EP2607683A2 - Moteur hydrostatique à pistons rotatifs - Google Patents

Moteur hydrostatique à pistons rotatifs Download PDF

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Publication number
EP2607683A2
EP2607683A2 EP20120008506 EP12008506A EP2607683A2 EP 2607683 A2 EP2607683 A2 EP 2607683A2 EP 20120008506 EP20120008506 EP 20120008506 EP 12008506 A EP12008506 A EP 12008506A EP 2607683 A2 EP2607683 A2 EP 2607683A2
Authority
EP
European Patent Office
Prior art keywords
circular arc
rotor
rotary piston
piston engine
engine according
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Withdrawn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
EP20120008506
Other languages
German (de)
English (en)
Inventor
Max Reither
Gerold Strohmaier
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.)
Bohm+wiedemann AG
Original Assignee
Bohm+wiedemann 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
Priority claimed from DE201110122027 external-priority patent/DE102011122027B3/de
Application filed by Bohm+wiedemann AG filed Critical Bohm+wiedemann AG
Publication of EP2607683A2 publication Critical patent/EP2607683A2/fr
Withdrawn legal-status Critical Current

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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
    • F04C2/104—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 having an articulated driving shaft
    • 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
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the invention relates to a hydrostatic rotary piston engine.
  • the invention relates to a hydrostatic rotary piston engine which can be used both as a hydraulic pump, but preferably as a hydraulic motor and, in particular, as a slow-running torque motor.
  • a hydrostatic rotary piston engine of this kind is among others from the EP 1 074 740 B1 known.
  • the rolling bearings of the hydrostatically highly loaded part of the shaft are arranged directly adjacent to a small axial distance in the fixed housing, so that a minimal amount of bending and tooth deformation on the shaft and, accordingly, a maximum amount of pressure and thus torque output can be achieved. Because of this bearing assembly no way to create a 1: 1 rotary connection between the rotary piston acting as a rotor and responsible for the commutation rotary valve, the rotary valve is driven synchronously via a gear transmission from the shaft.
  • this gear transmission is an eccentric internal gear, in which the disk-shaped rotary valve itself acts as an eccentric member of this transmission and thus performs an unavoidable orbital movement.
  • the object of the present invention is to improve the disadvantages known from the prior art.
  • the invention makes it possible to produce the required items in accordance with usual tolerance levels.
  • a hydrostatic rotary piston engine has a fixed Stator 1 with an internal toothing, wherein the internal toothing rotatably mounted rollers 2, which are arranged in roller seats 7.
  • the rotary engine also has a rotor 3, wherein the roller seats 7 have a geometric shape having a circular arc KB a) with circular arc ends K 1 , K 2 , b) with the radius R KB and c) a center M KB and to the circular arc ends of K 1, K 2 each having a shape deviating from the shape of the circular arc KB other geometrical shape, the distance a from the center M KB to points P 1, P 2 is greater than the radius R KB of the circular arc KB, wherein the points P 1 , P 2 correspond to the intersections of the respective other geometric shape deviating from the shape of the circular arc KB with a boundary surface d f of the internal toothing.
  • stator As a stator, the fixed, immovable part of a machine is understood.
  • the counterpart to the stator is called the rotor, which represents the moving, rotating part of the machine.
  • the stator has an internal toothing.
  • the internal gear has rotatably mounted rollers, which in turn are arranged in roller seats of the stator.
  • the radius of the rollers is inventively smaller than the radius R KB of a central circle with the center M KB of the roller seat. As a result, the role a certain play in the role seat is possible.
  • the boundary surface d f corresponds to the root circle of the Statorinnenverzahnung.
  • a different geometric shape deviating from the shape of the circular arc KB is to be understood as meaning geometries which deviate from the circular shape having the radius R KB .
  • the hydrostatic rotary piston engine additionally has a shaft.
  • a shaft is, in its simplest form, a rod-shaped machine element that is used to pass rotational motions and torques. Shafts, in contrast to axles, transmit torque and are subjected to torsion.
  • the shaft is preferably a hollow shaft, a flexible shaft, a crankshaft, a propeller shaft or a wobble shaft.
