EP0771948B1 - Dispositif de réglage de la capacité d'un compresseur à capacité variable - Google Patents

Dispositif de réglage de la capacité d'un compresseur à capacité variable Download PDF

Info

Publication number
EP0771948B1
EP0771948B1 EP96103572A EP96103572A EP0771948B1 EP 0771948 B1 EP0771948 B1 EP 0771948B1 EP 96103572 A EP96103572 A EP 96103572A EP 96103572 A EP96103572 A EP 96103572A EP 0771948 B1 EP0771948 B1 EP 0771948B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve portion
control device
chamber
capacity control
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.)
Expired - Lifetime
Application number
EP96103572A
Other languages
German (de)
English (en)
Other versions
EP0771948A1 (fr
Inventor
Hisatoshi Hirota
Naoyuki Ito
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.)
TGK Co Ltd
Original Assignee
TGK Co Ltd
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 TGK Co Ltd filed Critical TGK Co Ltd
Priority to US08/629,606 priority Critical patent/US5702235A/en
Publication of EP0771948A1 publication Critical patent/EP0771948A1/fr
Application granted granted Critical
Publication of EP0771948B1 publication Critical patent/EP0771948B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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

Definitions

  • the present invention relates to a capacity control device for a variable-capacity compressor used to compress a refrigerant in a refrigerating plant for an automotive air conditioning equipment, etc, according to the preamble part of claim 1.
  • a prior-art compressor for use with a refrigerating plant of an automotive air conditioning equipment is driven by the engine of the automobile.
  • the rotational speed of the compressor cannot be controlled individually because the compressor is directly coupled to the engine through a belt.
  • a variable-capacity compressor capable of changing the refrigerant capacity discharge amount is used.
  • Such compressors are adapted to provide high specific capacity with low speed and low specific capacity with high speed.
  • a rocking plate the inclination angle of which is variable, is generally driven by rotational motion of a rotating shaft for rocking motion in an airtight crank case.
  • a piston which reciprocates by the rocking motion of the rocking member, sucks refrigerant from a suction chamber into a cylinder for compression and discharges it into a discharge chamber.
  • a difference between the pressure in the crank case and the pressure in the suction chamber changes the inclination angle of the rocking member to hereby change the discharge amount of refrigerant.
  • a capacity control device is provided in order to change the inclination angle of the rocking plate when needed.
  • the high-pressure valve portion of the device serves for opening or closing the communication between the discharge chamber and the crank case.
  • the low-pressure valve portion serves for opening or closing the communication between the suction chamber and the crank case. Both valve portions conventionally are opened or closed by an electromagnetic solenoid reversing the open/close relationship between both valves upon actuation.
  • the pressure in the discharge chamber into which the compressed refrigerant is discharged may be at as high a pressure as, for example, about 30 Bar, it is necessary to have appropriately strong current to flow through the electromagnetic coil of the driving electromagnetic solenoid to open the high-pressure valve portion in communication with the discharge chamber against this high pressure.
  • the flow of large currents causes the electromagnetic coil to generate considerable heat. This may cause a defect such as refrigerant leakage when, for example, a sealing O-ring is deteriorated by the heat.
  • a capacity control device having the feature combination of claim 1.
  • the capacity control device for a compressor having a rocking member provided as to vary its inclination angle with respect to a rotating shaft in an airtight crank case, said rocking member being driven by rotational motion of the rotating shaft for rocking motion, and a piston connected to the rocking member, for discharging a refrigerant into a discharge chamber after sucking the refrigerant from a suction chamber into a cylinder for compression by reciprocating, said device serving for controlling the capacity of the variable-capacity compressor in which the inclination angle of the rocking member is changed by means of the difference between a pressure in the crank case and a pressure in the suction chamber to thereby change the discharge amount of the refrigerant, the following structural features are provided:
  • the pressure controlled by the pilot valve portion is used to actuate the operating member in the opening sense of the high pressure valve portion and with relatively high force.
  • High pressure acting on the high pressure valve portion in closing direction needs said relatively high force at the operating member to overcome the closing force.
  • This high force is generated without direct assistance by the solenoid, but instead by a servo-effect of the pressure acting in opening direction on the operating member.
