JP2013224638A - Control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a control valve capable of obtaining desired flow rate characteristics while securing the salability of a valve part during valve opening.SOLUTION: A control valve 1 includes a body 10 in which a fluid passage is formed, a valve seat 34 formed at an opening edge of a valve hole 32 provided at the fluid passage, and a valve element 38 driven in an axial direction of the valve hole 32 and attached to and detached from the valve seat 34 to open and close a valve part. The opening edge of the valve hole 32 is provided with a first taper surface having a first inclination angle with respect to the axial direction and a second taper surface connected continuously to a radial direction outer side of the first taper surface and having a second inclination angle larger than the first inclination angle with respect to the axial direction in which the first taper surface functions as the valve seat 34.

Description

  The present invention relates to a control valve, and more particularly 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 a variable displacement compressor control valve (simply provided between the discharge chamber and the crank chamber of the compressor or between the crank chamber and the suction chamber). It is also controlled by “control valve”).

  As such a control valve, for example, there is a valve that controls the crank pressure Pc by adjusting the amount of refrigerant introduced into the crank chamber in accordance with the suction pressure Ps (see, for example, Patent Document 1). For example, the control valve senses and displaces the suction pressure Ps, sets a pressure-sensitive portion, a valve portion that controls opening and closing of a passage from the discharge chamber to the crank chamber by receiving the driving force of the pressure-sensitive portion, and setting of the pressure-sensitive portion And a solenoid whose value can be changed by an external current. Such a control valve opens and closes the valve portion so that the suction pressure Ps is maintained at a set pressure set by an external current. In general, since the suction pressure Ps is proportional to the refrigerant temperature at the evaporator outlet, freezing or the like of the evaporator can be prevented by maintaining the set pressure at a predetermined value or higher. Also, when the engine load of the vehicle is large, the solenoid is turned off to fully open the valve unit, the crank pressure Pc is increased, and the swing plate is made substantially perpendicular to the rotating shaft, thereby minimizing the compressor. It can be operated at capacity.

JP 2011-43102 A

  By the way, many of such control valves have a configuration in which a valve seat is formed in a tapered shape as a countermeasure against refrigerant leakage in the valve portion, and the seating performance of the valve body is enhanced. For example, in the configuration described in Patent Document 1, a tapered surface is formed at the opening end of a valve hole provided in the body, and the tapered surface is used as a valve seat. However, depending on the inclination angle of the tapered surface (that is, the angle with respect to the axial direction of the valve hole: hereinafter also referred to as “taper angle”), it has been found that good sealing performance cannot be ensured or proper flow characteristics cannot be obtained. It was. That is, if the taper angle is reduced in order to improve the seating performance, the valve opening at the time of valve opening becomes small, and there is a possibility that a desired refrigerant flow rate cannot be obtained. Therefore, it is conceivable to shorten the length of the taper surface, but conversely, when the valve is opened, the refrigerant flow rate may change suddenly and a desired flow rate characteristic may not be obtained.

  The present invention has been made in view of such problems, and a main object thereof is to provide a control valve capable of obtaining a desired flow rate characteristic while ensuring the sealing performance of the valve portion when the valve is closed. There is.

  In order to solve the above problems, a control valve according to an aspect of the present invention includes a body having a fluid passage formed therein, a valve seat formed at an opening end of a valve hole provided in the fluid passage, and a valve. And a valve body that is driven in the axial direction of the hole and opens and closes the valve seat to open and close the valve portion. A first tapered surface having a first inclination angle with respect to the axial direction at the opening end of the valve hole, and a radially outer side of the first tapered surface, the first taper surface being larger than the first inclination angle with respect to the axial direction. And a second tapered surface having two inclination angles, and the first tapered surface functions as a valve seat.

  According to this aspect, by forming the valve seat on the first taper surface having a relatively small inclination angle, the seating performance of the valve body can be kept good, and the sealing performance of the valve portion when the valve is closed is ensured. it can. On the other hand, the valve opening degree at the time of valve opening can be adjusted by providing the 2nd taper surface with a relatively large inclination angle continuously from the 1st taper surface. That is, by adjusting the inclination angles of the first taper surface and the second taper surface, it is possible to obtain a desired flow rate characteristic while ensuring the sealing performance of the valve portion when the valve is closed.

  ADVANTAGE OF THE INVENTION According to this invention, it becomes possible to provide the control valve which can acquire a desired flow volume characteristic, ensuring the sealing performance of the valve part at the time of valve closing.

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. FIG. 3 is a diagram showing details of the valve portion. It is a figure which shows the seal structure of a sliding part. It is a figure which shows the support structure of a diaphragm. It is a figure showing the operation | movement process of a control valve. It is a figure showing the operation | movement process of a control valve. It is a partial expanded sectional view of the upper half part of the control valve concerning a 2nd embodiment. It is a figure which shows the seal structure of a sliding part. It is a figure showing the operation | movement process of a control valve.

