US3910729A - Compressor - Google Patents

Compressor Download PDF

Info

Publication number
US3910729A
US3910729A US373084A US37308473A US3910729A US 3910729 A US3910729 A US 3910729A US 373084 A US373084 A US 373084A US 37308473 A US37308473 A US 37308473A US 3910729 A US3910729 A US 3910729A
Authority
US
United States
Prior art keywords
piston
cylinder
variable volume
compressor
fluid
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
US373084A
Other languages
English (en)
Inventor
Robert E Jepsen
Jean C Liberty
Richard E Luybli
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.)
Sumitomo SHI Cryogenics of America Inc
Original Assignee
Air Products and Chemicals Inc
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 Air Products and Chemicals Inc filed Critical Air Products and Chemicals Inc
Priority to US373084A priority Critical patent/US3910729A/en
Priority to GB2383074A priority patent/GB1462936A/en
Priority to DE19742428376 priority patent/DE2428376A1/de
Priority to JP49071810A priority patent/JPS5037011A/ja
Application granted granted Critical
Publication of US3910729A publication Critical patent/US3910729A/en
Assigned to APD CRYOGENICS INC. reassignment APD CRYOGENICS INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: AIR PRODUCTS AND CHEMICALS, INC.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K33/00—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system
    • H02K33/18—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system with coil systems moving upon intermittent or reversed energisation thereof by interaction with a fixed field system, e.g. permanent magnets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/001—Gas cycle refrigeration machines with a linear configuration or a linear motor

