EP3441613A1 - Machine hydrostatique à pistons rotatifs et à engrenage - Google Patents

Machine hydrostatique à pistons rotatifs et à engrenage Download PDF

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Publication number
EP3441613A1
EP3441613A1 EP17185063.9A EP17185063A EP3441613A1 EP 3441613 A1 EP3441613 A1 EP 3441613A1 EP 17185063 A EP17185063 A EP 17185063A EP 3441613 A1 EP3441613 A1 EP 3441613A1
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EP
European Patent Office
Prior art keywords
teeth
shaft
rotary piston
hydrostatic
toothing
Prior art date
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Granted
Application number
EP17185063.9A
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German (de)
English (en)
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EP3441613B1 (fr
Inventor
Siegfried A. Eisenmann
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Individual
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Individual
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    • 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
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the invention relates to a hydrostatic geared rotary piston machine according to the orbit principle according to the preamble of claim 1.
  • Such a hydrostatic rotary piston engine according to the preamble is in the EP 1 776 525 A1 described.
  • a hydrostatic rotary piston engine is known from the EP 0 367 046 A1 ,
  • the working spaces between the teeth of the rotary piston and the stator are controlled by a drum-shaped rotary commutator.
  • the drive of this rotary commutator takes place there via a circular arc gear, which transmits the speed of the rotary piston to the speed of the rotary commutator 1: 1.
  • This rotary commutator is mounted radially in the machine housing with a necessary radial running clearance.
  • the working pressures of such rotary engines have increased to such an extent that such a constant relatively large clearance no longer meets the volumetric requirements.
  • the drive is over such circular arc gear subject to excessive backlash, so that thereby suffers the rotation angle accuracy between the rotary piston and the rotary commutator.
  • An exact drive of the rotary commutator, also referred to as a rotary valve and thus a high level of operational reliability at high working pressures over a long period are therefore not guaranteed without restriction.
  • Another disadvantage is also in the relatively complex construction of the machine.
  • a centrically mounted shaft rotates with a shaft external teeth centrally within a stationary stator in the housing with a Stator internal toothing, wherein between the stator inner toothing and the shaft outer toothing, a rotary piston is arranged, engage the rotary piston internal teeth in the shaft outer toothing with different numbers of teeth and its outer circular toothing in the stator inner toothing with different numbers of teeth.
  • 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.
  • Upon rotation of the shaft of the rotary piston performs an orbit movement about the shaft axis in the region between the stator inner teeth and the shaft outer teeth.
  • the rotary piston axis thus carries out a complex circular movement about the shaft and stator axis.
  • the orbit movement ie the rotational movement about an axis rotating in a circular path
  • fundamentally differs from the simple rotational movements about fixed axes of a gerotor machine.
  • the toothed chambers filled with hydraulic fluid also circulate around the shaft between the stator inner toothing and the outer circular toothing, while the toothed chambers of a gerotor machine are fixed in their foundation.
  • the object of the invention is to provide a hydrostatic geared rotary piston machine, which is characterized on the one hand by a compact and relatively simple design, on the other hand by a high performance potential, an accurate drive of the rotary valve and high reliability even at high working pressures.
  • the combination of these properties currently applies in the prior art as a conflict of goals.
  • a particular axial play compensated disk-shaped rotary valve of the known design is used according to the invention and the drive of this rotary valve is improved by an almost backlash-free, toothed, cup-shaped swash sleeve, which has a large diameter surrounds stable and continuous wave.
  • the internal gear between the shaft and the rotary piston is also optimized for the highest possible displacement per shaft revolution.
  • the aforementioned machine is usable for much higher working pressures and the kinematic drive ratios for the disc-shaped rotary valve compared to the mentioned known machine much more precise angle, easier and cheaper.
  • the dimensions and thus the weight of the machine by at least 15% are reduced, which also contributes to a reduction in manufacturing costs.