  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 of the present embodiment is configured as a control valve that controls a variable capacity compressor (not shown) (simply referred to as “compressor”) installed in a refrigeration cycle of an 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 includes a swing plate to which a compression piston is connected, and adjusts the discharge amount of the refrigerant by changing the stroke of the piston by changing the angle of the swing plate. The control valve 1 changes the angle of the swing plate by controlling the flow rate of refrigerant introduced from the discharge chamber of the compressor into the crank chamber. For example, alternative chlorofluorocarbon (HFO-1234yf) is used as the refrigerant, but a refrigerant having a high operating pressure such as carbon dioxide may be used. In that case, an external heat exchanger such as a gas cooler may be arranged in the refrigeration cycle instead of the condenser.

  The control valve 1 has a valve portion in a refrigerant passage that allows communication between the discharge chamber of the compressor and the crank chamber, and is configured as an electromagnetic valve that controls the flow rate of refrigerant introduced from the discharge chamber into the crank chamber. An orifice or the like for allowing the refrigerant in the crank chamber to leak into the suction chamber is also provided between the crank chamber and the suction chamber, but illustration and detailed description thereof are omitted. 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 includes a stepped cylindrical body 10, a valve portion provided inside the body 10, and the like.

  From the upper end side of the body 10, a port 12 (functions as a “crank chamber communication port”), a port 14 (functions as a “discharge chamber communication port”), and a port 16 (functions as a “suction chamber communication port”). Is provided. The internal space provided with the port 14 forms a discharge pressure chamber 18 into which the discharge pressure Pd is introduced. The internal space provided with the port 12 forms a crank pressure chamber 20 from which the crank pressure Pc is derived. The internal space provided with the port 16 forms a suction pressure chamber 22 (corresponding to a “pressure sensing chamber”) into which the suction pressure Ps is introduced.

  A strainer 24 is provided around the port 14. The strainer 24 includes a filter that suppresses foreign matter such as metal powder contained in the discharge refrigerant from flowing into the discharge pressure chamber 18. A strainer 26 is provided around the port 12. The strainer 26 includes a filter that suppresses foreign matters contained in the refrigerant in the crank chamber from flowing into the crank pressure chamber 20.

  The body 10 has a first guide hole 28 that connects the discharge pressure chamber 18 and the crank pressure chamber 20, a second guide hole 30 that connects the discharge pressure chamber 18 and the suction pressure chamber 22, and the first guide hole 28 and the second guide hole 28. A valve hole 32 formed between the guide hole 30 and the guide hole 30 is provided coaxially in the axial direction. A valve seat 34 is formed integrally with the body 10 at the opening end of the valve hole 32 on the discharge pressure chamber 18 side. A long operating rod 36 is disposed so as to penetrate the body 10 in the axial direction.

  The operating rod 36 has a stepped columnar shape, and one end side thereof is slidably supported by the first guide hole 28, and the other end side is slidably supported by the second guide hole 30. That is, the operating rod 36 is supported at two points by the body 10 at one end and the other end thereof. A valve body 38 is integrally provided at the axial center of the operating rod 36. The valve body 38 is attached to and detached from the valve seat 34 from the discharge pressure chamber 18 side to open and close the valve portion. The operating rod 36 has an internal passage 40 formed in the upper half thereof, and a communication hole 42 that communicates the inside and the outside is provided at the lower end of the internal passage 40. The refrigerant introduced from the port 14 and passing through the valve portion is led to the internal passage 40 through the communication hole 42 and led to the crank pressure chamber 20. The details of the operating rod 36 and its peripheral structure will be described later.

  A spring receiving member 44 is screwed into the upper end opening of the body 10, and a spring 46 (“attached”) biases the valve body 38 in the valve closing direction between the spring receiving member 44 and the operating rod 36. Functioning as a “force member”). The load of the spring 46 can be adjusted by the screwing amount of the spring receiving member 44 into the body 10.

  The valve body 2 and the solenoid 3 are connected via a cylindrical connection member 48 made of a magnetic material. That is, the lower end portion of the body 10 is press-fitted into the upper end portion of the connection member 48, and the upper end portion of the case 50 of the solenoid 3 is press-fitted into the lower end portion of the connection member 48. A port 16 is provided on the lower end side portion of the body 10, and a suction pressure chamber 22 is formed in a space surrounded by the valve body 2 and the solenoid 3.

  On the other hand, the solenoid 3 functions as a case 50 that also functions as a yoke, a molded coil 52 disposed in the case 50, and a bottomed cylindrical sleeve 54 (“housing”) inserted into the molded coil 52. ), And a core 56 fixed in the sleeve 54, and a plunger 58 arranged to face the core 56 in the axial direction. The mold coil 52 includes a cylindrical bobbin 60 and an electromagnetic coil 62 wound around the bobbin 60. A ring-shaped plate 64 made of a magnetic material is molded at the lower end of the mold coil 52. This plate 64 forms a magnetic circuit together with the case 50. The lower end portion of the case 50 is crimped to fix the mold coil 52, and the upper end portion is crimped to be fixed to the connecting member 48. In the present embodiment, the body 10 and the case 50 form the entire body of the control valve 1.

