EP2820299A1 - Flüssigkolbenanordnung mit plattentauscher für die quasi-isotherme verdichtung und entspannung von gasen - Google Patents
Flüssigkolbenanordnung mit plattentauscher für die quasi-isotherme verdichtung und entspannung von gasenInfo
- Publication number
- EP2820299A1 EP2820299A1 EP13703838.6A EP13703838A EP2820299A1 EP 2820299 A1 EP2820299 A1 EP 2820299A1 EP 13703838 A EP13703838 A EP 13703838A EP 2820299 A1 EP2820299 A1 EP 2820299A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- liquid
- pressure
- liquid piston
- piston
- pressure chamber
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
-
- 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
- F04B39/0005—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 adaptations of pistons
- F04B39/0011—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 adaptations of pistons liquid pistons
Definitions
- the invention relates to a liquid piston arrangement with plate exchanger for the quasi-isothermal compression and expansion of gases.
- High-pressure air storage uses the energy contained in compressed air. For example, at times when more power is produced than consumed, the excess energy can be used to pump air under pressure into a storage tank. When power is needed in the
- Compressed air stored energy back into other forms of energy eg. As electric power, converted or machines or vehicles are driven directly.
- Screw compressors, scroll compressors or liquid piston compressors limit the temperature fluctuations, where the heat first passes to the drops and then passes to an external exchanger.
- the return of the spray precipitate from the high-pressure region is technically complicated.
- motorized operation laxation
- an additional fluid circuit must ensure the spray, which in turn must be discarded in the exhaust to return to the circuit.
- the invention is therefore based on the object to provide a liquid piston arrangement for approximately isothermal processes in the higher pressure range.
- the problem underlying the invention is solved by the features of claim 1.
- Advantageous developments and refinements of the invention are specified in the subclaims.
- Claim 15 describes a method for compressing and relaxing gases. Further, in claims 16, 17 and 18 further advantageous liquid piston arrangements are mentioned.
- FIG. 1 shows a liquid piston arrangement with two liquid pistons, two hydrostatic control units and a low pressure generator or expander; 2A to 2D, the liquid piston assembly of FIG. 1 during the
- FIG. 4 shows a section through a laminated core from FIG. 3A
- FIG. 6 shows the torque curve as a result of the combined operation of the liquid piston arrangement of FIG. 5;
- FIGS 7A to 7D show a liquid piston assembly with a single point valve during operation; and Fig. 8 shows a part of a liquid piston arrangement with a heat exchanger roller.
- the liquid piston arrangements described below and shown schematically in the figures have liquid pistons which each contain a laminated core with fixed distances between the sheets.
- the laminated core fills the entire rectangular liquid piston working space.
- the free surface of the liquid between the sheets embodies the piston.
- the laminated core is displaceable in order to move the valve cone fastened to the upper package side surface without clearance in the metal sheets and to guide it for a gap-free circuit between low-pressure chamber and high-pressure chamber. When closed, therefore, no air dream remains in the high-pressure chamber.
- the laminated core absorbs the heat generated during the work cycles.
- the laminated core Since the laminated core is completely lapped at each stroke, it remains close to the temperature of the liquid. From the liquid, the heat is released through a heat exchanger to the environment.
- the rectangular high-pressure chamber is arranged obliquely, whereby the low-pressure valve cone can shut off the working space of a low-pressure piston with the high-pressure chamber in the closed position dead volume and enforces the position of the high-pressure valve flap at the upper corner of the laminated core a funnel-like inflow during compression and thus prevents swirling cross currents.
- liquid piston arrangements described here prevent any dead space, make high-pressure heat exchangers superfluous and ensure process-oriented switching accuracy.
- the plate exchangers described below are inserted in a respective kinematic chain whose losses wave / air or electricity / air does not negate the achieved efficiency again.
- There are topological designs are provided which avoid in particular air pockets by turbulence and high accelerations, friction by lateral forces and aging, by means of harmonious interaction of the elements of the "liquid connecting rod".
- liquid piston arrangements shown in FIGS. 1 to 8 in particular satisfy one or more or even all of the following conditions:
- the circuit in air should be leak-free, preferably by means of seat valves between the high pressure cylinder and Vordruckraum and the pressure side to the memory, and also remain completely dead space, to avoid turbulence.
- a reduction between shaft and piston movement should be ensured, since the stroke frequency 1 to 2 Hz is not exceeded and the shaft should have at least 1500 rpm.
- the connecting rod / piston volume should be periodically circulated through a tank without pressure, so that bubbles, dust and moisture can be removed.
