EP3181904A1 - Soupape de commande de compresseur à capacité variable - Google Patents

Soupape de commande de compresseur à capacité variable Download PDF

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Publication number
EP3181904A1
EP3181904A1 EP16195709.7A EP16195709A EP3181904A1 EP 3181904 A1 EP3181904 A1 EP 3181904A1 EP 16195709 A EP16195709 A EP 16195709A EP 3181904 A1 EP3181904 A1 EP 3181904A1
Authority
EP
European Patent Office
Prior art keywords
valve element
valve
sub
plunger
pressure
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP16195709.7A
Other languages
German (de)
English (en)
Inventor
Yoshiyuki Kume
Hisashi Asano
Masaki Tomaru
Masaharu Itoh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
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 Fujikoki Corp filed Critical Fujikoki Corp
Publication of EP3181904A1 publication Critical patent/EP3181904A1/fr
Withdrawn legal-status Critical Current

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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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • 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
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1013—Adaptations or arrangements of distribution members the members being of the poppet valve type
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1818—Suction pressure
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1845—Crankcase pressure
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a variable-capacity compressor control valve for use in an automotive air conditioner or the like.
  • variable-capacity swash plate compressor such as the one schematically shown in FIG. 9 has been used as a compressor for an automotive air conditioner.
  • the variable-capacity swash plate compressor 100 includes a rotating shaft 101 that is rotationally driven by an on-vehicle engine, a swash plate 102 that is attached to the rotating shaft 101, a crank chamber 104 in which the swash plate 102 is disposed, a piston 105 that is reciprocated by the swash plate 102, a discharge chamber 106 for discharging refrigerant compressed by the piston 105, a suction chamber 107 for sucking refrigerant, an in-compressor release passage (fixed orifice) 108 for releasing a pressure Pc in the crank chamber 104 to the suction chamber 107, and the like.
  • a control valve 1' used for the aforementioned variable-capacity compressor receives the discharge pressure Pd from the discharge chamber 106 of the compressor 100 and is configured to control the pressure Pc in the crank chamber 104 by controlling the discharge pressure Pd in accordance with the suction pressure Ps of the compressor 100.
  • Such a control valve 1' has, as the basic configuration, a valve body that includes a valve chamber with a valve orifice, a Ps introduction port communicating with the suction chamber 107 of the compressor 100, a Pd introduction port arranged upstream of the valve orifice and communicating with the discharge chamber 106 of the compressor 100, and a Pc outlet port arranged downstream of the valve orifice and communicating with the crank chamber 104 of the compressor 100; a valve element (valve stem) for opening or closing the valve orifice; an electromagnetic actuator with a plunger for moving the valve element in the direction to open or close the valve orifice (in the vertical direction); a pressure-sensitive chamber that receives the suction pressure Ps from the compressor 100 via the Ps introduction port; and a pressure-sensitive reaction member that urges the valve element in the direction to open or close the valve orifice in accordance with the pressure in the pressure-sensitive chamber.
  • the valve element and the valve orifice form a valve unit indicated by reference numeral 11' in FIG. 9 (for example
  • the plunger when current is flowed through a solenoid portion including a coil, a stator, an attractor, and the like of the electromagnetic actuator, the plunger is attracted by the attractor, and along with this, the valve element is moved in the direction to close the valve such that it follows the plunger by the urging force of a valve closing spring. Meanwhile, the suction pressure Ps introduced from the compressor 100 via the Ps introduction port is introduced into the pressure-sensitive chamber from an inlet/outlet chamber via a gap formed between the plunger and a guide pipe arranged around the outer periphery of the plunger or the like.
  • the pressure-sensitive reaction member e.g., a bellows device
  • the pressure-sensitive reaction member is expansively or contractively displaced in accordance with the pressure (suction pressure Ps) in the pressure-sensitive chamber (contracts if the suction pressure Ps is high, and expands if it is low), and the displacement (urging force) is then transmitted to the valve element, whereby the valve element portion of the valve element moves up or down with respect to the valve orifice to regulate the valve opening of the valve unit 11'.
  • the valve opening is determined by the force of attracting the plunger with the solenoid portion, the urging force (expansion or contraction force) that acts with the expansive or contractive displacement of the pressure-sensitive reaction member, the urging force of a plunger spring (valve opening spring) and the valve closing spring.
  • the pressure Pc in the crank chamber 104 (hereinafter also referred to as a crank chamber pressure Pc or simply referred to as a pressure Pc) is controlled in accordance with the valve opening.