  The plunger 58 is composed of two plungers divided with a thin film diaphragm 65 interposed therebetween, one of which is a first plunger 66 disposed inside the mold coil 52 and the other second plunger 68 connected to the body 10. It is disposed in a space surrounded by the member 48. The diaphragm 65 seals the upper end opening of the sleeve 54 and forms a reference pressure chamber in the sleeve 54. In the present embodiment, the reference pressure chamber is in a vacuum state, but may be filled with air, for example. The diaphragm 65 is a pressure-sensitive member having flexibility, and is configured by stacking a plurality of polyimide films. In the modification, a metal diaphragm may be employed as the diaphragm 65.

  A concave portion 70 is formed at the center of the upper surface of the second plunger 68, and the lower end surface of the operating rod 36 is supported on a flat surface at the center thereof so as to be able to contact and separate. Further, a flange portion 72 extending radially outward is provided at the upper end portion of the second plunger 68, and the lower surface of the flange portion 72 is made to correspond to the upper surface of the connection member 48. Thus, when the solenoid 3 is energized, an axial suction force is generated between the flange portion 72 and the connection member 48 so that the valve body 38 can move quickly in the valve closing direction. The second plunger 68 is biased upward by a spring 74 (corresponding to a “biasing member”) interposed between the second plunger 68 and a step formed in the connection member 48. The spring 74 has a larger spring force than the spring 46 that biases the valve body 38 in the valve closing direction.

  Below the second plunger 68, an assembly in which the first plunger 66, the core 56 and the spring 75 are accommodated in the sleeve 54 and the opening thereof is sealed with the diaphragm 65 is disposed. That is, a flange portion 76 extending outward in the radial direction is provided at the upper end opening of the sleeve 54, and an annular plate 78 is joined so as to sandwich the outer peripheral edge portion of the diaphragm 65 between the flange portion 76 and the flange portion 76. (Peripheral welding). The assembly is fixed to the connection member 48 and thus the body 10 by inserting the upper end of the diaphragm 65 into the lower end opening of the connection member 48 and press-fitting the annular member 80 from below. Is done. An O-ring 82 for sealing is interposed between the lower end surface of the connection member 48 and the plate 78.

  A molded coil 52 and a case 50 made of a magnetic material are disposed outside the sleeve 54. The sleeve 54 has a bottomed cylindrical shape and is configured by welding an upper half portion 84 made of a non-magnetic material and a lower half portion 86 made of a magnetic material. In the sleeve 54, the core 56 is press-fitted on the lower half 86 side, and the first plunger 66 is disposed on the upper half 84 side so as to be movable back and forth in the axial direction.

  The first plunger 66 is press-fitted into one end of a shaft 88 extending in the axial direction around the center of the core 56. The shaft 88 is positioned so that the axial position of one end thereof overlaps the axial position of the sliding portion 67 with the sleeve 54 in the first plunger 66. The other end of the shaft 88 is supported by a bearing member 90 disposed in the core 56. A retaining ring 92 is fitted in the middle of the shaft 88, and a spring receiver 94 is provided so that upward movement is restricted by the retaining ring 92. A spring 75 that biases the first plunger 66 in a direction away from the core 56 via a shaft 88 is interposed between the spring receiver 94 and the bearing member 90. The load of the spring 75 can be adjusted by changing the position of the bearing member 90 in the axial direction by pushing and deforming the bottom of the sleeve 54 from the outside in the assembly stage of the solenoid 3.

  A handle 96 is provided at the lower end opening of the case 50 so as to seal the inside of the solenoid 3 from below. The handle 96 also functions as a connector portion that exposes one end of a terminal 98 connected to the electromagnetic coil 62. The terminal 98 is connected to an external power source (not shown). Further, a sealing O-ring 99 is also provided between the handle 96 and the case 50 in order to prevent foreign matter from entering from the outside.

  Next, details of the main part of the control valve 1 will be described. FIG. 2 is a partially enlarged cross-sectional view corresponding to the upper half of FIG. FIG. 3 is a diagram showing details of the valve portion, and shows an enlarged view of a portion A in FIG. (A) shows the closed state of the valve portion, and (B) shows the opened state of the valve portion. FIG. 4 is a view showing a seal structure of the sliding portion. (A) shows the B section enlarged view of FIG. 2, (B) shows the C section enlarged view of FIG. FIG. 5 is a view showing a support structure of the diaphragm, and shows an enlarged view of a portion D in FIG.

