WO2020110427A1 - Soupape de commande pour compresseur à cylindrée variable - Google Patents

Soupape de commande pour compresseur à cylindrée variable Download PDF

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Publication number
WO2020110427A1
WO2020110427A1 PCT/JP2019/036058 JP2019036058W WO2020110427A1 WO 2020110427 A1 WO2020110427 A1 WO 2020110427A1 JP 2019036058 W JP2019036058 W JP 2019036058W WO 2020110427 A1 WO2020110427 A1 WO 2020110427A1
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WO
WIPO (PCT)
Prior art keywords
valve body
guide hole
main valve
valve
inlet
Prior art date
Application number
PCT/JP2019/036058
Other languages
English (en)
Japanese (ja)
Inventor
慎太郎 田野
恒 浅野
伊東　雅晴
駿 坂本
Original Assignee
株式会社不二工機
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社不二工機 filed Critical 株式会社不二工機
Publication of WO2020110427A1 publication Critical patent/WO2020110427A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves

Definitions

  • 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.
  • 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.
  • 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
  • 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.
  • variable displacement compressor control valve allows the pressure Pc of the crank chamber to escape to the suction chamber of the compressor via the Ps inlet/outlet.
  • 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.
  • the sub valve body opens the in-valve escape passage.
  • the main valve body that opens and closes the valve opening is slidably inserted into a guide hole provided in the valve body.
  • 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.
  • 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).
  • Pd-Ps leakage causes performance deterioration, and therefore it is required to suppress it as much as possible. Therefore, from the viewpoint of suppressing leakage of Pd-Ps, it is required to reduce the sliding surface gap, and it is further desired to increase the sliding portion (its axial length).
  • the valve body is likely to tilt and the operation becomes unstable. From this viewpoint as well, it is desirable to reduce the sliding surface gap.
  • 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.
  • a control valve for a variable displacement compressor 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.
  • 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.
  • 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.
  • 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.
  • the axial length of the intermediate annular groove portion is longer than the axial length of the high pressure side large diameter portion.
  • 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 comprises 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 axial length of the guide hole side groove is longer than the axial length of the intermediate annular groove portion.
  • the axial length of the guide hole side groove is shorter than the axial length of the intermediate annular groove portion.
  • the guide hole side groove is formed deeper than the intermediate annular groove portion.
  • 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.
  • 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.
  • the high pressure side small clearance ⁇ 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 ⁇ is formed therebetween, and a low pressure side small clearance ⁇ is formed between the inner wall surface of the guide hole and the low pressure side large diameter portion of the main valve body ( ⁇ , ⁇ ).
  • the intermediate annular groove portion from the high pressure (Pd) side via the high pressure side small clearance ⁇ of the high pressure side large diameter portion. Only small foreign matters of ⁇ or less intrude into the. In this case, since the intermediate large clearance ⁇ of the intermediate annular groove is sufficiently large, even if a small foreign matter of ⁇ or less enters and accumulates therein, it will not be clogged.
  • 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).
  • 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 and the Ps inlet/outlet side to communicate with each other is formed in the guide hole. Therefore, Pd-Ps leakage and the inclination of the valve body can be suppressed, and foreign matter can be prevented from accumulating in the sliding surface clearance (clearance) formed between the main valve body and the guide hole. And the operational stability can be improved, and malfunctions such as valve lock and valve body leaving can be less likely to occur.
  • 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. 1 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
  • 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 OU 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. 6 is an enlarged cross-sectional view of the main part of FIG. 1, taken along the line VV 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.
  • FIG. 1 shows a state in which a main valve is open and a sub valve is closed (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)
  • FIG. 4 shows a main valve: closed, a sub valve: an open state (when the compressor starts).
  • FIG. 5 is a cross-sectional view taken along the line UU of FIG. 1
  • FIG. 6 is a perspective view showing a main valve body 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
  • FIG. 8 is an enlarged sectional view of the main part of FIG. 2 taken along the line VV of FIG.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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-sensitive 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 arranged 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 46d of the push rod 46 is fitted and supported in the recess of the lower stopper 43.
  • the upper portion of the push rod 46 and the large diameter portion 46b are inserted (with a slight gap 34b) into the insertion hole 34a of the suction element 34.
  • the lower portion of the push rod 46 is inserted into a recessed hole 17b of the interior member 17 having a recessed cross-section described later.
  • a lower end portion 46a of the push rod 46 is fitted in a concave fitting insertion hole 17c formed at the center of the bottom portion of the concave hole 17b.
  • 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.
  • 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.
