JP2014190247A - Control valve for variable capacity compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a high flow rate to be attained when an auxiliary valve is opened, in a control valve in which a main valve and the auxiliary valve are driven by a single solenoid.SOLUTION: A control valve of an aspect comprises a body formed with a main passage for communicating a discharge chamber with a crank chamber and an auxiliary passage for communicating the crank chamber with a suction chamber, a main valve disposed in the main passage, an auxiliary valve disposed in the auxiliary passage, a power element for receiving suction pressure of the suction chamber and generating a driving force in a valve opening direction of the main valve corresponding to a value of the suction pressure and a solenoid for generating a driving force in a valve closing direction of the main valve corresponding to a current amount supplied. Then, when the main valve is controlled, the valve closed state of the auxiliary valve is kept and after the main valve is closed, the auxiliary valve is opened and it has a characteristic that a variation of an opening area of the auxiliary valve in respect to the amount of lift of the auxiliary valve from an auxiliary valve seat becomes larger than a variation of an opening area of the main valve in respect to the amount of lift from the main valve from a main valve seat.

Description

  The present invention relates to a control valve suitable for controlling the discharge capacity of a variable capacity compressor.

  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 auxiliary valve is opened with the main valve closed, thereby quickly reducing the crank pressure Pc, so that the compressor can be shifted to the maximum capacity operation state relatively quickly. . 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

  By the way, in recent years, there is a demand for a vehicle manufacturer to start the compressor more quickly. Pursuing further comfort by demonstrating air-conditioning performance more quickly will lead to vehicle sales promotion. For this purpose, the refrigerant flow rate when the auxiliary valve is open must be increased. However, since the control valve described above forms the sub valve hole in the main valve body, the size of the sub valve is restricted by the size of the main valve. For this reason, it is not easy to obtain a desired flow rate.

  The present invention has been made in view of such problems. In a control valve in which a main valve and a sub valve are driven by a single solenoid, a large flow rate can be obtained when the sub valve is opened. Objective.

  In order to solve the above problems, a control valve for a variable capacity compressor according to an aspect of the present invention provides a discharge capacity of a variable capacity compressor that compresses a refrigerant introduced into a suction chamber and discharges the refrigerant from the discharge chamber. The discharge chamber and the crank chamber communicate with each other in a control valve for a variable capacity compressor that is changed by adjusting the flow rate or pressure of at least one of the refrigerant introduced into the crank chamber and the refrigerant introduced from the crank chamber into the suction chamber A body formed with a main passage, a sub-passage communicating the crank chamber and the suction chamber, a main valve seat provided in the main passage, and a main valve body that is attached to and detached from the main valve seat to open and close the main valve; A sub-valve seat provided in the sub-passage, a sub-valve element that opens and closes the sub-valve by attaching to and detaching from the sub-valve seat, and a main valve that receives a predetermined sensed pressure and that corresponds to the magnitude of the sensed pressure A pressure sensing unit that generates a driving force in the valve opening direction, and Comprising a solenoid for generating the closing direction of the driving force of the main valve in accordance with the amount, the. When the main valve is controlled, the sub-valve is kept closed, and the sub-valve opens after the main valve is closed. The change in the opening area of the main valve with respect to the lift amount of the main valve body from the main valve seat The change in the opening area of the auxiliary valve with respect to the lift amount from the auxiliary valve seat of the auxiliary valve body is larger than that.

  According to this aspect, the sub valve has a larger inclination of the valve opening characteristic of the valve body lift amount-valve opening area than the main valve. That is, since a large flow rate can be obtained when the auxiliary valve is opened, the startability of the compressor can be improved. On the other hand, the opening area of the main valve can be adjusted relatively finely with respect to the lift amount of the main valve body, and the valve opening characteristic of the main valve can be kept stable, so that the capacity control of the compressor is maintained with high accuracy. can do.

  According to the present invention, in a control valve in which a main valve and a sub valve are driven by a single solenoid, a large flow rate can be obtained when the sub valve is opened.

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 figure showing the valve opening characteristic 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 FIG. 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.

  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 evaporation. 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”.

  The body 5 is provided with ports 12, 14, 16, and 18 from its upper end side. Among these, the port 12 is provided in the upper end opening of the body 5, and the ports 14, 16, and 18 are provided in the side of the body 5. Ports 12 and 18 function as “suction chamber communication ports” that communicate with the suction chamber, port 14 functions as “discharge chamber communication port” that communicates with the discharge chamber, and port 16 communicates with “crank chamber communication” that communicates with the crank chamber. Functions as a "port". An end member 13 is fixed to the upper end opening of the body 5. A plurality of communication grooves 15 for forming the port 12 are provided on the outer peripheral surface of the end member 13. 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 14 and the port 16 and a sub passage that communicates the port 16 and the port 18 are formed. The main passage is provided with a small-diameter main valve, and the sub-passage is provided with a large-diameter sub-valve. The auxiliary valve is arranged coaxially below the main valve, that is, on the side closer to the solenoid 3 than the main valve. That is, as shown in the figure, the control valve 1 has a configuration in which a power element 6, a main valve, a sub valve, and a solenoid 3 are sequentially arranged from one end side. A main valve hole 20 and a main valve seat 22 are provided in the main passage. A sub valve hole 32 and a sub valve seat 34 are provided in the sub passage.

  The port 12 communicates the pressure chamber 23 defined in the upper part of the body 5 with the suction chamber, and introduces the refrigerant having the suction pressure Ps into the pressure chamber 23. The power element 6 is disposed in the pressure chamber 23. The port 14 introduces a refrigerant having a discharge pressure Pd from the discharge chamber. The port 16 guides the refrigerant having the crank pressure Pc via the main valve toward the crank chamber during the 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. The port 18 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 the compressor is started.