  • variable-capacity swash plate compressor In response to the aforementioned variable-capacity compressor, an improved variable-capacity swash plate compressor, such as the one schematically shown in FIGS. 10A and 10B , for example, has already been proposed that is intended to reduce the time required to increase the discharge capacity at the compressor actuation time, and suppress or reduce a decrease in the operation efficiency of the compressor at the normal control time.
  • a control valve 2' used for such an improved variable-capacity swash plate compressor 200 has a valve element (valve stem) including a main valve element and a sub valve element, and has an in-valve release passage 16' in the main valve element.
  • the control valve 2' basically has a valve body that includes a valve chamber with a valve orifice, a Ps inlet/outlet port communicating with a suction chamber 107 of the compressor 200, a Pd introduction port arranged upstream of the valve orifice and communicating with a discharge chamber 106 of the compressor 200, and a Pc inlet/outlet port arranged downstream of the valve orifice and communicating with a crank chamber 104 of the compressor 200; a main valve element for opening or closing the valve orifice; an electromagnetic actuator with a plunger for moving the main valve element in the direction to open or close the valve orifice; a pressure-sensitive chamber that receives the suction pressure Ps from the compressor 200 via the Ps inlet/outlet port; and a pressure-sensitive
  • the in-valve release passage 16' for releasing the pressure Pc in the crank chamber 104 to the suction chamber 107 of the compressor 200 via the Ps inlet/outlet port is provided in the main valve element, and the sub valve element for opening or closing the in-valve release passage 16' is also provided so that when the plunger is continuously moved upward from the lowest position by the attraction force of the electromagnetic actuator, the sub valve element moves upward together with the plunger while closing the in-valve release passage 16', and the main valve element is also moved upward so as to follow the sub valve element. Then, after the valve orifice is closed by the main valve element, if the plunger is further moved upward, the sub valve element is configured to open the in-valve release passage 16'.
  • the main valve element and the valve orifice form a main valve unit indicated by reference numeral 11' in FIGS. 10A and 10B
  • the sub valve element and the in-valve release passage form a sub valve unit indicated by reference numeral 12' (for example, see Patent Document 2 below).
  • the suction pressure Ps introduced from the compressor 200 via the Ps inlet/outlet port is introduced into the pressure-sensitive chamber from an inlet/outlet chamber via a horizontal hole in the plunger or the like, and the pressure-sensitive reaction member (e.g., a bellows device) is expansively or contractively displaced in accordance with the pressure (suction pressure Ps) in the pressure-sensitive chamber (contracts if the suction pressure Ps is high, and expands if it is low), and the displacement (urging force) is then transmitted to the main valve element, whereby the main valve element portion of the main valve element moves up or down with respect to the valve orifice to regulate the valve opening of the main valve unit 11'.
  • the pressure-sensitive reaction member e.g., a bellows device
  • the valve opening is determined by the force of attracting the plunger with the solenoid portion, the urging force (expansion or contraction force) that acts with the expansive or contractive displacement of the pressure-sensitive reaction member, the urging force of a plunger spring (valve opening spring) and the valve closing spring, and force that acts on the main valve element in the valve opening direction and in the valve closing direction.
  • the pressure Pc in the crank chamber 104 is controlled in accordance with the valve opening.
  • the main valve element is always urged upward by the urging force of the valve closing spring, while the sub valve element is always urged downward by the urging force of the valve opening spring.
  • the sub valve unit 12' is closed and the in-valve release passage 16' is blocked in the main valve element. Therefore, there is no possibility that the crank chamber pressure Pc may be released to the suction chamber 107 via the in-valve release passage 16'.
  • a sub valve element portion of the sub valve element that opens or closes the in-valve release passage has a flat shape, and the sub valve element is guided so as not to be tilted by a predetermined amount or more upon insertion into an insertion hole of a latch member that is fixed to the inner peripheral portion of the plunger.
  • the present invention has been made in view of the foregoing, and it is an object of the present invention to provide a variable-capacity compressor control valve where a decrease in the sealability or the operability due to shaft misalignment can be effectively suppressed without requiring high dimensional accuracy.
  • a variable-capacity compressor control valve in accordance with the present invention basically includes a valve body including a valve chamber with a valve orifice, a Ps inlet/outlet port communicating with a suction chamber of a compressor, a Pd introduction port arranged upstream of the valve orifice and communicating with a discharge chamber of the compressor, and a Pc inlet/outlet port arranged downstream of the valve orifice and communicating with a crank chamber of the compressor; a main valve element adapted to open or close the valve orifice; an electromagnetic actuator with a plunger for moving the main valve element in a direction to open or close the valve orifice; a pressure-sensitive chamber adapted to receive a suction pressure Ps from the compressor via the Ps inlet/outlet port; a pressure-sensitive reaction member adapted to urge the main valve element in the direction to open or close the valve orifice in accordance with a pressure in the pressure-sensitive chamber; an in-valve release passage provided in the main valve
