Patent Application
20210172428
The present application claims priority of German Application Number 10 2019 133 576.0 filed Dec. 9, 2019, the disclosure of which is hereby incorporated by reference herein in its entirety.
The disclosure relates to a compressor and to a method for conveying and compressing a fluid for conveyance into a target system using such a compressor.
Compressors increase the pressure of gaseous fluids in one or more stages and are designed inter alia as piston compressors. A piston compressor increases the pressure by reducing the working space. Compressors of said type are known in various embodiments, for example through the brochure “Kompressoren” [compressors], dated November 2007, of the company Maximator GmbH.
DE 10 2018 109 443 A1 discloses a compressor device and a compression method. The compression device has at least one compression space in respectively one compression cylinder for a gas. The at least one compression cylinder is separated spatially by a spacing from the at least two drive cylinders.
DE 1 025 093 A includes a locomotive braking air pump in an upright tandem arrangement that is driven by a piston steam engine without a flywheel.
A piston-type pneumatic circulating pump is described in CN 103062011 A.
The compressors are proven in operation. The compression is realized via the piston compressor principle, in the case of which the pressure transmission results from the ratio of the area of the drive piston to the area of the high-pressure piston. The high pressure is built up in one or more high-pressure cylinders. Movement of the high-pressure piston out of the pressure cylinder results in the formation of a negative pressure, and the suction valve allows fluid for conveyance to flow in. The fluid for conveyance is the gaseous fluid to be conveyed and compressed by the compressor, for example argon, helium, hydrogen or nitrogen. Movement of the high-pressure piston into the pressure cylinder results in the fluid for conveyance that has flowed in being compressed. The suction valve closes and the pressure valve opens.
The transmission ratio can be almost doubled by doubling the area of the drive surface. For this purpose, two drive pistons are installed, and a larger pressure can be generated. This is necessary if the drive pressure is nominally insufficient to generate the desired target pressure or end pressure based on the transmission ratio.
The design of the compressor is realized according to the maximum operating pressure. Here, use is often made of compressors having two drive parts, wherein the first drive part has a first drive piston which is movable in a first drive chamber, and the second drive part has a second drive piston which is movable in a second drive chamber. The first drive piston and the second drive piston are each able to be subjected to a drive fluid on alternate sides in a manner controlled via a control unit. The first drive piston, the second drive piston and the high-pressure piston are coupled and jointly movable via a piston rod arrangement.
During the compression, the maximum transmission ratio is required only in the last third of the pressure build-up. Nevertheless, both drive chambers are filled with drive fluid. There appears to be a need for improvement here from ecological and economic aspects.
Proceeding from the above, the disclosure includes an object of providing an operationally efficient compressor, for which the consumption of drive fluid is reduced while the power is maintained, and of specifying an effective and more cost-effective method for conveying and compressing a fluid for conveyance into a target system.
According to the disclosure, the second drive part is assigned a second control unit, which is arranged after the first control unit. Via the second control unit, the subjecting of the second drive piston to drive fluid is able to be activated, wherein the subjecting of the second drive piston to drive fluid is activatable in a manner dependent on an actual pressure in a target system on the high-pressure side of the at least one first high-pressure part.
The disclosure provides a double-stage piston compressor for which the previously high or increased consumption of drive fluid is reduced and the power of the double-stage piston compressor is nevertheless utilized. Double-stage means that the compressor has two drive parts having two drive pistons and has at least one high-pressure part. The compressor is a double-acting compressor which has two drive parts and two high-pressure parts, wherein the drive pistons of the two drive parts and the high-pressure pistons of the two high-pressure parts are jointly movable in a manner coupled via a piston rod arrangement.
Pilot valves are installed in the compressor arrangement. The pilot valves serve for end-position switchover by the drive pistons. The pilot valves are actuated in the end positions by the drive pistons and pass control pulses on to a control slide. The pilot valves thus aerate and de-aerate the actuation space of the control slide. In this way, the control slide is pushed from one end position into the other end position.
The control slide is a constituent part of the first control unit. The control slide is an internally actuated four/two-way valve. The control slide serves for alternate subjecting of the top side and bottom side of the drive pistons to drive fluid. This is generally compressed air. The actuation of the control slide is realized via the pilot valves and ensures that the drive medium or the drive air passes to the respectively opposite side of the drive piston.