  The main valve hole 20 and the sub valve hole 32 are formed coaxially, and the pressure chamber 24 between the main valve hole 20 and the sub valve hole 32 communicates with the port 16. A guide hole 25 (functioning as a “first guide hole”) is provided between the port 14 and the pressure chamber 23. A guide hole 26 (functioning as a “second guide hole”) is provided between the port 14 and the port 16. A guide hole 27 (functioning as a “third guide hole”) is provided between the port 16 and the port 18. A stepped cylindrical subvalve element 36 is inserted through these guide holes. The guide hole 26 is slightly larger than the guide holes 25 and 27, and the auxiliary valve body 36 is slidably supported by the guide holes 25 and 27 at one end side and the other end side thereof. That is, the auxiliary valve body 36 is supported at two points by the body. A sub valve seat 34 is formed on the upper surface of the solenoid 3. The auxiliary valve body 36 is attached to and detached from the auxiliary valve seat 34 to open and close the auxiliary valve.

  The main valve hole 20 is provided in the reduced diameter part of the upper part of the subvalve body 36, and the main valve seat 22 is formed in the lower end opening part. On the other hand, a long operating rod 38 is provided along the axis of the body 5. The operating rod 38 has an upper half inserted through the sub-valve element 36 and a lower half inserted through the solenoid 3. The upper end portion of the operating rod 38 is slidably supported on the upper end portion of the sub-valve body 36, and is connected to the power element 6 at the distal end portion so as to be operatively connectable. The lower end portion of the operating rod 38 is connected to a plunger 50 (described later) of the solenoid 3. Further, the intermediate portion of the operating rod 38 is expanded in diameter to form the main valve body 30. The main valve body 30 opens and closes the main valve by being attached to and detached from the main valve seat 22 in the pressure chamber 24, and adjusts the flow rate of refrigerant flowing from the discharge chamber to the crank chamber. The operating rod 38 directly transmits a solenoid force to the main valve body 30 and the sub valve body 36.

  When the auxiliary valve body 36 is seated on the auxiliary valve seat 34 and closes the auxiliary valve, the communication state between the pressure chamber 24 and the port 18 is interrupted, and the relief of the refrigerant from the crank chamber to the suction chamber is interrupted. Further, when the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and opens the auxiliary valve, the pressure chamber 24 and the port 18 communicate with each other, and the relief of the refrigerant from the crank chamber to the suction chamber is allowed. In the upper part and the middle part of the sub-valve body 36, communication holes 35 and 37 that communicate with the inside and the outside are provided. The communication hole 35 communicates the port 14 and the main valve hole 20, and the communication hole 37 communicates the port 16 and the pressure chamber 24.

  A spring 44 (which functions as an “urging member”) for biasing the sub valve body 36 in the valve closing direction of the sub valve is interposed between the sub valve body 36 and the body 5. The power element 6 includes a bellows 45 (which functions as a “pressure-sensitive member”) that senses and displaces the suction pressure Ps, 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 operating rod 38.

  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. Between the plunger 50 and the core 46, a spring 47 (functioning as an “urging member”) that biases the plunger 50 in a direction away from the core 46 is interposed.

  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. A pressure chamber 24 is formed between the core 46 and the auxiliary valve body 36. On the other hand, the operating rod 38 is inserted so as to penetrate the center of the core 46 in the axial direction. The lower end portion of the operating rod 38 is press-fitted into the upper half of the plunger 50, and 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 operating rod 38 appropriately transmits a solenoid force, which is a suction force between the core 46 and the plunger 50, to the main valve body 30 or the sub valve body 36. On the other hand, the actuating rod 38 is loaded with a driving force (also referred to as “pressure-sensitive driving force”) due to the expansion / contraction operation of the power element 6 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 main valve body 30 to appropriately control the opening degree of the main valve. When the main valve is closed, the operating rod 38 is displaced relative to the body 5 according to the magnitude of the solenoid force, and the sub valve body 36 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 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 parallel to the axis is formed at a predetermined location on the outer peripheral surface of the shaft support member 60. The crank pressure Pc of the pressure chamber 24 is also guided to the inside of the sleeve 48 through the communication groove, the communication path 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. Note that the spring 47 functions as an off-spring that urges the core 46 and the plunger 50 in a direction to separate them from each other.

  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 crank pressure Pc 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.
The body 5 is configured by assembling a first body 81 and a second body 82. The first body 81 has a stepped cylindrical shape whose outer diameter gradually decreases upward, and can slide on the lower half of the sub-valve body 36 through a guide hole 27 formed on the inside thereof. I support it. The second body 82 has a stepped cylindrical shape, and is fixed so that its lower half is inserted into the upper half of the first body 81. The body 5 is configured such that the outer diameter decreases from the solenoid 3 side toward the power element 6 side by connecting the first body 81 and the second body 82, and the body 5 is connected to a mounting hole of a compressor (not shown). The ease of insertion is enhanced.

  A communication hole 83 that communicates the inside and the outside is provided on the lower side portion of the second body 82. A port 14 is formed in an overlap portion between the first body 81 and the second body 82. The power element 6 is provided so as to be accommodated in the upper half of the second body 82. The guide holes 25 and 26 are formed by slightly reducing the inner diameter of the lower half of the second body 82. The sliding surface of the guide hole 26 is provided with a sealing O-ring 28 (functioning as a “seal member”). As a result, the high-pressure refrigerant introduced from the port 14 is prevented from leaking to the port 16 through the gap between the sub valve body 36 and the guide hole 26.

