EP2549123A2 - Hydro-pneumatic drive system with one or more double medium working cylinders - Google Patents

Hydro-pneumatic drive system with one or more double medium working cylinders Download PDF

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Publication number
EP2549123A2
EP2549123A2 EP20120005348 EP12005348A EP2549123A2 EP 2549123 A2 EP2549123 A2 EP 2549123A2 EP 20120005348 EP20120005348 EP 20120005348 EP 12005348 A EP12005348 A EP 12005348A EP 2549123 A2 EP2549123 A2 EP 2549123A2
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EP
European Patent Office
Prior art keywords
working
compressed air
medium
double
drive system
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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.)
Withdrawn
Application number
EP20120005348
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German (de)
English (en)
Inventor
Otto Schell
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Individual
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Individual
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Publication date
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Publication of EP2549123A2 publication Critical patent/EP2549123A2/fr
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    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems

Definitions

  • the invention relates to a hydropneumatic drive system with at least one double-medium working cylinder, which has a working piston which can be moved in a working chamber.
  • Known pneumatic drives are known e.g. equipped with a standardized according to ISO 15552 working cylinder. Such has a profiled tube-like elongated housing with an inner working chamber. In this, a working piston between two end positions can be linearly reciprocated.
  • the working piston has a piston plate which is sealed radially with respect to the inner lateral surface of the working chamber, on which a piston, e.g. attached to one end of the housing led out piston rod.
  • the working chamber of the working piston is divided into two areas at the end connections for compressed air hoses of a compressed air working system are available.
  • the piston plate and attached thereto led out to the outside of the working cylinder piston rod can be placed either in a linear feed or return movement or a forward and reverse rotation.
  • different working means can be driven in manufacturing equipment via the piston rod of the working piston.
  • the invention is based on the object of designing a drive system such that, while avoiding the above-mentioned disadvantages traversing movements of a working piston both at a uniform speed and high accuracy as well as saving energy are executable
  • the invention is based on a mutual control of the divided by a movable piston in two areas working chamber of a working cylinder with different working media.
  • This is referred to below as a double-medium working cylinder and can be designed both as a linear working cylinder and as a rotary working cylinder.
  • a first part of the working chamber which can also be referred to as a pneumatic chamber part, can be connected to an active compressed air generator and controlled with compressed air.
  • the remaining on the other side of the working piston second part of the working chamber which can also be referred to as a hydraulic chamber part, coupled to a closed storage device and filled with a pressurized hydraulic medium over this.
  • the closed storage device contains a pressure compensation container for receiving the hydraulic medium which is under a pre-pressure via a compressed air cushion in the pressure compensation container.
  • the form of the compressed air cushion is set so that it is smaller than the minimum working pressure of the compressed air of the compressed air generator even at a maximum level of the hydraulic medium in the surge tank.
  • the pre-pressure of the hydraulic medium in the second part of the working chamber is thus always smaller than the minimum working pressure of the compressed air in the first part of the working chamber, by a connection of the compressed air from the active compressed air generator with the aid of a compressed air distributor in each case a linear or rotary movement of the working piston in the double-medium working cylinder.
  • the pneumatic chamber part of the working chamber thus increases and the hydraulic chamber part accordingly.
  • the hydraulic medium is displaced into the surge tank of the closed storage device.
  • the working piston is to move to a second, opposite position
  • the compressed air distributor is shut off via the compressed air distributor and the first part of the working chamber is opened, especially to the surroundings.
  • the pneumatic chamber part is now no longer under pressure and the pressurized hydraulic medium can flow back from the surge tank of the closed storage device.
  • the working piston is thus moved in the opposite direction, so that the hydraulic chamber part increases again and is filled with hydraulic fluid, and the pneumatic chamber part is vented through the opening and decreases accordingly.
  • the linear drive system according to the invention enables uniform, rattle-free movements of the working piston in both directions of travel. These are comparable to the movements generated by a purely hydraulically operated device. However, since in the invention on the high pressure side compressed air is used as the drive medium, they can be produced with considerably less effort than in a pure hydraulic system. There complex hydraulic pumps are required. In addition, significantly higher demands on the tightness of a hydraulic system must be made.
  • the hydropneumatic drive system according to the invention further enables a precise control of the movement of the piston rod of the working cylinder.
  • the piston rod can be stopped precisely by actuation of the controllable compressed air distributor with reaching a predetermined linear position or angular position or at this point the travel direction can be changed.
  • the current position may be supplemented with an additional e.g. electronic or optical linear scale or angular position sensor.
  • the repeatability at start and stop operations of the working cylinder has an order of magnitude of about 0.20 mm in the drive system according to the invention.
  • the double-medium working cylinder offers the further advantage that only the compressed air required for operation must be supplied by the compressed air generator on the pneumatic high-pressure side. This is determined by the throttle effect of the hydraulic low-pressure side of the working chamber, that is, by the possibly adjustable flow rate of the pressurized hydraulic medium between the hydraulic chamber part and the surge tank of the closed storage device.
  • a closed expansion vessel in particular a Membranausdehungsgefäß.
  • this can be done, for example, by a membrane expansion vessel from the heating industry or a large, tank-shaped Ausdehungsgefäße be used.
  • This can be done away from the dual medium working cylinders e.g. be placed in a separate room or building.
  • the double-medium working cylinder thus has no additional external attachments.
