Control valve for variable displacement compressor

Abstract

To provide a variable-capacity compressor control valve that is configured for easily setting the opening degree of an in-valve release passage, and thus can effectively reduce internal circulation of refrigerant within the compressor and effectively improve the operation efficiency of the compressor.SOLUTION: An in-valve large-opening release passage with a relatively large opening degree, which is used during the compressor actuation time, and an in-valve small-opening release passage with a relatively small opening degree, which is used during both the compressor actuation time and the normal control time (i.e., Pd→Pc control time), are formed using different passages.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present disclosure relates to a control valve for a variable displacement compressor used in a car air conditioner or the like, and more particularly to a control valve for a variable displacement compressor that can reduce internal circulation of a refrigerant inside the compressor and improve the operating efficiency of the compressor. [Background technology]

[0002] Conventionally, a swash plate type variable displacement compressor as shown in Fig. 8A and Fig. 8B has been used as a compressor for a car air conditioner. This swash plate type variable displacement compressor 100 has a rotating shaft 101 that is rotated by a vehicle engine, a swash plate 102 attached to the rotating shaft 101, a crank chamber 104 in which the swash plate 102 is disposed, a piston 105 that is reciprocated by the swash plate 102, a discharge chamber 106 for discharging the refrigerant compressed by the piston 105, a suction chamber 107 for sucking the refrigerant, an internal relief passage (fixed orifice) 108 for releasing the pressure Pc of the crank chamber 104 to the suction chamber 107, and the like.

[0003] On the other hand, the control valve 1' used in the above-mentioned variable displacement compressor is adapted to receive a discharge pressure Pd from the discharge chamber 106 of the compressor 100, and to regulate the discharge pressure Pd in ​​accordance with the suction pressure Ps of the compressor 100, thereby controlling the pressure Pc in the crank chamber 104. As a basic configuration, the control valve 1' has a valve chamber provided with a valve port and a Ps inlet / outlet communicating with the suction chamber 107 of the compressor 100, and a Pd inlet / outlet communicating with the discharge chamber 106 of the compressor 100 on the upstream side of the valve port. a valve body provided with a valve port and a Pc inlet / outlet downstream of the valve port that communicates with a crank chamber 104 of the compressor 100; a main valve body for opening and closing the valve port; an electromagnetic actuator having a plunger for moving the main valve body in the valve port opening / closing direction; a pressure sensing chamber into which a suction pressure Ps from the compressor 100 is introduced via the Ps inlet / outlet; and a pressure sensing responsive member for urging the main valve body in the valve port opening / closing direction in response to the pressure in the pressure sensing chamber. The main valve body is provided with an in-valve relief passage 16' for releasing the pressure Pc of the pressure regulator 104 to the suction chamber 107 of the compressor 100 through the Ps inlet and outlet, and a sub-valve body is provided for opening and closing the in-valve relief passage 16'. When the plunger is continuously moved upward from the lowest position by the attraction force of the electromagnetic actuator, the sub-valve body moves upward together with the plunger while keeping the in-valve relief passage 16' closed, and the sub-valve body is driven by the pressure regulator 102. Accordingly, the main valve body is moved upward and the valve port is closed by the main valve body. When the plunger is then moved further upward, the sub-valve body opens the intra-valve relief passage 16'. The main valve body and the valve port form a main valve section indicated by the symbol 11' in Figures 8A and 8B, and the sub-valve body and the intra-valve relief passage form a sub-valve section indicated by the symbol 12' (see, for example, JP 2013-130126 A, etc.).

[0004] In the control valve 1' having such a configuration, during normal control (Pd→Pc control), when a solenoid unit consisting of a coil, a stator, an attractor, etc. of the electromagnetic actuator is energized, the plunger is attracted to the attractor, and the sub-valve body moves upward together with the plunger, and the main valve body is moved in the valve closing direction by the biasing force of the valve closing spring following the movement of the sub-valve body. Meanwhile, the suction pressure Ps introduced from the compressor 100 through the Ps inlet / outlet is introduced from the inlet / outlet chamber through the horizontal hole of the plunger, etc. into the pressure-sensitive chamber, and the pressure-sensitive responsive member (for example, a bellows device) expands or contracts (contracts when the suction pressure Ps is high and expands when the suction pressure Ps is low) in response to the pressure in the pressure-sensitive chamber (suction pressure Ps), and the displacement (biasing force) is transmitted to the main valve body, whereby the main valve body portion of the main valve body rises and falls relative to the valve port, adjusting the valve opening of the main valve portion 11'. That is, the valve opening degree is determined by the suction force of the plunger by the solenoid portion, the biasing force (expansion force) due to the expansion and contraction displacement of the pressure-sensitive responsive member, the biasing forces by the plunger spring (valve-opening spring) and the valve-closing spring, and the forces in the valve-opening and valve-closing directions acting on the main valve body, and the pressure Pc in the crank chamber 104 (hereinafter sometimes referred to as crank chamber pressure Pc or simply pressure Pc) is controlled according to the valve opening degree. In this case, the main valve body is always biased upward by the biasing force of the valve-closing spring, and the sub-valve body is always biased downward by the biasing force of the valve-opening spring, so that the sub-valve portion 12' is closed, the in-valve relief passage 16' is blocked within the main valve body, and the crank chamber pressure Pc is not released to the suction chamber 107 through the in-valve relief passage 16'.

[0005] In contrast, when the compressor is started, the solenoid section is energized and the plunger is attracted to the suction element, causing the sub-valve body to move upward together with the plunger. Following this upward movement of the sub-valve body, the main valve body is caused to move in the valve closing direction by the force of the valve closing spring, and after the valve port is closed by the main valve body section of the main valve body, the plunger is caused to move further upward, thereby causing the sub-valve body to open the intra-valve relief passage 16'.

[0006] In this manner, in the conventional control valve 1', when the compressor is started, the crank chamber pressure Pc is released to the suction chamber 107 through two passages, the in-machine relief passage 108 and the in-valve relief passage 16', so that the time required for the discharge capacity to increase can be shortened. Also, during normal control (Pd→Pc control), the in-valve relief passage 16' is closed by the sub-valve element, so that the operating efficiency of the compressor 100 does not decrease.

