EP3728846A1 - Device and method for compressing a working medium - Google Patents

Device and method for compressing a working medium

Info

Publication number
EP3728846A1
EP3728846A1 EP19700822.0A EP19700822A EP3728846A1 EP 3728846 A1 EP3728846 A1 EP 3728846A1 EP 19700822 A EP19700822 A EP 19700822A EP 3728846 A1 EP3728846 A1 EP 3728846A1
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.)
Granted
Application number
EP19700822.0A
Other languages
German (de)
French (fr)
Other versions
EP3728846B1 (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 SI201930074T priority Critical patent/SI3728846T1/en
Priority to PL19700822T priority patent/PL3728846T3/en
Publication of EP3728846A1 publication Critical patent/EP3728846A1/en
Application granted granted Critical
Publication of EP3728846B1 publication Critical patent/EP3728846B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 compacting a
  • Hydraulic pump which has a working space and a pneumatic piston, wherein the pneumatic piston is connected to a hydraulic piston.
  • the hydraulic piston is moved in a hydraulic cylinder, on which a valve housing is pushed, which serves for the connection of hydraulic lines.
  • the operated air-piston compressor having 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.
  • the compressed air is passed through a heat exchanger after compression in the first stage of the compressor before being further compressed in the second stage.
  • the invention sets the goal to increase the efficiency of the drive of the high-pressure piston. This object is achieved by a device having the features of claim 1 and a method having the features of claim 8.
  • Working medium has at least the following components:
  • the heat exchanger for a heat exchange between the working medium after the compression in the second
  • the temperature of the drive medium can be increased in the compressed state before the drive piston with the
  • Drive medium is applied in the compressed state.
  • This principle can be applied to different types of compressors, in particular a single- or double-acting,
  • the compressor can also be designed as a piston compressor single or double acting, single stage or two stages.
  • the location and direction indications refer to the flow direction of the drive medium or the working medium in the compressor operation.
  • a closed circuit for the drive medium with a first line from Compressor to the first cylinder and provided with a second line from the first cylinder to the compressor.
  • Air circulation increases the energy efficiency compared to an open reference system without exhaust return.
  • the heat exchanger is preferably designed as a recuperator, wherein the compressed drive medium and the compressed
  • the heat exchanger is designed as a regenerator, wherein a heat storage is provided in a heat exchanger mass.
  • a heat exchanger may be provided, for example, a plate heat exchanger or a tube-in-tube heat exchanger.
  • a plate heat exchanger or a tube-in-tube heat exchanger.
  • various 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.
  • Hermetic compressor understood a design in which a preferably pressure-tight housing both a
  • “Semi-hermetic” compressor understood a design in which a drive motor with a compressor housing is pressure-tight and releasably connected.
  • an open compressor intended.
  • an open compressor intended.
  • Open compressor understood an embodiment in which protrudes from at least one side of a compressor unit, a shaft journal or other load transfer means, over the
  • Compressor and the closed circuit for the drive medium to set the drive medium at higher pressure than
  • the temperature of the drive medium is lowered during the return from the first cylinder to the compressor. In this way, the temperature of the drive medium after the
  • Working medium can be increased without affecting the temperature
  • the working medium is therefore in
  • a preferred embodiment further provides:
  • a control unit which is connected on the one hand with the temperature measuring element and on the other hand with the radiator to control the radiator in dependence on the temperature of the drive medium in the second conduit.
  • a first buffer memory between the compressor and the heat exchanger and / or a second buffer memory provided between the radiator and the compressor.
  • a spool is provided between the compressor and the first cylinder, which between a first position and a second
  • Switchable position to reciprocate a first volume of the first cylinder relative to a second volume of the first cylinder sealing drive piston by means of the drive medium back and forth. In the first position connects the
  • Control spool the first line with a first volume of the first cylinder and the second line with a second
  • the spool In the second position, the spool connects the first conduit to the second volume of the first cylinder and the second conduit to the first volume of the first cylinder.
  • Working medium has at least the following steps:
  • the method further comprises the step
  • the drive medium in the compressor is compressed from an input pressure to an output pressure, wherein the input pressure is greater than an ambient pressure.
  • the inlet pressure of the drive fluid at the inlet of the compressor is preferably between 0.5 bar and 50 bar, in particular between 2 bar and 30 bar.
