EP1998044A2 - Steuerventil für Verdichter mit variabler Leistung und Herstellungsverfahren dafür - Google Patents

Steuerventil für Verdichter mit variabler Leistung und Herstellungsverfahren dafür Download PDF

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Publication number
EP1998044A2
EP1998044A2 EP08009440A EP08009440A EP1998044A2 EP 1998044 A2 EP1998044 A2 EP 1998044A2 EP 08009440 A EP08009440 A EP 08009440A EP 08009440 A EP08009440 A EP 08009440A EP 1998044 A2 EP1998044 A2 EP 1998044A2
Authority
EP
European Patent Office
Prior art keywords
valve
aperture
shank portion
rod
compressor
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Withdrawn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
EP08009440A
Other languages
English (en)
French (fr)
Inventor
Daisuke Morisawa
Yoshiyuki Kume
Masayuki Imai
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 EP1998044A2 publication Critical patent/EP1998044A2/de
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • 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
    • F04B2027/1854—External parameters

Definitions

  • the present invention relates to a control valve for variable capacity compressors which is designed to be employed in air conditioners for vehicles, etc., and in particular to a control valve for variable capacity compressors which is designed such that a valve rod which is slidably and snugly inserted into a guide hole can be scarcely brought into a state of malfunction, and to a method for manufacturing such a control valve.
  • the control valve for variable capacity compressors which is designed to be employed in air conditioners for vehicles, etc. is generally constructed such that a cooling medium having a discharge pressure "Pd” is permitted to enter into the crank chamber of compressor from the discharge chamber of compressor so as to adjust the pressure "Pc" inside the crank chamber.
  • the flow rate of cooling medium having a discharge pressure "Pd” to the crank chamber is restricted in such a manner that the quantity of supply (throttling volume) of cooling medium to the crank chamber is controlled depending on the suction pressure "Ps" of compressor.
  • various proposals where an electromagnetic actuator (solenoid) is employed have been suggested or put into practice as seen from JP Patent Laid-open Publication (Kokai) No. 2006-291867 .
  • FIG. 7 illustrates one example of such a conventional control valve for a variable capacity compressor.
  • the control valve 5 shown herein comprises a valve main body 20, and an electromagnetic actuator 30; wherein the valve main body 20 comprises a valve rod 15 constituted by a shank portion 15c, an intermediate small diameter (neck) portion 15b which is made smaller in diameter than the shank portion 15c, and a valve body portion 15a which is made larger in diameter than the shank portion 15c; a guide hole 19 into which the shank portion 15c of valve rod 15 can be slidably and snugly inserted; and a valve chamber 21 having a valve aperture 22 whose lower portion (valve seat portion 22a) the valve body portion 15a is enabled to detachably contact with; the valve main body 20 being further provided with a plurality of filter(25A)-attached cooling medium inlet ports 25 formed along the outer circumferential wall of the valve chamber 21 (i.e.
  • valve aperture 22 locating on an upstream side of the valve aperture 22) for receiving a cooling medium having a discharge pressure "Pd" from the compressor, and with a cooling medium outlet port 26 disposed below the valve aperture 22 (i.e. on its downstream side) and communicated with a crank chamber of the compressor.
  • This electromagnetic actuator 30 is equipped with a coil 32 having a connector 31 for electroexcitation, with a cylindrical stator 33 disposed on the inner circumferential wall side of the coil 32, with an attractor 34 having U-shaped cross-section and being press-inserted into an inner circumferential lower end portion of the stator 33, with a flange(35a)-attached pipe 35 which is joined, through an upper edge portion thereof, by means of TIG welding, to an outer circumferential lower end portion (step portion) of the stator 33, with a plunger 37 slidably disposed so as to enable itself to move up and down inside the pipe 35 and placed below the attractor 34, and with a cylindrical housing 60 with an opening in its bottom and being disposed to cover the outer circumferential wall of the coil 32.
  • a hexagon socket head adjusting screw 65 is screwed on an upper portion of the stator 33.
  • a pressure sensitive chamber 45 into which the suction pressure "Ps" of compressor is to be introduced is formed between the adjusting screw 65 and the attractor 34 in the inner circumferential wall of stator 33.
  • this pressure sensitive chamber 45 there is disposed, as a pressure sensitive actuating member, a bellows main body 40 consisting of a bellows 41, a downwardly projected upper stopper 42, a reversed U-shaped lower stopper 43 and a compression coil spring 44.
  • a compression coil spring 46 for urging the bellows main body 40 to contract is disposed between the bellows main body 40 and the attractor 34.
  • a step-attached operating rod 14 piercing through the attractor 34 is disposed between the reversed U-shaped lower stopper 43 of bellows main body 40 and a U-shaped portion 37c of plunger 37.
  • a valve-opening spring 47 made of a compression coil spring for urging the valve rod 15 downward (in the direction to open the valve) by way of the plunger 37 is disposed between the attractor 34 and the U-shaped portion 37b of plunger 37.