- the outer exchanger should be connected to the low pressure side, since the lowest possible temperature differences with the environment are sought, which can hardly be achieved with a reasonable effort on high-pressure tube exchanger. In addition, therefore, a single outdoor exchanger can also serve Schokolbige systems.
- the piston movement reversal should be done with low accelerations, primarily according to a predetermined speed curve, which allows smoothing the pressure or torque pulsations in composite arrangements.
- FIG. 1 shows schematically a liquid piston arrangement 1 for the quasi-isothermal compression and expansion of gases with two liquid pistons 2 a, 2 b. Due to the same structure of the two liquid pistons 2 a, 2 b, the mutually corresponding elements of the liquid piston 2 a, 2 b, such. As high pressure spaces, laminated cores, etc., with number words ("first element” or "second element") are provided, as is the case in the following claims. For the sake of clarity, however, the description of the number words is omitted.
- the liquid pistons 2 a, 2 b each include a high-pressure chamber 3 a, 3 b and a laminated core 4 a, 4 b stored in the high-pressure chamber 3 a, 3 b.
- the laminated cores 4a, 4b each consist of a plurality of sheets, which are arranged in particular parallel to each other. Further, the sheets of a laminated core 4a, 4b may be arranged equidistantly and in particular have a distance between two adjacent sheets in the range of 0.3 to 0.8 mm.
- a liquid level 5a, 5b in the respective high-pressure chambers 3a, 3b and between the sheets of the sheet metal packets 4a, 4b represents the respective piston.
- the laminated cores 4a, 4b are slidably mounted in the high-pressure chambers 3a, 3b in order to forcibly control the low-pressure poppets 6a, 6b fastened to their upper sides, as a result of which low-pressure valves 7a, 7b are opened or closed.
- the undersides of the laminated cores 4a, 4b are fastened to spring-loaded control pistons 8a, 8b, by means of which the laminated cores 4a, 4b can be displaced in the high-pressure spaces 3a, 3b.
- the liquid piston assembly 1 further comprises a low pressure generator or expander 10, the z. B. can be configured as a reversible scroll unit or rotor rotor.
- the low-pressure generator or expander 10 is connected via an air line 1 1 with the low-pressure valves 7a, 7b in order to create a form in the high-pressure chambers 3a, 3b can.
- the other connection of the low pressure generator or expander 10 is equipped with a suction filter and / or muffler 12.
- the low-pressure generator or expander 10 is mounted on a shaft 13 and is driven by this.
- two variable, working in push-pull hydrostatic units 14a and 14b are provided, which can also be driven by the shaft 13 or can drive the shaft 13 during engine operation.
- the hydrostatic units 14a, 14b are connected via lines 15a, 15b to the high-pressure chambers 3a, 3b, so that they can feed or remove liquid into the high-pressure chambers 3a, 3b.
- the hydrostatic unit 14a controls the spool 8b via a pipe
- the hydrostatic unit 14b controls the spool 8a via a pipe 16b.
- a speed command 21 can be input, from which the actuator 20 together with the respective speed co of the shaft 13 and the delivery volume setting of the hydrostatic units 14a, 14b, the effective liquid feed or -dnähme calculated by the lines 15a, 15b the attack of the respective
- the hydrostatic units 14 a, 14 b are connected to a container 22 via filters 23 a, 23 b, an outer heat exchanger 24 and check valves 25.
- high-pressure valves 30a, 30b are arranged on the high-pressure chambers 3a, 3b.
- the high-pressure valves 30a, 30b consist of high-pressure valve flaps 31a, 31b which are located in cavities 32a, 32b are arranged and can be controlled by magnetic coils 33a, 33b. Connections from the high-pressure valves 30a, 30b to a storage space 35 are provided via lines 34a, 34b.
- the mode of operation of the liquid-piston arrangement 1 is explained below with reference to FIGS. 2A to 2D, wherein a distinction is made between two operating modes of the liquid-piston arrangement 1. In a first mode of operation, which is schematically illustrated in FIGS. 2A and 2B, gas is compressed by application of energy. In a second mode of operation, which is shown schematically in FIGS. 2C and 2D, the gas is expanded again and the energy released thereby is converted into a movement of the shaft 13.
- FIGS. 2A to 2D as well as all other figures, triangles symbolize the flow direction of the liquid in the respective lines. Filled triangles indicate a high pressure area, unfilled triangles a low pressure area. Flowless lines are shown in dashed lines.
