EP3619064A1 - Verfahren zum betreiben einer druckregelanlage mit einem mehrstufigen kompressor, sowie druckregelanlage - Google Patents
Verfahren zum betreiben einer druckregelanlage mit einem mehrstufigen kompressor, sowie druckregelanlageInfo
- Publication number
- EP3619064A1 EP3619064A1 EP18719486.5A EP18719486A EP3619064A1 EP 3619064 A1 EP3619064 A1 EP 3619064A1 EP 18719486 A EP18719486 A EP 18719486A EP 3619064 A1 EP3619064 A1 EP 3619064A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- pressure medium
- compression stage
- compression
- compressed
- 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.)
- Withdrawn
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/052—Pneumatic spring characteristics
- B60G17/0523—Regulating distributors or valves for pneumatic springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
- B60G17/0155—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit pneumatic unit
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/052—Pneumatic spring characteristics
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/052—Pneumatic spring characteristics
- B60G17/0523—Regulating distributors or valves for pneumatic springs
- B60G17/0528—Pressure regulating or air filling valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/056—Regulating distributors or valves for hydropneumatic systems
-
- 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
- F04B25/00—Multi-stage 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
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/02—Stopping, starting, unloading or idling control
- F04B49/03—Stopping, starting, unloading or idling control by means of valves
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/152—Pneumatic spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/154—Fluid spring with an accumulator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/20—Spring action or springs
- B60G2500/204—Pressure regulating valves for air-springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/20—Spring action or springs
- B60G2500/205—Air-compressor operation
Definitions
- the invention relates to a method for operating a pressure control system with a multi-stage compressor, in particular in a commercial vehicle, and a pressure control system with a multi-stage compressor.
- Multi-stage compressors are used to achieve a high compression of a pressure medium, in particular a gas, for example air, characterized in that the pre-compressed in a first compression stage pressure medium is additionally compressed in a subsequent second compression stage.
- a pressure medium in particular a gas, for example air
- such a multi-stage compressor can be used to provide the pressure medium with a corresponding pressure for supplying pressure springs.
- the multistage compressor compresses the introduced into a suction pressure medium from the atmosphere via two or more compression stages and transferred the multi-stage compressed pressure fluid to the springs.
- an already compressed pressure medium from a pressure medium supply can be used, which is compressed by the compressor once more.
- DE 103 21 771 A1 describes a multi-stage compressor in which a bypass line with a pneumatically controllable check valve is provided for switching off the first compression stage, which connects a suction chamber of the compressor with the first compression chamber.
- the pneumatic check valve is opened in dependence on the pressure in the suction, so that a pressure equalization between the suction and the compression chamber can take place. This serves to switch off the first compression stage as a function of the pressure of the pressure medium introduced into the suction space.
- high compression at a low volume flow can be achieved depending on the admitted pressure medium in single-stage operation.
- two-stage operation however, a high volume flow is achieved and the pressure medium flows through two compression stages.
- DE 10 201 1 083 614 A1 it is provided to compress air in an open operating mode by two compression stages and to supply the compressed air to a pressure medium reservoir.
- a closed mode of operation the already compressed air from the pressure fluid supply can be introduced into an intermediate volume between the first and the second compression stage and be recompressed by one of the compression stages in order to subsequently reach the consumers.
- Continue is also a return of air from the consumers provided in the pressure medium supply.
- electrically operated switching valves are provided, which lock and release the flow paths for the compressed or the air to be compressed accordingly.
- DE 10 2012 010 390 A1 describes a level control system in which, in a closed operating mode, already compressed air from a pressure reservoir is fed into consumers designed as struts via a compressor.
- a pressure limiting function is provided, which is designed either in the form of a drain valve or in the form of a pilot valve, which in each case discharge air into the atmosphere at a high pressure in the system.
- a compression capacity of a first compression stage of a multi-stage compressor is reduced or limited by a pressure relief valve.