[0007] In addition, in the above-mentioned variable displacement compressor control valve 1', the in-valve relief passage 16' is closed by the sub-valve body during normal control (Pd → Pc control), but a valve that releases some of the crank chamber pressure Pc to the suction chamber through the in-valve relief passage (auxiliary communication passage) together with the in-machine relief passage (fixed orifice) during normal control (Pd → Pc control) has already been developed (see, for example, Patent No. 5167121, International Publication No. 2018 / 043186, etc.). In a control valve of this configuration, depending on the system configuration, the passage area (opening area) of the in-machine relief passage (fixed orifice) can be reduced, and the internal circulation of the refrigerant in the compressor can be reduced, which may improve the operating efficiency of the compressor.

[0008] As described above, in a control valve that auxiliary releases the crank chamber pressure Pc to the suction chamber through the in-valve relief passage during normal control (Pd → Pc control), when the compressor is started or the volume of refrigerant flowing through the valve is large, it is desirable for the passage area of ​​the in-valve relief passage (i.e., the Pc-Ps flow path area) to be large, and when the power is turned off or the volume of refrigerant flowing through the valve is small, it is desirable for the passage area of ​​the in-valve relief passage (i.e., the Pc-Ps flow path area) to be small.

[0009] However, conventional control valves described in, for example, Japanese Patent No. 5167121 and International Publication No. 2018 / 043186 have the following problems to be solved.

[0010] In other words, in the control valve described in Patent Gazette No. 5167121, during normal control (Pd → Pc control), a certain amount of refrigerant determined by the passage area of ​​the relief passage within the valve flows into the suction chamber, which could lead to a deterioration in the operating efficiency of the compressor during normal control (Pd → Pc control).

[0011] In addition, in the control valve described in WO 2018 / 043186, compared to the control valve described in Japanese Patent No. 5167121, the passage area of ​​the in-valve relief passage is made variable, which makes it possible to reduce the minimum passage area of ​​the in-valve relief passage (Pc-Ps flow area) during normal control (Pd->Pc control). However, since the in-valve relief passage used when the compressor is started and the in-valve relief passage used during normal control (Pd->Pc control) are basically formed as a common (single) passage, there is little freedom in designing the passage area of ​​the in-valve relief passage (Pc-Ps flow area), and it is difficult to set the opening degree of the in-valve relief passage as described above. Summary of the Invention [Problem to be solved by the invention]

[0012] The present disclosure has been made in consideration of the above circumstances, and an exemplary embodiment relates to providing a control valve for a variable displacement compressor, which enables easy setting of the opening degree of an in-valve relief passage, effectively reduces internal circulation of refrigerant within the compressor, and effectively improves the operating efficiency of the compressor. [Means for solving the problem]

[0013] Therefore, a control valve for a variable displacement compressor according to an embodiment of the present disclosure basically comprises a valve body having a valve chamber in which a valve port is provided and a Ps inlet / outlet communicating with a suction chamber of a compressor, a Pd inlet / outlet communicating with a discharge chamber of the compressor provided upstream of the valve port and a Pc inlet / outlet communicating with a crank chamber of the compressor provided downstream of the valve port, a main valve body for opening and closing the valve port, and an electromagnetic actuator having a plunger for moving the main valve body in a valve port opening / closing direction, a pressure sensing chamber into which suction pressure Ps from the compressor is introduced via the Ps inlet / outlet, and a valve body having a pressure sensing chamber for moving the main valve body in a valve port opening / closing direction according to the pressure in the pressure sensing chamber. the large opening relief passage in the large opening valve for releasing the pressure Pc in the crank chamber to the suction chamber of the compressor via the Ps inlet and outlet; a sub-valve body which opens and closes the large opening relief passage in the large opening valve by movement of the plunger; and a small opening relief passage in the large opening valve which releases the pressure Pc in the crank chamber to the suction chamber of the compressor via the Ps inlet and outlet and has a smaller opening than the large opening relief passage, wherein the small opening relief passage is opened and closed in accordance with the movement of the main valve body due to the movement of the plunger, and is opened by the sub-valve body before the large opening relief passage is opened.

[0014] In one embodiment, the opening of the relief passage in the small opening valve is variable according to the amount of movement of the main valve body caused by the movement of the plunger. In another embodiment, the relief passage in the small opening valve is gradually narrowed as the opening of the main valve body gradually increases. This makes the opening of the main valve body smaller than when the small opening of the passage is a fixed area, thereby reducing internal circulation of the refrigerant.

[0015] In one aspect, the main valve element is slidably inserted into the valve body, the large-opening relief passage within the valve includes a through relief hole running vertically through the main valve element, and the small-opening relief passage within the valve includes a portion of the through relief hole and a communicating hole extending from the through relief hole to the sliding surface of the main valve element with the valve body.

[0016] In one embodiment, the small opening valve internal relief passage includes an inner circumferential groove provided on an upper side of a sliding surface of the valve body that slides against the main valve element.

[0017] In one embodiment, the small opening valve relief passage is opened before the valve port is closed by the main valve body.

[0018] In one aspect, when the plunger is continuously moved upward from the lowermost position by the suction force of the electromagnetic actuator, the sub-valve body is moved upward together with the plunger while keeping the large opening valve relief passage closed, thereby opening the small opening valve relief passage, and as the main valve body moves upward due to the movement of the plunger which gradually reduces the opening of the main valve body, the opening of the small opening valve relief passage is gradually increased, and thereafter, after the main valve body closes the valve port, the plunger is moved further upward, and the sub-valve body is moved upward together with the plunger while keeping the main valve body closing the valve port, thereby opening the large opening valve relief passage. Effect of the Invention

[0019] According to the present disclosure, a relief passage in the large opening valve with a relatively large opening used when the compressor starts up, and a relief passage in the small opening valve with a relatively small opening used both when the compressor starts up and during normal control (Pd→Pc control) can be formed as separate passages. Therefore, compared to the conventional system in which these are basically formed as a common (single) passage, the opening of the relief passages in the large opening and small opening valves can be easily set, the internal circulation of the refrigerant in the compressor can be effectively reduced, and the operating efficiency of the compressor can be effectively improved. [Brief description of the drawings]

