JP2018003886A - Variable capacity type compressor control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable capacity type compressor control valve that prevents internal oil of a crank chamber from being discharged more than necessary while securing a flow rate necessary for start up property, and can improve durability of a compressor.SOLUTION: In a variable capacity type compressor control valve, an auxiliary valve element 17 for opening and closing an in-valve relief passage 16 provided in a main valve element 15 has a curved surface part (auxiliary valve element part) 17a for changing a flow rate of fluid flowing through the in-valve relief passage 16 in accordance with a lift amount and a control angle of the curved surface part 17a is increased in a step-by-step manner as approaching a tip (lower end).SELECTED DRAWING: Figure 1

Description

  The present invention relates to a control valve for a variable displacement compressor used in a car air conditioner or the like.

  2. Description of the Related Art Conventionally, a swash plate type variable displacement compressor as schematically shown in FIG. 11 has been used as a compressor for a car air conditioner. The swash plate type variable displacement compressor 100 includes a rotary shaft 101 that is driven to rotate by an in-vehicle engine, a swash plate 102 attached to the rotary shaft 101, a crank chamber 104 in which the swash plate 102 is disposed, and the swash plate. The piston 105 reciprocated by the piston 102, the discharge chamber 106 for discharging the refrigerant compressed by the piston 105, the suction chamber 107 for sucking the refrigerant, and the pressure Pc of the crank chamber 104 for releasing the pressure Pc to the suction chamber 107 An in-flight escape passage (fixed orifice) 108 and the like are provided.

  On the other hand, the control valve 1 ′ used in the variable displacement compressor is supplied with the discharge pressure Pd from the discharge chamber 106 of the compressor 100 and adjusts the discharge pressure Pd according to the suction pressure Ps of the compressor 100. By controlling the pressure, the pressure Pc of the crank chamber 104 is controlled. As a basic configuration, the valve chamber has a valve chamber provided with a valve port and a Ps introduction port communicating with the suction chamber 107 of the compressor 100. A valve main body provided with a Pd introduction port communicating with the discharge chamber 106 of the compressor 100 upstream from the port and with a Pc outlet opening communicating with the crank chamber 104 of the compressor 100 downstream of the valve port. An electromagnetic actuator having a valve body (valve rod) for opening and closing the valve port, a plunger for moving the valve body in the valve port opening / closing direction (vertical direction), and the compressor 100 A pressure sensing chamber into which the suction pressure Ps is introduced through the Ps introduction port, and a pressure sensitive responsive member that urges the valve body in the valve opening / closing direction in accordance with the pressure in the pressure sensing chamber. The valve body and the valve port constitute a valve portion denoted by reference numeral 11 ′ in FIG. 11 (see, for example, Patent Document 1 below).

  In the control valve 1 ′ having such a configuration, when the solenoid portion including the coil, the stator, and the attractor of the electromagnetic actuator is energized, the plunger is attracted to the attractor, and the valve body is closed accordingly. The urging force of the spring is moved in the valve closing direction so as to follow the plunger. On the other hand, the suction pressure Ps introduced from the compressor 100 through the Ps introduction port enters the pressure sensitive chamber through a gap formed between the plunger and the guide pipe disposed on the outer periphery thereof. The pressure-responsive member (for example, a bellows device) is expanded and contracted according to the pressure in the pressure-sensitive chamber (suction pressure Ps) (contracts when the suction pressure Ps is high and expands when the pressure is low), and the displacement (biasing force) is This is transmitted to the valve body, whereby the valve body portion of the valve body moves up and down with respect to the valve port, and the valve opening degree of the valve portion 11 ′ is adjusted. That is, the valve opening degree is determined by the attraction force of the plunger by the solenoid part, the urging force (extension / contraction force) due to the expansion / contraction displacement of the pressure-sensitive response member, and the urging force by the plunger spring (valve opening spring) and the valve closing spring. The pressure Pc in the crank chamber 104 (hereinafter sometimes referred to as the crank chamber pressure Pc or simply the pressure Pc) is controlled in accordance with the valve opening.

  Further, for the variable capacity compressor, for example, the time required for the discharge capacity to be increased at the time of starting the compressor is shortened, and the reduction in the operation efficiency of the compressor at the time of normal control is suppressed or reduced. For this purpose, an improved swash plate type variable displacement compressor as shown in FIG. 12 has been proposed.

  In this improved swash plate type variable displacement compressor 200, a valve body (valve rod) in a control valve used therefor is composed of a main valve body and a sub-valve body, and an in-valve escape passage 16 'is formed in the main valve body. The control valve 2 ′ basically has a valve chamber provided with a valve port and a Ps inlet / outlet communicating with the suction chamber 107 of the compressor 200, upstream of the valve port. A valve main body provided with a Pd introduction port communicating with the discharge chamber 106 of the compressor 200 and provided with a Pc inlet / outlet communicating with the crank chamber 104 of the compressor 200 on the downstream side of the valve port; A suction valve Ps is introduced from the compressor 200 through the Ps inlet / outlet. The main valve body for opening and closing the valve, the electromagnetic actuator having a plunger for moving the main valve body in the valve opening / closing direction, and the compressor 200 Depending on the pressure chamber and the pressure in the pressure chamber A pressure sensitive member that biases the main valve body in the valve opening / closing direction, and a valve for releasing the pressure Pc of the crank chamber 104 to the suction chamber 107 of the compressor 200 through the Ps inlet / outlet. An inward release passage 16 ′ is provided in the main valve body, and a sub-valve body for opening and closing the in-valve escape passage 16 ′ is provided, and the plunger is moved upward from the lowest position by the suction force of the electromagnetic actuator. When continuously moved, the sub-valve moves together with the plunger while moving the valve escape passage 16 ′ in the upward direction, and the main valve moves upward so as to follow the sub-valve. When the plunger is further moved upward after the valve port is closed by the main valve body, the sub-valve body opens the in-valve escape passage 16 '. Thus, the main valve body and the valve port constitute a main valve portion denoted by reference numeral 11 'in FIG. 12, and the sub-valve portion denoted by reference numeral 12' is constituted by the sub-valve body and the valve relief passage. (For example, refer to Patent Document 2 below).

