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EP3728846B1 - Method and device for compacting a working substance - Google Patents

Method and device for compacting a working substance Download PDF

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Publication number
EP3728846B1
EP3728846B1 EP19700822.0A EP19700822A EP3728846B1 EP 3728846 B1 EP3728846 B1 EP 3728846B1 EP 19700822 A EP19700822 A EP 19700822A EP 3728846 B1 EP3728846 B1 EP 3728846B1
Authority
EP
European Patent Office
Prior art keywords
compressor
drive
medium
cylinder
pressure
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.)
Active
Application number
EP19700822.0A
Other languages
German (de)
French (fr)
Other versions
EP3728846A1 (en
Inventor
Robert Adler
Georg Fahrthofer
Sarah Gruber
Christoph Nagl
Markus Rasch
Markus Stephan
Henning WILLIG
Rene HIMMELSTEIN
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.)
MAXIMATOR GmbH
Original Assignee
MAXIMATOR GmbH
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 MAXIMATOR GmbH filed Critical MAXIMATOR GmbH
Priority to PL19700822T priority Critical patent/PL3728846T3/en
Priority to SI201930074T priority patent/SI3728846T1/en
Publication of EP3728846A1 publication Critical patent/EP3728846A1/en
Application granted granted Critical
Publication of EP3728846B1 publication Critical patent/EP3728846B1/en
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/008—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being a fluid transmission link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
    • F04B9/133—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting elastic-fluid motor

Definitions

  • the invention relates to a device for compressing a working medium with the features of the preamble of claim 1 and a method for compressing a working medium with the features of the preamble of claim 8.
  • U.S. 4,104,008 A. Such compressors are known in the prior art in various designs (see. For example U.S. 4,104,008 A. ).
  • the U.S. 4,104,008 A. discloses a compressed air operated hydraulic pump which has a working space and a pneumatic piston, the pneumatic piston being connected to a hydraulic piston.
  • an auxiliary slide which is sealed off from the working space, and a control slide, compressed air is conveyed to the pneumatic piston in order to move it against the spring force of a helical compression spring.
  • the movement of the pneumatic piston moves the hydraulic piston in a hydraulic cylinder onto which a valve housing is pushed, which is used to connect hydraulic lines.
  • the U.S. 5,324,175 A shows a two-stage, pneumatically operated reciprocating air compressor which has an integrated and coaxial drive piston, a piston for the first stage and a piston for the second stage.
  • the pressure side of the first stage of the compressor is the suction side of the second stage. After being compressed in the first stage of the compressor, the air to be compressed is passed through a heat exchanger before it is further compressed in the second stage.
  • the invention aims to increase the efficiency for driving the high-pressure piston.
  • the heat exchanger is set up for heat exchange between the working medium after compression in the second cylinder and the drive medium before it enters the first cylinder of the pressure booster.
  • the temperature of the drive medium in the compressed state can advantageously be increased before the drive piston is acted upon by the drive medium in the compressed state.
  • a higher work output is available for operating the high-pressure piston, so that the efficiency of the compressor can be increased.
  • This principle can be used with different types of compressors, in particular with a single or double-acting, single-stage or two-stage compressor.
  • the compressor can also be designed as a piston compressor, single or double-acting, single-stage or two-stage.
  • the location and direction information relate to the direction of flow of the drive medium or the working medium in compressor operation.
  • a closed circuit for the drive medium with a first line is from Compressor to the first cylinder and provided with a second line from the first cylinder to the compressor.
  • the heat exchanger is preferably designed as a recuperator, the compressed drive medium and the compressed working medium being separated from one another by means of at least one wall.
  • the heat exchanger is designed as a regenerator, with heat storage being provided in a heat exchanger mass.
  • a plate heat exchanger or a tube-in-tube heat exchanger can be provided as the heat exchanger.
  • a wide variety of designs of heat exchangers are known with which the heat content of the compressed working medium can be transferred to the compressed drive medium.
  • the compressor is designed to be fully hermetic or semi-hermetic.
  • a "fully hermetic" compressor is understood to mean a design in which a preferably pressure-tight housing encloses both a drive motor and a compressor unit, the enclosing housing in particular being welded and the media lines being passed through the housing.
  • a “semi-hermetic” compressor is understood to be an embodiment in which a drive motor is connected to a compressor housing in a pressure-tight and detachable manner.
  • an “open” compressor is understood to be an embodiment in which a shaft journal or another load transfer means protrudes from at least one side of a compressor unit, via which work output can be introduced into the compressor unit.
  • the compressor and the closed circuit for the drive medium are set up to circulate the drive medium at a higher pressure than ambient pressure.
  • a cooler for cooling the drive medium is arranged in the second line of the closed circuit between the first cylinder of the pressure booster and the compressor.
  • the temperature of the drive medium is reduced when it is returned from the first cylinder to the compressor.
  • the temperature of the drive medium can be increased by exchanging heat with the compressed working medium, without the temperature in the closed circuit as a whole continuing to increase.
  • the working medium is therefore advantageously conducted in a closed circuit at different temperature levels in order to achieve optimum efficiency when driving the high-pressure piston.
  • a first buffer store is preferably provided between the compressor and the heat exchanger and / or a second buffer store between the cooler and the compressor.
  • a control slide is provided between the compressor and the first cylinder, which can be switched between a first position and a second position, by means of the drive medium by means of the drive medium, by means of the drive medium, the drive piston sealing a first volume of the first cylinder against a second volume of the first cylinder and move forward.
  • the control slide In the first position, the control slide connects the first line to a first volume of the first cylinder and the second line to a second volume of the first cylinder.
  • the control slide connects the first line to the second volume of the first cylinder and the second line to the first volume of the first cylinder.
  • the drive medium in the compressor is compressed from an input pressure to an output pressure, the input pressure being greater than an ambient pressure.
  • the inlet pressure of the drive medium at the inlet of the compressor is preferably between 0.5 bar and 50 bar, in particular between 2 bar and 30 bar.
  • the outlet pressure of the drive medium at the outlet of the compressor is preferably between 1 bar and 100 bar, in particular between 5 bar and 40 bar.
  • the drive medium emerging from the first cylinder is preferably cooled by means of a cooler.
  • the drive medium is preferably different from the working medium.
  • the drive medium is gaseous, the drive medium preferably being one of air, nitrogen, CO 2 , argon or krypton or a mixture thereof.
  • the conventional compressors with gas drive have a high energy requirement in order to provide the drive power required to drive the high-pressure piston. Due to the closed circuit of the drive medium on the one hand and the heat transfer from the compressed working medium to the compressed drive medium on the other hand, the efficiency when operating the drive piston can be increased significantly.
  • the working medium is gaseous, with molecular hydrogen preferably being provided as the working medium.
  • the pressure of the working medium is preferably increased from an initial pressure, in particular between 3 bar and 500 bar, to a final pressure, in particular between 100 bar and 1500 bar, in particular between 700 bar and 1000 bar. These values are in turn to be understood as absolute pressure.
  • Fig. 1 shows a device according to the invention for compressing a working medium by means of a high pressure piston, with heat transfer from the compressed working medium to the compressed drive medium for the drive piston is carried out.
  • a device 1 for compressing a gaseous working medium, preferably molecular hydrogen, is shown schematically.
  • the device 1 has a compressor 2 for compressing a gaseous drive medium, preferably air.
  • a gaseous drive medium preferably air.
  • the compressor 2 can be designed as a piston or screw compressor.
  • the compressor can have exactly one stage or at least two stages.
  • the compressor 2 increases the pressure of the drive medium from an input pressure at an input 2a of the compressor 2 to an output pressure at an output 2b of the compressor 2.
  • the compressed drive medium is used to drive a pressure booster 3.
  • the pressure booster 3 also referred to as a pressure converter, has a drive piston 4 which is moved back and forth within a first cylinder 5 between a first end position and a second end position.
  • the drive medium is fed into the first cylinder 5.
  • the drive piston 4 seals a first volume 6 of the first cylinder 5 from a second volume 7 of the first cylinder 5.
  • the pressure booster 3 also has a high-pressure piston 8 with which the working medium is compressed from an initial pressure to a final pressure.
  • the high-pressure piston 8 can be moved to and fro within a second cylinder 9 between a first end position and a second end position.
  • the high-pressure piston 8 is connected to the drive piston 4 in such a way that the movement of the drive piston 4 is transmitted to the high-pressure piston 8.
  • the high-pressure piston 8 has a smaller piston area than the drive or low-pressure piston 4.
  • the drive piston 4 is double-acting with a further high-pressure piston 10 within a high-pressure cylinder 11 on the side of the drive piston 4 facing away from the high-pressure piston 8.
  • the working medium is at the initial pressure via a first feed line 12 to the second Cylinder 9 and fed to the high pressure cylinder 11 via a second feed line 13.
  • the working medium with the final pressure is diverted from the second cylinder 9 via a first discharge line 14 and from the high-pressure cylinder 11 via a second discharge line 15.
  • Valves 12a, 13a, 14a, 15a are provided in the supply and discharge lines.
  • the first discharge line 14 and the second discharge line 15 are brought together in a common discharge line 16. In the case of a single-acting design of the drive piston 4 (not shown), only the first discharge line 14 is provided.
  • the closed circuit 17 has a first line 18 from the outlet 2a of the compressor 2 to the first cylinder 5 and a second line 19 (return) from the first cylinder 5 back to the inlet 2b of the compressor 2.
  • a control device in particular a control slide 20, is provided for changing the direction of flow of the drive medium in the first cylinder 5.
  • the drive piston 4 can be pressurized from one side or from the other side, so that the switching of the control device causes the drive piston 2 to move back and forth.
  • the compressor 2 is designed fully hermetically or semi-hermetically. In this way, gas leaks can advantageously be reduced.
  • the drive medium seen in the direction of flow 21 of the drive medium, is guided between the compressor 2 and the first cylinder 5 of the pressure booster 3 via a heat exchanger 22 in which a heat exchange with the compressed working medium is carried out.
  • the heat exchanger 22 is connected to the first discharge line 14 and / or to the second discharge line 15, in the case of the double-acting compressor shown, to the common discharge line 16.
  • the heat content of the working medium can be increased for the drive piston 4 to increase the temperature of the drive medium before it enters the first cylinder 5.
  • the work that can be performed and consequently the performance on the pressure converter is increased as a result.
  • less (electrical) drive energy is required for the compressor 2 for the same work.
  • a cooler 23 is also arranged in the second line 19 in order to achieve cooling of the drive medium on the way from the first cylinder 5 of the pressure booster 3 back to the compressor 2.
  • the cooler 23 can be designed as a further heat exchanger with a fan 23a.
  • a temperature measuring element 26 is also provided in the second line 19, which transmits the temperature of the working medium to a control unit 27, which controls the fan 23a as a function of the temperature of the drive medium in the second line 19.
  • a first buffer store 24 is provided between the compressor 2 and the heat exchanger 22 and a second buffer store 25 is provided between the cooler 23 and the compressor 2.
  • compressor device 1 can have a wide variety of additional components and modifications compared to the embodiment shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