  • a recessed insertion hole 17c into which the lower end 46a of the push rod 46 is inserted is formed.
  • 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.
  • the bottom of the plunger 37 is formed with a slit 37s extending linearly from the outer periphery to the center (on the axis O).
  • a notch 37t which is wider than the slit 37s, is provided in the side portion of the plunger 37 corresponding to the slit 37s.
  • the height of the notch 37t (in the vertical direction) is set to be slightly larger than the height of the collar-shaped locking portion 10k of the main valve body 10.
  • the height of the slit 37s (in the vertical direction) (that is, the thickness of the bottom of the plunger 37 (the height in the vertical direction)) is made slightly smaller than the height of the upper small diameter portion 10d of the main valve body 10.
  • the main valve body 10 can move up and down with respect to the plunger 37 (detailed later). Further, the width of the notch 37t (in the circumferential direction) is made slightly larger than the outer diameter of the collar-shaped locking portion 10k of the main valve body 10. The width of the slit 37s (in the lateral direction) is made slightly larger than the outer diameter of the upper small diameter portion 10d of the main valve body 10 in consideration of the assemblability and the like, and the collar-shaped locking portion 10k of the main valve body 10 is provided. Is smaller than the outer diameter of. An outer peripheral portion of the slit 37s on the upper surface of the bottom of the plunger 37 serves as an inner collar-shaped hooking portion 37k for hooking the collar-shaped locking portion 10k of the main valve body 10.
  • 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.
  • 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).
  • 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.
  • 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, for example, a metal, 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
  • stepped sliding portion 10c The details of the stepped sliding portion 10c will be described later along with the guide hole 19 provided in the valve body 20.
  • the stepped sliding portion 10c of the main valve body 10 (the upper end portion protruding upward from the guide hole 19 thereof) is inserted into the cylindrical leg portion 37a provided on the lower surface of the plunger 37.
  • the upper small diameter portion 10d is loosely fitted in the slit 37s.
  • the collar-shaped locking portion 10k is loosely fitted inside the plunger 37 below the interior member 17 (in other words, a space between the bottom of the plunger 37 and the lower end of the interior member 17).
  • 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.
  • 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.
  • 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.
  • the lower end portion of the guide hole 19 serves as a valve opening 22 (valve seat portion) that is opened and closed by the main valve body portion 10a of the main valve body 10.
  • the main valve body 11 is composed of the main valve body portion 10 a and the valve opening 22.
  • the seat member 20B (and the cylindrical portion 15b of the sub-valve body 15 described later) (the outer diameter thereof) (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.
  • 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.
  • 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. 50 is disguised.
  • the biasing force of the valve closing spring 50 pushes the main valve body 10 (the stepped portion between the stepped sliding portion 10c and the upper small diameter portion 10d) against the plunger 37 (the lower surface thereof).
  • 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 hole 20C, and a ring-shaped filter member 25A is arranged on the outer periphery of the Pd introducing ports 25.
  • a ring-shaped filter member 25A is arranged on the outer periphery of the Pd introducing ports 25.
  • a plurality of lateral holes 25s communicating 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.
  • An upper side of the lid-shaped member 48 and a lower side of the accommodation hole 18 serve as a Pc inlet/outlet chamber (inlet/outlet) 26 communicating 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.
  • 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.
  • a vertical groove 16b whose lower end opens to the valve chamber 21 (and 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.
  • an annular recess 16a continuous with the vertical groove 16b is formed on the upper inner circumference of the main body member 20A (in other words, the upper end portion of the recess 20C).
  • the vertical groove 16b (extending in the vertical direction) and the (circumferential) annular recess 16a form a communication passage 16A in the valve body that connects the Pc inlet/outlet chamber 26 and the Ps inlet/outlet chamber 28.
  • 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.
  • 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 tubular portion 15b serves as a sub valve body portion 15a that opens and closes the in-valve escape passage 16 by coming into contact with and separating from the sub valve seat portion 23 which is an upper end edge portion of the in-valve communication passage 16A. ..
  • the sub-valve seat portion 23 and the sub-valve body portion 15a constitute the sub-valve portion 12.
  • a flange-shaped lower spring receiving portion 15c is provided (outwardly) in a protruding manner on the lower end portion of the tubular portion 15a.
  • a flange-shaped upper spring receiving portion 20c is projectingly provided on the upper end portion (inner periphery) of (the body member 20A of) the valve body 20.
  • An inverted cone that urges the sub valve body 15 downward (in the valve closing direction to close the valve escape passage 16 (the valve main body communication passage 16A)) between the lower spring receiving portion 15c and the upper spring receiving portion 20c.
  • a valve-closing spring 51 which is a compression coil spring, is compressed.
  • the upper end of (the tubular portion 15b of) the sub valve body 15 is positioned above the stopper portion 24A (the upper end thereof) by a predetermined dimension.
  • the stopper 15j is provided so as to project inward.
