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EP1657452A1 - Oscillateur pneumatique - Google Patents

Oscillateur pneumatique Download PDF

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Publication number
EP1657452A1
EP1657452A1 EP04026664A EP04026664A EP1657452A1 EP 1657452 A1 EP1657452 A1 EP 1657452A1 EP 04026664 A EP04026664 A EP 04026664A EP 04026664 A EP04026664 A EP 04026664A EP 1657452 A1 EP1657452 A1 EP 1657452A1
Authority
EP
European Patent Office
Prior art keywords
oscillator
piston
control section
oscillator device
chamber
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
EP04026664A
Other languages
German (de)
English (en)
Other versions
EP1657452B1 (fr
Inventor
Steffen Hülsmann
Heiko Haase
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.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
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 Festo SE and Co KG filed Critical Festo SE and Co KG
Priority to DE200450005715 priority Critical patent/DE502004005715D1/de
Priority to EP04026664A priority patent/EP1657452B1/fr
Priority to DK04026664T priority patent/DK1657452T3/da
Publication of EP1657452A1 publication Critical patent/EP1657452A1/fr
Application granted granted Critical
Publication of EP1657452B1 publication Critical patent/EP1657452B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/04—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member with oscillating cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/224—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston which closes off fluid outlets in the cylinder bore by its own movement