[0020] [Figure 1] 1 is a longitudinal cross-sectional view showing a state (normal control (power off)) of a main valve of an embodiment of a control valve for a variable displacement compressor according to the present disclosure, in which the main valve is fully open, the sub-valve is closed, and the auxiliary sub-valve is closed. [Diagram 2]1 is a vertical cross-sectional view showing an embodiment of a control valve for a variable displacement compressor according to the present disclosure in a state where a main valve is open, a sub-valve is closed, and an auxiliary sub-valve is open (during normal control (when power is applied)). FIG. [Diagram 3] 1 is a longitudinal cross-sectional view showing an embodiment of a control valve for a variable displacement compressor according to the present disclosure in a state where a main valve is closed, a sub-valve is closed, and an auxiliary sub-valve is open (during compressor startup transition). FIG. [Figure 4] 1 is a longitudinal cross-sectional view showing an embodiment of a control valve for a variable displacement compressor according to the present disclosure in a state where a main valve is closed, a sub-valve is open, and an auxiliary sub-valve is open (at compressor startup). FIG. [Diagram 5] FIG. 2 is an external perspective view of a main valve body used in the control valve for a variable displacement compressor according to the present disclosure. [Figure 6] 3A to 3C are diagrams for explaining the operation of an embodiment of a control valve for a variable displacement compressor according to the present disclosure. [Figure 7] FIG. 13 is a diagram showing the relationship between the current value (plunger lift amount) of the electromagnetic actuator and the flow path area of ​​the Pd-Pc flow path and the Pc-Ps flow path during operation of an embodiment of the control valve for a variable displacement compressor according to the present disclosure. [Figure 8A] FIG. 13 is a diagram showing a refrigerant pressure flow state between a compressor and a control valve in a conventional example, during normal control. [Figure 8B] FIG. 13 is a diagram showing a refrigerant pressure flow state between a compressor and a control valve in a conventional example, and shows the state when the compressor is started. [Figure 9] FIG. 5 is a diagram showing the bottom of the plunger in FIGS. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0021] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings.

[0022] 1 to 4 are vertical cross-sectional views showing an embodiment of a control valve for a variable displacement compressor according to the present disclosure, in which Fig. 1 shows a state in which the main valve is fully open, the sub-valve is closed, and the auxiliary sub-valve is closed (during normal control (when power is off)), Fig. 2 shows a state in which the main valve is open, the sub-valve is closed, and the auxiliary sub-valve is open (during normal control (when power is on)), Fig. 3 shows a state in which the main valve is closed, the sub-valve is closed, and the auxiliary sub-valve is open (when the compressor is starting), and Fig. 4 shows a state in which the main valve is closed, the sub-valve is open, and the auxiliary sub-valve is open (when the compressor is starting). Fig. 2 shows a state in which the valve opening of the valve port 22 is adjusted (from the fully open state) by energizing the electromagnetic actuator 30 (energizing on) during energization control (from the state in Fig. 1) (valve opening: small state).

[0023] In this specification, descriptions indicating positions and directions such as up and down, left and right, front and back, etc. are given for the sake of convenience in accordance with the drawings to avoid making the explanation complicated, and do not necessarily indicate the positions and directions when the control valve of the present disclosure is actually installed in a compressor.

[0024] In addition, in each figure, the gaps formed between components, the separation distances between components, etc. may be drawn larger or smaller than the dimensions of each component in order to make the present disclosure easier to understand and for convenience in drawing.

[0025] The control valve 1 in the illustrated embodiment basically comprises a valve body 20 provided with a valve port 22, a main valve element 10 for opening and closing the valve port 22, an electromagnetic actuator 30 for moving the main valve element 10 in the valve port opening and closing direction (up and down), and a bellows device 40 as a pressure-sensitive responsive member.

[0026] The electromagnetic actuator 30 includes a bobbin 38, a coil 32 for energizing the bobbin 38, a stator 33 and an attractor 34 arranged on the inner periphery of the coil 32, a guide pipe 35 whose upper end is joined by welding to the outer periphery (step portion) of the lower end of the stator 33 and the attractor 34, a bottomed cylindrical plunger 37 arranged below the attractor 34 on the inner periphery of the guide pipe 35 so as to be able to slide freely in the vertical direction, a cylindrical housing 60 with a bottomed hole that is fitted onto the coil 32, a connector portion 31 attached to the upper side of the housing 60 via an attachment plate 39, and a holder 29 arranged between the lower end (bottom hole) of the housing 60 and the lower end of the guide pipe 35 for fixing them to the upper part of the valve body 20 (main body member 20A). In this example, a cylindrical attractor 34 is integrally molded on the lower inner periphery of a cylindrical stator 33, with an insertion hole 34a having a diameter smaller than the inner diameter of the stator 33 formed at its center (along the axis O). The upper end (thin wall portion) of the housing 60 is crimped and fixed to an annular groove 31a provided on the outer periphery of the connector portion 31, with an O-ring 31A as a sealing material sandwiched therebetween (crimped portion 61). Here, the portion of the electromagnetic actuator 30 consisting of the coil 32, the stator 33, the attractor 34, etc., excluding the plunger 37, is referred to as a solenoid portion 30A.

[0027] A short cylindrical stator 65 is fixed to the upper part of the stator 33 by press-fitting or the like, and a pressure-sensing chamber 45 into which the suction pressure Ps of the compressor is introduced is formed between the stator 65 and the attractor 34 on the inner circumferential side of the stator 33. A bellows device 40 is disposed in the pressure-sensing chamber 45, and the bellows device 40 is composed of a bellows 41, an inverted convex upper stopper 42, an inverted concave lower stopper 43, and a compression coil spring 44, as a pressure-sensing responsive member. Further, a stepped rod-shaped push rod 46 is disposed below the bellows device 40 along the axis O as a thrust transmission member. A portion of the push rod 46 slightly above the center has a large diameter (large diameter portion 46b), and an upper end portion 46d of the push rod 46 is inserted and supported in the recess of the lower stopper 43, and the large diameter portion 46b of the push rod 46 is inserted (with a small gap 34b) into the insertion hole 34a of the attractor 34. In addition, the lower part of the push rod 46 is inserted into a concave hole 17b of the sub-valve body 17, which has a concave cross-section as described below, and its lower end part 46a is fitted into a concave insertion hole 17c formed in the center of the bottom of the concave hole 17b.