- the pressure relief valve self-regulating an intermediate pressure of a pre-compressed pressure medium conveyed by the first compression stage limited, so that the first compression stage contributes to a total compression capacity of the multi-stage compressor, especially in the closed mode only to a limited extent, and thus the proportion of the first compression stage in the energy consumption of the multi-stage compressor in the closed mode can be reduced or limited.
- the advantage can already be achieved that the compression capacity of the first compression stage when switching to the closed operating mode of the pressure control system, which is operated with the multi-stage compressor, can be adjusted in a simple and reliable self-regulating or automatic, if that in the first Compression stage precompressed pressure medium reaches a certain limit pressure, since the pressure relief valve then opens automatically.
- no control of additional valves by a pneumatic or an electronics is required.
- the first compression stage here is not necessarily meant to be the compression stage initially located in the multi-stage compressor in the flow direction. Rather, it is understood that the first compression stage may be any compression stage in the multi-stage compressor, followed by at least one additional compression stage - a second compression stage -, which does not necessarily adjacent to the first compression stage in the context of the invention.
- the second compression stage is thus only in the flow direction behind the first compression stage, wherein the second compression stage is not necessarily to be regarded as the last compression stage of the multi-stage compressor.
- the pressure relief valve as a differential pressure valve, preferably as a check valve, in particular as a ball check valve with a by a spring force against a constriction pushing ball executed, which opens from a dependent on the spring force limit pressure.
- a differential pressure valve preferably as a check valve, in particular as a ball check valve with a by a spring force against a constriction pushing ball executed, which opens from a dependent on the spring force limit pressure.
- an open mode of operation of the pressure control system of the multi-stage compressor pressure medium for example, provided via a suction intake air from the atmosphere, precompressed by the first compression stage, for example, to an intermediate pressure of 5-6bar at a stabilizing pressure of the first compression stage, for example 10-15bar, and introduced into an intermediate volume. From there, the precompressed air passes into a second compression stage, in which it is further compressed, for example, to a final pressure of 20 bar, and from which it passes through an air dryer in one or more consumers, such as air springs of the pressure control system, and / or in a pressure medium supply ,
- the overall compaction performance in the open mode of operation is determined in particular by these two compression stages, wherein as already stated, further compression stages may be present.
- the closed operating mode is set in particular when a supply to the load of the pressure control system with high-pressure and / or dried pressure medium is to take place. This is particularly the case when a rapid pressurization of the consumer is desired, for example, when a fast control by providing a high end flow rate, ie a high amount of air per time from the second or last compression stage, by the air spring control is required .
- the closed operating mode can be set when a recovery of pressure medium should be made from the consumers in the pressure medium supply, since then a renewed compression is to ensure.
- a switching valve for example, which connects the pressure medium supply or the consumers to the storage line, is opened so that already compressed pressure medium, referred to below as charge pressure medium, can flow into the storage line.
- the supercharging pressure medium can be the pressure medium stored in the pressure medium reservoir, which has already been compressed to a supply pressure. If, however, in the closed operating mode, a recovery of already compressed pressure medium from the consumers into the pressure medium reservoir takes place, then the pressure medium from the consumers is the supercharging pressure medium, which is introduced into the storage line.
- two separate switching valves can be provided for the consumers and the pressure medium supply, which control the inflow into the storage line.
- the supercharging pressure medium reaches the intermediate volume between the first and the second compression stage via the storage line.
- the intermediate volume thus there is a pressure which is slightly lower than the supply pressure in the pressure medium supply or the pressure in the consumers, since the pressures drop by the passage of the switching valve and the storage line.
- the already highly compressed supercharging pressure medium can thus be additionally compressed by the second compression stage.
- a storage volume flow of the charge line, already compressed in the storage line, ie an amount of air per time into the intermediate volume, is in this case dependent in particular on a nominal diameter of the switching valve and possibly further upstream valves through which the supercharging pressure flows.
- the storage volume flow in turn determines also the end volume flow of the pressure medium conveyed through the second or last compression stage.
