EP2585719A2 - Machine hydrostatique à piston rotatif à volume variable en continu - Google Patents

Machine hydrostatique à piston rotatif à volume variable en continu

Info

Publication number
EP2585719A2
EP2585719A2 EP11727168.4A EP11727168A EP2585719A2 EP 2585719 A2 EP2585719 A2 EP 2585719A2 EP 11727168 A EP11727168 A EP 11727168A EP 2585719 A2 EP2585719 A2 EP 2585719A2
Authority
EP
European Patent Office
Prior art keywords
piston
rotary piston
rotary
teeth
stator
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Withdrawn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
EP11727168.4A
Other languages
German (de)
English (en)
Inventor
Siegfried A. Eisenmann
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP11727168.4A priority Critical patent/EP2585719A2/fr
Publication of EP2585719A2 publication Critical patent/EP2585719A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/22—Rotary-piston engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/104—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a hydrostatic
  • a hydrostatic rotary piston engine of this type is known from WO 2006/010471. Such hydrostatic
  • Cavitation hazard should be at these narrowest cross sections in the Flow system, the oil velocity does not exceed the value of 10 m / s to a maximum of 12 m / s. If such a hydraulic motor is operated in the cavitation area, a considerable amount of noise is generated and the imploding cavitation bubbles lead to the destruction of the machine after a short time. These cavitation bubbles contain up to 10% air in the original fluid and also arise at these high levels
  • Brake energy recovery is possible by the specially designed as a wheel motor high-torque hydraulic motors are switched in the case of braking to pumps and absorb torque. These high-torque hydraulic motors suck fluid from the tank and convey it under pressure into one or more hydraulic accumulators. The energy stored there can then be used again while driving.
  • the problem of narrow flow cross sections at the commutator or rotary valve is much more dramatic here than in the case of the
  • Inner rotor axis are not on top of each other, but they are spaced parallel to each other.
  • the inner rotor is thus eccentric to the outer rotor, the Ausserver leopardung and the internal teeth partially interlock.
  • the outer rotor is indeed as a stator
  • this stator is also an external rotor rotatable in the housing about an axis.
  • this teaching can not be transferred to rotary engines. While a gerotor machine or rotary piston machine consists of an outer rotor and an inner rotor with fixed axes of rotation rotates in a rotary piston centric bearing shaft with a shaft external teeth centrally within a stator fixed in the housing with a stator internal teeth, wherein between the stator - Internal teeth and the shaft external teeth
  • Rotary piston is arranged, whose rotary piston internal teeth in the shaft outer teeth with
  • the rotary piston performs a rotary motion about its own rotary piston axis, which is spaced parallel but not fixed to the shaft and stator axis.
  • the rotary piston axis thus carries out a complex circular movement about the shaft and stator axis.
  • Axle basically from the simple rotational movements around fixed axes of a gerotor machine.
  • Rotary piston machine also carry the filled with hydraulic fluid tooth chambers between the stator inner teeth and the circular piston external teeth through a circular motion around the shaft, while the tooth chambers are fixed in a gerotor machine in its basis. Therefore, the known in gerotor machines principles of axial displacement the two rotors in a rotary piston engine not applicable.
  • the invention therefore has as its object the
  • the object underlying the invention is to provide a variable volume hydrostatic
  • conventional vehicle transmissions
  • the invention overcomes the above drawbacks while retaining the aforementioned advantages of such high torque hydraulic motors.
  • a rotary piston performs a rotational movement about its own axis and makes this axis a circular motion in the opposite direction of rotation than the rotary piston. That means that in this
  • a meshing width between a rotatable inner rotor and a rotatable outer rotor as generally known in the art. Because with such a
  • the invention represents a further development of the invention
  • the rotary piston machine is received before the
  • hydrostatic rotary piston engine also called
  • low-speed high-torque rotary piston engine may be referred to, comprises acting as an output Power unit in the housing of the rotary piston engine
  • the power section consists essentially of a fixed, centric stator, a
  • the stator has a stator internal toothing with the