  • the sub valve element has a sub valve element portion with a tapered portion, and dimensions and a shape of each part are designed such that when the sub valve element closes the in-valve release passage, the tapered portion enters the in-valve release passage, and the sub valve element is thus aligned with the main valve element by the tapered portion.
  • part of the tapered portion is located in the in-valve release passage when the sub valve element is at the highest elevated position with respect to the main valve element.
  • the sub valve element is preferably supported by the pressure-sensitive reaction member at an end portion on a side opposite to the sub valve element portion, and is pressed against the plunger by a plunger spring such that the sub valve element moves up or down with the plunger.
  • the tapered portion has a protrusion that extends toward the in-valve release passage.
  • a sub valve element has a sub valve element portion with a tapered portion, and the dimensions and the shape of each part are designed such that when the sub valve element closes the in-valve release passage, the tapered portion enters the in-valve release passage, and the sub valve element is thus aligned with the main valve element by the tapered portion. Therefore, in comparison with the conventional art in which a sub valve element portion of a sub valve element has a flat shape, it is possible to effectively suppress a decrease in the sealability or the operability due to shaft misalignment without requiring high dimensional accuracy.
  • the tapered portion As part of the tapered portion is located in the in-valve release passage even when the sub valve element is at the highest elevated position with respect to the main valve element, the tapered portion surely enters the in-valve release passage when the sub valve element closes the in-valve release passage. Thus, further relaxation of the dimensional accuracy can also be achieved.
  • FIGS. 1 to 3 are longitudinal sectional views each showing the first embodiment of the variable-capacity compressor control valve in accordance with the present invention.
  • FIG. 1 is a view in which the main valve element is in the open position and the sub valve element is in the closed position (at the normal control time)
  • FIG. 2 is a view in which the main valve element is in the closed position and the sub valve element is in the closed position (at the time of transition to compressor actuation)
  • FIG. 3 is a view in which the main valve element is in the closed position and the sub valve element is in the open position (at the compressor actuation time).
  • a control valve 1 in the shown embodiment has a valve body 20 with a valve orifice 22; a valve element 10 with a main valve element 15 for opening or closing the valve orifice 22; an electromagnetic actuator 30 for moving the valve element 10 (main valve element 15) in the direction to open or close the valve orifice (in the vertical direction); and a bellows device 40 that serves as a pressure-sensitive reaction member.
  • the electromagnetic actuator 30 includes a bobbin 38, an energization coil 32 wound around the bobbin 38, a connector head 31 attached to the upper side of the bobbin 38 with an attachment plate 39 interposed therebetween, a stator 33 and an attractor 34 arranged on the inner peripheral side of the coil 32, a guide pipe 35 whose upper end portion is joined by welding to the outer periphery of the lower end portion (a step portion) of the stator 33 and the attractor 34, a plunger 37 having a recessed cross section and arranged vertically slidably on the inner peripheral side of the guide pipe 35 below the attractor 34, a cylindrical housing 60 externally arranged around the coil 32, and a holder 29 arranged between the lower end portion of the housing 60 and the guide pipe 35 and adapted to fix them to the top of the valve body 20.
  • the attractor 34 with a recessed cross section is integrally molded with the inner periphery of the bottom of the cylindrical stator 33.
  • a portion of the electromagnetic actuator 30 including the coil 32, the stator 33, the attractor 34, and the like and excluding the plunger 37 is referred to as a solenoid portion 30A.
  • a stator 65 in a short columnar shape is attached to the top of the stator 33 by press fitting or the like, and a pressure-sensitive chamber 45, which receives a suction pressure Ps in a compressor 100, is formed between the stator 65 and the attractor 34 on the inner peripheral side of the stator 33.
  • the pressure-sensitive chamber 45 has arranged therein the bellows device 40 that serves as a pressure-sensitive reaction member and includes bellows 41, an upper stopper 42 in an inverted projection shape, a lower stopper 43 in an inverted recessed shape, and a compression coil spring 44.
  • a top small-diameter portion 17d (an end portion on the side opposite to a sub valve element portion 17a) of a sub valve element 17 described below is fitted and inserted in and supported by the recess of the lower stopper 43, and a compression coil spring 46, which urges the bellows device 40 in the direction to contract the bellows device 40, is provided in a compressed state between the lower stopper 43 and the attractor 34.