Definitions

  • the invention relates to a pneumatic oscillator device, comprising an oscillator housing, in which there is an oscillating chamber, in which an oscillator piston is arranged linearly displaceable back and forth, which divides the oscillation chamber axially into two working chambers, which are alternately acted upon in opposite directions with compressed air and vented to to cause an oscillatory movement of the oscillator piston between two end positions.
  • a valve slide is caused to oscillate by alternately loading and unloading two external working chambers in order to supply or relieve two outputs alternately with a fluid.
  • an additional valve device is provided, in which internal fluid flows influence one another in such a way that the connected working chambers are alternately pressurized and vented. The necessary control engineering and construction effort is relatively large.
  • the oscillator device is used to generate electrical energy
  • at least one permanent magnet is coupled in motion with the oscillator piston, which thus participates in the oscillatory motion and which is arranged so that it moves relative to a relative to the oscillator housing coil assembly, so that an electrical voltage is induced therein, which can be tapped as electrical energy for any purpose.
  • an electrical voltage is induced therein, which can be tapped as electrical energy for any purpose.
  • the oscillator piston In order to ensure a relatively large stroke of the oscillator piston, the oscillator piston during its reciprocating movement expediently passes through a transitional movement phase during which it shuts off all supply air and exhaust air openings. Due to the pressure difference between the trapped in the working chambers volumes during this transitional movement phase further safe movement is ensured without compressed air is supplied and discharged with respect to the working chambers. If a very high-frequency Oszillatonsterrorism be generated, which requires only a small stroke, can also be dispensed with the aforementioned transition movement phase. In particular, the gradual continuous closing of one opening may then be superposed with the gradual, continuous opening of the other openings, and vice versa.
  • a particularly high-frequency oscillation movement is also favored by the fact that the oscillator piston is arranged without seal displaceable in the oscillation chamber.
  • the coefficient of friction can be reduced to a minimum in this way.
  • one of the working chambers via a throttle point can be permanently connected to a compressed air source, which pressure moderately ensures a slight asymmetry, which has a preferred position of the oscillator piston result , In regular operation, this pressurization does not cause any significant adverse effects due to the very low flow rate.
  • measures which enable a mechanical displacement of the oscillator piston into an end position for example an actuating tappet protruding from the oscillator housing.
  • the oscillator piston two axially spaced, each having an axial control length having control sections, between which is arranged by at least one circumferential piston recess of the oscillator piston axially offset from each control section Beaufschlagungsabterrorism, wherein the both sides of the Beaufschlagungsabterrorismes lying piston recesses are each connected via at least one compensation channel with the disposed beyond the immediately adjacent control section working chamber, wherein at least a first and second exhaust opening are present, the axially spaced circumferentially open into the oscillation chamber and wherein, moreover, at least one first and second supply air opening are provided, the axially spaced from each other between the two exhaust openings open circumferentially in the oscillation chamber.
  • the position of the Zu poverty- and exhaust air openings and the dimensions and the stroke length of the oscillator piston are coordinated so that in each of the two axial end positions of the oscillator piston, the one exhaust opening covered and shut off by its associated control section and the other exhaust port with its associated working chamber is connected, while at the same time communicates the each closed exhaust port adjacent supply air opening with the shut-off control section adjacent piston recess and the other air inlet opening is covered and shut off by the other control section.
  • a gradual closure of the hitherto open and a gradual opening of the hitherto sealed Zu Kunststoffbuch- or exhaust port instead, with reverse opening and closing behavior when approaching the opposite end position. It can be provided an intermediate transition-movement phase, in which all Zu poverty- and exhaust air openings are covered and shut off by the two control sections.
  • the compensation channels ensure that there is constant pressure equalization at the control sections and that they only act on the oscillator piston in the currently desired direction of movement to produce effective pressure forces.
  • Mainly responsible for the oscillator piston moving force are provided axially on both sides of the loading portion of the oscillator piston surfaces.
  • the two piston recesses are expediently designed in each case in the manner of annular grooves.
  • the equalizing channels can be borehole-like channels which axially pass the control section away from the center line, opening at one end to the associated working chamber and at the other end to the associated piston recess.
  • the compensation channels can also be provided as groove-like circumferential recesses or recesses on the outside of the control section.
  • the oscillator device is used to generate electrical energy, wherein a permanent magnet is coupled to the oscillator piston, there is, inter alia, the possibility of fixing the permanent magnet to a rod which is fixed on the oscillator piston and projects axially out of the oscillation chamber.
  • the coil assembly sits in such a case coaxially following the oscillation chamber.
  • the coil arrangement coaxially surrounds the oscillation chamber, wherein the permanent magnet is arranged directly on the oscillator piston within the oscillation chamber.
  • FIGS. 1 to 4 and on the other in FIG. 5 are designed as examples in such a way that electrical energy can be generated with their help solely through the use of compressed air.
  • FIGS. 1 to 4 and on the other in FIG. 5 are designed as examples in such a way that electrical energy can be generated with their help solely through the use of compressed air.
  • other applications of the oscillator device 1 with corresponding constructive modification are also possible without departing from the inventive concept.