  • the compactness of the construction according to the invention is unsurpassed.
  • the invention represents a further development of the hydrostatic rotary piston engines known from the prior art, for which reason the general basic structure of the hydrostatic rotary piston engine according to the invention, which is already essentially known from the prior art, will be discussed below, before the features according to the invention are explained.
  • a rotary piston machine according to the orbit principle, wherein an internally toothed stator is fixed in space, a rotary piston performs a rotational movement about its own axis and makes this axis a circular movement in the opposite direction of rotation than the rotary piston.
  • the hydrostatic rotary piston engine which can also be referred to as a low-speed high-torque rotary piston engine in particular, comprises a power unit acting as an output, which is arranged in the housing of the rotary piston engine or forms a logical section of the housing or the machine.
  • the power unit is essentially composed of a fixed, central stator, a movable rotary piston and a portion of a centrally rotatably mounted, serving as an output shaft engaging with the rotary piston.
  • the stator has a stator internal toothing with the number of teeth Z4.
  • the rotary piston has a partially engaged in the stator inner teeth of the stator circular external piston teeth with a number of teeth Z3 and a circular piston internal teeth with a number of teeth Z2.
  • the shaft meshes with its first external shaft teeth with a number of teeth Z1 partially the rotary piston internal teeth of the rotary piston, wherein the rotary piston for performing an orbit movement is arranged and dimensioned eccentric to the shaft axis and the teeth numbers Z1, Z2, Z3, Z4 in such a ratio stand each other, that form with working fluid ver and disposable tooth chambers between the stator inner teeth of the stator and the circular piston outer teeth of the rotary piston.
  • the hydrostatic gear rotary piston machine thus comprises a stator provided with a stator internal toothing, stationary stator with the number of teeth Z4 and within the stator - to perform an eccentricity orbiting orbital movement - eccentrically arranged rotary piston, which partially into the stator Internal teeth engaging rotary piston outer teeth having a number of teeth Z3, wherein the number of teeth difference between the number of teeth Z4 and the number of teeth Z3 is one. Z4 minus Z3 is 1.
  • a circular piston internal toothing with a number of teeth Z2 is arranged in the interior of the rotary piston.
  • a circular piston internal toothing with a number of teeth Z2 is arranged.
  • Centrally to the stator is arranged about a shaft axis rotatably mounted shaft.
  • On the shaft turn a partially engaging in the circular piston internal toothing shaft outer toothing is arranged with a number of teeth Z1.
  • Tooth chambers are arranged radially between the stator inner teeth and the outer circular teeth and are of the stator inner toothing and the outer circular toothing radially limited in the radial direction and sealed substantially by the engagement of these teeth.
  • a disk-shaped rotary valve which is mounted centrically running to the shaft and the stator, the control of the supply and disposal of the tooth chambers with the working fluid.
  • the rotary valve is rotatably mounted about the central, longitudinally extending shaft of the geometric shaft axis.
  • the rotary valve itself thus does not orbit movement, but rotates about the shaft axis.
  • the supply and disposal of the tooth chambers with the working fluid by rotation of the rotary valve is commutated so controlled over substantially radially in the rotary valve pressure window that the working fluid from the pressure port into a first part of the tooth chambers with the working pressure into and out of a second Part of the tooth chambers is passed out to a low pressure port, so that the working pressure in the first part of the tooth chambers leads to an orbit movement of the rotary piston and the working fluid displaced from the second part of the tooth chambers, whereby the shaft is set in rotation, and vice versa.
  • the disk-shaped rotary valve is rotatable centrically about the shaft axis and mounted centrically running to the shaft and the stator.
  • the disk-shaped rotary valve is for commutating the supply and disposal of the tooth chambers with the working fluid for introducing working fluid into a first part of the tooth chambers with the working pressure and for discharging the working fluid from one second part of the tooth chambers designed to generate the output and connected to the tooth chambers.