  In the control valve 2 ′ having such a configuration, during normal control (Pd → Pc control), when a solenoid portion including a coil, a stator, and an attractor of an electromagnetic actuator is energized, the plunger is attracted to the attractor. Accordingly, the sub-valve element moves upward in unison with the plunger, and the main valve element is moved in the valve-closing direction by the urging force of the valve-closing spring following this movement. On the other hand, the suction pressure Ps introduced from the compressor 200 through the Ps inlet / outlet is introduced from the inlet / outlet chamber into the pressure sensitive chamber through the side hole of the plunger, and the pressure sensitive reaction member (for example, the bellows device) is pressure sensitive. Expansion and contraction displacement (contraction when suction pressure Ps is high and expansion when suction pressure Ps is low) according to the pressure in the chamber (suction pressure Ps), and the displacement (biasing force) is transmitted to the main valve body. The main valve body portion of the main valve body is raised and lowered to adjust the valve opening degree of the main valve portion 11 ′. That is, the valve opening includes the plunger suction force by the solenoid part, the biasing force (extension force) due to the expansion / contraction displacement of the pressure sensitive member, the biasing force due to the plunger spring (valve opening spring) and the valve closing spring, and the main valve It is determined by the force in the valve opening direction and the force in the valve closing direction acting on the body, and the pressure Pc in the crank chamber 104 is controlled according to the valve opening degree. In this case, the main valve body is always urged upward by the urging force of the valve closing spring, and the sub valve body is always urged downward by the urging force of the valve opening spring. Is closed, the in-valve escape passage 16 ′ is blocked in the main valve body, and the crank chamber pressure Pc is not released to the suction chamber 107 through the in-valve escape passage 16 ′.

  On the other hand, when the compressor is started, the solenoid is energized and the plunger is attracted to the suction element. The sub-valve moves together with the plunger, and the main valve follows the upward movement. After the body is moved in the valve closing direction by the urging force of the valve closing spring, and the valve port is closed by the main valve body portion of the main valve body, the plunger is further moved upward, whereby the sub valve body is moved. The in-valve escape passage 16 ′ is opened, and the crank chamber pressure Pc is released to the suction chamber 107 through two passages of the in-flight escape passage 108 and the in-valve escape passage 16 ′ (for details, see Patent Document 2 below). Etc.)

JP 2010-185285 A JP 2013-130126 A

  However, in the variable displacement compressor control valve 2 ′ as described above, the sub-valve part of the sub-valve element that opens and closes the in-valve escape passage is a flat type (flat shape). Therefore, the relationship between the valve opening (lift amount) and the flow rate in the sub valve section, that is, the flow rate characteristic becomes a linear characteristic (a characteristic in which the rate of change of the flow rate with respect to the change in the valve opening degree is constant), and startability is unnecessary. Even in this case, the flow rate (passage flow rate) increases, which may lead to oil outflow in the crank chamber of the compressor.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to prevent excessive discharge of oil in the crank chamber while ensuring a flow rate when startability is required, and It is an object of the present invention to provide a variable displacement compressor control valve capable of improving durability.

  In order to achieve the above object, a control valve for a variable displacement compressor according to the present invention basically has a valve chamber provided with a valve port and a Ps inlet / outlet communicating with a suction chamber of the compressor, A valve body provided with a Pd introduction port communicating with the discharge chamber of the compressor upstream from the valve port, and provided with a Pc inlet / outlet communicating with the crank chamber of the compressor downstream from 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 the valve port opening and closing direction, and a suction pressure Ps from the compressor via the Ps inlet / outlet A pressure-sensitive chamber to be introduced; and a pressure-sensitive response member that urges the main valve body in the valve opening / closing direction in accordance with the pressure in the pressure-sensitive chamber, and the pressure Pc of the crank chamber is set to the Ps inlet / outlet An in-valve escape passage for escaping to the compressor suction chamber via the A sub-valve element is provided in the valve body and opens and closes the relief passage in the valve, and the sub-valve element has a curved surface portion that changes the flow rate of the fluid flowing in the relief passage according to the lift amount. The curvature or control angle of the curved surface portion is increased continuously or stepwise as it approaches the tip.

  The curved surface portion is preferably a spherical surface portion, an elliptical surface portion, a plurality of inverted frustoconical tapered surface portions whose control angles are increased stepwise as approaching the tip, or the spherical surface portion or the elliptical surface portion. It is comprised by the combination with the taper surface part of one step or a plurality of steps.

  In a preferred aspect, the curved surface portion has a symmetrical shape with respect to the central axis of the subvalve element.

  In another preferred embodiment, the curvature or control angle on the tip side from the portion of the curved surface portion seated on the main valve body is increased continuously or stepwise as the tip is approached.

  In another preferred aspect, a part of the curved surface portion is positioned in the in-valve escape passage when the sub-valve is in the highest position with respect to the main valve.

