EP0144790A2 - Compresseur - Google Patents

Compresseur Download PDF

Info

Publication number
EP0144790A2
EP0144790A2 EP84113488A EP84113488A EP0144790A2 EP 0144790 A2 EP0144790 A2 EP 0144790A2 EP 84113488 A EP84113488 A EP 84113488A EP 84113488 A EP84113488 A EP 84113488A EP 0144790 A2 EP0144790 A2 EP 0144790A2
Authority
EP
European Patent Office
Prior art keywords
compressor
valve
refrigerant
passage
suction
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
EP84113488A
Other languages
German (de)
English (en)
Other versions
EP0144790B1 (fr
EP0144790A3 (en
Inventor
Teruo Maruyama
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.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial 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
Priority claimed from JP21130983A external-priority patent/JPS60104793A/ja
Priority claimed from JP59056653A external-priority patent/JPS60201088A/ja
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP0144790A2 publication Critical patent/EP0144790A2/fr
Publication of EP0144790A3 publication Critical patent/EP0144790A3/en
Application granted granted Critical
Publication of EP0144790B1 publication Critical patent/EP0144790B1/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/16—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves

Definitions

  • the present invention generally relates to compressors and more particularly to, a variable output type rotary compressor for use in an air conditioner and the like.
  • a prior art variable output type compressor in which a discharge valve 204 provided in a cylinder formed with a cylinder chamber 203 is released away from the cylinder by a solenoid valve including a solenoid 200 such that compression of high-pressure gas 206 is stopped.
  • a solenoid valve including a solenoid 200 such that compression of high-pressure gas 206 is stopped.
  • the solenoid valve is lowered so as to close a front passage of the high-pressure gas 206, so that pressure for depressing a plunger 201 in the leftward direction in Fig. 1 decreases and thus, the plunger 201 is pushed in the rightward direction in Fig. 1 - by an urging force of a spring 202.
  • the known compressor of Fig. 1 has such a disadvantage that since it becomes necessary to secure a sufficiently large space for the solenoid 200, the compressor becomes large in size and weight and complicated in structure. Furthermore, the prior art compressor of Fig. 1 has been disadvantageous in that it is difficult to select material for stably bonding adjacent ones of turns of the winding wire of the solenoid 200 to one another since the solenoid 200 is heated at high temperature and under high pressure and that manufacture of the solenoid 200 is difficult, thereby resulting in high production cost of the compressor.
  • an essential object of the present invention is to provide an improved variable output type compressor in which a valve provided with a driving member made of shape memory alloy is incorporated such that electric current applied to the driving means is controlled, with substantial elimination of the disadvantages inherent in conventional compressors of this kind.
  • Another important object of the present invention is to provide an improved compressor of the above described type which is simple in structure, compact in size and can be manufactured at low cost.
  • an improved compressor comprising: a fixed member; a movable member which is movable relative to said fixed member such that a cylinder chamber for effecting suction and compression strokes of refrigerant therein is defined between said fixed member and said movable member; said fixed member being formed with a plurality of suction ports for the refrigerant and a discharge port for the refrigerant such that said suction ports and said discharge port open into said cylinder chamber; a valve which is connected with a passage communicating, through one of said suction ports, with said cylinder chamber; said valve including a member which is made of shape memory alloy such that said valve opens or closes said passage upon expansion or contraction of said member; and a power source for supplying electric power to said member.
  • FIG. 3 schematically shows refrigerant passages connected with the compressor K1 arranged to adjust refrigerating capability of the air conditioner.
  • the compressor Kl generally includes a cylinder 11 formed with a vane chamber, i.e., a cylinder chamber 41, axially extending therethrough, vanes 12, a rotor 14 rotatably provided in the cylinder chamber 41 and formed with grooves 13 for receiving the vanes 12 slidably therein, respectively, passages 23, 24, 26 and 27 and a supply source 28 for the refrigerant.
  • the cylinder 11 is further formed with suction ports 15 and 17 opening into the cylinder chamber 41 and a discharge port 22 opening into the cylinder chamber 41.
  • the passages 23 and 24 are, respectively, communicated with the cylinder chamber 41 through the suction ports 15 and 17, while the passage 27 is led from the passage 24 such that the passages 23 and 27 are connected with the passage 26 provided with the supply source 28.
