JP2020084904A - Control valve for variable displacement compressor - Google Patents

Abstract

To provide a variable displacement compressor which suppresses Pd-Ps leakage and inclination of a valve body, further, can prevent foreign matters from being accumulated in a sliding surface gap formed between a main valve body and a guide hole and, thereby, can hardly cause defective actuation such as valve lock and desertion.SOLUTION: A sliding part for a guide hole 19 in a main valve body 10 is formed of, successively from the Pd introduction port 26 side to Ps inlet/outlet port 27 side, a high-pressure side large diameter part 10f having a diameter Da, a middle annular groove part 10g having a diameter Db smaller than Da and a prescribed axial direction length and, when a low-pressure side large diameter part 10h of which the diameter Dc is larger than Dh is provided and at least main valve body 19 is closed in the guide hole 19, a longitudinal groove 19g which can communicate a sliding surface gap (middle size clearance β portion) which is formed between the middle annular groove part 10g in the main valve body 10 and an inner wall surface of the guide hole is formed.SELECTED DRAWING: Figure 7

Description

The present invention 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 valve element caused by foreign matter flowing into a sliding surface gap formed between the valve element and a guide hole. The present invention relates to a control valve for a variable displacement compressor that is less likely to cause malfunction.

Generally, a control valve for a variable displacement compressor used in a car air conditioner or the like introduces a discharge pressure Pd from a discharge chamber of the compressor and regulates the discharge pressure Pd according to a suction pressure Ps of the compressor. As a result, the pressure Pc in the crank chamber is controlled, and normally, as seen in Patent Documents 1 and 2 below, Ps communicating with the valve chamber provided with the valve port and the suction chamber of the compressor. An inlet/outlet is provided, a Pd inlet communicating with the discharge chamber of the compressor is provided upstream of the valve opening, and a Pc inlet/outlet communicating with the crank chamber of the compressor is provided downstream of the valve opening. Valve main body, a main valve body (valve rod) for opening and closing the valve opening, an electromagnetic actuator having a plunger for moving the main valve opening and closing direction, and suction from the compressor A pressure-sensitive chamber into which the pressure Ps is introduced via the Ps inlet/outlet, and a pressure-sensitive responsive member such as a bellows device for urging the main valve body in the valve opening/closing direction according to the pressure in the pressure-sensitive chamber, Is equipped with.

In addition to the above-described configuration, the variable displacement compressor control valve disclosed in Patent Document 2 below allows the pressure Pc of the crank chamber to escape to the suction chamber of the compressor via the Ps inlet/outlet. Is provided with a sub-valve body for opening and closing the intra-valve escape passage, and when the plunger is continuously moved upward from the lowest position by the suction force of the electromagnetic actuator. , The auxiliary valve body moves upward together with the plunger while keeping the escape passage in the valve closed, and the main valve body is moved upward so as to follow the auxiliary valve body. After the valve mouth is closed by the body, when the plunger is further moved in the upward direction, the sub valve body opens the in-valve escape passage.

Japanese Patent No. 5553514 JP, 2013-130126, A Japanese Patent No. 4031945

By the way, in the conventional control valve for a variable displacement compressor disclosed in Patent Documents 1 and 2 and the like, the main valve body that opens and closes the valve opening is slidably inserted into a guide hole provided in the valve body. However, the size of the sliding surface gap (clearance) formed between (the outer peripheral surface of) the main valve body and (the inner wall surface of) the guide hole is extremely important.

That is, in the conventional control valve, a differential pressure is generated above and below the guide hole (for example, the upper side of the guide hole is on the low pressure (Ps) side, and the lower side of the guide hole is on the high pressure (Pd) side). There is a phenomenon of leakage from the Pd) side to the low pressure (Ps) side through the sliding surface gap. Such leakage (referred to as Pd-Ps leakage) causes performance deterioration, and thus it is required to suppress it as much as possible. Therefore, from the viewpoint of suppressing Pd-Ps leakage, it is required to reduce the sliding surface gap, and further, it is desired to increase the sliding portion (its axial length).

Further, when the sliding surface gap is large, the valve body is likely to tilt and the operation becomes unstable. Therefore, from this viewpoint as well, it is desired to reduce the sliding surface gap.

Further, foreign matter (cutting and polishing dust, abrasives, friction powder due to sliding friction, dust from the outside, etc.) remaining in the sliding surface gap enters and accumulates. However, there is a case where the main valve body is stuck due to the clogging of the sliding surface gap (valve lock, valve body left behind) and other malfunctions. If no measures are taken, problems due to such foreign matter tend to occur as the sliding surface gap becomes smaller.

In order to prevent malfunctions due to such foreign matter from occurring easily, conventionally, a foreign matter catching annular groove is provided in the main valve body, and the sliding surface gap is closer to the low pressure (Ps) side than the high pressure (Pd) side. Although various measures such as increasing the size (see Patent Document 3) have been adopted, it has not been sufficient as a measure against malfunction due to foreign matter.

The present invention has been made in view of the above circumstances, and an object of the present invention is to suppress the leakage of Pd-Ps and the inclination of the valve body, and to form a sliding member formed between the main valve body and the guide hole. A control valve for a variable displacement compressor that can prevent foreign matter from accumulating in the moving surface gap, and thus prevent malfunctions such as valve lock and valve body leaving without reducing controllability and operational stability. To provide.

In order to achieve the above object, a control valve for a variable displacement compressor according to the present invention basically comprises a main valve body having a main valve body portion and a guide hole into which the main valve body is slidably inserted. A valve chamber provided with a valve port for contacting and separating the main valve body, and a Ps inlet/outlet communicating with a suction chamber of the compressor, and communicating with a discharge chamber of the compressor upstream of the valve port. And a valve main body provided with a Pc inlet/outlet that communicates with the crank chamber of the compressor downstream of the valve port, and for moving the main valve body in the valve opening/closing direction. An electromagnetic actuator, a pressure-sensitive chamber into which suction pressure Ps is introduced from the compressor through the Ps inlet/outlet, and biases the main valve body in the valve opening/closing direction in accordance with the pressure in the pressure-sensitive chamber. A pressure-sensitive responsive member. The sliding portion of the main valve body is a high-pressure side large-diameter portion having a diameter of Da and a predetermined axial length of Db smaller than the Da, in order from the Pd inlet side to the Ps inlet/outlet side. And a low-pressure side large-diameter portion having a diameter Dc larger than Db is provided in the guide hole, and at least when the main valve body is closed in the guide hole, One or a plurality of guide hole side grooves capable of communicating the sliding surface gap formed between the intermediate annular groove portion and the inner wall surface of the guide hole with the Ps inlet/outlet side are formed. There is.

