing force of the spring 44 when the solenoid 3 is turned off, the weight of the actuating rod 38 and the plunger 50 is not affected during the seating. As a result, it is possible to suppress the wear of the valve portion and the occurrence of a striking sound when the auxiliary valve is closed.

  In the present embodiment, the operating rod 38 is not fixed to either the sub-valve body 36 or the plunger 50. That is, when the auxiliary valve is opened and closed, these are operatively connected, and are loosely fitted to each other. Therefore, when the auxiliary valve body 36 is seated on the auxiliary valve seat 34, there is an allowance for autonomous alignment. In other words, the dimensional accuracy of these connecting portions can be relaxed, and the assemblability can be improved.

  Furthermore, in this embodiment, even if the main valve body 30 is locked due to the entry of foreign matter into the guide hole 24 when the main valve is opened, the unlocking mechanism by the solenoid force operates. If the lock cannot be released even when the maximum current of the steady control is supplied, it is possible to release the lock by applying a larger solenoid force by supplying the additional current to the solenoid 3. As a result, the urging force accompanying the driving of the operating rod 38 acts on the main valve body 30 in the direction of closing the main valve (that is, the direction in which the lock is released) and opens the sub valve on the sub valve body 36. Acts in the direction (that is, the direction in which the auxiliary valve functions). That is, the function for releasing the lock of the main valve body 30 and the function for opening / closing the sub valve (function for changing the valve opening set value of the sub valve according to the current supply value) can be operated simultaneously. As a result, the lock can be reliably released, and the auxiliary valve can be opened to start the compressor normally.

[Second Embodiment]
FIG. 5 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the second embodiment. The control valve of the present embodiment is different from the first embodiment in the configuration of the pressure sensitive part and the support structure of the main valve body. For this reason, below, it demonstrates centering on difference with 1st 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 different from the first embodiment in that the power element 206 includes a diaphragm instead of a bellows as a pressure-sensitive member. The control valve 201 is configured by integrally assembling a valve main body 202 and a solenoid 203. Also in this embodiment, the body 205, the core 46, the case 56, and the end member 58 form the body of the entire control valve 201.

  The power element 206 includes a hollow housing 210 fixed to the upper end opening of the body 205, and a thin film diaphragm 245 disposed so as to partition the inside of the housing 210 into a sealed space S1 and an open space S2. Is done. The open space S <b> 2 communicates with the working chamber 22. The diaphragm 245 is made of a polyimide film in the present embodiment, but may be made of a thin metal plate such as beryllium copper or stainless steel.

  The housing 210 has a first housing 212 and a second housing 214 both made of a metal material such as stainless steel. A diaphragm 245 is disposed so as to partition the first housing 212 and the second housing 214. A disk-shaped disc 216 is welded to the surface of the diaphragm 245 on the sealed space S1 side, and the diaphragm 245 is biased downward (in the valve opening direction of the main valve) between the disc 216 and the first housing 212. A spring 88 is interposed. Also, a bottomed cylindrical disk 218 is welded to the surface of the diaphragm 245 on the open space S2 side, and can be operatively connected to the operating rod 238 through a fitting groove 90 provided at the center of the lower surface.

  The diaphragm 245 is deformed in the axial direction (the opening and closing directions of the main valve and the subvalve) according to the differential pressure between the crank pressure Pc of the working chamber 22 and the reference pressure of the sealed space S1 (reference pressure chamber). However, even if the differential pressure increases, if the diaphragm 245 is displaced upward by a predetermined amount, the disc 216 is locked to the first housing 212, and thus the displacement is restricted.

  Further, the spring 42 is not directly supported by the operating rod 238 but is interposed between the main valve body 30 and the solenoid 3. Specifically, a spring 42 is interposed between the shaft support member 260 press-fitted into the upper end portion of the core 46 and the main valve body 30.

  In the above configuration, the effective pressure receiving diameter A of the diaphragm 245, the effective pressure receiving diameter B in the main valve of the main valve body 30, and the effective pressure receiving diameter C of the sliding portion of the main valve body 30 are set equal. For this reason, in the state where the main valve body 30 and the power element 206 are operatively connected, the influence of the discharge pressure Pd and the crank pressure Pc acting on the main valve body 30 is substantially canceled. As a result, the main valve body 30 opens and closes based on the suction pressure Ps received in the pressure chamber 28 in the control state of the main valve. That is, the control valve 201 functions as a so-called Ps sensing valve.