[0028] The sub-valve body 17, which has a concave cross section and a concave hole 17b with a diameter substantially the same as the insertion hole 34a of the suction element 34, is inserted and fixed in the plunger 37 by press-fitting or the like, so that the sub-valve body 17 and the plunger 37 can move up and down together. The sub-valve body 17 is fitted into the plunger 37 with its upper end aligned with the upper end of the plunger 37 (in other words, its upper end is positioned on the inner circumference of the upper end of the plunger 37) and its lower end with a gap from the bottom of the plunger 37 (as will be described later in detail, with a gap that allows the brim-shaped locking portion 10k of the main valve body 10 to be positioned slightly up and down). A concave insertion hole 17c into which the lower end 46a of the push rod 46 is inserted is formed in the center of the bottom of the concave hole 17b of the sub-valve body 17.

[0029] A plunger spring (valve-opening spring) 47 made of a cylindrical compression coil spring is compressed and fitted between a step portion (a downward annular terrace surface) 46c formed on the upper part of the large diameter portion 46b of the push rod 46 and the bottom (the upward surface around the insertion hole 17c at) of the recessed hole 17b of the sub-valve body 17 fitted into the plunger 37. The plunger 37 is urged downward (in the valve-opening direction) via the sub-valve body 17 by (the compression force of) this plunger spring 47, and the bellows device 40 is held in the pressure sensing chamber 45 via the push rod 46. In addition, the plunger spring 47 (compressive force) urges the sub-valve body 17 in the direction of closing the large opening valve internal relief passage 16 (through relief hole 16A) described later, and the lower end (flat surface) of the sub-valve body 17 forms the sub-valve body portion 17a which opens and closes the large opening valve internal relief passage 16 (described in detail later).

[0030] A slit 37s with a through hole for passing the flange-shaped locking portion 10k of the main valve body 10 is formed in the bottom of the plunger 37, which extends linearly from near the outer periphery to the center (on the axis O). The height (in the vertical direction) of the slit 37s (i.e., the thickness (vertical height) of the bottom of the plunger 37) is slightly smaller than the height of the upper small diameter portion 10d of the main valve body 10, so that the main valve body 10 can move up and down relative to the plunger 37 (described in detail later). In addition, the width (in the horizontal direction) of the slit 37s is set to be slightly larger than the outer diameter of the upper small diameter portion 10d of the main valve body 10 and smaller than the outer diameter of the flange-shaped locking portion 10k of the main valve body 10, taking into consideration ease of assembly, and the outer peripheral portion of the slit 37s on the bottom upper surface of the plunger 37 is made into an inner flange-shaped locking portion 37k for locking the flange-shaped locking portion 10k of the main valve body 10. Fig. 9 shows the bottom of the plunger 37 with the slit 37s as seen in the vertical direction. In this figure, the contour of the slit 37s may be formed at least partially by a first circular contour portion 37sa and at least partially by an elliptical contour portion 37sb, particularly by a second circular contour portion 37sb.

[0031] In addition, in this example, a communicating groove 37d consisting of a D-cut surface or one or more vertical grooves, etc. is formed at a predetermined position on the outer periphery of the plunger 37 (in the illustrated example, the side on which the slit 37s is formed), and a gap 36 is formed between the outer periphery of the plunger 37 and the inner periphery of the guide pipe 35.

[0032] The main valve body 10, which is disposed below the plunger 37 and the sub-valve body 17, is made of, for example, a nonmagnetic metal, and is formed of a stepped shaft-like member disposed along the axis O. This main valve body 10 is composed of, from the bottom, a relatively large-diameter main valve body portion 10a, a lower small-diameter portion 10b, a vertically long intermediate insert portion 10c, an upper small-diameter portion 10d, and a flange-shaped locking portion 10k, and an annular groove 10A is provided in two upper and lower stages on the outer periphery of the lower portion of the intermediate insert portion 10c.

[0033] As described above, the upper small diameter portion 10d of the main valve body 10 is loosely fitted into the slit 37s, and the flange-shaped locking portion 10k is loosely fitted into the plunger 37 below the sub-valve body 17 (in other words, the space between the bottom of the plunger 37 and the lower end of the sub-valve body 17). The flange-shaped locking portion 10k has a smaller diameter than the sub-valve body 17 and a larger diameter than the width of the slit 37s, so that when the plunger 37 is moved upward relative to the main valve body 10, the inner flange-shaped hooking portion 37k formed from the outer periphery of the slit 37s is hooked onto the flange-shaped locking portion 10k and locked to prevent it from coming off. The intermediate fitting portion 10c has a diameter slightly larger than the width of the slit 37s and smaller than the outer diameter of the plunger 37.

[0034] In addition, in this example, a through escape hole 16A that constitutes part of the large opening valve escape passage 16 described later is formed so as to penetrate (run through) the center of the main valve body 10 in the vertical direction (in other words, along the axis O), and the intermediate insertion portion 10c is formed with a communicating hole 15A consisting of a horizontal hole which, together with the through escape hole 16A, constitutes part of the small opening valve escape passage 15 described later, and an outer circumferential groove 15B consisting of an annular recessed groove that passes through the outer circumferential portion (outer opening) of the communicating hole 15A (in other words, connected to the communicating hole 15A) (see Figure 5).

[0035] On the other hand, the valve body 20 is divided into two parts: a stepped cylindrical main body member 20A having a fitting hole 20C at the center of the upper part and a accommodating hole 18 connected to the recessed hole 20C and having a slightly smaller diameter than the recessed hole 20C at the center of the lower part, and a cylindrical seat member 20B which is inserted and fixed into the recessed hole 20C by press fitting or the like.

[0036] The seat member 20B is made of stainless steel (SUS), high-hardness brass, or the like, and a stopper portion 24A for determining the lowest position of the plunger 37 is protruded from the upper side of the stepped fitting portion 24 that is fitted into the recessed hole 20C (in other words, protruding from the fitting portion 24 toward the Ps entrance / exit chamber 28 side). In this example, the outer diameter of the seat member 20B (the stopper portion 24A) is slightly smaller than the outer diameter of the plunger 37, and the upper end surface of the stopper portion 24A (the surface that abuts against the plunger 37) is an annular flat surface. The lower end of the fitting portion 24 of the seat member 20B is abutted against the step portion (terrace portion) between the recessed hole 20C and the accommodation hole 18 of the main body member 20A. Further, a guide hole 19 into which the intermediate fitting portion 10c of the main valve body 10 is slidably inserted is formed so as to penetrate vertically through the center of the seat member 20B (i.e., along the axis O), and the lower end of this guide hole 19 serves as a valve port (valve seat portion) 22 that is opened and closed by the main valve body portion 10a provided at the lower end of the main valve body 10. Here, the main valve portion 11 is composed of the main valve body portion 10a and the valve port 22.