In a preferred aspect, the guide hole side groove of the guide hole is formed between the intermediate annular groove portion of the main valve body and the inner wall surface of the guide hole in the entire stroke of the main valve body from fully closed to fully opened. The sliding surface gap and the Ps inlet/outlet side can be always communicated with each other.

In another preferred aspect, the axial length of the intermediate annular groove portion is longer than the axial length of the high-pressure side large diameter portion.

In a further preferred aspect, the axial lengths of the high pressure side large diameter portion, the intermediate annular groove portion, and the low pressure side large diameter portion are made longer in that order.

The guide hole side groove preferably includes a vertical groove extending in the axial direction of the guide hole, an inclined groove or a spiral groove formed in a direction inclined with respect to the axial direction of the guide hole, or a notch.

In another preferred aspect, the axial length of the guide hole side groove is longer than the axial length of the intermediate annular groove portion.

In another preferred aspect, the axial length of the guide hole side groove is shorter than the axial length of the intermediate annular groove portion.

In another preferred aspect, the guide hole side groove is formed deeper than the intermediate annular groove portion.

In another preferred aspect, the cross-sectional area of the refrigerant passage space formed by the guide hole side groove and the cross-sectional area of the refrigerant passage space formed by the intermediate annular groove portion are made equal.

In another preferred aspect, an in-valve escape passage for escaping the pressure Pc in the crank chamber to the suction chamber of the compressor via the Ps inlet/outlet is provided in the valve body or in the main valve body, and A sub valve body is provided that opens and closes the valve escape passage.

In the control valve of the present invention, the high pressure side small clearance α is formed between the inner wall surface of the guide hole and the high pressure side large diameter portion of the main valve body, and the inner wall surface of the guide hole and the intermediate annular groove portion of the main valve body are formed. An intermediate large clearance β is formed therebetween, and a low pressure side small clearance γ is formed between the inner wall surface of the guide hole and the low pressure side large diameter portion of the main valve body (α<β, γ<β).

For example, if the upper side of the guide hole is on the low pressure (Ps) side and the lower side of the guide hole is on the high pressure (Pd) side, then the intermediate annular groove portion from the high pressure (Pd) side via the high pressure side small clearance α of the high pressure side large diameter portion. Only small foreign matters of α or less intrude into the. In this case, since the intermediate large clearance β of the intermediate annular groove is sufficiently large, even if a small foreign matter of α or less enters and accumulates therein, it will not be clogged.

Foreign matter that has entered the intermediate annular groove portion is made to communicate with the intermediate annular groove portion (intermediate large clearance β portion) and the low pressure (Ps) side by the guide hole side groove, at least when the main valve body closes. The foreign matter is discharged from the intermediate annular groove portion to the low pressure (Ps) side through the guide hole side groove.

As described above, in the control valve of the present invention, a small clearance (a large diameter portion on the low pressure side and a large diameter portion on the high pressure side) is formed in the upper and lower ends of the main valve body, and a large clearance (in the middle portion of the main valve body). Since an intermediate annular groove portion) is formed and a guide hole side groove that allows the intermediate annular groove portion of the main valve body to communicate with the Ps inlet/outlet side is formed in the guide hole, leakage of Pd-Ps and inclination of the valve body are suppressed. In addition, foreign matter can be prevented from accumulating in the sliding surface gap (clearance) formed between the main valve body and the guide hole, and as a result, controllability and operational stability can be improved. It is possible to prevent malfunctions such as valve lock and valve body leaving.

FIG. 3 is a vertical cross-sectional view showing a state (during normal control) of a main valve: open and a sub valve: close to one embodiment of the variable displacement compressor control valve according to the present invention. FIG. 3 is a vertical cross-sectional view showing a state where a main valve is closed and a sub valve is closed (when the compressor is started (part 1)) of the control valve for a variable displacement compressor according to the present invention. FIG. 3 is a vertical cross-sectional view showing a main valve:closed state, a sub valve:closed state (at the time of transition to starting of the compressor (No. 2)) of the embodiment of the control valve for a variable displacement compressor according to the present invention. FIG. 3 is a vertical cross-sectional view showing a main valve:closed state, a sub valve:opened state (at the time of starting the compressor) of an embodiment of the variable displacement compressor control valve according to the present invention. Sectional drawing which follows the UU arrow line of FIG. 1 is a perspective view showing a main valve element used in an embodiment of a control valve for a variable displacement compressor according to the present invention. FIG. 5 is an enlarged cross-sectional view of the main part of FIG. 1 taken along the line V-V of FIG. 5. FIG. 5 is an enlarged cross-sectional view of the main part of FIG. 2, taken along the line VV of FIG. 5.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

1 to 4 are vertical sectional views showing an embodiment of a control valve for a variable displacement compressor according to the present invention. FIG. 1 shows a main valve: open state, a sub valve: closed state (during normal control). ), FIG. 2 and FIG. 3 show a main valve: closed state, a sub valve: a closed state (when the compressor starts transition), and FIG. 4 shows a main valve: closed, a sub valve: an open state (when the compressor starts). There is. Further, FIG. 5 is a cross-sectional view taken along the line U-U of FIG. 1, and FIG. 6 is a perspective view showing a main valve element used in an embodiment of a variable displacement compressor control valve according to the present invention. 7 is an enlarged sectional view of the main part of FIG. 1 taken along the line VV of FIG. 5, and FIG. 8 is an enlarged sectional view of the main part of FIG. 2 taken along the line of the VV arrow of FIG.

It should be noted that, in the present specification, the description indicating the position, direction such as up/down, left/right, front/rear, etc. is added for convenience according to the drawings in order to avoid the description from being complicated, and is actually installed in the compressor. Does not necessarily mean the position or direction.

Further, in each drawing, the gaps formed between the members and the separation distances between the members are larger than the dimensions of the respective constituent members in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn smaller.