  As shown in FIG. 2, the actuating rod 36 has a stepped cylindrical shape having a large diameter portion 100, a medium diameter portion 102, and a small diameter portion 104 from the upper part toward the lower part. The large diameter portion 100 is slidably supported in the first guide hole 28, and the small diameter portion 104 is slidably supported in the second guide hole 30. The medium diameter portion 102 passes through the valve hole 32. A communication hole 42 is formed in the medium diameter portion 102, and an internal passage 40 is formed so as to connect the medium diameter portion 102 and the inside of the large diameter portion 100. The valve body 38 is formed integrally with the lower portion of the large diameter portion 100.

  That is, the operating rod 36 is stably supported by the upper and lower two-point support. Further, since the valve body 38 is provided in the middle part of the two support portions, the valve body 38 is prevented or suppressed from being inclined with respect to the axis of the valve hole 32, and hysteresis is applied to the valve opening characteristics of the valve portion. The possibility of causing it is very low. Moreover, the refrigerant | coolant leak in the valve part resulting from the inclination of a valve body can be prevented or suppressed. As a result, it is possible to maintain the valve opening characteristics of the valve portion satisfactorily.

  The passage connecting the first guide hole 28, the valve hole 32 and the second guide hole 30 is formed in a stepped circular hole shape so that the inner diameter gradually decreases downward corresponding to the shape of the operating rod 36. Yes. The upper end opening of the valve hole 32 is formed with a tapered surface whose diameter increases upward, and a valve seat 34 is formed on the tapered surface. A tapered surface that increases in diameter upward is also formed between the valve hole 32 and the second guide hole 30.

  As shown in FIG. 3, the opening end of the valve hole 32 is provided with a first tapered surface 106 that functions as a valve seat 34, and further, a second tapered surface above the first tapered surface 106 and radially outward. 108 is continuously provided. The first tapered surface 106 has a first inclination angle θ1 with respect to the axial direction. The second tapered surface 108 has a second inclination angle θ2 larger than the first inclination angle θ1 with respect to the axial direction (θ2> θ1).

  In the present embodiment, the first inclination angle θ1 is set to 45 degrees and the second inclination angle θ2 is set to 60 degrees, but the first inclination angle θ1 and the second inclination angle θ2 are acute angles (θ1, θ2 <90 °). If the second inclination angle θ2 is larger than the first inclination angle θ1 (θ2> θ1), other angles can be adopted. For example, the first inclination angle θ1 is set in the range of 30 to 60 degrees (30 ° <θ1 <60 °), and the second inclination angle θ2 is in the range of 45 to 75 degrees (45 ° <θ1 <75 °). It may be set with. In the present embodiment, the surface of the valve body 38 facing the valve seat 34 is a tapered surface of 60 degrees with respect to the axial direction, but the valve seat 34 is seated on its outer edge (edge portion). It is not always necessary to have a tapered surface. For example, the surface of the valve body 38 that faces the valve seat 34 may be perpendicular to the axial direction (90 °).

  Thus, by making the valve seat 34 have a tapered surface (first tapered surface 106), the seating performance of the valve body 38 can be kept good as shown in FIG. The sealability of the part can be secured. On the other hand, by providing the second taper surface 108 having a larger taper angle outside the first taper surface 106, the valve opening at the time of valve opening is sufficiently increased as shown in FIG. Can be secured. That is, when the valve is opened, the edge portion of the valve body 38 is displaced to the height position of the second tapered surface 108. In this embodiment, the diaphragm 65 having a smaller stroke than that of the bellows or the like is employed as the pressure-sensitive member. Therefore, there is a great technical significance in ensuring the flow rate as a two-stage tapered shape as described above.

  Here, it is conceivable to provide a short tapered surface only with the first tapered surface 106 without providing the second tapered surface 108, but in such a configuration, the flow rate is abrupt with respect to the opening of the valve portion. It becomes difficult to obtain a desired flow rate. That is, the seating performance of the valve body 38 can be improved while keeping the flow rate appropriate by forming the vicinity of the valve seat 34 in a two-step tapered shape as in the present embodiment. In other words, by setting each of the plurality of tapered surfaces to an optimum angle in accordance with a desired flow rate characteristic, it is possible to achieve both countermeasures against leakage of the valve portion and good controllability.

  Returning to FIG. 2, a first seal accommodating portion 110 made of an annular concave groove is provided below the first guide hole 28, and an O-ring 112 (functioning as a “first seal member”) is fitted therein. ing. The O-ring 112 seals the gap between the operating rod 36 and the first guide hole 28, and regulates refrigerant leakage from the discharge pressure chamber 18 to the crank pressure chamber 20. On the other hand, the small-diameter portion 104 of the operating rod 36 is provided with a second seal housing portion 114 formed of an annular concave groove, and an O-ring 116 (functioning as a “second seal member”) is fitted therein. The O-ring 116 seals the gap between the operating rod 36 and the second guide hole 30 and restricts the leakage of the refrigerant from the discharge pressure chamber 18 to the suction pressure chamber 22.