  According to the present invention, the sub-valve element that opens and closes the in-valve escape passage provided in the main valve body has a curved surface portion that changes the flow rate of the fluid flowing through the in-valve escape passage according to the lift amount, and the curved surface thereof. Since the curvature or control angle of the part is increased continuously or stepwise as it approaches the tip, for example, a conventional control valve in which the sub-valve part of the sub-valve element that opens and closes the escape passage in the valve is flat As compared with, the flow rate of the fluid flowing through the valve escape passage can be increased according to the lift amount while suppressing the flow rate during low lift (when startability is not required). Therefore, it is possible to prevent unnecessary (unnecessary) discharge of oil in the crank chamber while ensuring a flow rate when startability is required (when the crank chamber pressure Pc and the suction pressure Ps are high), and the durability of the compressor Can be improved.

BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional view which shows the state (at the time of normal control) of the main valve of the 1st Embodiment of the control valve for variable displacement compressors which concerns on this invention: Open and subvalve: Closed. BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional view which shows the state (at the time of a compressor starting transition) of the main valve of the 1st Embodiment of the control valve for variable displacement type compressors which concerns on this invention: Closed and a subvalve. BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional view which shows the state (at the time of compressor starting) of the main valve of the 1st Embodiment of the control valve for variable displacement type compressors which concerns on this invention: Closed and a subvalve. It is a figure which shows the plunger used for the control valve for variable displacement compressors which concerns on this invention, (A) is a front view, (B) is a left view, (C) is a bottom view, (D) is (A) ) Is a cross-sectional view according to the line of XX arrow, (E) is a cross-sectional view according to the line of arrow Y-Y of (B). The figure which shows the flow volume characteristic of the subvalve part of 1st Embodiment of the control valve for variable displacement compressors which concerns on this invention. The longitudinal cross-sectional view which shows the state (at the time of normal control) of the main valve of the 2nd Embodiment of the control valve for variable displacement compressors which concerns on this invention: Open and a subvalve. The longitudinal cross-sectional view which shows the state (at the time of a compressor starting transition) of the main valve of the 2nd Embodiment of the control valve for variable displacement type compressors which concerns on this invention: Closed and a subvalve. The longitudinal cross-sectional view which shows the main valve of the 2nd Embodiment of the control valve for variable displacement type compressors which concerns on this invention: Closed and a subvalve: An open state (at the time of compressor starting). (A) is a principal part expanded longitudinal cross-sectional view which shows the other example of a subvalve body, (B) is a figure which shows the flow volume characteristic of the subvalve part containing the subvalve body shown by (A). (A) is a principal part expanded longitudinal cross-sectional view which shows the further another example of a subvalve body, (B) is a figure which shows the flow volume characteristic of the subvalve part containing the subvalve body shown by (A). The figure which shows the refrigerant | coolant pressure distribution | circulation condition between the compressor and control valve in a 1st prior art example. It is a figure which shows the refrigerant | coolant pressure distribution | circulation condition between the compressor and control valve in a 2nd prior art example, (A) is at the time of normal control, (B) is a figure which shows the time of compressor starting.

  Embodiments of the present invention will be described below with reference to the drawings.

<First Embodiment>
1 to 3 are longitudinal sectional views showing a first embodiment of a control valve for a variable displacement compressor according to the present invention, respectively. FIG. 1 shows a state in which a main valve is open and a sub valve is closed (normal control). 2), FIG. 2 shows the main valve: closed, sub valve: closed (when the compressor starts up), and FIG. 3 shows the main valve: closed, sub valve: open (when the compressor is started).

  In the present specification, descriptions representing positions and directions such as up and down, left and right, and front and rear are given for convenience in accordance with the drawings in order to avoid complicated explanation, and are actually incorporated in the compressor. It does not necessarily indicate the position and direction at.

  In each drawing, the gap formed between the members, the separation distance between the members, etc. are larger than the dimensions of each constituent member for easy understanding of the invention and for convenience of drawing. Or it may be drawn small.

  The control valve 1 of the illustrated embodiment includes a valve body 20 provided with a valve port 22, a valve body 10 having a main valve body 15 for opening and closing the valve port 22, and the valve body 10 (main valve body 15). Is provided with an electromagnetic actuator 30 for moving the valve opening and closing direction (vertical direction) and a bellows device 40 as a pressure-sensitive response member.

  The electromagnetic actuator 30 is disposed on the inner peripheral side of the bobbin 38, a coil 32 for energization excitation encased in the bobbin 38, a connector head 31 mounted on the upper side of the bobbin 38 via a mounting plate 39, and the coil 32. The stator 33 and the suction element 34, the guide pipe 35 whose upper end is joined to the outer periphery (step part) of the lower end of the stator 33 and the suction element 34 by welding, and the inner periphery of the guide pipe 35 below the suction element 34. A plunger 37 having a concave cross section disposed slidably in the vertical direction, a cylindrical housing 60 externally inserted into the coil 32, and a lower end portion of the housing 60 and the guide pipe 35. And a holder 29 for fixing them to the upper part of the valve body 20. In this example, a suction element 34 having a concave cross section is integrally formed on the lower inner periphery of a cylindrical stator 33. Here, the part which consists of the coil 32, the stator 33, the attractor 34, etc. except the plunger 37 among the electromagnetic actuators 30 is called solenoid part 30A.