[Configuration of control valve 1]
The control valve 1 of the illustrated embodiment is basically a valve body 20 provided with a valve opening 22, a main valve body 10 for opening and closing the valve opening 22, and a main valve body 10 for opening and closing a valve opening and closing direction ( An electromagnetic actuator 30 for moving in the vertical direction) and a bellows device 40 as a pressure sensitive member are provided.

The electromagnetic actuator 30 includes a bobbin 38, a coil 32 for energizing and energizing the bobbin 38, a stator 33 and an attractor 34 arranged on the inner peripheral side of the coil 32, and lower ends of the stator 33 and the attractor 34. A guide pipe 35 whose upper end is joined to the outer circumference (step) by welding, and a bottomed cylindrical plunger which is vertically slidably arranged below the suction element 34 and on the inner circumference side of the guide pipe 35. 37, a cylindrical housing 60 externally fitted to the coil 32, a connector portion 31 mounted on the upper side of the housing 60 via a mounting plate 39, and between the lower end portion of the housing 60 and the lower end portion of the guide pipe 35. And a holder 29 for fixing them to the upper part of (the main body member 20A of) the valve main body 20. In this example, a cylindrical suction element 34 having a through hole 34a having a diameter smaller than the inner diameter of the stator 33 formed at the center (along the axis O) is integrally formed on the lower inner circumference of the cylindrical stator 33. Has been done. Here, a portion of the electromagnetic actuator 30 excluding the plunger 37, which includes the coil 32, the stator 33, the suction element 34, and the like, is referred to as a solenoid portion 30A.

On the upper part of the stator 33, an adjusting member in which a female screw portion 64a formed on the inner periphery of a cylindrical holding member 64 and a male screw portion 65a formed on the outer periphery of an adjustment screw 65 having a hexagonal hole are screwed together. 61 is provided. In the adjusting member 61, the lower half of the adjusting screw 65 is fitted into the lower half of the holding member 64 (with an O-ring 62 as a sealing material interposed therebetween), and A male screw portion 65a provided on the outer circumference of the upper portion is screwed to a female screw portion 64a provided on the inner circumference of the upper portion of the holding member 64. The adjusting member 61 is inserted into a fitting insertion hole 31 a that is provided at a substantially central portion of the connector portion 31 and a central hole 39 a that is provided at a substantially central portion of the mounting plate 39, and is provided so as to project on a lower outer periphery of the holding member 64. The flange portion 64b and the ring-shaped pressing member 63 fitted in (the fitting groove formed in) the upper outer periphery are cooperatively held and fixed by the connector portion 31 and the mounting plate 39 (incapable of vertical movement). The lower end portion (of the holding member 64) (the portion below the flange portion 64b) is arranged (interpolated) on the inner peripheral side of the upper end portion of the stator 33.

A pressure sensing chamber 45, into which the suction pressure Ps of the compressor is introduced, is formed between the suction member 34 and the adjusting member 61 (adjusting screw 65 and holding member 64) on the inner peripheral side of the stator 33. A bellows device 40 including a bellows 41, a downward convex upper stopper 42, a downward concave lower stopper 43, and a compression coil spring 44 is disposed in the pressure sensitive chamber 45 as a pressure sensitive responding member. Further, below the bellows device 40, a stepped rod-shaped push rod 46 as a thrust transmission member is arranged along the axis O. The substantial center of the push rod 46 has a large diameter (large diameter portion 46b), the upper end portion 46d of the push rod 46 is fitted and supported in the concave portion of the lower stopper 43, and the insertion hole 34a of the suction element 34 is formed. The upper portion of the push rod 46 and the large-diameter portion 46b are internally inserted (with a slight gap 34b). Further, the lower portion of the push rod 46 is inserted into a recessed hole 17b of an interior member 17 having a recessed cross-section described later, and a lower end portion 46a of the push rod 46 is a recessed fitting formed at the center of the bottom portion of the recessed hole 17b. It is fitted into the insertion hole 17c.

An internal member 17 having a concave cross section, which has a vertically elongated concave hole 17b having substantially the same diameter as the insertion hole 34a of the suction element 34, is internally fixed to the plunger 37 by press fitting or the like. The interior member 17 has its upper end aligned with the upper end of the plunger 37 (in other words, its upper end is positioned inside the upper end of the plunger 37), and its lower end has a gap with the bottom of the plunger 37. In this state (which will be described later in detail), the flange-shaped engaging portion 10k of the main valve body 10 is fitted in the plunger 37 in a state in which there is a gap in which it can be moved up and down. At the center of the bottom of the recessed hole 17b of the interior member 17, a recessed insertion hole 17c into which the lower end 46a of the push rod 46 is inserted is formed.

The stepped portion (downward annular terrace surface) 46c formed at the upper part of the large diameter portion 46b of the push rod 46 and the bottom portion of the recessed hole 17b of the interior member 17 fitted in the plunger 37 (in the vicinity of the fitting insertion hole 17c A plunger spring (valve opening spring) 47 made of a cylindrical compression coil spring is compressed between the upper surface and the upper surface). This (compressive force) of the plunger spring 47 urges the plunger 37 downward (in the valve opening direction) via the interior member 17, and the bellows device 40 within the pressure sensitive chamber 45 via the push rod 46. Is held.

In addition, a slit 37s linearly extending from the outer periphery to the center (on the axis O) is formed at the bottom of the plunger 37, and the slit 37s is formed at a portion corresponding to the slit 37s on the side portion of the plunger 37. A wider cutout 37t is provided. The height (vertical direction) of the notch 37t is slightly larger than the height of the collar-shaped locking portion 10k of the main valve body 10, and the height (vertical direction) of the slit 37s (that is, the plunger 37). Has a thickness (height in the vertical direction) slightly smaller than the height of the upper small diameter portion 10d of the main valve body 10, and the main valve body 10 can move up and down with respect to the plunger 37. (Detailed later). The width of the notch 37t (in the circumferential direction) is slightly larger than the outer diameter of the collar-shaped locking portion 10k of the main valve body 10, and the width of the slit 37s (in the lateral direction) is easy to assemble. In consideration of the above, the outer diameter of the upper small-diameter portion 10d of the main valve body 10 is made slightly larger and the outer diameter of the collar-shaped locking portion 10k of the main valve body 10 is made smaller, and the bottom portion of the plunger 37 is An outer peripheral portion of the slit 37s on the upper surface is an inner collar-shaped locking portion 37k for locking the collar-shaped locking portion 10k of the main valve body 10.