  • the shaft is supported by radial bearings, in particular rolling bearings.
  • a main bearing On a shaft output side of the shaft, a main bearing is arranged.
  • a shaft opposite side On a shaft opposite side, which is located at the other end of the shaft - the shaft output side opposite - is arranged a sub-camp.
  • the main bearing and / or the auxiliary bearing are in particular designed as radial bearings, as rolling bearings, as roller bearings or preferably as tapered roller bearings, in particular in X-arrangement.
  • a torsionally rigid hydrostatic axial balance piston for axial backlash the disc-shaped rotary valve, which acts axially on the rotary valve.
  • the axial balance piston is arranged around the shaft.
  • the hydrostatic geared rotary piston engine has a housing, which is logically, ie with respect to individual functional sections, divided into several parts. These parts are not necessarily to be understood as separate or separable pieces, but as logical sections. Thus, it is possible to form several parts in one piece or individual parts in several pieces. In a preferred embodiment, however, the individual housing parts are each designed as a separable housing piece.
  • the housing is divided at least into a driven-side housing part, an inlet and outlet housing part and an axially in the axial direction, ie along the shaft axis, viewed intermediate power section, and in particular an axially disposed between the inlet and outlet housing and the power unit control plate.
  • the output-side housing part comprises the main bearing.
  • the main bearing is arranged radially between the driven-side housing part and the shaft output side of the shaft. From the driven-side housing part, the shaft output side of the shaft and the local shaft end are led out of the housing.
  • the inlet and outlet housing part Seen in the axial direction on the output side housing part opposite side of the housing is the inlet and outlet housing part.
  • This 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 port, which serves as an input, the rotary piston engine can be supplied.
  • the inlet and outlet housing part comprises the disk-shaped rotary valve, which is rotatably mounted therein about the shaft axis.
  • the inlet and outlet housing part includes connections and Channels, which are designed for supply and disposal of the disc-shaped rotary valve with the working fluid.
  • the inlet and outlet housing part in particular comprises the balance piston.
  • the seen in the axial direction between the driven-side housing part and the inlet and outlet housing part arranged power part acts as a drive of the machine to include the stator, the rotary piston, the tooth chambers and the shaft outer teeth.
  • the control plate includes windows and control plate channels to guide the working fluid substantially in the axial direction from the disc-shaped rotary valve to the tooth chambers.
  • the housing parts are clamped together by means of axially extending screws.
  • the auxiliary bearing in the inlet and outlet housing part and the disk-shaped rotary valve are arranged in the axial direction between the power unit and the sub-camp. Axial between the main bearing and the sub-camp are thus the power unit and the rotary valve, and in particular the hydrostatic axial compensating piston, and a cup-shaped sleeve.
  • This cup-shaped sleeve which is also referred to below as a wobble sleeve, is arranged radially around the shaft and extends from this radially spaced apart in the axial direction.
  • the cup-shaped sleeve surrounds the shaft axis and the shaft wobbling, since it is rotatably mounted one end about the shaft axis, the other end about the rotary piston axis.
  • the sleeve extends viewed in the axial direction between the power unit and the input and Auslassgepurteil in the housing and is in particular passed freely through the control plate.
  • the sleeve has a first outer sleeve toothing and a second outer sleeve toothing.
  • the first sleeve external teeth engages with a number of teeth Z5 on the side of the power unit in the rotary piston internal teeth and meshes them.
  • the number of teeth Z5 of the first sleeve external teeth is equal to the number of teeth Z2 of the rotary piston internal teeth.
  • the second outer sleeve toothing engages with a number of teeth Z6 on the side of the inlet and outlet housing part in a rotary valve internal toothing of the rotary valve and meshes with the rotary valve internal toothing has the number of teeth Z7.
  • the number of teeth Z6 of the second external sleeve toothing is equal to the number of teeth Z7 of the rotary valve internal toothing.
