US3286911A - Compressors - Google Patents

Compressors Download PDF

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Publication number
US3286911A
US3286911A US484410A US48441065A US3286911A US 3286911 A US3286911 A US 3286911A US 484410 A US484410 A US 484410A US 48441065 A US48441065 A US 48441065A US 3286911 A US3286911 A US 3286911A
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US
United States
Prior art keywords
cylinder
cylinders
pistons
coils
gas
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
US484410A
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English (en)
Inventor
Clarke Michael Edward
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.)
BOC Group Ltd
Original Assignee
British Oxigen Ltd
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Filing date
Publication date
Application filed by British Oxigen Ltd filed Critical British Oxigen Ltd
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Publication of US3286911A publication Critical patent/US3286911A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders
    • 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
    • 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

Definitions

  • Compressors comprising a cylinder, a piston in the cylinder, a coil spring co-axial with the cylinder and attached at one end to the piston and anchored at the other end with respect to to the cylinder, a coil co-axial with and attached to the piston and means for producing a magnetic field co-ax-ial with and directed generally radially of the axis of the cylinder and directed through the coil.
  • the radially directed magnetic field acts on the alternating current flooring in the coil and causes the unitary coil and piston to reciprocate.
  • Such known compressors have the disadvantage that they are not dynamically balanced and either vibrate relative to their surroundings, if resiliently mounted, or transfer vibrations to their surroundings, if fixedly mounted. Such vibrations are known to result in damage to such fittings external to the cornpressor, as conduits.
  • a compressor comprising two cylinders rigidly connected together and located in axial alignment, a piston in each cylinder, a spring connected at its ends to the pistons or two springs each connected at one end to a respective one of the pistons and anchored at the other end with respect to the cylinders, means for producing two magnetic fields substantially radial of the axis of the cylinders and through a portion of each piston or an axial extension thereof, two coils located one in each of the radial fields and co-axial with and rigidly connected one to each of the pistons, the means for producing two magnetic fields substantially radially of the axis of the cylinders co-operating with the coils when an alternating current is supplied either to the means for producing the radial magnetic fields or to the coils or to both, to form two linear motors serving to reciprocate the pistons in antiphas'e relationship, and valve means for allowing flow of the gas to be compressed into each cylinder and flow of compressed gas trom each cylinder.
  • the cylinders are arranged in axially aligned opposition.
  • the gas compressed in one of the cylinders may be led to the other cylinder for further compression and in this case the two cylinders may be of differing cross-sectional areas.
  • the alternating current supplied to the coils when the magnetic fields substantially radial of the axis of the cylinders are nonalternating fields, has a frequency substantially equal to the natural frequency of the piston and spring assembly.
  • FIGURE 1 shows in axial section a two-stage compressor in accordance with the present invention.
  • FIGURE 2 shows diagrammatically an axial section of a further two-stage compressor in accordance with the present invention.
  • the two stage compressor shown in FIGURE 1 comprises a tubular housing 1 to the ends of which are attached by bolts 2, plates 3 of annular shape and formed of magnetic material.
  • the plates 3 have apertu res 4 coaxial with the tubular housing 1.
  • Cylinders 5 and 6 are attached to the remote faces of the plates 3 and are located coaxially with the apertures 4 in the plates 3 and hence with one another.
  • the cylinders 5 and 6 are closed at their remote ends by cylinder heads 7 and 8.
  • Each cylinder head 7 and 8 has formed therein an inlet port 9 and an exhaust. port 10 and includes pressure-operated inlet and outlet valves 11 and 12 respectively, all springbiased towards a closed position.
  • the cylinders 5 and 6 and the cylinder heads 9 and 10 are provided with passages 13 for flow of coolant.
  • the working space within the cylinder 5 has a greater cross-sectional area than the working space within the cylinder 6 since the cylinder 5 constitutes the cylinder of the low pressure stage and the cylinder 6 constitutes the cylinder of the high pressure stage of the two-stage compressor. 7
  • a conduit 14 extends from the exhaust port 10 of the low pressure stage to a heat exchanger 15 and a conduit 16 extends .from the heat exchanger 15. to the inlet port 9 of the high pressure stage.
  • Conduits 17 and 18 communicate with, for example, a gas cleaner and drier and with a pressure storage vessel, or the like, respectively;
  • pistons 19 and 20 Disposed in the cylinders 5 and 6 arepistons 19 and 20 respectively, each having two piston rings.
  • pistons 19 and 20 are of different diameters each appro priate to their related cylinders 5 and 6.
  • Each piston 19 and 20 has a tubular skirt portion 21 of a diameter greater than the diameter of the pistons.
  • the tubular skirt portions 21 extend through the apertures 4 inthe annular plates 3 and have formed on their free ends radially directed flanges 22.
  • a barrier plate 23 Located within the housing 1 and at the middle of the axial length thereof is a barrier plate 23 secured to the housing 1. Secured one to each side of the barrier plate 23 are a pair of pole-pieces 24.
  • the pole-pieces 24 have the :form of a mandrel extending in an axial direction and are each of a length to extendfrom'the barrier plate 23 through the aperture 4 in the relatedend plate 3 so as to'terminate at the side of the end plate 3 remote from the barrier plate 23.