  • the rotary piston has a partially engaged in the stator inner teeth of the stator Kreiskolben- external teeth with a number of teeth c and a rotary piston internal teeth with a number of teeth b.
  • the rotary piston has a rotary piston outer diameter.
  • the shaft meshes with its first external shaft teeth with a number of teeth a partially the rotary piston internal teeth of the rotary piston, wherein the rotary piston arranged to perform an orbital movement so eccentric to the shaft axis and
  • An inlet and outlet part is used for supply and disposal of the power unit with the working fluid, wherein the working fluid at a working pressure via a pressure connection, as
  • Input serves, the rotary piston engine can be supplied.
  • the rotary valve is rotatably mounted about the central, longitudinally extending shaft of the geometric shaft axis.
  • the rotary valve is arranged over substantially radially in the rotary valve Pressure window the supply and disposal of the tooth chambers with the working fluid by rotation of the rotary valve so
  • Tooth chambers is directed out to a low pressure port, so that the working pressure in the first part of
  • Toothed chambers leads to an orbit movement of the rotary piston and the working fluid from the second part of the tooth chambers
  • the rotary valve has a specific rotary valve outside diameter, either by the actual
  • Pressure valve radially arranged pressure resistant is determined.
  • the rotary engine comprises a gear transmission in the form of an eccentric gear designed in particular as a wobble gear, which between a second
  • Shaft external teeth of the shaft with a number of teeth w and an internal toothing of a fixed internal gear with a number of teeth z is arranged as a synchronous drive for the rotary valve.
  • the eccentric gear, in particular the wobble gear exclusively in
  • Rotary piston engine which is also connected to the low-pressure port arranged.
  • the shaft is mounted on both sides of the power unit immediately adjacent radial bearings, in particular bearings. Due to the aforementioned structure of the hydrostatic rotary piston engine, a continuous shaft with large shaft diameters and high torsional strength can be used. Thus, it is possible to expose both shaft ends to a high torque flux and, for example, both
  • shaft ends as output, or one shaft end as the output and the other shaft end for connecting a brake or a second drive, whereby the entire
  • eccentric gear in particular designed as a wobble gear eccentric gear has an eccentric, which has an eccentric internal teeth with a number of teeth x and an eccentric external teeth with a number of teeth y.
  • the eccentric internal toothing partially meshes with a second shaft outer toothing of the shaft with a number of teeth w.
  • the eccentric external teeth partially mesh with a fixed internal gear with a number of teeth z.
  • the ratio of the numbers of teeth w, x, y, z is such that the eccentric eccentric to the
  • pot-shaped connecting part is eccentric with the
  • Rotary valve is transferable.
  • the number of teeth a is smaller than the number of teeth b, the number of teeth c smaller than the number of teeth d, the number of teeth w smaller than the number of teeth x and the number of teeth y smaller than the number of teeth z, the respective tooth difference preferably one or two teeth.
  • Tumble angle is correspondingly large. However, then the rotational speed of the eccentricity is relatively small.
  • this ratio is preferably between -3 and -9.
  • the stator internal toothing is formed by circular cylindrical rollers, which leads to further increased pressure performance and excellent service life. Measurements have shown that by the transition to roles in the stator of the starting efficiency and also the stator internal toothing.
  • a rotationally fixed axial second balance piston which acts axially on the rotary valve.
  • the axial second compensating piston is arranged, for example, around the wobble gear.
  • the fixed internal ring gear is in the axial second
  • Balancing piston formed.
  • the force on the rotary valve is applied for example by means of a plate spring.
  • the wheel load Preferably, it should be arranged as close to the center of the wheel. It is advantageous if this bearing is as close as possible to the wheel flange and
  • the shaft is preferably formed integrally with a wheel flange on which a wheel for direct drive is directly mountable.
  • the rotary piston is relative to
  • the first shaft outer teeth of the shaft and the stator inner teeth of the stator extend axially such that the rotary piston inner teeth on the first shaft outer teeth and the outer circular piston teeth on the stator inner teeth can be moved axially.