The drive parts serve for receiving the drive medium and actuate the high-pressure piston(s) of the compressor via a piston rod and, in this way, compress the respective fluid for conveyance to a higher pressure.
The high-pressure part(s) of the compressor is/are respectively assigned a compressor head, which has inlet and outlet valves. The compressor head closes off the compression space, that is to say the pressure cylinder of the high-pressure part, and separates the compression space spatially from the ambient pressure. The compressor head contains the inlet and outlet valves. By way of said inlet and outlet valves, the fluid for conveyance to be compressed passes into the compression space of the compressor and out of the compression space again.
The high-pressure part(s) of the compressor serves/serve for compression of the respective fluid for conveyance. The high-pressure part is made substantially of the pressure cylinder, the compressor head, which has inlet and outlet valves, and the high-pressure piston, which has sealing and guide elements.
The provision of a supply to the second drive part is activatable and deactivatable via a switching logic. The disclosure incorporates the finding that, over two thirds of the filling and compression process, there is no need for both drive chambers for the conveyance and compression of the fluid for conveyance. The second drive part is activated and the second drive piston is subjected to drive fluid only from a specific actual pressure in the target system on the high-pressure side. This is generally first used in the last third of the compression process, in order to build up or to obtain the desired end pressure. The switchover is realized in a manner dependent on the pressure. The occurrence of force equilibrium between the drive pressure and end pressure results in the second drive piston in the second drive part being additionally activated, and the compressor is able to continue to compress the fluid for conveyance until attainment of the target pressure.
In order to control the provision of a supply to the second drive chamber, the continuous connection of the two drive chambers is interrupted. The compressor is firstly operated only with one drive chamber in a first compression stage. The second drive chamber is activated according to requirement. For this purpose, the second control unit is arranged after the first control unit.
The first control unit and the second control unit are integrated into a control mechanism which controls the system or the compressor and the method in such a way that all the operations are performed in chronological and logical order.
In terms of practical use, the second control unit has two three-way valves.
One aspect of the disclosure provides that each three-way valve has an outlet and a sound damper arranged thereafter. The sound dampers serve for noise-reduced discharge of the expanding drive medium from the compressor. After use, the drive medium exits the compressor via the sound dampers. By way of the additional sound dampers, which are arranged after the two three-way valves, sound damping is realized in both compression stages of the compressor.
The compressor according to the disclosure has two drive parts. These are normally driven by compressed air. The compressor has a wide variety of applications, such as filling processes, testing processes, decanting processes or else emptying processes.
The implementation of the switching logic provided according to the disclosure may be realized manually, pneumatically or electrically.
For manual actuation of the second control unit, manual valves are installed. For the compression process, this means that the compressor runs with the first drive piston until the drive piston stops on account of force equilibrium on the drive side and the high-pressure side (standstill pressure). Then, for example by means of a ball valve, there is a switchover to the two-piston drive, that is to say, in addition to the first drive piston, the second drive chamber and the second drive piston arranged therein are subjected to drive fluid.
For the pneumatic actuation of the second control unit, this has pneumatically actuatable valves. These may be actuated via pressure switches, so that a switchover between the one-piston drive and the two-piston drive is possible according to operating pressure.
For electrical actuation of the second control unit, electrically actuatable valves are installed. These may also be retrofitted in existing programmable logic controllers. The system comprises integrated pressure transducers, whose information is used to switch between one-piston drive and two-piston drive with memory-programmable control. In the programmable logic controller, switchover pressures are stored, and there is a switch to the efficient mode via solenoid valves of the compressor.
A method according to the disclosure for conveying and compressing a fluid for conveyance into a target system uses a compressor according to the disclosure. The supply of drive fluid to the individual drive chambers or to the drive pistons arranged there is activated or deactivated via the switching logic provided according to the disclosure. In a first compression stage, the first drive piston of the first drive part is subjected to drive fluid and fluid for conveyance is conveyed into the target system until the occurrence of force equilibrium on the drive side and the high-pressure side. Then, in a second compression stage, the second drive part is activated and, in addition to the first drive piston, the second drive piston is subjected to drive fluid and fluid for conveyance is conveyed into the target system until attainment of a target pressure or the desired end pressure.