- this energy transfer can be up to an acceptable maximum energy limit, in particular a current limit of, for example, 35 A for operating the second compression stage additionally used.
- a current limit of, for example, 35 A for operating the second compression stage additionally used.
- the nominal diameter of the switching valve and thus the storage volume flow can be designed higher without exceeding the acceptable maximum energy limit. Consequently, an active power of the pressure control system increases, since at the same acceptable electric power, a significantly increased end flow rate can be ensured by the second compression stage with the same energy use.
- the first compression stage attempts to provide a pre-compressed pressure medium, which is compressed to the supercharging pressure of the supercharging pressure medium, which then prevails in the intermediate volume.
- the pressure relief valve opens as soon as the intermediate pressure of the pre-compressed pressure medium is greater than the limiting pressure, wherein the pre-compressed pressure medium is discharged in this case via a vent line outgoing from the pressure relief valve into the atmosphere or into the suction line. If the venting creates an intermediate pressure that is less than the limit pressure, it closes the pressure relief valve again.
- the first compression stage thus only promotes up to the limit pressure in the intermediate volume.
- the intermediate volume In the intermediate volume is thus in the closed operating mode, a mixture of the pre-compressed from the first compression stage pressure means and the respective supercharging pressure from the storage line. As a result, a mixing pressure medium with a mix volume flow and a mixing pressure, which are composed of the respective volume flows or pressures, is conveyed from the intermediate volume into the second compression stage.
- the mixing pressure medium In the open operating mode, the mixing pressure medium consists only of the pressure medium pre-compressed by the first compression stage, since no charge pressure medium is introduced into the intermediate volume.
- a power consumption of the first compression stage can be limited, since the first compression stage compacts only until reaching the limit pressure and performs compaction work.
- the drive power of an engine of the compressor is thus automatically reduced or limited, the energy requirement decreases and can thus be tuned in the closed mode mainly to the operation of the second or further compression stages and thus the final flow rate.
- the main part of the total compression capacity is achieved in the closed mode of operation by a compression of the recirculated from the storage line in the intermediate volume and not funded by the first compression stage supercharging pressure.
- the pre-compressed pressure medium thus contributes only a small part of this maximum pressure to the limiting pressure.
- An inflow of the supercharging pressure medium from the intermediate volume back into the first compression stage is prevented by a first outlet valve in the first compression stage, for example a check valve opening to the intermediate volume.
- the consumers can be supplied with a pressure medium which has reached a high drying stage, since the proportion of non-dried pressure medium, which is conveyed essentially from the first compression stage and thus from the environment, is limited.
- the limiting pressure is set in such a way or the multi-stage compressor designed such that no performance loss occurs in the open operating mode by the limit pressure is adjusted to the pressure required in the intermediate volume in the open mode. This is the case, for example, at a limit pressure of 5 bar, which is necessary for a final pressure of 20 bar in the open operating mode, in particular to comply with energy requirements, such as a current limit of 35A, and a fixed end flow rate of the compressed pressure medium.
- the supercharging pressure medium is not introduced into the multi-stage compressor through the first compression stage, a simple structure and reliable operation of the pressure regulator can be achieved because the uncompressed pressure medium in the open mode and the supercharged pressure medium in the closed mode at different locations in the multi-stage compressor are introduced and thus no switching of the pressure medium source in the first compression stage is necessary.
- a simple and cost-effective design of the pressure control system can be realized, with which the efficiency of the compressor can be optimally tuned, d. H. a high storage volume flow by increasing the nominal diameter, in particular of the switching valve with a simultaneously definable maximum energy consumption and an at least partially dried pressure medium.
- the optimal operation of the pressure control system is thus achieved for the closed operating mode by an optimally designed second compression stage, which is defined by the maximum storage volume flow, which is defined in particular by the nominal size of the switching valve and the reduced first compression stage to the power limit of the multi-stage compressor or upper energy limit is filled.
