Patent Application
20210033085
The invention relates to a device for compressing a working medium having 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.
Such compressors are known in the prior art in various designs (cf. e.g. U.S. Pat. No. 4,104,008 A). U.S. Pat. No. 4,104,008 A discloses a compressed-air-operated hydraulic pump which comprises a working chamber and a pneumatic piston, wherein the pneumatic piston is connected to a hydraulic piston. With the aid of an auxiliary slider which is sealed with respect to the working chamber and a control slider, compressed air is conveyed to the pneumatic piston in order to move this against a spring force of a helical compression spring. Due to the movement of the pneumatic piston, the hydraulic piston is moved in a hydraulic cylinder onto which a valve housing is pushed, which is used for connection of hydraulic lines.
U.S. Pat. No. 5,324,175 A discloses a two-stage, pneumatically operated air-piston compressor which comprises 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 compression in the first stage of the compressor, the air to be compressed is guided through a heat exchanger before it is further compressed in the second stage.
DE 30 18 625 A1 and U.S. Pat. No. 6,386,841 B1 disclose various designs of compressors which, however, are not designed with a view to improving the efficiency of the compressor.
However, the high energy consumption of compressors having a gas drive proves to be disadvantageous.
Against this background, it is the object of the invention to increase the efficiency for 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.
The device according to the invention for compressing a working medium comprises at least the following components:
According to the invention, the heat exchanger is adapted for heat exchange between the working medium after compression in the second cylinder and the drive medium before entry into the first cylinder of the pressure translator. Advantageously the temperature of the drive medium in the compressed state can thus be increased before the drive piston is exposed to the drive medium in the compressed state. As a result, a higher working power is available for operation of the high-pressure piston so that the efficiency of the compressor can be increased.
This principle can be used in various types of compressors, in particular in a single- or double-acting, single-stage or two-stage compressor. The compressor as a piston compressor can also be designed as single- or double-acting, single-stage or two-stage.
For the purposes of this disclosure, the positional and directional information such as “before”, “after”, “between” etc. relates to the flow direction of the drive medium or the working medium in compressor operation.
In a preferred embodiment, a closed circuit for the drive medium with a first line from the compressor to the first cylinder and with a second line from the first cylinder to the compressor is provided. In the article by Andreas P. Weiss, “Higher energy efficiency—theoretical considerations on an ideal compressed air system with closed air circuit” (original German title: “Höhere Energieeffizienz—Theoretische Überlegungen zu einem idealen Druckluftsystem mit geschlossenem Luftkreislauf”, O+P 5/2009, it was shown in a different context that in a compressed air system with a compressed air cylinder, the configuration of a closed air circuit increases the energy efficiency compared with an open reference system without return of waste air.
The heat exchanger is preferably designed as a recuperator, wherein the compressed drive medium and the compressed working medium are separated from one another by means of at least one wall. In an alternative design, the heat exchanger is designed as a regenerator wherein heat storage is provided in a heat exchanger mass.
A plate heat exchanger or a tube-in-tube heat exchanger, for example, can be provided as heat exchanger. However, various designs of heat exchangers are known by means of which the heat content of the compressed working medium can be transferred to the compressed working medium.
In order to further reduce the required drive power, it is favourable if the compressor is designed to be fully hermetic or semi-hermetic.
For the purposes of this disclosure a “fully hermetic” compressor is understood as a design in which a preferably pressure-tight housing encloses both a drive motor and also a compressor unit, wherein the enclosing housing is in particular welded and the media lines are guided through the housing.
For the purposes of this disclosure a “semi-hermetic” compressor is understood as a design in which a drive motor is connected in a pressure-tight and detachable manner to a compressor housing.
In a further embodiment an open compressor is provided. For the purposes of this disclosure an “open” compressor is understood as a design in which a shaft journal or another load transfer means projects from at least one side of a compressor unit, by means of which working power can be introduced into the compressor unit.
According to a particularly preferred embodiment, the compressor and the closed circuit for the drive medium are adapted to guide the drive medium at pressure higher than ambient pressure in the circuit.