[0037] In this example, an inner circumferential groove 19A is formed at the upper end of the guide hole 19 (in other words, the inner circumferential surface of the seat member 20B) and is made of an annular step having a predetermined depth (height) in the vertical direction, which constitutes part of the relief passage 15 in the small opening valve described later.

[0038] The main body member 20A is made of, for example, aluminum, brass, or resin, and in a state where the seat member 20B (the fitting portion 24) is inserted into the recessed hole 20C of the main body member 20A, a Ps inlet / outlet chamber 28 for the suction pressure Ps of the compressor is formed on the outer periphery of the stopper portion 24A (in other words, on the upper end side of the seat member 20B in the main body member 20A), and a plurality of Ps inlets / outlets 27 are formed on the outer periphery side of the Ps inlet / outlet chamber 28. The suction pressure Ps introduced from the Ps inlet / outlet 27 to the Ps inlet / outlet chamber 28 is introduced into the pressure sensing chamber 45 through a gap 36 (in this example, a gap formed by the communication groove 37d) formed between the outer periphery of the plunger 37 and the guide pipe 35, a gap 34b formed between the outer periphery of the push rod 46 and the suction element 34, etc.

[0039] In addition, a guide hole 19 and the accommodation hole 18, which is larger in diameter than the main valve body portion 10a, are connected to the bottom center of the recessed hole 20C of the main body member 20A in order to accommodate the main valve body portion 10a of the main valve body 10. A valve-closing spring 50 made of a conical compression coil spring is compressed between the bottom outer circumferential corner of the accommodation hole 18 and a step portion (terrace portion) 10f provided on the lower outer periphery of the main valve body portion 10a of the main valve body 10. The main valve body 10 is urged in the valve-closing direction (upward) by the urging force of this valve-closing spring 50, and the main valve body 10 (the upper end of the brim-shaped engagement portion 10k) is pressed against the sub-valve body 17 (the lower surface). Here, the inside of the accommodation hole 18 (the portion below the valve port 22 of the seat member 20B) becomes a valve chamber 21.

[0040] A plurality of Pd inlets 25 communicating with the discharge chamber of the compressor are opened in the recessed hole 20C, and a ring-shaped filter member 25A is disposed around the outer periphery of the Pd inlets 25. A plurality of horizontal holes 25s communicating with the Pd inlets 25 and communicating with the guide hole 19 are provided in the fitting portion 24 of the seat member 20B inserted into the recessed hole 20C (particularly, the portion below the portion of the fitting portion 24 into which the intermediate fitting portion 10c of the main valve body 10 is inserted, and upstream of the valve port 22).

[0041] A lid-like member 48 functioning as a filter is fixed to the lower end of the main body member 20A by engagement, press-fitting, or the like, and the area above the lid-like member 48 and below the accommodation hole 18 (in other words, the lower end side of the seat member 20B in the main body member 20A and downstream of the valve port 22) constitutes a Pc inlet / outlet chamber (inlet / outlet) 26 that communicates with the crank chamber of the compressor. This Pc inlet / outlet chamber (inlet / outlet) 26 communicates with the Pd introduction port 25 via the valve chamber 21 → the gap between the valve port 22 and the main valve body portion 10a → the gap between the lower part of the guide hole 19 and the lower small diameter portion 10b → the horizontal hole 25s of the fitting portion 24.

[0042] Furthermore, in this embodiment, a through escape hole 16A is provided that penetrates the interior center of the main valve body 10 in the vertical direction (axis O direction) to communicate between the Pc inlet / outlet chamber 26 and the Ps inlet / outlet chamber 28 (Ps inlet / outlet 27).

[0043] This through relief hole 16A constitutes part of the relief passage 16 within the large opening valve, and the upper end of this through relief hole 16A (i.e., the upper end of the main valve body 10) forms the sub-valve seat portion 23 with which the lower end (sub-valve body portion) 17a of the sub-valve body 17 comes into contact and separates.

[0044] As described above, the sub-valve element 17 is inserted and fixed to the plunger 37 above the main valve element 10, the outer diameter of the sub-valve element 17 (= the inner diameter of the plunger 37) is larger than the outer diameter of the flange-shaped locking portion 10k of the main valve element 10, and the lower end portion (flat surface) of the sub-valve element 17 comes into contact with and separates from the sub-valve seat portion (inverted truncated cone surface portion) 23, which is the upper end edge portion of the through-hole 16A, to form the sub-valve element portion 17a that opens and closes the large-opening intra-valve relief passage 16 (through-hole 16A). Here, the sub-valve seat portion 23 and the sub-valve element portion 17a form the sub-valve portion 12.

[0045] In this embodiment, as described above, the large opening valve internal relief passage 16 for releasing the pressure Pc of the crank chamber to the suction chamber of the compressor via the Ps inlet / outlet 27 is formed by the Pc inlet / outlet chamber 26, the valve chamber 21, the through relief hole 16A provided in the main valve body 10, inside the plunger 37, the Ps inlet / outlet chamber 28, etc., and the large opening valve internal relief passage 16 is opened and closed by the sub-valve body portion (lower end portion) 17a of the sub-valve body 17 coming into contact with and separating from the sub-valve seat portion 23, which is the upper edge portion of the through relief hole 16A.