  • a portion of each pole-piece 24 is encompassed by the skirt 21 of the related piston 19 or 20 and at least this portion of each pole piece is of a diameter less than the internal diameter of the skirt 21.
  • the pole-pieces'24 have formed at their ends adjacent the barrier plate 23 radially directed flanges 25. Mounted between the flanges 25 of the pole pieces 24 and the flanges 22 on the piston skirts 21 are The two coil springs 26 coaxial with the pole-pieces 24. The springs 26 are secured at one end by 'bolts 27 "to the barrier plate 23 and at the other end to the piston skirts 21. The springs 26 are, in this case, formed by machining a helical slot in a tube.
  • the electromagnets 28 are secured to the end plates 3 by bolts 29.
  • direct current is supplied to the electromagnets 28 and a magnetic field is thereby formed between the end plates 3 and the pole-pieces 24.
  • These two magnetic fields are directed general-1y radially of the polepieces 24, that is, normal to the axes of the cylinders 5 and 6.
  • Alternating current is supplied through the leads 33 to the coils 31 and 32.
  • valve 12 in the cylinder head 7 opens and allows gas to flow from the cylinder 5.
  • valve 12 in the cylinder head 8 opens and allows gas now having been compressed in both stages to flow from the cylinder through the port 10 and conduit 15.
  • the compression and delivery of gas has a damping effect upon the reciprocating pistons but provided the i drive power of the linear motors constituted in part by the electromagnets 28 and the coils 31 and 32 is ade quate, such damping has little effect on the resonant frequencies of the piston and spring systems.
  • the constancy of the resonant frequency could be impaired if the dead volume of the cylinders, that is, the l volume of the gas space within the cylinders when the pistons are at the end of their compression strokes, were to be too large. Gas remaining in the dead volumeis at high pressure and exerts a force .on the related piston which is in the same direction as the force exerted on the. piston by the related spring and hence the gas in thecylinder performs work on the piston and tends to raise the resonant frequency of the piston and spring systems.
  • the springs 26 are formed by machining a helical slot in a tube.
  • rod or wire springs are formed by machining a helical slot in a tube.
  • tubular springs may be used.
  • FIGURE 2 shows diagrammatically a further embodiment of the present invention.
  • FIGURE 2 there is shown an electromagnet40 of right as seen in FIGURE 1.
  • a single coil spring 48 extends be: tween and is connected to the free ends of the coils 47.
  • Located radially within the coils 47 and coil spring .48 is a means of supports (not shown) extending through the coil spring 48 at the middle of the axial length of the spring 43, that is, the supports are located in the nodal plane of the spring 48.
  • the operation of the arrangement shown in FIGURE 2 is similar to that of the arrangement shown in FIGURE 1.
  • the electromagnet 40 is caused "to create magnetic fields across the annular gaps between the pole-pieces. 41 and the pole-piece 49.
  • Alternating current is passed through the coils 47 so that the pistons 45 and 46 tend to move in anti-phase relationship.
  • mag-- netic fields in which the coils 31 and 32 or 47 are located are described as being created by electromagnets 28 or 40 it is to be understood that permanent magnets may be used.
  • electromagnets excited by direct current enables the use of comparatively compact and low weight components for producing the magnetic field through the coils 31 and 32 or 47.
  • Electromagnets excited by alternating current may be used in place of the electromagnets 28 or 40 excited by direct current. In this case it is arranged that alternating currents in the coils of the electromagnets and in the moving coils are in phase. In the case where alternating currents of the same frequency are supplied to the electromagnets and to the coils it is necessary to arrange that the natural frequency of the piston and spring system is twice the frequency of the alternating currents.
  • etficiency of a compressor according to the present invention may be lower than that of a conventional induction motor it is high when compared to the eficiency of a compressor unit comprising a rotary motor and one or more reciprocating pistons.
  • Compressors constructed according to the present invention are well suited for operation at ambient temperatures and lower, and the absence of bearings, shaft seals, connecting rods and of liquid lubricants are important advantages in thatthey enable contamination of the gas to be avoided.
  • a compressor comprising:
  • a second cylinder rigidly connected to and located in alignment with said first cylinder
  • valve means allowing flow of the gas to be compressed into each cylinder and flow of compressed gas from each cylinder.
  • a compressor comprising:
  • a second cylinder rigidly connected to and located in axial alignment with said first cylinder
  • valve means allowing flow of the gas to be compressed into each cylinder and flow of compressed gas from each cylinder.
  • the said cylinders are in axially aligned opposition.
  • a compressor as in claim 2, wherein: the said means for producing two magnetic fields substantially radial of the axis ofthe cylinders comprises:
  • each of said springs is a helically cut tube.
  • a compressor comprising:
  • a second cylinder rigidly connected to and located in opposition to and in axial alignment with said first cylinder
  • valve means allowing flow of the gas to be compressed into each cylinder and fiow of compressed gas from each cylinder.
  • a compressor as in claim 10 wherein:
  • one of said cylinders has a larger cross-sectional area than the other of said cylinders.
  • a compressor as in claim 10 wherein: 5 ORE GN PA the said spring is a helically cut tube. 978,600 4/1951 Franca 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
US484410A 1964-09-04 1965-09-01 Compressors Expired - Lifetime US3286911A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB36451/64A GB1099223A (en) 1964-09-04 1964-09-04 Compressors