- an additional pressure relief valve may be provided in the storage line, which sets a maximum supercharging pressure in the storage line, the maximum supercharging pressure depending on the maximum energy limit can be selected so that the second compression stage is not operated above its performance limit.
- the structure of the second compression stage of the multi-stage compressor can be adjusted by, for example, designed a larger piston, which provides for the compression in the second compression stage.
- the vote of the predetermined by the pressure relief valve limit pressure can be carried out in particular as a function of a predetermined energy consumption of the pressure control system.
- a predetermined upper energy limit can be provided, for example an upper current limit to which the total compaction power of the multi-stage compressor is adjusted.
- the pressure relief valve or the limit pressure is determined in such a way that the first compression stage is used for compression until the specified upper energy limit for the compressor is reached. In order not to exceed this, the pressure relief valve opens, so that the power consumption of the first compression stage does not increase any further and the power consumption is kept within the limits.
- the final volume flow and the total compression capacity can be optimally matched to one another while maintaining the energy specifications in the closed operating mode.
- the multi-stage compressor is designed as a piston compressor, wherein a first piston is formed by a first compression stage and a second piston, the second compression stage, which are interconnected by the intermediate volume, wherein further compression stages can be present with other pistons. Both pistons are moved by a motor via a piston drive to successively compress the pressure medium in the corresponding compression space.
- the pistons have different piston diameters in order to be able to achieve a pre-compression through the first compression stage and an additional compression through the second compression stage and, if necessary, further compression by further compression.
- the reciprocating compressor is part of a pressure control system, which supplies compressed air via a compression of air as a pressure means to achieve, for example, a suspension or lifting and lowering of a part of the vehicle, this can take place in a closed or an open mode of operation.
- the pressure relief valve and the associated transmission lines for tuning the compressor in the closed operating mode to save space in a compressor housing, for example in a compressor cover, to be installed.
- space and weight can be saved and also a simple structure with low pneumatic transmission paths and thus few pressure losses can be achieved.
- advantageously easy retrofitting of the additional pneumatic components in an existing multi-stage compressor is possible.
- Fig. 1 is an air spring system with a two-stage compressor
- FIG. 2 shows a two-stage compressor with an integrated pressure relief valve.
- Fig. 3 is a flowchart for carrying out the inventive
- a pressure control system such as an air spring system 1 which has four pressure medium chambers 3.1, 3.2, 3.3, 3.4, each associated with a consumer, such as air springs of a vehicle 200.
- the pressure medium chambers 3.i are supplied with a compressed pressure medium L3, for example air, wherein the compressed pressure medium L3 is compressed in a two-stage compressor 4, for example a piston compressor shown in FIG.
- the two-stage compressor 4 has a first compression stage 5 and a second compression stage 6, each having a suction chamber 5.1, 6.1 and a compression chamber 5.2, 6.2, wherein the pressure medium L1, L2 flowing into the respective suction chamber 5.1, 6.1 in the compression chamber 5.2 , 6.2 is compressed.
- the compaction stages are driven fen 5, 6 by a motor 7, which causes a located in the respective compression stage 5, 6 piston 8, 9 moves up and down and thereby the pressure in the suction chamber 5.1, 6.1 provided pressure medium L1 is compressed accordingly.
- the pressure control system 1 can be operated in two operating modes, an open operating mode BMo (open mode) and a closed operating mode BMc (closed mode), in each of which air is conveyed and compressed as pressure means L1, L2, L3, L4, L5 ,
- intake air L1 is exhausted from the atmosphere 100, i. H.
- an air pressure or suction pressure p1 of about 1 bar, via a suction line 10 and a first inlet valve 1 1 in the first suction 5.1 of the first compression stage 5 introduced.
- the intake air L1 is first precompressed via the first piston 8 and thereby passed into the first compression chamber 5.2.
- the precompressed air L2 flows at an intermediate pressure p2 via a first outlet valve 12, for example a check valve, into an intermediate volume 13.