[0046] Further, in this embodiment, in addition to the above configuration, in order to auxiliary communicate the Pc inlet / outlet chamber 26 and the Ps inlet / outlet chamber 28 (Ps inlet / outlet 27), a communication hole 15A is provided in the upper part of the intermediate fitting portion 10c of the main valve body 10, which extends laterally (perpendicular to the axis O) from the through-hole 16A formed inside the main valve body 10 to the outer circumferential surface (specifically, the sliding surface with the seat member 20B of the valve body 20 of the main valve body 10) and is a horizontal hole with a smaller diameter than the through-hole 16A, and a peripheral groove 15B is provided in the outer circumferential surface of the intermediate fitting portion 10c, which is an annular recessed groove passing through the outer circumferential portion (outer opening) of the communication hole 15A. That is, in this example, the communication hole 15A extends laterally from the upper part of the through-hole 16A and opens at the outer circumferential surface (the peripheral groove 15B provided in the outer circumferential surface).

[0047] In addition, an inner circumferential groove 19A having a predetermined depth (height) in the vertical direction and consisting of an annular step that is open to the Ps entry / exit chamber 28 side (upper side) is provided at the upper end (i.e., the upper side of the sliding surface with the intermediate insertion portion 10c of the main valve body 10) of the inner circumferential surface (guide hole 19) of the seat member 20B of the valve body 20, into which the intermediate insertion portion 10c of the main valve body 10 is inserted. This inner circumferential groove 19A is located above the communicating hole 15A and the outer circumferential groove 15B when the main valve body 10 is in the lowest position (when the electromagnetic actuator 30 (solenoid portion 30A) is turned off, the lowest end face of the plunger 37 abuts against the stopper portion 24A to take the lowest position, and the valve orifice 22 is fully open), and is formed in a position that overlaps (connects with) the communicating hole 15A and the outer circumferential groove 15B (upper portion) when the plunger 37 is continuously moved upward from the lowest position by the suction force of the electromagnetic actuator 30 and the main valve body 10 is moved upward together with the plunger 37.

[0048] The communication hole 15A and the outer peripheral groove 15B provided in the main valve element 10, and the inner peripheral groove 19A provided in the valve body 20, together with the through relief hole 16A, constitute a part of the small opening valve relief passage 15, and when the main valve element 10 moves up and down relative to the valve body 20, the outer peripheral portion (outer opening) of the communication hole 15A (and the outer peripheral groove 15B) slides against the inner peripheral surface (guide hole 19) of the seat member 20B of the valve body 20 to open and close the small opening valve relief passage 15 (communication hole 15A). In other words, the outer peripheral portion (outer opening) of the communication hole 15A (and the outer peripheral groove 15B) and the inner peripheral surface (guide hole 19) of the seat member 20B of the valve body 20 constitute the auxiliary sub-valve portion 13 in the small opening valve relief passage 15.

[0049] In this embodiment, as described above, the Pc inlet / outlet chamber 26, the valve chamber 21, the through relief hole 16A provided in the main valve body 10, the communicating hole 15A, the outer peripheral groove 15B, the inner peripheral groove 19A provided in the valve body 20, the Ps inlet / outlet chamber 28, etc. constitute a small opening intra-valve relief passage 15 for releasing the pressure Pc in the crank chamber to the suction chamber of the compressor via the Ps inlet / outlet 27, and as the main valve body 10 moves up and down relative to the valve body 20, the outer peripheral portion (outer opening) of the communicating hole 15A (and the outer peripheral groove 15B) slides against the inner peripheral surface (guide hole 19) of the seat member 20B of the valve body 20, thereby opening and closing the small opening intra-valve relief passage 15.

[0050] Needless to say, the method of formation, shape, and arrangement of the large opening valve relief passage 16 (through relief hole 16A) and the small opening valve relief passage 15, as well as the method of opening and closing the large opening valve relief passage 16 and the small opening valve relief passage 15, are not limited to the examples shown in the figures.

[0051] In the above embodiment, the valve body 20 is made up of two parts, the main body member 20A and the seat member 20B. However, it goes without saying that the valve body 20 may be made up of a single part.

[0052] Here, in the control valve 1 of this embodiment, as shown in FIG. 1, when the plunger 37, the main valve body 10, and the sub-valve body 17 are in their lowest positions (the lowest end face of the plunger 37 abuts against the stopper portion 24A, the main valve portion 11 is fully open, the sub-valve portion 12 is fully closed, and the auxiliary sub-valve body 13 is fully closed), the vertical distance between the main valve body portion 10a of the main valve body 10 and the valve port (valve seat portion) 22 is set to a first lift amount La, the distance between the inner flange-shaped engaging portion 37k of the plunger 37 and the flange-shaped engaging portion 10k of the main valve body 10 is set to a predetermined amount Ly, and the maximum lift amount (second lift amount) Lb of the plunger 37 (the lift amount from the lowest position to the highest position of the plunger 37) is the first lift amount La + a predetermined amount Ly. To account for component tolerances and seat wear, the length Lb between the plunger 37 and the aspirator 34 may be equal to La+Ly+ε, where ε is the small distance. Also, at this time, the communication hole 15A and the outer peripheral groove 15B provided in the (intermediate fitting portion 10c of) the main valve body 10 are positioned directly below the inner peripheral groove 19A provided in the (seat member 20B of) the valve body 20.

[0053] Next, the operation of the control valve 1 having the above configuration will be briefly described.

[0054] Fig. 6 is a diagram for explaining the operation of an embodiment of the control valve for a variable displacement compressor according to the present disclosure, showing changes in the flow state of the refrigerant in the Pd-Pc flow path and the Pc-Ps flow path. Fig. 7 is a diagram showing the relationship between the current value (plunger lift amount) of the electromagnetic actuator and the flow path area of ​​the Pd-Pc flow path and the Pc-Ps flow path during the operation of an embodiment of the control valve for a variable displacement compressor according to the present disclosure.

[0055] In the control valve 1 of this example, when the electromagnetic actuator 30 (solenoid portion 30A) is turned off (when the valve port 22 is fully open), the small opening valve relief passage 15 is blocked within the main valve body 10 (in other words, the small opening valve relief passage 15 is closed), and when the electromagnetic actuator 30 (solenoid portion 30A) is turned on (when the valve opening of the valve port 22 is being controlled or when the valve is closed), the communication hole 15A and the outer peripheral groove 15B provided in the main valve body 10 (intermediate insertion portion 10c) communicate with the inner peripheral groove 19A provided in the valve body 20 (seat member 20B), and the pressure Pc in the crank chamber is released to the suction chamber through the small opening valve relief passage 15 (in other words, the small opening valve relief passage 15 is opened). When the current is turned off, the bottom end of the push rod 46 may be separated from the fitting surface of the sub-valve body 17. Therefore, the small opening valve relief passage 15 may be closed by the planar contact between the plunger 37 and the stopper portion 24A.