  • a main valve 25 is provided between the passages 24 and 27.
  • the compressor Kl further includes a rear plate 40, a front plate 42 confronting the rear plate 40, a rotary shaft 43 coupled with the rotor 14, a rear casing 44 coupled with the rear plate 40, a spool having a head portion 47, a compression spring 46 wound around the spool 45, a plug 49 provided with a sealing member 48, and a sealing member 50 provided between the rear plate 40 and the rear casing 44.
  • a back pressure portion 51 is defined between the head portion 4.7 of the spool 45 and the plug 49 and oil 52 is filled into the rear casing 44.
  • the main valve 25 is constituted by the spool 45, the compression spring 46 and the suction port 17.
  • the compressor K1 is in a control cancel mode for cancelling control of the refrigerating capability of the air conditioner, in which the spool 45 is displaced leftwards by the compression spring 46 due to low pressure of the back pressure portion 51.
  • the vanes 12, and the rotor 14 are movable members, while the cylinder 11, the rear plate 40 and the front plate 42 are fixed members such that the cylinder chamber 41 is defined between the movable members (vanes 12 and rotor 14) and the fixed members (cylinder 11, rear plate 40 and front plate 42).
  • the compressor Kl further includes a pilot valve 66 for controlling the main valve 25 and the pilot valve 66 is adapted to be actuated by a coiled tension spring 54 made of shape memory alloy.
  • the compressor K1 includes a spool 52, a coiled tension spring 53 made of ordinary metal other than shape memory alloy, a valve casing 55 for accommodating the pilot valve 66 therein, and upper and lower covers 56 and 57 provided at upper and lower portions of the spring casing 55, respectively.
  • the spool 52 has a small diameter portion 65 formed at a central portion thereof.
  • the coiled tension spring 53 is held between hook members 58 and 60 which are secured to a lower portion of the upper cover 56 and an upper portion of the spool 52, respectively.
  • the coiled tension spring 54 is held between hook members 59 and 61 which are, respectively, fixed to an upper portion of the lower cover 57 and a lower portion of the spool 52. Openings 62, 64 and 63 for accommodating the coiled tension spring 53, the spool 52 and the coiled spring 54, respectively, are formed in the valve casing 55 so as to extend in alignment with one another in this order.
  • the pilot valve 66 is mainly constituted by the spool 52, coiled tension springs 53 and 54 and upper and lower covers 56 and 57. It should be noted that the valve casing 55 is formed at a rear portion of the rear casing 44.
  • an electrical circuit of the compressor K1 includes a power source 68 having the coiled tension spring 54 as its load and a switch 69.
  • the compressor Kl includes a low-pressure and low-temperature supply source of the refrigerant and a high-pressure and high-temperature discharge side for the refrigerant.
  • the supply source has a supply pressure Ps and the discharge side has a discharge pressure Pd.
  • the compressor K1 further includes a passage 70 for connecting the supply source Ps and the opening 64, a passage 71 for connecting the discharge side and the opening 64, a passage 72 for connecting the passages 70 and 71, a passage 73 for connecting the passage 72 and the back pressure portion 51 of the main valve 25, a passage 74 for connecting the supply source and the opening 63, and a passage 75 for connecting the supply source and the opening 62.
  • a 12-volt battery commonly used for motor vehicles was employed as the power source 68.
  • Ni-Ti alloy which has a transformation point of 40 to 50°C and is held in a contracted state when subjected to high temperatures above the transformation point, was employed as shape memory alloy for the coiled tension spring 54. Meanwhile, the opening 62 for the coiled tension spring 53 and the opening 63 for the coiled tension spring 54 are communicated with the supply source for the refrigerant through the passages 75 and 74, respectively, and thus, are held at low temperature and lower pressure at all times.
  • the compressor Kl is in a control mode for controlling the refrigerating capability of the air conditioner.
  • the power source 68 of the compressor K1 is turned on and off intermittently as shown in Fig. 9a such that the voltage of the power source 68 has a pulse width T1 and a pulse period T0. Accordingly, temperature t of the coiled tension spring 54 varies periodically as shown in Fig. 9b.
  • Fig. 10 there is shown a modification of Fig. 9.
  • responsive characteristics of rise at the time of changeover from cancellation of control of the refrigerating capability of the air conditioner to start of control of the refrigerating capability of the air conditioner are improved. Namely, the voltage is continuously applied to the coiled tension spring 54 in a duration Ts immediately after the changeover and then, is intermittently applied to the coiled tension spring 54 in the same manner as shown in Fig. 9 after the coiled tension spring 54 has been heated sufficiently higher than the transformation point tl.