Die Erfindung betrifft eine Vorrichtung zum Verdichten eines Arbeitsmediums mit den Merkmalen des Oberbegriffs von Anspruch 1 sowie ein Verfahren zum Verdichten eines Arbeitsmediums mit den Merkmalen des Oberbegriffs von Anspruch 8.The invention relates to a device for compressing a working medium with the features of the preamble of claim 1 and a method for compressing a working medium with the features of the preamble of claim 8.

Derartige Verdichter sind im Stand der Technik in verschiedenen Ausführungen bekannt (vgl. z.B. die US 4,104,008 A ). Die US 4,104,008 A offenbart eine druckluftbetriebene Hydraulikpumpe, die einen Arbeitsraum und einen Pneumatikkolben aufweist, wobei der Pneumatikkolben mit einem Hydraulikkolben verbunden ist. Mithilfe eines Hilfsschiebers, der gegen den Arbeitsraum abgedichtet ist, und eines Steuerschiebers, wird Druckluft zum Pneumatikkolben befördert, um diesen entgegen einer Federkraft einer Schraubendruckfeder zu bewegen. Durch die Bewegung des Pneumatikkolbens wird der Hydraulikkolben in einem Hydraulikzylinder bewegt, auf den ein Ventilgehäuse aufgeschoben ist, das zum Anschluss von Hydraulikleitungen dient.Such compressors are known in the prior art in various designs (see. For example U.S. 4,104,008 A. ). The U.S. 4,104,008 A. discloses a compressed air operated hydraulic pump which has a working space and a pneumatic piston, the pneumatic piston being connected to a hydraulic piston. With the help of an auxiliary slide, which is sealed off from the working space, and a control slide, compressed air is conveyed to the pneumatic piston in order to move it against the spring force of a helical compression spring. The movement of the pneumatic piston moves the hydraulic piston in a hydraulic cylinder onto which a valve housing is pushed, which is used to connect hydraulic lines.