  • the relatively low opening force of the pilot valve portion and a moderate control flow rate through the pilot valve position lead to a precise control of the servo-effect, and consequently of the reciprocating operation of the high pressure valve portion and low pressure valve portion and finally of the variation of the compressor capacity. It is possible to use a compact, lightweight and inexpensive solenoid, because the solenoid is assisted by the servo-effect which uses the inherent pressure capacity of the high pressure refrigerant in the system.
  • a rotating shaft 11 is mounted in an airtight crank case 12 of a variable capacity compressor 10 and is rotatively driven by a driving pulley 13.
  • a rocking plate 14 is disposed in the crank case 12 on shaft 11 in inclined fashion with respect to the rotating shaft 11, and is rocked by the rotation of the rotating shaft 11.
  • a piston 17 is coupled to the rocking plate 14 through a rod 18.
  • the piston 17 reciprocates in the cylinder 15 to suck refrigerant into the cylinder 15 from a suction chamber 20 formed upstream of the cylinder 15, and to discharge it into a discharge chamber 21 downstream after a refrigerant is compressed in the cylinder 15.
  • a block 31 housing a capacity control device 30 is formed e.g. in the same block as the variable-capacity compressor 10.
  • a body cylinder 32 is fitted in a coaxial stepped bore formed in block 31, a body cylinder 32 is fitted.
  • O-rings 33 serve for sealing between portions of the block 31 and fitting portions of the body cylinder 32.
  • hollow operating rod 35 In a through-hole formed along the center axis of the body cylinder 32, there is disposed hollow operating rod 35 defining an opening/closing valve member which is free to advance or retreat axially.
  • a high-pressure valve portion 36 is formed between the head or upper end position of the operating rod 35 and the body cylinder 32.
  • the high-pressure valve portion 36 is adapted to open or close a communicating path between a high-pressure communicating path 37 leading to the discharge chamber 21 at high pressure pressure Pd and a pressurising flow path 38 leading to the crank case 12.
  • the discharge chamber 21 communicates with the crank case 12 to increase the pressure in the crank case 12.
  • the inlet portion to the high-pressure valve portion 36 is covered with a filter 39 for removing dust, etc.
  • a low-pressure valve portion 41 which is adapted to open or close a communicating path between a pressure reducing flow path 42 leading to the crank case 12 and a low-pressure communicating path 43 leading to the suction chamber 20.
  • the low-pressure valve portion 41 opens, the crank case 12 communicates with the suction chamber 20 to decrease the pressure in the crank case 12.
  • the high-pressure valve portion 36 and the low-pressure valve portion 41 are opened or closed at the same time by the operating rod 35, which is axially advanceable and retreatable, so that when the high-pressure valve portion 36 is closed, the low-pressure valve portion 41 is opened, and when the high-pressure valve portion 36 is opened, the low-pressure valve portion 41 is closed.
  • a through-hole Along the centre axis of the operating rod 35 there is formed a through-hole.
  • a pilot valve portion 48 which can be opened or closed by means of a ball valve 47.
  • the pressure responding diameter of the pilot valve portion 48 is formed much smaller than that of the high-pressure valve portion 36 (for example, 1/4). Accordingly, since the effective pressure-receiving area is proportionate to the square of the hole diameter, the effective pressure-receiving area for the pilot valve portion 48 is much smaller than that for the high-pressure valve portion 36 (for example 1/16).
  • a driving rod 49 is provided for transmitting the movement of an electromagnetic solenoid 50 (electromagnetic coil 50a iron core 50b) for opening or closing the pilot valve portion 48 by means of the ball valve 47.
  • Driving rod 49 is loosely fitted in the through hole so that refrigerant can pass through the clearance between the outer periphery of the driving rod 49 and the inner periphery of the through-hole of operating rod 35.
  • a small rod 51 loosely passing through a valve seat in that portion is interposed between driving rod 49 and ball valve 47 transmitting the advance or retreat motion of the driving rod 49 to the ball of the base valve 47.
  • valve member 44 fixed to the other end portion of the operating rod 35 is axially movably fitted in a tubular case 52.
  • the clearance between the outer peripheral surface of the driving rod 49 and the operating rod 35 conductively leads to a pressurising chamber 53 defined by the tubular case 52 and the valve member 44.
  • the pilot valve portion 48 is adapted to open or close the communicating path between the high pressure communicating path 37 and the pressurising chamber 53.
  • pilot valve portion 48 When pilot valve portion 48 is opened, the discharge chamber 21 communicates with the pressurising chamber 53 to increase the pressure in the pressurising chamber 563. Since pressurising chamber 53 is as big as valve member 44, the diameter of the pressurising chamber 53 is bigger than the diameter of the high-pressure valve portion 36 for example, twice as big.
  • a leakage hole 54 for conductively connecting the pressurising chamber 53 to the low-pressure communicating path 43 is formed.
  • Leakage hole 54 has a much smaller diameter than the diameter of the opening or valve seat in the pilot valve portion 48.