[Third Embodiment]
FIG. 6 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the third embodiment. The control valve of the present embodiment is different from the first embodiment in the pressure receiving structure of the pressure sensing unit. For this reason, below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 301 is configured as a Ps sensing valve, but differs from the first embodiment in that the power element 6 directly senses the suction pressure Ps instead of the crank pressure Pc. The control valve 301 is configured by integrally assembling the valve main body 302 and the solenoid 3. Also in this embodiment, the body 305, the core 46, the case 56, and the end member 58 form the body of the entire control valve 301.

  A working chamber 322 is defined in the body 305 by a partition wall 306 provided at an upper portion thereof. The power element 6 is accommodated in the working chamber 322. An insertion hole 308 is provided at the center of the partition wall 306. The operating rod 38 has an upper end that slidably penetrates the insertion hole 308, and can be operatively connected to the power element 6. The port 12 is provided below the partition wall 306. The spring 44 is interposed between the partition wall 306 and the auxiliary valve body 36. The body 305 is provided with a communication path 310 that allows the working chamber 322 and the pressure chamber 28 to communicate with each other. The suction pressure Ps of the pressure chamber 28 is also introduced into the working chamber 322 through the communication path 310.

  In the present embodiment, the effective pressure receiving diameter B in the main valve of the main valve body 30 and the effective pressure receiving diameter C of the sliding portion of the main valve body 30 are set equal. For this reason, the influence of the discharge pressure Pd acting on the combined body of the main valve body 30 and the sub valve body 36 is cancelled. Since the working chamber 322 in which the power element 6 is disposed is filled with the suction pressure Ps, the control valve 301 functions as a so-called Ps sensing valve. In addition, since the differential pressure (Pc-Ps) between the crank pressure Pc and the suction pressure Ps acts on the combined body of the main valve body 30 and the sub-valve body 36 in the control state of the main valve, the discharge pressure Pd is particularly low. In this case, the opening sensitivity of the main valve is increased.

[Fourth Embodiment]
FIG. 7 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the fourth embodiment. The control valve of the present embodiment is different from the third embodiment in the configuration of the pressure sensitive part and the support structure of the main valve body. For this reason, below, it demonstrates centering on difference with 3rd Embodiment. In the figure, components that are substantially the same as those in the second and third embodiments are denoted by the same reference numerals.

  The control valve 401 includes a power element 206 having a diaphragm as a pressure-sensitive member, as in the second embodiment. The control valve 401 is configured as a Ps sensing valve that operates when the power element 206 directly senses the suction pressure Ps. The control valve 401 is configured by assembling a valve body 402 and a solenoid 403 integrally. Also in this embodiment, the body 405, the core 446, the case 56, and the end member 58 form the body of the entire control valve 401.

  The upper end opening of the body 405 is sealed by the power element 206, and a working chamber 322 is defined between the power element 206 and the partition wall 306. The suction pressure Ps of the pressure chamber 28 is also introduced into the working chamber 322 via the communication path 310. The shaft support member 60 as in the third embodiment is not provided at the upper end portion of the core 446. The spring 42 is interposed between the main valve body 30 and the core 446.

  In the above configuration, the effective pressure receiving diameter B in the main valve of the main valve body 30 and the effective pressure receiving diameter C of the sliding portion of the main valve body 30 are set equal to each other as in the third embodiment. For this reason, the influence of the discharge pressure Pd acting on the combined body of the main valve body 30 and the sub valve body 36 is cancelled. Since the working chamber 322 in which the power element 206 is disposed is filled with the suction pressure Ps, the control valve 401 functions as a so-called Ps sensing valve.

[Fifth Embodiment]
FIG. 8 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the fifth embodiment. The control valve of the present embodiment is different from the first embodiment in the configuration of the pressure sensitive part and each valve element. For this reason, below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 501 is configured by assembling the valve body 502 and the solenoid 3 integrally. Also in this embodiment, the body 505, the core 46, the case 56, and the end member 58 form the body of the entire control valve 501. The port 12 is provided at the upper end opening of the body 505. An end member 513 is fixed to the upper end opening of the body 505. The refrigerant is introduced or led out through a plurality of communication grooves 15 provided on the outer peripheral surface of the end member 513 and a communication hole 515 provided in the center of the end member 513.

  A working chamber 522 is formed between the port 12 and the main valve hole 18 to be filled with the crank pressure Pc. The power element 506 is disposed in the working chamber 522. An annular strainer 17 is attached to the port 14. The strainer 17 includes a filter for suppressing entry of foreign matter into the body 505. On the other hand, a bottomed cylindrical strainer 11 is attached to the port 12. The strainer 11 includes a filter for suppressing entry of foreign matter into the body 505.