  • the output 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.
  • cooling of the drive medium emerging from the first cylinder is preferably carried out by means of a cooler.
  • the drive medium is preferably different from the working medium.
  • the drive medium is gaseous, wherein as drive medium preferably one of air, nitrogen, CO2, argon or krypton or a mixture thereof is provided.
  • the conventional gas-powered compressors require a large amount of energy to provide the drive power needed 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 fluid to the compressed drive medium on the other hand, the efficiency in the operation of the drive piston can be significantly increased.
  • the working medium is gaseous, with preferably molecular hydrogen 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 again to be understood as absolute pressure.
  • Fig. 1 shows an inventive device for compressing a working medium by means of a high pressure piston, wherein a heat transfer from the compressed working fluid to the compressed drive medium for the drive piston is performed.
  • 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 may be designed as a piston or screw compressor.
  • the compressor may 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 2 a of the compressor 2 to an output pressure at an output 2 b 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 transducer, has a drive piston 4, which is reciprocated within a first cylinder 5 between a first end position and a second end position.
  • the drive medium is directed into the first cylinder 5.
  • the drive piston 4 seals a first volume 6 of the first cylinder 5 with respect to a second volume 7 of the first cylinder 5.
  • the pressure booster 3 also has a high pressure piston 8, with which the working fluid is compressed from an initial pressure to a final pressure.
  • the high-pressure piston 8 is reciprocable 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 such 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 surface 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 facing away from the high pressure piston 8 side of the drive piston 4 is formed.
  • the working fluid is the second with the initial pressure via a first supply line 12 Cylinder 9 and fed via a second supply line 13 to the high-pressure cylinder 11.
  • the working fluid is discharged with the final pressure via a first discharge line 14 from the second cylinder 9 and via a second discharge line 15 from the high-pressure cylinder 11.
  • a first discharge line 14 from the second cylinder 9 and via a second discharge line 15 from the high-pressure cylinder 11.
  • the supply and discharge valves 12a, 13a, 14a, 15a are provided.
  • the first derivative 14 and the second derivative 15 are merged in a common derivative 16.
  • only the first derivative 14 is provided.
  • the closed circuit 17 has a first line 18 from the output 2a of the compressor 2 to the first cylinder 5 and a second line 19 (feedback) from the first cylinder 5 back to the input 2b of the compressor 2.
  • a control device in particular a control slide 20, for changing the flow direction of the drive medium in the first cylinder 5 is provided.
  • 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 reciprocating movement of the drive piston 2.
  • the compressor 2 is designed to be fully hermetic or semi-hermetic.
  • gas leaks can thus be reduced.
  • the drive medium As seen from FIG. 1, the drive medium, as seen in the flow direction 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 content of the working medium can be increased after compression in the second cylinder 9 to increase the temperature of the drive medium before entering the first cylinder 5 for the drive piston 4.
  • less (electrical) power is needed for the compressor 2 for the same work compared to a conventional system.
  • a cooler 23 is 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 may be formed as a further heat exchanger with a fan 23 a.
  • 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 in dependence on the temperature of the drive medium in the second line 19.
  • a first buffer memory 24 is provided between the compressor 2 and the heat exchanger 22 and a second buffer memory 25 between the radiator 23 and the compressor 2.

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

Abstract

The invention relates to a device (1) and a method for compressing a working medium, comprising: - compressing a drive medium in a compressor (2); - moving a drive piston (4) within a first cylinder (5) by means of the compressed drive medium; - moving a high-pressure piston (8), which compresses the working medium, within a second cylinder (9) by means of the drive piston (2); and - transferring heat from the compressed working medium to the compressed drive medium before the compressed drive medium enters the first cylinder (5) of the drive piston (4).

Description

Vorrichtung und Verfahren zum Verdichten eines Arbeitsmediums  Apparatus and method for compressing a working medium
Die Erfindung betrifft eine Vorrichtung zum Verdichten eines The invention relates to a device for compacting a
Arbeitsmediums mit den Merkmalen des Oberbegriffs von Anspruch 1 sowie ein Verfahren zum Verdichten eines Arbeitsmediums mit den Merkmalen des Oberbegriffs von Anspruch 8. Working medium with the features of the preamble of claim 1 and a method for compressing a working medium having 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) . Such compressors are known in the prior art in various designs (see, for example, US 4,104,008 A).