Definitions

  • ABSTRACT A compressor for pressurizing a fluid characterized by opposed reciprocating pistons or cylinders driven by [52] 417/417 f g i fl g linear electric motors. Movable pistons or cylinders 51 l t Cl /66 are made to operate along a common axis 180 apart 17/04 to provide high pressure fluid to the refrigerator.
  • the apparatus includes in one embodiment means for reciprocating the cylinder rela- [56] References cued tive to a fixed piston, the compressor in either mode UNITED STATES PATENTS having controls to limit the stroke thereby minimizing 2,988,264 6/196! Reutter 417/418 contact of the piston with the end of the cylinder.
  • This invention pertains to compressors for raising the internal pressure of a fluid to a high level and, in particular, for pressurizing fluids to be used in refrigeration systems.
  • a refrigeration compressor is used to raise the pressure of a working fluid such as a refrigerant gas, which gas is then expanded through a nozzle to a lower pressure, thereby absorbing heat and producing refrigeration by the expansion. In normal closed cycle refrigeration systems, this gas, after expansion, is recompressed and recycled through the expansion orifice to further produce refrigeration.
  • the most common type of refrigeration compressor is the reciprocating type having one or more pistons attached to a crankshaft for movement in a corresponding cylinder or cylinders for compressing the gas therein.
  • Such rotary compressors contain a crankshaft and flywheel with the attendant bearings, connecting rods with wrist pins, gears, and the like.
  • Such compressors operate usually at high noise levels and are subject to severe vibration loading and for ultra-high pressure applications, such compressors tend to be extremely large.
  • the pistons are integral with the motor coil and guide shaft and are fabricated to slide in a cylinder which is integral with the motor shell and permanent magnet.
  • the entire motor case is pressurized with a gas and the pressure is maintained at an intermediate level between the inlet and outlet pressure of the compressor to minimize the motor force necessary to operate the compressor.
  • limit springs are located at both ends of the piston assembly to prevent contact of the top of the piston with the cylinder at the ends of the stroke.
  • the springs can be replaced by gas cushions or a resonant spring system to further provide effective operation of the compressor. The energy expended in compressing the limit spring and the gas in the motor case outside of the cylinder is recovered following the compression stroke and the fact that the piston is driven in both directions reduces the size, weight, and power requirements of the overall compressor.
  • a linear compressor of this type having no flywheel, crankshaft, rotary bearings, gears, and the like, removes the primary sources of mechanical wear, failure, noise, friction, and vibration. By operating the pistons 180 apart along a common axis, the vibration and noise of the overall compressor can be essentially eliminated.
  • the linear compressor requires bearings only to maintain alignment of the piston and cylinder and coil and magnet. Since there are no connecting rods, the number of bearings is reduced and the side loading on the bearings present is lowered thus reducing bearing wear significantly.
  • the compressor further includes dry film lubrication of the bearings eliminating oil contamination in the compressor.
  • vIt is another object of this invention to provide a linear compressor having small size and low power requirements.
  • FIG. 1 is a longitudinal section taken along the line 11 of FIG. 2 of a compressor according to the present invention.
  • FIG. 2 is a transverse section taken along the line 2-2 of FIG. 1.
  • FIG. 3 is an end view of an alternate embodiment of a compressor according to the present invention.
  • FIG. 4 is a view taken along line 44 of FIG. 3.
  • FIG. 5 is a view taken along line 55 of FIG. 4.
  • FIG. 6 is an elevational view partially in section of a compressor according to the present invention wherein there is employed an alternate piston return mechanism.
  • FIGS. 1 and 2 there is shown a compressor 10 including a cylindrical housing having a first half 12 and a second half 14.
  • Housing section 12 includes a receiver on end 16 for receiving an instrument probe 18, whereas housing section 14 has a receiver 20 for receiving a hose or other fluid fitting 22.
  • a piston 24 Disposed within the housing sections 12 and 14 and affixed thereto is a piston 24 having a longitudinal bore 26, a first piston end 28 and a second piston end 30.
  • Surrounding piston end 28 is a first cylinder 32 and surrounding second piston end 30 is a second cylinder 34 defining a first chamber 36 and a second chamber 38 between piston and cylinder 2832 and 30-34 respectively.
  • the cylinders 3234 are affixed to a crown member 40, 42 respectively as by a plurality of fasteners shown as 44.