- the precompressed air L2 passes via a second inlet valve 14 into the second suction chamber 6.1 of the second compression stage 6, from which the precompressed air L2 is further compressed via a second piston 9 (see Fig. 2) and into the second compression chamber 6.2 is initiated.
- the compressed air L3 arrives at a final pressure p3 via a second outlet valve 15 into an outlet line 16 to an air dryer 17 and a nozzle 18.
- the outlet line 16 then leads the compressed air L3 to the pressure medium chambers 3.1, 3.2, 3.3, 3.4 of the connected consumers, for example the air springs, as well as via a supply line 19 to a pressure medium supply 20, in which the compressed air L3 stored air L4 with a supply pressure p4, which is slightly lower than the final pressure p3 due to losses, is stored.
- the pressure medium supply 20 and the pressure medium chambers 3.1, 3.2, 3.3, 3.4 are each by a controllable valve 21 .1, 21 .2, 21 .3, 21 .4, 21 .5, 21 .6, for example, a 2/2-way solenoid valve , connected to the outlet line 1 6 and the supply line 19, so that depending on the position of the controllable valves 21 .i the compressed air L3 in the pressure medium chambers 3.1, 3.2, 3.3, 3.4 for controlling the consumer or in the pressure medium supply 20 can flow.
- a controllable valve 21 .1, 21 .2, 21 .3, 21 .4, 21 .5, 21 .6, for example, a 2/2-way solenoid valve connected to the outlet line 1 6 and the supply line 19, so that depending on the position of the controllable valves 21 .i the compressed air L3 in the pressure medium chambers 3.1, 3.2, 3.3, 3.4 for controlling the consumer or in the pressure medium supply 20 can flow.
- the compressed air L3 is introduced into the first pressure medium chamber 3.1, with the second valve 21 .2 into the second pressure medium chamber 3.2, with the third valve 21 .3 open into the third pressure medium chamber 3.3 and when the fourth valve 21 open .4 In the fourth pressure medium chamber 3.4 passed, in which case the fifth valve 21 .5 is closed and thus no compressed air L3 can flow into the pressure medium reservoir 20.
- valves 21 .1, 21 .2, 21 .3, 21 .4, 21 .6 are in the closed position and the fifth valve 21 .5 is open, air L 3 drilled and compressed in the air dryer 17 can be opened Pressure fluid supply 20 introduced and stored therein. Pressure monitoring can take place via a pressure gauge 30. Via an additional discharge valve 31, the compressed air L3 can be discharged into the atmosphere 100.
- the stored in the pressure medium supply 20 air L4 can be admitted in the closed mode BMc as Aufladetikstoff A in the intermediate volume 13, so that the already compressed air L4 is compressed one more time.
- the fifth valve 21 .5 is closed and a first switching valve 22 a is opened, which is connected in a - L is the fifth valve 21 .5 and the pressure medium supply 20 branching storage line 23 is arranged.
- the storage line 23 is connected to the intermediate volume 13, so that in the open position of the first switching valve 22a, the stored air L4 can flow as Aufladetikstoff A in the intermediate volume 13 and in the second suction 6.1 to be recompressed by the second compression stage 6 again , An inflow of the stored air L4 in the first compression stage 5 is prevented by the first exhaust valve 12, which closes in this direction.
- the first switching valve 22a is in this case also closed and the fifth valve 21 .5 open to allow a return to the pressure medium reservoir 20. If only a compression of stored air L4 is provided in the pressure control system 1, the path via the second switching valve 22b can also be omitted.
- a nominal diameter NW of the switching valves 22a, 22b is selected here, for example, between 1 mm and 4 mm, so that a high storage volume flow QS can be set in the intermediate volume 13.
- a vent line 25 branches off between the first outlet valve 12 and the first compression chamber 5.2, which discharges either into the suction line 10 or into the atmosphere 100.
- the pressure relief valve 26 for example, a check valve, which opens from a limiting pressure pG, arranged.
- the pressure relief valve 26 is controlled as a function of the intermediate pressure p2 of the precompressed in the first compression stage 5 pressure medium L2.