  • a convex stopper 28 for regulating the lowermost descending position of the plunger 37 is projected upward from an upper central portion of the valve main body 20.
  • a guide hole 19 in which the valve rod 15 is slidably and snugly inserted is formed at a central portion of valve main body 20 over the valve chamber, this guide hole 19 being formed also piercing through the convex stopper 28.
  • a suction pressure cooling medium-introducing chamber 23 for enabling a cooling medium of suction pressure of the compressor to be introduced therein is formed between the plunger 37 and an upper outer circumferential wall of the valve main body 20 (an outer circumferential wall of the convex stopper 28).
  • a plurality of suction pressure cooling medium-introducing ports 27 are formed in the outer circumferential wall of the suction pressure-introducing chamber 23.
  • a cooling medium of suction pressure "Ps" that has been introduced into the suction pressure cooling medium-introducing chamber 23 from the cooling medium-introducing ports 27 is designed to be introduced into the pressure sensitive chamber 45 via longitudinal grooves 37a, 37a, ... formed on the outer circumferential wall of plunger 37, via a communication hole 37d formed at a central axis of plunger 37 and via a communication hole 39 formed in the attractor 34.
  • a valve-closing spring 48 made of a conical compression spring for urging the valve rod 15 upward is disposed at a lower portion (a cooling medium outlet port 26) of the valve main body 20.
  • a lower flange portion 35a of the pipe 35 is mounted, through an 0-ring 57, on an upper end of the valve main body 20.
  • a flange (56a)-attached short cylindrical pipe holder 56 is disposed between the flange portion 35a and the coil 32.
  • These flange portions 35a and 56a are both fixed to each other by means of the upper outer circumferential caulking portion 29 of the valve main body 20.
  • An open bottom portion 61 of the housing 60 is press-inserted in and fixed to an upper end portion of the pipe holder 56.
  • An upper end portion 62 of the housing 60 is calked to the flange portion 31c of the connector 31.
  • An O-ring 66 is interposed between the housing 60 and the connector 31 and the coil 32.
  • a recessed portion 31a in which a projected portion 31b to be engaged with the hexagonal hole of the adjusting screw 65 is formed.
  • An upper portion of the stator 33 as well as an upper portion of the adjusting screw 65 is inserted into this recessed portion 31a.
  • the bellows main body 40 (the interior thereof is kept in vacuum) is caused to displace, i.e. contract or expand depending on the pressure (the suction pressure "Ps") inside the pressure sensitive chamber 45 (when the suction pressure "Ps" is high, the bellows main body 40 is contracted, and when the suction pressure "Ps" is low, the bellows main body 40 is expanded). Then, this displacement is transmitted, via the operating rod 14 and the plunger 37, to the valve rod 15, thereby making it possible to adjust the degree of opening of valve (the lifting height of the valve body portion 15a from the valve seat portion 22a of valve aperture 22).
  • the degree of opening of valve will be determined depending on the attracting force of the plunger 37 to be effected by the solenoid portion consisting of the coil 32, the stator 33 and the attractor 34, on the urging force of the bellows main body 40, on the urging force of the valve-opening spring 47 and the valve-closing spring 48, and on the load in the valve-opening direction and the load in the valve-closing direction to be imposed by the discharge pressure "Pd" on the valve rod 15. Further, depending on this degree of opening of valve, the magnitude of restriction of cooling medium of discharge pressure "Pd" that has been introduced from the discharge pressure cooling medium inlet port 25 into the valve chamber 21, i.e.
  • the quantity of cooling medium to be introduced into the crank chamber (magnitude of restriction) can be adjusted.
  • the pressure "Pc" of cooling medium outlet port 26 side (hereinafter referred to as an outlet port pressure Pc), i.e. the pressure inside the crank chamber, can be controlled.
  • Pc outlet port pressure
  • the inclination angle of the wobble plate of compressor as well as the stroke of piston can be adjusted, thus increasing or decreasing the quantity of cooling medium to be discharged.
  • the conventional control valve 5 for variable capacity compressors is accompanied with the following problems to be overcome.
  • this control valve 5 is constructed such that the discharge pressure cooling medium inlet port 25 is provided on the upstream side of the valve aperture 22 and the cooling medium outlet port 26 is provided on the downstream side of the valve aperture 22, and that the valve body portion 15a is provided at an lower end portion of the shank portion 15c of valve rod 15 and designed to open and close the valve aperture 22 through the movement thereof from the underside of valve aperture 22, thus enabling the discharge pressure "Pd" to be acted on the valve rod 15.
  • the discharge pressure cooling medium inlet port 25 is provided on the upstream side of the valve aperture 22 and the cooling medium outlet port 26 is provided on the downstream side of the valve aperture 22, and that the valve body portion 15a is provided at an lower end portion of the shank portion 15c of valve rod 15 and designed to open and close the valve aperture 22 through the movement thereof from the underside of valve aperture 22, thus enabling the discharge pressure "Pd" to be acted on the valve rod 15.