  • Affixed to the crowns 40 and 42 is a thin metal cylinder 46, 48 having a wall thickness of approximately 0.010 inches.
  • Surrounding the shells 46 and 48 respectively are coils 50 and 52 such as normally found in a linear assembly motor as will hereinafter be more fully explained.
  • the assembly of the cylinder 32, crown 40, thin cylindrical shell 46, and coil 50, and of the cylinder 34, crown 42, thin cylindrical shell 48 and coil 52 are each mounted for movement along the longitudinal axis of the compressor as is shown, thereby forming a variable volume between the respective piston and cylinder for chambers 36 and 38 respectively.
  • cylinders 32 and 34 Disposed within chambers 36 and 38 respectively at the top of cylinders 32 and 34 are rubber cushioning pads 54, 56 cushioning the contact of the re spective cylinders with the corresponding end of the fixed piston 24.
  • limit springs 58, 60 At the top of cylinders 32, 34 respectively between the cylinder and the respective housing 12 and 14, there are included limit springs 58, 60 for absorbing the energy from the excursion of the respective cylinders.
  • housing sections 12 and 14 Disposed within housing sections 12 and 14 and affixed thereto is a pair of magnet assemblies consisting of pole pieces 62, 64, magnets 66, 68, and washers 70, 72 respectively.
  • Electrical feed through 76 is disposed between housing sections 12 and 14 for feeding the current through conductors 78 and 80 to the respective coils 50 and 52.
  • the necessary electronics are adequately disclosed in the aforementioned US. Pat. No. 3,469,163.
  • FIG. 2 there is shown a gas inlet conduit 82, which also functions as an outlet conduit and communicates with the longitudinal bore 26 in piston 24.
  • a pressure transducer assembly 84 and water cooling conduits 86 (inlet) and 88 (outlet).
  • housing sections 12 and 14 there are a plurality of bumper pads 90 for cushioning the contact of the movable cylinder assembly to the fixed piston 24.
  • FIGS. 1 and 2 and FIGS. 3, 4 The compressor of FIGS. 1 and 2 and FIGS. 3, 4 and is ideally suited for operation to control a refrigerator as shown in US. Pat. No. 3,620,029.
  • the inlet-outlet conduit 82 being coupled directly to the conduit 30 just above conduit 48 of the refrigerator as shown in FIG. 1 of the aforementioned patent.
  • the transducer assembly 18 is of the linear displacement type sold by Schaevitz Engineering Co. and as Model No. AC LUDT type 500 MI-IR. Such a transducer monitors the position of the cylinder in regard to the time during a respective stroke.
  • Pressure transducer assembly 84 (sold by Statham Instruments Inc. as type PA 208TC-lM-350) is included to determine pressure in relation to time of the cycle for monitoring the overall perfonnance of the compressor and for establishing a P-V diagram for the system.
  • the electronics are so wired that the respective coils 50 and 52 are wired in parallel and are set up so that the respective cylinders 32, 34 are operated 180 apart along a common axis with the pistons moving simultaneously in opposite directions, therebyminimizing the vibration and the operating noise of the compressor.
  • the coils are energized simultaneously so that their motions are identical but opposed.
  • the compressor After the compressor is assembled and tested to assure there are no leaks, it can be charged through fitting 22 with the working fluid, e.g. helium, which fills the entire internal volume of the compressor. The entire internal portion of the compressor is charged to a pressure level intermediate, the minimum and maximum working pressures of the compressor. After the compressor is charged with the initial charge of helium, the fitting 22 is sealed and the compressor is ready for use.
  • the working fluid e.g. helium
  • piston rings shown generally at 92 are included to prevent excessive leakage between the piston and the cylinder.
  • a preferred type of piston ring construction is shown in US. Pat. No. 3,540,746.
  • the inlet-outlet conduit 82 is connected to a refrigerator of the displacer-expander type such as shown in US Pat. No. 3,620,029 and described above.
  • the inlet-outlet fitting 82 is connected directly to the cold end of such a refrigeration apparatus and the entire system is charged with a working fluid such as helium by means of fitting 22. After charging, the system is purged of ambient atmosphere.
  • the compressor is set in motion by energizing the coil 50, 52, causing the respective cylinders 32, 34 to move toward the ends of the housing 12, 14 respectively causing the fluid to enter into chambers 36, 38. As is shown in the drawing when the respective cylinders reach the outermost limit of their excursion, the coil is at its maximum insertion into the magnetic field.
  • the abrupt change in the back electromotive force (BEMF) is sensed, thus cutting off the current flow to the coil.
