EP0857256B1 - Pneumo-hydraulic converter for energy storage - Google Patents

Pneumo-hydraulic converter for energy storage Download PDF

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Publication number
EP0857256B1
EP0857256B1 EP96934298A EP96934298A EP0857256B1 EP 0857256 B1 EP0857256 B1 EP 0857256B1 EP 96934298 A EP96934298 A EP 96934298A EP 96934298 A EP96934298 A EP 96934298A EP 0857256 B1 EP0857256 B1 EP 0857256B1
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EP
European Patent Office
Prior art keywords
pressure
pneumo
piston
hydraulic converter
hydraulic
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EP96934298A
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German (de)
French (fr)
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EP0857256A1 (en
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Ivan Cyphelly
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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
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • 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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • a pneumo-hydraulic converter with reciprocating double pistons is known. the one with the best possible efficiency a compressed air reservoir with a hydraulic circuit connects, such that energy can flow into the store (charging) or from the store can be removed (unloading).
  • US-A 2,751,144 shows a compressor, i. H. a device with the hydraulic Work can be converted into pneumatic work. With this device, the Gas is compressed during the working stroke of the piston, the outside of the A cooling device is provided in the cylinder. This makes cooling possible protect the compressor from overheating overall, but it is not possible during the compression a significant amount of heat without adding or removing heat. Therefore the gas will heat up during the working stroke of the piston.
  • the compression work required however increases with the temperature of the gas, so that the efficiency of a such a compressor is low.
  • isothermal compression however, it makes it necessary to continuously dissipate heat during the working stroke. This is however, so far it has not been sufficient at technically usable working speeds Way possible.
  • the object of the invention is to achieve good efficiency while increasing the To achieve clock frequency.
  • This heat exchanger can either run with the reciprocating piston set or stay firm.
  • the heat exchanger running is about a third less Sliding seals require and also the tubular bundle the kink and dent resistance the piston set significantly increased
  • the description is based on the representation of the Restrict converters with a rotating heat exchanger: the desired increase in Clock frequency forces a radically dead space-reducing workspace arrangement.
  • the high buckling forces caused the buckling strength to become an extremely important one constructive factor that is also taken into account in the arrangement of the valves got to.
  • the high-pressure converter consists of three coaxial coaxial cables of approximately the same length Cylinder tube pieces, the pre-pressure tube 1, which surrounds the pre-pressure piston 2, has a substantially larger diameter than the two in relation to the pre-pressure tube 1 symmetrically arranged high-pressure chamber tubes 3a, 3b, which are also longitudinally symmetrical Include high pressure pistons 4a, 4b.
  • the pre-pressure pipe 1 analogously via valve flanges 5a, 5b with the two screwed-in high pressure chamber tubes 3a, 3b connected, each fastened by means of screw caps 6a, 6b Connection covers 7a, 7b are completed.
  • a set of three pistons that are mechanically firmly connected by the tubular rod 8 are and thus define 2 x 3 working spaces, namely between the connection covers 7a, 7b and the high-pressure pistons 4a, 4b, the oil spaces 9a, 9b, between the high-pressure pistons 4a, 4b and the valve flanges 5a, 5b, the high pressure air spaces 10a, 10b and between the Valve flanges 5a, 5b and the pre-pressure piston 2, the air pre-pressure spaces 11a, 11b.
  • the Air high-pressure spaces 10a, 10b are with the air pre-pressure spaces 11a, 11b via the exchange valves 12a, 12b connected, the outside world communicates with the pre-pressure rooms 11a, 11b via the low pressure valves 13a, 13b and the air reservoir 14 can the air high pressure spaces 10a, 10b act on the high pressure valves 15a, 15b from the air reservoir 14 are supplied by the supply lines 16a, 16b via the connections 17a, 17b.
  • pilot control by means of hydraulic loading is shown in 1 on the high pressure valves 15a, 15b, the pressure chambers 18a, 18b each of the electrical 2-way pilot valves connected to a pressure source 19 20a, 20b are either released or acted upon, whereby the valve pistons 21a, 21b are moved over the rods 22a, 22b with nuts 23a, 23b with the high pressure valves 15a, 15b are connected.
  • Similar devices can also be used for the replacement valves 12a, 12b and the low pressure valves 13a, 13b are provided, here only the actuating rods 24a, 24b and 25a, 25b are shown.
  • a wiring option is available, starting at the oil connections 26a, 26b of the converter, with feed lines 27a, 27b to a 4-way valve 28, which is a variable hydrostatic unit 29 with a flywheel 30 and an electric motor / generator 31 acted upon.
  • the exchange circuit begins with the feed pump 32, which is the exchange liquid by the external exchanger 33 via the connection 34b in the connection cover 7b and through the feed pipe 35b into the tube rod 8.
  • the pre-pressure piston 2 relaxed air in room 11b is displaced into the environment via the open low-pressure valve 13b and at the same time that from the previous movement in the air high-pressure space 10a below Prepressed air remaining through the open exchange valve 12a through the expanding Form pressure chamber 11a brought to outlet pressure.
  • the hydrostatic unit emerging oil sucked into the oil space 9a.
  • the through the upholstery in the Oil space 9b is therefore not only the result of high pressure in the air high-pressure chamber 10b, this also adds to that by the form on the large area of the pre-pressure piston 2 resulting thrust, which over the tubular rod 8 and Tubes 38 of the exchanger bundle is transmitted. There is a risk of kinking here!
  • the converter only works as a compressor, there is no forced control of the valves, it only has to switch the 4-way switching valve 28 either automatically (through the pressure peak at the stop) or be synchronized with the converter stroke using a proximity switch.
  • the compressor can also be used for simple compression tasks (e.g. for cooling circuits) without pre-pressure cylinder.
  • the tube bundle heat exchanger can do this either fixed or moving, as there are no buckling forces.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Hydrogen, Water And Hydrids (AREA)
  • Reciprocating Pumps (AREA)