Die US 4,104,008 A offenbart eine druckluftbetriebene  US 4,104,008 A discloses a compressed air powered
Hydraulikpumpe, die einen Arbeitsraum und einen Pneumatikkolben aufweist, wobei der Pneumatikkolben mit einem Hydraulikkolben verbunden ist. Mithilfe eines Hilfsschiebers, der gegen den Hydraulic pump, which has a working space and a pneumatic piston, wherein the pneumatic piston is connected to a hydraulic piston. Using an auxiliary slide, which is against the
Arbeitsraum abgedichtet ist, und eines Steuerschiebers, wird Workspace is sealed, and a spool, is
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. Air supplied to the pneumatic piston to move it against a spring force of a helical compression spring. By the movement of the pneumatic piston, the hydraulic piston is moved in a hydraulic cylinder, on which a valve housing is pushed, which serves for the connection of hydraulic lines.
Die US 5,324,175 A zeigt einen zweistufigen, pneumatisch US 5,324,175 A shows a two-stage, pneumatic
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. operated air-piston compressor having 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. The compressed air is passed through a heat exchanger after compression in the first stage of the compressor before being further compressed in the second stage.
In den DE 30 18 625 Al und US 6,386,841 Bl sind verschiedene In DE 30 18 625 A1 and US 6,386,841 Bl are various
Ausführungen von Verdichtern gezeigt, welche jedoch nicht im Versions of compressors shown, which are not in the
Hinblick darauf ausgelegt sind, die Effizienz der Verdichter zu erhöhen . Are designed to increase the efficiency of the compressor.
Als nachteilig erweist sich jedoch der hohe Energieverbrauch von Verdichtern mit Gasantrieb. However, the high energy consumption of compressors with gas drive proves disadvantageous.
Vor diesem Hintergrund setzt sich die Erfindung zum Ziel, den Wirkungsgrad für den Antrieb des Hochdruckkolbens zu erhöhen. Diese Aufgabe wird durch eine Vorrichtung mit den Merkmalen von Anspruch 1 und ein Verfahren mit den Merkmalen von Anspruch 8 gelöst . Against this background, the invention sets the goal to increase the efficiency of the drive of the high-pressure piston. This object is achieved by a device having the features of claim 1 and a method having the features of claim 8.
Die erfindungsgemäße Vorrichtung zum Verdichten eines The inventive device for compacting a
Arbeitsmediums weist zumindest die folgenden Komponenten auf: Working medium has at least the following components:
- einen Kompressor zur Kompression eines Antriebsmediums; - A compressor for compression of a drive medium;
- einen Druckübersetzer mit einem mittels des Antriebsmediums betätigbaren Antriebskolben innerhalb eines ersten - A pressure booster with an actuatable by means of the drive medium drive piston within a first
Zylinders und mit einem das Arbeitsmedium verdichtenden Hochdruckkolben innerhalb eines zweiten Zylinders,  Cylinder and with a working medium compressing high-pressure piston within a second cylinder,
- einen Wärmetauscher zwischen dem Kompressor und dem ersten Zylinder des Druckübersetzers zur Wärmeübertragung vom verdichteten Arbeitsmedium auf das komprimierte  - A heat exchanger between the compressor and the first cylinder of the pressure booster for heat transfer from the compressed working fluid to the compressed
Antriebsmedium.  Drive medium.
Erfindungsgemäß ist der Wärmetauscher für einen Wärmeaustausch zwischen dem Arbeitsmedium nach der Verdichtung im zweiten According to the invention, the heat exchanger for a heat exchange between the working medium after the compression in the second
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 Cylinder and the drive medium before entering the first cylinder of the pressure booster set up. Advantageously, the temperature of the drive medium can be increased in the compressed state before the drive piston with the
Antriebsmedium im komprimierten Zustand beaufschlagt wird. Drive medium is applied in the compressed state.
Dadurch steht eine höhere Arbeitsleistung für den Betrieb des Hochdruckkolbens zur Verfügung, so dass der Wirkungsgrad des Verdichters gesteigert werden kann. As a result, a higher performance for the operation of the high-pressure piston is available, so that the efficiency of the compressor can be increased.