  • 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 engaging 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.
  • 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.
  • 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 is formed for escape to the suction chamber of the compressor via 27.
  • 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
  • the maximum lift amount (third lift amount) Lc (>Lb) 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.
  • control valve 1 Next, the operation of the control valve 1 configured as described above will be outlined.
  • the lift amount of the plunger 37 is at most the first lift amount La at the maximum.
  • the lift amount of the plunger 37 is set to the third lift amount Lc.
  • the bellows 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 in the pressure-sensitive chamber 45 (suction pressure Ps), and the displacement is the push rod 46 or the interior member. It is transmitted to the main valve body 10 via the 17 and the plunger 37. Thereby, the valve opening (separation distance between the valve opening 22 and the main valve body portion 10a) is adjusted, and the crank chamber pressure Pc is adjusted according to the valve opening.
  • 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. It is not stopped (because of Lb>La), and the sub valve body 15 is always urged downward by the urging force of the valve closing spring 51. Therefore, the sub-valve body portion 15a is pressed against the sub-valve seat portion 23 (the sub-valve portion 12 is closed), and 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.
  • 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 10a of 10, the plunger 37 is further moved upward. As a result, the sub valve body 15 opens the in-valve escape passage 16, and the pressure Pc in the crank chamber is released to the suction chamber through the in-valve escape passage 16.
  • 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. Moving.
  • 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).
  • 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).
  • 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.
  • 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). ).
  • the inner flange-shaped hooking portion 37k of the plunger 37 is locked by the flange-shaped locking portion 10k of the main valve body 10, that is, the plunger 37 is further extended by Lx-(Lb-La).
  • 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.
  • 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).
  • 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.
  • the stepped sliding portion 10c is sequentially arranged from bottom to 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.
  • 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).
  • a small clearance ⁇ on the high pressure side (for example, about 8 to 20 ⁇ m, which is close to the processing limit) is formed between the inner wall surface of the guide hole 19 having a constant hole diameter (inner diameter) and the large diameter portion 10f on the high pressure side of the main valve body 10.
  • a large intermediate clearance ⁇ (for example, about 100 ⁇ m 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 sliding surface gap (intermediate large clearance ⁇ 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).
  • the intermediate large clearance ⁇ 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.
  • 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.
  • 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 ⁇ 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.
  • 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 ⁇ of the high pressure side large diameter portion 10f from the high pressure (Pd) side.
  • Ps low pressure
  • Pd high pressure
  • the intermediate large clearance ⁇ of the intermediate annular groove 10g is sufficiently large, even if a small foreign matter of ⁇ 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 ⁇ 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.
  • 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 A large clearance (intermediate annular groove portion 10g) is formed in the intermediate portion, and a vertical groove 19g that allows the intermediate annular groove portion 10g of the main valve body 10 and the Ps inlet/outlet 27 side to communicate with each other is formed in the guide hole 19. Therefore, while suppressing Pd-Ps leakage and the inclination of the valve body, foreign matter does not accumulate 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.
  • each vertical groove 19g and the intermediate annular groove portion 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 ⁇ 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 (medium large clearance ⁇ portion) and the low pressure (Ps inlet/outlet 27) side are always communicated.
  • the vertical groove 19g and the intermediate large clearance ⁇ portion of the intermediate annular groove portion 10g do not necessarily have to overlap each other when the main valve body 10 is opened.
  • 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.
  • the vertical groove 19g and the intermediate large clearance ⁇ portion of the intermediate annular groove portion 10g must always overlap.
  • 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.
  • the axial length U1 of the vertical groove 19g as the guide hole side groove is made longer than the axial length L2 of the intermediate annular groove portion 10g (U1>L2), a small clearance portion ( Since the large-diameter portion 10h) on the low-pressure side becomes long, the leakage of Pd-Ps can be further suppressed.
  • 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.
  • 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.
  • 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.
  • the present invention is applied to the control valve 1 including the sub-valve body 15.
  • the present invention can be applied to a control valve not including the sub-valve body (for example, see Patent Document 1 above). Is.
  • 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 Housing 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 entrance/exit chamber (entrance/exit) 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 Sensitive Chamber 46 Push Rod 50 Valve Closing Spring 51 Valve Closing Spring ⁇ High Pressure Side Small Clearance ⁇ Medium Large Clearance ⁇ Low Pressure Side Small Clearance