  • a temperature actuator employed in a compressor K2 according to a second embodiment of the present invention.
  • the temperature actuator of the compressor K2 includes, so to speak, a "bistable multiple circuit" having a self-retaining function.
  • changeover between the control cancel mode for cancelling control of the refrigerating capability of the air conditioner and the control mode for controlling the refrigerating capability of the air conditioner can be sequentially effected when one pulse having a proper pulse width is applied to a compression spring made of shape memory alloy.
  • the temperature actuator of the compressor K2 includes compression springs 100 and 101 made of shape memory alloy, a spool 102 having a small diameter portion 109 formed at a central portion thereof, power sources 105 and 106 and switches 107 and 108.
  • the power source 105 and the switch 107 are provided for the compression spring 103, while the power source 106 and the switch 108 are provided for the compression spring 104.
  • Openings 103, 110 and 104 for accommodating the compression spring 100, the spool 102 and the compression spring 101, respectively, are so provided as to extend in alignment with one another in this order.
  • characters Psc and Psd represent a suction pressure and an intermediate pressure, respectively.
  • the temperature actuator of the compressor K2 further includes a passage 111 for connecting the supply source of the refrigerant and the opening 110 for the spool 102, a passage 112 for connecting the intermediate pressure Psd and the opening 110, a reservoir portion 113 provided in the course of the passage 112, a passage 114 for connecting the opening 104 and the suction pressure Psc, a passage 115 for connecting the back pressure portion51 of the main valve 25 and the opening 110, a passage 116 branched from the passage 115 and communicating with the opening 110, a passage 117 branched from the passage 116 and communicating with the opening 103 for the compression spring 100, and a passage 118 branched from the passage 111 and communicating with the opening 104 for the compression spring 101.
  • the compression springs 100 and 101 made of shape memory alloy are so manufactured as to be held in an expanded state at temperatures higher than the transformation point such that the following conditions (1) to (3) are satisfied.
  • the compressor K2 is in the control cancel mode for cancelling control of the refrigerating capability of the air conditioner.
  • the switch 107 for the power source 105 and the switch 108 for the power source 106 are in an "off" state.
  • a small amount of the low-temperature refrigerant is supplied from the supply source into the opening 103 for the compression spring 100 via the passage 111, the opening 110, and the passages 116 and 117 so as to be drawn out of the opening 103 into a passage having the suction pressure Psc.
  • the switch 107 is turned on from the state of Fig. 11.
  • the spool 102 is displaced leftwards.
  • the intermediate pressure Psd is introduced into the back pressure portion 51 of the main valve 25 via the passage 112, the reservoir portion 113, the opening 110 and the passages 116 and 115. Consequently, the spool 45 is displaced rightwards such that control of the refrigerating capability of the air conditioner is started.
  • the intermediate pressure Psd is introduced into the opening 103 for the compression spring 100 through the passage 112, the reservoir portion 113, the opening 110 and the passage 103.
  • the switch 107 is turned off from the state of Fig. 13.
  • the spool 102 is held in the same state as in the case where the voltage is applied to the compression spring 100 (Fig. 12).
  • the switch 108 is turned on from the state of Fig. 13. Since the above condition (3) is satisfied at this time, the spool 102 is displaced rightwards. As a result, the refrigerant under the intermediate pressure Psd is prevented from being supplied to the opening 103. Thus, since the opening 103 is communicated with the supply source through the passage 111, the opening 110 and the passages 116 and 117, the above condition (1) is satisfied again. Accordingly, even if the switch 108 is set to the "off" state, the spool 102 is held in the same state as shown in Fig. 11.
  • FIG. 15 there is shown PV characteristic of the compressor K1.
  • curves A and B indicate states of the control cancel mode and the control mode, respectively.
  • characters Psc and Ps represent the suction pressure and the supply pressure, respectively, the suction supply Ps becomes larger than the suction pressure Psc due to pressure drop.
  • the reservoir portion 113 is .provided between the passage having the intermediate pressure Psd and the opening 110 for the spool 102 so as to function as an accumulator for stabilizing variations of the intermediate pressure Psd. Since only a small amount of the refrigerant is required to flow from the passage having the intermediate pressure Psd, volume of the reservoir portion 113 can be made sufficiently small.