Die US 5,324,175 A zeigt einen zweistufigen, pneumatisch betriebenen Luft-Kolbenkompressor, der einen integrierten und koaxialen Antriebskolben, einen Kolben für die erste Stufe und einen Kolben für die zweite Stufe aufweist. Die Druckseite der ersten Stufe des Kompressors ist die Saugseite der zweiten Stufe. Die zu komprimierende Luft wird nach der Kompression in der ersten Stufe des Kompressors durch einen Wärmetauscher geführt, bevor sie in der zweiten Stufe weiter komprimiert wird.The U.S. 5,324,175 A shows a two-stage, pneumatically operated reciprocating air compressor which has an integrated and coaxial drive piston, a piston for the first stage and a piston for the second stage. The pressure side of the first stage of the compressor is the suction side of the second stage. After being compressed in the first stage of the compressor, the air to be compressed is passed through a heat exchanger before it is further compressed in the second stage.

In den DE 30 18 625 A1 und US 6,386,841 B1 sind verschiedene Ausführungen von Verdichtern gezeigt, welche jedoch nicht im Hinblick darauf ausgelegt sind, die Effizienz der Verdichter zu erhöhen.In the DE 30 18 625 A1 and US 6,386,841 B1 various designs of compressors are shown, which, however, are not designed with a view to increasing the efficiency of the compressors.

Als nachteilig erweist sich jedoch der hohe Energieverbrauch von Verdichtern mit Gasantrieb.However, the high energy consumption of gas-powered compressors has proven to be a disadvantage.

Vor diesem Hintergrund setzt sich die Erfindung zum Ziel, den Wirkungsgrad für den Antrieb des Hochdruckkolbens zu erhöhen.Against this background, the invention aims to increase the efficiency for driving the high-pressure piston.

Diese Aufgabe wird durch eine Vorrichtung mit den Merkmalen von Anspruch 1 und ein Verfahren mit den Merkmalen von Anspruch 8 gelöst.This object is achieved by a device with the features of claim 1 and a method with the features of claim 8.

Die erfindungsgemäße Vorrichtung zum Verdichten eines Arbeitsmediums weist zumindest die folgenden Komponenten auf:

  • einen Kompressor zur Kompression eines Antriebsmediums;
  • einen Druckübersetzer mit einem mittels des Antriebsmediums betätigbaren Antriebskolben innerhalb eines ersten Zylinders und mit einem das Arbeitsmedium verdichtenden Hochdruckkolben innerhalb eines zweiten Zylinders,
  • einen Wärmetauscher zwischen dem Kompressor und dem ersten Zylinder des Druckübersetzers zur Wärmeübertragung vom verdichteten Arbeitsmedium auf das komprimierte Antriebsmedium.
The device according to the invention for compressing a working medium has at least the following components:
  • a compressor for compressing a drive medium;
  • a pressure booster with a drive piston that can be actuated by means of the drive medium within a first cylinder and with a high-pressure piston that compresses the working medium within a second cylinder,
  • a heat exchanger between the compressor and the first cylinder of the pressure booster for heat transfer from the compressed working medium to the compressed drive medium.

Erfindungsgemäß ist der Wärmetauscher für einen Wärmeaustausch zwischen dem Arbeitsmedium nach der Verdichtung im zweiten Zylinder und dem Antriebsmedium vor dem Eintritt in den ersten Zylinder des Druckübersetzers eingerichtet. Vorteilhafterweise kann so die Temperatur des Antriebsmediums im komprimierten Zustand erhöht werden, bevor der Antriebskolben mit dem Antriebsmedium im komprimierten Zustand beaufschlagt wird. Dadurch steht eine höhere Arbeitsleistung für den Betrieb des Hochdruckkolbens zur Verfügung, so dass der Wirkungsgrad des Verdichters gesteigert werden kann.According to the invention, the heat exchanger is set up for heat exchange between the working medium after compression in the second cylinder and the drive medium before it enters the first cylinder of the pressure booster. In this way, the temperature of the drive medium in the compressed state can advantageously be increased before the drive piston is acted upon by the drive medium in the compressed state. As a result, a higher work output is available for operating the high-pressure piston, so that the efficiency of the compressor can be increased.

Dieses Prinzip kann bei verschiedenen Typen von Verdichtern, insbesondere bei einem einfach- oder doppeltwirkenden, einstufigen oder zweistufigen Verdichter genutzt werden. Der Kompressor kann als Kolbenverdichter ebenfalls einfach- oder doppeltwirkend, einstufig oder zweistufig ausgeführt sein.This principle can be used with different types of compressors, in particular with a single or double-acting, single-stage or two-stage compressor. The compressor can also be designed as a piston compressor, single or double-acting, single-stage or two-stage.

Für die Zwecke dieser Offenbarung beziehen sich die Orts- und Richtungsangaben, wie "vor", "nach", "zwischen", etc., auf die Strömungsrichtung des Antriebsmediums bzw. des Arbeitsmediums im Verdichterbetrieb.For the purposes of this disclosure, the location and direction information, such as “before”, “after”, “between”, etc., relate to the direction of flow of the drive medium or the working medium in compressor operation.

Bei einer bevorzugten Ausführungsform ist ein geschlossener Kreislauf für das Antriebsmedium mit einer ersten Leitung vom Kompressor zum ersten Zylinder und mit einer zweiten Leitung vom ersten Zylinder zum Kompressor vorgesehen. In dem Artikel von Andreas P. Weiß, "Höhere Energieeffizienz - Theoretische Überlegungen zu einem idealen Druckluftsystem mit geschlossenem Luftkreislauf", O+P 5/2009, wurde in einem anderen Zusammenhang gezeigt, dass bei einem Druckluftsystem mit einem Druckluftzylinder die Ausbildung eines geschlossenen Luftkreislaufes die Energieeffizienz gegenüber einem offenen Referenzsystem ohne Abluftrückführung erhöht.In a preferred embodiment, a closed circuit for the drive medium with a first line is from Compressor to the first cylinder and provided with a second line from the first cylinder to the compressor. In the article by Andreas P. Weiß, "Higher energy efficiency - Theoretical considerations for an ideal compressed air system with a closed air circuit", O + P 5/2009, it was shown in a different context that a compressed air system with a compressed air cylinder creates a closed air circuit increases the energy efficiency compared to an open reference system without exhaust air recirculation.

Der Wärmetauscher ist bevorzugt als Rekuperator ausgeführt, wobei das komprimierte Antriebsmedium und das verdichtete Arbeitsmedium mittels zumindest einer Wand voneinander getrennt sind. Bei einer alternativen Ausführung ist der Wärmetauscher als Regenerator ausgeführt, wobei eine Wärmespeicherung in einer Wärmetauschermasse vorgesehen ist.The heat exchanger is preferably designed as a recuperator, the compressed drive medium and the compressed working medium being separated from one another by means of at least one wall. In an alternative embodiment, the heat exchanger is designed as a regenerator, with heat storage being provided in a heat exchanger mass.