Dieses Prinzip kann bei verschiedenen Typen von Verdichtern, insbesondere bei einem einfach- oder doppeltwirkenden, This principle can be applied to different types of compressors, in particular a single- or double-acting,
einstufigen oder zweistufigen Verdichter genutzt werden. Der Kompressor kann als Kolbenverdichter ebenfalls einfach- oder doppeltwirkend, einstufig oder zweistufig ausgeführt sein. single-stage or two-stage compressors are used. The compressor can also be designed as a piston compressor single or double acting, single stage or two stages.
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 indications, such as "before", "after", "between", etc., refer to the flow direction of the drive medium or the working medium in the 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 In a preferred embodiment, a closed circuit for the drive medium with a first line 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
Überlegungen zu einem idealen Druckluftsystem mit geschlossenem Luftkreislauf" , O+P 5/2009, wurde in einem anderen Zusammenhang gezeigt, dass bei einem Druckluftsystem mit einem Considerations for an Ideal Compressed Air System with Closed Air Circulation ", O + P 5/2009, was shown in another context, that in a compressed air system with a
Druckluftzylinder die Ausbildung eines geschlossenen Compressed air cylinder forming a closed
Luftkreislaufes die Energieeffizienz gegenüber einem offenen Referenzsystem ohne Abluftrückführung erhöht. Air circulation increases the energy efficiency compared to an open reference system without exhaust return.
Der Wärmetauscher ist bevorzugt als Rekuperator ausgeführt, wobei das komprimierte Antriebsmedium und das verdichtete The heat exchanger is preferably designed as a recuperator, wherein the compressed drive medium and the compressed
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. Working medium are separated by means of at least one wall. In an alternative embodiment, the heat exchanger is designed as a regenerator, wherein a heat storage is 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. As a heat exchanger may be provided, for example, a plate heat exchanger or a tube-in-tube heat exchanger. However, various 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 reduce the required drive power further, it is advantageous if the compressor is designed to be fully hermetic or semi-hermetic.
Für die Zwecke dieser Offenbarung wird als For the purposes of this disclosure, as
„vollhermetischer" Kompressor eine Ausführung verstanden, bei welcher ein vorzugsweise druckdichtes Gehäuse sowohl einen  "Hermetic" compressor understood a design in which a preferably pressure-tight housing both a
Antriebsmotor als auch eine Verdichtereinheit umschließt, wobei das umschließende Gehäuse insbesondere verschweißt ist und die Medienleitungen durch das Gehäuse durchgeführt sind. Drive motor and a compressor unit encloses, wherein the enclosing housing is in particular welded and the media lines are performed by the housing.
Für die Zwecke dieser Offenbarung wird als For the purposes of this disclosure, as
„halbhermetischer" Kompressor eine Ausführung verstanden, bei welcher ein Antriebsmotor mit einem Verdichtergehäuse druckdicht und lösbar verbunden ist.  "Semi-hermetic" compressor understood a design in which a drive motor with a compressor housing is pressure-tight and releasably connected.
Bei einer weiteren Ausführungsform ist ein offener Kompressor vorgesehen. Für die Zwecke dieser Offenbarung wird als In another embodiment, an open compressor intended. For the purposes of this disclosure, as
„offener" Kompressor eine Ausführung verstanden, bei welcher aus wenigstens einer Seite einer Verdichtereinheit ein Wellenzapfen oder ein anderes Lastübertragungsmittel ragt, über das "Open" compressor understood an embodiment in which protrudes from at least one side of a compressor unit, a shaft journal or other load transfer means, over the
Arbeitsleistung in die Verdichtereinheit eingebracht werden kann. Work performance can be introduced into the compressor unit.
Gemäß einer besonders bevorzugten Ausführungsform sind der According to a particularly preferred embodiment of the
Kompressor und der geschlossene Kreislauf für das Antriebsmedium dazu eingerichtet, das Antriebsmedium bei höherem Druck als Compressor and the closed circuit for the drive medium to set the drive medium at higher pressure than
Umgebungsdruck im Kreis zu führen. Ambient pressure in a circle.