  • the rotary piston engine adjusting which with the
  • Rotary piston axially to its axial displacement are engaged.
  • Under adjustment means are generally means for axially displacing the rotary piston to understand
  • the adjusting members between the rotary piston and the rolling bearings are left and right axially displaceable.
  • a radially extending second wall of the tooth chambers is axially displaceable together with the rotary piston and axially coupled to the rotary piston.
  • the second wall is the first wall spaced parallel opposite, wherein the
  • Toothed chambers between the first and second wall are arranged and extend there axially.
  • the first wall is formed by a so-called circular piston plate and the second wall by a so-called stator plate.
  • the circular piston plate and the stator plate seal the tooth chambers axially. This means that both between the stator plate and the stator internal teeth and the circular external teeth, as well as between the
  • the rotary piston plate is axial
  • the rotary piston plate coupled radially to the rotary piston has, in the housing, a free mobility in the radial direction and in the circumferential direction corresponding to the orbital movement of the rotary piston plate.
  • the stator plate is axially movable and axially coupled to the rotary piston, but decoupled radially from the rotary piston, so that they so no orbital motion and no rotational movement performs, but is rotationally fixed.
  • Circular piston plate can be downsized and enlarged.
  • the axially fixed circular piston plate engages with its circular piston plate internal teeth in the
  • Rotary piston plate is axially displaceable. Due to the
  • Circular piston plate in the housing so radially sealed is that the circular piston plate seals the tooth chambers outwards during their orbit movement. This happens
  • the circular piston plate is mounted in a disc-like recess in the housing, in particular between a first housing part and a second housing part of the housing, radially movable and radially sealing.
  • the radial sealing takes place in particular by means of a stator adjacent to the radially outward
  • the axially movable stator plate preferably engages with its stator outer teeth in the stator inner toothing in the axial direction sealing manner a precise fit.
  • the stator plate external teeth and the stator internal teeth have the same number of teeth d and essentially the same
  • stator plate is axially displaceable relative to the axially fixed stator together with the rotary piston. Due to the fit of the stator plate
  • Stator plate external teeth with the stator internal teeth are both in axially sealing, but axially movable contact.
  • a compensating piston is axially coupled to the stator plate. It is possible to integrally form the stator plate and the balance piston.
  • the balance piston engages in an axial
  • the balance piston is arranged in the fixed housing and acted upon by the working pressure of the working fluid of the tooth chambers, by a direct or indirect connection between the Compensating cylinder and the pressure connection exists.
  • Pressurization takes place in such a way that the working pressure in the compensating cylinder over the stator plate at least partially counteracts the working pressure in the tooth chambers and thus a force on the rotary piston in the direction of a
  • Dental chambers acts.
  • a first force resulting from the working pressure in the first part of the tooth chambers acts on the opposite other side of the stator plate, a second force resulting from the working pressure in the first
  • Balancing cylinder results, exercised. These two forces counteract each other and partially compensate, so that the axial holding and adjusting force of the rotary piston is reduced.
  • the balance piston and the balance cylinder have
  • a ring shape for example, a ring shape and in particular extend around the shaft. Preferably, they are between the
  • Balancing cylinder to be reversed. Under a Balancing piston is thus according to the invention also a
  • the adjusting members are designed as a control piston which is axially engaged with the rotary piston.
  • the control piston is so axially coupled to the rotary piston, that the rotary piston by means of the control piston is axially displaceable.
  • the control piston engages in an axial control cylinder arranged in the fixed housing such that a force can be exerted on the rotary piston for axial displacement of the rotary piston and for changing the volume of the tooth chambers.
  • the control cylinder can be acted upon by a control pressure.
  • the control piston can be acted upon by a control pressure.