  • the oscillator device 1 has an oscillator housing 2, in which an elongated, preferably a cylindrical cross-section having oscillation chamber 3 is formed.
  • an elongated, preferably a cylindrical cross-section having oscillation chamber 3 is formed.
  • it is a circular cylindrical oscillation chamber 3, although elongated cross-sectional shapes would be possible, for example elliptical type or with straight longitudinal sides and semi-circular narrow sides.
  • the oscillator housing 2 is indicated only schematically. According to FIGS. 1 to 4, it may be composed of several components, in particular a pipe section 5 defining the peripheral peripheral surface 4 of the oscillation chamber 3 and two housing covers 7a, 7b defining the axial end surfaces 6a, 6b of the oscillation chamber 3, the latter being sealed to the pipe section 5 are connected. For connection fastening screws 8 can be used.
  • the end surfaces defining abutment surfaces can also be specified by other fixed to the housing surfaces, for example, with respect to the housing adjustable stop members.
  • the oscillator piston 13 divides in the oscillation chamber 3, two axially outer first and second working chambers 14a, 14b from each other, change their volumes during the oscillatory motion 12 by these alternately in opposite directions become larger and smaller.
  • the oscillator piston 13 has a subdivided into a plurality of fixedly interconnected sections structure. Axially in the middle of the oscillator piston 13 has a biasing portion 15, whose outer periphery is formed complementary to the inner periphery of the oscillation chamber 3 and slidably abuts against the peripheral surface 4.
  • the loading section 15 is adjoined axially on both sides, with the interposition of a respective first and second piston recess 16a, 16b having a certain axial length, a first or second control section 17a, 17b, which also has a control length "a" on the peripheral surface 4 slidably applied.
  • the outer contour of the control sections 17 a, 17 b corresponds to the cross-sectional contour of the oscillation chamber 3.
  • the piston recesses 16a, 16b are expediently designed in the manner of annular grooves which extend along the entire piston circumference, wherein they are open towards the circumferential surface 4.
  • the axial length of Piston recesses 16a, 16b smaller than that of the loading portion 15 and the control portions 17a, 17b. Conveniently, they are slit-like narrow.
  • a first and a second supply air opening 22a, 22b are present, both of which open into the oscillation chamber 3 in the region lying axially between the junctions of the two exhaust air openings 18a, 18b on the circumference.
  • These two supply air openings 22a, 22b are in turn axially spaced from each other, wherein the first supply air opening 22a closer to the first exhaust port 18a and the second supply air port 22b closer to the second exhaust port 18b.
  • the first exhaust air opening 18a is associated with the first axial end surface 6a lying on the left in the drawing, while the second exhaust air opening 18b is located in the vicinity of the second axial end surface 6b lying on the right in the drawing.
  • the distribution of the junctions of the various openings 18a, 18b, 22a, 22b along the circumference of the oscillation chamber 3 is arbitrary in the embodiment in which both the piston recesses 16a, 16b and the control portions 17a, 17b extend along the entire circumference of the piston.
  • the junctions of the exhaust ports 18a, 18b and on the other hand the junctions of the supply air openings 22a, 22b with each other an axially extending line on diametrically opposite sides.
  • the two supply air openings 22a, 22b are constantly connected to a compressed air source "P" during operation of the oscillator device.
  • each supply air opening 22a, 22b communicates with a supply air duct 24 penetrating the housing wall.
  • each channel 22, 23 is provided with a coupling piece 25 in which a fluid line, for example, an elastic hose, releasably fixable under sealing, for example in the context of a plug connection.
  • a fluid line for example, an elastic hose
  • the exhaust ducts 23 may terminate freely on the outer circumference of the oscillator housing 2, without connection possibility for a fluid line, if a direct connection to the immediate atmospheric environment of the oscillator device 1 is desired.
  • the arrangement and distribution of the mouths of the exhaust ports 18a, 18b and inlet openings 22a, 22b and the configuration of the oscillator piston 13 are coordinated so that the oscillator piston 13 forms a valve member with respect to the exhaust ports and air inlets, which in response to its current position certain interconnection between on the one hand the exhaust ports 18a, 18b and supply air openings 22a, 22b and on the other hand causes the two working chambers 14a, 14b.
  • This interconnection manifests itself in that there are opposite pressure differences between the two working chambers 14a, 14b in the two end positions of the oscillator piston 13.
  • this integrated self-controlling function ensures that the oscillator piston 13 performs the oscillatory movement 12 and causes the reversal of its direction of movement itself when reaching the end positions, if only at the two supply air openings 22a, 22b, an overpressure and at the two exhaust ports 18a, 18b a lower in this regard Pressure, preferably atmospheric pressure, is applied.
  • the design in the embodiments is also made such that during the movement of the oscillator piston 13 between its two end positions, a transitional movement phase occurs during which the oscillator piston 13 all Zu Kunststoff- and exhaust ports 18 a, 18 b; 22a; 22b from the oscillation chamber 3 blocks.
  • a transitional movement phase occurs during which the oscillator piston 13 all Zu Kunststoff- and exhaust ports 18 a, 18 b; 22a; 22b from the oscillation chamber 3 blocks.
  • the oscillator piston 13 bears against the first axial end surface 6a, wherein the first exhaust air opening 18a is covered and shut off by the first control section 17a located radially inwards.
  • the first exhaust air opening 18a expediently lies in the vicinity of the first piston recess 16a, which in turn is connected to the first supply air opening 22a by being radially aligned therewith.
  • the second exhaust port 18b is in the first end position on the axial side of the second control portion 17b opposite to the urging portion 15, and is not covered thereby, so that it is connected to the second working chamber 14b.
  • the second supply air opening 22b is simultaneously covered and closed radially inwardly by the second control section 17b. In this case, the second supply air opening 22b is located in the vicinity of the end region of the second control section 17b opposite the loading section 15.