Gemäß einer bevorzugten Ausführungsform ist in der zweiten According to a preferred embodiment is in the second
Leitung des geschlossenen Kreislaufes ein Kühler zur Kühlung des Antriebsmediums zwischen dem ersten Zylinder des Conduction of the closed circuit a cooler for cooling the drive medium between the first cylinder of the
Druckübersetzers und dem Kompressor angeordnet. Bei dieser Pressure booster and the compressor arranged. At this
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 Embodiment, the temperature of the drive medium is lowered during the return from the first cylinder to the compressor. In this way, the temperature of the drive medium after the
Komprimierung durch Wärmeaustausch mit dem verdichteten Compression by heat exchange with the compacted
Arbeitsmedium erhöht werden, ohne dass die Temperatur im Working medium can be increased without affecting the temperature
geschlossenen Kreislauf insgesamt immer weiter gesteigert werden würde. Vorteilhafterweise wird das Arbeitsmedium daher im closed cycle would be increased more and more. Advantageously, the working medium is therefore in
geschlossenen Kreislauf auf verschiedenen Temperaturstufen closed circuit at different temperature levels
geführt, um einen optimalen Wirkungsgrad beim Antrieb des led to optimum efficiency in driving the
Hochdruckkolbens zu erzielen. To achieve 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: In order to lower the temperature of the drive medium in the return line from the compressor to the appropriate level, a preferred embodiment further provides:
— ein Temperaturmesselement in der zweiten Leitung,  A temperature measuring element in the second line,
— 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 .  - A control unit which is connected on the one hand with the temperature measuring element and on the other hand with the radiator to control the radiator in dependence on the temperature of the drive medium in the second conduit.
Zum Ausgleich von Druckspitzen bzw. Druckschwankungen ist To compensate for pressure peaks or pressure fluctuations
bevorzugt ein erster Pufferspeicher zwischen dem Kompressor und dem Wärmetauscher und/oder ein zweiter Pufferspeicher zwischen dem Kühler und dem Kompressor vorgesehen. Gemäß einer bevorzugten Ausführungsform ist zwischen dem Kompressor und dem ersten Zylinder ein Steuerschieber vorgesehen, welcher zwischen einer ersten Stellung und einer zweiten Preferably, a first buffer memory between the compressor and the heat exchanger and / or a second buffer memory provided between the radiator and the compressor. According to a preferred embodiment, a spool is provided between the compressor and the first cylinder, which between a first position and a second
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 Switchable position to reciprocate a first volume of the first cylinder relative to a second volume of the first cylinder sealing drive piston by means of the drive medium back and forth. In the first position connects the
Steuerschieber die erste Leitung mit einem ersten Volumen des ersten Zylinders und die zweite Leitung mit einem zweiten Control spool the first line with a first volume of the first cylinder and the second line with a second
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. Volume of the first cylinder. In the second position, the spool connects the first conduit to the second volume of the first cylinder and the second conduit to the first volume of the first cylinder.
Das erfindungsgemäße Verfahren zum Verdichten eines The inventive method for compacting a
Arbeitsmediums weist zumindest die folgenden Schritte auf: Working medium has at least the following steps:
- Komprimierung eines Antriebsmediums in einem Kompressor;  - Compression of a drive medium in a compressor;
- Bewegen eines Antriebskolbens mittels des komprimierten  - Moving a drive piston by means of the compressed
Antriebsmediums innerhalb eines ersten Zylinders;  Drive medium within a first cylinder;
- Bewegen eines das Arbeitsmedium verdichtenden  - moving a working medium compressing
Hochdruckkolbens mittels des Antriebskolbens innerhalb eines zweiten Zylinders, und  High-pressure piston by means of the drive piston within a second cylinder, and
- eine Wärmeübertragung vom verdichteten Arbeitsmedium auf  - A heat transfer from the compressed working fluid
das komprimierte Antriebsmedium vor dem Eintritt des  the compressed drive medium before the entry of
komprimierten Antriebsmediums in den ersten Zylinder des Antriebskolbens .  compressed drive medium in the first cylinder of the drive piston.