  • BEMF back electromotive force
  • the cylinders are then returned inwardly (toward the center of the compressor), thereby causing the fluid to be compressed in their respective cylinder volumes 36, 38. Cylinder return is accomplished by the differential pressure existing between cylinder volumes 36, 38 and the compressor housing and the stored energy in springs 58, 60. During this compression stroke, the gas exits through conduit 82.
  • the fact that the motor casing is pressurized to an intermediate level between the suction and compression pressures of the compressor results in a gas cushioning of the cylinder during both points of maximum excursion. Because of the pressure differential and the springs acting in co-operation, the electric motor does not have to exert such a large force in compressing the fluid by recovering energy expended in compressing the gas, which energy can be recovered on the expansion stroke.
  • the only input energy required in order to maintain the cycle is that necessary to overcome the electrical resistance and hysteresis, gas throttling, irreversibility, friction, and work removed by the refrigeration device.
  • the compressor 10' consists of movable cylinders 32' and 34' and in basic construction, is similar to the compressor of FIGS. 1 and 2.
  • a guide cylinder I00 and 102 for guiding the excursion of cylin ders'32 and 34 and assuring their axial alignment.
  • the respective cylinders 32', 34 move axially inside the cylindrical bore of the respective guide cylinders and are positioned with the aid of guide rings 104, 106 preferably fabricated from a carbon-graphite filled teflon material such as used in seals and piston rings.
  • the guide rings 104, 106 are of sufficient axial length to prevent misalignment or wobbling of the respective cylinders during their excursion.
  • Each guide cylinder includes a series of vent holes 108, 110 that communicate with the interior of the housing of the compressor and furthermore which communicate with the interior volume of compressor housing through vent ports 112, 114 in the respective cylinders.
  • the vent holes-vent port fluid circulating system serves as means for cooling the compressor by transferring the heat from the helium to the outside shell of the compressor where it can be readily dissipated by air cooling or water cooling the compressor shell. This further aids in the overall effectiveness of the compressor.
  • FIG. 6 another embodiment 115 of the compressor according to the present invention.
  • the piston 117 moves relative to the cylinder 116.
  • the piston includes a guide ring 118 and suitable piston rings 120 such as shown in US Pat. No. 3,540,746.
  • On the head of the piston 117 is an inlet valve 122 for admitting gas into the piston chamber from the center of the piston stem 124 as is shown in the embodiments of FIGS. l-5.
  • suitable discharge valves 126 for providing the pressurized fluid to a point of use.
  • the compressor of FIG. 6 operates in the traditional manner of fluid compressor.
  • the springs 130 and 132 are selected to have the same spring constant in that they exert equal force; the spring 130 being the compression stroke spring and the spring 132 being the suction stroke spring.
  • the springs are sized so that at the half-way point each spring is exerting an equal force and the piston would tend to remain at rest. In this way, the springs act as a resonant spring mass system and the coil or motor drive need only overcome the friction forces of the guide ring and the piston rings together with any windage forces that are available and the force to compress the gas, thereby resulting in a more compact compressor.
  • the compressor of FIG. 6 is identical to the compressors of FIGS. l-4 in that it has a piston and cylinder on either end which operate 180 apart along a common axis.
  • the spring mass system approaches a resonant spring system, thereby enabling the fabrication of a dry lubricated compressor; only the guide ring and the piston rings being subject to wear.
  • Such compressors need no oil lubrication and can have a short stroke dry lubricated motor coupled to a short stroke dry lubricated compressor.
  • the dual spring system illustrated in relation to FIG. 6 can be used with the devices of FIGS 1 through 4. It is also possible, and in fact, may be advantageous to have springs of unequal spring constant with a'c ompressor such as shown in FIGS. 1 through 4 because of the differential fluid pressure between the cylinder volumes and the compressor housing.
  • the moving pistons or cylinders can be arranged so that at points of maximum excursion they contact the elastomeric pads. It is also possible to operate the compressor so that such contact is limited to either the maximum compression or suction stroke, or contact is eliminated altogether.
  • Such sensors include ultrasonic devices, proximity probes, accelerometers, limit switches and the like.
