US3538357A - Fluid circulating apparatus for reciprocating machines - Google Patents

Fluid circulating apparatus for reciprocating machines Download PDF

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Publication number
US3538357A
US3538357A US788595A US3538357DA US3538357A US 3538357 A US3538357 A US 3538357A US 788595 A US788595 A US 788595A US 3538357D A US3538357D A US 3538357DA US 3538357 A US3538357 A US 3538357A
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reciprocating
machine
chamber
fluid
cylinder
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US788595A
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English (en)
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Maurice Barthalon
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    • 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
    • H02K33/16—Motors with reciprocating, oscillating or vibrating magnet, armature or coil system with polarised armatures moving in alternate directions by reversal or energisation of a single coil system
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/003—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 free-piston type pumps
    • 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
    • F04B31/00—Free-piston pumps specially adapted for elastic fluids; Systems incorporating such pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F7/00—Pumps displacing fluids by using inertia thereof, e.g. by generating vibrations therein
    • 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

Definitions

  • the machine is characterized in that said device comprises a chamber having a delivery orifice for the fluid and means for causing the fluid to move by inertia, said means comprising a surface belonging to said chamber, movable with respect to the base, and arranged so as to cause the fluid to pass from the chamber to another region of the machine.
  • The'present invention concerns a machine having reciprocating movement and comprising an oscillating moving assembly and a means for the circulation within the machine of a fluid, more particuarly a liquid.
  • This liquid may be especially the auxiliary liquid used for the lubrication or the cooling of the machine or of an associated machine.
  • the remarkable features of the invention allow it to be used to make a particularly simple pump having variable stroke.
  • the invention is advantageously but not limitatively applied to reciprocating, variable stroke, linear energy converters, for example of the electro-motor type described especially in US. Pat. No. 3,461,806 for Reciprocating Electric Motor.
  • the invention also applies to linear energy converters in particular of the motor-alternator type, more particularly those which are the subject of the applicants application for a Pat. 594,191 filed November 14, 1966 for Electromagnetic Machines. As these machines are often of low unit power and are intended to be manufactured in large quantities at moderate prices, they need lubrication and/ or cooling arrangements which are robust, cheap and adapted to the variable stroke of the machine.
  • circulation means in which an intermittent rotary movement is derived from the oscillating movement of the moving assembly which drive a pump through a free wheel.
  • the present invention is intended to remedy these difficulties and to allow reciprocating machines to be manufactured which comprise a means for the circulation of the fluid which will be simple and of very low cost price.
  • the reciprocating movement machine which comprises a base, a stator mounted on this base, a moving assembly lodged within the stator and having reciprocating movement with re- 3,538,357 Patented Nov.
  • a device for circulating within the machine a fluid, more particularly a liquid is characterised in that said device comprises a chamber having a delivery orifice for the fluid and means for causing the fluid to move by force of inertia, comprising a surface in the chamber, movable with respect to said base and arranged so as to cause the fluid to pass from said chamber to another region of the machine.
  • the fluid circulating in the machine is more especially a liquid, such as an auxiliary liquid ensuring the lubrication of the machine.
  • the stator is elastically mounted with respect to the base such that it is submitted to a reciprocating movement relative to the base by the reaction of the moving assembly, and the chamber is connected to the stator such that its surfaces ensure the propulsion of the liquid by the forces of inertia.
  • this assembly has a chamber having an axis parallel to the direction of movement of said assembly and in which is mounted a secondary moving assembly comprising a plunger moving under the effect of the forces of inertia along the axis of said chamber and substantially sealing the same.
  • the plunger defines in the chamber at least one variable volume which is connected alternately to an intake channel connected to a reservoir of liquid and to a delivery channel.
  • This embodiment provides a greater flow of liquid than the preceding one while being particularly simple and sure.