  • the bore diameter "Da" of valve aperture 22 is made slightly larger than the outer diameter "Db" of the shank portion 15c so as to enable the shank portion 15c of valve rod 15 to be inserted from the underside of valve aperture 22.
  • the outer diameter "Dc" of the valve body portion 15a is made larger than the bore diameter "Da” of valve aperture 22 (Db ⁇ Da ⁇ Dc).
  • an object of the present invention is to provide a control valve for a variable capacity compressor, which makes it possible to obviate any adverse influence on the control of compressor that may be caused by the discharge pressure "Pd" without sophisticating the structure.
  • Another object of the present invention is to provide a method of manufacturing such a control valve.
  • a control valve for a variable capacity compressor which fundamentally comprises a valve main body constituted by a valve rod having a shank portion, an intermediate small diameter portion which is made smaller in diameter than the shank portion, and a valve body portion which is made larger in diameter than the shank portion, by a guide hole into which the shank portion of valve rod can be slidably and snugly inserted, and by a valve chamber having a valve aperture with which the valve body portion is enabled to detachably contact, the valve main body being further provided with a discharge pressure cooling medium inlet port which is disposed on an upstream side of the valve aperture and designed to receive a cooling medium having a discharge pressure "Pd" from the compressor, and with a cooling medium outlet port which is disposed on a downstream side of the valve aperture and communicated with a crank chamber of the compressor; an electromagnetic actuator for driving the valve rod to move in the direction of opening or closing the valve aperture; and a
  • valve body portion is formed contiguous to the lower side of the intermediate small diameter portion of valve rod and designed to be moved from the underside of the valve aperture so as to close or open the valve aperture.
  • the bore diameter of the valve aperture is set so as to enable the shank portion of valve rod to pass therethrough but, after the assembling of valve, the effective aperture area thereof is reduced.
  • valve aperture is provided, on the underside thereof, with a valve seat with which the valve body portion can be detachably contacted, this valve seat being restricted in bore diameter as compared with an upper portion of the valve aperture.
  • the outer peripheral portion of the valve seat is beaten or pressed by making use of a punch, etc. so as to reduce the bore diameter thereof.
  • the effective aperture area of the valve aperture is set to such that the suction pressure (Ps) can be maintained at approximately a constant value or slightly lowered even when the discharge pressure "Pd" is increased.
  • the effective aperture area of the valve aperture is set to such that the load in the valve-opening direction to be imposed by the discharge pressure (Pd) on the valve rod becomes approximately the same as the load in the valve-closing direction, or such that the load in the valve-closing direction becomes slightly larger than the load in the valve-opening direction.
  • the method of manufacturing a control valve for a variable capacity compressor is directed to the manufacture of a control valve for a variable capacity compressor comprising a valve main body constituted by a valve rod having a shank portion, an intermediate small diameter portion which is made smaller in diameter than the shank portion, and a valve body portion which is made larger in diameter than the shank portion, by a guide hole into which the shank portion of valve rod can be slidably and snugly inserted, and by a valve chamber having a valve aperture with which the valve body portion is enabled to detachably contact, the valve main body being further provided with a discharge pressure cooling medium inlet port which is disposed on an upstream side of the valve aperture and designed to receive a cooling medium having a discharge pressure (Pd) from the compressor, and with a cooling medium outlet port which is disposed on a downstream side of the valve aperture and communicated with a crank chamber of the compressor; an electromagnetic actuator for driving the valve rod to move in the direction of opening or closing the valve aperture; and
  • the outer peripheral portion of the valve seat provided on a lower end portion of the valve aperture is beaten or pressed by making use of a punch, etc. so as to reduce the bore diameter thereof.
  • the bore diameter of valve aperture is made larger than the outer diameter of the shank portion of valve before the assembling of the control valve so as to enable the shank portion to pass through the valve aperture from underside of the valve aperture, and, at the same time, the outer diameter of valve body portion is made larger than the bore diameter of valve aperture in order to open or close the valve aperture from the underside of valve aperture by means of this valve body portion (i.e. the valve body portion is enabled to detachably contact with the valve seat which is provided on an lower end portion of valve aperture).
  • the valve body portion is enabled to detachably contact with the valve seat which is provided on an lower end portion of valve aperture.
  • the outer peripheral portion of the valve seat is beaten or pressed from the underside thereof by making use of a punch, etc. so as to reduce the bore diameter of valve seat, thereby reducing the effective aperture area of the valve aperture.
  • FIG. 1 shows a longitudinal sectional view illustrating one embodiment of the control valve for a variable capacity compressor according to the present invention.