  • the compressor K1 includes an upper portion 19 of the cylinder 11, and vanes 20a and 20b defining a vane chamber 18a therebetween.
  • the rotor 14 is rotated about its rotary axis O in the counterclockwise direction in Fig. 16.
  • An angle G is measured about the rotary axis O in the counterclockwise direction in Fig. 16 at an arbitrary position of a tip of the vane 20a by setting the angle 6 to zero when the tip of the vane 20a passes by the upper portion 19 of the cylinder 11.
  • Fig. 16a shows a state in which the vane 20a has just passed by the upper portion 19.
  • FIG. 16b shows a state in which the vane 20a is disposed between the suction ports 15 and 17 such that the refrigerant is supplied into the vane chamber 18a only via the suction port 15.
  • Fig. 16c shows a state in which the vane 20a has passed by the suction port 17 and the vane 20b following the vane 20a is now passing by the suction port 15. Thereafter, supply of the refrigerant into vane chamber 18a via the suction port 15 is prevented by the vane 20b such that supply of the refrigerant into the vane chamber 18a via the suction port 17 is started.
  • Fig. 16d shows a state in which the refrigerant is supplied into the vane chamber 18a only through the suction port 17.
  • FIG. 16e shows a state in which the vane 20b has just passed by the suction port 17.
  • the suction stroke of the cylinder 11 is completed at this time.
  • the angle e in Fig. 16e is set to 225° approximately and volume of the vane chamber 18a reaches a maximum value at this time.
  • a solid line C and a one- dot chain line D respectively indicate the control cancel mode (Fig. 16) and a state in which the refrigerant is prevented from flowing into the vane chamber through the suction port 17 by closing the main valve 25 (Fig. 3).
  • the main valve 25 When the main valve 25 is closed, the refrigerant is prevented from flowing into the vane chamber 18a through the suction port 17 as shown in Fig. 16d.
  • the curves A and B in Fig. 15 indicate the states of the control cancel mode and the control mode, respectively.
  • the pilot valve provided with the member made of shape memory alloy was employed in order to close or open the main passage.
  • the spring 46 (Fig. 4) for the main valve 25 is made of shape memory alloy such that the main passage is directly closed or opened by the main valve 25.
  • the compressor K3 includes a cylinder 311 formed with a vane chamber, i.e., a cylinder chamber 322 axially extending therethrough, vanes 312, a rotor 314 rotatably provided in the cylinder chamber 322 and formed with grooves 313 for receiving the vanes 312 slidably therein, respectively, passages 318 and 319, a valve 320 (hereinbelow, referred to as an "SMA valve”) provided with a member made of shape memory alloy, and a supply source 321 for the refrigerant.
  • SMA valve a valve 320
  • the cylinder 311 is further formed with suction ports 315 and 316 opening into the cylinder chamber 322 and a discharge port 317 opening into the cylinder chamber 322.
  • the cylinder chamber 322 is defined by the vanes 312, rotor 314, cylinder 311 and side plates of the cylinder 311.
  • suction and compression of the refrigerant are performed in the control cancel mode for cancelling control of the refrigerating capability of the air conditioner.
  • the compressor K3 further includes a rear plate 323, a front plate 324 confronting the rear plate 323, a rotary shaft 325 coupled with the rotor 314, a rear casing 324 coupled with the rear plate 323, a clutch pulley 327, a discharge pipe joint 328, a suction pipe joint 329, a head cover 330 formed with a suction chamber 331, an intermediate plate 333 and a wire 334 for supplying electrical power to the SMA valve 320.
  • the compressor K3 is formed with a through-hole 332 communicating with the suction chamber 331 and the passage 318. Meanwhile, the passages 318 and 319 are defined between the rear plate 323 and the intermediate plate 333.
  • the SMA valve 320 in the open and closed states, respectively.
  • the SMA valve 320 includes a circular plate 335 formed with an opening 337, a spool 336, a bolt 338 for securing the plate 335 to the spool 336, a torsion spring 339 wound around the spool 336, a torsion spring 340 (hereinafter referred to as an "SMA spring") made of shape memory alloy and wound around the spool 336, a ball 341 provided at a lower end of the spool 336 for supporting the spool 336, a casing 342 secured to the intermediate plate 333 with bolts 343, and a bolt 346 acting as a stopper for the plate 335.
  • SMA spring torsion spring
  • the rear plate 323 is formed with a through-hole 344.
  • the rear plate 323 is formed with a recess 345 for receiving the plate 335 rotatably therein, while the plate 335 is formed with a groove 347.
  • the torsion spring 339 has one end 348 secured to the spool 336 and the other end 349 secured to the intermediate plate 333.
  • the SMA spring 340 has one end 350 secured to the spool 336.