[0056] In detail, during normal control (Pd→Pc control), the lift amount of the plunger 37 (and the sub-valve body 17) is set to the first lift amount La at most, and when the compressor is started (Pc→Ps control), the lift amount of the plunger 37 (and the sub-valve body 17) is set to the second lift amount Lb.

[0057] That is, during normal control (Pd→Pc control), when the solenoid section 30A consisting of the coil 32, stator 33, attractor 34, etc. is energized from off (see Figure 1), the plunger 37 and sub-valve body 17 are both attracted (upward) to the attractor 34, and following the movement of the plunger 37 and sub-valve body 17, the main valve body 10 is moved upward (in the valve closing direction) by the force of the valve closing spring 50. On the other hand, the suction pressure Ps introduced from the compressor to the Ps inlet / outlet 27 is introduced from the Ps inlet / outlet chamber 28 through the gap 36 between the outer periphery of the plunger 37 and the guide pipe 35 and into the pressure-sensing chamber 45, and the bellows device 40 (inside is a vacuum pressure) expands or contracts (contracts when the suction pressure Ps is high and expands when the suction pressure Ps is low) in accordance with the pressure in the pressure-sensing chamber 45 (suction pressure Ps). This displacement is transmitted to the main valve body 10 via the push rod 46, sub-valve body 17 and plunger 37, thereby adjusting the valve opening (the distance between the valve port 22 and the main valve body portion 10a), and the pressure Pc in the crank chamber is adjusted in accordance with the valve opening (see Figures 1, 2, 6 and 7).

[0058] In this case, the main valve body 10 is always biased upward by the biasing force of the valve-closing spring 50, and the sub-valve body 17 is always biased downward by the biasing force of the valve-opening spring 47, so that the sub-valve body portion 17a is pressed against the sub-valve seat portion 23 (the sub-valve portion 12 is closed), and the large opening valve relief passage 16 is blocked within the main valve body 10. Therefore, the pressure Pc in the crank chamber is not released to the suction chamber through the large opening valve relief passage 16 (see Figures 1, 2, and 6).

[0059] Furthermore, when the electromagnetic actuator 30 (solenoid section 30A) is powered off (see Figure 1), as described above, the communication hole 15A and outer peripheral groove 15B provided in the main valve body 10 (intermediate insertion section 10c) are arranged lower than the inner peripheral groove 19A provided in the valve body 20 (seat member 20B), and the outer peripheral portion (outer opening) of the communication hole 15A (and outer peripheral groove 15B) is blocked by the inner peripheral surface (guide hole 19) of the seat member 20B of the valve body 20 (auxiliary sub-valve section 13 is closed), and the relief passage 15 within the small opening valve is also blocked within the main valve body 10. On the other hand, when the electromagnetic actuator 30 (solenoid portion 30A) is energized and excited, the main valve body 10 moves upward (in the valve closing direction) due to the movement of the plunger 37, and the main valve body 10 moves upward (lifts) relative to the valve body 20, and the communication hole 15A and outer peripheral groove 15B provided in the main valve body 10 (intermediate insertion portion 10c) are made to communicate with the inner peripheral groove 19A provided in the valve body 20 (seat member 20B), thereby opening the small opening valve relief passage 15 and releasing the pressure Pc in the crank chamber to the suction chamber through the small opening valve relief passage 15. The opening (passage area, i.e., Pc-Ps flow path area) of this small opening valve relief passage 15 gradually increases as the upward lift amount (valve closing direction) of the plunger 37 and the main valve body 10 increases (see Figures 1, 2, 6, and 7).

[0060] In other words, in the control valve 1 of this embodiment, during normal control (Pd→Pc control), the large opening relief passage 16 in the valve remains closed by the sub-valve body 17 (in other words, before the large opening relief passage 16 in the valve is opened by the sub-valve body 17), and the pressure Pc in the crank chamber is released to the suction chamber only through the small opening relief passage 15 in the valve, which has a relatively small opening and whose opening (Pc-Ps flow path area) is variable depending on the upward lift amount (valve closing direction) of the plunger 37 and the main valve body 10.

[0061] In contrast, when the compressor is started, the solenoid section 30A is energized and excited, so that the plunger 37 and the sub-valve element 17 are attracted (upward) by the suction element 34, and the main valve element 10 is caused to move upward following the upward movement of the plunger 37 and the sub-valve element 17. After the valve opening 22 is closed by the main valve element section 10a of the main valve element 10, the plunger 37 and the sub-valve element 17 are caused to move upward further, whereby the sub-valve element 17 opens the large opening valve relief passage 16, and the pressure Pc in the crank chamber is released through the large opening valve relief passage 16 (together with the above-mentioned small opening valve relief passage 15) to the suction chamber (see Figures 4, 6 and 7).

[0062] In detail, until the lift amount (upward movement amount) of the plunger 37 (and the sub-valve body 17) reaches the first lift amount La, the main valve body 10 moves in the valve closing direction to follow the upward movement of the plunger 37 and the sub-valve body 17 due to the force of the valve closing spring 50, and when the upward movement amount reaches the first lift amount La, the valve port 22 is closed by the main valve body portion 10a of the main valve body 10 (the state shown in Figure 3), and the plunger 37 and the sub-valve body 17 are further moved upward by the predetermined amount Ly from the closed state of this main valve portion 11 (the state shown in Figure 4). In other words, after the upward movement of the plunger 37 and the sub-valve body 17 reaches the first lift amount La, the sub-valve body 17 is pulled toward the suction element 34 together with the plunger 37 by a predetermined amount Ly until the inner flange-shaped engaging portion 37k of the plunger 37 is engaged with the flange-shaped engaging portion 10k of the main valve body 10 (first lift amount La+predetermined amount Ly=second lift amount Lb). In this case, since the main valve body 10 remains immobile in the closed valve state, the sub-valve body portion 17a of the sub-valve body 17 is lifted by the predetermined amount Ly from the sub-valve seat portion 23, thereby opening the large opening degree intra-valve relief passage 16. When the inner flange-shaped engaging portion 37k of the plunger 37 is engaged with the flange-shaped engaging portion 10k of the main valve body 10, the plunger 37 and the sub-valve body 17 cannot be pulled up any further even if the solenoid portion 30A generates a suction force.