Gemäß einer besonders bevorzugten Ausführungsform umfasst das Verfahren weiters den Schritt According to a particularly preferred embodiment, the method further comprises the step
- Leiten des Antriebsmediums in einem geschlossenen Kreislauf vom Kompressor über den ersten Zylinder zurück zum  - Passing the drive medium in a closed circuit from the compressor via the first cylinder back to
Kompressor .  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, wherein the input pressure is 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 fluid at the inlet of the compressor is preferably between 0.5 bar and 50 bar, in particular between 2 bar and 30 bar. The output 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 pressures 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. To lower the temperature of the drive medium in front of the compressor, cooling of the drive medium emerging from the first cylinder is preferably carried out 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, wherein as drive medium preferably one of air, nitrogen, CO2, argon or krypton or a mixture thereof is provided. The conventional gas-powered compressors require a large amount of energy to provide the drive power needed 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 fluid to the compressed drive medium on the other hand, the efficiency in the operation of the drive piston can be significantly increased.
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 preferably molecular hydrogen 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 again to be understood as absolute pressure.
Die Erfindung wird im Folgenden anhand eines in der Zeichnung gezeigten Ausführungsbeispiels weiter erläutert. The invention will be explained below with reference to an 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 an inventive device for compressing a working medium by means of a high pressure piston, wherein a heat transfer from the compressed working fluid to the compressed drive medium for the drive piston is performed.
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. Various types of compressors 2 are known in the prior art. For example, the compressor 2 may be designed as a piston or screw compressor. The compressor may 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 2 a of the compressor 2 to an output pressure at an output 2 b 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 transducer, has a drive piston 4, which is reciprocated within a first cylinder 5 between a first end position and a second end position. For driving the drive piston 4, the drive medium is directed into the first cylinder 5. The drive piston 4 seals a first volume 6 of the first cylinder 5 with respect to a second volume 7 of the first cylinder 5. The pressure booster 3 also has a high pressure piston 8, with which the working fluid is compressed from an initial pressure to a final pressure. The high-pressure piston 8 is reciprocable within a second cylinder 9 between a first end position and a second end position. For this, the high pressure piston 8 is connected to the drive piston 4 such that the movement of the drive piston 4 is transmitted to the high pressure piston 8. In order to achieve a pressure increase from the low-pressure side to the high-pressure side, the high-pressure piston 8 has a smaller piston surface 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 facing away from the high pressure piston 8 side of the drive piston 4 is formed. The working fluid is the second with the initial pressure via a first supply line 12 Cylinder 9 and fed via a second supply line 13 to the high-pressure cylinder 11. After compression, the working fluid is discharged with the final pressure via a first discharge line 14 from the second cylinder 9 and via a second discharge line 15 from the high-pressure cylinder 11. In the supply and discharge valves 12a, 13a, 14a, 15a are provided. In the embodiment shown, the first derivative 14 and the second derivative 15 are merged in a common derivative 16. In a single-acting embodiment of the drive piston 4 (not shown), only the first derivative 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. As further seen from Fig. 1, the working fluid is guided in a closed circuit 17. The closed circuit 17 has a first line 18 from the output 2a of the compressor 2 to the first cylinder 5 and a second line 19 (feedback) from the first cylinder 5 back to the input 2b of the compressor 2. In addition, a control device, in particular a control slide 20, for changing the flow direction of the drive medium in the first cylinder 5 is provided. 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 reciprocating movement of the drive piston 2. In the embodiment shown, the compressor 2 is designed to be fully hermetic or semi-hermetic. Advantageously, gas leaks can thus 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 . As can be seen from FIG. 1, the drive medium, as seen in the flow direction 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 with the first derivative 14 and / or with the second discharge line 15, in the case of the double-acting compressor shown with the common discharge line 16, respectively. Thus, the heat content of the working medium can be increased after compression in the second cylinder 9 to increase the temperature of the drive medium before entering the first cylinder 5 for the drive piston 4. The ideal gas equation (p * V = n * R * T) shows that the Product p * V is increased when the temperature of the compressed drive fluid is increased. The deliverable work and thus performance at the pressure converter is thereby increased. Thus, less (electrical) power is needed for the compressor 2 for the same work compared to a conventional system.