  • the sleeve and its teeth are designed to tumble 1: 1 rotary coupling between the rotary piston and the disk-shaped rotary valve and allows the rotary valve with the speed of the rotary piston, which, however, in relation to the rotary valve to another, rotating in space axis - the rotary piston axis - turns to drive.
  • the number of teeth difference between the number of teeth Z2 and the number of teeth Z1 is 2.
  • Z2 minus Z1 equals 2.
  • the cup-shaped sleeve may be cylindrical or conical, but may also have any other shape which at least partially surrounds the shaft and at one end has said first sleeve external teeth and the other end said second sleeve external teeth.
  • the cup-shaped sleeve may also have a grid structure.
  • the number of teeth Z3 to the number of teeth Z4 has the values 10:11 or 11:12 or 12:13, and / or the number of teeth Z1 has the values 15 to the number of teeth Z2 : 17 or 16:18 or 17:19.
  • the number of teeth Z3 to the number of teeth Z4 preferably has the value 11:12 and the number of teeth Z1 to the number of teeth Z2 the value 16:18.
  • hydrostatic axial compensating piston is seen in the axial direction between the disk-shaped rotary valve and the sub-bearing in the inlet and outlet housing part.
  • volumetric efficiency is always a significant factor as it significantly affects overall efficiency.
  • the influencing variables on the volumetric efficiency are among others the axial leakage gaps of the rotary piston to the side walls. If, for example, the axial running play is chosen to be too small, the machine runs the risk that the rotary piston will jam axially at a higher temperature, so that there is a risk of eating while the mechanical efficiency drops. Desirable is thus a compliance of at least one side wall in the machine housing. This flexibility would have without special measures, however, that the internal hydraulic axial forces increase the axial play again because of the smaller stiffness of this side wall.
  • a control plate - with windows and control plate channels between the tooth chambers and the disc-shaped rotary valve - arranged for supply and disposal of the tooth chambers with the working fluid is designed compliant.
  • the latter is achieved in particular by the fact that the thickness in the axial direction of the control plate and / or the material thereof are such that the axial running play of the rotary piston between the driven-side housing part and the inlet and outlet housing part decreases or remains the same with increasing working pressure of the working fluid.
  • the invention thus provides to make this control plate much thinner because of the required axial compliance, but to support them on the opposite side with sufficiently large hydraulic compensation surfaces. These are present when the axial saddleden Compensation surfaces on the rotary valve are large enough. Accordingly, the compensation surface of the Balance piston have an overcompensated size. If these hydraulic compensation surfaces on the control plate are overcompensated to a sufficient extent, for example by 10 to 15%, there is the possibility that with increasing working pressure, the axial play of the rotary piston between its side walls is smaller. Since the axial leakage current according to the law of Hagen-Poiseuille decreases with the cube of the leakage gap reduction, the volumetric efficiency can be improved, especially at high working pressure.
  • the compliance of the control plate can also be influenced by the selection of the material used for it.
  • plain bearing materials such as lead bronze or brass alloys
  • high-strength ones Aluminum plain bearing alloys in question.
  • these have the great advantage that emergency running properties significantly improve the sliding conditions.
  • the much lower modulus of elasticity of these materials increases their above-mentioned compliance.
  • the compliance of the control plate can be influenced by the selection of the thickness of the plate.
  • the plate stiffness is proportional to the cube of the plate thickness, inversely proportional to the elastic modulus of the plate material.
  • the deflection of the circumferentially clamped annular plate can be calculated relatively easily, if the differential force is known.
  • the deflection at the inner edge of the circular ring plate which is here.
  • the shaft output side of the shaft is therefore formed in an advantageous embodiment as a cone for mounting a wheel flange by means of an axial nut to form a compact wheel motor.
  • stator internal toothing is formed by rotatable, in particular circular cylindrical rollers, which leads to further increased pressure performance and excellent service life and whereby the Anfahr fürsgrad and also the mechanical-hydraulic efficiency can be significantly increased.