  As shown in FIG. 4A, the first seal accommodating portion 110 accommodates the O-ring 112, but the axial width is configured to be slightly larger than the O-ring 112 in consideration of its assembling property. On the other hand, a gap is formed between the actuating rod 36 and the first guide hole 28 before and after the first seal housing portion 110, and the high-pressure side clearance CL 1 on the discharge pressure chamber 18 side of the first seal housing portion 110. This is configured to be larger than the low pressure side clearance CL2 on the crank pressure chamber 20 side. In the present embodiment, the high pressure side clearance CL1 is set to be larger than the width of the filter mesh of the strainer 24. On the other hand, the low pressure side clearance CL2 is set smaller than the width of the mesh of the filter.

  Similarly, as shown in FIG. 4B, the second seal accommodating portion 114 accommodates the O-ring 116, but the axial width is configured to be slightly larger than the O-ring 116 in consideration of its assembling property. ing. On the other hand, a gap is formed between the actuating rod 36 and the second guide hole 30 before and after the second seal accommodating portion 114, and the high pressure side clearance CL3 on the discharge pressure chamber 18 side of the second seal accommodating portion 114 is reduced. This is configured to be larger than the low-pressure side clearance CL4 on the suction pressure chamber 22 side. In the present embodiment, the high pressure side clearance CL3 is set to be larger than the width of the filter mesh of the strainer 24. On the other hand, the low pressure side clearance CL4 is set smaller than the width of the mesh of the filter.

  With such a configuration, each O-ring is disposed in each seal housing portion, so that the O-ring is pressed so as to close the low-pressure side clearance by the front-rear differential pressure. As a result, the sealing performance of the sliding portion of the operating rod 36 can be maintained satisfactorily. Further, since the low pressure side clearance is relatively small, even if the O-ring 112 is deformed, there is no problem of increasing the sliding resistance by being sandwiched by the low pressure side clearance. On the other hand, since the high-pressure side clearance is relatively large, even if a foreign object enters from the high-pressure side, it is possible to prevent or suppress the entry of the foreign object. As a result, the smooth operation of the operating rod 36 and thus the valve body 38 can be maintained. In addition, by providing a filter, foreign matter that enters the body 10 is restricted to a sufficiently small amount with respect to the high-pressure side clearance. Further, the amount of foreign matter guided between the operating rod 36 and the first guide hole 28 and the amount of foreign matter guided between the operating rod 36 and the second guide hole 30 are suppressed. As a result, it is difficult for foreign matter to be caught.

  Returning to FIG. 2, the diaphragm 65 is supported in such a manner that the outer peripheral edge portion is sandwiched between the flange portion 76 of the sleeve 54 and the plate 78, and the flange portion 76 and the plate 78 are further connected to the connection member 48. It is fixed in such a manner that it is sandwiched between the lower surface and the annular member 80. The diaphragm 65 senses the suction pressure Ps on the side surface opposite to the reference pressure chamber, and displaces the outer peripheral edge portion of the diaphragm 65 as a fulcrum, thereby giving a driving force in the valve opening direction or the valve closing direction to the plunger 58. .

  Here, since the diaphragm 65 is disposed close to the solenoid 3, foreign matter such as metal powder contained in the refrigerant is easily attracted by the magnetic attraction force. As a result, if a foreign object is caught near the fulcrum of the diaphragm 65, there is a concern that local damage may occur due to repeated stress for each operation of the solenoid 3. Therefore, in this embodiment, the support structure near the fulcrum of the diaphragm 65 is devised.

That is, as shown in FIG. 5, when the fulcrum P is located slightly inside the welded portion W (that is, the joint between the flange portion 76 and the plate 78 via the diaphragm 65) in the diaphragm 65, the position of the fulcrum P and its The plate 78 is formed so that the gap S1 on the plate 78 side is larger than the gap S2 on the sleeve 54 side. That is, the plate 78 has a stepped portion 120 that is bent slightly outward from the fulcrum P and toward the connection member 48, and has a step portion 120 that is opposed to the fulcrum P and an inner portion thereof is separated from the diaphragm 65. The distance L between the stepped portion 120 and the diaphragm 65 is equal to or greater than the plate thickness of the plate 78 and is sufficiently larger than the foreign matter that is supposed to enter. Since the gap S1 is sufficiently large at the position where the diaphragm 65 is displaced, even if a foreign substance (see a black circle in the figure) enters one side of the diaphragm 65 as indicated by an arrow in the figure, the foreign substance is in contact with the plate 78 and the diaphragm. It is possible to avoid a situation in which local stress is generated by being sandwiched between the gaps with 65. The inner portion of the diaphragm 65 from the fulcrum P does not come into contact with the stepped portion 120 during the displacement process. The step portion 120 also functions as a sandwiching portion that sandwiches the O-ring 82 with the connection member 48.
The sleeve 54 has a tapered surface 79 in a direction away from the diaphragm 65 inward from the peripheral edge (near the inner end of the welded portion W) in the flange portion 76, and the inner end of the tapered surface 79 is R. The shape is rounded. The diaphragm 65 may be in contact with the flange portion 76 in the course of its displacement from the fulcrum P. However, since the flange portion 76 is formed in a tapered shape and an R shape in this way, local stress is generated. It is prevented. Further, although the gap S2 between the taper surface 79 of the sleeve 54 and the diaphragm 65 is smaller than the gap S1 between the plate 78 and the diaphragm 65, the opening end of the sleeve 54 is sealed by the diaphragm 65. There is no entry of foreign matter. For this reason, the durability of the diaphragm 65 can be maintained high.
In this embodiment, the starting point (R-shaped starting point) of the stepped portion 120 of the plate 78 is set outside the fulcrum P, but may be set at the position of the fulcrum P. Since the fulcrum P itself in the diaphragm 65 is not displaced, even if the fulcrum P and the starting point of the stepped portion 120 coincide with each other, it is possible to prevent or suppress the biting of foreign matter.