  • a hydraulic medium in addition to hydraulic oil and a liquid is suitable, which have lubricating properties.
  • a known from the metal cutting machining cooling lubricant can be used, e.g. Drilling water or cutting oil.
  • Such a medium ensures a constant lubrication of the working piston. Furthermore, leaks are immediately visible.
  • a particular advantage of the invention is that the storage device for the pressurized hydraulic medium is a closed system.
  • the local pressure equalization tank must therefore be filled only once with hydraulic medium during commissioning of the device according to the invention and acted upon with the respective required form.
  • a compressed air cushion forms above the current fill level of the hydraulic medium in the surge tank of the closed storage device.
  • the compressed air cushion can be used independently for a long time autonomously to carry out a plurality of traversing movements of one or more parallel-connected double-medium working cylinder without further expenditure of auxiliary energy.
  • Another advantage of the invention is that compressed air is used as the working medium on the drive side. This can be easily generated and easily distributed to a plurality of workstations of a manufacturing facility. In addition, compressed air is only needed for refilling the pneumatic chamber part of a double-medium working cylinder, while no energy has to be expended for driving the working piston from the hydraulic side during operation. This results in the production of compressed air savings in energy costs of 50 to 80% compared to fully pneumatic actuators.
  • the reverse side after a filling of the memory with hydraulic medium and the one-time initial training of a Compressed air cushion can be operated by applying the pressure equalization tank with pre-pressure during operation without further energy consumption. Furthermore, there is a reduction of operating noise by about 50%, since no venting of the working chamber is required in a movement of the working piston against the pressurized hydraulic medium.
  • the hydropneumatic drive system according to the invention is thus particularly effective and economically operable without much effort. It does not require an independent hydraulic system with separate pressure generation or a double-sided pneumatic system. Rather, both the pneumatically induced working movement in the one direction of travel and the hydraulically induced working movement can be generated in the opposite working movement with the same working cylinder. This represents as a double-medium working cylinder thus the only structural unit between the two media circles.
  • different travel speeds of the working pistons in one or more double-medium working cylinders during a power stroke can be achieved by throttling the flow rate of the hydraulic medium.
  • an adjustable throttle device between the second part of a working chamber and the closed storage device for the pressurized hydraulic medium is particularly advantageous.
  • an adjustable throttle device e.g. a valve with variable flow cross section suitable.
  • FIG. 1 shows the block diagram of a first embodiment of executed according to the invention hydropneumatic drive system.
  • This contains a running example as a linear actuator double-medium working cylinder B, which in the example of Fig. 1 on the left side via a compressed air connection A1 with compressed air LV and on the example of the Fig. 1 right side is fed via a hydraulic port A2 with a pressurized hydraulic medium HM.
  • the double-medium working cylinder B forms a combined pneumatic and hydraulic cylinder for driving a in the example of Fig. 1
  • the working piston K with piston plate KZ and piston rod KS can under the influence of the two controlling media in a first direction of travel KV, eg a feed, and a second direction of travel KR, eg a retract, off or retracted.
  • the working chamber A in a first part AL also called pneumatic chamber part
  • a second part AF also called hydraulic chamber part divided.
  • a supply V21 of compressed air LV for a feed KV or a discharge V22 of compressed air LV takes place at a return KR of the working piston K.
  • the hydraulic connection A2 in push-pull a discharge H21 of hydraulic medium HM at a feed KV in the surge tank H and a supply H22 of hydraulic medium HM at an automatic return KR of the working piston K.
  • the value of the compressed air cushion HD exerted on the hydraulic medium HM in the surge tank H in each case is less than the working pressure of the compressed air LV, is switched on the connection of compressed air LV of the working piston K in a feed KV and thereby the hydraulic medium HM on the Hydraulic connection A2 in the surge tank H of the closed Memory device M displaced. If, on the other hand, the compressed air LV is switched off and the pneumatic chamber part AL of the working chamber A is opened, a return KR of the working piston K is made possible by the prestressed hydraulic medium HM pushing back into the hydraulic chamber portion AF and the hydraulic chamber portion AL is vented.
  • a controllable compressed air system P available.
  • This contains an active compressed air generator D with a compressor D1 and a compressed air storage tank D2 fed by it.
  • the compressed air LV generated therefrom is fed to a controllable compressed air distributor V, in particular a valve, via a feed V1 as supply air V21.
  • the compressed air distributor V can be switched over by an electrical control signal V41 between two operating states. In a first operating state, the compressed air V22 is supplied via the outlet V2 to the double-medium working cylinder A for carrying out a feed KV.
  • the compressed air supply LV is shut off and the first part AL of the working chamber A is opened via a vent V3, in particular with respect to the surrounding atmosphere.
  • the exhaust air L22 located therein can thus escape and the working piston A perform a return thrust KR, in particular into a starting position.
  • the closed storage device M for the pressurized hydraulic medium contains a surge tank as a passive hydraulic accumulator H. This has a filling with hydraulic medium HM. Volume and pressure equalization takes place by means of a compressed air cushion HD located above it and under a pre-pressure. A filling and pressurization is possible via a closable feed H1.
  • the hydraulic medium HM can flow back through an outlet H2 at the bottom of the surge tank H in the double medium working cylinder B, or is at feed KV from the double-medium working cylinder out preferably over an additional, interposed adjustable throttle device W back into the Pressure equalizing tank H pushed back.
  • the degree of filling with hydraulic medium in the interior of the surge tank H varies.
  • the working piston K in eg a starting position at the left end of the working chamber A, the second part AF of the working chamber A is almost completely filled with hydraulic medium. Accordingly, the surge tank H has emptied and the level of the hydraulic medium assumes a minimum value.
  • the working piston K in eg an end position at the right end of the working chamber A, the second part AF of the working chamber A is almost completely emptied. Accordingly, the surge tank H has filled and the level of the hydraulic medium assumes a maximum value.