The conveyance and compression of a fluid for conveyance into a target system may involve for example a process of decanting or introducing a gaseous fluid into a container, for example into a pressurized-gas vessel. The conveyance and compression of the fluid may however also involve the provision of a supply to gas internal pressure systems or test and control units for compressed air and gases, as well as systems for filling of airbag gas containers. A target system may also be a test stand for pressure tests.
The disclosure uses the drive of the compressor via a drive piston during approximately two thirds of a decanting or filling process. This is the first compression stage. In the second compression stage, use is made of all the drive pistons, both the one in the first drive part and the one in the second drive part, specifically for the remaining part of the decanting or filling process, that is to say the conveyance and compression of the fluid for conveyance into a target system according to the target pressure and the target quantity for conveyance. In this way, the relatively high costs for the drive fluid and also the high consumption of drive fluid are reduced. Air or compressed air are used as drive fluid. The consumption of drive fluid can be reduced by up to 40%. Also a reduction in the filling time for the conveyance and compression of the fluid for conveyance into the target system can be reduced by up to 20%. Also, existing compressors can, with little outlay, be converted or retrofitted and equipped according to the disclosure. As a result of the reduction in the consumption of drive fluid as well as the reduction in process times, the operating costs can be lowered and both economic and ecological advantages are obtained.
The disclosure is described in more detail below on the basis of drawings. In the drawings:
The figures use the same reference numerals for identical or similar components, even when there is no repeated description on grounds of simplification.
The compressor 1 has a first drive part 6 and a second drive part 7 and also a high-pressure part 8.
The compressor 1 works according to the principle of a pressure transmitter. Further details of a compressor 1 are explained on the basis of
The compressor 1 as per
The first drive piston 11 and the second drive piston 13 and also the two high-pressure pistons 15 and 17 are jointly movable in an axial direction in a manner coupled via a piston rod arrangement 18. The piston rod arrangement 18 comprises piston rods 19, 20 and 21. The piston rod 19 is incorporated between the first drive piston 11 and the second drive piston 13. The piston rod 20 connects the first drive piston 11 and the first high-pressure piston 15. The piston rod 21 connects the second drive piston 13 and the second high-pressure piston 17. The piston rods 19, 20, 21 of the piston rod arrangement 18 extend in alignment along a common longitudinal axis LA.
The first drive chamber 10 and the second drive chamber 12 are separated by a central wall 22. The two high-pressure parts 8 and 9 are respectively flange-mounted onto the end walls 23 and 24 of the first drive part 6 and second drive part 7. The piston rod 19 passes through an opening 25 in the central wall 22 and is guided there. The piston rods 20, 21 respectively pass through openings 26 and 27 in the end walls 23 and 24.
The high-pressure parts 8 and 9 or the pressure cylinders 14, 16 thereof have, respectively at an end side, a compressor head 28, 29, which is merely indicated in the illustration in
The first drive piston 11 and the second drive piston 13 are each able to be subjected to drive fluid AF on alternate sides in a manner controlled via a first control unit 32. The control unit 32 comprises a control slide in the form of a four/two-way valve 33. The feeding of drive fluid AF at an operating pressure pL is realized via a connection 34. The discharge of expanded working fluid AF is realized via an outlet 35 and a sound damper 36 arranged thereafter.
A second control unit 37 is assigned to the second drive part 7. The second control unit 37 is arranged after the first control unit 32. The subjecting of the second drive chamber 12 and the second drive piston 13 to drive fluid AF is able to be activated or deactivated via the second control unit 37. The second control unit 37 is designed to interrupt or to activate the supply of drive fluid AF to the second drive chamber 12 separately in a controlled manner. In this way, the compressor 1 can be operated with only the first drive chamber 10. The second drive chamber 12 is additionally activated according to requirement. The subjecting of the second drive piston 13 to drive fluid AF is activatable in a manner dependent on an actual pressure pBactual in the target system 2 on the high-pressure side HS of the high-pressure part(s) 8, 9.
The second control unit 37 has two three-way valves 38, 39. The three-way valves 38, 39 each have an outlet 40 with a sound damper 41 integrated or arranged thereafter.
The control slide or the four/two-way valve 33 of the first control unit 32 is, via a line path 42, connected to that part of the first drive chamber 10 which is at the top side 43, facing the first high-pressure piston 15, of the first drive piston 11. A line path 44 connects the four/two-way valve 33 to that part of the first drive chamber 10 which is at the bottom side 45 of the first drive piston 11. The first three-way valve 38 is connected to the line path 42 via a line path 46, and, via a line path 47, is connected to that part of the second drive chamber 12 which is at the bottom side 48 of the second drive piston 13. The second three-way valve 39 is connected to the line path 44 via a line path 49, and, via a line path 50, is connected to that part of the second drive chamber 12 which is at the top side 51 of the second drive piston 13.