According to a preferred embodiment, a cooler for cooling the drive medium in the second line of the closed circuit is arranged between the first cylinder of the pressure translator and the compressor. In this 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 can be increased after compression by heat exchange with the compressed working medium without the temperature in the closed circuit as a whole being increased further and further. Advantageously therefore the working medium is guided in the closed circuit at different temperature stages in order to achieve an optimal efficiency during driving of the high-pressure piston.
In order to specifically reduce the temperature of the drive medium in the return line from the compressor to the suitable level, in a preferred embodiment there is further provided
In order to compensate for pressure peaks or pressure fluctuations, there is preferably provided a first buffer storage device between the compressor and the heat exchanger and/or a second buffer storage device between the cooler and the compressor.
According to a preferred embodiment, a control slider is provided between the compressor and the first cylinder which can be switched between a first position and a second position in order to move to and from the drive piston which seals a first volume of the first cylinder with respect to a second volume of the first cylinder by means of the drive medium. In the first position, the control slider 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 slider 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 method according to the invention for compressing a working medium comprises at least the following steps:
According to a particularly preferred embodiment, the method further comprises the step
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 higher than an ambient pressure.
The input pressure of the drive medium at the input 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 output of the compressor is preferably between 1 bar and 100 bar, in particular between 5 bar and 40 bar.
For the purposes of this disclosure, all the pressure values should be understood as absolute pressures.
In order to lower the temperature of the drive medium before the compressor, a cooling of the drive medium emerging from the first cylinder is preferably undertaken by means of a cooler.
The drive medium is preferably different from the working medium. According to a particularly preferred embodiment, the drive medium is gaseous, wherein preferably one of air, nitrogen, CO2, argon or krypton or a mixture thereof is provided as drive medium. The conventional compressors with gas drive have a high energy requirement in order to provide the required drive power for the drive of the high-pressure piston. As a result of 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 during operation of the drive piston can be increased substantially.
In a particularly preferred application, the working medium is gaseous, wherein preferably molecular hydrogen is provided as working medium. Preferably the pressure of the working medium is raised 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 each to be understood as absolute pressure.
The invention will be explained further hereinafter with reference to an exemplary embodiment shown in the drawing.
As is further apparent from the drawing, the compressed drive medium is used to drive a pressure translator 3. The pressure translator 3, also designated as pressure converter, comprises a drive piston 4 which is moved to and from within a first cylinder 5 between a first end position and a second end position. For the drive of the drive piston 4 the drive medium is guided 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 translator 3 additionally comprises a high-pressure piston 8 by means of which the working medium is compressed from an initial pressure to a final pressure. The high-pressure piston 8 is movable 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 manner that the movement of the drive piston 4 is transmitted to the high-pressure piston 8. In order to achieve a pressure translation 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 configured to be 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 supplied with an initial pressure via a first supply line 12 to the second cylinder 9 and via a second supply line 13 to the high-pressure cylinder 11. After the compression, the working medium at the final pressure is led off 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 combined in a common discharge line 16. In a single-acting design of the drive piston 4 (not shown) only a first discharge line 14 is provided.
As is further apparent from
As is apparent from
In the embodiment shown, a cooler 23 is additionally arranged in the second line 19 in order to achieve a cooling of the drive medium on the way from the first cylinder 5 of the pressure translator 3 back to the compressor 2. The cooler 23 can be configured as a further heat exchanger with a fan 23a. In the embodiment shown a temperature measuring element 26 is additionally provided in the second line 19 which transmits the temperature of the working medium to a control unit 27 which actuates the fan 23a depending on the temperature of the drive medium in the second line 19.
Furthermore, a first buffer storage device 24 is provided between the compressor 2 and the heat exchanger 22 and a second buffer storage device 25 is provided between the cooler 23 and the compressor 2.
For better clarity, only the components required to understand the embodiment shown are depicted in the drawing. Naturally, the compressor device 1 can have various additional components and modifications compared to the embodiment shown.
| Number | Date | Country | Kind |
|---|---|---|---|
| 18152933.0 | Jan 2018 | EP | regional |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2019/051537 | 1/23/2019 | WO | 00 |