- a pre-pressure in the respective high-pressure chamber 3a, 3b is initially created with the aid of the pressure provided by the low-pressure generator or expander 10. Subsequently, this pressure is increased by pumping liquid into the high-pressure chamber 3a, 3b.
- the high-pressure valve 30a, 30b opens and an increase in pressure in the storage space 35 can be achieved.
- FIGS. 2A and 2B show the two positions of the laminated cores 4a, 4b controlled by the control pistons 8a, 8b.
- the laminated core 4a in the upper position, so that the low-pressure valve 7a is closed, whereas the laminated core 4b is in the lower position and the low-pressure valve 7b is opened accordingly.
- the positions of the laminated cores 4a, 4b are exactly reversed.
- FIG. 2A shows that the hydrostatic unit 14a conveys liquid from the container 22 via the filter 23a and pumps the liquid further into the high-pressure space 3a, which results in a rising liquid level 5a there.
- the hydrostatic unit 14a conveys liquid from the container 22 via the filter 23a and pumps the liquid further into the high-pressure space 3a, which results in a rising liquid level 5a there.
- the low pressure generator or expander 10 a form of z. B. 1 to 6 bar generated. Due to the rising liquid level 5a, this pressure now increases successively.
- the high-pressure valve 30a opens and a feed into the storage space 35 can take place.
- the liquid contained in the high pressure space 3b is pumped from the hydrostatic unit 14b via the heat exchanger 24 into the tank 22. Since the low-pressure valve 7b is opened, prevails in the high pressure chamber 3b of the low pressure generator or expander 10 generated form.
- control pistons 8a, 8b are switched so that the positions of the sheet metal pawls 4a, 4b and thus the low-pressure poppet 7a, 7b as shown in Fig. 2B result.
- the liquid level 5b rises due to the liquid supplied from the tank 22 from the hydrostatic unit 14b.
- the high pressure valve 30b opens and the gas in the storage space 35 is further compressed.
- the cycle consisting of the two working phases shown in Figs. 2A and 2B is repeated, whereby a desired pressure in the storage space 35 in the range of, for example, 200 to 300 bar can be generated.
- the energy that has been used to generate this pressure can be converted into a movement of the shaft 13 in the so-called motor operation.
- FIGS. 2C and 2D The two operating phases of the engine operation are shown in FIGS. 2C and 2D.
- the spool 8a urges the laminated core 4a to the upper position, so that the low-pressure valve 7a is closed, whereas the laminated core 4b is in the lower position and the low-pressure valve 7b is opened accordingly.
- the positions of the laminated cores 4a, 4b are exactly reversed.
- the shaft 13 is driven via the hydrostatic unit 14a by the high pressure generated in the high-pressure chamber 3a.
- the liquid which is thereby pressed out of the high-pressure space 3a flows via the hydrostatic unit 14a and the outer heat exchanger 24 into the container 22.
- the hydrostatic unit 14b pumps liquid from the container 22 into the high-pressure space 3b in which the low-pressure generator or expander 10 generates the form via the opened low-pressure valve 7b.
- the energy that is used to operate the hydrostatic unit 14b and the low-pressure generator or expander 10 ultimately comes from the energy that has been transferred from the hydrostatic unit 14a to the shaft 13.
- other machines can be driven by the shaft 13, for example, a generator for power generation.
- the functionalities of the two liquid pistons 2a, 2b are exactly the opposite as in FIG. 2C.
- the targeted opening and closing of the high-pressure valve 30b creates a high-pressure in the high-pressure space 3b, which presses back the liquid previously pumped by the hydrostatic unit 14b into the high-pressure chamber 3b.
- the hydrostatic unit 14b converts a part of the energy stored in the storage space 35 into a movement of the shaft 13. A portion of this energy in turn is used by the hydrostatic unit 14a and the low pressure generator or expander 10 to pump liquid from the container 22 in the high-pressure chamber 3a and the form in the high-pressure chamber 3a to create.
- the cycle consisting of the work phases shown in Figs. 2C and 2D is repeated.
- the laminated cores 4a, 4b in the high-pressure chambers 3a, 3b act as heat exchangers and ensure an approximately isothermal operation even in higher pressure ranges.
- the resulting in the compression and relaxation temperature fluctuations are transmitted in the high-pressure chambers 3a, 3b of the air to the metal plates of the laminated cores 4a, 4b and from these to the liquid that flows around the laminated cores 4a, 4b. From the liquid, the temperature fluctuations are finally discharged via the outer heat exchanger 24 to the environment.