  • the SMA valve 320 further includes an electrically insulating plate 351 and the SMA spring 340 has the other end 352 secured to the insulating plate 351.
  • a voltage is applied to the SMA spring 340 by a battery provided outside the SMA valve 320 such that electric current is sequentially passed through respective conductive members, i.e., the wire 334, other end 352, SMA spring 340, one end 350, spool 336, torsion spring 339, other end 349 and intermediate plate 333.
  • input terminals of the SMA valve 320 connected to two terminals of the power source are the wire 334 and the compressor K3 (ground).
  • Ni-Ti alloy having a transformation point of 40 to 50°C was employed as shape memory alloy for the SMA spring 340. It is so arranged that when temperature of the SMA spring 340 exceeds the transformation point, the SMA spring 340 is so actuated as to rotate the spool 336 and the plate 335 in the clockwise direction as indicated by the arrow A in Fig. 20a. Therefore, when electric current is passed through the SMA spring 340, temperature of the SMA spring 340 reaches the transformation point due to its heat generation, so that the plate 335 is rotated until the plate 335 is prevented from being rotated further upon contact of the plate 335 with the bolt 346.
  • the vane chamber 322 is communicated with the passage 319 leading to the supply source 321 for the refrigerant. Namely, since the refrigerant filled into the vane chamber 322 after the suction stroke is again returned (bypassed) to the supply source 321, control of the refrigerating capability of the air conditioner is effected to a large extent.
  • the SMA valve 320 comprising the SMA spring 340 made of shape memory alloy and having a torsional restoring force and the torsion spring 339 in combination, it becomes possible to control the refrigerating capability of the air conditioner by the compressor K3 having a remarkably simple construction as compared with conventional compressors employing solenoid valves. Since the plate 335 confronting the vane chamber 322 is rotated flush with the surface of the rear plate 323, drop of efficiency of the compressor K3 due to clearance volume at the time of the control cancel mode does not take plate. This is because the opening 337 is shielded by the rotor 314 in the control cancel mode as shown in Fig. 21b. It is dimensionally so arranged that a small clearance of a few times ten microns is defined between the rotor 314 and the rear plate 323.
  • the compressor K3' which is a modification of the compressor K3, whose response property is improved.
  • the compressor K3' includes a passage 358 for connecting the passage 319 and a space 359 formed in the casing 342 for accommodating the SMA spring 340, a passage 360 for connecting the space 359 and a vane chamber 361 disposed at the side of the suction ports, and a hole 362 led from the passage 360 and opening into the vane chamber 361.
  • the SMA spring 340 is heated by passing electric current therethrough. Then, when the power source is turned off, it takes a long time due to heat capacity of the SMA spring 340 to allow the SMA spring 340 to drop in temperature.
  • Acuators employing members made of shape memory alloy have been hitherto proposed in the field of robots, etc. but have such a fatal drawback as the above described poor response property.
  • the compressor K3' such a fact is taken into consideration that the compressor of the refrigerating cycle is provided with the refrigerating source.
  • the low-temperature refrigerant is caused to flow through the passages 358 and 360 as indicated by the arrows in Fig. 22 so as to cool the SMA spring 340 rapidly, thereby improving the response property of the SMA spring 340.
  • the valve includes the spring made of shape memory alloy and the ordinary spring. However, it can be also so arranged that the valve includes two springs made of shape memory alloy and the springs have restoring forces oriented in opposite directions, respectively so as to be alternately subjected to voltage.
  • the compressor K4 includes a cylinder 500 formed with suction ports 502a and 502b and discharge ports 508a and 508b, a rotor 501, a main valve 503, a supply source 504 for the refrigerant, and a suction passage 505. Cylinder chambers 506a and 506b are defined between the rotor 501 and the cylinder 500.
  • a pilot valve including a member made of shape memory alloy can be employed for opening or closing the main valve 503.
  • the member made of shape memory alloy and provided in the compressor is expanded or contracted when subjected to voltage so as to close or open the passage of the refrigerant such that the refrigerating capability can be easily adjusted externally of the compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Temperature-Responsive Valves (AREA)
EP84113488A 1983-11-10 1984-11-08 Compresseur Expired - Lifetime EP0144790B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP21130983A JPS60104793A (ja) 1983-11-10 1983-11-10 圧縮機
JP211309/83 1983-11-10
JP56653/84 1984-03-23
JP59056653A JPS60201088A (ja) 1984-03-23 1984-03-23 圧縮機