  A valve chamber 26 is provided on the opposite side of the main valve hole 18 from the working chamber 522 and communicates with the port 14. On the opposite side of the valve chamber 26 from the main valve hole 18, a guide hole 24 is formed coaxially with the main valve hole 18. The port 16 is provided so as to communicate between the inside and the outside at the axial direction intermediate portion of the guide hole 24. A pressure chamber 28 is formed on the opposite side of the guide hole 24 from the valve chamber 26. A partition wall 576 is provided at an intermediate portion in the axial direction of the main valve body 530. The partition wall 576 functions as an “engaged portion” that can be appropriately connected to the engagement portion 78 of the operating rod 538 on the lower surface thereof. The actuating rod 538 has a stepped cylindrical shape that gradually decreases in diameter toward the upper side, and penetrates an insertion hole provided in the center of the partition wall 576. A plurality of communication holes 532 for allowing the refrigerant to pass therethrough are formed around the insertion hole of the partition wall 576. The port 16 communicates with the internal passage 535 and the pressure chamber 28 of the main valve body 530 through the communication hole 532. The spring 42 is interposed between the partition wall 576 and the shaft support member 60.

  The auxiliary valve body 536 has a stepped cylindrical shape and is provided integrally with the power element 506. The power element 506 is configured such that the upper end opening of the bellows 45 is closed by a first stopper 584 and the lower end opening is closed by a second stopper 586. The first stopper 584 has a T-shaped cross section, and has a large-diameter portion 590 that is slidably supported by the body 505 and a small-diameter portion 592 that constitutes an axis within the bellows 45. On the outer peripheral surface of the large diameter portion 590, a plurality of communication grooves 594 for allowing the refrigerant to circulate are provided. That is, in the present embodiment, the power element 506 is not fixed to the body 505 and can be displaced in the axial direction. Between the end member 513 and the first stopper 584, a spring 596 ("biasing member") that biases the power element 506 downward (in the valve opening direction of the main valve and in the valve closing direction of the auxiliary valve). Is functioning). Note that the spring 596 functions as an off-spring that urges the core 46 and the plunger 50 in a direction to separate them from each other. The spring load of the spring 596 is set larger than the spring load of the spring 42.

  The second stopper 586 has a bottomed cylindrical shape and closes the lower end opening of the bellows 45 at the bottom. The second stopper 586 is formed with a T-shaped communication path 539 that allows communication between the inside and the outside. The auxiliary valve body 536 is press-fitted and fixed to the lower half of the second stopper 586. Thereby, the sub-valve body 536 is configured to operate integrally with the bellows 45. An insertion hole 540 is provided on the inner side of the sub valve body 536, and the upper end portion of the operating rod 538 passes through the slidable state. The upper end of the actuating rod 538 is formed in an R shape, and removably contacts the center of the bottom of the second stopper 586. With such a configuration, the crank pressure Pc is filled in the second stopper 586. That is, the upper end portion of the operating rod 538 receives the crank pressure Pc. It should be noted that the position of the engaging portion 78 is set so that the engaging portion 78 is spaced apart from the partition wall 576 by a predetermined distance L when the auxiliary valve body 536 is seated on the auxiliary valve seat 34. ing. The predetermined interval L functions as so-called “play”.

  In the above configuration, the effective pressure receiving diameter A of the bellows 45, the effective pressure receiving diameter B of the main valve body 530 in the main valve, and the effective pressure receiving diameter C of the sliding portion of the main valve body 530 are set equal. In such a configuration, in the control state of the main valve in which the main valve body 530 and the power element 506 are operatively connected, the power element 506 is pressed against the end member 513 by the solenoid force, so that the power element 506 is substantially body. It will be in the state fixed to 505. At this time, the influence of the discharge pressure Pd and the crank pressure Pc acting on the main valve body 530 is substantially canceled. As a result, the main valve body 30 opens and closes based on the suction pressure Ps received in the pressure chamber 28 in the control state of the main valve. That is, the control valve 501 functions as a so-called Ps sensing valve.

[Sixth Embodiment]
FIG. 9 is a cross-sectional view showing the configuration of the control valve according to the sixth embodiment. 10 is a partially enlarged cross-sectional view corresponding to the upper half of FIG. The control valve of the present embodiment is slightly different from that of the fifth embodiment in the support structure for the pressure sensitive part and the valve body. For this reason, below, it demonstrates centering on difference with 5th Embodiment. In the figure, the same components as those in the fifth embodiment are denoted by the same reference numerals.