- the compression capacity of the first compression stage 5 is automatically restricted via the overpressure valve 26 in that a delivery of precompressed pressure medium L2 is limited to the limit pressure pG.
- the precompressed air L2 present in the first compression space 5.2 is at least partially returned to the intake line 10 or optionally into the atmosphere 100 from the limit pressure pG, so that less precompressed air L2 is conveyed through the first outlet valve 12 into the intermediate volume 13.
- a compression thus takes place mainly via the second compression stage 6, in order to supply the pressure medium chambers 3.i with air or to achieve a recovery in the pressure fluid supply 20.
- the pressure relief valve 26 is preferably designed as a differential pressure valve, in particular a ball check valve with a spring, wherein the Spring presses a ball against a valve opening. As soon as the pressure in the vent line 25 is higher than the limit pressure pG, the ball releases the valve opening, so that precompressed air L2 can flow through the overpressure valve 26 and thereby a pressure limitation of the first compression stage 5 can be achieved.
- a power limitation can be achieved with which the energy requirement of the compressor 4 can be adjusted or minimized since pre-compression of the intake air L1 to the supercharging pressure pA prevailing in the intermediate volume 13 is not necessary.
- the required power consumption of the motor 7 of the compressor 4 is thus limited because the first piston 8 has less compaction work to do.
- the required power consumption of the motor 7 of the compressor 4 is thus limited because the first piston 8 has less compaction work to do.
- This can be used to optimize the second compression stage 6, so that an optimal adjustment in particular of an end volume flow QE of the second compression stage 6 and a piston diameter D2 of the second compression stage 6 can take place. This can be achieved, in particular, by using a nominal width NW of, for example, 1 mm for the switching valves 22a, 22b, so that the storage volume flow QS is increased into the intermediate volume 13 and thus also the final volume flow QE increases.
- BMc In closed mode BMc is located in the intermediate volume 13 a mix pressure L6, in which the proportion of the supercharging pressure A and the pre-compressed pressure fluid L2 are present with a maximum of the limit pressure pG.
- the mixing pressure medium L6 is conveyed into the second compression stage 6 with a mixing pressure p6 and a mixed volume flow QM, which are given by the respective pressures or volume flows of the supercharging pressure medium A and the precompressed pressure medium L2.
- the open mode BMo only the pre-compressed air L2 is promoted with the intermediate pressure p2 through the intermediate volume 13 in the second compression stage 6, without causing a mixture with the supercharging pressure A.
- the mixing pressure medium L6 thus consists exclusively of the precompressed air L2 with the intermediate pressure p2, which corresponds at most to the limiting pressure pG.
- the multi-stage piston compressor 4 with the first and the second compression stage 5, 6 is shown in a schematic view.
- the two compression stages 5, 6 are connected to each other via the intermediate volume 13, so that in the first compression stage 5 precompressed by the first piston 8 air L2 can be promoted in the second compression stage 6 in particular in the open mode BMo to there from the second piston. 9 to be condensed further.
- the supercharging pressure A is directed into the intermediate volume 13 via the storage line 23.
- the pressure relief valve 26, the storage line 23 and the vent line 25 can be arranged to save space, for example, in the compressor cover 28 of the compressor housing 29.
- the method according to the invention for operating the air suspension system in the closed operating mode BMc can be carried out as follows:
- the supercharging pressure A is released in a first step St1 .1 via the respective switching valve 22a, 22b and via the storage line 23 into the intermediate volume 13, from which it is compressed again via the second compression stage 6. Via the outlet valve 12, an inflow into the first compression stage 5 is prevented.
- a second step St1 .2 the compressor 4 compresses intake air L1 via the first compression stage 5, which is then further compressed by the second compression stage 6 via the intermediate volume 13 together with the supercharging pressure A (see step St1 .1) Mixture (Mix réellestoff L6) of precompressed air L2 and supercharging A is promoted.
