EP0771948A1 - Kapazitätsregelvorrichtung für einen Verdichter mit veränderlicher Fördermenge - Google Patents

Kapazitätsregelvorrichtung für einen Verdichter mit veränderlicher Fördermenge Download PDF

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Publication number
EP0771948A1
EP0771948A1 EP96103572A EP96103572A EP0771948A1 EP 0771948 A1 EP0771948 A1 EP 0771948A1 EP 96103572 A EP96103572 A EP 96103572A EP 96103572 A EP96103572 A EP 96103572A EP 0771948 A1 EP0771948 A1 EP 0771948A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve portion
chamber
pressure valve
operating member
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.)
Granted
Application number
EP96103572A
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English (en)
French (fr)
Other versions
EP0771948B1 (de
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/de
Application granted granted Critical
Publication of EP0771948B1 publication Critical patent/EP0771948B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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

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 capacitydischarge 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. Since it is apprehended that 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.
EP96103572A 1995-10-31 1996-03-07 Kapazitätsregelvorrichtung für einen Verdichter mit veränderlicher Fördermenge Expired - Lifetime EP0771948B1 (de)

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 true EP0771948A1 (de) 1997-05-07
EP0771948B1 EP0771948B1 (de) 2000-01-19

Family

ID=17661752

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96103572A Expired - Lifetime EP0771948B1 (de) 1995-10-31 1996-03-07 Kapazitätsregelvorrichtung für einen Verdichter mit veränderlicher Fördermenge

Country Status (5)

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

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0919720A3 (de) * 1997-11-28 1999-12-08 Fujikoki Corporation Kontrollventil für Kompressoren mit variabler Fördermenge
EP1247981A2 (de) * 2001-04-06 2002-10-09 Fujikoki Corporation Kontrollventil für Kompressoren mit variabler Fördermenge
EP1099852A3 (de) * 1999-11-10 2003-08-20 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen variablen Verdrängungskompressor
CN100356059C (zh) * 2004-03-25 2007-12-19 株式会社不二工机 变容式压缩机的控制阀
CN111742141A (zh) * 2018-02-27 2020-10-02 伊格尔工业股份有限公司 容量控制阀
EP3998403A4 (de) * 2019-07-11 2023-05-31 Eagle Industry Co., Ltd. Kapazitätssteuerungsventil
US11802552B2 (en) 2019-07-12 2023-10-31 Eagle Industry Co., Ltd. Capacity control valve

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001099060A (ja) * 1999-10-04 2001-04-10 Fuji Koki Corp 可変容量型圧縮機用制御弁
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

Citations (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
DE3810099A1 (de) * 1987-03-28 1988-10-13 Toyoda Automatic Loom Works Taumelscheibenkompressor mit variabler foerderleistung
US4860549A (en) * 1986-12-16 1989-08-29 Nihon Radiator Co., Ltd. Variable displacement wobble plate type compressor
DE4310922A1 (de) * 1992-04-03 1993-10-07 Saginomiya Seisakusho Tokyo Kk Elektromagnetisches Steuerventil

Patent Citations (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
US4860549A (en) * 1986-12-16 1989-08-29 Nihon Radiator Co., Ltd. Variable displacement wobble plate type compressor
DE3810099A1 (de) * 1987-03-28 1988-10-13 Toyoda Automatic Loom Works Taumelscheibenkompressor mit variabler foerderleistung
DE4310922A1 (de) * 1992-04-03 1993-10-07 Saginomiya Seisakusho Tokyo Kk Elektromagnetisches Steuerventil

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0919720A3 (de) * 1997-11-28 1999-12-08 Fujikoki Corporation Kontrollventil für Kompressoren mit variabler Fördermenge
EP1099852A3 (de) * 1999-11-10 2003-08-20 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen variablen Verdrängungskompressor
EP1247981A2 (de) * 2001-04-06 2002-10-09 Fujikoki Corporation Kontrollventil für Kompressoren mit variabler Fördermenge
EP1247981A3 (de) * 2001-04-06 2005-04-13 Fujikoki Corporation Kontrollventil für Kompressoren mit variabler Fördermenge
CN100356059C (zh) * 2004-03-25 2007-12-19 株式会社不二工机 变容式压缩机的控制阀
CN111742141A (zh) * 2018-02-27 2020-10-02 伊格尔工业股份有限公司 容量控制阀
EP3998403A4 (de) * 2019-07-11 2023-05-31 Eagle Industry Co., Ltd. Kapazitätssteuerungsventil
JP7350458B2 (ja) 2019-07-11 2023-09-26 イーグル工業株式会社 容量制御弁
US11802552B2 (en) 2019-07-12 2023-10-31 Eagle Industry Co., Ltd. Capacity control valve

Also Published As

Publication number Publication date
DE69606261T2 (de) 2000-06-08
JP3490557B2 (ja) 2004-01-26
ES2142510T3 (es) 2000-04-16
DE69606261D1 (de) 2000-02-24
JPH09126124A (ja) 1997-05-13
ATE189042T1 (de) 2000-02-15
EP0771948B1 (de) 2000-01-19

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