Abstract

PCT No. PCT/CH96/00386 Sec. 371 Date May 1, 1998 Sec. 102(e) Date May 1, 1998 PCT Filed Nov. 1, 1996 PCT Pub. No. WO97/17546 PCT Pub. Date May 15, 1997In order to maintain high efficiency close, to isothermy despite high frequencies in a pneumo-hydraulic converter with reciprocating pistons, pipe cluster-heat exchange pipes (38) are provided in the gas working chambers of the converter and the exchange fluid in the pipes is kept at approximately ambient temperature. For this the gas working chambers must be arranged axially next to one another and, in order to eliminate dead space, connected in pairs by conical exchange valves (12a/12b) which take in the entire wall thickness of the valve flange (5a/5b) dividing the air chambers.

Description

Es ist ein pneumo-hydraulischer Wandler mit hin- und hergehenden Doppelkolben bekannt. der mit bestmöglichem Wirkungsgrad einen Druckluftspeicher mit einem Hydraulikkreislauf verbindet, derart, daß Energie in den Speicher fließen kann (Laden) oder aus dem Speicher entnommen werden kann (Entladen).A pneumo-hydraulic converter with reciprocating double pistons is known. the one with the best possible efficiency a compressed air reservoir with a hydraulic circuit connects, such that energy can flow into the store (charging) or from the store can be removed (unloading).

Die guten Wirkungsgrade der isothermen Vorgänge werden in dem genannten System dadurch angestrebt, daß die Arbeitsräume (Kolbenräume) bei jedem Hub durch das Arbeitsmedium Öl temperaturmäßig stabilisiert werden; dies bedingt relativ langsame Vorgänge, da die begrenzte Geschwindigkeit der Wärmeübertragung von der Zylinder-Mantelfläche auf die Luft während des Arbeitshubes die Temperaturschwankungen bei erhöhter Taktfrequenz nicht ausgleichen kann; die Folge sind große Baueinheiten im Verhältnis zu der bewältigten Leistung.The good efficiencies of the isothermal processes are thereby in the system mentioned strived for the working spaces (piston spaces) with each stroke through the working medium Temperature stabilized oil; this requires relatively slow processes since the limited speed of heat transfer from the cylinder surface to the Air during the working stroke the temperature fluctuations with increased clock frequency not can compensate; the result is large building units in relation to the mastered Power.