- the overpressure valve 26 opens in a third step St1 .3, so that the pressure medium L2 precompressed by the first compression stage 5 is proportionally discharged into the intake line 10 or the atmosphere 100. The other part of the precompressed air L2 continues to reach the intermediate volume 13.
- the intake air L1 from the atmosphere 100 enters the first compression stage 5 in a step St2.1.
- the intake air L1 is precompressed to the intermediate pressure p2 in a second step St2.2 and in a third step St2.3 embedded in the intermediate volume 13.
- the precompressed pressure medium L2 passes into the second compression stage 6, in which in a fourth step St2.4 a renewed compression to the final pressure p3 takes place.
- the compressed pressure medium L3 enters the pressure medium chambers 3.i or the pressure medium reservoir 20.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Vehicle Body Suspensions (AREA)
- Supercharger (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017004359.0A DE102017004359A1 (de) | 2017-05-05 | 2017-05-05 | Verfahren zum Betreiben einer Druckregelanlage mit einem mehrstufigen Kompressor, sowie Druckregelanlage |
PCT/EP2018/059459 WO2018202402A1 (de) | 2017-05-05 | 2018-04-12 | Verfahren zum betreiben einer druckregelanlage mit einem mehrstufigen kompressor, sowie druckregelanlage |
Publications (1)
Publication Number | Publication Date |
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EP3619064A1 true EP3619064A1 (de) | 2020-03-11 |
Family
ID=62044680
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP18719486.5A Withdrawn EP3619064A1 (de) | 2017-05-05 | 2018-04-12 | Verfahren zum betreiben einer druckregelanlage mit einem mehrstufigen kompressor, sowie druckregelanlage |
Country Status (5)
Country | Link |
---|---|
US (1) | US11351828B2 (de) |
EP (1) | EP3619064A1 (de) |
CN (1) | CN110636950A (de) |
DE (1) | DE102017004359A1 (de) |
WO (1) | WO2018202402A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102017004361A1 (de) * | 2017-05-05 | 2018-11-08 | Wabco Gmbh | Verfahren zum Betreiben einer Druckregelanlage mit einem mehrstufigen Kompressor, sowie Druckregelanlage |
DE102017011527A1 (de) * | 2017-12-13 | 2019-06-13 | Wabco Gmbh | Druckluftversorgungsanlage zum Betreiben einer Pneumatikanlage. Verfahren und Fahrzeug |
Family Cites Families (22)
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US5769610A (en) * | 1994-04-01 | 1998-06-23 | Paul; Marius A. | High pressure compressor with internal, cooled compression |
DE19515895A1 (de) * | 1995-04-29 | 1996-10-31 | Bosch Gmbh Robert | Druckluft-Versorgungseinrichtung für Fahrzeug-Druckluftanlagen sowie Verfahren zum Steuern der Druckluft-Versorgungseinrichtung |
US5863186A (en) * | 1996-10-15 | 1999-01-26 | Green; John S. | Method for compressing gases using a multi-stage hydraulically-driven compressor |
DE10321771C5 (de) | 2003-05-15 | 2017-01-19 | Continental Teves Ag & Co. Ohg | Verfahren zur Leistungsbegrenzung eines mehrstufigen Kompressor und Kompressor zur Durchführung des Verfahrens |
DE102008034240B4 (de) * | 2008-07-23 | 2014-12-18 | Wabco Gmbh | Niveauregelanlage für Fahrzeuge und Verfahren zum Betreiben einer Niveauregelanlage |
DE102011083614A1 (de) | 2011-03-01 | 2012-09-06 | Continental Teves Ag & Co. Ohg | Trocknerschaltung für eine pneumatische Regelvorrichtung eines Fahrzeugs |