  • the flow rate of the hydraulic medium HM and thus the travel speed of the working piston A can be adjusted.
  • an electrical control signal W1 can this example in the example of Fig. 2 exemplary parallel throttle elements W2, which have different flow cross sections for the hydraulic medium HM, are switched on or shut off.
  • the representation of the throttle device W is only an example. In practice, this can be carried out for example by a suitably designed and controllable valve
  • Fig. 2 shows one with the example of Fig. 1 comparable linear drive system. Since all elements are present accordingly, this can basically be attributed to the above description Fig. 1 be referred.
  • the piston rod KS of the working piston A is led out on the left side of the double-medium working cylinder B.
  • the traversing KV, KR the piston rod KS are thus compared to the example of Fig. 1 turned around.
  • Fig. 3 shows another example of a drive system designed according to the invention.
  • Their closed storage device for the hydraulic medium is exemplified with three parallel operated double-medium working cylinders.
  • the active compressed air generator D and of the pressure compensation container H a large number of double-medium working cylinders can be operated simultaneously.
  • the hydropneumatic drive system according to the invention it is thus possible to have a comprehensive manufacturing area to operate with a plurality of dual medium working cylinders with a single surge tank. Since the arrangement on the hydraulic side of the double-medium working cylinder is closed, in all double-medium working cylinders for the execution of one of the two traversing directions, such as a return or a reverse rotation, no constant power supply is required.
  • the closed storage device for the hydraulic medium can be equipped with an additional, adjustable throttle device for the hydraulic medium.
  • an additional, adjustable throttle device for the hydraulic medium This makes it possible for the movements of the working pistons to take place at at least one of the two traversing directions, for example during a feed or pre-rotation, with different speeds that can be set independently of one another.
  • An example of such an embodiment is in the example of Fig. 3 already shown and will be explained in detail below.
  • the hydropneumatic drive system in the example of Fig. 3 is fed by a controllable compressed air system P.
  • This compressed air LV is provided with as constant as possible form of eg 6 bar. Since the drive system in Fig. 3 By way of example, three double-medium working cylinder B1, B2, B3, the compressed air LV is supplied to three controllable valves VK1, VK2, VK3 and supplied thereto in each case the first part of the working chambers.
  • valves VK1, VK2, VK3 are designed as opening valves and can be switched so that the working chambers of the double-medium working cylinder for performing a movement of the respective working piston in a second direction of travel, such as a reverse or a reverse rotation, are opened for pressure reduction, special in the atmosphere.
  • the double-medium working cylinders B1, B2, B3 are in Fig. 3 shown as a linear piston. It can be used instead or in addition also rotary pistons.
  • valves VK1, VK2, VK3 are advantageous according to the valve V in the example of FIGS. 1 and 2 built up.
  • the opening valve VK1 on a supply VK11 for the compressed air LV.
  • the compressed air LV for performing a movement of the working piston KB1 in a first direction of travel KB1V, for example, a feed or a pre-rotation, the double-medium working cylinder B1 supplied in a feed direction VK121.
  • the opening valve VK1 can be switched so that the first part AB1L of the working chamber AB1 is opened via a vent VK13 and thus a discharge of the compressed air LV takes place in a discharge direction VK122 in the atmosphere.
  • This allows, according to the invention, a movement of the working piston KB1 in the double-medium working cylinder B1 in a second travel direction KB1R, for example a reverse thrust or a reverse rotation.
  • this movement is carried out according to the invention via the hydraulic medium HM which is under a pre-pressure without any additional auxiliary energy.
  • the hydraulic medium HM from the closed storage device M flows automatically via the hydraulic connection AB12 into the second part AB1F of the working chamber AB1, ie the hydraulic chamber part, of the double-medium working cylinder B1.
  • the structure of the further double-medium working cylinder B2, B3 in Fig. 3 and their interaction with the respectively associated opening valves VK2, VK3 are corresponding.
  • the opening valves VK1, VK2, VK3 can be actuated via an electrical control such that their working pistons can be moved between selected start, intermediate and end values and forward and backward depending on the application. Due to the resulting fluctuating filling of the second parts of the working chambers of the double-medium working cylinder with hydraulic medium and the level of the hydraulic medium HM in the interior of the surge tank H. This varies in the example of Fig. 3 in dashed line by a minimum or maximum level Hmin or Hmax shown.
  • the form of the compressed air cushion HD on the hydraulic medium HM in the surge tank H of the closed Storage device M is set so that it is smaller than the minimum working pressure of the compressed air supplied by the compressed air generator D even at a maximum level Hmax of the hydraulic medium HM in the surge tank H. It is thus possible at any time to completely empty the working chambers of the associated double-medium working cylinders by means of the compressed air LV, thereby displacing the hydraulic medium therefrom into the pressure equalizing tank.
  • the closed storage device M is equipped with an additional adjustable throttle device W.
  • a throttle subdevice WB1, WB2, WB3 is connected between the outlet H2 for the hydraulic medium HM at the pressure equalizing tank H and the hydraulic connection of each double-medium working cylinder B1, B2, B3.
  • These each have at least one branch of an adjustable throttle element and a controllable start-stop valve.
  • the throttle sub-assembly WB1 three parallel branches each comprising an adjustable throttle element D1, D2 and D3 and a downstream controllable start-stop valve S1, S2 and S3, respectively.
  • This makes it possible to specify three different speeds of the working piston KB1 in the double-medium working cylinder B1 in one direction of travel, for example a feed in the direction of KB1V.
  • the choke branches can also be switched on when returning to KB1R.
  • a throttle part means may comprise an additional controllable shut-off valve, which is connected in parallel to the existing of the throttle elements and controllable start-stop valves branches.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP20120005348 2011-07-22 2012-07-21 Hydro-pneumatic drive system with one or more double medium working cylinders Withdrawn EP2549123A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201120103604 DE202011103604U1 (de) 2011-07-22 2011-07-22 Linearantriebssystem mit einem Doppelmediumarbeitszylinder