  • the refrigerant in the pressurising chamber 53 gradually leaks into the low-pressure communicating path 43 so that the pressure in the pressurising chamber 53 becomes an appropriate pressure between Pd and Ps.
  • Compression coil springs 55, 56 abut on the ball valve 47 and the valve member 44, respectively, to bias the operating rod 35 in both directions.
  • leakage hole 54 is provided in operating rod 35 at a higher position than in figure 1 and close to pilot valve portion 48, i.e. below the opening into the through hole of the operating rod 35 adjacent to the lower side of ball valve 47.
  • Leakage hole 54 in figure 6 conductively connects pressurising flow-path 38 to the through-hole of operating rod 35 and via said through-hole to pressurising chamber 53.
  • the purpose of the leakage hole 54 in this elevated position is similar as explained in connection with leakage hole 54 in the lower position shown in figure 1.
  • driving rod 49 is formed with a long longitudinal extension bridging the distance between movable iron core 50b and the pilot valve portion 48 situated at the upper end of operating rod 35.
  • a shortened driving rod 49 is used.
  • pilot valve portion 48 is provided within a lower portion of operating rod 35 and close to valve member 44.
  • pilot valve portion 48 is situated between pressure reducing flow-path 42 and low-pressure communicating path 43.
  • the electromagnetic coil 50a of the electromagnetic solenoid 50 is electrically energised to cause the iron core 50b to press the driving rod 49 upwardly and to move the ball valve 47 outwardly to open the pilot valve portion 48.
  • the electromagnetic solenoid 50 would generate heat if a great driving force would be required to overcome a differential pressure between Pd and Pc which exerts on the high-pressure valve portion 36. Since, however, the effective pressure-receiving area of the pilot valve portion 48 is much smaller than that of the high-pressure valve portion 36, the pilot valve portion 48 can be opened with a small driving force, and accordingly, the calorific value of the electromagnetic solenoid 50 is very low.
  • Figure 2 shows a state immediately after the pilot valve portion 48 has been opened.
  • the low-pressure valve portion 41 still remains opened.
  • the high-pressure valve portion 36 is closed.
  • the pilot valve portion 48 has been opened, whereby the high-pressure refrigerant at the high-pressure communicating path 37 side passes along the outer periphery of the driving rod 49 into the pressurising chamber 53 the refrigerant pressure in the pressurising chamber 53 gradually increases.
  • the diameter of the pressurising chamber 53 is bigger than that of the high-pressure valve portion 36 and has a bigger effective pressure-receiving area, as the pressure in the pressurising chamber 53 increases, the force acting on the operating rod 35 in opening direction of the high-pressure valve portion 36 becomes greater than the force in closing direction.
  • the low-pressure valve portion 41 fully closes and the high-pressure valve portion 36 enters the fully-opened state.
  • the pressure Pc in the crank case 12 becomes a high pressure equal to the pressure Pd in the discharge chamber 21.
  • the inclination angle of the rocking plate 14 further becomes smaller, and the capacity of the variable-capacity compressor 10 becomes minimal.
  • the inclination angle of the rocking plate 14 becomes zero, the rocking member is adjusted pneumatically) to the shaft, and the capacity of the variable-capacity compressor 10 becomes zero.
  • the pressure in the pressurising chamber 53 then is maintained at a pressure between Pd and Ps by taking a balance between the refrigerant at high pressure Pd flowing from the pilot valve portion 48 and the refrigerant flowing from the leakage hole 54 into the low-pressure communicating path 43 at low pressure (Ps).
  • the capacity of the compressor 10 cannot only be changed from a maximum to a minimum, but it is possible to stop the operating rod 35 in any intermediate position in which both the high-pressure valve portion 36 and the low-pressure valve portion 41 are opened as shown in figure 3. This is done by adjusting the amount of current for the electromagnetic coil 50a of the electromagnetic solenoid 50. Since the rocking plate 14 inclines at an angle adapted thereto, the capacity discharge amount of the variable capacity compressor 10 can be controlled arbitrarily. It is recommendable to match the magnitude of the current for the electromagnetic coil 50a and the capacity of the variable-capacity compressor 10 in order to achieve a linear change.
  • the high-pressure valve portion can be opened or closed with a desirable small solenoid force, because the high-pressure valve portion is opened or closed with assistance of the pressure acting in the pressurising chamber on the operating member having a bigger effective pressure-receiving area than the high-pressure valve portion.
  • the pilot valve portion has an effective pressure-receiving area that is smaller than that of the high-pressure valve portion for opening or closing the communicating path between the crank case and the discharge chamber at high pressure. Therefore, the electromagnetic solenoid for driving the valve requires only a weak current. This greatly suppresses heat generation in the electromagnetic coil and prevents defects resulting from heat generation.