  • the plunger 37 has a cylindrical upper half portion 37A and a columnar lower half portion 37B.
  • a columnar lower half portion 37B Provided in the center of the columnar lower half portion 37B is an insertion hole 37b through which a waist portion 17b of the sub valve element 17 that extends downward through the attractor 34 and a top small-diameter portion 15f (described in detail below) of the main valve element 15 are inserted.
  • the outer peripheral portion of the insertion hole 37b on the upper surface of the columnar lower half portion 37B serves as a latch portion 37a to which an intermediate large-diameter latch portion 17c of the sub valve element 17 is latched.
  • a plunger spring (valve opening spring) 47 constructed from a cylindrical compression coil spring, which urges the sub valve element 17 and the plunger 37 downward (in the direction to open the valve), is provided in a compressed state between the attractor 34 and the intermediate large-diameter latch portion 17c of the sub valve element 17 (plunger 37) so that the sub valve element 17 (or the intermediate large-diameter latch portion 17c thereof) is pressed against the plunger 37 by the plunger spring 47 and thus is caused to move up or down with the plunger 37.
  • the bottom of the columnar lower half portion 37B of the plunger 37 (a portion that is above the lower end portion by a predetermined distance) has a cut-in 37t with an approximately semicircular shape in plan view (in the horizontal direction) that is formed so as to overlap the insertion hole 37b.
  • a slit 37s with approximately the same width as the hole diameter of the insertion hole 37b is formed that extends linearly from the edge portion at the lower end of the columnar lower half portion 37B to the insertion hole 37b.
  • the height (in the vertical direction) of the cut-in 37t is slightly larger than the height of a flanged latch portion 15k of the main valve element 15, and the height (in the vertical direction) of the slit 37s is slightly smaller than the height of the top small-diameter portion 15f of the main valve element 15.
  • the main valve element 15 is movable in the vertical direction with respect to the plunger 37 (which will be described in detail below).
  • the width (in the horizontal direction) of the slit 37s is set slightly larger than the outside diameter of the top small-diameter portion 15f of the main valve element 15 and smaller than the outside diameter of the flanged latch portion 15k of the main valve element 15 taking into consideration the assembling properties and the like.
  • the valve element 10 has the main valve element 15 and the sub valve element 17 arranged in the vertical direction (along the direction of the axial line O).
  • the main valve element 15 arranged on the lower side has, sequentially arranged from the bottom side, a bottom fit-insertion portion 15b, a lower small-diameter portion 15c, a main valve element portion 15a, an intermediate small-diameter portion 15d, a top fit-insertion portion 15e, the top small-diameter portion 15f, and the flanged latch portion 15k.
  • a stepped release through-hole 16A forming part of an in-valve release passage 16 is provided in the center of the main valve element 15 such that it penetrates the center of the main valve element 15 in the vertical direction, and the upper end portion of the release through-hole 16A serves as a sub valve seat portion 23 with/from which the lower end portion (sub valve element portion) 17a of the sub valve element 17 is moved into contact or away.
  • the intermediate small-diameter portion 15d of the main valve element 15 has a plurality of horizontal holes 16s.
  • the top small-diameter portion 15f of the main valve element 15 is loosely fitted in the insertion hole 37b (or a portion below the cut-in 37t thereof), and the flanged latch portion 15k of the main valve element 15 has a larger diameter than that of the insertion hole 37b so that when the plunger 37 is moved upward with respect to the main valve element 15, the flanged latch portion 15k is lathed to an inner flanged latch portion 37k that is formed by the outer peripheral portion of the insertion hole 37b, and thus, latching is achieved and slippage is prevented.
  • the sub valve element 17 arranged above the main valve element 15 has, sequentially arranged from the bottom side, an inverted conical tapered portion 17a, which is moved into contact with or away from the sub valve seat portion 23 that is the edge portion at the upper end of the release through-hole 16A, the waist portion 17b having the intermediate large-diameter latch portion 17c formed thereon, a truncated conical portion 17e, and a top small-diameter portion 17d that is inserted in and supported by the recess of the lower stopper 43.
  • the tapered portion 17a serves as the sub valve element portion that opens or closes the in-valve release passage 16.
  • the sub valve seat portion 23 and the sub valve element portion 17a form the sub valve unit 12.
  • a portion below the intermediate large-diameter latch portion 17c of the waist portion 17 is inserted into the insertion hole 37b of the plunger 37 with a small gap therebetween, and a portion above the intermediate large-diameter latch portion 17c and below the attractor (a portion arranged inside the cylindrical upper half portion 37A) has a slightly larger diameter than those of the other portions.
  • each part around the sub valve element 17 e.g., a gap between the waist portion 17b and the insertion hole 37b