  The upper surface 90 of the main valve body 30 functions as an “attachment / detachment portion” that opens / closes the main valve seat 22 and opens / closes the main valve, and also moves the sub valve body 36 upward (the sub valve's It also functions as an “engaging part” that presses in the valve opening direction). On the other hand, the upper surface 92 of the intermediate portion of the sub valve body 36 functions as a “locking portion” in which the upward displacement of the sub valve body 36 is restricted by being locked to the lower surface of the second body 82. The upper end portion 94 of the actuating rod 38 is slidably inserted into the upper end portion of the sub-valve element 36, and also functions as a partition wall that isolates the pressure chamber 23 from other pressure chambers.

  With such a configuration, when the solenoid 3 is not energized, the operating rod 38 is pushed down by the urging force of the spring 47 (see FIG. 1). As a result, as shown in the figure, the main valve body 30 is separated from the main valve seat 22, and the main valve is fully opened. The auxiliary valve body 36 maintains the closed state of the auxiliary valve by the urging force of the spring 44, but the downward displacement thereof is restricted by the auxiliary valve body 36 seated on the auxiliary valve seat 34. In the present embodiment, the shape and size of the auxiliary valve body 36 are set so that the upper surface 92 is spaced from the lower surface of the second body 82 with a predetermined interval L1 when the auxiliary valve is closed.

  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 first stopper 84 has a stepped columnar shape and extends in the axial direction inside the bellows 45. The second stopper 86 has a disc shape, and the center portion of the upper surface thereof is disposed opposite to the lower end surface of the first stopper 84. 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. The bellows 45 expands or contracts in the axial direction (opening / closing direction of the main valve) according to the differential pressure between the suction pressure Ps of the pressure chamber 23 and the reference pressure of the reference pressure chamber S. However, even if the differential pressure increases, if the bellows 45 contracts by a predetermined amount, the second stopper 86 comes into contact with the first stopper 84 and is locked, so that the contraction is restricted.

  In the above configuration, the main valve body 30 and the main valve seat 22 constitute a main valve, and the flow rate of the refrigerant introduced from the discharge chamber into 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 (seal part diameter) of the sub valve of the sub valve body 36 and the effective pressure receiving diameter B (seal part diameter) of the sliding portion with the guide hole 27 of the sub valve body 36 are as follows. Are set equal. For this reason, most of the effects of the crank pressure Pc and the suction pressure Ps acting on the auxiliary valve body 36 are canceled. Further, the effective pressure receiving diameter C (seal portion diameter) of the sliding portion with the guide hole 25 of the sub-valve body 36 and the effective pressure receiving diameter D (sealing portion diameter) of the sliding portion with the guide hole 26 of the sub-valve body 36 are also shown. And are set equal. For this reason, the influence of the discharge pressure Pd acting on the auxiliary valve body 36 is cancelled.

That is, the influence of the crank pressure Pc and the suction pressure Ps is canceled for the portion where the auxiliary valve body 36 is formed large. On the other hand, a differential pressure (Pc−Ps) between the crank pressure Pc and the suction pressure Ps acts in the opening direction of the auxiliary valve on the small diameter portion which is the upper half of the auxiliary valve body 36. Therefore, it cannot be larger than the urging force of the sub valve by the spring 44 in the valve closing direction. As a result, the closed state of the auxiliary valve can be stably maintained during the control of the compressor even when the auxiliary valve body 36 is configured to be large. Can be opened. In other words, in order to cancel the influence of the crank pressure Pc and the suction pressure Ps on the portion where the auxiliary valve body 36 is formed large, even if the size of this portion is changed, the auxiliary valve body 36 is caused by the differential pressure (Pc−Ps). The load that is received does not increase. For this reason, it becomes possible to set the magnitude | size of the subvalve body 36 freely. Further, the effective pressure receiving diameter E (seal part diameter) of the main valve body 30 in the main valve and the effective pressure receiving diameter F (seal part diameter) of the sliding part of the main valve body 30 are set equal. Thereby, the influence of the discharge pressure Pd acting on the main valve body 30 is canceled, and the behavior of the main valve body 30 can be kept stable during the control of the main valve.
In the modified example, the effective pressure received by the difference (D−E) between the effective pressure receiving diameter D and the effective pressure receiving diameter E is obtained by reducing the outer diameter of the lower end opening of the auxiliary valve body 36 to have a stepped shape. The area and the effective pressure receiving area due to the difference (B−A) between the effective pressure receiving diameter B and the effective pressure receiving diameter A may be made equal. Thereby, you may cancel the influence by the differential pressure | voltage (Pc-Ps) which acts on the subvalve body 36. FIG. Alternatively, the effective pressure receiving area by the effective pressure receiving diameter C (the area of the solid part including the effective pressure receiving area by the effective pressure receiving diameter F) and the difference between the effective pressure receiving diameter B and the effective pressure receiving diameter A (B−A). And may be equal. Thereby, you may cancel the influence of the suction pressure Ps which acts when the main valve body 30 and the subvalve body 36 are united.

  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 23 becomes the predetermined set pressure Pset. The set pressure Pset is basically adjusted in advance by the spring load of the springs 44, 47, 88 and the load of the bellows 45, and the evaporator can be prevented from freezing from the relationship between the temperature in the evaporator and the suction pressure Ps. Set as pressure value. 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.