  • compressors In constructing compressors according to the foregoing invention, it has been shown that vibration and noise are balanced by using the two pistons operating apart along a common axis and moving simultaneously in opposite directions. With no rotary motion, there is no need for rotary bearings, gearing, connecting rods and associated wrist pins, flywheels, thereby eliminating any forces caused by such mechanical devices. The absence of such mechanical devices eliminates the primary sources of mechanical wear, failure, noise, friction, and vibration in conventional reciprocating or rotary-type compressors. Such compressors can be constructed with a minimum of precision parts resulting in low production costs. a
  • the working pressures for one piston cylinder combination could be 15 pounds per square inch (psi) suction and 60 psi compression, and the other piston cylinder combination 60 psi suction and 240 psi compression.
  • the piston return could be accomplished with an internal housing pressure less than the suction pressure of either one of the piston cylinder combination or greater than the compression pressure of either piston cylinder combination.
  • a compressor for pressurizing a fluid comprising in combination:
  • a first piston and cylinder disposed in the first chamber and mounted for relative reciprocation thereby defining a first variable volume fluid chamber
  • a second piston and cylinder disposed in the second chamber and mounted for relative reciprocation thereby defining a second variable volume fluid chamber
  • first and second piston and cylinder combination v mounted relative to each other for reciprocation along the major axis of the housing;
  • a compressor according to claim 1 wherein the first and second cylinders are fixed to the housing and the first and second pistons are reciprocated in relation thereto.
  • a compressor according to claim 1 wherein the means for causing reciprocating motion between the piston and cylinder includes a linear motor having a coil mounted for" movement into and out of a magnetic field.
  • impact cushioning means includes means for pressurizing the compressor housing with a working fluid at a pressure intermediate that of the maximum and minimum pressure in the variable volume during operation.
  • the impact cushioning means further includes limit springs and elastomeric bumperpads.
  • a compressor forpressurizing a fluid comprising in combination:
  • an elongate generally cylindrical closed housing having a major and minor axis and first and second ends defining first and second chambers in said housing;
  • a second piston and cylinder disposed in the second chamber and mounted for reciprocation of the piston and the cylinder relative to'each other thereby defining a second variable volume fluid chamber
  • first and second piston and cylinder combination mounted relative to each other for reciprocation along the major axis of the housing;
  • said means includes pressurizing the compressor housing with a working fluid at a pressure intermediate that of the maximum and minimum pressure in the variable volume chambers during operation of the compressor.
  • a compressor according to claim 1 1 wherein the means for causing the reciprocating motion between the piston and cylinder includes a linear motor having a coil mounted for movement into and out of a magnetic field.
  • a compressor according to claim 13 wherein there is included means for limiting the excursion between each piston and the cylinder said means including at least two preloaded springs acting as a resonant spring mass system and the coil is energized only during the portion of the cycle when the coil is entering the magnetic field.
  • a compressor according to claim 13 wherein the coil is mounted for movement so that it can be selectively energized during the portion of the stroke when the variable volume is decreasing, during the portion of the stroke when the variable volume is increasing or during the entire reciprocation cycle.
  • a compressor for pressurizing a fluid comprising in combination:
  • an elongate generally cylindrical closed housing having a major and minor axis in a first and second end defining first and second chambers in said housing;
  • a first piston and cylinder disposed in the first chamber and mounted for relative reciprocation thereby defining a first variable volume fluid chamber
  • a second piston and cylinder disposed in the second chamber and mounted for relative reciprocation thereby defining a second variable volume fluid chamber
  • first and second piston and cylinder combination mounted relative to each other for reciprocation along the major axis of the housing;
  • each independent piston and cylinder combination to cause reciprocating motion of each piston and cylinder independent of the other, said means including a linear motor having a coil mounted for movement into and out of a fixed magnetic field;