- the liquid piston arrangement 1 shown in FIG. 1 is a basic version of a push-pull circuit which fulfills all of the abovementioned conditions without a volumetric flask, but with two hydrostatic units 14a, 14b and with the separate low-pressure generator or expander 10, which is not the case in terms of price and efficiency Optimum represents (in combined operation, it would be four hydrostatic units, with a single low pressure generator or expander would suffice). From this basic version, all further liquid piston arrangements described below can be derived.
- FIG. 3A schematically shows a liquid piston arrangement 50 with two volumetric flasks as entrainment of a pilot pressure piston, whereby a second hydrostatic unit and the low pressure generator or expander are dispensed with, but with the aid of a reversing valve and a circulating pump in the treatment unit, as will be described below.
- Various operating states of the liquid piston assembly 50 are shown in Figs. 3A to 3D.
- the liquid piston arrangement 50 has two liquid pistons 51a, 51b, each comprising a high-pressure chamber 52a, 52b and a laminated core 53a, 53b mounted in the high-pressure chamber 52a, 52b.
- the laminated cores 53a, 53b of sheet stacks which are mounted by means of spring-loaded control piston 54a, 54b in the longitudinal axis slidably in the high-pressure chambers 52a, 52b.
- the movement of the laminations 53a, 53b determines the movement of low pressure poppets 55a, 55b and thus the opening and closing of low pressure valves 56a, 56b because the low pressure poppets 55a, 55b are fixedly connected to the respective stack of laminations on the upper stacking surface.
- the sheet metal plates of the laminated cores 53a, 53b can be provided with a spacing coupling 57a, 57b or other inserts, by means of which the distance between the metal sheets is predetermined.
- the distances between two adjacent sheet metal plates in the laminated cores 53a, 53b may be constant.
- the metal plates can be aligned parallel to each other, and the distance between adjacent metal plates is in particular between 0.3 and 0.8 mm.
- the laminated cores 53a, 53b may be in the form of a rectangular prism, as shown schematically in FIG. 4, which is a section of the laminated core 53a in the cylinder block 58a along the line A-A 'shown in FIG. 3A, ie, a vertical section to the longitudinal axis of the laminated core 53a, shows.
- the laminated cores 53a, 53b fill the respective high-pressure chamber 52a, 52b perpendicular to the longitudinal axis, ie in the plane shown in FIG.
- the low-pressure valves 56a, 56b mutatis mutandis connect the pre-pressure chambers 59a, 59b of the pilot pressure piston 60 with the respective high-pressure chambers 52a, 52b.
- the high-pressure valve flaps 65a, 65b are arranged in a respective cavity 67a, 67b together with holding magnet coils 68a, 68b and are guided coaxially therefrom.
- the respective liquid piston mirror 70a, 70b is moved by a measuring piston 72a, 72b coupled to the liquid connection 71a, 71b, which also carries the preliminary pressure piston 60 (the measuring pistons 72a, 72b and the priming piston 60 are connected to one another via a rod) and at each stroke a complete flushing of the respective laminated core 53a, 53b causes and thus an indirect exchange with an outer measuring piston 72a, 72b coupled to the liquid connection 71a, 71b, which also carries the preliminary pressure piston 60 (the measuring pistons 72a, 72b and the priming piston 60 are connected to one another via a rod) and at each stroke a complete flushing of the respective laminated core 53a, 53b causes and thus an indirect exchange with an outer
- Heat exchanger 75 This flow passes through a 7/2-way diverter valve 76a, 76b, which operates a non-pressurized circuit with the outer heat exchanger 75, a filter 77 and a reservoir 78.
- This arrangement allows a perfect replacement of the piston fluid at each stroke, as it flows depending on the direction either directly from - as shown in Fig. 3A on the left side exemplified - sheet stack 53a to the volumetric flask 72a via an exchange volume 80a and a check valve 81a, when moving of the volumetric flask 72a to the left (low pressure compression), corresponding to the illustrated slide position of the 7/2-way switch valve 76a, or high-pressure compression - as shown in Fig.
- a suction / exhaust valve 86a arranged dream-free on the admission-pressure chamber 59a is closed in order to generate the required admission pressure in the admission-pressure chamber 59a.
- a suction / exhaust valve 86b arranged dead-space-free on the pre-pressure space 59b is opened so that a pressure equalization in the pre-compression space 59b with the environment can take place.
- the suction / exhaust valves 86a, 86b are each opened and closed by means of a control piston.
- the volumetric pistons 72a, 72b are inserted in the respective hydraulic path between the controllable hydrostatic unit 87 and the 7/2-way diverter valve 76a, 76b and thus obey the mechanically or electronically impressed modified sine velocity profiles, which increase the acceleration of the liquid piston mirrors 70a, 70b limit.