DE102011013440A1 (de) * | 2011-03-09 | 2012-09-13 | Wabco Gmbh | Verfahren zur Drucksteuerung in einem Fahrzeug sowie Drucksteuereinrichtung |
DE102011102169A1 (de) * | 2011-05-20 | 2013-05-16 | Linde Aktiengesellschaft | Verdichten von Medien |
DE102011084921A1 (de) | 2011-10-20 | 2013-04-25 | Continental Teves Ag & Co. Ohg | Kompressorschaltung für eine pneumatische Regelvorrichtung eines Fahrzeugs |
DE102012005303B4 (de) * | 2011-12-23 | 2020-11-12 | Wabco Gmbh | Druckluftversorgungsanlage, pneumatisches System und Verfahren zum Betreiben desselben |
DE102012001736A1 (de) * | 2012-01-31 | 2013-08-01 | Wabco Gmbh | Druckluftversorgungsanlage, pneumatisches System und Verfahren zum Betreiben einer Druckluftversorgungsanlage bzw. eines pneumatischen Systems |
DE102012006382A1 (de) * | 2012-03-30 | 2013-10-02 | Wabco Gmbh | Druckmittelversorgungsanlage, pneumatisches System und Verfahren zum Betreiben einer Druckmittelversorgungsanlage |
US20130280095A1 (en) * | 2012-04-20 | 2013-10-24 | General Electric Company | Method and system for reciprocating compressor starting |
DE102012010390B4 (de) | 2012-05-29 | 2023-01-05 | Amk Holding Gmbh & Co. Kg | Niveauregelung für Fahrzeuge mit mindestens einer Luftfeder |
DE102013003513A1 (de) * | 2013-03-04 | 2014-09-04 | Wabco Gmbh | Verdichteranordnung zum Betreiben einer Druckluftversorgungsanlage, Druckluftversorgungsanlage und Druckluftversorgungssystem sowie Fahrzeug mit einer solchen Druckluftversorgungsanlage |
DE102014207509A1 (de) * | 2014-04-17 | 2015-10-22 | Continental Teves Ag & Co. Ohg | Integrierte Luftversorgungseinheit |
DE102014116672B4 (de) * | 2014-11-14 | 2016-08-18 | Kaeser Kompressoren Se | Zwischenkühlerbypass |
DE102017004369A1 (de) * | 2017-05-05 | 2018-11-08 | Wabco Gmbh | Verfahren zum Betreiben einer Druckregelanlage mit einem mehrstufigen Kompressor, sowie Druckregelanlage |
DE102017004414A1 (de) * | 2017-05-05 | 2018-11-08 | Wabco Gmbh | Drosselanordnung sowie Druckregelanlage mit einer derartigen Drosselanordnung |
DE102017004361A1 (de) * | 2017-05-05 | 2018-11-08 | Wabco Gmbh | Verfahren zum Betreiben einer Druckregelanlage mit einem mehrstufigen Kompressor, sowie Druckregelanlage |
DE102017004360A1 (de) * | 2017-05-05 | 2018-11-08 | Wabco Gmbh | Verfahren zum Betreiben einer Druckregelanlage mit einem mehrstufigen Kompressor, sowie Druckregelanlage |
DE102017011527A1 (de) * | 2017-12-13 | 2019-06-13 | Wabco Gmbh | Druckluftversorgungsanlage zum Betreiben einer Pneumatikanlage. Verfahren und Fahrzeug |
-
2017
- 2017-05-05 DE DE102017004359.0A patent/DE102017004359A1/de not_active Withdrawn
-
2018
- 2018-04-12 WO PCT/EP2018/059459 patent/WO2018202402A1/de active Application Filing
- 2018-04-12 US US16/610,519 patent/US11351828B2/en active Active
- 2018-04-12 EP EP18719486.5A patent/EP3619064A1/de not_active Withdrawn
- 2018-04-12 CN CN201880029111.1A patent/CN110636950A/zh not_active Withdrawn
Also Published As
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US20200148022A1 (en) | 2020-05-14 |
US11351828B2 (en) | 2022-06-07 |
CN110636950A (zh) | 2019-12-31 |
DE102017004359A1 (de) | 2018-11-08 |
WO2018202402A1 (de) | 2018-11-08 |
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