  • Control cylinder and the control piston arranged such that the rotary piston is displaced by the pressurization in the control cylinder in a direction such that the
  • Control pressure an increase in the volume of the dental chambers.
  • control piston and the control cylinder may be arranged annularly in the housing around an output section of the shaft in a ring-shaped manner, wherein the output section corresponds to that
  • a radially extending intermediate disc is arranged between the control piston and the rotary piston.
  • the rotary piston slides in
  • the control piston is arranged, for example, such that it presses the rotary piston in particular via this washer against the opposite balance piston and in particular against the control springs.
  • the working pressure in the compensating piston counteracts the control pressure in the control piston kinematically.
  • control pressure in the control cylinder can in a possible variant of the invention by the working pressure of
  • Working fluids are generated.
  • the control piston can be acted upon by the working pressure of the working fluid.
  • the control pressure is equal to the working pressure.
  • the effective surfaces of the control cylinder, the control piston, the stator plate, the rotary piston plate and optionally the compensating cylinder and the balance piston are in this case preferably dimensioned such that the control cylinder with increasing torque on the driven shaft and thus with increase in working pressure the rotary piston in the direction of an enlarged Volume of the tooth chambers presses.
  • Control pressure connection acts on the control piston.
  • Control pressure can be varied.
  • the control piston can be acted upon, in particular by means of a valve, either with the working pressure of the working fluid or with a control pressure from the control pressure port.
  • the hydrostatic rotary piston machine according to the invention can be used not only as a motor for generating an output, but is also excellently suitable as a pump.
  • the hydrostatic rotary piston engine has the great advantage that a recuperative
  • Brake energy recovery is possible by the specially designed as a wheel motor hydraulic motor is switched in the case of braking to a pumping operation and receives torque. This sucks hydrostatic
  • Rotary piston engine the working fluid from the tank and promotes this under pressure in one or more
  • Hydraulic accumulator The stored energy can be stored in the
  • Suction volume of the rotary piston engine can therefore change, in particular reduced, when there is a change from traction mode to overrun mode, which is also called suction or pumping mode in particular to reduce the risk of cavitation in suction operation.
  • the rotary valve As large as possible.
  • the rotary valve outer diameter is larger by a factor of 1.3 to 1.5 than the outer diameter of the rotary piston.
  • the inventive hydrostatic rotary piston engine can thus as an economic direct drive, in particular
  • Hub drive with recuperative braking energy recovery can be used in a vehicle.
  • volume-variable hydrostatic rotary piston engine will be explained below purely by way of example with reference to the figures 1 to 8, which illustrate concrete embodiments, to which the invention is not limited.
  • Figure 2 is a same longitudinal section in the position of
  • Figure 4 shows a cross section along the section line B-B of
  • Figure 1 which shows the non-axially movable, but together with the rotary piston an orbital movement exporting circular piston plate, which is hatched from bottom right to top left, in cross section; a longitudinal section through the wheel motor in the range of required pressure lines to
  • Fig. 7 shows a longitudinal section through the wheel motor in the region of the required pressure lines to
  • Fig. 8 is a longitudinal section through an alternative
  • Working fluid in the form of a working fluid is
  • I connected outer annular space 2 is applied to a disk-shaped rotary valve 3 with pressure, as shown in Figure 1.
  • the disk-shaped rotary valve 3 is a
  • Shaft axis 50 of a shaft 11 centrally rotatable and to the shaft
  • the power unit 51 has a center fixed stator 52 having one
  • the power unit 51 includes the centered about the shaft axis 50 rotatably mounted Wave 11 with a partial in the
  • the rotary piston 8 is thus for performing an orbital movement
  • the rotary valve 3 ver and disposed of the tooth chambers 6 via axial channels 4 and radial channels 5 in the stator 52 with the working fluid such that the working fluid of the as
  • the rotary valve 3 has as large a size as possible
  • Rotary valve outer diameter 69 as shown in Figures 1, 2 and 7 can be seen.