  • the parts or components which correspond to those of the conventional control valve 5 for a variable capacity compressor which is shown in FIG. 7 will be identified by the same reference numbers and the features which differ from those of the conventional control valve 5 will be mainly explained as follows.
  • the bore diameter "Da" of valve aperture 22 is made slightly larger than the outer diameter "Db" of the shank portion 15c of valve rod so as to enable the shank portion 15c of valve rod 15 to pass through the valve aperture 22 from underside of the valve aperture 22, and, at the same time, the outer diameter "Dc" of valve body portion 15a is made larger than the bore diameter "Da" of valve aperture 22 in order to open or close the valve aperture 22 from the underside of valve aperture 22 by means of this valve body portion 15a (i.e.
  • valve body portion 15a is enabled to detachably contact with the valve seat 22a which is provided on an lower end portion of valve aperture 22).
  • a step is executed so as to reduce the effective aperture area of the valve aperture 22 as described below.
  • valve rod 15 is urged upward by means of the valve-closing spring 48 to push the valve rod against the plunger 37 in the aforementioned conventional control valve
  • this embodiment is featured in that the valve rod 15 is formed integral with the operating rod 14, that the valve-closing spring 48 is not employed, and that an annular groove portion (small diameter portion) 15d is formed at a boundary region between the shank portion 15c of valve rod 15 and the large diameter portion 14b (which is the same in diameter as the shank portion 15c) of operating rod 14, and an engaging portion 38 which is provided at a bottom portion of hole 37g of the plunger 37 is fitted in the annular groove portion 15d, thereby enabling the plunger 37 to move up and down together with the movement of valve rod 15.
  • valve rod 15 when the control valve is constructed such that the valve rod 15 is enabled to move in the valve-closing direction by means of only the urging force of the valve-closing spring 48, foreign material may be caught in the slide-contacting interface between the valve rod 15 and the guiding hole 19, or the sliding resistance of valve rod 15 may be caused to increase due to the oil-seizing, etc., thereby giving rise to the malfunctioning of the valve rod 15 such as locking of valve rod 15. For example, there may be generated a situation wherein the valve rod 15 cannot be moved in the valve-closing direction and is left behind even if the plunger is pulled close to the attractor.
  • valve rod 15 is substantially directly connected with the plunger as described above, it is possible to obviate the aforementioned problems and, at the same time, it is possible to dispense with the valve-closing spring 48.
  • valve aperture 22 After finishing the assembling of valve, i.e. after the insertion of the operating rod 14 as well as the shank portion of valve rod 15, via the valve aperture 22, into the guide hole 19, a cylindrical punch 80 is introduced into the coolant discharge port 26 formed below the valve aperture 22 as shown in FIG. 2(B) . Then, by making use of an annular molding portion 81 having a wedge-like or triangular cross-section and projected from the top end face of the punch 80, a lower end portion of the valve aperture 22 (or the outer peripheral portion of the valve seat portion 22a disposed below the lower end portion of the valve aperture 22) is beaten from the underside of valve seat portion 22a.
  • the outer diameter "Dm” and inner diameter “Dn” of the punch 80 are dimensioned such that the punch 80 can be slidably inserted into an annular space defined by both the inner wall of the coolant discharge port 26 and the outer wall of valve body portion 15a. Further, the diameter of the distal end of annular molding portion 81 is set larger, by a predetermined dimension, than the bore diameter "Da” of valve aperture (or the bore diameter of the valve seat portion 22a disposed below the lower end portion of the valve aperture 22).
  • the annular molding portion 81 is enabled to thrust into the lower end portion of the valve aperture 22 (or the outer peripheral portion of the valve seat portion 22a), thereby creating an annular recessed portion 22c and, at the same time, pushing the lower end portion (or the valve seat portion 22a) inwards to reduce the bore diameter of the valve seat portion 22a as shown in FIG.2 (C) and FIG.3(A) .
  • valve seat portion 22a that has been pushed inwards and reduced in inner diameter is made smaller than the bore diameter "Da” of upper portion of valve aperture 22 (Dd ⁇ Db ⁇ Da ⁇ Dc), thus reducing the effective aperture area of valve aperture 22.
  • valve aperture 22 Since the effective aperture area of valve aperture 22 is reduced as described above, as shown in FIG. 3(B) , the load in the valve-closing direction (lifting force) "A" to be imposed on the valve rod 15 by the discharge pressure "Pd” would become the same level as that of conventional control valve shown in FIG. 4 (corresponding to the outer diameter "Db" of shank portion 15c).
  • the load in the valve-opening direction "B' " to be imposed on the valve rod 15 by the discharge pressure "Pd" can be made approximately the same in level as the load in the valve-closing direction "A", or the load in the valve-closing direction "A” can be set slightly larger than the load in the valve-opening direction "B' ".
  • the punch 80 is employed for reducing the effective aperture area of the valve aperture 22.
  • the punch 80 is employed for reducing the effective aperture area of the valve aperture 22.