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, moreover, a cooler 23 is 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 may be formed as a further heat exchanger with a fan 23 a. 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 in dependence on 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 memory 24 is provided between the compressor 2 and the heat exchanger 22 and a second buffer memory 25 between the radiator 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 may have a variety of additional components and modifications over the embodiment shown

Claims

Patentansprüche : Claims:
1. Vorrichtung (1) zum Verdichten eines Arbeitsmediums 1. Device (1) for compressing a working medium
aufweisend : comprising:
— einen Kompressor (2) zur Kompression eines Antriebsmediums; - A compressor (2) for compression of a drive medium;
— einen Druckübersetzer (3) mit einem mittels des - A pressure intensifier (3) with a means of the
Antriebsmediums betätigbaren Antriebskolben (4) innerhalb eines ersten Zylinders (5) und mit einem das Arbeitsmedium verdichtenden Hochdruckkolben (8) innerhalb eines zweiten Zylinders ( 9) ;  Drive medium actuated drive piston (4) within a first cylinder (5) and with a working medium compressing the high-pressure piston (8) within a second cylinder (9);
gekennzeichnet durch  marked by
— einen Wärmetauscher (22) zwischen dem Kompressor (2) und  - A heat exchanger (22) between the compressor (2) and
dem ersten Zylinder (5) des Druckübersetzers (3) zur  the first cylinder (5) of the pressure booster (3) for
Wärmeübertragung vom verdichteten Arbeitsmedium auf das komprimierte Antriebsmedium.  Heat transfer from the compressed working fluid to the compressed drive medium.
2. Vorrichtung nach Anspruch 1, gekennzeichnet durch 2. Apparatus according to claim 1, characterized by
— einen geschlossenen Kreislauf (17) für das Antriebsmedium mit einer ersten Leitung (18) vom Kompressor (2) zum ersten Zylinder (5) und mit einer zweiten Leitung (19) vom ersten Zylinder (5) zum Kompressor (2) .  - 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. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Kompressor (2) vollhermetisch, halbhermetisch oder offen ausgeführt ist. 3. A device according to claim 2, characterized in that the compressor (2) is designed to be fully hermetic, semi-hermetic or open.
4. Vorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Kompressor (2) und der geschlossene Kreislauf (17) für das Antriebsmedium dazu eingerichtet sind, das Antriebsmedium bei höherem Druck als Umgebungsdruck im Kreis zu führen. 4. Apparatus 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 a higher pressure than ambient pressure in the circuit.
5. Vorrichtung nach einem der Ansprüche 2 bis 4, gekennzeichnet durch 5. Device according to one of claims 2 to 4, characterized by
— einen Kühler (23) zur Kühlung des Antriebsmediums in der zweiten Leitung (19) zwischen dem ersten Zylinder (5) des Druckübersetzers (3) und dem Kompressor (2) .  - A cooler (23) for cooling the drive medium in the second line (19) between the first cylinder (5) of the pressure booster (3) and the compressor (2).
6. Vorrichtung nach Anspruch 5, gekennzeichnet durch 6. Apparatus according to claim 5, characterized by
— ein Temperaturmesselement (26) in der zweiten Leitung (19), A temperature measuring element (26) in the second line (19),
— eine Steuereinheit (27), welche einerseits mit dem Temperaturmesselement (26) und andererseits mit dem Kühler (23) verbunden ist, um den Kühler (23) in Abhängigkeit von der Temperatur des Antriebsmediums in der zweiten Leitung (19) zu steuern. - A control unit (27), which on the one hand with the Temperature sensing element (26) and on the other hand connected to the radiator (23) to control the radiator (23) in dependence on the temperature of the drive medium in the second conduit (19).
7. Vorrichtung nach einem der Ansprüche 1 bis 6, gekennzeichnet durch 7. Device according to one of claims 1 to 6, characterized by
- einen ersten Pufferspeicher (24) zwischen dem Kompressor (2) und dem Wärmetauscher (22) und/oder einem zweiten Pufferspeicher (25) zwischen dem Kühler (23) und dem Kompressor (2 ) .  - A first buffer memory (24) between the compressor (2) and the heat exchanger (22) and / or a second buffer memory (25) between the radiator (23) and the compressor (2).