  • the device for circulating the liquid comprises a chamber forming a dispenser for the liquid, in unit with the moving assembly and formed by a tubular piece inclined with respect to the axis of movement of this assembly.
  • the lower part of this dispenser is pierced with an orifice which is dipped in the liquid contained in the reservoir, whereas its upper part has a smaller section orifice for the distribution of the liquid.
  • FIG. 1 is an axial section view of the machine conforming to the invention.
  • FIG. 2 is a view of the same machine on section IIII of FIG. 1.
  • FIG. 3 is an axial section of a second embodiment of the invention.
  • FIG. 4 is a view of the machine represented on FIG. 3 with section IV-IV of FIG. 3.
  • FIG. 5 is a section view of a modification of the embodiment according to FIG. 4.
  • FIG. 6 is an axial section view of a third embodiment of the invention. 1
  • FIG. 7 is a corresponding view with section on VII- VII of FIG 6.
  • the fluid is an auxiliary liquid forming the lubricating oil whose circulation is ensured, in accordance with the invention, by means which comprise a chamber forming an oil reservoir 6 disposed in the lower part of cylinder 1 and communicating with a delivery orifice in the form of an annular groove 7, practiced in the internal surface of cylinder 1, and entering the cylinder in the region of the mid point of the surface swept by piston 2 and at a distance from the cylinder head at least equal to the cylinder bore.
  • the groove 7 also communicates with a drilling 9 in which the level gauge 11 is housed (FIG. 2) and with a filling orifice 12 closed by a blank 13. This blank is itself drilled with a passage 14 closed by a block 15 of porous material through which air can pass but not oil.
  • the oscillating moving assembly of which piston 2 forms a part, is not dynamically balanced, such that in operation the stator of the machine has a reciprocating movement provoked by reaction of the moving assembly and in phase opposition with the latter, the amplitudes of these two movements being inversely proportional to the corresponding masses.
  • the sufaces of reservoir 6 are thus subjected to a periodic acceleration whose value is maximum at the moment when the speed of the stator changes direction.
  • the oil contained in reservoir 6 is thus projected by the forces of inertia onto the end walls 16 and 17 which thus exercise a pressure on the oil and part of the oil projected mounts progressively towards the groove 7, this progression being aided by the action of the surface tension of the oil.
  • a continuous film of oil is thus established between the surface of cylinder 1 and piston 2, this film being renewed at each stroke of the piston.
  • the small clearance between these two surfaces prevents air leakage and limits the delivery of oil during operation; furthermore it prevents oil leakage during transport of the machine when it may be temporarily inverted.
  • the permeability to air of porous block 15 maintains in reservoir 6 a pressure equal to the atmopheric pressure, which prevents oil from being driven up towards the compressor while its practically zero permeability to oil prevents the latter from escaping to the outside.
  • FIGS. 3 to 5 illustrate another embodiment of the invention applicable to this range of machines, which also gives a higher delivery of oil.
  • the machine represented is a linear motor-compressor intended for the compression of expensive or dangerous gases.
  • This motor-compressor is suspended by links 31, within a sealed casing 32, whose lower part 33 forms the reservoir of auxiliary liquid which in this case again, is the lubricating oil of the machine.
  • the moving assembly of the compressor comprises a piston 34 having a reciprocating movement within a cylinder 35.
  • the moving assembly and the piston 34 is formed a cylindrical chamber 36 co-axial with this piston and in which a secondary moving assembly comprising a slide-block such as a plunger 37 moves freely.
  • This plunger thus divides the chamber 36 into two volumes 36a and 36b, which are variable according to the position of the plunger.
  • the clearance between the surfaces of the plunger 37 and of the chamber 36 are sufliciently small to make oil leakage from one volume to another negligible.
  • Each of the volumes 36a and 36b is connected to the external surface of piston 34 by a radial orifice 38a, 38b drilled at a certain distance from the end surfaces 39a, 39b of the chamber 36 such that when the plunger 37 commences to block off one of these orifices 38a, 38b, there remains a residual volume between the face of this plunger and the corresponding surface 39a, 39b.
  • the orifice 38a is drilled at a certain distance from the end 46 of the piston 34, equal to at least the bore of the latter.
  • the internal surface of cylinder 35 also includes three annular grooves 41, 42a, 42b.
  • the groove 41 is connected by an admission channel 43 to the oil reservoir 33.
  • Grooves 42a and 42b symetrically arranged with respect to group 41, are connected by radial orifices 44a and 44b to a channel 45 for the delivery of oil in the machine.