  • the dimensions and the shape of each part around the sub valve element 17 are designed such that even when the sub valve element 17 is slightly tilted at a position where it has been moved upward with respect to the main valve element 15 (i.e., a position where the in-valve release passage 16 is open), the lower end portion of the sub valve element portion (a tapered portion) 17a in an inverted conical shape enters the release through-hole 16A, and the sub valve element 17 is thus aligned with the main valve element 15 by the sub valve element portion 17a as the sub valve element 17 moves closer to the main valve element 15 (i.e., when the sub valve element 17 closes the in-valve release passage 16).
  • each part are designed such that part of the sub valve element portion 17a in an inverted conical shape is located in the release through-hole 16A when the sub valve element 17 is at the highest elevated position with respect to the main valve element 15 (see FIG. 3 , in particular).
  • the main valve element 15 When the valve element 10 (the main valve element 15 and the sub valve element 17) and the plunger 37 are assembled, for example, the main valve element 15 is moved horizontally with respect to the plunger 37 so that the flanged latch portion 15k and the top small-diameter portion 15f of the main valve element 15, which has been assembled in advance to the valve body 20 (or a guide hole 19 thereof), are inserted into the cut-in 37t and the slit 37s of the plunger 37, respectively, and the top small-diameter portion 15f is fitted and inserted into the insertion hole 37b provided in the center of the plunger 37, and thereafter, the sub valve element 17 (or a portion below the intermediate large-diameter latch portion 17c thereof) may be inserted into the insertion hole 37b from above.
  • valve body 20 has a two-split structure that includes a body member 20A having a fit recess hole 20C in the center at the top thereof, and a support member 20B that is fixedly inserted into the recess hole 20C by press fitting or the like.
  • the support member 20B is produced from a material with relatively high hardness, such as stainless steel (SUS), and has a protruding stopper portion 24A for defining the lowest position of the plunger 37, on the upper side of a fit-insertion portion 24 that is fitted and inserted in the recess hole 20C.
  • the guide hole 19 an upper guide hole 19A into which the top fit-insertion portion 15e of the main valve element 15 is slidably fitted and inserted is formed in the center of the support member 20B such that it penetrates the support member 20B in the vertical direction, and the lower end portion of the upper guide hole 19A serves as the valve orifice 22 (a valve seat portion) that is opened or closed by the main valve element portion 15a of the main valve element 15.
  • the main valve element portion 15a and the valve orifice 22 form a main valve unit 11.
  • the support member 20B is produced from a material with high hardness, such as stainless steel, as described above, the specific gravity of the support member 20B is also high.
  • the body member 20A is produced from a material, such as aluminum, brass, or resin, that has relatively low specific gravity (a material with relatively low hardness) as compared to stainless steel and the like.
  • An inlet/outlet chamber 28 for the suction pressure Ps in the compressor 100 is formed around the outer periphery of the stopper portion 24A, and a plurality of Ps inlet/outlet ports 27 are formed around the outer peripheral side of the inlet/outlet chamber 28 in a state in which the support member 20B (or the fit-insertion portion 24 thereof) is inserted in the recess hole 20C of the body member 20A.
  • the suction pressure Ps introduced into the inlet/outlet chamber 28 from the Ps inlet/outlet ports 27 is introduced into the pressure-sensitive chamber 45 via the slit 37s and the cut-in 37t formed at the bottom of the plunger 37, a gap formed between the waist portion 17b of the sub valve element 17 and the insertion hole 37b of the plunger 37, a gap 36 formed between the outer periphery of the plunger 37 and the guide pipe 35, and the like.
  • a reception hole 18, which has a larger diameter than those of the guide hole 19 and the main valve element portion 15a and has a smaller diameter than that of the recess hole 20C and is adapted to store the main valve element portion 15a of the main valve element 15, is provided continuously with the center of the bottom of the recess hole 20C of the body member 20A, and the guide hole 19 (a lower guide hole 19B) into which the bottom fit-insertion portion 15b of the main valve element 15 is slidably fitted and inserted is formed in the center of the bottom of the reception hole 18.
  • a valve closing spring 50 constructed form a conical compression coil spring is provided in a compressed state between the corner on the outer periphery of the bottom of the reception hole 18 and a stepped portion (terrace portion) 15g provided on the outer periphery of the bottom of the main valve element portion 15a of the main valve element 15.
  • the inside of the reception hole 18 (a portion below the valve orifice 22 of the support member 20B) is the valve chamber 21.
  • the valve chamber 21 has a plurality of Pd introduction ports 25 communicating with a discharge chamber 106 of the compressor 100.
  • a ring-like filter member 25A is arranged around the outer periphery of the Pd introduction ports 25 of the body member 20A.
  • the lower end portion of the body member 20A has a lid-like member 48, which functions as a filter, fixed thereto by engagement, press fitting, or the like.
  • a Pc inlet/outlet chamber (inlet/outlet port) 26 which communicates with a crank chamber 104 of the compressor 100, is provided on the side above the lid-like member 48 below the main valve element 15.