  Next, the operation of the control valve 1 will be described. 6 and 7 are diagrams showing the operation process of the control valve. FIG. 6 shows the maximum capacity operation state of the control valve. FIG. 7 shows a relatively stable control state. FIG. 2 which has already been described shows the minimum capacity operation state of the control valve. In the following, description will be given based on FIG. 1 with reference to FIGS. 2, 6 and 7 as appropriate.

  In the control valve 1, when the solenoid 3 is not energized, that is, when the automobile air conditioner is not operating, no suction force acts between the core 56 and the plunger 58. In addition, since the suction pressure Ps is high, the first plunger 66 in contact with the diaphragm 65 is displaced downward against the load of the spring 75. On the other hand, as shown in FIG. 2, the second plunger 68 is biased upward by the spring 74 so as to be separated from the first plunger 66, so that the valve body 38 is biased to its fully open position via the operating rod 36. To do. At this time, the refrigerant having the discharge pressure Pd introduced into the port 14 from the discharge chamber of the compressor passes through the fully opened valve portion and flows from the port 12 to the crank chamber. Therefore, the crank pressure Pc increases and the compressor operates at the minimum capacity.

  On the other hand, when the maximum control current is supplied to the electromagnetic coil 62 of the solenoid 3 as when the automobile air conditioner is started, the first plunger 66 resists the biasing force of the spring 74 via the diaphragm 65. Then, the second plunger 68 is sucked. Therefore, as shown in FIG. 6, the second plunger 68 moves downward by being sucked and abutted against the diaphragm 65, and accordingly, the valve body 38 is pushed down by the spring 46 and the valve seat is moved. 34, the valve portion is fully closed. At this time, the operating rod 36 is in a state of being separated from the second plunger 68.

  When the suction pressure Ps in the suction chamber becomes sufficiently low in this way, as shown in FIG. 7, the diaphragm 65 senses the suction pressure Ps and is displaced upward, and the second plunger 68 comes into contact with the operating rod 36. At this time, if the control current supplied to the electromagnetic coil 62 of the solenoid 3 is reduced according to the set temperature of the air conditioning, the second plunger 68 and the first plunger 66 are integrated in the adsorbed state, and the suction pressure Ps and the spring are integrated. It moves upward to a position where the load of 46, 74, 75 and the suction force of the solenoid 3 are balanced. As a result, the valve body 38 is pushed up by the second plunger 68 and is separated from the valve seat 34 and set to a predetermined opening degree. Therefore, the refrigerant having the discharge pressure Pd is controlled to a flow rate corresponding to the opening degree and introduced into the crank chamber, and the compressor shifts to an operation with a capacity corresponding to the control current.

  When the control current supplied to the electromagnetic coil 62 of the solenoid 3 is constant, the diaphragm 65 senses the suction pressure Ps and controls the valve opening. For example, when the refrigeration load increases and the suction pressure Ps increases, the valve body 38 is displaced downward together with the operating rod 36, the second plunger 68, the diaphragm 65, and the first plunger 66. The opening is reduced and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps decreases and approaches the set pressure. Conversely, when the refrigeration load decreases and the suction pressure Ps decreases, the valve body 38 is displaced upward to increase the valve opening, so that the compressor operates to reduce the discharge capacity. As a result, the suction pressure Ps increases and approaches the set pressure. In this way, the control valve 1 controls the discharge capacity of the compressor so that the suction pressure Ps becomes the set pressure set by the solenoid 3.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. The control valve according to the present embodiment has many parts in common with the first embodiment except for the configuration of the body and the valve driver. For this reason, about the component similar to 1st Embodiment, the same code | symbol is attached | subjected etc., and the description is abbreviate | omitted suitably. FIG. 8 is a partially enlarged cross-sectional view of the upper half of the control valve according to the second embodiment. FIG. 9 is a diagram showing a seal structure of the sliding portion. (A) shows the B section enlarged view of FIG. 8, (B) shows the C section enlarged view of FIG. FIG. 10 is a diagram showing an operation process of the control valve, and shows a state when the bleed function of the control valve is operated. FIG. 8 shows the minimum capacity operation state of the control valve.