Als Wärmetauscher kann beispielsweise ein Plattenwärmetauscher oder ein Rohr-in-Rohr-Wärmetauscher vorgesehen sein. Es sind jedoch verschiedenste Ausführungen von Wärmetauschern bekannt, mit welchen der Wärmegehalt des verdichteten Arbeitsmediums auf das komprimierte Antriebsmedium übertragen werden kann.For example, a plate heat exchanger or a tube-in-tube heat exchanger can be provided as the heat exchanger. However, a wide variety of designs of heat exchangers are known with which the heat content of the compressed working medium can be transferred to the compressed drive medium.

Um die benötigte Antriebsleistung weiter zu verringern, ist es günstig, wenn der Kompressor vollhermetisch oder halbhermetisch ausgeführt ist.In order to further reduce the drive power required, it is advantageous if the compressor is designed to be fully hermetic or semi-hermetic.

Für die Zwecke dieser Offenbarung wird als "vollhermetischer" Kompressor eine Ausführung verstanden, bei welcher ein vorzugsweise druckdichtes Gehäuse sowohl einen Antriebsmotor als auch eine Verdichtereinheit umschließt, wobei das umschließende Gehäuse insbesondere verschweißt ist und die Medienleitungen durch das Gehäuse durchgeführt sind.For the purposes of this disclosure, a "fully hermetic" compressor is understood to mean a design in which a preferably pressure-tight housing encloses both a drive motor and a compressor unit, the enclosing housing in particular being welded and the media lines being passed through the housing.

Für die Zwecke dieser Offenbarung wird als "halbhermetischer" Kompressor eine Ausführung verstanden, bei welcher ein Antriebsmotor mit einem Verdichtergehäuse druckdicht und lösbar verbunden ist.For the purposes of this disclosure, a “semi-hermetic” compressor is understood to be an embodiment in which a drive motor is connected to a compressor housing in a pressure-tight and detachable manner.

Bei einer weiteren Ausführungsform ist ein offener Kompressor vorgesehen. Für die Zwecke dieser Offenbarung wird als "offener" Kompressor eine Ausführung verstanden, bei welcher aus wenigstens einer Seite einer Verdichtereinheit ein Wellenzapfen oder ein anderes Lastübertragungsmittel ragt, über das Arbeitsleistung in die Verdichtereinheit eingebracht werden kann.In another embodiment is an open compressor intended. For the purposes of this disclosure, an “open” compressor is understood to be an embodiment in which a shaft journal or another load transfer means protrudes from at least one side of a compressor unit, via which work output can be introduced into the compressor unit.

Gemäß einer besonders bevorzugten Ausführungsform sind der Kompressor und der geschlossene Kreislauf für das Antriebsmedium dazu eingerichtet, das Antriebsmedium bei höherem Druck als Umgebungsdruck im Kreis zu führen.According to a particularly preferred embodiment, the compressor and the closed circuit for the drive medium are set up to circulate the drive medium at a higher pressure than ambient pressure.

Gemäß einer bevorzugten Ausführungsform ist in der zweiten Leitung des geschlossenen Kreislaufes ein Kühler zur Kühlung des Antriebsmediums zwischen dem ersten Zylinder des Druckübersetzers und dem Kompressor angeordnet. Bei dieser Ausführungsform wird die Temperatur des Antriebsmediums bei der Rückführung vom ersten Zylinder zum Kompressor gesenkt. Auf diese Weise kann die Temperatur des Antriebsmediums nach der Komprimierung durch Wärmeaustausch mit dem verdichteten Arbeitsmedium erhöht werden, ohne dass die Temperatur im geschlossenen Kreislauf insgesamt immer weiter gesteigert werden würde. Vorteilhafterweise wird das Arbeitsmedium daher im geschlossenen Kreislauf auf verschiedenen Temperaturstufen geführt, um einen optimalen Wirkungsgrad beim Antrieb des Hochdruckkolbens zu erzielen.According to a preferred embodiment, a cooler for cooling the drive medium is arranged in the second line of the closed circuit between the first cylinder of the pressure booster and the compressor. In this embodiment, the temperature of the drive medium is reduced when it is returned from the first cylinder to the compressor. In this way, after compression, the temperature of the drive medium can be increased by exchanging heat with the compressed working medium, without the temperature in the closed circuit as a whole continuing to increase. The working medium is therefore advantageously conducted in a closed circuit at different temperature levels in order to achieve optimum efficiency when driving the high-pressure piston.

Um die Temperatur des Antriebsmediums in der Rückleitung vom Verdichter gezielt auf das passende Niveau abzusenken, ist bei einer bevorzugten Ausführungsform weiters vorgesehen:

  • ein Temperaturmesselement in der zweiten Leitung,
  • eine Steuereinheit, welche einerseits mit dem Temperaturmesselement und andererseits mit dem Kühler verbunden ist, um den Kühler in Abhängigkeit von der Temperatur des Antriebsmediums in der zweiten Leitung zu steuern.
In order to lower the temperature of the drive medium in the return line from the compressor specifically to the appropriate level, a preferred embodiment also provides:
  • a temperature measuring element in the second line,
  • a control unit which is connected on the one hand to the temperature measuring element and on the other hand to the cooler in order to control the cooler as a function of the temperature of the drive medium in the second line.

Zum Ausgleich von Druckspitzen bzw. Druckschwankungen ist bevorzugt ein erster Pufferspeicher zwischen dem Kompressor und dem Wärmetauscher und/oder ein zweiter Pufferspeicher zwischen dem Kühler und dem Kompressor vorgesehen.To compensate for pressure peaks or pressure fluctuations, a first buffer store is preferably provided between the compressor and the heat exchanger and / or a second buffer store between the cooler and the compressor.