  • the Pc inlet/outlet chamber (inlet/outlet port) 26 communicates with the Pd introduction ports 25 via the release through-hole 16A ⁇ the horizontal holes 16s ⁇ a gap between the bottom of the upper guide hole 19A and the intermediate small-diameter portion 15d ⁇ a gap between the valve orifice 22 and the main valve element portion 15a ⁇ the valve chamber 21.
  • the in-valve release passage 16 for releasing the pressure Pc in the crank chamber 104 to a suction chamber 107 of the compressor 100 via the Ps inlet/outlet ports 27 is formed by the release through-hole 16A formed in the main valve element 15, the cut-in 37t and the slit 37s provided in the plunger 37, the inlet/outlet chamber 28, and the like.
  • the in-valve release passage 16 is adapted to be opened or closed as the sub valve element portion 17a of the sub valve element 17 is moved into contact with or away from the sub valve seat portion 23 that is the upper end portion of the release through-hole 16A of the main valve element 15.
  • the clearance in the vertical direction between the main valve element portion 15a of the main valve element 15 and the valve orifice 22 (valve seat portion) is represented by a first lift amount Lv
  • the clearance between the inner flanged latch portion 37k of the plunger 37 and the flanged latch portion 15k of the main valve element 15 is represented by a predetermined amount La.
  • the maximum lift amount (second lift amount) Lp of the plunger 37 corresponds to the first lift amount Lv + the predetermined amount La.
  • the lift amount of the plunger 37 is slightly greater than the first lift amount Lv at the maximum, and at the compressor actuation time (Pc ⁇ Ps control time), the lift amount of the plunger 37 is the second lift amount Lp.
  • the suction pressure Ps introduced into the Ps inlet/outlet ports 27 from the compressor 100 is introduced into the pressure-sensitive chamber 45 from the inlet/outlet chamber 28 via the slit 37s and the cut-in 37t of the plunger 37 and the like, and the bellows device 40 (the inside thereof is at a vacuum pressure) is expansively or contractively displaced in accordance with the pressure (suction pressure Ps) in the pressure-sensitive chamber 45 (contracts if the suction pressure Ps is high, and expands if it is low), and the displacement is then transmitted to the main valve element 15 via the plunger 37 and the sub valve element 17, whereby the valve opening (the clearance between the valve orifice 22 and the main valve element portion 15a) is regulated, and the pressure Pc in the crank chamber 104 is controlled in accordance with the valve opening.
  • the inclination angle of the swash plate 102 and the stroke of the piston 105 in the compressor 100 are controlled to increase or decrease the discharge capacity.
  • the main valve element 15 is always urged upward by the urging force of the valve closing spring 50, while the sub valve element 17 is always urged downward by the urging force of the valve opening spring 47. Therefore, the sub valve element portion 17a is in a state of being pressed against the sub valve seat portion 23 (the sub valve unit 12 is closed), and the in-valve release passage 16 is blocked in the main valve element 15. Therefore, there is no possibility that the crank chamber pressure Pc may be released to the suction chamber 107 via the in-valve release passage 16.
  • the solenoid portion 30A is supplied with current and energized, and the plunger 37 is attracted by the attractor 34 so that the sub valve element 17 moves upward together with the plunger 37.
  • the main valve element 15 is also moved upward and the valve orifice 22 is closed by the main valve element portion 15a of the main valve element 15.
  • the plunger 37 is further moved upward, whereby the sub valve element 17 is caused to open the in-valve release passage 16.
  • the pressure Pc in the crank chamber 104 is released into the suction chamber 107 via two passages that are an in-compressor release passage 108 and the in-valve release passage 16.
  • the main valve element 15 moves in the direction to close the valve such that it follows the upward movement of the plunger 37 and the sub valve element 17 by the urging force of the valve closing spring 50. Then, when the upward movement amount reaches the first lift amount Lv, the valve orifice 20 is closed by the main valve element portion 15a of the main valve element 15 (the state shown in FIG. 2 ), and the plunger 37 is further moved upward by the predetermined amount La with the main valve unit 11 in the closed valve state (the state shown in FIG. 3 ).
  • the main valve element 15 remains still in the closed valve state.
  • the sub valve element portion 17a of the sub valve element 17 is lifted from the sub valve seat portion 23 by the predetermined amount La, whereby the in-valve release passage 16 is opened.
  • each part are designed such that when the sub valve element 17 closes the in-valve release passage 16, the tapered portion (sub valve element portion) 17a provided at the lower end portion of the sub valve element enters the release through-hole 16A of the in-valve release passage 16, and the sub valve element 17 is thus aligned with the main valve element 15 by the tapered portion 17a. Therefore, in comparison with the conventional art in which a sub valve element portion of a sub valve element has a flat shape, it is possible to effectively suppress a decrease in the sealability or the operability due to shaft misalignment without requiring high dimensional accuracy.