  As shown in FIG. 9, the control valve 601 is configured by assembling a valve body 602 and a solenoid 603 integrally. Also in this embodiment, the body 605, the core 646, the case 56, and the end member 58 form the entire body of the control valve 601. In the present embodiment, the end member 613 is fixed to the upper end opening of the body 605, and the power element 606 is fixed to the end member 613. On the other hand, between the plunger 50 and the core 646 in the solenoid 603, a spring 47 (functioning as an “urging member”) that biases the plunger 50 in a direction away from the core 646 is interposed.

  As shown in FIG. 10, the first stopper 684 of the power element 606 is integrally formed with the end member 613. The main valve body 630 has its lower end opening portion attached to and detached from the upper end surface of the core 646, whereby the communication state between the internal passage 635 and the pressure chamber 28 is blocked or opened. In other words, the lower end opening of the main valve body 630 and the upper end surface of the core 646 constitute a “shut-off valve” that opens and closes the internal passage 635.

  On the other hand, a cylindrical locking member 612 is press-fitted into the upper end portion of the operating rod 538, and the relative movement range of the partition wall 576 is restricted by the engaging portion 78 and the locking member 612. In the drawing, a state in which the partition wall 576 is in contact with the locking member 612 and the main valve body 630 is positioned at the top dead center relative to the operating rod 638 is shown.

  With such a configuration, when the solenoid 603 is not energized, the operating rod 538 is pushed down by the biasing force of the spring 47. At this time, the locking member 612 abuts against the partition wall 576 and opens the main valve body 630 in the valve opening direction. Energize to. As a result, as shown in the figure, the main valve is fully opened and the shut-off valve portion is closed. In this embodiment, a gap is formed between the bottom surface of the plunger 50 and the bottom surface of the sleeve 48 even if the solenoid 603 is turned off so that the shut-off valve portion is reliably closed at this time. Dimensional configuration.

  At this time, the auxiliary valve body 536 is separated from the main valve body 630 together with the power element 606, and the auxiliary valve is opened. As a result, the crank pressure Pc is introduced into the internal passage 635 of the main valve body 630. Thereby, the influence of the crank pressure Pc acting on the main valve body 630 and the sub-valve body 636 is cancelled. As a result, the pressure difference (Pc−Ps) does not act on the valve body, so that when the solenoid 3 is energized next time, the main valve body 630 can be driven in the valve closing direction with a small solenoid force.

  In the above configuration, the effective pressure receiving diameter A of the bellows 45, the effective pressure receiving diameter B of the main valve body 630 in the main valve, and the effective pressure receiving diameter C of the sliding portion of the main valve body 630 are set equal. For this reason, the influence of the discharge pressure Pd and the crank pressure Pc acting on the main valve body 630 is substantially canceled. As a result, in the control state of the main valve, the main valve body 630 opens and closes based on the suction pressure Ps received in the pressure chamber 28. That is, the control valve 601 functions as a so-called Ps sensing valve.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the specific embodiments, and various modifications can be made within the scope of the technical idea of the present invention. Nor.

  In each of the above embodiments, a so-called Ps sensing valve that operates by sensing the suction pressure Ps is shown as the control valve. However, it may be configured as a so-called Pc sensing valve that operates by sensing the crank pressure Pc. In that case, the port 16 is communicated with the crank chamber.

  In each of the above embodiments, an example in which a single port 12 is provided as a crank chamber communication port (introduction / exit port) communicating with the crank chamber has been described. In the modification, the crank chamber communication port is introduced into the first port (derivation port) for deriving the refrigerant in the working chambers 22, 322, 522 to the crank chamber, and the refrigerant in the crank chamber is introduced into the working chambers 22, 322, 522. It may be configured separately from the second port (introduction port).

  In the above embodiment, the spring (coil spring) is exemplified as the urging member for the springs 42, 44, 47, 88, etc., but an elastic material such as rubber or resin, or an elastic mechanism such as a leaf spring may be employed. Needless to say, it is good.

  In the above embodiment, the control valve for the variable capacity compressor is exemplified. However, for example, a three-way valve of another form is a composite valve in which a main valve and a sub valve are provided in a common body and driven by a single solenoid. If so, the same embodiment can be applied.

  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.