  • the Drehventil- outside diameter 69 is larger by a factor of 1.3 to 1.5 than the outer diameter of the rotary piston 68. Since the rotary valve 3 together with windows 7 ensures that, for example, in Figure 3, only the first part 6a of the tooth chambers 6 is applied to the left of the axial distance DD with working pressure, the rotary piston 8 rotates in Figure 3 in
  • the torque can be tapped via a driven out of the housing 19 output-side portion 65 of the shaft 10.
  • the rotary piston 8 and the shaft 10 rotate in the same direction, as shown
  • Embodiment in the clockwise direction as illustrated in Figure 3 by the two arrows.
  • the rotary valve 3 is in a known manner by means of a
  • Rotary valve 3 is used, driven.
  • the wobble mechanism 56 has an eccentric internal toothing 58 with a number of teeth x and an eccentric external toothing 59 with a number of teeth y.
  • the eccentric internal toothing 58 meshes with a second shaft outer toothing 60 of the shaft 11 with a number of teeth w.
  • the eccentric external teeth 59 meshes with a fixed internal gear ring 61 with a number of teeth z.
  • the numbers of teeth w, x, y, z are dimensioned such that the eccentric 57 performs eccentric to the shaft axis 50 between the shaft 11 and the inner ring gear 61 during rotation of the shaft 11 an orbital movement. Possible number of teeth combinations can be found in the above statements.
  • a pot-shaped connecting part 62 is rotatably coupled to the eccentrically rotatable eccentric 57 at one end. Otherwise it is
  • the shaft 11 is radially mounted on both sides of the power section 51 adjacent radial bearings 63, which are designed as rolling bearings in O arrangement.
  • a rotationally fixed axial second compensating piston 55 which acts axially on the rotary valve 3, arranged around the wobble gear 56.
  • Circular external gear teeth 12 and the stator internal teeth 13 is.
  • the stator internal teeth is shown in the form of rollers 13, which is a particularly advantageous embodiment of this tooth shape
  • Shaft axis 50 axially displaceable.
  • the displaceability is made possible by adjusting members 22, which are in engagement with the rotary piston 8 and by means of which same axially
  • the tooth chambers 6 are arranged in the axial direction between an axially fixed circular piston plate 17 and an axially movable stator plate 14. They are by the circular piston plate 17 and the
  • Stator plate 14 axially limited and sealed.
  • Circular piston plate 17 is axially fixed and radially coupled to the rotary piston 8. Thus, it performs the orbital motion of the rotary piston 8 together with the rotary piston 8.
  • the stator plate 14 is axially movable, axially with the
  • Rotary piston 8 coupled and radially from the rotary piston. 8
  • the volume of the tooth chambers 6 is thus continuously variable by the axial displacement of the rotary piston 8 and the stator plate 14 by means of the adjusting members 22.
  • This Balancing piston 15a is arranged in the stationary housing 19 and can be acted upon by the working pressure of the working fluid of the toothed chambers 6.
  • the compensating piston 15a engages in an axial - in particular annular - compensating cylinder 15b in such a way that the working pressure in the compensating cylinder 15b via the stator plate 14 to the
  • Dental chambers 6 acts. Between the compensating piston 15a and the compensating cylinder 15b act control springs 16 which press the compensating piston 15a axially against the rotary piston 8 and thus the rotary piston 8 in the direction of a starting position with a reduced volume of the tooth chambers 6.
  • Tooth engagement between the circular piston external teeth 12 and the stator inner teeth 13 is particularly bulky, so that accordingly a large displacement per
  • Rotary piston 8 moved to the right.
  • the control springs 16 are completely compressed and thereby generate the highest possible axial force on the stator plate 14.
  • stator plate 14 In FIG. 2, the stator plate 14 is in its left limit position.
  • the control springs 16 are largely relaxed, corresponding to a low pressure in the tooth chambers 6.
  • the effective width of the tooth engagement between the rotary piston External teeth 12 and the stator inner teeth 13 is greatly reduced. This results in the desired strong reduction of the specific amount of swallowing in the ratio of the reduced effective tooth width to the maximum effective tooth width in FIG. 1. The transition from the maximum
  • Figures 1 and 2 is performed by the circular piston plate 17.
  • This has a circular piston plate internal teeth 18, which corresponds exactly to the circular piston external teeth 12 of the rotary piston 8, wherein a movement of a few hundredths of a millimeter is provided, so that a high degree of tightness between the tooth chambers. 6 and the non-pressurized interior of the machine.
  • This running clearance need not be greater than that it is ensured that the rotary piston is axially displaceable therein.
  • This circular piston plate 17 must thus join the orbit movement of the rotary piston 8 with as little friction loss. It is not axial
  • Circular piston plate 17 is thus in a disc-like
  • Figure 5 shows a cross section through the axial center of this circular piston plate 17, into which a groove 20 is radially inserted from the outside, so that by the orbital movement of the Circular piston plate 17 between a housing ring 21 displaced viscous working fluid does not generate excessive crushing losses.
  • the adjusting members 22 are, as shown in Figures 1 and 2, as an annular centric to the
  • Control piston 22 a formed, which is axially in engagement with the rotary piston 8 via a radially extending washer 66, as shown in Figures 1 and 2.
  • the control piston 22a is arranged such that it presses the rotary piston 8 against the compensating piston 15a and against the control springs 16 via the intermediate disc 66.
  • an axial control cylinder 22 b is arranged, which is acted upon by a control pressure and in which the control piston 22 a engages such that by means of the control pressure in the control cylinder 22 b, a force on the rotary piston 8 for axial displacement of the rotary piston 8 can be exercised. Because of this
  • Both the control piston 22a and the control cylinder 22b annularly surround the output section 65 of the shaft 11 in an annular manner.
  • Circular piston plate 17 and thus also on the rotary piston 8. To avoid tilting and resulting large frictional forces, it is necessary for both the rotary piston 8 and in particular for the stator plate 14 with her
  • Balance piston 15 a good leadership relationship. Therefore, it is preferable that the balance piston 15a is fixedly connected to the stator plate 14 to improve the guide ratio. Furthermore, it is desirable to constructively, as well as the tooth engagement between the rotary piston internal teeth 9 and the first shaft external teeth 10 as long as possible out.
  • channels 71 are shown in which the
  • the rotary piston engine has a control pressure port 67 which is connected to the control cylinder 22b via lines such that the control piston 22a can be acted upon with a control pressure from the control pressure port 67.
  • a separate pressure line with a control pressure connection 67 is provided for the supply of the regulating piston 22a.
  • the amount of swallowing calculated increases the torque of the
  • Rademotors disproportionately to increase the pressure, so that the traction of the drive increases accordingly dramatically.
  • This automatism can be modified by the design of the core lines of the control springs 16.
  • the supply pump which supplies the working fluid to the pressure port 1, which is driven for example by an internal combustion engine, automatically reduces the output speed of the rotary piston engine and thus the input speed of the wheels.
  • converter is better than the hydrodynamic converter, since the oil flow losses are smaller.
  • FIG. 8 shows an alternative embodiment of a volume-variable hydrostatic head according to the invention
  • Rotary piston engine with a along the shaft axis 50 elongated rotary piston 8, an elongated shaft 11, a longer control piston 22a and a longer
  • Control cylinder 22b and a greater distance from
  • Figure 9 shows a longitudinal section through a complex
  • Balancing cylinder 15b and the control springs 16 are moved radially outward and the eccentric 56 is designed as a classic Exzentergetiebe with an alternative 1: 1- connection to the rotary valve.
  • Eccentric 56 has an eccentric 57 with a
  • the eccentric internal teeth 58 meshes with a second shaft outer teeth 60 of the shaft 11.
  • the eccentric external teeth 59 meshes with a
  • Shaft axis 50 between the shaft 11 and the inner ring gear 61 during rotation of the shaft 11 performs an orbit movement.
  • a cup-shaped connecting part 62 is rotatably connected to the eccentrically rotatable eccentric 57 at one end
  • the cup-shaped connecting part 62 is connected in a rotationally fixed manner via an eccentric connection to the centrically rotatable rotary valve 3. A rotational movement of the shaft 11 is thus transmitted via the eccentric 57 to the rotary valve 3.
  • the invention is not limited to the exemplary embodiments shown schematically and illustrated here in the drawings.
  • a kinematic reversal is possible according to the invention, in which the shaft 11 is stationary and the housing 19 rotates, which at

Abstract

L'invention concerne une machine hydrostatique à piston rotatif selon le principe orbital, présentant un élément de puissance (51) servant de sortie et muni d'un stator fixe (52), un piston rotatif (8) et un arbre monté rotatif (11), le piston rotatif (8) étant disposé de manière excentrique par rapport à l'arbre (11) afin d'effectuer un mouvement orbital. Le mouvement de rotation du piston rotatif (8) et de l'arbre (11) est produit par le fait qu'un fluide de travail (6) est apporté, au moyen d'un tiroir tournant (3), à des chambres de dents (8) formées entre le stator (52) et le piston rotatif (8) et en est évacué. Selon l'invention, on peut modifier le volume des chambres de dents (8) et donc le volume d'admission de la machine à piston rotatif. A cet effet, le piston rotatif (8) peut être déplacé axialement par rapport au stator (52) au moyen d'organes de réglage. Les chambres de dents (6) sont étanchées en direction axiale par une plaque de piston rotatif (17) axialement fixe et radialement couplée au piston rotatif (8) et par une plaque de stator (14) axialement couplée au piston rotatif (8) et radialement désaccouplée du piston rotatif (8), le volume des chambres de dents (6) pouvant être modifié en continu par le déplacement axial du piston rotatif (8) et de la plaque de stator (14) au moyen des organes de réglage (22). Le volume d'admission variable permet à la fois un fonctionnement économique en tant que moteur, le volume d'admission s'adaptant au besoin momentané de puissance et de couple et les pertes hydrauliques pouvant ainsi être réduites, et un fonctionnement en tant que pompe pour l'utilisation par récupération de l'énergie de freinage, la cavitation pouvant être évitée en mode pompe par l'adaptation du volume d'admission en fonction de la vitesse de rotation. La machine à piston rotatif convient ainsi entre autres en tant que moteur de roue pour l'entraînement hydraulique direct d'un véhicule avec récupération de l'énergie de freinage.
EP11727168.4A 2010-06-23 2011-06-21 Machine hydrostatique à piston rotatif à volume variable en continu Withdrawn EP2585719A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11727168.4A EP2585719A2 (fr) 2010-06-23 2011-06-21 Machine hydrostatique à piston rotatif à volume variable en continu

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP10166995 2010-06-23
PCT/EP2011/060372 WO2011161117A2 (fr) 2010-06-23 2011-06-21 Machine hydrostatique à piston rotatif à volume variable en continu
EP11727168.4A EP2585719A2 (fr) 2010-06-23 2011-06-21 Machine hydrostatique à piston rotatif à volume variable en continu

Publications (1)

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EP2585719A2 true EP2585719A2 (fr) 2013-05-01

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EP (1) EP2585719A2 (fr)
WO (1) WO2011161117A2 (fr)

Cited By (1)

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EP3441613A1 (fr) * 2017-08-07 2019-02-13 Siegfried A. Eisenmann Machine hydrostatique à pistons rotatifs et à engrenage

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CN102720630B (zh) * 2012-06-08 2014-09-24 燕山大学 双转子壳体转动凸轮连杆滚柱多速马达
CN102828895B (zh) * 2012-09-07 2015-10-21 镇江大力液压马达股份有限公司 径向支撑轴阀配流摆线液压马达
DE102014015809A1 (de) 2014-10-24 2016-04-28 Man Truck & Bus Ag Hydraulischer Radantrieb für ein Kraftfahrzeug und Verfahren zu dessen Betrieb
DE202017006651U1 (de) 2017-12-27 2018-03-01 Siegfried Alexander Eisenmann Stufenlos regelbare hydrostatische Kreiskolbenmaschine

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US3805526A (en) * 1972-11-03 1974-04-23 Aplitec Ltd Variable displacement rotary hydraulic machines
CH701073B1 (de) * 2004-07-22 2010-11-30 Siegfried A Dipl-Ing Eisenmann Hydrostatischer Kreiskolbenmotor.
EP2235374B1 (fr) 2008-01-21 2011-07-20 Siegfried A. Eisenmann Pompe à engrenage intérieur, à volume variable

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3441613A1 (fr) * 2017-08-07 2019-02-13 Siegfried A. Eisenmann Machine hydrostatique à pistons rotatifs et à engrenage

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WO2011161117A3 (fr) 2013-01-03
WO2011161117A2 (fr) 2011-12-29

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