Publications (1)

Publication Number Publication Date
US3286911A true US3286911A (en) 1966-11-22

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US484410A Expired - Lifetime US3286911A (en) 1964-09-04 1965-09-01 Compressors

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US (1) US3286911A (xx)
GB (1) GB1099223A (xx)
NL (1) NL6511326A (xx)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3791770A (en) * 1973-05-24 1974-02-12 R Farkos Electromagnetic pump or motor device with axially spaced piston members
WO1984003139A1 (en) * 1983-02-14 1984-08-16 Gen Pneumatics Corp Closed cycle cryogenic cooling apparatus
WO1985003111A1 (en) * 1984-01-04 1985-07-18 Mechanical Technology Incorporated Multistage resonant compressor
US4566291A (en) * 1983-02-14 1986-01-28 General Pneumatics Corporation Closed cycle cryogenic cooling apparatus
US20040096345A1 (en) * 2002-11-14 2004-05-20 Mnde Technologies L.L.C. Fluid pumps with increased pumping efficiency
US20050023905A1 (en) * 2003-07-31 2005-02-03 Japan Servo Co., Ltd. Toroidal-coil linear stepping motor, toroidal-coil linear reciprocating motor, cylinder compressor and cylinder pump using these motors
EP2527653A1 (en) * 2011-05-23 2012-11-28 Nederlandse Organisatie voor toegepast -natuurwetenschappelijk onderzoek TNO A free piston type compressor
EP2921704A1 (en) * 2014-03-17 2015-09-23 Nederlandse Organisatie voor toegepast- natuurwetenschappelijk onderzoek TNO A free piston type fluid pump
US20170002801A1 (en) * 2015-07-01 2017-01-05 Lg Electronics Inc Linear compressor
US20170074255A1 (en) * 2015-09-11 2017-03-16 Toyota Jidosha Kabushiki Kaisha Fuel pump
US20170096988A1 (en) * 2015-10-01 2017-04-06 Toyota Jidosha Kabushiki Kaisha Fuel pump
US20170096987A1 (en) * 2015-10-06 2017-04-06 Toyota Jidosha Kabushiki Kaisha Fuel Pump
US10240589B2 (en) * 2016-04-14 2019-03-26 Toyota Jidosha Kabushiki Kaisha Plunger electric fuel pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR978600A (fr) * 1948-11-23 1951-04-16 Samga Et Bavox Ets Perfectionnements aux compresseurs, pompes et autres machines analogues
US2872101A (en) * 1955-12-19 1959-02-03 Stempel Hermetik Gmbh Electromagenetic compressor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR978600A (fr) * 1948-11-23 1951-04-16 Samga Et Bavox Ets Perfectionnements aux compresseurs, pompes et autres machines analogues
US2872101A (en) * 1955-12-19 1959-02-03 Stempel Hermetik Gmbh Electromagenetic compressor