  • the wave external teeth of the shaft is conical in a development with a smaller diameter amount seen in the axial direction formed on its shaft output side, as explained in more detail in the embodiments.
  • an aspect of the invention provides that a tooth head shortening is provided on the tooth head of the shaft external teeth by mathematically provided at the points and the tooth head, where the teeth are disengaged, the tooth flank radius is greater than at the point of the deepest tooth engagement, whereupon will be discussed in more detail in the embodiments.
  • a development of the invention comprises a hydrostatic geared rotary piston engine in the form of a Geared double-circle piston machine, which is composed of two coupled hydrostatic geared rotary piston engines. These two hydrostatic geared rotary piston engines each correspond to one of the hydrostatic geared rotary piston engines according to the invention.
  • the shaft opposite side of the shaft of the first hydrostatic geared rotary piston engine is coupled to the shaft opposite side of the shaft of the second hydrostatic geared rotary piston engine axially - in particular by means of a sleeve - and torque-effectively connected.
  • the first hydrostatic geared rotary piston engine and the second hydrostatic geared rotary piston engine have, in particular, different absorption rates, in particular differently dimensioned toothed chambers.
  • a first toothed-gear toothing on the shaft opposite side of the shaft of the first hydrostatic gear rotary piston machine and a corresponding second toothed-toothed teeth of the second hydrostatic gear rotary piston engine are each connected torque-effective with the sleeve.
  • This sleeve is supported in particular radially by a common roller bearing in the inlet and outlet housing part of the first hydrostatic gear-type rotary piston engine and in the inlet and outlet housing part of the second hydrostatic gear-type rotary piston machine.
  • the rolling bearing is designed as a centering of the first hydrostatic geared rotary piston engine with the second hydrostatic geared rotary piston engine.
  • FIG. 1 shows a longitudinal section through a first embodiment of the hydrostatic gear rotary piston engine
  • FIG. 2 shows a cross section through the power section of this machine. The two FIGS. 1 and 2 will be described together below.
  • the hydrostatic gear rotary piston machine has a provided with a stator inner teeth 1 centric fixed stator 2 with the number of teeth Z4 equal to 12, and a within the stator 2, for carrying out an eccentricity e circular orbital motion, eccentrically arranged rotary piston 4th which partially engages in the stator inner teeth 1
  • Rotary external external toothing 3 with a number of teeth Z3 equal to 11 has.
  • the number of teeth difference between the number of teeth Z4 equal to 12 and the number of teeth Z3 equal to 11 is 1, as in FIG. 2 seen.
  • the stator inner teeth 1 is formed as a rotatable rollers.
  • a circular piston internal toothing 5 is formed with a number of teeth Z2.
  • a shaft 6 is arranged centrically to the stator 2 and rotatably mounted about a geometric shaft axis 52 in a tapered roller main bearing 9 and a tapered roller sub-bearing 11.
  • a shaft external toothing 7 is formed with a number of teeth Z1, which partially engages in the rotary piston inner toothing 5.
  • the geometric shaft axis 52 is thus also the geometric axis of the shaft outer toothing 7, the stator 2 and the stator inner toothing 1.
  • the number of teeth difference between the number of teeth Z2 and the number of teeth Z1 is 2.
  • the tooth chambers 53a, 53b formed by the number of teeth difference between the number of teeth Z4 and the number of teeth Z3 between the stator inner teeth 1 and the outer circular teeth 3 are radially formed by the stator inner teeth 1 and the outer circular teeth 3, as in FIG FIG. 2 shown, and axially from a driven side wall 58 and opposite from a control plate 25, as in FIG. 1 shown, essentially sealed limited.
  • the stator 2, the rotary piston 4, the tooth chambers 53a, 53b and the shaft outer toothing 7 form the power part 51 of the housing 24 which acts as a drive.