Claims (12)

  1. Dispositif de réglage de la capacité (30) d'un compresseur à capacité variable (10), ledit compresseur comportant un élément basculant (14) à angle d'inclinaison variable pouvant être modifié par rapport à un arbre rotatif (11) dans un carter étanche à l'air (12), l'élément basculant (14) étant entraíné par un mouvement rotatif dudit arbre rotatif dans un mouvement basculant, et un piston (17) connecté au dit élément basculant (14), afin de délivrer un fluide frigorifique à l'intérieur d'une chambre de décharge (21) après aspiration du fluide frigorifique depuis une chambre d'aspiration (20) à l'intérieur d'un cylindre (15) pour y être comprimé par mouvement alternatif, ledit dispositif réglant la capacité dudit compresseur à capacité variable dans lequel l'angle d'inclinaison dudit élément basculant est modifié par la différence existant entre une pression dans ledit carter et une pression dans ladite chambre d'aspiration afin de modifier la quantité de décharge de fluide frigorifique,
    caractérisé par
    une partie de clapet haute pression (36) destinée à ouvrir ou à fermer la communication entre ladite chambre de décharge (21) et ledit carter (12) ;
    une partie de clapet basse pression (41) destinée à ouvrir ou à fermer la communication entre ladite chambre d'aspiration (20) et ledit carter (12) ;
    une élément de commande de clapet (35) destiné à l'ouverture ou à la fermeture de manière à inverser la relation d'ouverture / fermeture entre ladite partie de clapet haute pression (36) et ladite partie de clapet basse pression (41) par avancement ou par retrait ;
    une chambre de mise en pression (53) destinée à appliquer une pression sur ledit élément de commande de clapet (35) dans une direction qui ouvre ladite partie de clapet haute pression au moyen d'une surface effective de réception de pression plus importante qu'une surface effective de réception de pression de ladite partie de clapet haute pression ;
    et une partie de clapet pilote (48) comportant une surface effective de réception de pression plus étroite que ladite surface effective de réception de pression de ladite partie de clapet haute pression (36) destinée à être commandée par un solénoïde électromagnétique (50) pour ouvrir ou fermer un passage de communication entre ladite chambre de décharge (21) et ladite chambre de mise en pression (53).
  2. Dispositif de réglage de capacité selon la revendication 1, caractérisé en ce qu'une partie d'extrémité de l'élément de commande (35) définit un élément de piston de grande dimension (44) situé en engagement coulissant dans ladite chambre de mise en pression (53).
  3. Dispositif de réglage de capacité selon la revendication 2, caractérisé en ce que l'élément de piston de grande dimension (44) est une partie d'un élément mobile de clapet de la partie de clapet basse pression (41).
  4. Dispositif de réglage de capacité selon au moins l'une des revendications 1 à 3, caractérisé en ce que l'élément de commande (35) est une tige de commande creuse recevant une tige d'entraínement mobile longitudinalement (49), une extrémité de la tige d'entraínement (49) peut être actionnée de manière positive par un noyau mobile (50b) du solénoïde (50), l'autre extrémité de la tige d'entraínement étant adaptée pour s'engager sur un élément de fermeture de la partie de clapet pilote (48).
  5. Dispositif de réglage de capacité selon au moins l'une des revendications 1 à 4, caractérisé en ce que la partie de clapet pilote (48) est située à l'intérieur de l'élément de commande (35), de préférence soit à l'intérieur d'une partie de l'élément de commande (35) définissant un élément mobile de clapet de la partie de clapet haute pression (36), soit à l'intérieur d'une partie de l'élément de commande (35) faisant partie d'un élément mobile de clapet de la partie de clapet basse pression (41).
  6. Dispositif de réglage de capacité selon la revendication 4, caractérisé en ce que la surface de pression de la partie de clapet pilote (48) est définie par la surface d'étanchéité entre ledit élément de fermeture et une ouverture de siège de clapet de la partie de clapet pilote (48), ladite ouverture de siège de clapet étant de préférence un prolongement d'un trou traversant de l'élément de commande (35).
  7. Dispositif de réglage de capacité selon la revendication 4, caractérisé en ce que la tige d'entraínement (49) comporte un jeu à l'intérieur du trou traversant de l'élément de commande (35) et définit un passage de communication longitudinal entre ladite partie de clapet pilote (48) et ladite chambre de mise en pression (53).
  8. Dispositif de réglage de capacité selon la revendication 1, caractérisé en ce que ladite partie de clapet pilote (48) est un clapet à bille et à ressort (47).
  9. Dispositif de réglage de capacité selon au moins l'une des revendications 1 à 8, caractérisé en ce qu'un trou de fuite (54) est aménagé dans l'élément de commande (35) afin d'établir une connexion de débit entre ladite chambre de mise en pression (53) et, soit un passage de communication basse pression, soit un passage de débit de mise en pression (38).
  10. Dispositif de réglage de capacité selon les revendications 6 et 9, caractérisé en ce que le trou de fuite (54) a une dimension plus petite que ladite ouverture de siège de clapet de ladite partie de clapet pilote (48).
  11. Dispositif de réglage de capacité selon les revendications 6, 9 et 10, caractérisé en ce que le trou de fuite (54) est situé dans la paroi de l'élément de commande (35) à proximité de la partie de clapet haute pression (36).
  12. Dispositif de réglage de capacité selon les revendications 6, 9 et 10, caractérisé en ce que le trou de fuite (54) est situé dans la paroi d'un carter tubulaire statique (52) renfermant la chambre de mise en pression (53).
EP96103572A 1995-10-31 1996-03-07 Dispositif de réglage de la capacité d'un compresseur à capacité variable Expired - Lifetime EP0771948B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US08/629,606 US5702235A (en) 1995-10-31 1996-04-09 Capacity control device for valiable-capacity compressor