  Further, a short cylindrical stator 65 is fixed to the upper portion of the stator 33 by press fitting or the like, and between the stator 65 and the suction element 34 on the inner peripheral side of the stator 33, the compressor 100. A pressure-sensitive chamber 45 into which the suction pressure Ps is introduced is formed. In the pressure-sensitive chamber 45, a bellows 41, an inverted convex upper stopper 42, an inverted concave lower stopper 43, which serve as pressure sensitive response members, A bellows device 40 including a compression coil spring 44 is disposed. Further, an upper small-diameter portion (end portion on the opposite side of the sub-valve body portion 17a) 17d of the sub-valve body 17 to be described later is fitted and supported in the recess of the lower stopper 43. A compression coil spring 46 that urges the bellows device 40 in a contracting direction is contracted between the child 34.

  The plunger 37 includes a cylindrical upper half portion 37A and a columnar lower half portion 37B. The sub-valve element 17 extends downward through the suction element 34 at the center of the columnar lower half portion 37B. An insertion hole 37b through which the body portion 17b and the upper small-diameter portion 15f (detailed later) of the main valve body 15 are inserted is formed, and the outer peripheral portion of the insertion hole 37b on the upper surface of the cylindrical lower half portion 37B is a sub valve. A latching portion 37a for latching the intermediate large-diameter locking portion 17c of the body 17 is provided.

  A cylindrical compression between the suction element 34 and the intermediate large-diameter locking portion 17c (plunger 37) of the sub-valve body 17 biases the sub-valve body 17 and the plunger 37 downward (in the valve opening direction). A plunger spring (valve opening spring) 47 made of a coil spring is mounted in a compressed manner, and the plunger spring 47 presses the sub-valve element 17 (the intermediate large-diameter locking portion 17 c) against the plunger 37 together with the plunger 37. It is designed to move up and down.

  Further, as is well understood with reference to FIG. 4, a flat surface is formed so that the lower part of the cylindrical lower half part 37B of the plunger 37 (the part above the lower end part by a predetermined distance) overlaps the insertion hole 37b. A substantially semicircular cut 37t is formed (in the lateral direction) when viewed, and a cylindrical shape is formed below the cut 37t (that is, a portion between the cut 37t and the lower end of the cylindrical lower half 37B). A slit 37 s is formed that extends linearly from the lower end edge of the lower half portion 37 </ b> B to the insertion hole 37 b and has the same width as the diameter of the insertion hole 37 b. The height (in the vertical direction) of the notch 37t is slightly larger than the height of the hook-shaped locking portion 15k of the main valve body 15, and the height (in the vertical direction) of the slit 37s is the main valve body 15. The main valve body 15 can move up and down with respect to the plunger 37 (details will be described later). Further, the width (in the lateral direction) of the slit 37s is slightly larger than the outer diameter of the upper small diameter portion 15f of the main valve body 15 in consideration of assemblability and the like, and the hook-like engagement of the main valve body 15 is performed. It is made smaller than the outer diameter of the part 15k.

  The valve body 10 includes a main valve body 15 and a sub-valve body 17 that are arranged in the vertical direction (along the axis O direction).

  The main valve body 15 disposed on the lower side includes, in order from the bottom, a lower insertion portion 15b, a lower small diameter portion 15c, a main valve body portion 15a, an intermediate small diameter portion 15d, an upper insertion portion 15e, an upper small diameter portion 15f, And a stepped through hole 16A that constitutes a part of the in-valve escape passage 16 so as to penetrate in the longitudinal direction at the center of the inside. The upper end portion of the relief hole 16 </ b> A serves as a sub valve seat portion 23 to which the lower end portion (sub valve body portion) 17 a of the sub valve body 17 is separated. The intermediate small diameter portion 15d of the main valve body 15 is provided with a plurality of lateral holes 16s.

  The upper small-diameter portion 15f of the main valve body 15 is loosely fitted into the insertion hole 37b (the portion below the notch 37t), and the hook-shaped locking portion 15k of the main valve body 15 has a larger diameter than the insertion hole 37b. When the plunger 37 is moved upward with respect to the main valve body 15, the hook-shaped locking portion 15k is hooked by the inner hook-shaped hooking portion 37k formed of the outer peripheral portion of the insertion hole 37b. It is designed to be locked out.

  In addition, the sub-valve element 17 disposed on the upper side of the main valve element 15 opens and closes the in-valve escape passage 16 by being in contact with the sub-valve seat portion 23 which is the upper edge of the through-release hole 16A in order from the bottom. And the upper small-diameter portion 17d that is inserted into and supported by the recessed portion of the lower stopper 43. The sub-valve body portion 17a, the body portion 17b in which the intermediate large-diameter locking portion 17c is formed, and the truncated cone portion 17e. Here, the auxiliary valve seat part 23 is comprised by the auxiliary valve seat part 23 and the auxiliary valve body part 17a. In this example, a portion of the body portion 17b below the intermediate large-diameter locking portion 17c is inserted into the insertion hole 37b of the plunger 37 with a slight clearance, and the intermediate large-diameter locking portion 17c. The upper part and the lower part of the suction element 34 (the part disposed inside the cylindrical upper half part 37A) are slightly larger in diameter than the other parts.