Publications (3)

Publication Number Publication Date
EP0144790A2 true EP0144790A2 (fr) 1985-06-19
EP0144790A3 EP0144790A3 (en) 1986-12-30
EP0144790B1 EP0144790B1 (fr) 1990-03-07

Family

ID=26397612

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84113488A Expired - Lifetime EP0144790B1 (fr) 1983-11-10 1984-11-08 Compresseur

Country Status (2)

Country Link
EP (1) EP0144790B1 (fr)
DE (1) DE3481537D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0261507A1 (fr) * 1986-09-25 1988-03-30 Diesel Kiki Co., Ltd. Compresseur rotatif à palettes avec dispositif pour adaptation de refoulement et réglage y relatif
EP0693406A2 (fr) * 1994-07-15 1996-01-24 Daewoo Electronics Co., Ltd Valve utilisant des alliages à mémoire et système de freinage antiblocage avec une telle valve
EP0697315A3 (fr) * 1994-08-17 1998-04-15 Daewoo Electronics Co., Ltd Valve utilisant des alliages à mémoire et système de freinage antiblocage comportant une telle valve

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57187572A (en) * 1981-05-11 1982-11-18 Sharp Kk Refrigeration cycle
JPS58138288A (ja) * 1982-02-09 1983-08-17 Nippon Soken Inc 回転圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57187572A (en) * 1981-05-11 1982-11-18 Sharp Kk Refrigeration cycle
JPS58138288A (ja) * 1982-02-09 1983-08-17 Nippon Soken Inc 回転圧縮機