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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)
EP08009440A 2007-06-01 2008-05-23 Steuerventil für Verdichter mit variabler Leistung und Herstellungsverfahren dafür Withdrawn EP1998044A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007147091A JP2008298013A (ja) 2007-06-01 2007-06-01 可変容量型圧縮機用制御弁及びその製造方法

Publications (1)

Publication Number Publication Date
EP1998044A2 true EP1998044A2 (de) 2008-12-03

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EP08009440A Withdrawn EP1998044A2 (de) 2007-06-01 2008-05-23 Steuerventil für Verdichter mit variabler Leistung und Herstellungsverfahren dafür

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EP (1) EP1998044A2 (de)
JP (1) JP2008298013A (de)
KR (1) KR20080105996A (de)
CN (1) CN101315072A (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2474737A3 (de) * 2011-01-07 2014-12-17 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
EP3020671A1 (de) 2014-11-17 2016-05-18 Lisa Dräxlmaier GmbH Methode und Vorrichtung zum Sammeln einer Leitung
EP3020672A1 (de) 2014-11-17 2016-05-18 Lisa Dräxlmaier GmbH Vorrichtung zum Aufwickeln eines biegeschlaffen strangförmigen Elements und Verfahren dazu
DE102015220693A1 (de) 2015-10-22 2017-04-27 Lisa Dräxlmaier GmbH Vorrichtung zum Legen eines biegeschlaffen, strangförmigen Elements und Verfahren dazu
US10253760B2 (en) 2012-05-02 2019-04-09 Nuovo Pignone Srl Adjusting opening times of a cam actuated valve, reciprocating compressor and method

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6395696B2 (ja) * 2015-12-16 2018-09-26 株式会社不二工機 可変容量型圧縮機用制御弁
JP6632503B2 (ja) * 2016-09-30 2020-01-22 株式会社不二工機 可変容量型圧縮機用制御弁
KR102100294B1 (ko) * 2018-11-19 2020-04-13 동일기계공업 주식회사 이물질 끼임 방지를 위한 가변용량 압축기용 제어밸브
US12264744B2 (en) * 2020-09-28 2025-04-01 Eagle Industry Co., Ltd. Valve

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006291867A (ja) 2005-04-12 2006-10-26 Fuji Koki Corp 可変容量型圧縮機用制御弁

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006291867A (ja) 2005-04-12 2006-10-26 Fuji Koki Corp 可変容量型圧縮機用制御弁

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2474737A3 (de) * 2011-01-07 2014-12-17 TGK CO., Ltd. Regelventil für einen Verdichter mit variabler Verdrängung
US8956127B2 (en) 2011-01-07 2015-02-17 Tgk Co., Ltd. Control valve for variable displacement compressor
US10253760B2 (en) 2012-05-02 2019-04-09 Nuovo Pignone Srl Adjusting opening times of a cam actuated valve, reciprocating compressor and method
EP3020671A1 (de) 2014-11-17 2016-05-18 Lisa Dräxlmaier GmbH Methode und Vorrichtung zum Sammeln einer Leitung
EP3020672A1 (de) 2014-11-17 2016-05-18 Lisa Dräxlmaier GmbH Vorrichtung zum Aufwickeln eines biegeschlaffen strangförmigen Elements und Verfahren dazu
DE102015220693A1 (de) 2015-10-22 2017-04-27 Lisa Dräxlmaier GmbH Vorrichtung zum Legen eines biegeschlaffen, strangförmigen Elements und Verfahren dazu

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KR20080105996A (ko) 2008-12-04
JP2008298013A (ja) 2008-12-11
CN101315072A (zh) 2008-12-03

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