  The auxiliary valve body portion 17a is a curved surface portion that changes the flow rate of the fluid flowing through the in-valve escape passage 16 in accordance with the lift amount from the auxiliary valve seat portion 23 of the through escape hole 16A. The body part 17a is the inverse of a plurality of stages (here, two stages) in which the control angle (the angle of intersection with the central axis O of the sub-valve body 17) increases stepwise as it approaches the tip (lower end). It has frustoconical tapered surface portions 17A and 17B (such a valve body may be referred to as a multistage valve). Specifically, in this example, the control angle θ2 of the lower tapered surface portion 17B made of a conical surface is set larger than the control angle θ1 of the upper tapered surface portion 17A made of a truncated cone surface, and the sub-valve body portion 17a is It is configured to be seated on the auxiliary valve seat portion 23 of the through relief hole 16A at a predetermined position of the upper taper surface portion 17A (that is, a control angle between the upper taper surface portion 17A and the lower taper surface portion 17B). The boundary portion in which the sub valve body portion 17a is seated on the sub valve seat portion 23 enters the through relief hole 16A). Thus, a characteristic that protrudes downward (in other words, a characteristic in which the rate of change of the flow rate with respect to the change in the valve opening changes before and after the inflection point) is obtained (see FIG. 5).

  The sub-valve part 17a has a symmetrical shape with respect to the central axis O of the sub-valve element 17, and when the sub-valve part 17a is seated on the sub-valve seat part 23 of the through relief hole 16A. The sub-valve body 17 is aligned with the main valve body 15 (when the sub-valve body 17 closes the in-valve escape passage 16).

  Further, the dimensional shape of each part around the sub-valve element 17 (for example, a gap between the body part 17b and the insertion hole 37b) is a position where the sub-valve element 17 is moved upward with respect to the main valve element 15. Even when the sub-valve body 17 approaches the main valve body 15 (that is, when the sub-valve body 17 closes the in-valve escape path 16) even in a state of being slightly inclined in the position (that is, the position where the in-valve escape path 16 is opened). ), The lower end portion of the sub-valve body portion (curved surface portion) 17a enters the through escape hole 16A, and the sub-valve body portion 17a is aligned with the main valve body 15 by the sub-valve body portion 17a. Is set. More specifically, when the sub-valve element 17 is at the most elevated position (position where the lift amount is maximum) with respect to the main valve element 15, a part of the sub-valve part (curved surface part) 17a (particularly, the tip part). ) Is set so that each part is dimensioned in the through escape hole 16A (see, in particular, FIG. 3).

  When assembling the valve body 10 (the main valve body 15 and the sub-valve body 17) and the plunger 37, for example, the hook-shaped locking portion 15k of the main valve body 15 that is assembled in advance to the valve body 20 (the guide hole 19 thereof). The main valve body 15 is moved laterally with respect to the plunger 37 so that the upper small diameter portion 15f is inserted into the notch 37t and the slit 37s of the plunger 37, respectively, and the upper portion is inserted into the insertion hole 37b provided at the center of the plunger 37. The sub-valve element 17 (the lower portion of the intermediate large-diameter locking portion 17c) may be inserted from above into the insertion hole 37b after the small-diameter portion 15f is inserted.

  On the other hand, the valve main body 20 has a two-part configuration of a main body member 20A provided with a concave hole 20C for fitting in the upper center and a support member 20B that is inserted and fixed into the concave hole 20C by press fitting or the like. Yes.

  The support member 20B is made of a relatively hard material such as stainless steel (SUS), for example, and is a convex for defining the lowest position of the plunger 37 on the upper side of the insertion portion 24 to be inserted into the concave hole 20C. 24A-shaped stopper part 24A is protrudingly provided. Further, a guide hole 19 (upper guide hole 19A) into which the upper fitting insertion portion 15e of the main valve body 15 is slidably fitted so as to penetrate in the vertical direction is formed in the central portion of the support member 20B. A lower end portion of the upper guide hole 19A is a valve port 22 (valve seat portion) that is opened and closed by the main valve body portion 15a of the main valve body 15. Here, the main valve part 11 is comprised by the main valve body part 15a and the valve port 22. FIG. As described above, since the support member 20B is made of a high-hardness material such as stainless steel, its specific gravity is also high.

  The main body member 20A is made of a material having a relatively low specific gravity (ie, a material having a relatively low hardness) compared to, for example, aluminum, brass, or stainless steel such as resin, and the support member 20B is inserted into the recessed hole 20C of the main body member 20A. In the state where the (insertion portion 24) is inserted, an inlet / outlet chamber 28 for the suction pressure Ps of the compressor 100 is formed on the outer periphery of the stopper portion 24A, and a plurality of inlet / outlet chambers 28 are provided on the outer peripheral side of the inlet / outlet chamber 28. Ps inlet / outlet 27 is formed. The suction pressure Ps introduced into the inlet / outlet chamber 28 from the Ps inlet / outlet 27 is formed between the slit 37s and the notch 37t formed at the bottom of the plunger 37, and between the body 17b of the sub-valve body 17 and the insertion hole 37b of the plunger 37. Are introduced into the pressure sensitive chamber 45 through a gap 36 formed between the outer periphery of the plunger 37 and the guide pipe 35.

  Further, in the center of the bottom of the recessed hole 20C of the main body member 20A, a hole having a diameter larger than that of the guide hole 19 and the main valve body 15a for accommodating the main valve body 15a of the main valve body 15 and the recessed hole 20C. An accommodation hole 18 having a diameter smaller than the diameter is provided continuously, and a guide hole 19 (lower guide hole 19B) into which a lower fitting insertion portion 15b of the main valve body 15 is slidably fitted is inserted in the lower center of the accommodation hole 18. ) Is formed. A valve closing spring comprising a conical compression coil spring between the bottom outer peripheral corner portion of the receiving hole 18 and a step portion (step portion) 15 g provided on the lower outer periphery of the main valve body portion 15 a of the main valve body 15. The main valve element 15 (the stepped portion between the upper fitting portion 15e and the upper small diameter portion 15f) is pressed against the plunger 37 by the urging force of the valve closing spring 50.