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
US373084A 1973-06-25 1973-06-25 Compressor Expired - Lifetime US3910729A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US373084A US3910729A (en) 1973-06-25 1973-06-25 Compressor
GB2383074A GB1462936A (en) 1973-06-25 1974-05-29 Compressor
DE19742428376 DE2428376A1 (de) 1973-06-25 1974-06-12 Kompressor
JP49071810A JPS5037011A (enrdf_load_stackoverflow) 1973-06-25 1974-06-22

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US373084A US3910729A (en) 1973-06-25 1973-06-25 Compressor

Publications (1)

Publication Number Publication Date
US3910729A true US3910729A (en) 1975-10-07

Family

ID=23470867

Family Applications (1)

Application Number Title Priority Date Filing Date
US373084A Expired - Lifetime US3910729A (en) 1973-06-25 1973-06-25 Compressor

Country Status (4)

Country Link
US (1) US3910729A (enrdf_load_stackoverflow)
JP (1) JPS5037011A (enrdf_load_stackoverflow)
DE (1) DE2428376A1 (enrdf_load_stackoverflow)
GB (1) GB1462936A (enrdf_load_stackoverflow)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4534714A (en) * 1983-02-15 1985-08-13 Smith Raymond H Fluid operating device
US4783968A (en) * 1986-08-08 1988-11-15 Helix Technology Corporation Vibration isolation system for a linear reciprocating machine
US4860543A (en) * 1986-08-08 1989-08-29 Helix Technology Corporation Vibration isolation system for a linear reciprocating machine
US5277561A (en) * 1991-12-19 1994-01-11 Linde Aktiengesellschaft Very low temperature piston pump
US5295809A (en) * 1991-11-21 1994-03-22 Linde Aktiengesellschaft Valved piston pump with cylinder biasing means
US6129527A (en) * 1999-04-16 2000-10-10 Litton Systems, Inc. Electrically operated linear motor with integrated flexure spring and circuit for use in reciprocating compressor
US6250895B1 (en) * 1998-08-11 2001-06-26 Matsushita Electric Industrial Co., Ltd. Linear compressor
WO2002077454A1 (en) * 2001-03-23 2002-10-03 Lg Electronics Inc. Reciprocating compressor
EP1143146A3 (en) * 2000-04-04 2003-06-18 The BOC Group plc Piston stroke control for a vacuum pump
WO2003038975A3 (de) * 2001-11-02 2003-09-18 Leybold Vakuum Gmbh Antrieb für den kolben eines linearkühlers
US6657217B2 (en) 2001-04-10 2003-12-02 York International Corporation Probe for sensing movement in a compressor system
KR100425732B1 (ko) * 2001-11-30 2004-04-06 엘지전자 주식회사 대향형 왕복동식 압축기
US6733245B2 (en) * 2001-11-19 2004-05-11 Lg Electronics Inc. Piston support structure of reciprocating compressor
GB2436400A (en) * 2006-03-25 2007-09-26 Hymatic Eng Co Ltd A piston /cylinder assembly comprising armature driven cylinder and fixed piston.
CN100414097C (zh) * 2004-10-13 2008-08-27 Lg电子株式会社 线性压缩机
US20100154442A1 (en) * 2008-12-22 2010-06-24 Michael Steven Schoenoff Portable Refrigerant Recovery Machine
US20110058962A1 (en) * 2009-09-04 2011-03-10 Kabushiki Kaisha Toyota Jidoshokki Compressor for use in a vehicle
US8624448B2 (en) 2008-11-18 2014-01-07 Institute fuer Luft- und Kaeltetechnik gemeinnutzige GmbH Electrodynamic linear oscillating motor
JP2017072044A (ja) * 2015-10-06 2017-04-13 トヨタ自動車株式会社 燃料ポンプ
US10180122B2 (en) 2015-09-11 2019-01-15 Toyota Jidosha Kabushiki Kaisha Fuel pump
CN109236605A (zh) * 2018-11-13 2019-01-18 天津探峰科技有限公司 直线压缩机