  • a core 40 blocks off the bore of piston 34 thus forming a cavity 36, after introduction of the plunger 37.
  • the oil contained in the volume 36b is delivered into the distribution channel 45, while oil is drawn from the reservoir 33 into volume 36a through channel 43.
  • the reverse takes place, the oil from volume 36a being discharged through channels 44a and 45, while oil is drawn in from reservoir 33 to the volume 36b. Thanks to this arrangement the channel 45 is fed with oil under pressure at each stroke of the piston 34.
  • the radial orfice 38b drilled in the wall of chamber 36 has an opening beyond the extremity of the cylinder 35 when piston 34 is at its inner dead point (position shown in FIG. 5).
  • the oil is thus delivered directly to the extremity of cylinder 35, which allows the annular groove 42b and the radial orifice 44b which, in the application shown in FIG. 3, were formed in the internal surface of cylinder 35, to be eliminated.
  • Measurements have been carried out on an arrangement of this type mount on a 200 w. motor-compressor.
  • the bore of the chamber 36 was 8 mm.
  • the stroke of plunger 37 was mm.
  • the intake pressure in volumes 36a and 36b was 100 grammes per cm.
  • the delivery pressure 800 grammes per cm was 100 grammes per cm.
  • the clearance between the plunger 37 and the surface of the chamber 36 was several hundredths of a millimeter, which required no special precautions during machining. Under these conditions an oil delivery of 300 litres per hour was obtained.
  • the fluid may be a gaseous medium, the machine then acting as a pump for this medium.
  • FIGS. 6 to 10 In the case where the machine is of too high a unit power to be able to use the embodiment represented in FIG. 1 and where it does not include an auxiliary piston as in the embodiment shown in FIG. 3, a third embodiment may advantageously be used, which will now be described, referring to FIGS. 6 to 10.
  • the machine is a variable reluctance motor-alternator, whose motor part includes motor pistons 61 and scavenge pistons 62, moving within cylinder 63 closed by cylinder heads 64 which carry sparking plugs 65.
  • the pistons 62 are connected by a shaft 66, on which is fixed a magnetic armature 67, driven by this shaft in a reciprocating movement.
  • This armature moves in air gaps 68 and 69 of a magnetic circuit which comprises two pole pieces 71a and 7112 joined by a common yoke 72.
  • Each of these pole pieces carries an excitation coil 73a, 73b through which runs a direct current of appropriate sign, while a field coil 74 for generating the alternating current surrounds the assembly of the two pole pieces 71a, 71b.
  • the fixed parts of the machine such as the cylinder 63 and magnetic circuits are mounted on a hollow base in the form of a body 75.
  • auxiliary liquid in this embodiment is intended for cooling the coils.
  • a reservoir 76 for the cooling oil is formed in the lower part of the body 75 and the shaft 66 carries a chamber acting as oil dispenser 77 formed by a. tubular piece whose axis is inclined with respect to the direction of reciprocating movement of the moving assembly.
  • the lower part 79 of the distributor 77 is open and dips into the oil of reservoir 76 while the upper part of the dispenser is drilled with an orifice 78 of smaller section than the central channel of the dispenser.
  • a particularly inexpensive embodiment of dispenser 77 consists of forming it (FIG. 8) from a tube brazed to shaft 66, this tube being partially flattened such as to give an ovoid section (FIG. 9). At its upper end (FIG. 10) tube 77 is completely flattened over part of its diameter so as to form the output orifice 78 of a small section.
  • auxiliary liquid circulating means according to the invention may be advantageously employed on all machines of medium or low unit power, having reciprocating movement, thanks to its very low cost price and its certain operation, which requires practically no maintenance.
  • the slope G of the tangent T to curve B is 35 to 40% greater than slope G of the tangent T to curve A. the inertia forces are consequently greater and the eflicacy of the device is higher in linear converters with reciprocating moving assemblies.
  • fluid circulating apparatus comprising a chamber formed in the machine and adapted to receive a fluid, a delivery orifice for the chamber, surface means in the chamber movable relative to the base of the machine in response to reciprocation of the reciprocating assembly, said surface means formed to transmit to said fluid the forces of inertia generated as a result of said reciprocation, and guiding walls in the chamber movable with respect to the base and formed to guide the fluid towards the delivery orifice.
  • Fluid circulating apparatus according to claim 1, wherein means are provided for mechanically connecting the chamber for the fluid to the reciprocating assembly.