  The inside of the accommodation hole 18 (the lower part from the valve port 22 of the support member 20B) serves as a valve chamber 21, and a Pd introduction port 25 communicating with the discharge chamber 106 of the compressor 100 is provided in the valve chamber 21. A plurality of openings are opened. A ring-shaped filter member 25A is disposed on the outer periphery of the Pd introduction port 25 in the main body member 20A.

  Further, a lid-like member 48 functioning as a filter is fixed to the lower end portion of the main body member 20A by engagement, press-fitting or the like, and the compressor 100 is located above the lid-like member 48 and below the main valve body 15. The Pc entrance / exit chamber (entrance / exit) 26 communicates with the crank chamber 104. This Pc entrance / exit chamber (entrance / exit) 26 is formed between the through relief hole 16A → the lateral hole 16s → the gap between the lower portion of the upper guide hole 19A and the intermediate small diameter portion 15d → the valve port 22 and the main valve body portion 15a. The clearance is communicated with the Pd inlet 25 through the valve chamber 21.

  Further, in this embodiment, the pressure Pc of the crank chamber 104 is changed to the Ps inlet / outlet 27 by the through relief hole 16A formed in the main valve body 15, the notch 37t and the slit 37s provided in the plunger 37, the inlet / outlet chamber 28, and the like. An in-valve escape passage 16 is formed to escape to the suction chamber 107 of the compressor 100 through the auxiliary valve seat 17, which is the upper edge of the through-hole 16 </ b> A of the main valve body 15. When the valve body portion 17a is separated from and connected to the valve body, the in-valve escape passage 16 is opened and closed.

  Here, in the control valve 1 of the present embodiment, as shown in FIG. 1, the plunger 37, the main valve body 15, and the sub-valve body 17 are in the lowest lowered position (the lowermost end surface of the plunger 37 is the stopper portion. 24A, the main valve part 11 is fully open, and the sub-valve part 12 is fully closed). The vertical separation distance between the main valve body 15a of the main valve body 15 and the valve port 22 (valve seat part). Is the first lift amount Lv, the separation distance between the inner hook-shaped latching portion 37k of the plunger 37 and the hook-shaped locking portion 15k of the main valve body 15 is a predetermined amount La, and the maximum lift amount of the plunger 37 ( The second lift amount Lp (the lift amount from the lowest position of the plunger 37 to the highest position) is the first lift amount Lv + the predetermined amount La.

  Next, the operation of the control valve 1 configured as described above will be outlined.

  During normal control (Pd → Pc control), the lift amount of the plunger 37 is set to be slightly greater than the first lift amount Lv, and when the compressor is activated (Pc → Ps control), the lift amount of the plunger 37 is increased. The amount is the second lift amount Lp.

  That is, during normal control (Pd → Pc control), when the solenoid portion 30A including the coil 32, the stator 33, and the attractor 34 is energized, the plunger 37 is attracted to the attractor 34. Since the intermediate large-diameter locking portion 17c of the sub-valve body 17 is locked to the latching portion 37a of the plunger 37, the sub-valve body 17 moves upward together with the plunger 37 and follows this movement. Thus, the main valve body 15 is moved upward (in the valve closing direction) by the urging force of the valve closing spring 50. On the other hand, the suction pressure Ps introduced from the compressor 100 to the Ps inlet / outlet 27 is introduced from the inlet / outlet chamber 28 into the pressure sensing chamber 45 through the slit 37s and the notch 37t of the plunger 37, and the bellows device 40 (the inside is vacuum). (Pressure) expands and contracts according to the pressure in the pressure sensing chamber 45 (suction pressure Ps) (shrinks when the suction pressure Ps is high, expands when the pressure is low), and the displacement is via the plunger 37 and the sub-valve body 17. 15, thereby adjusting the valve opening (separation distance between the valve port 22 and the main valve body 15 a), and adjusting the pressure Pc of the crank chamber 104 according to the valve opening. Accordingly, the inclination angle of the swash plate 102 of the compressor 100 and the stroke of the piston 105 are adjusted, and the discharge capacity is increased or decreased.

  In this case, the main valve body 15 is always urged upward by the urging force of the valve closing spring 50, and the sub valve body 17 is always urged downward by the urging force of the valve opening spring 47. The valve body portion 17 a is pressed against the sub valve seat portion 23 (the sub valve portion 12 is closed), and the valve relief passage 16 is blocked in the main valve body 15. Therefore, the crank chamber pressure Pc is not released to the suction chamber 107 through the in-valve escape passage 16.

  On the other hand, at the time of starting the compressor, the solenoid portion 30A is energized and energized, and the plunger 37 is attracted to the attractor 34. The sub-valve body 17 moves upward together with the plunger 37 and follows this upward movement. After the main valve body 15 is moved upward and the valve port 22 is closed by the main valve body portion 15a of the main valve body 15, the plunger 37 is further moved upward, whereby the sub-valve body is moved. 17 opens the in-valve escape passage 16, and the pressure Pc in the crank chamber 104 is released to the suction chamber 107 through two passages of the in-flight escape passage 108 and the in-valve escape passage 16.