  • the tapered roller main bearing 9 On a shaft output side 8 of the shaft 6, the tapered roller main bearing 9 is arranged while on a the shaft output side 8 at the other end of the shaft 6 opposite shaft opposite side 55, the tapered roller sub-bearing 11 is located.
  • FIG. 1 the extremely stable design of the shaft 6 is shown, wherein the driven side main tapered roller bearing 9 is selected with a particularly high load rating. This is very close to the meshing between the rotary piston 4 and the shaft outer teeth 7 of the shaft 6 arranged for the smallest possible deflection of the shaft 6 by the tooth force, since the tapered roller sub-bearing 11 is placed at the utmost possible distance thereof. At maximum working pressure, at the point of meshing, the amount of shaft deflection should not exceed the value of 15 to 20 microns.
  • FIG. 1 shown is an inlet and outlet housing 54 of the housing 24, which a driven-side housing part 10, left in FIG. 1 , Seen in the axial direction opposite.
  • the inlet and outlet housing part 54 includes a disc-shaped rotary valve 12 and ports 21 and 22 and channels 56 for supply and disposal of the disc-shaped rotary valve 12 with working fluid.
  • the disc-shaped rotary valve 12 is rotatably centered about the shaft axis 52 and centered on the shaft 6 and the stator 2 in the inlet and outlet housing part 54 between the power unit 51 and the tapered roller sub-bearing 11 and serves for the commutating control of the supply and disposal of the tooth chambers 53a, 53b with the working fluid for introducing working fluid into a first part 53a of the tooth chambers at a working pressure and for discharging the working fluid from a second part 53b of the tooth chambers to produce the output.
  • the rotary valve 12 is for connecting a first part 53a of the circular tooth chambers with one of the two ports 21 and 22 for supplying these tooth chambers 53a with the working fluid under working pressure and a second part 53b of the circular tooth chambers with the other of the two ports 21 and 22 for performing the working fluid from these tooth chambers 53 b formed and connected to the tooth chambers 53 a, 53 b respectively via the channels 56.
  • a hydrostatic axial compensating piston 17 for axial backlash of the disc-shaped rotary valve 12.
  • control plate 25 Seen in the axial direction between the power part 51 and the inlet and outlet housing part 54, the control plate 25 is arranged.
  • This control plate 25 has windows 26 and control plate channels 57 between the tooth chambers 53a, 53b and the pressure windows 27 formed in the disk-shaped rotary valve 12 for the supply and disposal of the tooth chambers 53a, 53b with the working fluid.
  • the thickness d in the axial direction of the control plate 25 and its material are such that the axial running clearance of the rotary piston 4 between the driven-side housing part 10 and the inlet and outlet housing part 54 decreases or remains the same with increasing working pressure of the working fluid.
  • the tapered roller main bearing 9 in the driven-side housing part 10 from which the shaft output side 8 of the shaft 6 is led out of the housing 24, while the tapered roller sub-bearing 11 is located in the inlet and outlet housing part 54.
  • a cup-shaped sleeve 13 is arranged between the rotary piston 12 and the rotary valve 12.
  • the cup-shaped sleeve 13 surrounds the shaft 6 radially spaced and staggers upon rotation of the rotary piston 4 about the shaft axis 52. As in FIG. 1 As seen in the axial direction, it extends between the power part 51 and the inlet and outlet housing part 54 in the housing 24 and is guided through a corresponding recess in the control plate 25.
  • the wobble sleeve 13 has a first outer sleeve toothing 14 with a number of teeth Z5 on the side of the power section 51, ie in the direction of the output side, and a second outer sleeve toothing 15 with a number of teeth Z6 on the side of the inlet and outlet housing 54, ie Direction opposite to the output side.
  • the first outer sleeve toothing 14 meshes with the inner circular toothing 5, whose number of teeth Z2 is equal to the number of teeth Z5.
  • the second sleeve outer teeth 15 meshes with a rotary valve internal teeth 16 with a number of teeth Z6 corresponding number of teeth Z7 of the rotary valve 12.