  On the other hand, when the control valve 1 is started, the main valve body 30 is seated on the main valve seat 22 by displacing the operating rod 38 relative to the sub-valve body 36 by energizing the solenoid 3. It closes and the driving force of the valve opening direction can be given to the subvalve body 36 through the main valve body 30. Thereby, the auxiliary valve body 36 can be lifted from the auxiliary valve seat 34 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 this configuration, when the sub-valve body 36 is locked due to a foreign object biting into the sliding portion between the sub-valve body 36 and the guide holes 25, 26, 27, an unlocking mechanism (interlocking mechanism) is released. , Also functions as a pressing mechanism).

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 bellows 45 shrinks and the power element 6 does not function substantially. Further, the operating rod 38 is pushed down by the urging force of the spring 47, the main valve body 30 is separated from the main valve seat 22, and the main valve is fully opened. On the other hand, the sub-valve element 36 is kept seated on the sub-valve seat 34 by the biasing force of the spring 44, and the sub-valve maintains the closed state.

  On the other hand, when a control current is supplied to the electromagnetic coil 54 of the solenoid 3 such as when the air conditioner for automobiles is started, the operating rod 38 is driven upward by the solenoid force and the main valve is closed as shown in FIG. , The vice valve is opened. That is, first, the operating rod 38 is relatively displaced with respect to the sub valve body 36, whereby the main valve body 30 is seated on the main valve seat 22 and the main valve is closed. Subsequently, while the main valve body 30 is seated on the main valve seat 22, the operating rod 38 is further displaced relative to the body 5, so that the sub valve body 36 is separated from the sub valve seat 34 and the sub valve is operated. Open the valve. However, when the upper surface 92 of the sub-valve element 36 is locked to the body 5, the lift amount of the sub-valve element 36 (that is, the opening degree of the sub-valve) is regulated. In addition, since the suction pressure Ps is usually relatively high at the time of startup, the bellows 45 maintains the contracted state and the auxiliary valve is maintained open.

  That is, when a 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 the sub valve is opened to quickly relieve the refrigerant in the crank chamber to the suction chamber. As a result, the compressor can be started quickly. 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.

  Even when the sub-valve body 36 is locked in the valve opening direction due to foreign matter being caught in the sliding portion of the sub-valve element 36 when the control valve 1 is activated, the sub-valve element is driven by the solenoid force. The lock can be released by pressing 36. Even if the sub-valve element 36 is locked in the valve closing direction due to the foreign matter biting into the sliding portion of the sub-valve element 36, the suction pressure Ps is reduced by the activation of the control valve 1 and the bellows 45 is extended. The second stopper 86 comes into contact with the upper end surface of the sub-valve body 36 and presses it downward, so that the lock can be released.

  When the current value supplied to the solenoid 3 is in the control state set to a predetermined value, as shown in FIG. 4, the suction pressure Ps is relatively low, so that the bellows 45 extends, and the operation rod 38 operates. Connected. Thereby, the main valve body 30 operates and adjusts the opening degree of the main valve. At this time, the main valve body 30 has a force in the valve opening direction by the spring 47, a solenoid force in the valve closing direction by the solenoid 3, and a force that opposes the solenoid force by the power element 6 that operates according to the suction pressure Ps. Stop at the balanced valve lift position. In the control state of the main valve, the auxiliary valve body 36 is kept seated on the auxiliary valve seat 34 by the urging force of the spring 44, so the closed state of the auxiliary valve is maintained.

  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, the suction force does not act between the core 46 and the plunger 50, so that the main valve body 30 is separated from the main valve seat 22 by the biasing force of the spring 47 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 refrigerant having the discharge pressure Pd introduced from the discharge chamber of the compressor to the port 16 passes through the fully opened main valve and flows from the port 14 to the crank chamber. Therefore, the crank pressure Pc is increased and the compressor is operated at the minimum capacity.

  FIG. 5 is a diagram illustrating a valve opening characteristic of the control valve. In the figure, the horizontal axis indicates the displacement of the operating rod 38, and the vertical axis indicates the valve opening (opening area) of the main valve and the subvalve. The displacement of the operating rod 38 corresponds to the lift amount of the main valve body 30 from the main valve seat 22 and the lift amount of the sub valve body 36 from the sub valve seat 34. The solid line in the figure indicates the main valve, and the alternate long and short dash line indicates the subvalve.

  As shown in FIG. 2, when the solenoid 3 is turned off and the operating rod 38 is at the bottom dead center, the lift amount of the main valve body 30 is maximized, and the solenoid 3 is turned from off to on as shown in FIG. Thus, when the operating rod 38 is at the top dead center, the lift amount of the auxiliary valve body 36 is maximized. At the midpoint of the displacement of the operating rod 38, there is a fully closed point where the lift amounts of the main valve body 30 and the sub valve body 36 are both zero, that is, the main valve and the sub valve are closed simultaneously. When the operating rod 38 is displaced downward with reference to the fully closed point, the opening degree of the main valve gradually increases while the sub valve is closed. Conversely, when the operating rod 38 is displaced upward with reference to the fully closed point, the opening of the sub valve gradually increases while the main valve is closed. In the process where the operating rod 38 is displaced upward, the sub-valve begins to open as soon as the main valve closes. Further, the main valve starts to open simultaneously with the closing of the sub-valve in the process in which the operating rod 38 is displaced downward.