Gemäß einer bevorzugten Ausführungsform ist zwischen dem Kompressor und dem ersten Zylinder ein Steuerschieber vorgesehen, welcher zwischen einer ersten Stellung und einer zweiten Stellung umschaltbar ist, um den ein erstes Volumen des ersten Zylinders gegenüber einem zweiten Volumen des ersten Zylinders abdichtenden Antriebskolben mittels des Antriebsmediums hin- und her zu bewegen. In der ersten Stellung verbindet der Steuerschieber die erste Leitung mit einem ersten Volumen des ersten Zylinders und die zweite Leitung mit einem zweiten Volumen des ersten Zylinders. In der zweiten Stellung verbindet der Steuerschieber die erste Leitung mit dem zweiten Volumen des ersten Zylinders und die zweite Leitung mit dem ersten Volumen des ersten Zylinders.According to a preferred embodiment, a control slide is provided between the compressor and the first cylinder, which can be switched between a first position and a second position, by means of the drive medium by means of the drive medium, by means of the drive medium, the drive piston sealing a first volume of the first cylinder against a second volume of the first cylinder and move forward. In the first position, the control slide connects the first line to a first volume of the first cylinder and the second line to a second volume of the first cylinder. In the second position, the control slide connects the first line to the second volume of the first cylinder and the second line to the first volume of the first cylinder.

Das erfindungsgemäße Verfahren zum Verdichten eines Arbeitsmediums weist zumindest die folgenden Schritte auf:

  • Komprimierung eines Antriebsmediums in einem Kompressor;
  • Bewegen eines Antriebskolbens mittels des komprimierten Antriebsmediums innerhalb eines ersten Zylinders;
  • Bewegen eines das Arbeitsmedium verdichtenden Hochdruckkolbens mittels des Antriebskolbens innerhalb eines zweiten Zylinders, und
  • eine Wärmeübertragung vom verdichteten Arbeitsmedium auf das komprimierte Antriebsmedium vor dem Eintritt des komprimierten Antriebsmediums in den ersten Zylinder des Antriebskolbens.
The method according to the invention for compressing a working medium has at least the following steps:
  • Compression of a drive medium in a compressor;
  • Moving a drive piston by means of the compressed drive medium within a first cylinder;
  • Moving a high-pressure piston compressing the working medium by means of the drive piston within a second cylinder, and
  • a heat transfer from the compressed working medium to the compressed drive medium before the compressed drive medium enters the first cylinder of the drive piston.

Gemäß einer besonders bevorzugten Ausführungsform umfasst das Verfahren weiters den Schritt

  • Leiten des Antriebsmediums in einem geschlossenen Kreislauf vom Kompressor über den ersten Zylinder zurück zum Kompressor.
According to a particularly preferred embodiment, the method further comprises the step
  • Guiding the drive medium in a closed circuit from the compressor via the first cylinder back to the compressor.

Gemäß einer besonders bevorzugten Ausführungsform wird das Antriebsmedium im Kompressor von einem Eingangsdruck auf einen Ausgangsdruck komprimiert, wobei der Eingangsdruck größer als ein Umgebungsdruck ist.According to a particularly preferred embodiment, the drive medium in the compressor is compressed from an input pressure to an output pressure, the input pressure being greater than an ambient pressure.

Der Eingangsdruck des Antriebsmediums am Eingang des Kompressors beträgt bevorzugt zwischen 0,5 bar und 50 bar, insbesondere zwischen 2 bar und 30 bar. Der Ausgangsdruck des Antriebsmediums am Ausgang des Kompressors beträgt bevorzugt zwischen 1 bar und 100 bar, insbesondere zwischen 5 bar und 40 bar.The inlet pressure of the drive medium at the inlet of the compressor is preferably between 0.5 bar and 50 bar, in particular between 2 bar and 30 bar. The outlet pressure of the drive medium at the outlet of the compressor is preferably between 1 bar and 100 bar, in particular between 5 bar and 40 bar.

Für die Zwecke dieser Offenbarung sollen sämtliche Druckwerte als Absolutdrucke verstanden werden.For the purposes of this disclosure, all pressure values are to be understood as absolute pressures.

Zur Temperaturabsenkung des Antriebsmediums vor dem Kompressor wird bevorzugt eine Kühlung des aus dem ersten Zylinder austretenden Antriebsmediums mittels eines Kühlers vorgenommen.In order to lower the temperature of the drive medium upstream of the compressor, the drive medium emerging from the first cylinder is preferably cooled by means of a cooler.

Das Antriebsmedium ist vorzugsweise von dem Arbeitsmedium verschieden. Gemäß einer besonders bevorzugten Ausführungsform ist das Antriebsmedium gasförmig, wobei als Antriebsmedium vorzugsweise eines von Luft, Stickstoff, CO2, Argon oder Krypton oder eine Mischung daraus vorgesehen ist. Die herkömmlichen Verdichter mit Gasantrieb haben einen hohen Energiebedarf, um die benötigte Antriebsleistung für den Antrieb des Hochdruckkolbens zur Verfügung zu stellen. Durch den geschlossenen Kreislauf des Antriebsmediums einerseits und die Wärmeübertragung vom verdichteten Arbeitsmedium auf das komprimierte Antriebsmedium andererseits kann der Wirkungsgrad beim Betrieb des Antriebskolbens wesentlich erhöht werden.The drive medium is preferably different from the working medium. According to a particularly preferred embodiment, the drive medium is gaseous, the drive medium preferably being one of air, nitrogen, CO 2 , argon or krypton or a mixture thereof. The conventional compressors with gas drive have a high energy requirement in order to provide the drive power required to drive the high-pressure piston. Due to the closed circuit of the drive medium on the one hand and the heat transfer from the compressed working medium to the compressed drive medium on the other hand, the efficiency when operating the drive piston can be increased significantly.

Bei einer besonders bevorzugten Anwendung ist das Arbeitsmedium gasförmig, wobei als Arbeitsmedium vorzugsweise molekularer Wasserstoff vorgesehen ist. Bevorzugt wird der Druck des Arbeitsmediums von einem Anfangsdruck, insbesondere zwischen 3 bar und 500 bar, auf einen Enddruck, insbesondere zwischen 100 bar und 1500 bar, insbesondere zwischen 700 bar und 1000 bar, angehoben. Diese Werte sind wiederum jeweils als Absoluter Druck zu verstehen.In a particularly preferred application, the working medium is gaseous, with molecular hydrogen preferably being provided as the working medium. The pressure of the working medium is preferably increased from an initial pressure, in particular between 3 bar and 500 bar, to a final pressure, in particular between 100 bar and 1500 bar, in particular between 700 bar and 1000 bar. These values are in turn to be understood as absolute pressure.

Die Erfindung wird im Folgenden anhand eines in der Zeichnung gezeigten Ausführungsbeispiels weiter erläutert.The invention is explained further below with the aid of an exemplary embodiment shown in the drawing.