  DESCRIPTION OF SYMBOLS 1 Control valve, 2 Valve body, 3 Solenoid, 5 Body, 6 Power element, 12, 14, 16 port, 20 Main valve seat, 22 Actuation chamber, 24 Guide hole, 26 Valve chamber, 28 Pressure chamber, 30 Main valve body 34 Sub valve seat, 36 Sub valve body, 38 Acting rod, 42, 44 Spring, 45 Bellows, 50 Plunger, 76 Acting surface, 78 Engaging portion, 238 Acting rod, 201 Control valve, 202 Valve body, 203 Solenoid, 205 body, 206 power element, 222 pressure chamber, 230 main valve body, 236 sub-valve body, 245 diaphragm, 301 control valve, 302 valve body, 305 body, 322 working chamber, 401 control valve, 402 valve body, 403 solenoid, 405 body, 501 system Control valve, 502 valve body, 505 body, 506 power element, 522 working chamber, 530 main valve body, 535 internal passage, 536 sub-valve body, 538 actuating rod, 601 control valve, 602 valve body, 603 solenoid, 605 body, 606 Power element, 630 Main valve body, 635 Internal passage, 636 Sub valve body.

Claims (8)

A body provided with an introduction port for introducing or deriving the working fluid, an introduction port for introducing the working fluid, and a deriving port for deriving the working fluid;
The main valve is opened and closed by being attached to and detached from a main valve seat that is slidably supported by the body and formed between the inlet port and the inlet / outlet port, while the inlet / outlet port communicates with the outlet port A main valve body in which an internal passage is formed;
A sub-valve element that opens and closes the sub-valve by attaching to and detaching from the end of the internal passage or the sub-valve seat formed inside,
A pressure sensing unit provided on one end side of the body for sensing a sensed pressure, and generating a driving force for driving the main valve body in a valve opening direction when the sensed pressure becomes lower than a set pressure;
A solenoid that is provided on the other end side of the body and generates a solenoid force for driving the main valve body in a valve closing direction according to the amount of current supplied;
An operating rod that is interposed between the pressure-sensitive portion and the solenoid, and that can transmit the solenoid force directly to the pressure-sensitive portion without passing through either the main valve body or the sub-valve body;
With
The control valve is characterized in that the sub-valve element is not fixed to the operating rod and is loosely fitted with a predetermined clearance . A first biasing member that biases the main valve body in a valve closing direction of the main valve;
A second urging member that urges the sub valve body in the valve closing direction of the sub valve;
The control valve according to claim 1, further comprising:   The actuating rod has a pressing portion for transmitting a solenoid force for driving the sub-valve element in a valve opening direction of the sub-valve to the sub-valve element when the main valve is closed. The control valve according to claim 2.   2. The actuating rod has an engaging portion capable of directly transmitting the solenoid force to the main valve body by engaging with an engaged portion provided on the main valve body. 4. The control valve according to any one of 3. The actuating rod has an engaging portion capable of directly transmitting the solenoid force to the main valve body by engaging with an engaged portion provided on the main valve body,
The first urging member moves the main valve body in a valve closing direction of the main valve so that a predetermined interval is formed between the engaging portion and the engaged portion in a closed state of the sub valve. 4. The control valve according to claim 2, wherein the control valve is biased.   The said 1st biasing member is interposed between the said operating rod and the said main valve body, and it can displace | move integrally with the said operating rod, The any one of Claim 2, 3, 5 characterized by the above-mentioned. Control valve. The sub-valve element and the pressure-sensitive part are integrally configured,
The control valve according to claim 1 , wherein the operating rod is configured to be able to be operatively connected to the pressure-sensitive portion through the sub-valve element . At least of the refrigerant introduced into the crank chamber from the discharge chamber and the refrigerant led out from the crank chamber to the suction chamber, the discharge capacity of the variable capacity compressor that compresses the refrigerant introduced into the suction chamber and discharges it from the discharge chamber It is configured as a control valve for a variable capacity compressor that is changed by adjusting one flow rate or pressure,
The body includes a crank chamber communication port that communicates with the crank chamber as the inlet / outlet port, a discharge chamber communication port that communicates with the discharge chamber as the introduction port, and a suction chamber communication that communicates with the suction chamber as the outlet port. Port and formed,
The pressure sensing unit senses the suction pressure of the suction chamber or the crank pressure of the crank chamber as the sensed pressure, and when the sensed pressure becomes lower than a set pressure, applies a force in the valve opening direction to the main valve body. The control valve according to claim 1, wherein the control valve is operated.

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