Further, a portion corresponding to the slit 37s is cut out on the lower surface of the plunger 37 (specifically, a portion wider than the outer diameter of the stepped sliding portion 10c of the main valve body 10 is cut out. In a plan view, a substantially C-shaped cylindrical leg portion 37a is provided (downward) so as to project. The tubular leg portion 37a is externally inserted (with a slight gap) into (the upper end portion of) the stepped sliding portion 10c of the main valve body 10, and the lower end portion of the auxiliary valve body 15 to be described later. An outer brim-shaped hooking portion 37j for hooking the brim-shaped locking portion 15j is provided so as to project (outward).

Further, in this example, the D-cut surface 37d is formed at a predetermined position (the portion where the notch 37t and the slit 37s are formed in the illustrated example) on the outer periphery of the plunger 37, and the plunger 37 (the D-cut surface 37d thereof) is formed. A gap 36 is formed between the outer periphery of) and the guide pipe 35. Instead of the D-cut surface 37d of the plunger 37, one or a plurality of vertical grooves may be formed to form the gap 36 between the outer circumference of the plunger 37 and the guide pipe 35.

The main valve body 10 is made of metal, for example, and is formed of a stepped shaft-shaped solid member arranged along the axis O. The main valve body 10 includes, in order from the bottom, a relatively large diameter main valve body portion 10a, a lower small diameter portion 10b, a stepped sliding portion 10c that is long in the up-down direction, an upper small diameter portion 10d, and a collar-shaped locking portion 10k. It consists of

Details of the stepped sliding portion 10c will be described later together with the guide hole 19 provided in the valve body 20.

As described above, the stepped sliding portion 10c of the main valve body 10 (the upper end portion projecting upward from the guide hole 19 thereof) is inserted into the cylindrical leg portion 37a provided on the lower surface of the plunger 37, and The small-diameter portion 10d is loosely fitted in the slit 37s, and the collar-shaped locking portion 10k is below the interior member 17 inside the plunger 37 (in other words, the bottom portion of the plunger 37 and the lower end portion of the interior member 17). It is loosely fitted in the space between). The collar-shaped locking portion 10k has a diameter larger than the width of the slit 37s, and when the plunger 37 is moved upward with respect to the main valve body 10, an inner collar-shaped portion formed of an outer peripheral portion of the slit 37s. The hooking portion 37k is hooked on the collar-shaped locking portion 10k so that the hooking portion 37k is retained and locked. Further, the stepped sliding portion 10c also has a larger diameter than the width of the slit 37s, and the outer peripheral portion of the slit 37s on the lower surface of the plunger 37 has a stepped sliding portion 10c of the main valve body 10 and an upper small diameter. It is adapted to be brought into contact with the stepped portion with the portion 10d.

On the other hand, the valve main body 20 includes a stepped cylindrical main body member 20A having a concave hole 20C for fitting provided at the center of the upper part and an accommodating hole 18 having a slightly smaller diameter connected to the concave hole 20C at the lower center. It has a two-part configuration with a cylindrical sheet member 20B that is inserted and fixed in the recessed hole 20C by press fitting or the like.

The seat member 20B is made of metal such as stainless (SUS), and is located above the fitting insertion portion 24 that is fitted into the recessed hole 20C (in other words, protrudes from the fitting insertion portion 24 toward the Ps inlet/outlet chamber 28 side). Therefore, a stopper portion 24A for defining the lowermost position of the plunger 37 is provided in a protruding manner. The lower end portion of (the fitting insertion portion 24 of) the seat member 20B is brought into contact with the step portion (hill portion) between the recessed hole 20C of the main body member 20A and the accommodation hole 18. A guide hole 19 into which the stepped sliding portion 10c of the main valve body 10 is slidably inserted so as to vertically penetrate (that is, along the axis O) in the central portion of the seat member 20B. Is formed, and the lower end portion of the guide hole 19 serves as a valve opening 22 (valve seat portion) which is opened and closed by the main valve body portion 10a of the main valve body 10. Here, the main valve body 11 is composed of the main valve body portion 10 a and the valve opening 22.

The seat member 20</b>B (and the cylindrical portion 15 b of the sub-valve body 15 described later) (the outer diameter thereof) has a smaller diameter than the plunger 37.

The main body member 20A is made of, for example, aluminum, brass, resin, or the like, and in the state where the seat member 20B (the fitting insertion portion 24) is inserted into the recessed hole 20C of the main body member 20A, the outer periphery of the stopper portion 24A ( In other words, the Ps inlet/outlet chamber 28 of the suction pressure Ps of the compressor is formed on the upper end side of the sheet member 20B in the main body member 20A, and a plurality of Ps inlet/outlet chambers 28 (in the illustrated example, on the outer peripheral side) are formed. Two) Ps inlets/outlets 27 are formed. The suction pressure Ps introduced into the Ps inlet/outlet chamber 28 from the Ps inlet/outlet 27 is the gap 36 formed between the outer periphery of the plunger 37 and the guide pipe 35 (in this example, the gap formed by the D-cut surface 37d). ), and is introduced into the pressure-sensitive chamber 45 through a gap 34b formed between the outer periphery of the push rod 46 and the suction element 34.

Further, a guide hole 19 for accommodating the main valve body portion 10a of the main valve body 10 and the accommodation hole 18 having a diameter larger than that of the main valve body portion 10a are continuously provided at the center of the bottom of the recessed hole 20C of the main body member 20A. Has been done. A valve closing spring formed of a conical compression coil spring is provided between a bottom outer peripheral corner of the accommodation hole 18 and a step portion (terrace) 10e provided on the lower outer periphery of the main valve body 10a of the main valve body 10. The main valve body 10 (the stepped portion between the stepped sliding portion 10c and the upper small diameter portion 10d) is pressed against the plunger 37 (the lower surface thereof) by the biasing force of the valve closing spring 50. Here, the inside of the accommodation hole 18 (the portion below the valve opening 22 of the seat member 20B) is a valve chamber 21.