  • the opposite orifices are located on the axially outer end face of the respective control section 17a, 17b.
  • the compensation channels 26a, 26b are formed in the embodiment bore-like. However, it is also possible, for example, a design in the form of axially extending surface depressions on the outer circumference of the associated control section, as indicated by dash-dotted lines in Figure 5 at 26c exemplified.
  • a plurality of compensation channels 26a, 26b distributed around the longitudinal axis 27 are provided per control section 17a, 17b, each of which causes a plurality of parallel fluid connections.
  • the same overpressure prevails in the above-mentioned first end position in the first working chamber 14a as in the first piston recess 16a communicating with the first supply air opening 22a. Accordingly, the same low pressure or atmospheric pressure prevails in the second piston recess 17b as in the second working chamber 14b communicating with the exhaust opening 18b.
  • the first end position prevails in the first working chamber 14a, a much higher pressure than in the second working chamber 14b, so that the force F S1 is greater than the oppositely acting force F S2 and the oscillator piston 13 is in the direction of the second end position in motion. Due to the selected control length "a" of the two control sections 17a, 17b, the first exhaust air opening 18a and the second supply air opening 22b remain closed while the first supply air opening 22a and the second exhaust air opening 18b simultaneously move through the control section 17a moving over it. 17b gradually closed.
  • indications of pressures in the working chambers 14a, 14b are to be understood as indications of the respective volume combination consisting of assigned piston recess and exhaust air openings extending therebetween.
  • the second exhaust air opening 18b and the first supply air opening 22a remain shut off, while the first exhaust air opening 18a communicates with the first working chamber 14a and the second supply air opening 22b with the second piston recess 16b and thus with the second working chamber 14b occurs.
  • the oscillator piston 13 has not yet reached its second end position.
  • the first supply air opening 22a and the second exhaust opening 18b are further blocked by the overlap on the part of the associated control section 17a, 17b, while the second supply air opening 22b communicates with its full cross section with the second piston recess 16b and thus the second working chamber 14b, while at the same time the first exhaust port 18a is connected with its full cross section with the first working chamber 14a.
  • the stopped in the second end position oscillator piston 13 immediately includes the return movement in the first end position shown in Figure 1, the described movements occur again, but now in the opposite direction.
  • one of the working chambers 14b is expediently connected permanently to a compressed air source via a throttle point 32.
  • a throttle point 32 By this preferred designed as a bore with a very small cross-section throttle point to achieve a slight asymmetry in the balance of power, which has the consequence that the oscillator piston is forced to start operation in an end position, from which then start the oscillation movement.
  • the compressed air source used to supply the throttle point 32 suitably agrees with those to which the supply air openings 22a, 22b are connected.
  • the throttle body 32 may be connected in the housing wall to the common channel 24 '.
  • the throttling channel 32 'assigned to the throttle position 32 may be separate from the outer surface the oscillator housing, where a further coupling piece 25 'may be provided, via which a fluid line leading to the compressed air source can be releasably connected.
  • the oscillator piston 13 is expediently arranged without a seal in the oscillation chamber 3 in a sliding manner. Exact processing guarantees the valve function required for operation even without elastomeric sealants by shutting off and releasing the supply air and exhaust air openings.
  • the oscillator piston 13 is used as a drive member for a movement tap. More precisely, the oscillator piston 13 serves to generate an oscillating stroke movement 33 of a permanent magnet 34, indicated by a double arrow, relative to a coil arrangement 35 fixed with respect to the oscillator housing 2.
  • the already mentioned rod 28 acts as a support for the at least one permanent magnet 34.
  • the preferably integrally formed with the oscillator piston 13 rod 28 passes through a working chamber 14b and this final lid 7b in an axially movable manner and is outside of the oscillation chamber 3 equipped with the permanent magnet 34.
  • the coil arrangement 35 is arranged coaxially to the longitudinal axis 27 of the oscillator piston 13 and attached to the oscillator housing 2 via a holder 36.
  • the permanent magnet 34 moves continuously in opposite directions through the coil assembly 35, in which thus an electrical voltage is induced, which can be tapped for the operation of electrical and / or electronic means.
  • the coil assembly 35 is disposed in coaxial extension of the oscillation chamber 3 outside the same, the coil assembly 35 is in the embodiment of Figure 5 in a the oscillation chamber 3 coaxially enclosing constellation.
  • the responsible for the magnetic induction at least one permanent magnet 34 is seated in this case directly on the oscillator piston 13 within the oscillation chamber 3, so that a lead out of the oscillator piston 13 motion-coupled actuators from the oscillation chamber 3 is unnecessary.
  • a lead out of the oscillator piston 13 motion-coupled actuators from the oscillation chamber 3 is unnecessary.
  • a modification of the design according to FIGS. 1 to 4 can be made instead of the rodless embodiment shown in FIG opposite axial side a rod 28 'of the same cross-section through the local housing cover 7a leads out, which is also connected to the oscillator piston 13. If required, a movement tap may also be effected on this further rod 28 ', for example in order to drive a further permanent magnet co-operating with a second coil arrangement.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP04026664A 2004-11-10 2004-11-10 Oscillateur pneumatique Expired - Lifetime EP1657452B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE200450005715 DE502004005715D1 (de) 2004-11-10 2004-11-10 Pneumatische Oszillatorvorrichtung
EP04026664A EP1657452B1 (fr) 2004-11-10 2004-11-10 Oscillateur pneumatique
DK04026664T DK1657452T3 (da) 2004-11-10 2004-11-10 Pneumatisk oscillatoranordning