- the operating fluid should preferably have a very low vapor pressure, such as.
- a very low vapor pressure such as.
- water or an ionic liquid from the methyl imidazolium group and in particular the hydrophobic ionic liquid l-ethyl-3-methylimidazolium bis (trifluoromethyl-sulfonyl) amide (EMIM BTA) since this the solubility of air under pressure minimal is and the condensation is easily separated out.
- Exhaust valve 86a, 86b is introduced via its control piston by reversing the direction of the measuring piston 72a, 72b or the reversal of the flow of a hydrostatic unit 87 at the dead centers.
- the hydrostatic unit 87 is controlled by a control unit 88, which in turn is controlled by running on a processor or other processing unit software.
- the high pressure valve flaps 65a, 65b perform a complex task, especially in the case of engine operation, because here the switching point is not tied to the dead centers and must be determined in the motor case by means of computers and sensors. Indeed, working with a liquid piston allows fixing the upper delivery dead point of the respective volumetric flask 72a, 72b over the valve seat plane, the liquid will only bypass the high pressure valve flap 65a, 65b and partially fill the cavity 67a, 67b.
- Control of the magnetic retaining coils 68a, 68b is performed by a control unit, such as the processor.
- FIG. 3A shows how a high pressure is generated in the high pressure space 52b in the compression of the gas
- the high pressure compression of the gas in the high pressure space 52a is shown in FIG. 3B (the storage space in which the compressed gas is stored is in FIG Figures 3A to 3D are not shown for clarity, but the ports for the reservoir are shown on the high pressure valves 66a, 66b).
- the control pistons 54a, 54b are driven such that the low pressure valve 56a is closed, i.e., closed. That is, the laminated core 53a is in the upper position, and the low-pressure valve 56b is opened, that is, it is in the upper position. h., the laminated core 53b is in the lower position.
- the liquid located in the right chamber of the volumetric flask 72a is pumped by the hydrostatic unit 87 via the check valve 82a into the high-pressure space 52a, whereby a high pressure is generated there.
- the liquid in the high-pressure chamber 52b is conveyed via the 7/2 way valve.
- Switch valve 76b and the check valve 81b promoted in the left chamber of the volumetric flask 72b.
- the suction / exhaust valve 86a is opened so that a pressure equalization in the pre-pressure space 59a with the Environment can take place.
- the suction / exhaust valve 86b is closed to produce the required pre-pressure in the pre-compression space 59b.
- the liquid contained in the exchange volume 80a is circulated by the pump 85 in FIG. 3B. In this case, for example, the exchange volume 80a is emptied into the reservoir 78 and new liquid pumped from the reservoir 78 in the exchange volume 80a.
- 3C and 3D show the two operating phases in the expansion of the gas, ie the engine operation, in which the stored energy in the compressed gas from the hydrostatic unit 87 or units connected thereto in other forms of energy, eg. As electrical energy or mechanical work is converted.
- Fig. 3C shows a working phase in which the low pressure valve 56a is opened and the low pressure valve 56b is closed. Further, the suction / exhaust valves 86a, 86b are closed and opened, respectively.
- the high-pressure space 52b which is initially filled with the liquid, is acted upon by the pressure present in the storage space via the opened high-pressure valve 66b.
- liquid is passed from the high-pressure chamber 52b via the 7/2-way switch valve 76b, the exchange volume 80b and the check valve 81b into the left-hand chamber of the volumetric flask 72b.
- the volumetric flask 72b thus moves to the right and drives the hydrostatic unit 87.
- the liquid from the right chamber of the volumetric flask 72a is pumped via the 7/2-way diverter valve 76a and the check valve 82a into the high-pressure chamber 52a, via the opened low-pressure valve 56a is generated by means of the likewise coupled to the volumetric flask 72b Vordruckkolbens 60 of the form.
- the liquid contained in the exchange volume 80a is circulated by the pump 85 in FIG. 3C.
- Fig. 3D the second working phase is shown in the engine operation.
- the low-pressure valve 56a is closed, and the low-pressure valve 56b is opened.
- the suction / exhaust valves 86a, 86b are opened and closed, respectively.
- About the open high-pressure valve 66a of the first filled with liquid high-pressure chamber 52a is acted upon by the pressure present in the storage space.
- liquid is pressed from the high-pressure space 52a via the 7/2-way diverter valve 76a, the exchange volume 80a and the check valve 81a into the right-hand chamber of the volumetric flask 72a.
- the volumetric flask 72 a thus moves to the left and drives the hydrostatic unit 87.
- the liquid from the left chamber of the volumetric flask 72b is pumped via the check valve 82b into the high-pressure chamber 52b, in which the pre-pressure is generated via the opened low-pressure valve 56b by means of the pre-pressure piston 60 likewise coupled to the volumetric flask 72a becomes.
- the liquid in the exchange volume 80b is circulated by the pump 85 in FIG. 3D.
- 3A with a simple volumetric flask is more suitable for small systems, since only two liquid points, two volumetric flasks with intermediate intermediate pressure piston and a circulation pump must be added to the two liquid piston to form an autonomous push-pull element by doubling a low-pulsation composite unit.
- two volumetric flasks with intermediate intermediate pressure piston and a circulation pump must be added to the two liquid piston to form an autonomous push-pull element by doubling a low-pulsation composite unit.
- a liquid piston assembly with four liquid piston as shown schematically in Fig. 5.
- the four pistons provide a compact speed controllable unit with low torque pulsations, the characteristics of which are evident in the diagram shown in FIG.
- the liquid piston arrangement comprises two push-pull elements 101 and 101 'with volumetric flasks 102a, 102b, 102a', 102b ', which are hydraulically connected to a common shaft 15 by means of a respective variable hydrostatic unit 103, 103'.
- Each of the push-pull elements 101, 101 ' contains two liquid pistons, which are operated in push-pull.
- the two displacement volume curves Q (vi) and Q (V2) are shifted by half a stroke in push-pull against each other.
- the individual torque of the respective unit M (vi), M (V2) and by the sum of the shifted individual torques arises analogously to the course of torque M.
- the hyperbolic pressure peak is due to the displacement volume curve Q (v) 5 also shows the versatility of the switch valve concept with the arrangement of a single processing unit 105 in conjunction with the respective switch valve housings 106, 106 'and the replacement containers 107, 107' the four liquid piston housings 108a, 108b, 108a ', 108b'.
- the liquid piston arrangement is also suitable, on the basis of purely mechanical elements, for the speed adjustment with "impressed pressure” (this is the speed control from the pressure source, the torque against the load determines the speed) during engine operation, specifically with the aid of steam engine linkage 6 is determined by scanning a cam profile 110, which is transmitted to the rocker 12 by the movement of the piston rod 11, whereby the amplitude of the transmission to the displacement volume adjustment 104 is determined by the height adjustment of the engagement engagement of the rod 1 13 by means of screw hand wheel 1 14.
- the curve Q (v) can thus be modulated up to the reversal of the direction of rotation as soon as the height adjustment reaches beyond the pivot point of the rocker 1 12.
- Fig. 7A shows schematically a liquid piston assembly 150 with a simplified switch valve concept.
- the liquid piston assembly 150 works with only one switch valve 151 which controls two measuring pistons 152a, 152b of this push-pull element as a function of the pressure difference across the hydrostatic unit 153, which occurs between the lines 154a, 154b and acts on the switch valve 151.
- the other elements of this simplified piston measuring push-pull element are two liquid pistons 165a, 165b with valves and control piston and a storage space 166. Connecting lines 167a, 167b lead from the liquid piston 165a, 165b to the storage space 166.
- a liquid tank 168 is a maintenance unit with filter and
- a computer actuator 169 moves the displacement volume adjustment of the hydrostatic unit 153 in response to the feedback 170 of the piston position and the setpoint input 171, wherein the possibility of a direct coupling of Vordruckkolben 172 a, 172 b is indicated by dashed lines.
- FIGS. 7A to 7D Various operating states of the liquid piston assembly 150 are shown in Figs. 7A to 7D, with Figs. 7A and 7B showing the compression of the gas using energy, and Figs. 7C and 7D showing the expansion of the gas.
- the hydrostatic unit 153 pumps liquid into the left chamber of the volumetric flask 152a.
- the right chamber of the volumetric flask 152a is emptied into the liquid tank 168. Further, the liquid is pumped from the right chamber of the measuring piston 152b into the liquid piston 165a.
- the liquid piston 165b is drained. In this case, the air in the liquid piston 165a is compressed until the pressure is high enough for the high-pressure valve of the liquid piston 165a to open.
- Fig. 7B the second position of the switch valve 151 is shown.
- the hydrostatic unit 153 pumps liquid into the right chamber of the measuring piston 152b, and the left chamber of the measuring piston 152b is discharged into the liquid tank 168.
- the volumetric flask 152a pumps liquid into the liquid piston 165b while the liquid piston 165a is being emptied. Thereby, the pressure in the storage space 166 is increased via the liquid piston 165b.
- liquid from the liquid piston 165b is pumped by the pressure of the gas from the storage space 166 into the left chamber of the measuring piston 152a.
- the liquid from the right chamber of the volumetric flask 152a is pumped into the liquid piston 165a.
- the volumetric flask 152b drives, via its right-hand chamber, the hydrostatic unit 153 and the shaft connected thereto.
- the switch valve 151 shown in Fig. 7D are the
- the liquid piston 165a transfers the high pressure from the storage space 166 to the measuring piston 152b, whereby the measuring piston 152a drives the hydrostatic unit 153, which converts the energy into a movement of the shaft.
- FIGS. 1 to 7 exclusively as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the topmost tip.
- FIGS. 1 to 7 also as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the topmost tip.
- FIGS. 1 to 7 also as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the topmost tip.
- FIGS. 1 to 7 exclusively as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the topmost tip.
- FIGS. 1 to 7 exclusively as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the topmost tip.
- FIGS. 1 to 7 exclusively as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the topmost tip.
- FIGS. 1 to 7 exclusively as a tilted rectangular prism for receiving the laminated core, with the high-pressure valve at the top
- the (heat) exchanger roller 181 is embedded in the cylinder body 182, whose oblique parting line 183 with the piston block 184 produces a convergence towards the high pressure valve 185, similar to the prismatic laminated core 53a, 53b of FIG. 3A.
- the (heat) exchanger roller 181 is wound around a cylinder body 186 of the piston block 184.
- the (heat) exchanger roller 181, together with the cylinder body 186, is penetrated laterally from below by a pin-shaped seat valve body 187, so that the connection between the admission pressure chamber 189 and the liquid piston space in the (heat) exchanger roller 181 can be connected via a cone 188 ,
- the cone 188 is moved to open or close the connection between the pressure chamber 189 and the liquid piston space in the (heat) exchanger roller 181.
- the movement of the cone 188 is effected by acting on a control piston 190 via a connection nipple 191, whereby a retaining spring 192 is compressed.
- FIG. 8 the elements already known from FIG. 3A are provided in FIG. 8, such as intake / exhaust valve, volumetric flask, pilot pressure piston, hydraulic fluid, etc., which ensure friction-free operation.
- the roller part including control valves can of course also be operated without a volumetric flask, in the sense of FIG. 1 with separate low-pressure generator or expander.
- the exchanger roller 181 including control valves shown in FIG. 8 can also be inserted into the liquid piston arrangements shown in FIGS. 1, 3, 5 and 7.
- the indirect exchanger made of sheet metal plates with fine and fixed distances between the plates is inserted in push-pull circuits with adjustable hydrostatic units for the purpose of low-loss kinematic connection with a fast-rotating shaft. Attention is paid to the rigorous cyclic exchange of the liquid, so that optimum heat removal with continuous treatment (degassing, decanting, water separation) in a pressureless sump tank is possible. Different types of push-pull elements are possible (with two hydrostatic units and external pre-pressure generation, with turnout valves).
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012003288A DE102012003288B3 (de) | 2012-02-20 | 2012-02-20 | Flüssigkolbenanordnung mit Plattentauscher für die quasi-isotherme Verdichtung und Entspannung von Gasen |
PCT/EP2013/052946 WO2013124202A1 (de) | 2012-02-20 | 2013-02-14 | Flüssigkolbenanordnung mit plattentauscher für die quasi-isotherme verdichtung und entspannung von gasen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2820299A1 true EP2820299A1 (de) | 2015-01-07 |
EP2820299B1 EP2820299B1 (de) | 2016-09-28 |
Family
ID=47710178
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13703838.6A Not-in-force EP2820299B1 (de) | 2012-02-20 | 2013-02-14 | Flüssigkolbenanordnung mit plattentauscher für die quasi-isotherme verdichtung und entspannung von gasen |
Country Status (7)
Country | Link |
---|---|
US (1) | US9234534B2 (de) |
EP (1) | EP2820299B1 (de) |
BR (1) | BR112014020814A2 (de) |
CA (1) | CA2864610A1 (de) |
DE (1) | DE102012003288B3 (de) |
DK (1) | DK2820299T3 (de) |
WO (1) | WO2013124202A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2984345B1 (de) * | 2013-04-12 | 2018-09-12 | Eaton Corporation | Gradientenmedien eines druckbehälters für wärmeaustausch in einem kompressionssystem |
WO2014169108A2 (en) * | 2013-04-12 | 2014-10-16 | Eaton Corporation | Pressure vessel having plurality of tubes for heat exchange |
US10408211B2 (en) | 2013-07-12 | 2019-09-10 | Eaton Intelligent Power Limited | Hydraulic system for pressurization of gas with reduction of dead volume |
DE102013227017B4 (de) * | 2013-12-20 | 2015-07-16 | Carnoo Ug (Haftungsbeschränkt) | Verdichtervorrichtung sowie Verfahren und Vorrichtung zum Betreiben eines links- oder rechtsdrehenden Kreisprozesses, insbesondere unter Einsatz einer solchen Verdichtervorrichtung |
WO2017198725A1 (en) | 2016-05-17 | 2017-11-23 | Enairys Powertech Sa | Hybrid multistage gas compression/expansion systems and methods |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US586100A (en) * | 1897-07-13 | Air-compressor | ||
DE3408633A1 (de) * | 1984-03-09 | 1985-09-19 | Manfred Dr. 8060 Dachau Eckert | Prinzip und anlage fuer isotherme verdichtung von gasen und daempfen |
US5454426A (en) | 1993-09-20 | 1995-10-03 | Moseley; Thomas S. | Thermal sweep insulation system for minimizing entropy increase of an associated adiabatic enthalpizer |
DE4430716A1 (de) | 1994-08-30 | 1996-03-07 | Roland Bitzer | Isotherm-hydraulischer Hochdruckverdichter |
WO1998017492A1 (de) | 1996-10-18 | 1998-04-30 | Tcg Unitech Aktiengesellschaft | Antriebssystem für ein kraftfahrzeug |
CN1274050A (zh) | 1999-05-14 | 2000-11-22 | 杨双来 | 高压气泵 |
EP2158389A4 (de) | 2007-05-09 | 2016-03-23 | Ecole Polytechnique Fédérale De Lausanne Epfl | Energiespeichersysteme |
WO2009034421A1 (en) | 2007-09-13 | 2009-03-19 | Ecole polytechnique fédérale de Lausanne (EPFL) | A multistage hydro-pneumatic motor-compressor |
WO2009152141A2 (en) | 2008-06-09 | 2009-12-17 | Sustainx, Inc. | System and method for rapid isothermal gas expansion and compression for energy storage |
DE102008042828B4 (de) * | 2008-10-14 | 2010-12-16 | Ago Ag Energie + Anlagen | Verfahren und Vorrichtung zum Betreiben eines Stirling-Kreisprozesses |
FR2944992B1 (fr) | 2009-05-04 | 2011-07-01 | Cerlase | Procede de transfert d'un motif sur un objet |
FR2945327A1 (fr) | 2009-05-07 | 2010-11-12 | Ecoren | Procede et equipement de transmission d'energie mecanique par compression et/ou detente quasi-isotherme d'un gaz |
US8359857B2 (en) | 2009-05-22 | 2013-01-29 | General Compression, Inc. | Compressor and/or expander device |
ATE528508T1 (de) * | 2009-06-02 | 2011-10-15 | Ago Ag En & Anlagen | Flüssigkolbenwandler |
US8196395B2 (en) | 2009-06-29 | 2012-06-12 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
JP2013515945A (ja) | 2009-12-24 | 2013-05-09 | ジェネラル コンプレッション インコーポレイテッド | 圧縮及び/又は膨張装置内の伝熱を最適化する方法及び装置 |
-
2012
- 2012-02-20 DE DE102012003288A patent/DE102012003288B3/de not_active Expired - Fee Related
-
2013
- 2013-01-29 US US13/752,840 patent/US9234534B2/en not_active Expired - Fee Related
- 2013-02-14 WO PCT/EP2013/052946 patent/WO2013124202A1/de active Application Filing
- 2013-02-14 CA CA2864610A patent/CA2864610A1/en not_active Abandoned
- 2013-02-14 DK DK13703838.6T patent/DK2820299T3/en active
- 2013-02-14 BR BR112014020814A patent/BR112014020814A2/pt not_active Application Discontinuation
- 2013-02-14 EP EP13703838.6A patent/EP2820299B1/de not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2013124202A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP2820299B1 (de) | 2016-09-28 |
US9234534B2 (en) | 2016-01-12 |
CA2864610A1 (en) | 2013-08-29 |
DE102012003288B3 (de) | 2013-03-14 |
WO2013124202A1 (de) | 2013-08-29 |
US20130213213A1 (en) | 2013-08-22 |
DK2820299T3 (en) | 2017-01-09 |
BR112014020814A2 (pt) | 2019-08-27 |
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