  • liquid circulating apparatus comprising a chamber formedin the stator and adapted to receive a liquid, a delivery orifice for the chamber, at least one wall of the chamber being formed to transmit to the liquid the forces of inertia resulting from reciprocation of the reciprocating assembly, and guiding walls of the chamber movable with respect to the base and formed to guide the liquid towards the delivery orifice.
  • Liquid circulating apparatus in which is provided a medium permeable to air and impermeable to the liquid, and means to vent the chamber to the atmosphere through said medium to maintain the chamber at atmospheric pressure while preventing leakage of the liquid therefrom.
  • a reciprocating machine including a base, a stator mounted on the base, a guiding cylinder formed within the stator, and a reciprocating assembly including a piston reciprocating within the guiding cylinder, fluid circulating apparatus comprising a chamber formed in the machine and adapted to receive a fluid, a delivery orifice for the chamber, the orifice opening into the cylinder through the surface of the cylinder and being blocked by the piston during a portion of its reciprocating movement, surface means in the chamber movable relative to the base of the machine in response to reciprocation of the reciprocating assembly, said surface means formed to transmit to said fluid the forces of inertia generated as a result of said reciprocation, and guiding Walls in the chamber movable with respect to the base and formed to guide the fluid towards the delivery orifice.
  • Fluid circulating apparatus according to claim 5, wherein the delivery orifice opens into the middle part of the cylinder surface swept by the reciprocating movement of the piston.
  • a reciprocating machine including a base, a stator mounted on the base, a reciprocating assembly guided by and movable with respect to the stator, a reservoir for fluid and a delivery passage for said fluid
  • fluid circulating apparatus comprising a chamber formed as a cylinder in the machine and having an axis parallel to the direction of movement of the reciprocating assembly, an orifice in the wall of said cylinder, a plunger movable within the chamber in response to the forces of inertia upon reciprocation of the reciprocating assembly, said plunger defining in said chamber at least one variable volume, and means for connecting said orifice during reciprocation of the reciprocating assembly alternately to the fluid reservoir and to the delivery passage.
  • Fluid circulating apparatus in which the wall of said cylinder includes a second orifice, and means for connecting said second orifice during reciprocation of the reciprocating assembly alternately to the fluid reservoir and to the delivery passage.
  • Fluid circulating apparatus in which said orifices are located in the Wall of said cylinder at positions remote from the end walls of the chamber, thereby providing at the ends of the chamber volumes serving as a damper for the plunger.
  • Fluid circulating apparatus in which said orifices in the wall of said cylinder are located at a distance from the ends of said cylinder equal at least to the diameter of the bore of the cylinder.
  • a reciprocating machine including a base, a stator mounted on the base, an external cylinder formed in a portion of the stator, a reciprocating assembly guided by and movable with respect to the stator, the assembly including a piston adapted to reciprocate in the external cylinder, fluid circulating apparatus comprising a chamber for the fluid formed as an internal cylinder in the piston coaxially with the external cylinder, a plunger movable in the internal cylinder by the forces of inertia resulting from reciprocation of the reciprocating assembly, first and second orifices extending from the internal cylinder through the piston, and passage means forming portions of fluid circuits in the stator and in the surface of the external cylinder, said orifices completing said fluid circuits when moved into coincidence with said passage means during reciprocation of the reciprocating assembly.
  • liquid circulating apparatus comprising a tabular device forming a chamber for the liquid, means connecting the tubular device to the reciprocating assembly and inclined with respect to the axis of movement of the reciprocating assembly, an orifice in the lower portion of the tubular device which extends into the reservoir, and a delivery orifice in the upper part of the tubular device, said delivery orifice having an area smaller than that of the remaining portion of the tubular device.
  • a method of circulating fluid in a reciprocating machine having a reciprocating assembly guided by and movable with respect to a stator comprising the steps of flowing a quantity of fluid into a chamber having a delivery orifice in the machine, utilizing the forces of inertia resulting from movement of the reciprocating assembly to set the fluid in motion with respect to the chamber and utilizing the reaction forces developed by guiding walls of the chamber to circulate the fluid towards the delivery orifice and through the orifice to another region of the machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
US788595A 1968-01-12 1969-01-02 Fluid circulating apparatus for reciprocating machines Expired - Lifetime US3538357A (en)