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04026664A EP1657452B1 (fr) 2004-11-10 2004-11-10 Oscillateur pneumatique

Publications (2)

Publication Number Publication Date
EP1657452A1 true EP1657452A1 (fr) 2006-05-17
EP1657452B1 EP1657452B1 (fr) 2007-12-12

Family

ID=34927316

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04026664A Expired - Lifetime EP1657452B1 (fr) 2004-11-10 2004-11-10 Oscillateur pneumatique

Country Status (3)

Country Link
EP (1) EP1657452B1 (fr)
DE (1) DE502004005715D1 (fr)
DK (1) DK1657452T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
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WO2011056855A1 (fr) * 2009-11-03 2011-05-12 Sustainx, Inc. Systèmes et procédés de stockage d'énergie produite par un gaz comprimé au moyen d'ensembles vérins couplés
CN107014583A (zh) * 2017-05-08 2017-08-04 大连理工大学 一种多功能两端开口压力振荡管测试平台
CN107917928A (zh) * 2017-11-01 2018-04-17 大连理工大学 一种双开口多管束制冷机非稳态导热测试平台
CN109114067A (zh) * 2018-09-21 2019-01-01 仁兴机械（佛山）有限公司 一种气缸、油缸结构

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US8250863B2 (en) 2008-04-09 2012-08-28 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8474255B2 (en) 2008-04-09 2013-07-02 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8677744B2 (en) 2008-04-09 2014-03-25 SustaioX, Inc. Fluid circulation in energy storage and recovery systems
US7958731B2 (en) 2009-01-20 2011-06-14 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US7802426B2 (en) 2008-06-09 2010-09-28 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
US8359856B2 (en) 2008-04-09 2013-01-29 Sustainx Inc. Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery
US8448433B2 (en) 2008-04-09 2013-05-28 Sustainx, Inc. Systems and methods for energy storage and recovery using gas expansion and compression
US8479505B2 (en) 2008-04-09 2013-07-09 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8037678B2 (en) 2009-09-11 2011-10-18 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US20100307156A1 (en) 2009-06-04 2010-12-09 Bollinger Benjamin R Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage and Recovery Systems
US8240140B2 (en) 2008-04-09 2012-08-14 Sustainx, Inc. High-efficiency energy-conversion based on fluid expansion and compression
US7832207B2 (en) 2008-04-09 2010-11-16 Sustainx, Inc. Systems and methods for energy storage and recovery using compressed gas
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
US8171728B2 (en) 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems
US8191362B2 (en) 2010-04-08 2012-06-05 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8234863B2 (en) 2010-05-14 2012-08-07 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8495872B2 (en) 2010-08-20 2013-07-30 Sustainx, Inc. Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas
US8578708B2 (en) 2010-11-30 2013-11-12 Sustainx, Inc. Fluid-flow control in energy storage and recovery systems
WO2012158781A2 (fr) 2011-05-17 2012-11-22 Sustainx, Inc. Systèmes et procédés pour un transfert thermique biphasé efficace dans des systèmes de stockage d'énergie à air comprimé
US20130091836A1 (en) 2011-10-14 2013-04-18 Sustainx, Inc. Dead-volume management in compressed-gas energy storage and recovery systems