  However, in this embodiment, since the seal part diameter in the subvalve of the subvalve body 36 is considerably larger than the seal part diameter in the main valve of the main valve body 30, the valve lift amount of the subvalve is larger than that of the main valve. -The inclination of the valve opening characteristic of the valve opening (opening area) increases. That is, since the opening area of the auxiliary valve can be greatly changed with respect to the lift amount of the auxiliary valve body 36 (displacement of the operating rod 38), a large flow rate can be obtained when the auxiliary valve is opened. As a result, the startability of the compressor can be improved. In particular, at the time of starting the compressor, the liquid refrigerant must be discharged in a state where the differential pressure (Pc-Ps) is small. Therefore, it is desirable that the opening degree of the auxiliary valve is large, and the configuration of the present embodiment is advantageous in that respect. is there. On the other hand, since the opening area of the main valve can be adjusted relatively finely with respect to the lift amount of the main valve body 30 (displacement of the actuating rod 38), the valve opening characteristic of the main valve can be kept stable and the compression can be maintained. The capacity control of the machine can be maintained with high accuracy.

  As described above, in the present embodiment, the auxiliary valve seat 34 is not formed on the main valve body 30 but is formed on a part of the body 5. For this reason, regardless of the size of the main valve body 30, the sizes of the auxiliary valve hole 32 and the auxiliary valve body 36 can be set. That is, the size of the sub valve can be set regardless of the size of the main valve. In particular, the auxiliary valve body 36 can be made sufficiently large by providing the auxiliary valve body 36 closer to the solenoid 3 than the power element 6, that is, on the side where the outer diameter of the body 5 is increased. In the present embodiment, as described above, the inclination of the valve opening characteristic of the auxiliary valve is made considerably larger than that of the main valve, so that a large flow rate can be obtained when the auxiliary valve is opened, and the bleed function can be enhanced. Further, the main valve seat 22 is provided integrally with the auxiliary valve body 36, so that the number of parts can be reduced. Further, the main valve seat 22 (valve seat forming portion) and the sub valve body 36 are integrated, so that the main valve seat 22 moves after the main valve is closed, and at the same time, the sub valve is integrated with the main valve seat 22. Since the auxiliary valve is opened by the movement of the body 36, there is no need to individually adjust the closing timing of the main valve and the opening timing of the auxiliary valve, the selection of parts and adjustment parts can be reduced, and the assemblability is greatly improved. .

[Second Embodiment]
FIG. 6 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the second embodiment. 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 configured by integrally assembling a valve main body 202 and a solenoid 203. The body 205 is formed of a single member, and an adjustment member 213 is screwed into the upper end opening. The port 12 opens to the side at the top of the body 205. An annular strainer 17 is attached to the port 14. The strainer 17 includes a filter for suppressing entry of dust and the like into the body 205. The upper end of the operating rod 238 extends to the inside of the power element 206. The upper end of the sub-valve element 236 is not exposed to the pressure chamber 23 and receives the discharge pressure Pd.

  On the other hand, the solenoid 203 includes a core 246, a sleeve 248, a plunger 250, a bobbin 52, an electromagnetic coil 54, a case 256, and an end member 58. In the present embodiment, the body 205, the case 256, and the end member 58 form the body of the entire control valve 201. The lower end portion of the operating rod 238 is inserted through the upper portion of the plunger 250. There is no spring provided between the plunger 250 and the core 246. On the other hand, a spring 247 (which functions as an “urging member”) for biasing the plunger 250 in a direction away from the core 246 is interposed between the sub valve body 236 and the operating rod 238.

  The valve body 202 and the solenoid 203 are fixed by press-fitting the lower end portion of the body 205 into the upper end portion of the case 256. A valve seat member 260 is fitted on the upper surface of the core 246, and the upper surface of the valve seat member 260 forms the auxiliary valve seat 34. The valve seat member 260 is a non-magnetic annular member and is made of PTFE (polytetrafluoroethylene) in the present embodiment, but may be an elastic body such as rubber. The valve seat member 260 may be fitted to the core 246 or may be baked.

7 is a partially enlarged cross-sectional view corresponding to the upper half of FIG.
The guide hole 25 of the body 205 supports the upper part 262 of the operating rod 238 so as to be slidable. A spring receiving member 240 is provided below the main valve body 30 in the operating rod 238. A spring 247 is interposed between the sub valve body 236 and the spring receiving member 240. The spring 247 biases the auxiliary valve body 236 in the valve opening direction. In the present embodiment, the operating rod 238 and the plunger 250 are not fixed as in the first embodiment, but the operating rod 238 is biased toward the plunger 250 by the reaction force of the spring 247, so the operating rod 238 And the plunger 250 can always be kept in contact with each other. In other words, the operation rod 238 does not need to be press-fitted into the plunger 250.

  The auxiliary valve body 236 is slidably inserted into the guide hole 26 and the guide hole 27. That is, the auxiliary valve body 236 is supported at two points by the body. A sealing O-ring 228 (functioning as a “seal member”) is provided on the surface of the sub valve body 236 facing the guide hole 26. As a result, the refrigerant introduced from the port 14 is prevented from leaking to the port 16 through the gap between the sub valve body 236 and the guide hole 26.

  The power element 206 includes a base member 284 and a bellows 245. The base member 284 is formed in a bottomed cylindrical shape by press-molding a metal material, and has a flange portion 286 that extends radially outward at a lower end opening thereof. The bellows 245 is closed at the upper end of the bellows-shaped body, and the lower end opening is airtightly welded to the upper surface of the flange 286. The bellows 45 expands and contracts with the main body of the base member 284 as an axis. The bellows 245 is supported by the adjusting member 213 at the end opposite to the flange portion 286. Between the flange portion 286 and the body 205, a spring 290 (which functions as a “biasing member”) that biases the bellows 245 in the reduction direction is interposed.