A plurality of Pd introducing ports 25 communicating with the discharge chamber of the compressor are opened in the concave holes 20C, and a ring-shaped filter member 25A is arranged on the outer periphery of the Pd introducing ports 25, and The fitting insertion portion 24 of the seat member 20B inserted in the hole 20C (particularly, the portion below the portion where the stepped sliding portion 10c of the main valve body 10 is inserted) communicates with the Pd introduction port 25. At the same time, a plurality of horizontal holes 25s continuous with the guide hole 19 are provided.

A lid-shaped 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 is above the lid-shaped member 48 and below the accommodation hole 18 (in other words, the main body). The lower end side of the sheet member 20B in the member 20A is a Pc inlet/outlet chamber (inlet/outlet) 26 that communicates with the crank chamber of the compressor. The Pc inlet/outlet chamber (inlet/outlet) 26 has a valve chamber 21→a gap between the valve opening 22 and the main valve body 10a→a gap between the lower portion of the guide hole 19 and the lower small diameter portion 10b→a fitting portion 24. It communicates with the Pd introduction port 25 through the horizontal hole 25s.

Further, in the present embodiment, the valve body communication passage 16A (see FIG. 5) for communicating the Pc inlet/outlet chamber 26 and the Ps inlet/outlet chamber 28 between the body member 20A and the seat member 20B of the valve body 20. Is provided.

Specifically, a vertical groove 16b whose lower end opens to the valve chamber 21 (and the Pc inlet/outlet chamber 26) is formed on the outer periphery of the fitting insertion portion 24 of the seat member 20B in the valve body 20, and inside the upper portion of the body member 20A. At the periphery (in other words, the upper end portion of the recessed hole 20C), an annular recess 16a is formed which is continuous with the vertical groove 16b. The vertical groove 16b (extending in the vertical direction) and the (circular) annular recess 16a are formed. Thus, the valve main body communication passage 16A that communicates the Pc inlet/outlet chamber 26 and the Ps inlet/outlet chamber 28 is formed. The communication passage 16A in the valve body constitutes a part of the relief passage 16 in the valve, and the upper end portion of the communication passage 16A in the valve body (the upper end portion of the annular recess 16C) is the lower end portion of the sub-valve body 15 ( The sub-valve body portion 15a is a sub-valve seat portion 23 that comes into contact with and separates from the sub-valve seat portion 23a.

On the other hand, on the outer periphery of the stopper portion 24A of the seat member 20B projecting to the Ps inlet/outlet chamber 28 side, a sub valve body 15 for opening/closing the valve relief passage 16 (valve body communication passage 16A) is vertically arranged. It is slidably distributed.

The sub-valve body 15 is made of, for example, a metal, and has a tubular portion 15b that is slidably inserted into the stopper portion 24A and has a diameter substantially the same as (the outer diameter of) the stopper portion 24A. A lower end portion of the portion 15b serves as a sub valve body portion 15a that opens and closes the in-valve escape passage 16 by contacting and separating from the sub valve seat portion 23 that is an upper end edge portion of the valve main body communication passage 16A. Here, the sub-valve seat portion 23 and the sub-valve body portion 15a constitute the sub-valve portion 12.

Further, a flange-shaped lower spring receiving portion 15c is provided (outwardly) on the lower end portion of the tubular portion 15a, and at the upper end portion (inner periphery) of (the body member 20A of) the valve body 20. Has a flange-shaped upper spring receiving portion 20c projecting from the lower spring receiving portion 15c and the upper spring receiving portion 20c. A valve closing spring 51, which is an inverted conical compression coil spring for urging the passage 16A) in a valve closing direction), is compressed.

The upper end of (the cylindrical portion 15b of) the auxiliary valve body 15 is positioned above the stopper portion 24A (the upper end thereof) by a predetermined dimension, and the upper end of the (the cylindrical portion 15b of) the auxiliary valve body 15 is located. The opening (upper end on the side opposite to the sub-valve body portion 15a) is provided with a flange-like locking portion 15j for moving the sub-valve body 15 in conjunction with the plunger 37 so as to project inward. Here, the brim-shaped locking portion 15j is provided in a portion of the upper end opening that is slightly over half the circumference. The brim-shaped locking portion 15j projects from the upper end opening of the tubular portion 15b toward the tubular leg portion 37a side of the plunger 37 that is externally inserted into the stepped sliding portion 10c of the main valve body 10, When the plunger 37 is moved upward with respect to the sub-valve element 15, the outer brim-shaped hooking portion 37j of (the cylindrical leg portion 37a of) the plunger 37 hooks the brim-shaped locking portion 15j. It is supposed to be stopped.

In the present embodiment, as described above, the pressure Pc of the crank chamber is set to Ps inlet/outlet by the Pc inlet/outlet chamber 26, the valve chamber 21, the valve body internal communication passage 16A provided in the valve body 20, the Ps inlet/outlet chamber 28, and the like. An in-valve escape passage 16 for escape to the suction chamber of the compressor via 27 is configured, and the sub-valve seat portion 23, which is the upper end edge of the communication passage 16A in the valve main body, has a sub-valve body portion of the sub-valve body 15 ( By separating and contacting the lower end portion 15a, 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 10, and the sub valve body 15 are in the lowest position (the lowermost end surface of the plunger 37 (that is, The lower end surface of the outer brim-shaped hooking portion 37j of the cylindrical leg portion 37a of the plunger 37 abuts on (the upper surface of) the stopper portion 24A, and the main valve portion 11 is fully opened and the sub valve portion 12 is fully closed. The vertical distance between the main valve body portion 10a of the valve body 10 and the valve opening 22 (valve seat portion) is set to the first lift amount La, and the outer flange-like hooking portion 37j of the plunger 37 and the sub valve body. The distance from the flange-shaped engaging portion 15j of 15 is the second lift amount Lb (>La), and the distance between the inner flange-like engaging portion 37k of the plunger 37 and the flange-shaped engaging portion 10k of the main valve body 10 is increased. The distance is a predetermined amount Lx, and the maximum lift amount (third lift amount) Lc (>Lb) of the plunger 37 (the lift amount from the lowest descent position to the highest lifted position of the plunger 37) is the first lift amount La+ It is a fixed amount Lx. That is, the separation distances are set so that the relationship of Lx>Lb-La is established.