Publications (1)

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EP2549123A2 true EP2549123A2 (fr) 2013-01-23

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Family Applications (1)

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EP20120005348 Withdrawn EP2549123A2 (fr) 2011-07-22 2012-07-21 Hydro-pneumatic drive system with one or more double medium working cylinders

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EP (1) EP2549123A2 (fr)
DE (2) DE202011103604U1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112145488A (zh) * 2020-10-16 2020-12-29 芜湖森永机器有限公司 双面机高精度气液联动驱动系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR102013024307B1 (pt) * 2013-09-23 2022-03-29 Drausuisse Brasil Comércio E Locação De Unidades Hidráulicas Inteligentes S.A. Unidade geradora de pressão hidráulica com acionamento pneumático
DE102016217198B4 (de) 2016-09-09 2022-12-15 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Drehantrieb

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3176801A (en) * 1962-10-12 1965-04-06 Northrop Corp Precision motion control device
GB1401770A (en) * 1971-12-29 1975-07-30 Plessey Co Ltd Numerical control of hydraulic actuators
DE3436679A1 (de) * 1984-10-05 1986-04-10 Franz 8922 Peiting Henke Hydropneumatische antriebsvorrichtung
US4765225A (en) * 1986-08-22 1988-08-23 Birchard William G Digitally controlled air-over-hydraulic actuator and method
DE19928540A1 (de) * 1999-04-30 2000-11-09 Guenter Diehm Positioniervorrichtung, basierend auf einer Stellkolben-Zylinder-Einheit
US6711984B2 (en) * 2001-05-09 2004-03-30 James E. Tagge Bi-fluid actuator
ES2285927B2 (es) * 2006-01-02 2008-09-01 J.M. Herliz, S.L. Cilindro hidroneumatico.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112145488A (zh) * 2020-10-16 2020-12-29 芜湖森永机器有限公司 双面机高精度气液联动驱动系统

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DE202011103604U1 (de) 2012-07-24
DE202012102695U1 (de) 2012-11-06

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