  • the tapered portion 17a As part of the tapered portion 17a is located in the release through-hole 16A of the in-valve release passage 16 even when the sub valve element 17 is at the highest elevated position with respect to the main valve element 15 (the state shown in FIG. 3 ), the tapered portion 17a surely enters the release through-hole 16A of the in-valve release passage 16 when the sub valve element 17 closes the in-valve release passage 16. Thus, further relaxation of the dimensional accuracy can also be achieved.
  • a protrusion 17t which extends downward (toward the release through-hole 16A of the in-valve release passage 16), may also be provided at the tip end portion of the sub valve element portion 17a of the sub valve element 17 for guiding purposes to allow the lower end portion of the sub valve element portion 17a of the sub valve element 17 to easily enter the release through-hole 16A.
  • FIGS. 6 to 8 are longitudinal sectional views each showing the second embodiment of the variable-capacity compressor control valve in accordance with the present invention.
  • FIG. 6 is a view in which the main valve element is in the open position and the sub valve element is in the closed position (at the normal control time);
  • FIG. 7 is a view in which the main valve element is in the closed position and the sub valve element is in the closed position (at the time of transition to compressor actuation),
  • FIG. 8 is a view in which the main valve element is in the closed position and the sub valve element is in the open position (at the compressor actuation time).
  • the control valve 2 in the second embodiment basically differs from the control valve 1 in the aforementioned first embodiment only in the configurations of the valve body and the main valve element of the valve element.
  • configurations with the same functions as those in the first embodiment are denoted by the same reference numerals and the detailed description thereof will thus be omitted.
  • only the differences will be discussed in detail.
  • the top fit-insertion portion 15e and the intermediate small-diameter portion 15d of the main valve element 15 are formed longer than those of the control valve 1 in the first embodiment, while the lower small-diameter portion 15c and the bottom fit-insertion portion 15b on the lower side of the main valve element portion 15a are omitted.
  • the fit-insertion portion 24 of the support member 20B of the valve body 20 has a step formed thereon, and at a position below an upper large-diameter portion 24a (an outer shape corresponding to the fit-insertion portion 24 in the first embodiment), a lower small-diameter portion 24b, which is longer than the upper large-diameter portion 24a in the vertical direction, is provided, and at a lower end of the lower small-diameter portion 24b, a flanged abutment portion 24c adapted to abut the stepped portion (terrace portion) between the recess hole 20C and the reception hole 18 of the body member 20A is provided such that it protrudes outward.
  • the recess hole 20C of the body member 20A of the valve body 20 also has a step formed thereon, and has an upper large-diameter hole 20Ca (an outer shape corresponding to the recess hole 20C in the first embodiment) into which the upper large-diameter portion 24a is fitted and inserted, and a lower small-diameter hole 20Cb into which the lower small-diameter portion 24b is fitted and inserted, and further has a stepped reception hole 18 for storing the main valve element portion 15a of the main valve element 15 in a manner continuous with the center of the bottom of the lower small-diameter hole 20Cb.
  • a valve closing spring 50 constructed from a conical compression coil spring is provided in a compressed state between the stepped portion provided on the inner periphery of the reception hole 18 and the stepped portion (terrace portion) 15g provided on the outer periphery of the bottom of the main valve element portion 15a of the main valve element 15.
  • the inside of the reception hole 18 (a portion below the valve orifice 22 of the support member 20B) is the valve chamber 21.
  • the lower small-diameter hole 20Cb in the recess hole 20C has a plurality of Pd introduction ports 25 communicating with the discharge chamber 106 of the compressor 100.
  • a ring-like filter member 25A is arranged around the outer periphery of the Pd introduction ports 25 thereof, and the lower small-diameter portion 24b of the fit-insertion portion 24 (instead of the intermediate small-diameter portion 15d of the main valve element 15) has a plurality of horizontal holes 25a communicating with the Pd introduction ports 25.
  • the outer periphery of the upper large-diameter portion 24a abuts the inner periphery of the upper large-diameter hole 20Ca (that is, the upper large-diameter portion 24a is fitted into (fits snugly inside) the upper large-diameter hole 20Ca), and the support member 20B is fixedly inserted into the recess hole 20C of the body member 20A in a posture in which a small gap is provided between the outer periphery of the lower small-diameter portion 24b and the inner periphery of the lower small-diameter hole 20Cb.
  • control valve 2 in the second embodiment with the aforementioned configuration can also obtain operational effects that are similar to those of the control valve 1 in the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Magnetically Actuated Valves (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP16195709.7A 2015-12-16 2016-10-26 Soupape de commande de compresseur à capacité variable Withdrawn EP3181904A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2015245030A JP2017110544A (ja) 2015-12-16 2015-12-16 可変容量型圧縮機用制御弁