  As shown in FIG. 8, the control valve 201 is configured by assembling a valve body 202 and a solenoid 3 integrally. The operating rod 236 has an internal passage 240 for bleed formed in the small diameter portion 204 thereof. The internal passages 40 and 240 form a communication passage that penetrates the operating rod 236 in the axial direction. In the state shown in the figure, the second plunger 68 abuts against the operating rod 236 and seals the lower end opening thereof, so that the communication between the crank pressure chamber 20 and the suction pressure chamber 22 is blocked. When the plunger 68 is separated from the operating rod 236, the refrigerant is allowed to be led out from the crank pressure chamber 20 to the suction pressure chamber 22 through the communication path.

  As shown in FIG. 9A, the first seal housing portion 212 of the present embodiment has a larger depth of the groove than the first seal housing portion 110 of the first embodiment. And an O-ring 112, a gap S3 is formed. With such a configuration, even if the O-ring 112 is compressed in the axial direction due to the differential pressure between the front and the rear, and as a result, the O-ring 112 becomes reactive from the bottom surface of the first seal housing portion 212 even if the O-ring 112 increases radially outward. It is difficult to receive. Thereby, the sliding resistance between the O-ring 112 and the operating rod 236 is prevented from becoming excessive, and the smooth operation of the operating rod 236 and thus the valve body 38 is maintained.

  Similarly, the second seal accommodating portion 214 of the present embodiment has a larger depth of the recessed groove than the second seal accommodating portion 114 of the first embodiment, and is between the bottom surface and the O-ring 116. A gap S4 is formed in the gap. With such a configuration, even if the O-ring 116 is compressed in the axial direction by the differential pressure between the front and rear, and as a result, the O-ring 116 is increased from the bottom surface of the second seal housing portion 214 even if the O-ring 116 increases radially outward. It is difficult to receive. Thereby, the sliding resistance between the O-ring 116 and the body 210 is prevented from becoming excessive, and the smooth operation of the operating rod 236 and thus the valve body 38 is maintained.

  With the configuration as described above, when the maximum control current is supplied to the solenoid 3 as in the case where the automotive air conditioner is activated, the second plunger 68 is generated by the suction force of the solenoid 3 as shown in FIG. Is temporarily separated from the actuating rod 236. For this reason, the crank pressure chamber 20 and the suction pressure chamber 22 communicate with each other. As a result, the refrigerant in the crank chamber is led out from the port 16 to the suction chamber side through the crank pressure chamber 20, the internal passages 40 and 240, and the suction pressure chamber 22. That is, the passage from the discharge chamber to the crank chamber is blocked, and the refrigerant in the crank chamber is released not only through the orifice but also through the control valve 201, so that the compressor can quickly shift to the maximum capacity operation. In the present embodiment, the mechanism that abuts or separates the second plunger 68 and the operating rod 236 in this manner constitutes an “opening / closing mechanism”.

  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 the embodiment described above, a configuration in which a gap is provided in the radial direction of the O-ring (seal member) in the type having the bleed structure shown in FIG. In the modification, a configuration in which a gap is provided in the radial direction of the O-ring (seal member) may be applied to a type that does not have a bleed structure as shown in FIG.

  In the said embodiment, as shown in FIG. 2 etc., the example which provided the 1st seal | sticker accommodating part in the body and provided the 2nd seal | sticker accommodating part in the actuating rod was shown. In the modification, both the first seal housing portion and the second seal housing portion may be provided on the body. Or you may provide both a 1st seal | sticker accommodating part and a 2nd seal | sticker accommodating part in an action | operation rod. Or a 1st seal | sticker accommodating part may be provided in an action | operation rod, and a 2nd seal | sticker accommodating part may be provided in a body.

  In the above embodiment, the diaphragm 65 as the pressure-sensitive member is configured by stacking a plurality of polyimide films, but may be configured by another resin material or a metal thin plate such as beryllium copper or stainless steel.

  In the above-described embodiment, an example in which the control valve is configured as a so-called Ps sensing valve that performs capacity control so as to keep the suction pressure Ps of the variable capacity compressor at a set pressure has been described. The controlled object is not limited to these. For example, it can be configured as a so-called Pc sensing valve that introduces the crank pressure Pc from the port 16 and controls the capacity so as to keep the crank pressure Pc at a set pressure.

  In the above embodiment, the control valve is configured as a control valve that controls the flow rate of refrigerant introduced from the discharge chamber of the variable capacity compressor into the crank chamber. However, the flow rate of refrigerant led out from the crank chamber to the suction chamber is controlled. You may comprise as a control valve.