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FR135740 1968-01-12

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US (1) US3538357A (pt)
JP (1) JPS5241482B1 (pt)
BE (1) BE726476A (pt)
CH (1) CH485944A (pt)
DE (1) DE1966459C3 (pt)
ES (1) ES362400A1 (pt)
FR (1) FR1582781A (pt)
GB (2) GB1256612A (pt)
NL (2) NL6900316A (pt)
SE (1) SE354335B (pt)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4032264A (en) * 1975-04-04 1977-06-28 Man Design Co., Ltd. Closed-type electromagnetic compressor
DE3941019A1 (de) * 1988-12-16 1990-06-21 Walbro Corp Anordnung zum einbau einer brennstoffpumpe
US5231747A (en) * 1990-12-21 1993-08-03 The Boeing Company Drill/rivet device
US5261799A (en) * 1992-04-03 1993-11-16 General Electric Company Balanced linear motor compressor
US5263236A (en) * 1990-12-21 1993-11-23 The Boeing Company Drill quill bearing assembly
WO1997001032A1 (en) * 1995-06-23 1997-01-09 Lg Electronics, Inc. Oil supply apparatus for friction portion of linear compressor
US5913665A (en) * 1997-03-28 1999-06-22 Tetra Laval Holdings & Finance, Sa Fill pump with rolling diaphragms attached by vacuum to the piston
US20080267797A1 (en) * 2004-12-23 2008-10-30 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor
US20100236282A1 (en) * 2007-09-10 2010-09-23 Panasonic Corporation Refrigerant compressor
CN111486091A (zh) * 2019-11-21 2020-08-04 山东青耕电气有限公司 单缸转子式液体高频换向装置及其压缩机

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Publication number Priority date Publication date Assignee Title
FR2488344B1 (fr) * 1980-08-05 1985-12-27 Renault Generateur hydraulique a moteur a piston libre
IL106683A0 (en) * 1993-08-13 1993-12-08 N C A Ltd Fluid pump and method
DE102007028059B4 (de) 2007-06-19 2009-08-20 Webasto Ag Hubkolbenpumpe zum Fördern einer Flüssigkeit
CN114526526B (zh) * 2022-04-22 2022-08-05 彭光芳 一种多功能医疗空气净化设备

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US2161408A (en) * 1936-08-08 1939-06-06 Hoover Co Liquid circulating device
US2177795A (en) * 1938-05-27 1939-10-31 Delden Florenz J Von Compressor and electrodynamic actuating mechanism therefor
US2370347A (en) * 1944-04-27 1945-02-27 Joseph P Goebel Water scoop for locomotive tenders
US2633327A (en) * 1946-03-01 1953-03-31 Packard Motor Car Co Gas turbine wheel with liquid cooling means
US2875989A (en) * 1956-04-26 1959-03-03 Ohio Commw Eng Co Vibrator mixer
US2935629A (en) * 1955-10-29 1960-05-03 Chausson Usines Sa Electromagnetically energized mechanism
US2944160A (en) * 1958-05-16 1960-07-05 Charles B Dickinson Oscillatory motor-generator
US3058649A (en) * 1960-03-03 1962-10-16 Chausson Usines Sa Synchronous oscillating compressor actuated by an alternating magnetic field
US3103603A (en) * 1960-11-02 1963-09-10 Reutter Jean Leon Alternating current synchronous reciprocating motor unit
US3147914A (en) * 1962-03-27 1964-09-08 Westinghouse Electric Corp Compressor
US3344293A (en) * 1965-07-12 1967-09-26 Eugene A Wahl Electro-mechanical gyrator
FR1523129A (fr) * 1965-11-17 1968-05-03 Machines électromécaniques transformatrices d'énergie à reluctance variable