Fig. 1 zeigt eine erfindungsgemäße Vorrichtung zum Verdichten eines Arbeitsmediums mittels eines Hochdruckkolbens, wobei eine Wärmeübertragung vom verdichteten Arbeitsmedium auf das komprimierte Antriebsmedium für den Antriebskolben durchgeführt wird. Fig. 1 shows a device according to the invention for compressing a working medium by means of a high pressure piston, with heat transfer from the compressed working medium to the compressed drive medium for the drive piston is carried out.

In Fig. 1 ist schematisch eine Vorrichtung 1 zum Verdichten eines gasförmigen Arbeitsmediums, vorzugsweise molekularer Wasserstoff, gezeigt. Die Vorrichtung 1 weist einen Kompressor 2 zur Kompression eines gasförmigen Antriebsmediums, vorzugsweise Luft, auf. Im Stand der Technik sind verschiedenste Typen von Kompressoren 2 bekannt. Beispielsweise kann der Kompressor 2 als Kolben- oder Schraubenverdichter ausgeführt sein. Der Kompressor kann genau eine Stufe oder mindestens zwei Stufen aufweisen. Der Kompressor 2 erhöht den Druck des Antriebsmediums von einem Eingangsdruck an einem Eingang 2a des Kompressors 2 auf einen Ausgangsdruck an einem Ausgang 2b des Kompressors 2.In Fig. 1 a device 1 for compressing a gaseous working medium, preferably molecular hydrogen, is shown schematically. The device 1 has a compressor 2 for compressing a gaseous drive medium, preferably air. A wide variety of types of compressors 2 are known in the prior art. For example, the compressor 2 can be designed as a piston or screw compressor. The compressor can have exactly one stage or at least two stages. The compressor 2 increases the pressure of the drive medium from an input pressure at an input 2a of the compressor 2 to an output pressure at an output 2b of the compressor 2.

Wie aus der Zeichnung weiters ersichtlich, wird das komprimierte Antriebsmedium zum Antrieb eines Druckübersetzers 3 verwendet. Der Druckübersetzer 3, auch als Druckumwandler bezeichnet, weist einen Antriebskolben 4 auf, welcher innerhalb eines ersten Zylinders 5 zwischen einer ersten Endposition und einer zweiten Endposition hin- und her bewegt wird. Für den Antrieb des Antriebskolbens 4 wird das Antriebsmedium in den ersten Zylinder 5 geleitet. Der Antriebskolben 4 dichtet ein erstes Volumen 6 des ersten Zylinders 5 gegenüber einem zweiten Volumen 7 des ersten Zylinders 5 ab. Der Druckübersetzer 3 weist zudem einen Hochdruckkolben 8 auf, mit welchem das Arbeitsmedium von einem Anfangsdruck auf einen Enddruck verdichtet wird. Der Hochdruckkolben 8 ist innerhalb eines zweiten Zylinders 9 zwischen einer ersten Endstellung und einer zweiten Endstellung hin- und her bewegbar. Dafür ist der Hochdruckkolben 8 mit dem Antriebskolben 4 derart verbunden, dass die Bewegung des Antriebskolbens 4 auf den Hochdruckkolben 8 übertragen wird. Um eine Druckübersetzung von der Niederdruck- zur Hochdruckseite zu erzielen, weist der Hochdruckkolben 8 eine geringere Kolbenfläche als der Antriebs- bzw. Niederdruckkolben 4 auf. In der gezeigten Ausführung ist der Antriebskolben 4 doppeltwirkend mit einem weiteren Hochdruckkolben 10 innerhalb eines Hochdruckzylinders 11 auf der vom Hochdruckkolben 8 abgewandten Seite des Antriebskolbens 4 ausgebildet. Das Arbeitsmedium wird mit dem Anfangsdruck über eine erste Zuleitung 12 dem zweiten Zylinder 9 und über eine zweite Zuleitung 13 dem Hochdruckzylinder 11 zugeführt. Nach der Verdichtung wird das Arbeitsmedium mit dem Enddruck über eine erste Ableitung 14 vom zweiten Zylinder 9 und über eine zweite Ableitung 15 vom Hochdruckzylinder 11 abgeleitet. In den Zu- und Ableitungen sind Ventile 12a, 13a, 14a, 15a vorgesehen. In der gezeigten Ausführung werden die erste Ableitung 14 und die zweite Ableitung 15 in einer gemeinsamen Ableitung 16 zusammengeführt. Bei einer einfachwirkenden Ausführung des Antriebskolbens 4 (nicht gezeigt) ist lediglich die erste Ableitung 14 vorgesehen.As can also be seen from the drawing, the compressed drive medium is used to drive a pressure booster 3. The pressure booster 3, also referred to as a pressure converter, has a drive piston 4 which is moved back and forth within a first cylinder 5 between a first end position and a second end position. To drive the drive piston 4, the drive medium is fed into the first cylinder 5. The drive piston 4 seals a first volume 6 of the first cylinder 5 from a second volume 7 of the first cylinder 5. The pressure booster 3 also has a high-pressure piston 8 with which the working medium is compressed from an initial pressure to a final pressure. The high-pressure piston 8 can be moved to and fro within a second cylinder 9 between a first end position and a second end position. For this purpose, the high-pressure piston 8 is connected to the drive piston 4 in such a way that the movement of the drive piston 4 is transmitted to the high-pressure piston 8. In order to achieve a pressure boost from the low-pressure to the high-pressure side, the high-pressure piston 8 has a smaller piston area than the drive or low-pressure piston 4. In the embodiment shown, the drive piston 4 is double-acting with a further high-pressure piston 10 within a high-pressure cylinder 11 on the side of the drive piston 4 facing away from the high-pressure piston 8. The working medium is at the initial pressure via a first feed line 12 to the second Cylinder 9 and fed to the high pressure cylinder 11 via a second feed line 13. After compression, the working medium with the final pressure is diverted from the second cylinder 9 via a first discharge line 14 and from the high-pressure cylinder 11 via a second discharge line 15. Valves 12a, 13a, 14a, 15a are provided in the supply and discharge lines. In the embodiment shown, the first discharge line 14 and the second discharge line 15 are brought together in a common discharge line 16. In the case of a single-acting design of the drive piston 4 (not shown), only the first discharge line 14 is provided.