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Valve Housings (AREA)

Abstract

La présente invention concerne une soupape de commande pour un compresseur à cylindrée variable qui minimalise toute fuite côté Pd-Ps et toute inclinaison du corps de soupape et qui est en mesure d'empêcher toute matière étrangère de s'accumuler dans un espace entre des surfaces coulissantes, espace qui est formé entre un corps de soupape principal et un trou de guidage, et, par conséquent, qui est en mesure de rendre moins probable la survenue de défaillances de fonctionnement, telles que le blocage de soupape ou le déplacement du corps de soupape principal par rapport à sa position, sans donner lieu à une réduction de la contrôlabilité ou de la stabilité de fonctionnement. Une partie du corps de soupape principal 10 qui coulisse par rapport à un trou de guidage 19 comporte, en séquence depuis un côté orifice d'entrée de guidage Pd 26 jusqu'à un côté entrée/sortie Ps 27, une partie de grand diamètre côté haute pression 10f ayant un diamètre Da, une partie de rainure annulaire intermédiaire 10g ayant un diamètre Db inférieur à Da et une longueur axiale prédéterminée, et une partie de grand diamètre côté basse pression 10h ayant un diamètre Dc supérieur à Db. Quand au moins le corps de soupape principal 10 ferme le trou de guidage 19, une ou plusieurs rainures longitudinales 19g sont formées, qui servent de rainures côté trou de guidage qui permettent la communication entre le côté entrée/sortie Ps 27 et un espace de surface coulissante (partie β de jeu important intermédiaire) formé entre la partie de rainure annulaire intermédiaire 10g dans le corps de soupape principal 10 et la surface de paroi intérieure du trou de guidage 19.
PCT/JP2019/036058 2018-11-28 2019-09-13 Soupape de commande pour compresseur à cylindrée variable WO2020110427A1 (fr)

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JP2018-221886 2018-11-28
JP2018221886A JP2020084904A (ja) 2018-11-28 2018-11-28 可変容量型圧縮機用制御弁

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003301773A (ja) * 2002-04-09 2003-10-24 Sanden Corp 可変容量圧縮機の容量制御弁
JP2006291864A (ja) * 2005-04-12 2006-10-26 Fuji Koki Corp 可変容量型圧縮機用制御弁
WO2016104390A1 (fr) * 2014-12-25 2016-06-30 イーグル工業株式会社 Vanne de régulation de volume
JP2018003884A (ja) * 2016-06-28 2018-01-11 株式会社不二工機 可変容量型圧縮機用制御弁
JP2018053855A (ja) * 2016-09-30 2018-04-05 株式会社不二工機 可変容量型圧縮機用制御弁

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003301773A (ja) * 2002-04-09 2003-10-24 Sanden Corp 可変容量圧縮機の容量制御弁
JP2006291864A (ja) * 2005-04-12 2006-10-26 Fuji Koki Corp 可変容量型圧縮機用制御弁
WO2016104390A1 (fr) * 2014-12-25 2016-06-30 イーグル工業株式会社 Vanne de régulation de volume
JP2018003884A (ja) * 2016-06-28 2018-01-11 株式会社不二工機 可変容量型圧縮機用制御弁
JP2018053855A (ja) * 2016-09-30 2018-04-05 株式会社不二工機 可変容量型圧縮機用制御弁

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