8. Verfahren zum Verdichten eines Arbeitsmediums aufweisend: 8. A method for compressing a working medium comprising:
- Komprimierung eines Antriebsmediums in einem Kompressor (2); - Compression of a drive medium in a compressor (2);
- Bewegen eines Antriebskolbens (4) mittels des komprimierten Antriebsmediums innerhalb eines ersten Zylinders (5) ; - Moving a drive piston (4) by means of the compressed drive medium within a first cylinder (5);
- Bewegen eines das Arbeitsmedium verdichtenden  - moving a working medium compressing
Hochdruckkolbens (8) mittels des Antriebskolbens (2)  High-pressure piston (8) by means of the drive piston (2)
innerhalb eines zweiten Zylinders (9),  within a second cylinder (9),
gekennzeichnet durch  marked by
- eine Wärmeübertragung vom verdichteten Arbeitsmedium auf  - A heat transfer from the compressed working fluid
das komprimierte Antriebsmedium vor dem Eintritt des  the compressed drive medium before the entry of
komprimierten Antriebsmediums in den ersten Zylinder (5) des Antriebskolbens (4) .  compressed drive medium in the first cylinder (5) of the drive piston (4).
9. Verfahren nach Anspruch 8, gekennzeichnet durch: 9. The method according to claim 8, characterized by:
- Leiten des Antriebsmediums in einem geschlossenen Kreislauf (18) vom Kompressor (2) über den ersten Zylinder (5) zurück zum Kompressor (2) .  - Passing the drive medium in a closed circuit (18) from the compressor (2) via the first cylinder (5) back to the compressor (2).
10. Verfahren nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass das Antriebsmedium im Kompressor (2) von einem Eingangsdruck auf einen Ausgangsdruck komprimiert wird, wobei der Eingangsdruck größer als ein Umgebungsdruck ist. 10. The method according to claim 8 or 9, characterized in that the drive medium in the compressor (2) is compressed by an input pressure to an output pressure, wherein the input pressure is greater than an ambient pressure.
11. Verfahren nach Anspruch 10, dadurch gekennzeichnet, dass der Eingangsdruck zwischen 0,5 bar und 50 bar, insbesondere zwischen 2 bar und 30 bar, beträgt. 11. The method according to claim 10, characterized in that the inlet pressure between 0.5 bar and 50 bar, in particular between 2 bar and 30 bar, is.
12. Verfahren nach einem der Ansprüche 8 bis 11, gekennzeichnet durch 12. The method according to any one of claims 8 to 11, characterized by
Kühlung des aus dem ersten Zylinder (5) austretenden Antriebsmediums mittels eines Kühlers (23) .  Cooling of the drive medium emerging from the first cylinder (5) by means of a cooler (23).
13. Verfahren nach einem der Ansprüche 8 bis 12, dadurch gekennzeichnet, dass das Antriebsmedium gasförmig ist, wobei als Antriebsmedium vorzugsweise eines von Luft, Stickstoff, CCg, Agron oder Krypton oder eine Mischung daraus vorgesehen ist. 13. The method according to any one of claims 8 to 12, characterized in that the drive medium is gaseous, wherein as drive medium preferably one of air, nitrogen, CCg, Agron or Krypton or a mixture thereof is provided.
14. Verfahren nach einem der Ansprüche 8 bis 13, dadurch gekennzeichnet, dass das Arbeitsmedium gasförmig ist, wobei als Arbeitsmedium vorzugsweise molekularer Wasserstoff vorgesehen ist . 14. The method according to any one of claims 8 to 13, characterized in that the working medium is gaseous, wherein preferably molecular hydrogen is provided as the 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
SI201930074T SI3728846T1 (en) 2018-01-23 2019-01-23 Method and device for compacting a working substance
PL19700822T PL3728846T3 (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)

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

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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
WO2005121555A1 (en) * 2004-06-07 2005-12-22 Hunter Hitech Pty Ltd A 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

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JP2021511464A (en) 2021-05-06
HUE054963T2 (en) 2021-10-28
US11401925B2 (en) 2022-08-02
EP3514381A1 (en) 2019-07-24
DK3728846T3 (en) 2021-07-12
JP6962648B2 (en) 2021-11-05
ES2881647T3 (en) 2021-11-30
WO2019145314A1 (en) 2019-08-01
US20210033085A1 (en) 2021-02-04
PT3728846T (en) 2021-07-14
SI3728846T1 (en) 2021-08-31
PL3728846T3 (en) 2021-11-15
EP3728846B1 (en) 2021-06-02

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