Publications (1)

Publication Number Publication Date
EP3181904A1 true EP3181904A1 (fr) 2017-06-21

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EP16195709.7A Withdrawn EP3181904A1 (fr) 2015-12-16 2016-10-26 Soupape de commande de compresseur à capacité variable

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US (1) US20170175725A1 (fr)
EP (1) EP3181904A1 (fr)
JP (1) JP2017110544A (fr)
KR (1) KR20170072144A (fr)
CN (1) CN106884773A (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
EP3650695A4 (fr) * 2017-07-05 2021-03-31 Eagle Industry Co., Ltd. Soupape de commande de capacité
EP3650696A4 (fr) * 2017-07-06 2021-04-07 Eagle Industry Co., Ltd. Soupape de commande de capacité

Families Citing this family (4)

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JP6355617B2 (ja) * 2015-12-16 2018-07-11 株式会社不二工機 可変容量型圧縮機用制御弁
JP6600603B2 (ja) * 2016-06-28 2019-10-30 株式会社不二工機 可変容量型圧縮機用制御弁及びその組立方法
WO2019135335A1 (fr) * 2018-01-05 2019-07-11 株式会社不二工機 Électrovanne
JP6708911B2 (ja) * 2018-02-08 2020-06-10 株式会社不二工機 可変容量型圧縮機用制御弁

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EP2020507A2 (fr) * 2007-08-03 2009-02-04 Fujikoki Corporation Soupape de contrôle pour un compresseur à capacité variable
JP2010185285A (ja) 2009-02-10 2010-08-26 Fuji Koki Corp 制御弁
EP2410220A2 (fr) * 2010-07-21 2012-01-25 Fujikoki Corporation Soupape de contrôle pour compresseur de déplacement variable
EP2426358A2 (fr) * 2010-09-06 2012-03-07 Fujikoki Corporation Soupape de contrôle de compresseur à déplacement variable
JP2013130126A (ja) 2011-12-21 2013-07-04 Fuji Koki Corp 可変容量型圧縮機用制御弁

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JP6108673B2 (ja) * 2011-12-21 2017-04-05 株式会社不二工機 可変容量型圧縮機用制御弁
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Publication number Priority date Publication date Assignee Title
EP1650435A1 (fr) * 2004-10-22 2006-04-26 TGK Co., Ltd. Soupape de contrôle pour un compresseur à capacité variable
EP2020507A2 (fr) * 2007-08-03 2009-02-04 Fujikoki Corporation Soupape de contrôle pour un compresseur à capacité variable
JP2010185285A (ja) 2009-02-10 2010-08-26 Fuji Koki Corp 制御弁
EP2410220A2 (fr) * 2010-07-21 2012-01-25 Fujikoki Corporation Soupape de contrôle pour compresseur de déplacement variable
EP2426358A2 (fr) * 2010-09-06 2012-03-07 Fujikoki Corporation Soupape de contrôle de compresseur à déplacement variable
JP2013130126A (ja) 2011-12-21 2013-07-04 Fuji Koki Corp 可変容量型圧縮機用制御弁

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3650695A4 (fr) * 2017-07-05 2021-03-31 Eagle Industry Co., Ltd. Soupape de commande de capacité
EP3650696A4 (fr) * 2017-07-06 2021-04-07 Eagle Industry Co., Ltd. Soupape de commande de capacité

Also Published As

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KR20170072144A (ko) 2017-06-26
US20170175725A1 (en) 2017-06-22
CN106884773A (zh) 2017-06-23
JP2017110544A (ja) 2017-06-22

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