  Specifically, until the upward movement amount of the plunger 37 reaches the first lift amount Lv, the main valve body 15 follows the upward movement of the plunger 37 and the sub-valve body 17 by the biasing force of the valve closing spring 50. When the amount of upward movement reaches the first lift amount Lv, the main valve body portion 15a of the main valve body 15 closes the valve port 22 (the state shown in FIG. 2). The plunger 37 is further moved upward by the predetermined amount La from the closed state of the main valve portion 11 (state shown in FIG. 3). In other words, after the upward movement amount of the plunger 37 reaches the first lift amount Lv, the inner hook-shaped latching portion 37k of the plunger 37 is locked to the hook-shaped locking portion 15k of the main valve body 15. The sub-valve body 17 is lifted by the predetermined amount La (first lift amount Lv + predetermined amount La = second lift amount Lp). In this case, since the main valve body 15 remains stationary while being closed, the sub-valve body portion 17a of the sub-valve body 17 is lifted by a predetermined amount La from the sub-valve seat portion 23, and thereby the in-valve escape passage. 16 is opened. When the inner hook-shaped latching portion 37k of the plunger 37 is locked to the hook-shaped locking portion 15k of the main valve body 15, even if the solenoid portion 30A generates a suction force, the plunger 37 and the sub-valve body 17 It cannot be raised any more.

  Thus, in the control valve 1 of the present embodiment, the sub-valve body 17 that opens and closes the in-valve escape passage 16 provided in the main valve body 15 flows through the in-valve escape passage 16 according to the lift amount. It has a curved surface portion (subvalve body portion) 17a for changing the flow rate of fluid, and the control angle of the curved surface portion 17a, in particular, the main valve body 15 in the curved surface portion 17a (the subvalve seat portion 23 of the through relief hole 16A). Since the control angle on the tip side from the portion seated on the step is increased stepwise as it approaches the tip (lower end), for example, the sub-valve part of the sub-valve element that opens and closes the valve escape passage is made flat. Compared with the conventional control valve, the flow rate of the fluid flowing through the escape passage 16 in the valve can be increased according to the lift amount while suppressing the flow rate at the time of low lift (when startability is unnecessary) (see FIG. 5). Therefore, it is possible to prevent unnecessary (unnecessary) discharge of oil in the crank chamber while ensuring a flow rate when startability is required (when the crank chamber pressure Pc and the suction pressure Ps are high), and the durability of the compressor Can be improved.

Second Embodiment
FIGS. 6 to 8 are longitudinal sectional views showing a second embodiment of the control valve for a variable displacement compressor according to the present invention. FIG. 6 shows a state where the main valve is open and the sub valve is closed (normal control). 7), FIG. 7 shows the main valve: closed, the subvalve: closed (when the compressor starts up), and FIG. 8 shows the main valve: closed, the subvalve: open (when the compressor is started).

  The control valve 2 of the second embodiment is basically different from the control valve 1 of the first embodiment only in the configuration of the main valve body in the valve body and the valve body. Therefore, components having the same functions as those in the first embodiment are denoted by the same reference numerals and detailed description thereof is omitted, and only the differences described above will be described in detail below.

  In the control valve 2 of the present embodiment, the upper fitting portion 15e and the intermediate small diameter portion 15d of the main valve body 15 are formed longer than the control valve 1 of the first embodiment, and the lower side of the main valve body portion 15a. The lower small diameter portion 15c and the lower fitting insertion portion 15b are omitted.

  Moreover, the fitting insertion part 24 in the support member 20B of the valve body 20 is formed with a step, and the upper large diameter is provided below the upper large diameter part 24a (the outer shape corresponding to the fitting insertion part 24 of the first embodiment). A lower small-diameter portion 24b whose length in the vertical direction is longer than that of the portion 24a is provided at a lower end of the lower small-diameter portion 24b at a step portion (step terrace portion) between the recessed hole 20C and the accommodation hole 18 of the main body member 20A. A hook-shaped contact portion 24c to be contacted is provided so as to project outward.

  On the other hand, the concave hole 20C in the main body member 20A of the valve main body 20 is also formed with a step, and an upper large-diameter hole 20Ca into which the upper large-diameter portion 24a is inserted (an outer shape corresponding to the concave hole 20C in the first embodiment). The lower small-diameter hole 20Cb into which the lower small-diameter portion 24b is inserted is provided, and a stepped accommodation hole 18 for accommodating the main valve body portion 15a of the main valve body 15 is provided at the bottom center of the lower small-diameter hole 20Cb. It is connected continuously. Between the stepped portion provided on the inner periphery of the receiving hole 18 and the stepped portion (stepped portion) 15g provided on the lower outer periphery of the main valve body portion 15a of the main valve body 15, a conical compression coil spring is used. The valve closing spring 50 is contracted.

  Further, the inside of the accommodation hole 18 (the lower part from the valve port 22 of the support member 20B) is the valve chamber 21, but here, the discharge of the compressor 100 is discharged into the lower small-diameter hole 20Cb in the concave hole 20C. A plurality of Pd inlets 25 communicating with the chamber 106 are opened, and a ring-shaped filter member 25A is externally provided on the outer periphery of the Pd inlet 25 (instead of the intermediate small diameter portion 15d of the main valve body 15). A plurality of lateral holes 25 s communicating with the Pd introduction port 25 are provided in the lower small diameter portion 24 b of the insertion portion 24, and a Pc inlet / outlet chamber (entrance / exit) 26 communicating with the crank chamber 104 of the compressor 100 is The clearance between the valve chamber 21 → the valve port 22 and the main valve body 15a → the clearance between the lower portion of the guide hole 19 (upper guide hole 19A) and the intermediate small diameter portion 15d → the horizontal hole of the lower small diameter portion 24b 25s → lower small diameter part 24b and lower small (Details will be described later) gap between the hole 20Cb communicating with said Pd inlet 25 through.