Die US-A 2,751,144 zeigt einen Kompressor, d. h. eine Vorrichtung, mit der hydraulische Arbeit in pneumatische Arbeit umgewandelt werden kann. Mit dieser Vorrichtung wird das Gas während des Arbeitshubes des Kolbens komprimiert, wobei im Außenbereich des Zylinders eine Kühlvorrichtung vorgesehen ist. Dadurch ist zwar eine Kühlung möglich, um den Kompressor insgesamt vor Überhitzung zu schützen, aber es ist nicht möglich, während der Verdichtung eine nennenswerte Wärmemenge ohne Wärme zu- oder abzuführen. Daher wird sich das Gas während des Arbeitshubes des Kolbens erwärmen. Die erforderliche Kompressionsarbeit steigt jedoch mit der Temperatur des Gases, so daß der Wirkungsgrad eines solchen Verdichters gering ist. Optimal in dieser Hinsicht ist eine isotherme Verdichtung, die es jedoch erforderlich macht, während des Arbeitshubes laufend Wärme abzuführen. Dies ist jedoch bei technisch brauchbaren Arbeitsgeschwindigkeiten bisher nicht in ausreichender Weise möglich gewesen.US-A 2,751,144 shows a compressor, i. H. a device with the hydraulic Work can be converted into pneumatic work. With this device, the Gas is compressed during the working stroke of the piston, the outside of the A cooling device is provided in the cylinder. This makes cooling possible protect the compressor from overheating overall, but it is not possible during the compression a significant amount of heat without adding or removing heat. Therefore the gas will heat up during the working stroke of the piston. The compression work required however increases with the temperature of the gas, so that the efficiency of a such a compressor is low. Optimal in this regard isothermal compression however, it makes it necessary to continuously dissipate heat during the working stroke. This is however, so far it has not been sufficient at technically usable working speeds Way possible.

Aufgabe der Erfindung ist es, einen guten Wirkungsgrad bei gleichzeitiger Erhöhung der Taktfrequenz zu erreichen.The object of the invention is to achieve good efficiency while increasing the To achieve clock frequency.

Erfindungsgemäß wird dies durch die im Patentanspruch 1 genannten Merkmale erreicht. wonach rohrförmige Wärmetauscher einige der Arbeitsräume des Wandlers durchdringen, wobei ein äußerer Kreislauf die Tauschflüssigkeit annähernd auf Umgebungstemperatur hält.According to the invention this is achieved by the features mentioned in claim 1. where tubular heat exchangers penetrate some of the converter's work spaces, an external circuit keeps the exchange liquid approximately at ambient temperature.

Dieser Wärmetauscher kann entweder mit dem hin- und hergehenden Kolbensatz mitlaufen oder fest bleiben. Da jedoch der mitlaufende Wärmetauscher ungefähr ein Drittel weniger Gleitdichtungen erfordert und außerdem das rohrförmige Bündel die Knick- und Beulfestigkeit des Kolbensatzes wesentlich erhöht, wird sich die Beschreibung auf die Darstellung des Wandlers mit mitlaufendem Wärmetauscher beschränken: die erwünschte Erhöhung der Taktfrequenz zwingt nämlich zu einer radikal totraumreduzierenden Arbeitsraumanordnung. die hohe Knickkräfte verursacht, was die Knickfestigkeit zu einem außerordentlich wichtigen konstruktiven Faktor macht, der auch in der Anordnung der Ventile mitberücksichtigt werden muß.This heat exchanger can either run with the reciprocating piston set or stay firm. However, since the heat exchanger running is about a third less Sliding seals require and also the tubular bundle the kink and dent resistance the piston set significantly increased, the description is based on the representation of the Restrict converters with a rotating heat exchanger: the desired increase in Clock frequency forces a radically dead space-reducing workspace arrangement. The high buckling forces caused the buckling strength to become an extremely important one constructive factor that is also taken into account in the arrangement of the valves got to.