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2161408A (en) * 1936-08-08 1939-06-06 Hoover Co Liquid circulating device
US2177795A (en) * 1938-05-27 1939-10-31 Delden Florenz J Von Compressor and electrodynamic actuating mechanism therefor
US2370347A (en) * 1944-04-27 1945-02-27 Joseph P Goebel Water scoop for locomotive tenders
US2633327A (en) * 1946-03-01 1953-03-31 Packard Motor Car Co Gas turbine wheel with liquid cooling means
US2935629A (en) * 1955-10-29 1960-05-03 Chausson Usines Sa Electromagnetically energized mechanism
US2875989A (en) * 1956-04-26 1959-03-03 Ohio Commw Eng Co Vibrator mixer
US2944160A (en) * 1958-05-16 1960-07-05 Charles B Dickinson Oscillatory motor-generator
US3058649A (en) * 1960-03-03 1962-10-16 Chausson Usines Sa Synchronous oscillating compressor actuated by an alternating magnetic field
US3103603A (en) * 1960-11-02 1963-09-10 Reutter Jean Leon Alternating current synchronous reciprocating motor unit
US3147914A (en) * 1962-03-27 1964-09-08 Westinghouse Electric Corp Compressor
US3344293A (en) * 1965-07-12 1967-09-26 Eugene A Wahl Electro-mechanical gyrator
FR1523129A (fr) * 1965-11-17 1968-05-03 Machines électromécaniques transformatrices d'énergie à reluctance variable

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4032264A (en) * 1975-04-04 1977-06-28 Man Design Co., Ltd. Closed-type electromagnetic compressor
DE3941019A1 (de) * 1988-12-16 1990-06-21 Walbro Corp Anordnung zum einbau einer brennstoffpumpe
GB2227058A (en) * 1988-12-16 1990-07-18 Walbro Corp Mounting a fuel pump in a tank
US4961693A (en) * 1988-12-16 1990-10-09 Walbro Corporation Fuel pump isolation mount
GB2227058B (en) * 1988-12-16 1993-06-16 Walbro Corp Fuel delivery structure and fuel system.
US5577315A (en) * 1990-12-21 1996-11-26 The Boeing Company Method of upsetting rivets
US5263236A (en) * 1990-12-21 1993-11-23 The Boeing Company Drill quill bearing assembly
US5404633A (en) * 1990-12-21 1995-04-11 The Boeing Company Method of dynamically supporting a drill quill in a drill/rivet machine
US5752306A (en) * 1990-12-21 1998-05-19 The Boeing Company Method for upsetting a headed rivet by differential initiation of opposed electromagnetic rivet drivers
US5231747A (en) * 1990-12-21 1993-08-03 The Boeing Company Drill/rivet device
US5621963A (en) * 1990-12-21 1997-04-22 The Boeing Company Differential capacitance in an electromagnetic riveter
US5685058A (en) * 1990-12-21 1997-11-11 The Boeing Company Method for direct insertion of a headed rivet into a countersunk hole
US5261799A (en) * 1992-04-03 1993-11-16 General Electric Company Balanced linear motor compressor
WO1997001032A1 (en) * 1995-06-23 1997-01-09 Lg Electronics, Inc. Oil supply apparatus for friction portion of linear compressor
US5993175A (en) * 1995-06-23 1999-11-30 Lg Electronics Inc. Oil supply apparatus for friction portion of linear compressor
US5913665A (en) * 1997-03-28 1999-06-22 Tetra Laval Holdings & Finance, Sa Fill pump with rolling diaphragms attached by vacuum to the piston
US20080267797A1 (en) * 2004-12-23 2008-10-30 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor
US8038418B2 (en) * 2004-12-23 2011-10-18 Bsh Bosch Und Siemens Hausgeraete Gmbh Linear compressor
US20100236282A1 (en) * 2007-09-10 2010-09-23 Panasonic Corporation Refrigerant compressor
CN111486091A (zh) * 2019-11-21 2020-08-04 山东青耕电气有限公司 单缸转子式液体高频换向装置及其压缩机
CN111486091B (zh) * 2019-11-21 2023-12-08 山东青耕电气有限公司 单缸转子式液体高频换向装置及其压缩机

Also Published As

Publication number Publication date
DE1966459A1 (de) 1973-01-18
NL165813C (nl) 1981-05-15
NL7709327A (en) 1977-12-30
NL6900316A (pt) 1969-07-15
NL165813B (nl) 1980-12-15
ES362400A1 (es) 1970-12-01
DE1966459C3 (de) 1979-04-26
FR1582781A (pt) 1969-10-10
DE1966459B2 (de) 1978-08-31
BE726476A (pt) 1969-06-16
DE1901127A1 (de) 1969-08-07
JPS5241482B1 (pt) 1977-10-19
GB1256612A (pt) 1971-12-08
SE354335B (pt) 1973-03-05
GB1258879A (pt) 1971-12-30
CH485944A (fr) 1970-02-15

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