  In the present embodiment, the outer periphery of the upper large-diameter portion 24a and the inner periphery of the upper large-diameter hole 20Ca are in contact (in other words, the upper large-diameter portion 24a is fitted (inscribed) into the upper large-diameter hole 20Ca. The support member 20B is inserted and fixed in the recessed hole 20C of the main body member 20A in a posture having a slight gap between the outer periphery of the lower small diameter portion 24b and the inner periphery of the lower small diameter hole 20Cb.

  Needless to say, the control valve 2 of the second embodiment having the above-described configuration can obtain the same operation and effect as those of the control valve 1 of the first embodiment.

  In addition, as the sub-valve part (curved surface part) 17a of the sub-valve part 17 constituting the sub-valve part 12, as shown in FIGS. 9A and 9B, the control angle of the lower tapered surface part 17B is used. You may set (theta) 2 to 90 degrees (namely, it is a surface perpendicular | vertical with respect to the central axis O, and the shape which cut off the front-end | tip part (lower end part)). Moreover, in the said embodiment, although the inverted truncated cone-shaped taper surface part of the subvalve body part (curved surface part) 17a is set as 2 steps | paragraphs, of course, it is good also as a structure of 3 steps | paragraphs or more.

  Moreover, in the said embodiment, the subvalve body part (curved surface part) 17a of the subvalve body 17 is comprised by the taper surface part of several steps of inverted frustoconical shape in which the control angle was increased in steps toward the front end side. However, the present invention is not limited to this. As shown in FIGS. 10 (A) and 10 (B), it is configured by a spherical surface or an elliptical surface whose curvature is continuously increased toward the tip (lower end). Alternatively, such a valve body may be referred to as a ball valve, or the spherical portion or the tip (lower end) of the elliptical portion may be cut off. According to the example shown in FIGS. 10A and 10B, as the flow characteristic of the sub-valve portion 12, a smooth characteristic (in other words, a characteristic that the rate of change of the flow rate with respect to the change of the valve opening continuously changes). ) Is obtained. Further, it is a matter of course that a combination of a spherical surface portion or an elliptical spherical surface portion and one or a plurality of steps of an inverted frustoconical tapered surface portion may be used.

1 Control valve for variable displacement compressor (first embodiment)
2 Control valve for variable displacement compressor (second embodiment)
DESCRIPTION OF SYMBOLS 10 Valve body 11 Main valve part 12 Sub valve part 15 Main valve body 15a Main valve body part 15k Saddle-shaped latching | locking part 16 Intravalve relief passage 16A Through-relief hole 17 Subvalve body 17a Subvalve part (curved surface part)
17A Upper taper surface portion 17B Lower taper surface portion 19 Guide hole 19A Upper guide hole 19B Lower guide hole 20 Valve body 20A Body member 20B Support member 20C Recessed hole 21 Valve chamber 22 Valve port 23 Sub valve seat portion 25 Pd introduction Port 26 Pc inlet / outlet 27 Ps inlet / outlet 30 Electromagnetic actuator 30A Solenoid part 32 Coil 33 Stator 34 Suction element 37 Plunger 37k Inner collar-shaped latching part 37s Slit 37t Cut 40 Bellows device (pressure sensitive responsive member)
45 Pressure sensing chamber 50 Valve closing spring 65 Stator Lv First lift amount La Predetermined amount Lp Second lift amount

Claims (5)

A valve chamber provided with a valve port and a Ps inlet / outlet communicating with a suction chamber of the compressor, a Pd introduction port communicating with a discharge chamber of the compressor upstream from the valve port, and the valve port A valve body provided with a Pc inlet / outlet communicating with the crank chamber of the compressor further downstream, a main valve body for opening / closing the valve port, and for moving the main valve body in the valve port opening / closing direction An electromagnetic actuator having a plunger, a pressure sensing chamber into which suction pressure Ps is introduced from the compressor through the Ps inlet and outlet, and the main valve body in the valve opening / closing direction according to the pressure in the pressure sensing chamber A pressure-sensitive responsive member that urges the crank chamber, and a relief passage in the valve is provided in the main valve body for allowing the pressure Pc of the crank chamber to escape to the suction chamber of the compressor through the Ps inlet / outlet. A sub-valve element for opening and closing the relief passage in the valve is provided,
The sub-valve element has a curved surface part that changes the flow rate of the fluid flowing through the valve escape passage according to the lift amount, and the curvature or control angle of the curved surface part increases continuously or stepwise as it approaches the tip. A control valve for a variable displacement compressor, characterized in that   The curved surface portion includes a spherical surface portion, an elliptical surface portion, a plurality of steps of an inverted frustoconical tapered surface portion whose control angle is increased stepwise toward the tip, or one or more steps with the spherical surface portion or the elliptical surface portion. 2. The control valve for a variable displacement compressor according to claim 1, wherein the control valve is configured in combination with the tapered surface portion of a stage.   3. The control valve for a variable displacement compressor according to claim 1, wherein the curved surface portion has a symmetrical shape with respect to a central axis of the auxiliary valve body.   5. The curvature or control angle on the distal end side of a portion of the curved surface portion that is seated on the main valve body is increased continuously or stepwise as approaching the distal end. The control valve for the variable displacement compressor in the section.   5. The method according to claim 1, wherein a part of the curved surface portion is positioned in the escape passage in the valve when the sub-valve is in the highest position with respect to the main valve. A control valve for a variable displacement compressor according to claim 1.

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