  In the above embodiment, the solenoid split type is illustrated as the solenoid 3, but a solenoid composed of a single plunger may be adopted. In that case, you may provide a pressure sensitive part between an action | operation rod and a plunger, or the other side to a plunger with respect to an action | operation rod.

  In the said embodiment, although the control valve which controls the flow of a refrigerant | coolant was illustrated as a working fluid, you may comprise as an electromagnetic valve which controls the flow of working fluids other than a refrigerant | coolant.

  DESCRIPTION OF SYMBOLS 1 Control valve, 2 Valve body, 3 Solenoid, 10 Body, 18 Discharge pressure chamber, 20 Crank pressure chamber, 22 Suction pressure chamber, 28 1st guide hole, 30 2nd guide hole, 32 Valve hole, 34 Valve seat, 36 Actuating rod, 38 Valve body, 54 Sleeve, 56 Core, 58 Plunger, 62 Electromagnetic coil, 64 Plate, 65 Diaphragm, 66 First plunger, 68 Second plunger, 76 Flange, 78 Plate, 82 O-ring, 106 1st Taper surface, 108 second taper surface, 110 first seal housing portion, 112 O-ring, 114 second seal housing portion, 116 O-ring, 120 stepped portion, 201 control valve, 202 valve body, 210 body, 212 first seal Accommodation part, 214 second seal accommodation Part, 236 actuation rod, CL1 high pressure side clearance, CL2 low pressure side clearance, CL3 high pressure side clearance, CL4 low pressure side clearance, S1, S2, S3, S4 gap.

Claims (5)

A body with a fluid passage formed therein;
A valve seat formed at an opening end of a valve hole provided in the fluid passage;
A valve body that is driven in the axial direction of the valve hole, opens and closes the valve seat, and opens and closes the valve portion;
With
A first tapered surface having a first inclination angle with respect to the axial direction at the opening end of the valve hole, and a radially outer side of the first tapered surface, the first tapered angle with respect to the axial direction from the first inclination angle. And a second tapered surface having a large second inclination angle, and the first tapered surface functions as a valve seat. A guide hole provided coaxially with the valve hole in the body;
An operating rod that is slidably supported in the guide hole and in which the valve body is provided integrally;
A housing provided on the body; and a diaphragm provided to seal an opening of the housing to form a reference pressure chamber in the housing, wherein the diaphragm senses a sensed pressure outside the housing. Then, by displacing the peripheral part as a fulcrum, a pressure-sensitive part capable of applying a driving force in the opening / closing direction of the valve part to the valve body via the operating rod,
The control valve according to claim 1, further comprising: The suction pressure or the crank pressure is detected as the sensed pressure, and at least one of the refrigerant flow rate introduced from the discharge chamber into the crank chamber and the refrigerant flow rate led out from the crank chamber to the suction chamber is controlled to discharge the variable capacity compressor. It is configured as a control valve that changes the capacity,
The valve hole is provided in a refrigerant passage that communicates at least one of the discharge chamber and the suction chamber with the crank chamber,
The pressure sensing unit senses the suction pressure or the crank pressure of the suction chamber as the sensed pressure, and when the sensed pressure becomes lower than a set pressure, the valve body is opened in the valve opening direction via the actuating rod. Applying force,
The control valve according to claim 2, further comprising a solenoid that causes a solenoid force in a valve closing direction corresponding to the set pressure to act on the valve body via the operating rod. The body includes a discharge pressure chamber communicating with the discharge chamber, a crank pressure chamber communicating with the crank chamber, a pressure sensing chamber into which the pressure to be sensed is introduced, the discharge pressure chamber as the guide hole, and the The valve formed between the first guide hole connecting the crank pressure chamber, the second guide hole connecting the discharge pressure chamber and the pressure sensing chamber, and the first guide hole and the second guide hole. A hole is provided,
One end side of the operating rod is slidably supported in the first guide hole, while the other end side is slidably supported in the second guide hole, and the valve body is provided in an intermediate portion. The control valve according to claim 3, wherein an internal passage is formed for communicating the valve hole and the crank pressure chamber when the valve is opened. The solenoid includes a core fixed to the body, a plunger that transmits the driving force to the valve body while supporting the other end of the operating rod, and a magnetic circuit that includes the plunger and the core when energized. An electromagnetic coil to be generated,
The plunger is configured by arranging a first plunger facing the core and a second plunger supporting the other end of the operating rod in series in the axial direction,
An urging member that urges the diaphragm and the second plunger in a valve opening direction is disposed between the first plunger and the second plunger.
When the solenoid is energized, the first plunger and the second plunger operate integrally through the diaphragm, and when the solenoid is not energized, the second plunger is urged by the urging force of the urging member. The control valve according to claim 3 or 4, wherein the control valve is configured to be separated from the first plunger.

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