  • the cup-like wobble sleeve 13 during the orbit movement of the rotary piston 4 performs a wobbling motion with a wobble angle of approximately 5.5 degrees.
  • the backlashes at the teeth of the first sleeve external gear 14 and the rotary piston internal gear 5 and between the teeth of the second sleeve external teeth 15 and the rotary valve internal teeth 16 should preferably be as small as possible for an accurate commutation control of the power unit from the rotary piston External teeth 3 and the stator inner teeth 1. Therefore, the teeth of the first sleeve outer teeth 14, the second sleeve outer teeth 15 and the rotary valve internal teeth 16 are made very narrow.
  • blind recesses should still be provided between the windows 26 of the control plate 25 in the circumferential direction.
  • the arrangements of these windows 26 of the control plate 25 and the pressure windows 27 of the rotary valve 12 are shown in simplified form in the drawing and generally known to the skilled person.
  • stator inner teeth 1 and the rotary piston outer teeth 3 of the gerotor set and the rotary piston inner teeth 5 and shaft outer teeth 7 of the Internal gear between the shaft 6 and the rotary piston 4 are in FIG. 2 shown. Since one and the same eccentricity e, ie the same center distance between the shaft axis 52 and the rotary piston axis 50 must apply to both internal gears, the number of teeth difference is equal to two in the shaft eccentric internal gear. So that the absorption volume of the machine and the shaft diameter are as large as possible, the numbers of teeth are also large.
  • the pitch and, accordingly, the modulus of the teeth depend on the amount of eccentricity e of the entire moving set, which means the center distance for both internal gear at the same time.
  • the design of the internal gear between the shaft 6 and the rotary piston 4 has a significant influence on the displacement per shaft revolution and thus on the hydraulic power of the machine.
  • FIG. 3 shows a table that makes these ratios clear.
  • the essential variable for the displacement volume is the so-called conveying surface Ao of the rotor toothing between the outer circular toothing 3 and the stator inner toothing 1.
  • the calculation is based on the so-called stationary gearbox, in which the axial distance line or the eccentricity e stands still in space. In this state of motion, the rotors do not run as a rotary piston transmission but as a rotary piston transmission. Both wheels rotate around their own centers and form a normal internal gear machine.
  • Ao is independent of the number of teeth.
  • the outer diameter of the machine is the same in each case, thus also the basic conveying area Ao.
  • the small number of teeth difference of only two teeth between the rotary piston internal teeth 5 and the shaft outer teeth 7 can at the points 28 and 29 of the tooth head of the shaft outer teeth 7, in which the Gears disengage, tooth-head engagement disorders occur ( FIG. 2 ).
  • a tooth tip shortening is provided at these points of the tooth head of the shaft outer toothing 7. This can be done in a simple manner that in the calculation program for the tooth shape of the shaft external teeth 7 at these points mathematically the tooth flank radius 30 of the rotary piston internal teeth 5 is expected to be slightly larger than at the point of the deepest tooth engagement 31. Man ensures a continuous Transition of this tooth flank radius 30 from the point deepest tooth engagement 31 to the points 28 and 29, where the rotary piston internal teeth 5 is disengaged.
  • FIG. 4 shows a longitudinal section through a formed as a wheel motor second embodiment of the invention as a particularly compact construction.
  • This second embodiment differs in particular from the first embodiment in that the shaft output side 8 of the shaft 6 is designed as a cone 37 and on this cone 37 a wheel flange 18 is fastened by means of an axial nut 19 to form a compact wheel motor.
  • FIG. 5 shows a longitudinal section through a designed as a gear double-circle piston engine third embodiment of the invention.
  • This two- to three-stage hydrostatic rotary piston engine is a combination of a first hydrostatic geared rotary piston engine 40 with large displacement per revolution and a second hydrostatic geared rotary piston engine 41 with a smaller displacement per revolution.
  • the first and second hydrostatic geared rotary piston engines 40 and 41 respectively correspond with respect to their essential features of each of the above-described hydrostatic rotary piston engine according to the invention, however, they have different sized tooth chambers 53a, 53b with different axial extent, as in FIG. 5 shown.
  • the respective shaft opposite sides 55 of the shafts 6 of both machines 40 and 41 are torque-effective via a sleeve 42 via splined toothed gear teeth 43 a and 43 b interconnected, wherein the sleeve 42 radially through a common rolling bearing 44 in the inlet and outlet housing part 54 of the first hydrostatic gear rotary piston engine 40 and in the inlet and outlet housing part 54 of the second hydrostatic gear rotary piston machine 41 is mounted.
  • the rolling bearing 44 serves in an advantageous manner as centering of the two machines 40 and 41.
  • the length of this multistage hydrostatic rotary piston machine is only about twice the diameter.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP17185063.9A 2017-08-07 2017-08-07 Machine hydrostatique à pistons rotatifs et à engrenage Active EP3441613B1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202019001218U1 (de) 2019-03-13 2019-04-16 Siegfried Alexander Eisenmann Drehventilantrieb für Zahnrad-Kreiskolbenmotoren

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202022002619U1 (de) 2022-12-09 2023-02-01 Siegfried Alexander Eisenmann Hydrostatische Kreiskolbenmaschine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0367046A1 (fr) 1988-10-24 1990-05-09 Eisenmann, Siegfried A., Dipl.-Ing. Machine hydrostatique à piston rotatif
US5228846A (en) * 1991-11-25 1993-07-20 Eaton Corporation Spline reduction extension for auxilliary drive component
US5873243A (en) * 1996-10-10 1999-02-23 Eaton Corporation Torque generator steering device
US6019584A (en) * 1997-05-23 2000-02-01 Eaton Corporation Coupling for use with a gerotor device
EP1776525A1 (fr) 2004-07-22 2007-04-25 Eisenmann, Siegfried A., Dipl.-Ing. Moteur a piston rotatif hydrostatique
EP2585719A2 (fr) * 2010-06-23 2013-05-01 Siegfried A. Eisenmann Machine hydrostatique à piston rotatif à volume variable en continu
US20140271309A1 (en) * 2013-03-15 2014-09-18 Eaton Corporation Torque-generating steering device
DE202014006761U1 (de) * 2014-08-22 2015-11-24 Siegfried Eisenmann Hydrostatische Kreiskolbenmaschine nach dem Orbitprinzip

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0367046A1 (fr) 1988-10-24 1990-05-09 Eisenmann, Siegfried A., Dipl.-Ing. Machine hydrostatique à piston rotatif
US5228846A (en) * 1991-11-25 1993-07-20 Eaton Corporation Spline reduction extension for auxilliary drive component
US5873243A (en) * 1996-10-10 1999-02-23 Eaton Corporation Torque generator steering device
US6019584A (en) * 1997-05-23 2000-02-01 Eaton Corporation Coupling for use with a gerotor device
EP1776525A1 (fr) 2004-07-22 2007-04-25 Eisenmann, Siegfried A., Dipl.-Ing. Moteur a piston rotatif hydrostatique
EP2585719A2 (fr) * 2010-06-23 2013-05-01 Siegfried A. Eisenmann Machine hydrostatique à piston rotatif à volume variable en continu
US20140271309A1 (en) * 2013-03-15 2014-09-18 Eaton Corporation Torque-generating steering device
DE202014006761U1 (de) * 2014-08-22 2015-11-24 Siegfried Eisenmann Hydrostatische Kreiskolbenmaschine nach dem Orbitprinzip

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202019001218U1 (de) 2019-03-13 2019-04-16 Siegfried Alexander Eisenmann Drehventilantrieb für Zahnrad-Kreiskolbenmotoren

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