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3791770A (en) * 1973-05-24 1974-02-12 R Farkos Electromagnetic pump or motor device with axially spaced piston members
WO1984003139A1 (en) * 1983-02-14 1984-08-16 Gen Pneumatics Corp Closed cycle cryogenic cooling apparatus
US4566291A (en) * 1983-02-14 1986-01-28 General Pneumatics Corporation Closed cycle cryogenic cooling apparatus
WO1985003111A1 (en) * 1984-01-04 1985-07-18 Mechanical Technology Incorporated Multistage resonant compressor
US4538964A (en) * 1984-01-04 1985-09-03 Mechanical Technology Incorporated Multistage resonant compressor
US20040096345A1 (en) * 2002-11-14 2004-05-20 Mnde Technologies L.L.C. Fluid pumps with increased pumping efficiency
WO2004044421A2 (en) * 2002-11-14 2004-05-27 Mnde Technologies L.L.C. Fluid pumps with increased pumping efficiency
WO2004044421A3 (en) * 2002-11-14 2004-07-01 Mnde Technologies L L C Fluid pumps with increased pumping efficiency
US20050023905A1 (en) * 2003-07-31 2005-02-03 Japan Servo Co., Ltd. Toroidal-coil linear stepping motor, toroidal-coil linear reciprocating motor, cylinder compressor and cylinder pump using these motors
US7242118B2 (en) * 2003-07-31 2007-07-10 Japan Servo Co., Ltd. Toroidal-coil linear stepping motor, toroidal-coil linear reciprocating motor, cylinder compressor and cylinder pump using these motors
EP2527653A1 (en) * 2011-05-23 2012-11-28 Nederlandse Organisatie voor toegepast -natuurwetenschappelijk onderzoek TNO A free piston type compressor
WO2012161575A1 (en) * 2011-05-23 2012-11-29 Nederlandse Organisatie Voor Toegepast-Natuurwetenschappelijk Onderzoek Tno A free piston type torsion drive compressor
EP2921704A1 (en) * 2014-03-17 2015-09-23 Nederlandse Organisatie voor toegepast- natuurwetenschappelijk onderzoek TNO A free piston type fluid pump
US20170002801A1 (en) * 2015-07-01 2017-01-05 Lg Electronics Inc Linear compressor
US10371131B2 (en) * 2015-07-01 2019-08-06 Lg Electronics Inc. Linear compressor
US20170074255A1 (en) * 2015-09-11 2017-03-16 Toyota Jidosha Kabushiki Kaisha Fuel pump
US10180122B2 (en) * 2015-09-11 2019-01-15 Toyota Jidosha Kabushiki Kaisha Fuel pump
US20170096988A1 (en) * 2015-10-01 2017-04-06 Toyota Jidosha Kabushiki Kaisha Fuel pump
US10066613B2 (en) * 2015-10-01 2018-09-04 Toyota Jidosha Kabushiki Kaisha Fuel pump
US20170096987A1 (en) * 2015-10-06 2017-04-06 Toyota Jidosha Kabushiki Kaisha Fuel Pump
US10087916B2 (en) * 2015-10-06 2018-10-02 Toyota Jidosha Kabushiki Kaisha Fuel pump
US10240589B2 (en) * 2016-04-14 2019-03-26 Toyota Jidosha Kabushiki Kaisha Plunger electric fuel pump

Also Published As

Publication number Publication date
GB1099223A (en) 1968-01-17
NL6511326A (xx) 1966-03-07

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