  That is, the power element 206 is elastically supported between the adjustment member 213 and the body 205. By adjusting the screwing amount of the adjustment member 213 into the body 205, the set load of the power element 206 (the set load of the spring 88) can be adjusted. The main body of the base member 284 extends inward of the bellows 245 to the vicinity of the bottom thereof, and the upper bottom thereof is disposed close to the bottom of the bellows 245. The upper end portion of the operating rod 238 is inserted through the main body of the base member 284.

  Also in the present embodiment, the effective pressure receiving diameter E (seal part diameter) of the main valve of the main valve body 30 is set equal to the effective pressure receiving diameter F (seal part diameter) of the sliding part of the operating rod 238. Thereby, the influence of the discharge pressure Pd acting on the main valve body 30 is canceled, and the control of the main valve is stabilized. On the other hand, since the upper end portion of the sub valve body 236 is opened to the port 14, the sub valve body 236 has a differential pressure (Pd−Pc) between the discharge pressure Pd and the crank pressure Pc in the valve closing direction of the sub valve. Works. When the main valve is controlled, the sub valve body 236 is pressed against the sub valve seat 34 by this differential pressure (Pd−Pc), so that the closed state of the sub valve is stably maintained. That is, the control of the main valve is stably maintained.

  On the other hand, since the differential pressure (Pd−Pc) is small when the compressor is started, the auxiliary valve can be quickly opened by the driving force of the solenoid 203. Once the sub-valve element 236 starts to lift, the opening area of the sub-valve quickly increases as described above, so that the bleed function can be effectively exhibited. The valve opening characteristic shown in FIG. 5 can also be realized by the control valve 201 of the present embodiment.

  In the present embodiment, a non-magnetic valve seat member 260 is provided on the core 246 made of a magnetic material, and the sub-valve body 236 is attached to and detached from the valve seat member 260. Therefore, compared with the first embodiment. As a result, the sealing performance of the secondary valve is improved. That is, the refrigerant introduced through the port 14 may contain foreign matters such as metal powder. This is because the metal powder generated by wear on the piston of the compressor is discharged together with the refrigerant. Such foreign matter is easily attracted to the surface of a member constituting a magnetic circuit such as a core. For this reason, in the structure in which the valve seat (sub valve seat) is formed in the core itself as in the first embodiment, foreign matter may adhere to and stay in the valve seat, and the sealing performance of the valve portion may be reduced.

  In this regard, in the present embodiment, since the nonmagnetic valve seat member 260 is provided on the core 246 and the sub valve seat 34 is formed on the valve seat member 260, such adhesion of foreign matter can be prevented or suppressed. . As a result, the sealing performance between the auxiliary valve body 236 and the auxiliary valve seat 34 can be maintained satisfactorily. By configuring the valve seat member 260 with a member having elasticity or flexibility, even if a small amount of foreign matter adheres, the valve seat member 260 is bent due to the deflection of the valve seat member 260 when the sub valve body 236 is seated. You can maintain sex.

  That is, in the configuration in which the valve seat is provided on the magnetic member forming the magnetic circuit of the solenoid as in the present embodiment, a “nonmagnetic part” is provided by attaching a nonmagnetic material to a part of the magnetic member, When a valve seat is formed in the nonmagnetic part, the same effect can be obtained. The “nonmagnetic part” is preferably made of an elastic member or a flexible member. In addition, you may comprise the attachment or detachment part of the valve body attached to or detached from such a valve seat with an elastic member or a flexible member. Such a technical idea can be applied not only to the auxiliary valve but also to the main valve. It can also be applied to a control valve having a single valve.

[Third Embodiment]
FIG. 8 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 this embodiment differs from the second embodiment in the positional relationship between the sub valve and the main valve. For this reason, below, it demonstrates centering on difference with 2nd Embodiment. In the figure, the same components as those in the second embodiment are denoted by the same reference numerals.

  The control valve 301 is configured by integrally assembling a valve main body 302 and a solenoid 303. An adjustment member 313 is screwed into the upper end opening of the body 305. The port 12 is provided so as to penetrate the adjustment member 313. A port 16 is provided between the port 12 and the port 14. A guide hole 327 (functioning as a “third guide hole”) is provided in the upper portion of the body 305. The guide hole 26 is slightly larger than the guide holes 25 and 327.

  The sub valve body 336 has a stepped cylindrical shape and is inserted through the guide holes 327, 25, and 26. That is, the auxiliary valve body 336 is supported at two points by the body. A sub valve seat 34 is formed on the upper surface of the partition wall that separates the port 14 and the port 16 in the body 305. The sub valve body 336 partitions the body 305 into an inner pressure chamber 325 and an outer pressure chamber 326 below the guide hole 327. The pressure chamber 325 communicates with the port 12 through the pressure chamber 23. On the other hand, the pressure chamber 326 communicates with the port 16. Communication holes 337 and 35 are provided in the middle portion and the lower portion of the sub-valve body 36 to communicate the inside and the outside. The communication hole 337 allows the auxiliary valve hole 32 and the pressure chamber 23 to communicate with each other.

  The main valve hole 20 is provided in the lower part of the subvalve body 336, and the main valve seat 22 is formed in the lower end opening part. The upper half of the operating rod 338 passes through the auxiliary valve body 336 and is connected to the power element 206 so as to be operatively connectable. An O-ring 228 is provided on the surface of the auxiliary valve body 336 facing the guide hole 26.