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP283140/95 1995-10-31
JP28314095A JP3490557B2 (ja) 1995-10-31 1995-10-31 容量可変圧縮機の容量制御装置
JP28314095 1995-10-31

Publications (2)

Publication Number Publication Date
EP0771948A1 EP0771948A1 (fr) 1997-05-07
EP0771948B1 true EP0771948B1 (fr) 2000-01-19

Family

ID=17661752

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96103572A Expired - Lifetime EP0771948B1 (fr) 1995-10-31 1996-03-07 Dispositif de réglage de la capacité d'un compresseur à capacité variable

Country Status (5)

Country Link
EP (1) EP0771948B1 (fr)
JP (1) JP3490557B2 (fr)
AT (1) ATE189042T1 (fr)
DE (1) DE69606261T2 (fr)
ES (1) ES2142510T3 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4160669B2 (ja) * 1997-11-28 2008-10-01 株式会社不二工機 可変容量型圧縮機用制御弁
JP2001099060A (ja) * 1999-10-04 2001-04-10 Fuji Koki Corp 可変容量型圧縮機用制御弁
JP2001132632A (ja) * 1999-11-10 2001-05-18 Toyota Autom Loom Works Ltd 容量可変型圧縮機の制御弁
JP4829419B2 (ja) * 2001-04-06 2011-12-07 株式会社不二工機 可変容量型圧縮機用制御弁
JP4456906B2 (ja) * 2004-03-25 2010-04-28 株式会社不二工機 可変容量型圧縮機用の制御弁
DE502006008574D1 (de) * 2005-11-09 2011-02-03 Ixetic Bad Homburg Gmbh Sauggasdrosseleinrichtung
KR20190092234A (ko) * 2018-01-29 2019-08-07 한온시스템 주식회사 압축기의 제어장치, 그에 사용되는 전자식 제어밸브 및 그를 포함한 전동 압축기
KR102352195B1 (ko) * 2018-02-27 2022-01-17 이구루코교 가부시기가이샤 용량 제어 밸브
JP7350458B2 (ja) 2019-07-11 2023-09-26 イーグル工業株式会社 容量制御弁
EP3998401A4 (fr) 2019-07-12 2023-07-12 Eagle Industry Co., Ltd. Soupape de régulation de capacité