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US385113A (en) * 1888-06-26 of kupfebhammee
US835290A (en) * 1905-12-07 1906-11-06 Clarence H Richwood Fluid-actuated vibrator.
US2763060A (en) * 1952-07-28 1956-09-18 Bernard A Swanson Fluid pressure operated reciprocatory vibratory sheet material cutting shears
CH337157A (de) * 1954-12-18 1959-03-15 Mohr Rudolf Dr Pressluftarbeitsgerät
US5195560A (en) * 1992-04-27 1993-03-23 Muchlis Achmad Adjustable low frequency hydrofluidic oscillator
DE19636207A1 (de) * 1996-09-06 1998-03-12 Samson Ag Elektrisch-fluidischer Wandler
EP1071195A2 (fr) * 1999-07-21 2001-01-24 Westinghouse Air Brake Company Générateur électrique à entraínement pneumatique avec haut rendement

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Publication number Priority date Publication date Assignee Title
US385113A (en) * 1888-06-26 of kupfebhammee
US835290A (en) * 1905-12-07 1906-11-06 Clarence H Richwood Fluid-actuated vibrator.
US2763060A (en) * 1952-07-28 1956-09-18 Bernard A Swanson Fluid pressure operated reciprocatory vibratory sheet material cutting shears
CH337157A (de) * 1954-12-18 1959-03-15 Mohr Rudolf Dr Pressluftarbeitsgerät
US5195560A (en) * 1992-04-27 1993-03-23 Muchlis Achmad Adjustable low frequency hydrofluidic oscillator
EP0638145B1 (fr) 1992-04-27 1997-02-26 Hr Textron Inc. Oscillateur reglable a fluide hydraulique et a basse frequence
DE19636207A1 (de) * 1996-09-06 1998-03-12 Samson Ag Elektrisch-fluidischer Wandler
DE19636207C2 (de) 1996-09-06 2000-08-03 Samson Ag Elektrisch-fluidischer Wandler
EP1071195A2 (fr) * 1999-07-21 2001-01-24 Westinghouse Air Brake Company Générateur électrique à entraínement pneumatique avec haut rendement

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011056855A1 (fr) * 2009-11-03 2011-05-12 Sustainx, Inc. Systèmes et procédés de stockage d'énergie produite par un gaz comprimé au moyen d'ensembles vérins couplés
CN107014583A (zh) * 2017-05-08 2017-08-04 大连理工大学 一种多功能两端开口压力振荡管测试平台
CN107014583B (zh) * 2017-05-08 2023-07-04 大连理工大学 一种多功能两端开口压力振荡管测试平台
CN107917928A (zh) * 2017-11-01 2018-04-17 大连理工大学 一种双开口多管束制冷机非稳态导热测试平台
CN107917928B (zh) * 2017-11-01 2024-02-02 大连理工大学 一种双开口多管束制冷机非稳态导热测试平台
CN109114067A (zh) * 2018-09-21 2019-01-01 仁兴机械（佛山）有限公司 一种气缸、油缸结构

Also Published As

Publication number Publication date
DK1657452T3 (da) 2008-01-07
DE502004005715D1 (de) 2008-01-24
EP1657452B1 (fr) 2007-12-12

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