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5530933U (enrdf_load_stackoverflow) * 1978-08-18 1980-02-28
JPS5815632B2 (ja) * 1979-07-31 1983-03-26 松下電器産業株式会社 電磁往復動コンプレッサ−
JPS59153987A (ja) * 1983-02-19 1984-09-01 Sawafuji Electric Co Ltd 振動圧縮機
JPS6138277A (ja) * 1984-07-31 1986-02-24 Tokyo Miyairi Shoji Kk 高圧ガス容器の２段減圧容器弁
JPH0195423A (ja) * 1987-10-07 1989-04-13 Mitsubishi Electric Corp 往復運動装置
JP2550657B2 (ja) * 1988-05-07 1996-11-06 三菱電機株式会社 冷却機
GB9614304D0 (en) * 1996-07-08 1996-09-04 Isis Innovation Linear compressor motor
WO2011011434A2 (en) * 2009-07-22 2011-01-27 Vbox, Incorporated Gaseous fluid pump
CN106895596B (zh) * 2017-02-24 2019-04-05 广东美芝制冷设备有限公司 旋转式压缩机和具有其的制冷系统
CN107165806A (zh) * 2017-07-23 2017-09-15 林子杰 一种大型电磁式空气压缩器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2988264A (en) * 1959-08-20 1961-06-13 Chausson Usines Sa Alternating movement synchronous compressor
US3162134A (en) * 1961-11-24 1964-12-22 Mark E Lovell Electromagnetic pump and energizing means therefor
US3303990A (en) * 1964-02-11 1967-02-14 Mechanical Tech Inc Resonant piston compressor
US3515966A (en) * 1967-04-21 1970-06-02 Pierre Albert Marie De Valroge Motor and pump combination fed by a direct current or rectified current power source
US3729691A (en) * 1972-06-16 1973-04-24 Verta Tronics Inc Electro-mechanical oscillator of electrodynamical and electromagnetic types
US3784334A (en) * 1972-04-03 1974-01-08 Johnson Service Co Electromagnetically driven fluid compressing apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2988264A (en) * 1959-08-20 1961-06-13 Chausson Usines Sa Alternating movement synchronous compressor
US3162134A (en) * 1961-11-24 1964-12-22 Mark E Lovell Electromagnetic pump and energizing means therefor
US3303990A (en) * 1964-02-11 1967-02-14 Mechanical Tech Inc Resonant piston compressor
US3515966A (en) * 1967-04-21 1970-06-02 Pierre Albert Marie De Valroge Motor and pump combination fed by a direct current or rectified current power source
US3784334A (en) * 1972-04-03 1974-01-08 Johnson Service Co Electromagnetically driven fluid compressing apparatus
US3729691A (en) * 1972-06-16 1973-04-24 Verta Tronics Inc Electro-mechanical oscillator of electrodynamical and electromagnetic types

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4534714A (en) * 1983-02-15 1985-08-13 Smith Raymond H Fluid operating device
US4783968A (en) * 1986-08-08 1988-11-15 Helix Technology Corporation Vibration isolation system for a linear reciprocating machine
US4860543A (en) * 1986-08-08 1989-08-29 Helix Technology Corporation Vibration isolation system for a linear reciprocating machine
US5295809A (en) * 1991-11-21 1994-03-22 Linde Aktiengesellschaft Valved piston pump with cylinder biasing means
US5277561A (en) * 1991-12-19 1994-01-11 Linde Aktiengesellschaft Very low temperature piston pump
US6250895B1 (en) * 1998-08-11 2001-06-26 Matsushita Electric Industrial Co., Ltd. Linear compressor
US6129527A (en) * 1999-04-16 2000-10-10 Litton Systems, Inc. Electrically operated linear motor with integrated flexure spring and circuit for use in reciprocating compressor
EP1143146A3 (en) * 2000-04-04 2003-06-18 The BOC Group plc Piston stroke control for a vacuum pump
US6857857B2 (en) 2000-04-04 2005-02-22 The Boc Group Plc Reciprocating machines
WO2002077454A1 (en) * 2001-03-23 2002-10-03 Lg Electronics Inc. Reciprocating compressor
US20030129069A1 (en) * 2001-03-23 2003-07-10 Gyoo-Jong Bae Reciprocating compressor
US6875000B2 (en) 2001-03-23 2005-04-05 Lg Electronics Inc. Reciprocating compressor
US6744061B2 (en) 2001-04-10 2004-06-01 York International Corporation System and method for sensing movement in a compressor system
US6657217B2 (en) 2001-04-10 2003-12-02 York International Corporation Probe for sensing movement in a compressor system
WO2003038975A3 (de) * 2001-11-02 2003-09-18 Leybold Vakuum Gmbh Antrieb für den kolben eines linearkühlers
US20050225182A1 (en) * 2001-11-02 2005-10-13 Andreas Fiedler Drive for the piston of a linear cooler
US6733245B2 (en) * 2001-11-19 2004-05-11 Lg Electronics Inc. Piston support structure of reciprocating compressor
KR100425732B1 (ko) * 2001-11-30 2004-04-06 엘지전자 주식회사 대향형 왕복동식 압축기
CN100414097C (zh) * 2004-10-13 2008-08-27 Lg电子株式会社 线性压缩机
US8049375B2 (en) 2006-03-25 2011-11-01 The Hymatic Engineering Company Limited Electromagnetic transducer apparatus
GB2436400A (en) * 2006-03-25 2007-09-26 Hymatic Eng Co Ltd A piston /cylinder assembly comprising armature driven cylinder and fixed piston.
US20100061867A1 (en) * 2006-03-25 2010-03-11 The Hymatic Engineering Company Limited Electromagnetic Transducer Apparatus
GB2436400B (en) * 2006-03-25 2011-11-30 Hymatic Eng Co Ltd Electromagnetic Transducer Apparatus
US8624448B2 (en) 2008-11-18 2014-01-07 Institute fuer Luft- und Kaeltetechnik gemeinnutzige GmbH Electrodynamic linear oscillating motor
US20100154442A1 (en) * 2008-12-22 2010-06-24 Michael Steven Schoenoff Portable Refrigerant Recovery Machine
US8800306B2 (en) * 2008-12-22 2014-08-12 Bosch Automotive Service Solutions Llc Portable refrigerant recovery machine
US20110058962A1 (en) * 2009-09-04 2011-03-10 Kabushiki Kaisha Toyota Jidoshokki Compressor for use in a vehicle
US10180122B2 (en) 2015-09-11 2019-01-15 Toyota Jidosha Kabushiki Kaisha Fuel pump
JP2017072044A (ja) * 2015-10-06 2017-04-13 トヨタ自動車株式会社 燃料ポンプ
CN109236605A (zh) * 2018-11-13 2019-01-18 天津探峰科技有限公司 直线压缩机