Wie aus Fig. 1 weiters ersichtlich, wird das Arbeitsmedium in einem geschlossenen Kreislauf 17 geführt. Der geschlossene Kreislauf 17 weist eine erste Leitung 18 vom Ausgang 2a des Kompressors 2 zum ersten Zylinder 5 und eine zweite Leitung 19 (Rückführung) vom ersten Zylinder 5 zurück zum Eingang 2b des Kompressors 2 auf. Zudem ist eine Steuervorrichtung, insbesondere ein Steuerschieber 20, zur Änderung der Strömungsrichtung des Antriebsmediums im ersten Zylinder 5 vorgesehen. Dadurch kann der Antriebskolben 4 je nach Stellung der Steuervorrichtung von der einen Seite oder von der anderen Seite unter Druck gesetzt werden, so dass das Umschalten der Steuervorrichtung die Hin- und Her-Bewegung des Antriebskolbens 2 bewirkt. In der gezeigten Ausführung ist der Kompressor 2 vollhermetisch oder halbhermetisch ausgeführt. Vorteilhafterweise können so Gasleckagen reduziert werden.How out Fig. 1 It can also be seen that the working medium is guided in a closed circuit 17. The closed circuit 17 has a first line 18 from the outlet 2a of the compressor 2 to the first cylinder 5 and a second line 19 (return) from the first cylinder 5 back to the inlet 2b of the compressor 2. In addition, a control device, in particular a control slide 20, is provided for changing the direction of flow of the drive medium in the first cylinder 5. As a result, depending on the position of the control device, the drive piston 4 can be pressurized from one side or from the other side, so that the switching of the control device causes the drive piston 2 to move back and forth. In the embodiment shown, the compressor 2 is designed fully hermetically or semi-hermetically. In this way, gas leaks can advantageously be reduced.

Wie aus Fig. 1 ersichtlich, wird das Antriebsmedium in Strömungsrichtung 21 des Antriebsmediums gesehen zwischen dem Kompressor 2 und dem ersten Zylinder 5 des Druckübersetzers 3 über einen Wärmetauscher 22 geführt, in welchem ein Wärmeaustausch mit dem verdichteten Arbeitsmedium durchgeführt wird. Zu diesem Zweck ist der Wärmetauscher 22 mit der ersten Ableitung 14 und/oder mit der zweiten Ableitung 15, im Fall des gezeigten doppeltwirkenden Verdichters mit der gemeinsamen Ableitung 16, verbunden. Somit kann der Wärmegehalt des Arbeitsmediums nach der Verdichtung im zweiten Zylinder 9 zur Temperaturerhöhung des Antriebsmediums vor dem Eintritt in den ersten Zylinder 5 für den Antriebskolben 4 erhöht werden. Aus der idealen Gasgleichung (p*V=n*R*T) ergibt sich, dass das Produkt p*V erhöht wird, wenn die Temperatur des komprimierten Antriebsmediums erhöht wird. Die erbringbare Arbeit und folglich Leistung am Druckumsetzer wird dadurch erhöht. Somit wird für die gleiche Arbeit im Vergleich zu einem herkömmlichen System weniger (elektrische) Antriebsenergie für den Kompressor 2 benötigt.How out Fig. 1 As can be seen, the drive medium, seen in the direction of flow 21 of the drive medium, is guided between the compressor 2 and the first cylinder 5 of the pressure booster 3 via a heat exchanger 22 in which a heat exchange with the compressed working medium is carried out. For this purpose, the heat exchanger 22 is connected to the first discharge line 14 and / or to the second discharge line 15, in the case of the double-acting compressor shown, to the common discharge line 16. Thus, after compression in the second cylinder 9, the heat content of the working medium can be increased for the drive piston 4 to increase the temperature of the drive medium before it enters the first cylinder 5. From the ideal gas equation (p * V = n * R * T) it follows that that Product p * V is increased when the temperature of the compressed drive medium is increased. The work that can be performed and consequently the performance on the pressure converter is increased as a result. Thus, in comparison to a conventional system, less (electrical) drive energy is required for the compressor 2 for the same work.

In der gezeigten Ausführung ist zudem ein Kühler 23 in der zweiten Leitung 19 angeordnet, um eine Kühlung des Antriebsmediums am Weg vom ersten Zylinder 5 des Druckübersetzers 3 zurück zum Kompressor 2 zu erzielen. Der Kühler 23 kann als weiterer Wärmetauscher mit einem Ventilator 23a ausgebildet sein. In der gezeigten Ausführung ist zudem ein Temperaturmesselement 26 in der zweiten Leitung 19 vorgesehen, welches die Temperatur des Arbeitsmediums an eine Steuereinheit 27 übermittelt, welche den Ventilator 23a in Abhängigkeit von der Temperatur des Antriebsmediums in der zweiten Leitung 19 ansteuert.In the embodiment shown, a cooler 23 is also arranged in the second line 19 in order to achieve cooling of the drive medium on the way from the first cylinder 5 of the pressure booster 3 back to the compressor 2. The cooler 23 can be designed as a further heat exchanger with a fan 23a. In the embodiment shown, a temperature measuring element 26 is also provided in the second line 19, which transmits the temperature of the working medium to a control unit 27, which controls the fan 23a as a function of the temperature of the drive medium in the second line 19.

Weiters ist ein erster Pufferspeicher 24 zwischen dem Kompressor 2 und dem Wärmetauscher 22 und ein zweiter Pufferspeicher 25 zwischen dem Kühler 23 und dem Kompressor 2 vorgesehen.Furthermore, a first buffer store 24 is provided between the compressor 2 and the heat exchanger 22 and a second buffer store 25 is provided between the cooler 23 and the compressor 2.

Der besseren Übersicht halber sind in der Zeichnung lediglich die für das Verständnis der gezeigten Ausführungsform benötigten Komponenten dargestellt. Selbstverständlich kann die Verdichter-Vorrichtung 1 verschiedenste zusätzliche Komponenten und Modifikationen gegenüber der gezeigten Ausführungsform aufweisen.For the sake of clarity, only the components required for understanding the embodiment shown are shown in the drawing. Of course, the compressor device 1 can have a wide variety of additional components and modifications compared to the embodiment shown.