In a first compression stage, the compressor 1 is run in one-piston mode. This means that the first drive chamber 10 and the first drive piston 11 of the first drive part 6 are subjected to drive fluid AF.
The control slide or the four/two-way valve 33 guides the drive fluid AF to the top side 43 and to the bottom side 45 of the first drive piston 11 in an alternating manner. The drive fluid AF flows from the connection 34 at the drive pressure pL through the four/two-way valve 33 and to the top side 43 of the first drive piston 11 according to the arrows P1, P2. The four/two-way valve 33 is in the switching position illustrated in
The feeding of fluid for conveyance FF via the inlet valves 30 is respectively indicated by the arrows IN in
Via the line path 44, air can be discharged from the first drive chamber 10 via the four/two-way valve 33 and the outlet 35 with sound damper 36 arranged thereafter according to the arrows P3. The two three-way valves 38, 39 are open toward the outlet 40, and so, during the movement of the first drive piston 11 and the second drive piston 13, air can be discharged from the second drive chamber 12 and the three-way valves 38, 39 according to the arrows P4.
If the first drive piston 11 has moved to the right to an end position of the first drive piston 11 in the first drive chamber 10, a pilot valve (not illustrated here) opens. The pilot valve belongs to the first control unit 32. Drive fluid AF passes to the control slide of the control unit 32, and the four/two-way valve 33 is switched into the opposite switching position (
Drive fluid AF then flows to the bottom side 45 of the first drive piston 11 according to the arrows P5, P6. The drive piston 11, as well as the second drive piston 13 and the first high-pressure piston 15 and the second high-pressure piston 17, moves to the left in the plane of the figure in
During the movement of the first drive piston 11 to the left, air situated in the first drive chamber 10 can escape via the four/two-way valve 33 and the outlet 35 and the sound damper 36 according to the arrows P7. The second drive chamber 12 is aerated via the three-way valves 38, 39, with the result that air can escape according to the arrows P8.
In this way, fluid for conveyance FF is conveyed from the source system 3 until the occurrence of force equilibrium on the drive side and the high-pressure side HS. The compressor 1 is consequently operated via the first drive part 6 and the first drive piston 11 over two thirds of the filling process. Only in the last third of the conveyance and compression process is the total force of the two drive pistons 11 and 13 required. The second drive part 7 is activated, and the second drive piston 13 is additionally subjected to drive fluid AF, in a manner dependent on the actual pressure pBactual resulting from force equilibrium on the drive side and on the high-pressure side HS. The compressor 1 then runs in two-piston mode and conveys and compresses fluid for conveyance FF into the target system 2 until attainment of the target pressure pZ.
As can be seen in
After the end position is reached, the system in turn effects a reversal. Both the first control unit 32 and the second control unit 37 perform a switchover, and working fluid AF can, as illustrated in
In the first compression stage, the compressor 1 is operated only via the first drive part 6. In this way, the consumption of drive fluid AF can be reduced. Only in the second compression stage is the second drive part 7 activated, in order to obtain the desired end pressure or target pressure pZ during the compression process. The switchover is realized in a manner dependent on an actual pressure pBactual on the high-pressure side HS. A very high potential for reduction of the consumption costs for drive fluid AF and also in the filling time is possible, such as in the case of a large container volume and low entry pressures. By changing the activation pressure, that is to say the pressure at which the second drive part 7 is activated, with conditions otherwise the same, priority can be given, in a range, to the filling time or the consumption costs for drive fluid AF.
The foregoing description of some embodiments of the disclosure has been presented for purposes of illustration and description. The description is not intended to be exhaustive or to limit the disclosure to the precise form disclosed, and modifications and variations are possible in light of the above teachings. The specifically described embodiments explain the principles and practical applications to enable one ordinarily skilled in the art to utilize various embodiments and with various modifications as are suited to the particular use contemplated. It should be understood that various changes, substitutions and alterations can be made hereto without departing from the spirit and scope of the disclosure.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2019 133 576.0 | Dec 2019 | DE | national |