Non-Patent Citations (5)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, unexamined applications, section M, vol. 6, no. 17, January 30, 1982 THE PATENT OFFICE JAPANESE GOVERNMENT page 72 M 109 * JP-A 56 135 774 (A)(DAIKIN) * * TOTALITY * *
PATENT ABSTRACTS OF JAPAN, unexamined applications, section m, vol. 6, no. 45, March 20, 1982 THE PATENT OFFICE JAPANESE GOVERNMENT page 43 M 118 * JP-A 56 159 582(A)(NIPPON DENSO K.K.) * TOTALITY * *
PATENT ABSTRACTS OF JAPAN, unexamined applications, section M, vol. 7, no. 254, November 11, 1983 THE PATENT OFFICE JAPANESE GOVERNMENT page 95 M 255; & JP-A-58 138 288 (NIPPON JIDOSHA), * TOTALITY * *
PATENT ABSTRACTS OF JAPAN, unexamined applications, section M, vol.7, no. 254, November 11, 1983, THE PATENT OFFICE JAPANESE GOVERNMENT, page 95 M 255, *Kokai-no. 58-138 288(A)(NIPPON JIDOSHA)* *Totality* *
PATENT ABTRACTS OF JAPAN, unexamined applications, section M, vol. 6, no. 45, March 20, 1982, THE PATENT OFFICE JAPANESE GOVERNMENT, page 43 M 118,Kokai-no. 56-159 582(A)(NIPPON DENSO K.K.)**Totality* *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0261507A1 (fr) * 1986-09-25 1988-03-30 Diesel Kiki Co., Ltd. Compresseur rotatif à palettes avec dispositif pour adaptation de refoulement et réglage y relatif
EP0693406A2 (fr) * 1994-07-15 1996-01-24 Daewoo Electronics Co., Ltd Valve utilisant des alliages à mémoire et système de freinage antiblocage avec une telle valve
EP0693406A3 (fr) * 1994-07-15 1998-04-15 Daewoo Electronics Co., Ltd Valve utilisant des alliages à mémoire et système de freinage antiblocage avec une telle valve
EP0697315A3 (fr) * 1994-08-17 1998-04-15 Daewoo Electronics Co., Ltd Valve utilisant des alliages à mémoire et système de freinage antiblocage comportant une telle valve

Also Published As

Publication number Publication date
EP0144790B1 (fr) 1990-03-07
EP0144790A3 (en) 1986-12-30
DE3481537D1 (de) 1990-04-12

Similar Documents

Publication Publication Date Title
US4580949A (en) Sliding vane type rotary compressor
US5471959A (en) Pump control module
US4683725A (en) Air conditioner for automotive vehicles capable of cooling intake air supplied to an internal combustion engine
US5690475A (en) Scroll compressor with overload protection
JPH08189315A (ja) 内燃機関の弁駆動装置
JPS62132061A (ja) 無段変速機用油圧制御装置
KR910002401B1 (ko) 능력제어 컴프레서
US5018366A (en) Control circuit unit for a variable capacity compressor incorporating a solenoid-operated capacity control valve
EP0144790B1 (fr) Compresseur
JP2000205666A (ja) 空調装置
EP2458217B1 (fr) Contrôle de la température par modulation de largeur d'impulsion
JPH0465239B2 (fr)
US4840039A (en) Automatic expansion valve for a refrigeration circuit
EP0992657B1 (fr) Moteur à combustion interne à soupapes à commande électromagnétique
CN210033838U (zh) 一种用于螺杆压缩机的柱塞式容量调节装置
JPS62147181A (ja) 電磁比例式圧力制御弁
CN110425113B (zh) 压缩机及具有其的制冷设备
KR102672057B1 (ko) 밀폐형 압축기의 기동 보조 구조체
JPH0247275Y2 (fr)
JPH11107930A (ja) 可変容量圧縮機の容量制御弁
JPS63134895A (ja) 可変容量圧縮機
JPWO2013108352A1 (ja) 油圧制御回路
JPS60201088A (ja) 圧縮機
US3512900A (en) Pneumatic sequence controller
KR20240002566A (ko) 밀폐형 압축기의 기동 보조 구조체

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

Designated state(s): DE FR GB

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB

17P Request for examination filed

Effective date: 19870313

17Q First examination report despatched

Effective date: 19880511

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

ET Fr: translation filed
REF Corresponds to:

Ref document number: 3481537

Country of ref document: DE

Date of ref document: 19900412

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

Ref country code: GB

Payment date: 19931101

Year of fee payment: 10

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

Ref country code: FR

Payment date: 19931110

Year of fee payment: 10

Ref country code: DE

Payment date: 19931110

Year of fee payment: 10

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

Ref country code: GB

Effective date: 19941108

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

Effective date: 19941108

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

Ref country code: FR

Effective date: 19950731

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

Ref country code: DE

Effective date: 19950801

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST