EP0857877A2 - Convertisseur pneumatique-hydraulique - Google Patents

Convertisseur pneumatique-hydraulique Download PDF

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Publication number
EP0857877A2
EP0857877A2 EP98101341A EP98101341A EP0857877A2 EP 0857877 A2 EP0857877 A2 EP 0857877A2 EP 98101341 A EP98101341 A EP 98101341A EP 98101341 A EP98101341 A EP 98101341A EP 0857877 A2 EP0857877 A2 EP 0857877A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
converter
pneumatic
piston
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP98101341A
Other languages
German (de)
English (en)
Other versions
EP0857877A3 (fr
Inventor
Jörg Dantlgraber
Heino Försterling
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0857877A2 publication Critical patent/EP0857877A2/fr
Publication of EP0857877A3 publication Critical patent/EP0857877A3/fr
Withdrawn legal-status Critical Current

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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a pneumatic-hydraulic converter, with the help of a pneumatic one under pressure Gas stored energy via an intermediate hydraulic step ultimately be translated into mechanical performance should.
  • the invention has for its object a pneumatic-hydraulic To create transducers that are suitable instead an electric battery to which an electric motor is connected is used in a mobile working device in particular savings, compared to the electrical solution in terms of weight and costs and in the manufacture less harmful to the environment.
  • the task formulated above is based on claim 12 a second way by a pneumatic-hydraulic converter solved, in which a gas is also stored in a pressure vessel is and a piston from the pressure vessel in portions dispensable and relaxing gas is displaceable.
  • the piston is now a separating piston, which has a first working space separates a second working space of a separation cylinder.
  • the gas is delivered to the first work room. From the second work room hydraulic fluid can be displaced by the separating piston.
  • a hydraulic fluid can also be conveyed into a pressure line.
  • the above task is on a third way solved by a pneumatic-hydraulic converter, which like the converter according to claim 12, a pressure vessel with gas, a separating piston and a pressure line, at however between the pressure line and the second work space the separating piston a resonator with at least one pressure chamber is arranged by a movable mass part against a spring is limited and cyclically with a valve arrangement the second working space of the separating cylinder, a low pressure line and the pressure line is connectable.
  • a pneumatic-hydraulic converter which like the converter according to claim 12, a pressure vessel with gas, a separating piston and a pressure line, at however between the pressure line and the second work space the separating piston a resonator with at least one pressure chamber is arranged by a movable mass part against a spring is limited and cyclically with a valve arrangement the second working space of the separating cylinder, a low pressure line and the pressure line is connectable.
  • the pressure chamber which can be changed in terms of volume is achieved in cooperation with the spring-mass system that that during the connection of the pressure chamber on the one hand with the second work space and on the other hand with the low pressure line pressure medium flowing into the pressure chamber during the pressure chamber connection with the pressure line due to the stored in the spring Energy is pushed out of the pressure chamber again, so that depends on the switching frequency of the valve assembly Sets the volume flow of the hydraulic fluid in the pressure line. This is advantageously via the switching frequency of the switching valve controlled.
  • Switching frequencies in the over-resonance range of the spring-mass system ie in a frequency range above its resonance frequency.
  • volume flow of the hydraulic fluid also depends on the Time in which the pressure chamber with the second working chamber of the Separating cylinder is connected, depends, can be used to control the Volume flow can also be changed this time. It succeeds this way, despite falling gas pressure and hydraulic fluid pressure an even volume flow in the workrooms of the separating cylinder to generate in the pressure line. Possibly several separating pistons and several resonators are provided which are cyclical Dispense fluid into the pressure line.
  • Another setting option is the choice of opening times, in which the pressure line with the pressure chamber of the Resonators is connected. Because these times are opposite the connection time of the pressure chamber to the second work space of the Separating cylinder and shortened to the low pressure line accordingly, the pressure in the pressure line in the second working chamber pressure of the separating cylinder built up will.
  • the volume flow in the Pressure line can be lowered with the advantage that compared to one Volume flow control over the opening time between second working space of the separation cylinder and the pressure chamber better efficiency is achieved.
  • the converter pistons limit 10, 11 or 12 each from a work space 13, the Volume changes by moving a converter piston.
  • a work space is connected via a first solenoid valve 14 a compressed air reservoir 15 connectable, e.g. to a maximum Pressure of 200 bar can be charged.
  • Any solenoid valve 14 locks in a rest position that it under the action a return spring 16 occupies the connection between one Working space 13 and the pressure accumulator 15.
  • Each valve 14 can by driving an electromagnet 17 into a second switching position be brought in the compressed air from a compressed air reservoir 15 can flow into the work space 13.
  • About one any workspace can have a second electromagnetically actuated valve 18 13 are vented.
  • first pinion 26 which has a freewheel, not shown is connected to the drive shaft 27 of a hydraulic pump 28.
  • the pinion 26 may drive the drive shaft 27 when the Move both converter pistons 10 and 11 to the right.
  • the pinion 26 then rotates in the direction of arrow 29 and takes the drive shaft 27 with the freewheel.
  • a second pinion 30 is the pinion 26 with respect to FIG Rack 25 arranged opposite one another. This pinion is 30 also via a freewheel with the drive shaft 31 second hydraulic pump 32 connected.
  • the freewheel is ineffective when the two converter pistons 10 and 11 move to the left, wherein the pinion 30 is rotated in the direction of arrow 33. At a movement of the converter pistons 10 and 11 to the right is caused no torque from the pinion 30 to the drive shaft 31 transmitted.
  • each of the two hydraulic pumps 28 and 32 is always only in driven in the same direction.
  • the stroke volume of the two hydraulic pumps 28 and 32 is adjustable so that it corresponds to the way of the driving converter piston 10 or 11 or the pressure of the be adapted to gas relaxing in a work space can.
  • To the pressure line 34 is also a hydraulic accumulator 35 to equalize the pressure connected.
  • the pressure line 34 leads to an adjustable Hydraulic machine 36, e.g. for driving a forklift heard and which is also suitable in pressure medium from a tank to promote the memory 35 when the forklift is braked.
  • the embodiment according to FIG. 2 is correct with regard to the converter pistons 10 and 11 of the rack 25 and the two pinions 26 and 30 with the embodiment according to Figure 1.
  • Each pinion 26 or 30 is a further pinion downstream of a freewheel, the has the same axis as the pinion 26 and 30 and the same Pinion can be formed.
  • These subordinate sprockets both mesh with a gear 37, which is non-rotatable on the drive shaft 27 of a hydraulic pump 28 is seated.
  • the pinion 26 With a movement of the Converter piston 10 and 11 to the right, the pinion 26 is in the direction of the arrow 29 driven and can rotate about transfer the assigned freewheel to gear 37.
  • the other Pinion 30 can due to the freewheel downstream regardless of the direction of rotation of the gear 37 against the Turn in the direction of arrow 33.
  • the pinion 26 rotates freely and that Pinion 30, which now rotates in the direction of arrow 33, transmits its rotation on gear 37.
  • This gear 37 and with it the drive shaft 27 of the hydraulic pump 28 rotate so always in the same direction.
  • the hydraulic pump 28 in turn feeds into a pressure line 34 which connected a hydraulic accumulator 35 and a hydraulic machine 36 are.
  • the two converter pistons 10 and 11 of the embodiment according to FIG. 3 in turn work in opposite directions to one another and are over one Rack 25 rigidly connected.
  • the stroke volume the hydraulic pump 43 is up to a maximum positive value adjustable to a maximum negative value.
  • the hydraulic pump 43 is a pump that can be swiveled over zero. This means that the delivery direction of the hydraulic pump 43 without changing the direction of rotation the drive shaft 42 can be reversed. It means furthermore, that the direction of conveyance is also reversed Direction of rotation of the drive shaft 42 can be maintained. From the latter is followed in the pneumatic-hydraulic converter Figure 3 made use of.
  • the pinion 30 and with it the drive shaft 42 is at a movement of the converter pistons 10 and 11 to the left in one direction of rotation and with one movement the converter pistons 10 and 11 to the right in the other direction of rotation driven. Every time the direction of rotation is reversed, the hydraulic pump pivoted above zero so that the direction of conveyance is maintained and each conveyed pressure medium into the pressure line 34 becomes. A hydraulic accumulator 35 and a hydraulic machine are in turn connected to these 36 connected.
  • the stroke volume of the hydraulic pump 43 is during a full work cycle of the two Converter pistons 10 and 11 each from a large value to close reduced to zero, then opposite to a large value Sign enlarged and again close to zero decreased down.
  • the maximum value of the stroke volumes of the hydraulic pumps 28, 32 and 43 is in each case also dependent on that in the Compressed air storage 15 changed prevailing pressure.
  • the plunger is in the embodiment according to FIG 49 of a hydraulic pump 50, a first lever 51 of a toggle lever 52 hinged.
  • a second lever 53 of the toggle lever 52 is hingedly connected to an actuating piston 54, which in the direction stronger kink of the toggle lever 52 from one in a pressure chamber 55 of an actuating cylinder 56 prevailing pressure of a fluid Medium is acted upon.
  • a compression spring exerts in the opposite direction 57 a force on the actuating piston 54.
  • An articulated connection between the center joint between the two levers 51 and 53 and the converter piston 10 is produced via a coupling rod 57.
  • the inherent principle of the toggle lever is that the gear ratio between the path of the converter piston 10 and the path of the Plunger 49 of the hydraulic pump 50 depending on the the two levers 51 and 53 of the toggle lever 52 enclosed Angle changes and thereby an adjustment of the gear ratio to the pressure of the relaxing in the work space 13 Gases is possible. In this way, the plunger 49 10 pressure medium under the entire path of the converter piston a largely constant pressure in the pressure line 34 promote.
  • the pressure chamber 55 of the actuating cylinder 56 is with the compressed air reservoir 15 connected so that at the beginning of a work cycle in the working space 13 and in the pressure chamber 55 the same pressure as in that Compressed air reservoir 15 prevails. Between that from this pressure on an effective area of the control piston 54 generated force and Force of the compression spring 57 establishes a balance that depending on the pressure in the compressed air reservoir 15 in each case another position of the actuating piston 54 is reached. Since the Starting position of the converter piston 10 from the equilibrium position of the actuating piston 54 depends on the actuating cylinder 56 and the actuating piston 54 of the pneumatic-hydraulic converter 4 to the changing with increasing operating time Adjusted pressure in the compressed air reservoir 15.
  • FIG. 5 there are three converter pistons 10, 11 and 12 in a star shape to each other at equal angular intervals around the Drive shaft 27 of a hydraulic pump 28 arranged around.
  • the converter piston is connected to a crank pin via a push rod 60 61 a crank 62 is articulated, which is secured against rotation on the drive shaft 27 of the hydraulic pump 28 is attached.
  • the three converter pistons 10, 11 and 12 work 120 degrees apart.
  • the effective lever arm on the crank 62 whereby a Adaptation to the pressure of the relaxing in the work space 13 Gases can be done.
  • Masses an equalization of the output to the drive shaft 27 Torque achieved.
  • the stroke volume of the hydraulic pump 28 adjustable. Overall, it can therefore be largely constant Pressure in the pressure line 34 into which the hydraulic pump 28 promotes, be maintained.
  • the thrust crank principle can also be used with just one converter piston be realized.
  • an additional Flywheel provided, with the help of which to the drive shaft 27 deliverable torque is equalized.
  • a transmission gear can also be used the explanations according to FIGS. 1 to 3 and according to FIG. 5 in the drive shaft leading to the respective hydraulic pump installed the optimum drive speed for the hydraulic pump to obtain.
  • each converter piston from a compressed air accumulator assigned only to it 15 supplied with compressed air In principle it is too possible, several converter pistons from one and the same compressed air reservoir to supply with compressed air, one of each several solenoid valves 14 opens briefly.
  • the converter pistons 10 and 11 are wetted by the oil and can absorb heat from this oil, so that relaxation of the gas located in the work space 13 largely isothermally.
  • a hydraulic transformer is used 70 used. This is on the primary side of each Pressure valve 71 with two second working spaces 72 of a separating cylinder 73 connected.
  • This is a double separation cylinder formed of a central cylinder chamber 74 of a given Has diameter, on both sides in the axial direction each connects an outer cylinder chamber 75, the diameter smaller than the diameter of the central cylinder chamber 74 is.
  • the diameters are chosen so that the cross-sectional area the middle cylinder chamber 74 just twice as large or slightly smaller than twice the cross-sectional area of the cylinder chambers 75.
  • Both working spaces 72 are each provided with a suction valve 80 connected to a hydraulic fluid tank 81.
  • a conduit 82 leads from the bottom of each cylinder chamber 75 a valve 83, via which the one in a first switching position first working space 79 with a compressed air reservoir 15 and the another first work space 79 can be connected to the atmosphere. In the other switching position of the valve 83 are the connections vice versa.
  • a solenoid valve In a line between the valve 83 and the compressed air reservoir 15 is inserted a solenoid valve, the solenoid valve 14 from Figures 1 to 5 corresponds and therefore with the same reference number 14 is provided. Via the solenoid valve 14 is the short-term actuation of the electromagnet 17 Compressed air reservoir 15 depending on the position of the valve 83 briefly with the first work room or connected to the other first working space 79 of the separating cylinder 73.
  • the secondary unit of the hydraulic transformer 70 promotes Hydraulic fluid into a pressure line 34 to which a hydraulic motor 84 connected. This can be swiveled over zero, so it can the wheel 85 one without interchanging the pressure and suction connection driving mobile work tools forward and backward, too if, as shown in Figure 6, one firmly connected to the tank Has suction connection.
  • the hydraulic transformer 70 according to FIG. 6 can be a Have a primary unit with a constant displacement, which acts as a motor works and with their pressure input to the pressure valves 71 leading line 86 and with an outlet to the tank 81 connected is.
  • the stroke volume of the secondary unit is zero adjustable up to a maximum value.
  • the hydraulic transformer contains 70 in turn one on one side with line 86 and on the other hand primary unit connected to tank 81 90 with a constant stroke volume.
  • the primary unit 90 drives mechanically as a motor on a secondary unit 91, the stroke volume from a maximum positive value above zero to one maximum negative value is adjustable.
  • the direction of through the secondary unit 91 flowing hydraulic fluid can without Reversal of the direction of rotation of the drive can be reversed.
  • the secondary unit 91 is together with a hydraulic motor 92, the Stroke volume is constant in a closed hydraulic Cycle operated.
  • FIG. 8 shows a hydraulic transformer 70 in which both the primary unit 90 and the secondary unit 91 in their stroke volume is adjustable. You get a big one Adjustment range of the hydraulic transformer.
  • FIG. 9 shows how a hydraulic transformer 70 can be constructed.
  • the two units 90 and 91 of the hydraulic Transformer is common. Stuck on the wave and at a distance from each other two drums 102 into which in a fixed distance to the axis of each drum 102 and in one fixed angular distance from each other a series of axial bores 103 are introduced.
  • the axial bores 103 of both drums 102 are open to the same axial direction.
  • an axial piston 104 is displaceable, which has a variable volume Working space 105 between its one end face and the bottom of the respective axial bore 103.
  • Each axial piston 104 is supported with a spherical head via a slide shoe 106 on a swash plate 107, which by an axis of rotation perpendicular to the axis of the shaft 101 108 is pivotable.
  • the two units 90 and 91 act it is so-called swash plate axial piston machines, the basic structure of which is generally known is, so that it will not be discussed in more detail here got to. It is essential for the hydraulic transformer that the Primary unit 90 mechanically coupled to secondary unit 91 and drives it. It can be in contrast to the 9 also act as two individual units, whose shaft is coupled to one another via connecting means.
  • the pneumatic-hydraulic converter shown in Figure 11 is correct with regard to the compressed air reservoir 15, the valves 14 and 83 and the separation cylinder 73 and the line 86 with the execution 6, which is why the components mentioned in FIG. 11 are not shown in detail. Otherwise, the execution 11 shows a resonator 112, which is periodic by means of two actuatable switching valves 113 and 114 alternately with the line 86 and thus with a second work space 72 of the Separation cylinder, with a low-pressure line 115, which by a Tank 81 goes out, which is optionally biased, and with the Pressure line 34 is connected.
  • the valve 114 switches on Output 116 between the two lines 86 and 115 um.
  • the Valve 113 in turn switches a connection between the output 116 of the switching valve 114 and the pressure line 34 around.
  • the resonator 112 is formed by a cylinder 118 in which a pressure chamber connected to port 117 of switching valve 113 119 is limited by a movable piston 120 which a spring 121 on an end wall of the cylinder 118 supports.
  • the piston 120 forms a mass-spring system with the spring 121 with a certain resonance frequency.
  • hydraulic fluid delivered into the pressure chamber 119 is during the connection of the pressure chamber with the Pressure line 34 due to the hydraulic loading of the piston 120 energy stored in the mass-spring system conveyed into the pressure line 34, with the purpose of smoothing pressure fluctuations a hydraulic accumulator 35 is connected to the pressure line 34 is.
  • the hydraulic machine 93 is fed from the line 34, which drives the wheel 85 of a mobile working device.
  • the switching valves connect during a switching cycle 113 and 114 the pressure chamber 119 of the resonator 112 first with line 86 for a time T1. Then switches the valve 114 to connect the pressure chamber 119 to the To produce low pressure line 115 for a period of time T2 in the hydraulic fluid due to the inertia of the piston 120 is sucked from the tank 81 into the pressure chamber 119. Then switches the valve 113 and connects the for a time T3 Pressure chamber 119 with the pressure line 34. One chooses for the time T3 just half the period, so the piston 120 during all his movement to the left while he was the pressure chamber 119 reduced, press hydraulic fluid into pressure line 34.
  • the volume flow through the resonator 112 depends above all from the switching frequency of the valve arrangement and from that to the Period time referred to T1. Is the pressure in the pressure line 34 smaller than in line 86, so you take for the Time T3 advantageously half the period and changes the volume flow by changing the times T1 and T2. If the pressures in lines 34 and 86 are the same, so T2 can be zero, while T1 and T3 each half Correspond to the duration of the period. If you leave the time T1 at half Period duration and one shortens the time T3 in favor of the time T2, the piston 120 becomes at maximum after its reversal of movement Volume of the pressure chamber 119 from the spring 121 against the accelerated low pressure in line 115.
  • the pressure in the pressure line 34 is generated by a pressure transmitter 125 and the pressure in line 86 through a pressure transmitter 126 recorded.
  • the two pressure transmitters convert the pressure into an electrical one Signal around to an electrical control unit 127 is given that the electromagnets 111 of the two valves 113 and 114 controls.
EP98101341A 1997-02-08 1998-01-27 Convertisseur pneumatique-hydraulique Withdrawn EP0857877A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19704822 1997-02-08
DE19704822 1997-02-08

Publications (2)

Publication Number Publication Date
EP0857877A2 true EP0857877A2 (fr) 1998-08-12
EP0857877A3 EP0857877A3 (fr) 1999-02-10

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EP98101341A Withdrawn EP0857877A3 (fr) 1997-02-08 1998-01-27 Convertisseur pneumatique-hydraulique

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000037800A1 (fr) * 1998-12-22 2000-06-29 Tcg Unitech Aktiengesellschaft Dispositif pour convertir de l'energie stockee dans de l'air comprime en travail mecanique
DE19903907A1 (de) * 1999-02-01 2000-08-03 Mannesmann Rexroth Ag Verfahren und Einrichtung zum Antreiben eines hydraulischen Verbrauchers
WO2000068578A1 (fr) * 1999-05-06 2000-11-16 Tcg Unitech Aktiengesellschaft Dispositif de conversion d'energie pneumatique en energie hydraulique
EP1985866A1 (fr) * 2007-04-26 2008-10-29 Services Pétroliers Schlumberger Distributeur rotatif pour multiplicateur de pression
EP1988294A2 (fr) 2007-05-04 2008-11-05 Robert Bosch GmbH Entraînement hydropneumatique
WO2009126784A2 (fr) * 2008-04-09 2009-10-15 Sustainx, Inc. Systèmes et procédés de stockage et de récupération d’énergie à l’aide de gaz comprimé
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CN111879621A (zh) * 2020-07-23 2020-11-03 华侨大学 一种智能动态液压加载装置

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WO2009152141A2 (fr) * 2008-06-09 2009-12-17 Sustainx, Inc. Système et procédé pour la détente et la compression isotherme rapide de gaz pour le stockage d'énergie
WO2009152141A3 (fr) * 2008-06-09 2010-02-04 Sustainx, Inc. Système et procédé pour la détente et la compression isotherme rapide de gaz pour le stockage d'énergie
US8495872B2 (en) 2010-08-20 2013-07-30 Sustainx, Inc. Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas
US20170067454A1 (en) * 2014-02-23 2017-03-09 Isocurrent Energy Incorporated Compressed air energy storage system
JP2017520725A (ja) * 2014-05-12 2017-07-27 ラビー, ヴィアニーRABHI Vianney ピストン型圧力変換用のエンドストローク拡張機
CN111879621A (zh) * 2020-07-23 2020-11-03 华侨大学 一种智能动态液压加载装置
CN111879621B (zh) * 2020-07-23 2022-07-01 华侨大学 一种智能动态液压加载装置

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