[0063] In other words, in the control valve 1 of this embodiment, when the compressor is started, the pressure Pc in the crank chamber is released to the suction chamber through both the small opening valve relief passage 15, which has a relatively small opening, and the large opening valve relief passage 16, which has a relatively large opening.

[0064] In this manner, in the control valve 1 of this embodiment, when the compressor is started, the pressure Pc in the crank chamber is released to the suction chamber through the large opening valve relief passage 16, so that the time required for the discharge capacity to increase when the compressor is started can be significantly shortened. Also, during normal control (Pd→Pc control), the large opening valve relief passage 16 is closed by the sub-valve body 17, and the pressure Pc in the crank chamber is released to the suction chamber only through the small opening valve relief passage 15, so that the operating efficiency of the compressor does not decrease.

[0065] Furthermore, in the control valve 1 of this embodiment, the large opening relief passage 16 in the valve with a relatively large opening used when the compressor is started, and the small opening relief passage 15 in the valve with a relatively small opening used both when the compressor is started and during normal control (Pd→Pc control) can be formed as separate passages and opened and closed separately. Therefore, compared to the conventional type in which these are basically formed as a common (single) passage, the opening of the large opening and small opening relief passages in the valve can be easily set, the internal circulation of the refrigerant in the compressor 100 can be effectively reduced, and the operating efficiency of the compressor 100 can be effectively improved.

[0066] In addition, the opening (Pc-Ps flow path area) of the small opening valve relief passage 15 is variable according to the amount of movement (lift amount) of the main valve body 10 due to the movement of the plunger 37, and is gradually increased as the amount of movement (lift amount) of the main valve body 10 increases, so that the operating efficiency of the compressor 100 during normal control (Pd→Pc control) can be more effectively improved. [Explanation of symbols]

[0067] 1. Control valve for variable displacement compressor 10 Main valve body 10a Main valve body part 10b Lower small diameter section 10c Intermediate insertion part 10d Upper small diameter section 10k collar-shaped locking part 11 Main valve section 12 Sub-valve section 13 Auxiliary sub-valve section 15 Relief passage in small opening valve 15A communication hole 15B Outer groove 16 Relief passage in large opening valve 16A Through hole 17 Sub valve body 17a Sub-valve body 18 Storage Cave 19 Guide hole 19A Inner Groove 20 Valve body 20A Main body material 20B Sheet member 20C recessed hole 21 Valve chamber 22 Valve Orifice 23 Sub-valve seat part 24 Insertion part 24A Stopper part 25 Pd inlet 26 PC entrance / exit (entrance / exit) 27 Ps inlet / outlet 28 Ps room entry / exit 30 Electromagnetic Actuator 30A solenoid part 32 Coil 33 Stator 34 Attractor 35 Guide pipe 37 Plunger 37s Slit 37sa 1st circular contour section 37sb Oval contour section 40 Bellows device (pressure-sensitive component) 45 Pressure Sensing Room 46 Push rod 47 Plunger spring 50 Valve closing spring

Claims

1. a valve body having a valve chamber provided with a valve port and a suction pressure inlet / outlet communicating with a suction chamber of a compressor, a discharge pressure inlet / outlet communicating with a discharge chamber of the compressor provided upstream of the valve port, and a crank pressure inlet / outlet communicating with a crank chamber of the compressor provided downstream of the valve port; a main valve body for opening and closing the valve port; an electromagnetic actuator having a plunger for moving the main valve body in a valve opening / closing direction; a pressure sensing chamber into which suction pressure from the compressor is introduced via the suction pressure inlet / outlet; a pressure-sensitive responsive member that biases the main valve body in a valve opening / closing direction in response to the pressure in the pressure-sensitive chamber; a relief passage in the large opening valve for releasing the crank pressure in the crank chamber to the suction chamber of the compressor through the suction pressure inlet / outlet; a sub-valve body that opens and closes a relief passage in the large opening valve by movement of the plunger; a relief passage in a small opening valve, which releases the crank pressure in the crank chamber to the suction chamber of the compressor through the suction pressure inlet / outlet and has an opening smaller than that of the relief passage in the large opening valve, a control valve for a variable displacement compressor, characterized in that the small opening valve relief passage is opened and closed in accordance with the movement of the main valve body caused by the movement of the plunger, and is opened before the large opening valve relief passage is opened by the sub-valve body.

2. 2. The control valve for a variable displacement compressor according to claim 1, wherein the opening of the relief passage in the small opening valve is variable in accordance with the amount of movement of the main valve body caused by the movement of the plunger.

3. 2. A control valve for a variable displacement compressor according to claim 1, wherein the relief passage in the small opening valve is gradually narrowed as the main valve body gradually opens.

4. The main valve element is slidably inserted into the valve body, The large opening valve relief passage is configured to include a through relief hole that passes vertically through the main valve body, 2. The control valve for a variable displacement compressor according to claim 1, wherein the small opening valve internal relief passage includes a part of the through relief hole and a communication hole extending from the through relief hole to a sliding surface of the main valve element that contacts the valve body.

5. 5. The control valve for a variable displacement compressor according to claim 4, wherein the small opening valve internal relief passage includes an inner circumferential groove provided on an upper side of a sliding surface of the valve body with the main valve element.

6. 2. The control valve for a variable displacement compressor according to claim 1, wherein the small opening valve relief passage is opened before the valve port is closed by the main valve body.

7. 2. The control valve for a variable displacement compressor according to claim 1, wherein when the plunger is continuously moved upward from the lowermost position by the attractive force of the electromagnetic actuator, the main valve body is moved upward together with the plunger while the sub-valve body keeps the large opening valve relief passage closed, thereby opening the small opening valve relief passage, and the opening of the small opening valve relief passage is gradually increased as the main valve body moves upward due to the movement of the plunger which gradually reduces the opening of the main valve body, and thereafter, when the plunger is further moved upward after the main valve body closes the valve port, the sub-valve body is moved upward together with the plunger while the main valve body keeps the valve port closed, thereby opening the large opening valve relief passage.

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