  An intermediate pressure chamber 328 is formed between the body 305 and the solenoid 303. The lower end portion (main valve seat 22) of the sub valve body 336 is exposed to the intermediate pressure chamber 328. The main valve body 30 is attached to and detached from the main valve seat 22 from the intermediate pressure chamber 328 side to open and close the main valve. On the other hand, the body 305 is provided with a communication passage 350 that allows the intermediate pressure chamber 328 and the pressure chamber 326 to communicate with each other. That is, the refrigerant having the discharge pressure Pd introduced from the port 14 is reduced to the crank pressure Pc through the main valve and once introduced into the intermediate pressure chamber 328, and then to the port 16 via the communication passage 350 and the pressure chamber 326. Led.

  Although not shown in the figure, a spring 47 for biasing the plunger 250 in a direction away from the core 346 is interposed between the core 346 and the plunger 250 (see FIGS. 1 and 6). A spring 290 is interposed between the power element 206 and the auxiliary valve body 336. In the present embodiment, the body 305, the case 256, and the end member 58 form the entire body of the control valve 301.

  With such a configuration, when the solenoid 303 is not energized, the closed state of the auxiliary valve is maintained by the biasing force of the spring 290 as shown in the figure. Further, since the operating rod 338 is pushed downward by the spring 47 (see FIG. 1), the main valve body 30 is separated from the main valve seat 22, and the main valve is fully opened.

  In a stable control state of the control valve 301, the main valve body 330 is pushed up by the solenoid force, but does not engage with the sub valve body 336, so that the sub valve is not opened. The main valve body 330 operates autonomously so that the suction pressure Ps of the pressure chamber 23 becomes a predetermined set pressure Pset.

  On the other hand, when the control valve 301 is activated, the operation rod 338 is displaced relative to the sub valve body 336 by energizing the solenoid 303, so that the main valve body 330 is seated on the main valve seat 22 and the main valve is turned off. close up. At this time, by further displacing the operating rod 338 with respect to the body 305 with the main valve closed, the sub valve body 336 can be lifted from the sub valve seat 34 and the sub valve can be opened. That is, the control valve 301 also has a “forced valve opening mechanism” for forcibly opening the auxiliary valve using the driving force of the solenoid 303. In this configuration, when the sub-valve body 36 is locked due to a foreign matter biting into the sliding portion between the sub-valve body 336 and the guide holes 25, 26, and 327, an unlocking mechanism (interlocking mechanism) is released. , Also functions as a pressing mechanism). Further, the valve opening characteristic shown in FIG. 5 can also be realized by the control valve 301.

[Fourth Embodiment]
FIG. 9 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 second embodiment in the pressure receiving configuration of the main valve body. For this reason, below, it demonstrates centering on difference with 2nd Embodiment. In the figure, the same components as those in the second embodiment are denoted by the same reference numerals.

  The control valve 401 is configured by assembling a valve body 402 and a solenoid 403 integrally. A strainer 17 is also provided at the port 16 of the body 405. The upper end of the core 446 slightly protrudes inward of the body 405, and a ring-shaped guide member 460 is press-fitted into the upper end opening. The auxiliary valve body 436 is attached to and detached from the upper end surface of the core 446 to open and close the auxiliary valve. In the core 446, a pressure chamber 462 surrounded by the guide member 460 and the shaft support member 60 is formed, and a communication hole 448 for communicating the pressure chamber 462 and the port 18 is formed.

  The operating rod 438 is divided into a first rod 440 and a second rod 442. The first rod 440 is connected to the power element 206, and the second rod 442 is connected to the plunger 250 (see FIG. 6). The lower end of the first rod 440 is supported by the guide member 460 so as to be slidable. The upper end of the second rod 442 is slidably supported by the shaft support member 60, and the tip thereof is formed in a hemispherical shape. The second rod 442 is operatively connected in a point contact manner with the lower end surface of the first rod 440. Since the suction pressure Ps is introduced into the pressure chamber 462, the suction pressure Ps is filled inside the sleeve 248 (see FIG. 6), and the suction pressure Ps acts on the lower end surface of the first rod 440. . The main valve body 30 and the spring receiving member 240 are provided on the first rod 440.

  In such a configuration, the effective pressure receiving diameter E (seal part diameter) of the main valve of the main valve body 30, the effective pressure receiving diameter F (seal part diameter) of the upper sliding part of the first rod 440, and the first rod 440. The effective pressure receiving diameter G (seal part diameter) of the lower sliding part is set equal. Thereby, the influence of the discharge pressure Pd, the crank pressure Pc and the suction pressure Ps acting on the main valve body 30 is cancelled. The differential pressure (Pc-Ps) does not act on the main valve body 30, and the behavior of the main valve body 30 can be kept more stable when the main valve is controlled. In the modification, the first rod 440 and the second rod 442 may be integrally formed.

  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. Absent.

  In each of the above embodiments, the control valve is a so-called Ps sensing valve that operates by sensing the suction pressure Ps as the sensed pressure. However, the control valve may be configured as a so-called Pc sensing valve that operates by sensing the crank pressure Pc. Good. In that case, the port 12 is communicated with the crank chamber.

  In the said embodiment, although the example which employ | adopts the bellows 45,245 as a pressure sensitive member which comprises the power element 6 was shown, you may employ | adopt a diaphragm. In this case, a plurality of diaphragms may be connected in the axial direction in order to ensure an operation stroke necessary for the pressure sensitive member.

  In each of the above embodiments, an example in which a single port 16 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 divided into a first port (outlet port) for leading the refrigerant that has passed through the main valve to the crank chamber, and a second port (inlet port) for introducing the refrigerant in the crank chamber. It may be configured.