Claims (14)

  1. A device (1) for compressing a working medium comprising:
    - a compressor (2) for compressing a drive medium;
    - a pressure translator (3) with a drive piston (4) which can be actuated by means of the drive medium within a first cylinder (5) and with a high-pressure piston (8) which compresses the working medium within a second cylinder (9);
    characterized by
    - a heat exchanger (22) between the compressor (2) and the first cylinder (5) of the pressure translator (3) for transferring heat from the compressed working medium to the compressed drive medium.
  2. The device according to Claim 1, characterized by
    - a closed circuit (17) for the drive medium with a first line (18) from the compressor (2) to the first cylinder (5) and with a second line (19) from the first cylinder (5) to the compressor (2).
  3. The device according to Claim 2, characterized in that the compressor (2) is designed to be fully hermetic, semi-hermetic or open.
  4. The device according to Claim 2 or 3, characterized in that the compressor (2) and the closed circuit (17) for the drive medium are adapted to guide the drive medium at pressure higher than ambient pressure in the circuit.
  5. The device according to one of Claims 2 to 4, characterized by
    - a cooler (23) for cooling the drive medium in the second line (19) between the first cylinder (5) of the pressure translator (3) and the compressor (2).
  6. The device according to Claim 5, characterized by
    - a temperature measuring element (26) in the second line (19),
    - a control unit (27) which on the one hand is connected to the temperature measuring element (26) and on the other hand is connected to the cooler (23) in order to control the cooler (23) depending on the temperature of the drive medium in the second line (19) .
  7. The device according to one of Claims 1 to 6, characterized by
    - a first buffer storage device (24) between the compressor (2) and the heat exchanger (22) and/or a second buffer storage device (25) between the cooler (23) and the compressor (2).
  8. A method for compressing a working medium comprising:
    - compressing a drive medium in a compressor (2);
    - moving a drive piston (4) by means of the compressed drive medium within a first cylinder (5);
    - moving a high-pressure piston (8) which compresses the working medium by means of the drive piston (2) within a second cylinder (9),
    characterized by
    - a heat transfer from the compressed working medium to the compressed drive medium before entry of the compressed drive medium into the first cylinder (5) of the drive piston (4).
  9. The method according to Claim 8, characterized by:
    - guiding the drive medium in a closed circuit (18) from the compressor (2) via the first cylinder (5) back to the compressor (2).
  10. The method according to Claim 8 or 9, characterized in that the drive medium in the compressor (2) is compressed from an input pressure to an output pressure, wherein the input pressure is higher than an ambient pressure.
  11. The method according to Claim 10, characterized in that the input pressure is between 0.5 bar and 50 bar, in particular between 2 bar and 30 bar.
  12. The method according to one of Claims 8 to 11, characterized by:
    - cooling the drive medium emerging from the first cylinder (5) by means of a cooler (23).
  13. The method according to one of Claims 8 to 12, characterized in that the drive medium is gaseous, wherein preferably one of air, nitrogen, CO2, argon or krypton or a mixture thereof is provided as drive medium.
  14. The method according to one of Claims 8 to 13, characterized in that the working medium is gaseous, wherein preferably molecular hydrogen is provided as working medium.
EP19700822.0A 2018-01-23 2019-01-23 Method and device for compacting a working substance Active EP3728846B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL19700822T PL3728846T3 (en) 2018-01-23 2019-01-23 Method and device for compacting a working substance
SI201930074T SI3728846T1 (en) 2018-01-23 2019-01-23 Method and device for compacting a working substance

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP18152933.0A EP3514381A1 (en) 2018-01-23 2018-01-23 Method and device for compacting a working substance
PCT/EP2019/051537 WO2019145314A1 (en) 2018-01-23 2019-01-23 Device and method for compressing a working medium

Publications (2)

Publication Number Publication Date
EP3728846A1 EP3728846A1 (en) 2020-10-28
EP3728846B1 true EP3728846B1 (en) 2021-06-02

Family

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EP18152933.0A Withdrawn EP3514381A1 (en) 2018-01-23 2018-01-23 Method and device for compacting a working substance
EP19700822.0A Active EP3728846B1 (en) 2018-01-23 2019-01-23 Method and device for compacting a working substance

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP18152933.0A Withdrawn EP3514381A1 (en) 2018-01-23 2018-01-23 Method and device for compacting a working substance

Country Status (10)

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US (1) US11401925B2 (en)
EP (2) EP3514381A1 (en)
JP (1) JP6962648B2 (en)
DK (1) DK3728846T3 (en)
ES (1) ES2881647T3 (en)
HU (1) HUE054963T2 (en)
PL (1) PL3728846T3 (en)
PT (1) PT3728846T (en)
SI (1) SI3728846T1 (en)
WO (1) WO2019145314A1 (en)

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3665808A (en) * 1970-10-07 1972-05-30 Walter H Vestal Pumping system for liquid hydrocarbons and the like
DE2626954C2 (en) 1976-06-16 1985-04-11 Schmidt, Kranz & Co Gmbh, Zweigniederlassung Maschinenbau, 3421 Zorge Control slide arrangement for a hydraulic pump driven by compressed air
SE412939B (en) * 1977-09-09 1980-03-24 Kaelle Eur Control HYDRAULIC DRIVE DEPLACEMENT PUMP SEPARATELY FOR PUMPING OF THICK AND WIRING MEDIA
DE3018625C2 (en) * 1980-05-16 1982-11-18 Gebr. Eickhoff, Maschinenfabrik U. Eisengiesserei Mbh, 4630 Bochum Intensifier
US4527634A (en) * 1982-03-03 1985-07-09 Ici Americas Inc. Emergency vapor powered pump assembly
GB8417539D0 (en) * 1984-07-10 1984-08-15 Dale Mansfield Ltd Pumping arrangements
US4569480A (en) * 1984-08-03 1986-02-11 Speeflo Manufacturing Corporation Surge controlled air-hydraulic material sprayer
US5324175A (en) * 1993-05-03 1994-06-28 Northern Research & Engineering Corporation Pneumatically operated reciprocating piston compressor
US6386841B1 (en) * 1998-12-28 2002-05-14 Schmidt, Kranz & Co. Gmbh Pneumatically operated hydraulic pump
US20110044830A1 (en) * 2004-06-07 2011-02-24 Hunter Hitech Pty Ltd Pump assembly
FR2891347B1 (en) * 2005-09-28 2007-11-02 Air Liquide METHOD AND DEVICE FOR FILLING A PRESSURIZED GAS IN A RESERVOIR
JP5495293B2 (en) * 2009-07-06 2014-05-21 株式会社日立産機システム Compressor
JP6371653B2 (en) * 2014-09-19 2018-08-08 株式会社スギノマシン Ultra high pressure generator
AT515937B1 (en) * 2014-10-20 2016-01-15 Bhdt Gmbh Hydraulic drive for a pressure intensifier

Also Published As

Publication number Publication date
JP6962648B2 (en) 2021-11-05
PL3728846T3 (en) 2021-11-15
DK3728846T3 (en) 2021-07-12
ES2881647T3 (en) 2021-11-30
EP3728846A1 (en) 2020-10-28
WO2019145314A1 (en) 2019-08-01
EP3514381A1 (en) 2019-07-24
US11401925B2 (en) 2022-08-02
PT3728846T (en) 2021-07-14
JP2021511464A (en) 2021-05-06
SI3728846T1 (en) 2021-08-31
US20210033085A1 (en) 2021-02-04
HUE054963T2 (en) 2021-10-28

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