Da der Wandler sowohl als Kompressor wie auch als Entspanner arbeiten soll, müssen die Ventilsätze jeder Seite - bestehend jeweils aus Hochdruckventil, Austauschventil und Niederdruckventil - zwangsgesteuert werden, wobei unter gewissen Bedingungen Austausch- und Niederdruckventil in ihrer Bewegung gepaart werden können. Die Ausgestaltung dieser Ventile muß ebenso die topologischen Anforderungen des Wärmetauschers, wie auch das Imperativ minimalster Toträume erfüllen; die Lösung dieser Aufgaben und die Funktionsweise der Erfindung werden mit Hilfe von Zeichnungen erklärt, wobei

Fig. 1
einen Längsschnitt durch die Achse der vier zylindrischen Arbeitsräume zeigt,
Fig. 2
einen Schnitt quer zur Achse der Fig. 1 durch den Hochdruckraum und durch das Wärmetauscher-Rohrbündel darstellt, und schließlich
Fig. 3
den gleichen Schnitt, wie die Fig. 2 veranschaulicht, jedoch mit überbrückten Bündelrohren.
Since the converter is intended to work both as a compressor and as an expansion device, the valve sets on each side - consisting of a high-pressure valve, an exchange valve and a low-pressure valve - must be positively controlled, whereby the exchange and low-pressure valve can be paired in their movement under certain conditions. The design of these valves must meet the topological requirements of the heat exchanger as well as the imperative of minimal dead spaces; the solution of these objects and the functioning of the invention are explained with the aid of drawings, wherein
Fig. 1
shows a longitudinal section through the axis of the four cylindrical work spaces,
Fig. 2
a section transverse to the axis of FIG. 1 through the high pressure chamber and through the heat exchanger tube bundle, and finally
Fig. 3
the same section as Fig. 2 illustrates, but with bridged bundle tubes.

Der Wandler in seiner Hochdruckausführung besteht aus drei ungefähr gleich langen koaxialen Zylinderrohrstücken, wobei das Vordruckrohr 1, das den Vordruckkolben 2 umschließt, einen wesentlich größeren Durchmesser aufweist, als die zwei gegenüber dem Vordruckrohr 1 symmetrisch angeordneten Hochdruckkammerrohre 3a, 3b, die die ebenfalls längssymmetrischen Hochdruckkolben 4a, 4b beinhalten. Da ebenso die bewegten Teile wie auch die feststehenden Teile spiegelsymmetrisch in Bezug auf deren Längsmitte sind, ist das Vordruckrohr 1 sinngemäß über Ventilflansche 5a, 5b mit den zwei eingeschraubten Hochdruckkammerrohren 3a, 3b verbunden, die jeweils durch mittels Schraubkappen 6a, 6b befestigten Anschlußdeckel 7a, 7b abgeschlossen werden. Axial in den Zylinderrohrstücken gleitend befindet sich ein Satz von drei Kolben, die durch die Rohrstange 8 mechanisch fest verbunden sind und somit 2 x 3 Arbeitsräume definieren, und zwar zwischen den Anschlußdeckeln 7a, 7b und den Hochdruckkolben 4a, 4b, die Ölräume 9a, 9b, zwischen den Hochdruckkolben 4a, 4b und den Ventilflanschen 5a, 5b, die Luft-Hochdruckräume 10a, 10b und zwischen den Ventilflanschen 5a, 5b und dem Vordruckkolben 2 die Luft-Vordruckräume 11a, 11b. Die Luft-Hochdruckräume 10a, 10b sind mit den Luft-Vordruckräumen 11a, 11b über die Austauschventile 12a, 12b verbunden, die Außenwelt kommuniziert mit den Vordruckräumen 11a, 11b über die Niederdruckventile 13a, 13b und der Luftspeicher 14 kann die Luft-Hochdruckräume 10a, 10b über die Hochdruckventile 15a, 15b beaufschlagen, die vom Luftspeicher 14 durch die Zuleitungen 16a, 16b über die Anschlüsse 17a, 17b versorgt werden.The high-pressure converter consists of three coaxial coaxial cables of approximately the same length Cylinder tube pieces, the pre-pressure tube 1, which surrounds the pre-pressure piston 2, has a substantially larger diameter than the two in relation to the pre-pressure tube 1 symmetrically arranged high-pressure chamber tubes 3a, 3b, which are also longitudinally symmetrical Include high pressure pistons 4a, 4b. As the moving parts as well as the fixed parts are mirror-symmetrical with respect to their longitudinal center, is the pre-pressure pipe 1 analogously via valve flanges 5a, 5b with the two screwed-in high pressure chamber tubes 3a, 3b connected, each fastened by means of screw caps 6a, 6b Connection covers 7a, 7b are completed. Sliding axially in the cylinder tube pieces a set of three pistons that are mechanically firmly connected by the tubular rod 8 are and thus define 2 x 3 working spaces, namely between the connection covers 7a, 7b and the high-pressure pistons 4a, 4b, the oil spaces 9a, 9b, between the high-pressure pistons 4a, 4b and the valve flanges 5a, 5b, the high pressure air spaces 10a, 10b and between the Valve flanges 5a, 5b and the pre-pressure piston 2, the air pre-pressure spaces 11a, 11b. The Air high-pressure spaces 10a, 10b are with the air pre-pressure spaces 11a, 11b via the exchange valves 12a, 12b connected, the outside world communicates with the pre-pressure rooms 11a, 11b via the low pressure valves 13a, 13b and the air reservoir 14 can the air high pressure spaces 10a, 10b act on the high pressure valves 15a, 15b from the air reservoir 14 are supplied by the supply lines 16a, 16b via the connections 17a, 17b.

Eine Ausgestaltungsmöglichkeit der Vorsteuerung mittels hydraulischer Beaufschlagung ist in der Fig. 1 an den Hochdruckventilen 15a, 15b dargestellt, wobei die Druckräume 18a, 18b jeweils von den an eine Druckquelle 19 angeschlossenen elektrischen 2-Wege-Vorsteuerventilen 20a, 20b entweder gelüftet oder beaufschlagt werden, wodurch die Ventilkolben 21a, 21b bewegt werden, die über die Stangen 22a, 22b mit Muttern 23a, 23b mit den Hochdruckventilen 15a, 15b verbunden sind. Ähnliche Vorrichtungen können auch für die Austauschventile 12a, 12b und die Niederdruckventile 13a, 13b vorgesehen werden, wobei hier lediglich deren Betätigungsstangen 24a, 24b und 25a, 25b dargestellt sind.One possibility of designing the pilot control by means of hydraulic loading is shown in 1 on the high pressure valves 15a, 15b, the pressure chambers 18a, 18b each of the electrical 2-way pilot valves connected to a pressure source 19 20a, 20b are either released or acted upon, whereby the valve pistons 21a, 21b are moved over the rods 22a, 22b with nuts 23a, 23b with the high pressure valves 15a, 15b are connected. Similar devices can also be used for the replacement valves 12a, 12b and the low pressure valves 13a, 13b are provided, here only the actuating rods 24a, 24b and 25a, 25b are shown.

Zum besseren Verständnis ist, beginnend an den Ölanschlüssen 26a, 26b, eine Beschaltungsmöglichkeit des Wandlers dargestellt, mit Zuleitungen 27a, 27b zu einem 4-Wege-Ventil 28, das eine variable hydrostatische Einheit 29 mit Schwungrad 30 und Elektro-Motor/Generator 31 beaufschlagt. Der Tauscherkreislauf beginnt mit der Speisepumpe 32, die die Tauschflüssigkeit durch den externen Tauscher 33 über den Anschluß 34b im Anschlußdeckel 7b und über das Speiserohr 35b in die Rohrstange 8 einführt. Da diese Rohrstange 8 in der Ebene des Vordruckkolbens 2 durch einen konischen Stopfen 36 verschlossen ist, wird die Tauschflüssigkeit durch den Ringraum zwischen Speiserohr 35b und Rohrstange 8 zum Hochdruckkolben zurückgedrückt, in welchem über Radialbohrungen 37b die Tauscher-Bündelrohre 38 gespeist werden, also auch der Hochdruckkolben 4a - über dessen Radialbohrungen 37a wiederum die Rohrstange 8 erreicht wird; der Kreislauf zurück zur Speisepumpe 32 wird über das Speiserohr 35a und den Anschluß 34a geschlossen.For better understanding, a wiring option is available, starting at the oil connections 26a, 26b of the converter, with feed lines 27a, 27b to a 4-way valve 28, which is a variable hydrostatic unit 29 with a flywheel 30 and an electric motor / generator 31 acted upon. The exchange circuit begins with the feed pump 32, which is the exchange liquid by the external exchanger 33 via the connection 34b in the connection cover 7b and through the feed pipe 35b into the tube rod 8. Since this pipe rod 8 in the plane of Pre-pressure piston 2 is closed by a conical plug 36, the exchange liquid through the annular space between feed pipe 35b and pipe rod 8 to the high-pressure piston pressed back, in which the exchanger bundle tubes 38 are fed, so also the high pressure piston 4a - in turn via the radial bores 37a the pipe rod 8 is reached; the circuit back to the feed pump 32 is via the Feed tube 35a and the connection 34a closed.

Wie die Hochdruckkolben-Gleitdichtungen 39a, 39b und die Austauschventil-Gleitdichtungen 40a, 40b werden auch die Tauscherdichtungen 41a, 41b und 42a, 42b durch die ganze Kolbenbewegung hindurch mit voller Druckdifferenz belastet. Dies ist die eigentliche technologische Herausforderung des Konzeptes, insbesondere wenn die Rohrbündelausgestaltung zwecks Erhöhung der Knickfestigkeit und der Wärmeübertragung eine Bündelrohrüberbrückung 43, wie in Fig. 3, vorsieht. Lediglich die Gleitdichtung 44 des Vordruckkolbens 2 wird von den hohen Drücken verschont, da sie nur dem Vordruck ausgesetzt wird. Die restlichen nicht näher bezeichneten Dichtungen werden nur statisch oder kurzhubig beansprucht.Like the high-pressure piston sliding seals 39a, 39b and the replacement valve sliding seals 40a, 40b are the exchanger seals 41a, 41b and 42a, 42b through the whole Piston movement loaded with full pressure difference. This is the real technological one Challenge of the concept, especially when designing the tube bundle A bundle tube bypass to increase kink resistance and heat transfer 43, as in Fig. 3, provides. Only the sliding seal 44 of the upstream pressure piston 2 is spared from the high pressures as it is only exposed to the pre-pressure. The remaining Seals not specified are only subjected to static or short-stroke loads.

Die Funktionsweise des Wandlers soll nun in einem Zyklus der Entspannung (Entladung) erläutert werden, dem die dargestellte Stellung der Ventile entspricht, wobei sich der Kolbensatz gegen rechts bewegt. In dem zeichnerisch festgehaltenen Augenblick wird durch das offene Luft-Hochdruckventil 15b der Luft-Hochdruckraum 10b mit dem Luftspeicher 14 direkt verbunden. Die Druckkraft wird sinngemäß im Ölraum 9b aufgenommen und durch die Ölsäule in der Leitung 27b über das 4-Wege-Ventil 28 auf die Druckseite motorisch wirkenden hydrostatischen Einheit 29 übertragen, die folglich das Schwungrad 30 und den Generator 31 antreibt. Durch besagte Bewegung nach rechts wird außerdem mittels Vordruckkolbens 2 entspannte Luft im Raum 11b über das offene Niederdruckventil 13b in die Umwelt verdrängt und gleichzeitig die aus der vorhergehenden Bewegung im Luft-Hochdruckraum 10a unter Vordruck verbliebene Luft über das offene Austauschventil 12a durch den sich erweiternden Vordruckraum 11a auf Auslaßdruck gebracht. Durch dieselbe Bewegung wird das aus der hydrostatischen Einheit austretende Öl in den Ölraum 9a gesaugt. Die durch das Polster im Ölraum 9b aufgenommene Kraft entsteht also nicht nur durch die Hochdruckbeaufschlagung im Luft-Hochdruckraum 10b, es addiert sich hierzu auch der durch den Vordruck an der großen Fläche des Vordruckkolbens 2 entstehende Schub, der über die Rohrstange 8 und die Rohre 38 des Tauscherbündels übertragen wird. Hier lauert die Knickgefahr! An einer mittels Rechner zu ermittelnder Stelle dieses Rechtshubes muß nun das Hochdruckventil 15b geschlossen werden, damit die Entspannung dieses hierdurch definierten Volumens am Ende des Hubes genau den Vordruck ergibt, der nach der Hubumkehr durch das Verschieben des Inhalts des Lufthochruckraumes 10b in den Vordruckraum 11b durch Expansion den Auslaßdruck erreicht. Im Augenblick der Hubumkehr müssen also zusammen mit der Umschaltung von 28 auch 15a, 13a und 12b geöffnet und 12a und 13b geschlossen werden (wobei 13b ja schon durch den auflaufenden Vordruckkolben 2 in die Schließstellung gedrückt wird). Diese Umschaltung kann durch einen Näherungsschalter ausgelöst werden.The mode of operation of the converter should now be in a cycle of relaxation (discharge) are explained, which corresponds to the position of the valves shown, the piston set moved to the right. At the moment in the drawing, the open air high pressure valve 15b the air high pressure space 10b with the air reservoir 14 directly connected. The compressive force is taken up analogously in the oil space 9b and by the Oil column in line 27b via the 4-way valve 28 on the pressure side acting motor hydrostatic unit 29, which consequently transmits the flywheel 30 and the generator 31 drives. By said movement to the right, the pre-pressure piston 2 relaxed air in room 11b is displaced into the environment via the open low-pressure valve 13b and at the same time that from the previous movement in the air high-pressure space 10a below Prepressed air remaining through the open exchange valve 12a through the expanding Form pressure chamber 11a brought to outlet pressure. With the same movement, the hydrostatic unit emerging oil sucked into the oil space 9a. The through the upholstery in the Oil space 9b is therefore not only the result of high pressure in the air high-pressure chamber 10b, this also adds to that by the form on the large area of the pre-pressure piston 2 resulting thrust, which over the tubular rod 8 and Tubes 38 of the exchanger bundle is transmitted. There is a risk of kinking here! On one means The computer of the point of this rightward stroke to be determined must now close the high-pressure valve 15b so that the relaxation of this defined volume at the end of the Hubes gives exactly the form that after the stroke reversal by moving the content of the high pressure air space 10b into the pre-pressure space 11b by expansion the outlet pressure reached. At the moment of stroke reversal must therefore be together with the changeover from 28 also 15a, 13a and 12b are opened and 12a and 13b are closed (whereby 13b yes is already pressed into the closed position by the upstream pressure piston 2). This Switching can be triggered by a proximity switch.

Abschließend soll unterstrichen werden, daß die dargestellte topologische Ausgestaltung Teil der Erfindung ist und besonders gut zu dem beschriebenen, sich immer wiederholenden thermodynamischen Vorgang paßt, zumal durch die gewählte Druckraum- und Tauscheranordnung die totraumfreie Wechselventilbauart möglich wird, mit der das Konzept einer Wandlung mit höchsten Wirkungsgraden steht und fällt.Finally, it should be emphasized that the topological configuration shown is part the invention is and particularly well to the described, repetitive thermodynamic Process fits, especially due to the selected pressure chamber and exchanger arrangement the dead space-free shuttle valve design becomes possible with which the concept of a conversion stands and falls with the highest levels of efficiency.

Es soll schließlich darauf hingewiesen werden, daß innerhalb eines Hubes der aus diesem Wandler austretende Öldruck pro Hub in einem Verhältnis von ungefähr 1:30 schwankt (bei 200 bar im Luftspeicher 14), was dessen direkte Anwendung in vielen Fällen problematisch macht, da die hydrostatischen Einheiten über einen Verdrängervolumen-Regelbereich von höchstens 1:10 verfügen. Soll also der Wandler eine konstante Leistung bewältigen, empfiehlt sich der Weg über ein Schwungrad, das einen weiten Taktfrequenzbereich überbrücken kann, wobei die hydrostatische Einheit lediglich den effektiven Laständerungen zu folgen hat.Finally, it should be pointed out that within a stroke the out of this Oil pressure exiting the converter fluctuates in a ratio of approximately 1:30 (at 200 bar in the air storage 14), which makes its direct application problematic in many cases because the hydrostatic units have a displacement volume control range of have a maximum of 1:10. So if the converter is to cope with constant power, we recommend the way over a flywheel that can bridge a wide clock frequency range, the hydrostatic unit only has to follow the effective load changes.

Arbeitet der Wandler ausschließlich als Kompressor entfällt die Zwangssteuerung der Ventile, es muß lediglich das 4-Wege-Umschaltventil 28 entweder selbsttätig (durch die Druckspitze beim Anschlag) oder mittels Näherungsschalter mit dem Wandlerhub synchronisiert werden. Auch kann bei einfachen Verdichtungsaufgaben (z. B. für Kühlkreisläufe) der Kompressor ohne Vordruckzylinder ausgeführt werden. Der Rohrbündel-Wärmetauscher kann hierbei wahlweise feststehend oder mitlaufend sein, da keine Knickkräfte entstehen.If the converter only works as a compressor, there is no forced control of the valves, it only has to switch the 4-way switching valve 28 either automatically (through the pressure peak at the stop) or be synchronized with the converter stroke using a proximity switch. The compressor can also be used for simple compression tasks (e.g. for cooling circuits) without pre-pressure cylinder. The tube bundle heat exchanger can do this either fixed or moving, as there are no buckling forces.

Claims (9)

  1. Pneumo-hydraulic converter for the conversion of pneumatic work into hydraulic work and/or hydraulic work into pneumatic work, with at least one reciprocating piston (2, 4a, 4b), at least one gas working chamber (10a, 10b; 11a, 11b), which is partially defined by the piston (2, 4a, 4b) and in which is provided a gaseous working medium, and at least one oil working chamber (9a, 9b), which is partially defined by a piston (4a, 4b) and in which is provided a liquid working medium, the gas working chamber (10a, 10b; 11a, 11b) being connected to an air storage (14) by means of valves (15a, 15b), and the oil working chamber (9a, 9b) being connected to a hydraulic circuit, characterized in that a tubular heat exchanger (35a, 35b, 38) passing through the piston (2, 4a, 4b) is connected to an exterior cooling circuit, which is designed to maintain the temperature of the gaseous working medium at an essentially constant level.
  2. Pneumo-hydraulic converter as claimed in Claim 1, characterized in that the tubular heat exchanger (35a, 35b, 38) passes through the gas working chambers (10a, 10b; 11a, 11b) and the oil working chambers (9a, 9b).
  3. Pneumo-hydraulic converter as claimed in any of Claims 1 or 2, characterized in that the tubular heat exchanger (35a, 35b, 38) is rigidly connected in the piston (2).
  4. Pneumo-hydraulic converter as claimed in any of Claims 1 to 3, characterized in that there are provided at least one high-pressure piston (4a, 4b) and at least one pre-pressure piston (2) with larger diameter.
  5. Pneumo-hydraulic converter as claimed in any of Claims 1 to 4, characterized in that two high-pressure pistons (4a, 4b) and one pre-pressure piston (2) are provided, which are rigidly connected to one another.
  6. Pneumo-hydraulic converter as claimed in any of Claims 4 or 5, charaterized in that at least one high-pressure piston (4a, 4b) is positioned between an oil working chamber (9a, 9b) and a gas high-pressure chamber (10a, 10b).
  7. Pneumo-hydraulic converter as claimed in any of Claims 4 to 6, characterized in that the pre-pressure piston (2) is positioned between two gas pre-pressure chambers (11a, 11b).
  8. Pneumo-hydraulic converter as claimed in any of Claims 1 to 7, characterized in that in order to prevent dead volumes each gas high-pressure chamber (10a, 10b) is connected to a corresponding pre-pressure chamber (11a, 11b) via a conical seat valve (12a, 12b), which is guided on a tubular rod (8) or the exchange pipes (38), and which occupies the entire wall thickness of the valve flange (5a, 5b) separating the air chambers.
  9. Pneumo-hydraulic converter as claimed in any of Claims 1 to 8, characterized in that a proximity switch is provided for control of the valves (12a, 12b, 13a, 13b, 15a, 15b, 28).
EP96934298A 1995-11-03 1996-11-01 Pneumo-hydraulic converter for energy storage Expired - Lifetime EP0857256B1 (en)

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CH311495 1995-11-03
CH3114/95 1995-11-03
PCT/CH1996/000386 WO1997017546A1 (en) 1995-11-03 1996-11-01 Pneumo-hydraulic converter for energy storage

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CN102135080A (en) * 2011-03-02 2011-07-27 浙江杭钻机械制造股份有限公司 Hydraulic double-cylinder single-acting reciprocating pump driving system capable of reversing by rotary valve

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US6145311A (en) 2000-11-14
EP0857256A1 (en) 1998-08-12
CA2236746A1 (en) 1997-05-15
JPH11501387A (en) 1999-02-02
WO1997017546A1 (en) 1997-05-15
DE59601569D1 (en) 1999-05-06
ATE178389T1 (en) 1999-04-15
JP3194047B2 (en) 2001-07-30
OA10682A (en) 2001-05-03

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