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4606705A (en) * 1985-08-02 1986-08-19 General Motors Corporation Variable displacement compressor control valve arrangement
JPH0784865B2 (ja) * 1986-12-16 1995-09-13 カルソニック株式会社 容量可変斜板式コンプレツサの制御装置
JPS63243469A (ja) * 1987-03-28 1988-10-11 Toyota Autom Loom Works Ltd 揺動斜板型圧縮機におけるクランク室圧力の制御機構
JP3131015B2 (ja) * 1992-04-03 2001-01-31 株式会社鷺宮製作所 電磁式制御弁

Also Published As

Publication number Publication date
DE69606261T2 (de) 2000-06-08
JP3490557B2 (ja) 2004-01-26
EP0771948A1 (fr) 1997-05-07
ES2142510T3 (es) 2000-04-16
DE69606261D1 (de) 2000-02-24
JPH09126124A (ja) 1997-05-13
ATE189042T1 (de) 2000-02-15

Similar Documents

Publication Publication Date Title
US5702235A (en) Capacity control device for valiable-capacity compressor
US5282329A (en) Solenoid type control valve
JP3963619B2 (ja) 冷凍サイクルの圧縮容量制御装置
US4780059A (en) Slant plate type compressor with variable capacity mechanism with improved cooling characteristics
WO2019107377A1 (fr) Vanne de régulation de capacité et procédé pour vanne de régulation de capacité
US4586874A (en) Refrigerant compressor with a capacity adjusting mechanism
KR101208477B1 (ko) 용량제어밸브
US6485267B1 (en) Control valve for variable capacity compressors
KR960001632B1 (ko) 용량가변성 배출기구를 구비한 경사판형 압축기
JP3242496B2 (ja) 可変容量圧縮機の外部切換式容量制御弁
EP0771948B1 (fr) Dispositif de réglage de la capacité d'un compresseur à capacité variable
US6302656B1 (en) Solenoid controlled valve and variable displacement compressor
CA2020332C (fr) Compresseur a plateau incline
US6102668A (en) Electromagnetic control valve
EP0824191B1 (fr) Compresseur à déplacement variable
KR20060046254A (ko) 가변 용량 압축기용 제어 밸브
US6217291B1 (en) Control valve for variable displacement compressors and method for varying displacement
JPH04259683A (ja) 斜板式コンプレッサー
JP4070425B2 (ja) 冷凍サイクルの圧縮容量制御装置
JPH0343685A (ja) 容量可変型揺動式圧縮機
US6231321B1 (en) Air compressor
US4709555A (en) Variable delivery refrigerant compressor of double-acting swash plate type
EP0907021B1 (fr) Soupape de contrôle de déplacement pour utilisation dans un compresseur à capacité variable
JP3792939B2 (ja) 容量可変圧縮機及び容量制御弁
JP3678824B2 (ja) 容量可変圧縮機の容量制御装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LI LU MC NL PT SE

17P Request for examination filed

Effective date: 19970409

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 19990401

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LI LU MC NL PT SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 20000119

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000119

Ref country code: LI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000119

Ref country code: GR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000119

Ref country code: CH

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000119

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000119

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000119

REF Corresponds to:

Ref document number: 189042

Country of ref document: AT

Date of ref document: 20000215

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 69606261

Country of ref document: DE

Date of ref document: 20000224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000307

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000307

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

ITF It: translation for a ep patent filed

Owner name: PROPRIA S.R.L.

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2142510

Country of ref document: ES

Kind code of ref document: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000419

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000419

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000930

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20080328

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20080319

Year of fee payment: 13

Ref country code: GB

Payment date: 20080326

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20080429

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080319

Year of fee payment: 13

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090307

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20091130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090307

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091123

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20090309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090307