Also Published As

Publication number Publication date
GB1462936A (en) 1977-01-26
DE2428376A1 (de) 1975-01-16
JPS5037011A (enrdf_load_stackoverflow) 1975-04-07

Similar Documents

Publication Publication Date Title
US3910729A (en) Compressor
US3822388A (en) Stirling engine power system and coupler
US4750871A (en) Stabilizing means for free piston-type linear resonant reciprocating machines
US5522214A (en) Flexure bearing support, with particular application to stirling machines
JP3210851B2 (ja) 複式ダイヤフラムポンプ
US5146124A (en) Linear drive motor with flexible coupling
US4115037A (en) Opposed piston internal combustion engine-driven pump
US3588291A (en) Resonant piston pumps
US3471079A (en) Reciprocating vacuum pump
US5645407A (en) Balanced single stage linear diaphragm compressor
US12113427B2 (en) Linear electric generator
US6092999A (en) Reciprocating compressor with a linear motor
CA1298737C (en) Pressure actuated movable head for a resonant reciprocating compressor balance chamber
US4781546A (en) Linear resonant reciprocating machines
US4721440A (en) Linear gas compressor
US3274795A (en) Fluid operating apparatus
US5074755A (en) Hydraulically driven reciprocating compressor having a free-floating diaphragm
US4798054A (en) Linear drive motor with flexure bearing support
JP2025519781A (ja) 圧縮機装置及び圧縮機装置を備えた冷却装置
CN103277288B (zh) 直线电机驱动的隔膜压缩机
US5171129A (en) Hydraulically driven reciprocating compressor having a free-floating diaphragm
EP0119846B1 (en) Pneumatically controlled split cycle cooler
JP4241192B2 (ja) リニア圧縮機
CA1223447A (en) Cryogenic refrigerator
US4750870A (en) Pressure actuated movable head for a resonant reciprocating compressor balance chamber

Legal Events

Date Code Title Description
AS Assignment

Owner name: APD CRYOGENICS INC., A CORP OF PA.

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:AIR PRODUCTS AND CHEMICALS, INC., A CORP OF DE.;REEL/FRAME:004686/0713

Effective date: 19870310

Owner name: APD CRYOGENICS INC.,PENNSYLVANIA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:AIR PRODUCTS AND CHEMICALS, INC.;REEL/FRAME:004686/0713

Effective date: 19870310