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

During normal control (when controlling Pd→Pc), the lift amount of the plunger 37 is at most the first lift amount La at maximum, and when starting the compressor (when controlling Pc→Ps), the lift amount of the plunger 37 is increased. The amount is the third lift amount Lc.

That is, during normal control (during Pd→Pc control), when the solenoid portion 30A including the coil 32, the stator 33, and the suction element 34 is energized and excited, the plunger 37 is attracted to the suction element 34, and this movement occurs. Following this, the main valve body 10 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 to the Ps inlet/outlet 27 is introduced from the Ps inlet/outlet chamber 28 into the pressure sensitive chamber 45 through the gap 36 between the outer periphery of the plunger 37 and the guide pipe 35, and the bellows. The device 40 (vacuum pressure inside) expands and contracts (contracts when the suction pressure Ps is high and expands when the suction pressure Ps is high) according to the pressure (suction pressure Ps) in the pressure sensing chamber 45, and the displacement is the push rod 46 or the interior member 17. , Is transmitted to the main valve body 10 via the plunger 37, whereby the valve opening degree (separation distance between the valve opening 22 and the main valve body portion 10a) is adjusted, and according to the valve opening degree, the crank chamber The pressure Pc is adjusted.

In this case, the main valve body 10 is always urged upward by the urging force of the valve closing spring 50, and the flange-shaped engaging portion 15j of the sub valve body 15 is engaged with the outer flange-shaped engagement portion 37j of the plunger 37. Since it is not stopped (because of Lb>La), the sub valve body 15 is always urged downward by the urging force of the valve closing spring 51, so the sub valve body portion 15a is pressed against the sub valve seat portion 23. In this state (the sub valve portion 12 is closed), the in-valve escape passage 16 is blocked in the valve body 20. Therefore, the pressure Pc of the crank chamber is not released to the suction chamber through the in-valve escape passage 16.

On the other hand, when the compressor is activated, the solenoid portion 30A is energized and excited, the plunger 37 is attracted to the suction element 34, and the main valve body 10 is moved upward in accordance with the upward movement. After the valve opening 22 is closed by the main valve body portion 10a of 10, the plunger 37 is further moved in the upward direction, whereby the sub valve body 15 opens the in-valve escape passage 16, and the pressure in the crank chamber is increased. Pc is released to the suction chamber through the valve release passage 16.

In detail, until the upward movement amount of the plunger 37 reaches the first lift amount La, the main valve body 10 moves in the valve closing direction so as to follow the upward movement of the plunger 37 by the urging force of the valve closing spring 50. When it moves and the amount of upward movement reaches the first lift amount La, the valve opening 22 is closed by the main valve body portion 10a of the main valve body 10 (the state shown in FIG. 2). When the compressor is started, the plunger 37 is further moved upward from the closed state of the main valve portion 11 (since the main valve body 10 remains stationary in the closed state). Until the upward movement amount of the plunger 37 reaches the second lift amount Lb, the sub valve body 15 remains in the closed state by the urging force of the valve closing spring 51 (the sub valve body portion 15a is pressed against the sub valve seat portion 23). It remains immobile. When the upward movement amount reaches the second lift amount Lb, the outer brim-shaped hooking portion 37j of the plunger 37 is locked to the brim-shaped locking portion 15j of the sub valve body 15 (the state shown in FIG. 3). ). Then, from this state, until the inner collar-shaped hooking portion 37k of the plunger 37 is locked to the collar-shaped locking portion 10k of the main valve body 10, that is, the plunger 37 is further extended by Lx−(Lb−La). It is moved upward (state shown in FIG. 4). In other words, after the amount of upward movement of the plunger 37 reaches the first lift amount La, until the inner collar-shaped hooking portion 37k of the plunger 37 is locked by the collar-shaped locking portion 10k of the main valve body 10. The sub-valve body 15 is lifted (from the valve body 20) by the amount of Lx-(Lb-La). In this case, while the main valve body 10 remains stationary in the valve closed state, the sub-valve body portion 15a of the sub-valve body 15 is lifted from the sub-valve seat portion 23 by the amount of Lx-(Lb-La). This opens the valve escape passage 16. When the inner collar-shaped hooking portion 37k of the plunger 37 is locked to the collar-shaped locking portion 10k of the main valve body 10, even if the solenoid portion 30A generates a suction force, the plunger 37 and the sub valve body 15 will I can't raise more.

As described above, 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 in-valve escape passage 16, so that the discharge capacity is large at the start of the compressor. It is possible to significantly reduce the time required until it becomes. Further, during the normal control (during Pd→Pc control), the in-valve escape passage 16 is closed by the sub-valve body 15, so that the operating efficiency of the compressor does not decrease.

[Detailed Description of Main Valve Body 10 and Guide Hole 19]
Next, the stepped sliding portion 10c located in the intermediate portion of the main valve body 10 and the guide hole 19 of (the seat member 20B of) the valve body 20 into which the stepped sliding portion 10c is inserted will be described.

In the control valve 1 of the present embodiment, foreign matter is contained in the sliding surface gap (clearance) formed between (the outer peripheral surface of) the stepped sliding portion 10c of the main valve body 10 and (the inner wall surface of) the guide hole 19. The main valve body 10 may become stuck (valve lock, valve body left behind) due to clogging (cutting and grinding dust, abrasives, friction powder due to sliding friction, dust from the outside, etc. remaining after processing and assembly). In order to avoid it, the following measures are taken in the stepped sliding portion 10c of the main valve body 10 and the guide hole 19 of the valve body 20.

That is, as can be seen with reference to FIGS. 5 to 8, the stepped sliding portion 10c is sequentially arranged from the bottom to the top, in other words, from the high pressure (Pd inlet 25) side to the low pressure (Ps inlet/outlet 27) side. , A high-pressure side large-diameter portion 10f having a diameter Da and a relatively short axial length L1 (for example, about 0.3 mm), and an intermediate annular groove portion L2 having a diameter smaller than the Da and a relatively long axial length L2. A low-pressure side large-diameter portion 10h having a diameter Lg of 10 g and a diameter Dc (Dc=Da in this example) larger than the diameter Db and a considerably long axial length is provided. In this example, in the stepped sliding portion 10c, the axial lengths of the high pressure side large diameter portion 10f, the intermediate annular groove portion 10g, and the low pressure side large diameter portion 10h are made longer in that order (L1<L2< L3).

Therefore, a high pressure side small clearance α (for example, about 8 to 20 μm, which is close to the machining limit) is formed between the inner wall surface of the guide hole 19 having a constant hole diameter (inner diameter) and the high pressure side large diameter portion 10f of the main valve body 10. A large intermediate clearance β (for example, about 100 μm larger than the opening of the filter member 25A or the like) is formed between the inner wall surface of the guide hole 19 and the intermediate annular groove portion 10g of the main valve body 10. A low pressure side small clearance γ (for example, about 8 to 20 μm, which is close to the processing limit) is formed between the wall surface and the low pressure side large diameter portion 10h of the main valve body 10 (α<β, γ<β, α=γ. Or α≈γ).

On the other hand, in the guide hole 19, a sliding surface gap (intermediate large clearance β portion) formed between the intermediate annular groove portion 10g of the main valve body 10 and the inner wall surface of the guide hole 19 and a low pressure (Ps inlet/outlet 27). Four vertical grooves 19g as guide hole side grooves capable of communicating with the side are formed at 90° intervals (around the axis O).

Each vertical groove 19g is formed to be considerably deeper than the intermediate annular groove portion 10g of the main valve body 10, and the upper end thereof is opened (to the Ps inlet/outlet chamber 28 or the Ps inlet/outlet 27) and hangs along the axis O, Its axial length is U1, and its lower end portion is when the main valve body 10 is in the fully open state (in other words, when the main valve body 10 is in the lowest position) (state shown in FIG. 7). Also, in the above, the intermediate large clearance β portion of the intermediate annular groove portion 10g of the main valve body 10 is configured to overlap along the axis O direction. In this example, the overlap amount in the fully open state (when the main valve body 10 is at the lowest position) shown in FIG. 7 is Q1, and the fully closed state shown in FIG. 8 (the main valve body 10 is at the highest position). The overlap amount in (at a certain time) is set to Q2 which is about twice as large as Q1, and in the fully closed state shown in FIG. 8, the lower end of each vertical groove 19g has the intermediate annular groove 10g of the main valve body 10. It is designed to overlap with the upper half of the intermediate large clearance β portion.

Further, in this example, the total cross-sectional area of the refrigerant passage space formed by the four vertical grooves 19g (the cross-sectional area in the cross section perpendicular to the axis O. Hereinafter, referred to as "the cross-sectional area of the vertical groove 19g"). A cross-sectional area of the refrigerant passage space formed by the intermediate annular groove portion 10g (a cross-sectional area of an intermediate large clearance β portion formed between the refrigerant and the inner wall surface of the guide hole 19 in a cross section perpendicular to the axis O). The cross-sectional area of the annular groove portion 10g") is substantially equal.

Under such a configuration, the upper side of the guide hole 19 is the low pressure (Ps) side and the lower side of the guide hole 19 is the high pressure (Pd) side, and the high pressure side small clearance α of the high pressure side large diameter portion 10f from the high pressure (Pd) side. Only small foreign matters of α or less enter into the intermediate annular groove portion 10g through the. In this case, since the intermediate large clearance β of the intermediate annular groove 10g is sufficiently large, even if a small foreign matter of α or less enters and accumulates therein, it is not clogged.

The foreign matter that has entered the intermediate annular groove portion 10g is made to communicate between the intermediate annular groove portion 10g (intermediate large clearance β portion) and the low pressure (Ps) side by the vertical groove 19g serving as a guide hole side groove. It is discharged from the groove portion 10g through the vertical groove 19g to the low pressure (Ps) side.

As described above, in the control valve 1 of the present embodiment, small clearances (low pressure side large diameter portion 10h, high pressure side large diameter portion 10f) are formed at the upper and lower ends of the main valve body 10, and Since a large clearance (intermediate annular groove portion 10g) is formed in the intermediate portion and the guide hole 19 is formed with a vertical groove 19g capable of communicating the intermediate annular groove portion 10g of the main valve body 10 with the Ps inlet/outlet 27 side, While suppressing Pd-Ps leakage and the inclination of the valve body, prevent foreign matter from accumulating in the sliding surface gap (clearance) formed between the outer peripheral surface of the main valve body 10 and the inner wall surface of the guide hole 19. As a result, controllability and operational stability can be improved, and malfunctions such as valve lock and valve body leaving can be less likely to occur.

In the illustrated example, from the fully opened state shown in FIG. 7 to the fully closed state shown in FIG. 8 (that is, in the entire stroke from the fully closed to the fully opened main valve body 10), each vertical groove 19g and the intermediate annular groove portion. The intermediate large clearance β portion of 10 g overlaps along the direction of the axis O, and each vertical groove 19 g slides between the intermediate annular groove portion 10 g of the main valve body 10 and the inner wall surface of the guide hole 19. The surface gap (intermediate large clearance β portion) and the low pressure (Ps inlet/outlet 27) side are always communicated with each other, but the vertical groove 19g and the intermediate large clearance β portion of the intermediate annular groove portion 10g open the main valve body 10. It is not always necessary for the valves to overlap. However, when the main valve body 10 starts to open from the fully closed state, foreign matter flows into the intermediate annular groove portion 10g through the high-pressure side large diameter portion 10f, so that even a slight overlap is effective.

Further, when the main valve body 10 is closed, in order to make it easier for foreign matter to flow, the vertical groove 19g and the intermediate large clearance β portion of the intermediate annular groove portion 10g must always overlap.

Further, as in the present embodiment, by making the total of the cross-sectional areas of the four vertical grooves 19g and the cross-sectional area of the intermediate annular groove portion 10g substantially equal, the foreign matter that has entered the intermediate annular groove portion 10g is removed from the intermediate annular groove portion 10g. It is possible to smoothly flow (discharge) to the low pressure (Ps) side through the vertical groove 19g. The total cross-sectional area of the four vertical grooves 19g may be larger than the cross-sectional area of the intermediate annular groove portion 10g.

Further, as in the present embodiment, by making the axial length U1 of the vertical groove 19g as the guide hole side groove longer than the axial length L2 of the intermediate annular groove portion 10g (U1>L2), a small clearance portion ( Since the low-pressure side large-diameter portion 10h) becomes long, Pd-Ps leakage can be further suppressed.

On the other hand, although not shown, the axial length L2 of the intermediate annular groove portion 10g is made longer than the axial length U1 of the vertical groove 19g as the guide hole side groove (the axial length U1 of the vertical groove 19g is By making the intermediate annular groove portion 10g shorter than the axial length L2 (U1<L2), it is easier to form the annular groove in the main valve body 10 than to form the longitudinal groove in the valve body 20 side. Since the manufacturing cost can be suppressed and the number of sliding surfaces is reduced, it is difficult for hysteresis and catching to occur in the operation.

The number of the vertical grooves 19g as the guide hole side grooves may be one, or may be a plurality other than four. In addition to the vertical groove 19g extending in the axis O direction of the guide hole 19 (in other words, the moving direction of the main valve body 10), the guide hole side groove is, for example, inclined with respect to the axis O direction of the guide hole 19. The groove may be formed by an inclined groove or a spiral groove formed in the same direction, or may be formed by a notch having a triangular cross-section formed by notch processing (plastic processing). Needless to say, the position and size of the guide hole side groove can be changed as appropriate.

Further, the in-valve escape passage 16 for releasing the pressure Pc in the crank chamber to the suction chamber of the compressor through the Ps inlet/outlet 27 is not provided in the valve body 20 (for example, between the body member 20A and the seat member 20B). ) It may be provided in the main valve body 10 (see, for example, Patent Document 2 above). Needless to say, the location and shape of the sub-valve body 15 that opens and closes the in-valve escape passage 16, the connection mechanism with the plunger 37, and the like can be changed as appropriate.

Further, in the above-described embodiment, the present invention is applied to the control valve 1 including the sub-valve body 15. However, it is needless to say that the present invention can be applied to a control valve not including the sub-valve body (for example, see Patent Document 1 above). Is.

1 Control valve for variable displacement compressor 10 Main valve body 10a Main valve body section 10c Stepped sliding section 10f High pressure side large diameter section 10g Intermediate annular groove section 10h Low pressure side large diameter section 11 Main valve section 12 Sub valve section 15 Sub Valve body 16 Relief passage in valve 16A Communication passage in valve body 17 Interior member 18 Storage hole 19 Guide hole 19g Vertical groove (guide hole side groove)
20 valve body 20A body member 20B seat member 20C recessed hole 21 valve chamber 22 valve opening 23 auxiliary valve seat portion 24 fitting insertion portion 24A stopper portion 25 Pd introduction port 25s lateral hole 26 Pc entry/exit chamber (entrance/exit chamber)
27 Ps inlet/outlet 28 Ps inlet/outlet chamber 30 Electromagnetic actuator 30A Solenoid part 32 Coil 33 Stator 34 Suction element 37 Plunger 40 Bellows device (pressure sensitive member)
45 Pressure Sensing Chamber 46 Push Rod 50 Closing Spring 51 Closing Spring α High Pressure Side Small Clearance β Medium Large Clearance γ Low Pressure Side Small Clearance

Claims (10)

A main valve body having a main valve body section;
A guide hole into which the main valve body is slidably inserted; a valve chamber provided with a valve port for contacting and separating the main valve body portion; and a Ps inlet/outlet communicating with a suction chamber of a compressor, A valve body having a Pd inlet port communicating with the discharge chamber of the compressor upstream of the valve port and a Pc inlet port communicating with the crank chamber of the compressor downstream of the valve port,
An electromagnetic actuator for moving the main valve body in the opening and closing direction of the valve opening,
A pressure-sensitive chamber into which suction pressure Ps is introduced from the compressor through the Ps inlet/outlet;
A pressure-sensitive responsive member for urging the main valve element in the valve opening/closing direction in accordance with the pressure in the pressure-sensitive chamber,
The sliding portion of the main valve body has a large-diameter portion on the high-pressure side with a diameter of Da and a diameter of Db smaller than the Da, and has a predetermined axial length from the Pd inlet side to the Ps inlet/outlet side. An intermediate annular groove portion and a low-pressure side large-diameter portion having a diameter Dc larger than Db are provided, and at least when the main valve element is closed in the guide hole, the intermediate annular element in the main valve element. Variable, characterized in that one or a plurality of guide hole side grooves capable of communicating the sliding surface gap formed between the groove portion and the inner wall surface of the guide hole with the Ps inlet/outlet side are formed. Control valve for displacement type compressor. The guide hole side groove in the guide hole is formed between the intermediate annular groove portion of the main valve body and the inner wall surface of the guide hole in the entire stroke of the main valve body from fully closed to fully opened. The control valve for a variable displacement compressor according to claim 1, wherein the dynamic surface gap and the Ps inlet/outlet side can be constantly communicated with each other. The control valve for a variable displacement compressor according to claim 1 or 2, wherein an axial length of the intermediate annular groove portion is longer than an axial length of the high-pressure side large diameter portion. 4. The variable displacement compressor according to claim 3, wherein axial lengths of the high-pressure side large-diameter portion, the intermediate annular groove portion, and the low-pressure side large-diameter portion are increased in that order. Control valve. The guide hole side groove is configured by a vertical groove extending in the axial direction of the guide hole, an inclined groove or a spiral groove formed in a direction inclined with respect to the axial direction of the guide hole, or a notch. The control valve for a variable displacement compressor according to any one of claims 1 to 4. The control valve for a variable displacement compressor according to any one of claims 1 to 5, wherein an axial length of the guide hole side groove is longer than an axial length of the intermediate annular groove portion. .. The control valve for a variable displacement compressor according to any one of claims 1 to 5, wherein an axial length of the guide hole side groove is shorter than an axial length of the intermediate annular groove portion. .. 8. The control valve for a variable displacement compressor according to claim 1, wherein the guide hole side groove is formed deeper than the intermediate annular groove portion. 9. The cross-sectional area of the refrigerant passage space formed by the guide hole side groove and the cross-sectional area of the refrigerant passage space formed by the intermediate annular groove portion are made equal to each other. A control valve for a variable displacement compressor according to. An in-valve escape passage for releasing the pressure Pc in the crank chamber to the suction chamber of the compressor via the Ps inlet/outlet is provided in the valve body or in the main valve body, and the in-valve escape passage is opened/closed. A control valve for a variable displacement compressor according to any one of claims 1 to 9, characterized in that a sub valve body is provided.

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