  In the above-described embodiment, the spring (coil spring) is exemplified as the biasing member with respect to the springs 44, 47, 247, 290, 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, a so-called control valve for adjusting the flow rate or pressure of the refrigerant introduced from the discharge chamber of the variable capacity compressor to the crank chamber has been shown. However, in a modified example, the control valve is led out from the crank chamber to the suction chamber. You may comprise as a control valve of what is called extraction control which adjusts the flow volume or pressure of a refrigerant | coolant. In the case of the removal control, for example, in the control valve of any of the first to fourth embodiments, it is conceivable to adjust the solenoid force so as to use the valve opening region of the auxiliary valve as the control region. That is, since the insertion control is performed in the above embodiment, the left side of the fully closed point in FIG. 5, that is, the open region of the main valve is used as the control region. In the case of the removal control, the right side of the fully closed point in FIG. 5, that is, the open region of the auxiliary valve is used as the control region. Further, by adjusting the length of the actuating rod, the length of the plunger, or the position of the main valve element in the actuating rod, the fully closed point in FIG. You may enlarge the control range of a valve body. Thereby, the removal control using the valve opening region of the auxiliary valve as the control region may be realized. Further, for example, the configuration of the above embodiment can be applied as long as it is a compound valve in which a main valve and a subvalve are provided in a common body, such as a three-way valve of another form, and is driven by a single solenoid. .

  In the above embodiment, the reference pressure chamber S inside the bellows 45, 245 is in a vacuum state, but it may be filled with air or with a predetermined gas as a reference. Alternatively, any one of the discharge pressure Pd, the crank pressure Pc, and the suction pressure Ps may be satisfied. And it is good also as a structure which the power elements 6 and 206 operate | move by sensing the pressure difference inside and outside a bellows suitably.

  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, 3 Solenoid, 5 Body, 6 Power element, 22 Main valve seat, 30 Main valve body, 34 Sub valve seat, 36 Sub valve body, 38 Actuation rod, 45 Bellows, 201 Control valve, 203 Solenoid, 205 Body , 206 Power element, 236 Sub valve body, 238 Actuating rod, 245 Bellows, 260 Valve seat member, 301 Control valve, 303 Solenoid, 305 Body, 330 Main valve body, 336 Sub valve body, 338 Actuating rod, 401 Control valve, 402 valve body, 403 solenoid, 405 body, 438 actuating rod, 460 guide member, 462 pressure chamber.

Claims (5)

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 In the valve
A body formed with a main passage for communicating the discharge chamber and the crank chamber, and a sub-passage for communicating the crank chamber and the suction chamber;
A main valve seat provided in the main passage;
A main valve body that opens and closes the main valve by attaching to and detaching from the main valve seat;
An auxiliary valve seat provided in the auxiliary passage;
A sub-valve element that opens and closes the sub-valve by attaching to and detaching from the sub-valve seat;
A pressure sensing unit that receives a predetermined sensed pressure and generates a driving force in the valve opening direction of the main valve in accordance with the magnitude of the sensed pressure;
A solenoid that generates a driving force in the valve closing direction of the main valve in accordance with the amount of current supplied;
With
When the main valve is controlled, the auxiliary valve is kept closed, and the auxiliary valve is configured to open after the main valve is closed,
The change in the opening area of the sub valve with respect to the lift amount of the sub valve body from the sub valve seat is greater than the change in the opening area of the main valve with respect to the lift amount of the main valve body from the main valve seat. A control valve for a variable displacement compressor, characterized in that:   2. The control valve for a variable capacity compressor according to claim 1, wherein the main valve seat moves and the auxiliary valve opens at the same time as the main valve is closed. 3. An operating rod interposed between the pressure-sensitive part and the solenoid;
The operating rod is inserted into the sub-valve body, while the main valve body is provided integrally,
The main valve seat is provided integrally with the sub valve body,
In the control state of the main valve, the operating rod is displaced relative to the sub valve body, so that the lift amount of the main valve body changes while the sub valve is kept closed, and the main valve is The actuating rod and the sub-valve element are integrated with each other at the same time as the closing, so that the lift amount of the sub-valve element is changed while the main valve is kept closed. The control valve for a variable capacity compressor according to claim 2.   At least one of the differential pressure between the pressure of the discharge chamber and the pressure of the crank chamber and the differential pressure of the pressure of the discharge chamber and the pressure of the suction chamber with respect to the sub valve body is the valve closing direction of the sub valve. The control valve for a variable capacity compressor according to any one of claims 1 to 3, wherein the control valve is configured to act on the control valve. For a variable capacity compressor that changes the discharge capacity of a 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 that is led from the crank chamber to the suction chamber In the control valve,
A body formed with a main passage for communicating the discharge chamber and the crank chamber, and a sub-passage for communicating the crank chamber and the suction chamber;
A main valve seat provided in the main passage;
A main valve body that opens and closes the main valve by attaching to and detaching from the main valve seat;
An auxiliary valve seat provided in the auxiliary passage;
A sub-valve element that opens and closes the sub-valve by attaching to and detaching from the sub-valve seat;
A pressure sensing unit that receives a predetermined sensed pressure and generates a driving force in the valve closing direction of the auxiliary valve in accordance with the magnitude of the sensed pressure;
A solenoid that generates a driving force in the valve opening direction of the auxiliary valve according to the amount of current supplied;
With
When the sub valve is controlled, the main valve is kept closed, and the main valve is configured to open after the sub valve is closed,
The change in the opening area of the sub valve with respect to the lift amount of the sub valve body from the sub valve seat is greater than the change in the opening area of the main valve with respect to the lift amount of the main valve body from the main valve seat. A control valve for a variable displacement compressor, characterized in that:

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