  • the torque transmission to the shaft is preferably carried out by means of material, form or adhesion. This means that the connection of the torque transmission from the rotor by means of pluggable or rolling teeth, welds an eccentricity balancing shaft, such as. A flexible shaft can be done. Also preferred are friction linings that absorb the radial offset or by means of elements, such as balls, in radially arranged windows or oblong holes that allow torque transmission or translation.
  • the shaft is a centrically mounted shaft or fixed shaft. It is advantageous that the rotary engine works particularly well with a centrically mounted shaft that could not be used with other engines at all. In this case, a constant and correspondingly uniformly quiet rotary motion in the rotary engine can be achieved.
  • the deviating from the shape of the circular arc further geometric shape is configured such that it has, for example, a circular geometry with a different radius from the arc, connects tangentially rectilinear to the circular arc ends, curved, parabolic, exponential or other geometric shapes.
  • the distance A at least by 2/100 mm and at most by 3/100 mm larger than the radius of the circular arc executed.
  • a distance ⁇ P1P3 between the first intersection P 1 and the point P 3 is provided.
  • a distance ⁇ P2P4 is provided between the second intersection P 2 and the point P 4 .
  • the points P 3 , P 4 correspond to the ideal point of intersection of the circular arc with the boundary surface d f of the internal toothing of the stator.
  • the distance ⁇ P1P3 , ⁇ P2P4 corresponds at least to the difference between the distance A and the radius of the circular arc.
  • the arc includes an angle ⁇ of greater than 180 °.
  • a distance P 1 K 1 is enclosed by an angle ⁇ 1 and a distance K 2 P 2 by an angle ⁇ 2 .
  • the angles ⁇ 1 and ⁇ 2 are preferably the same size.
  • the rotor preferably has an external toothing which partially engages in the internal toothing of the stator. Furthermore, the rotor has an internal toothing.
  • the additional shaft has an external toothing, which partially meshes with the internal toothing of the rotor.
  • an orbital movement with the rotor can be carried out in such a manner that working chambers can be filled with disposable dental chambers between the internal toothing of the stator and the external toothing of the rotor and can be filled between the roller seats of the stator and the rollers of the internal toothing.
  • working fluid can preferably be fed to the tooth chambers through supply bores of a distributor plate and, by means of a rotary valve, the tooth chambers can be discharged through disposal bores of a distributor plate working fluid.
  • the rotor is dimensioned such that upon contact of the rollers with the external toothing of the rotor, the center of the diameter of the rollers has an eccentricity e to the center of the diameter of the roller seat in the internal toothing of the stator. That is, due to the eccentricity with working fluid ver- and disposable areas between the roller seat of the stator and the rollers of the internal teeth can form.
  • the roller seat of the stator has at least one contact surface on which the roller can rest. Accordingly, the role comes to a right or a left contact surface on the roller seat for concern.
  • the at least one contact surface can have a circular cross section, a curved cross section, a trumpet-shaped cross section or a straight cross section for receiving the roller.
  • the cross section of the roller seats in the stator - due to the dimensions of the rotor - not completely closed by the roller, so that a gap s between the roller seat of the stator and the roller adjusts.
  • This gap results from the above-mentioned eccentricity in conjunction with the corresponding cross-sectional position of the roller seat and the respective formation of the bearing surfaces. If false, i. Too small dimensioning of the rotor or without attaching the rotor in the rotary piston engine, however, the gap s would be closed by the roller.
  • the high-pressure working fluid of the supply chamber can penetrate through the open gap between the roller and its example.
  • An angle ⁇ preferably results from an extended straight line of a tangent contact point of the roller on the roller seat in the stator to the theoretical slot shape of the roller seat.
  • the angle ⁇ is -15 ° ⁇ ⁇ ⁇ + 15 °.
  • the roller just can not slide out of its roller seat, but the eccentricity is large enough to compensate for the existing tolerances and other positional deviations.
  • the gap (s) is always present according to the invention.
  • the toothed chambers are supplied with the working fluid at a first pressure through the supply bores of the distributor plate.
  • the expanded working fluid is discharged with a second pressure through the disposal holes in the same way through the distributor plate and the rotary valve again.
  • the rollers are tiltably mounted in the roller seat.
  • the rollers are designed so that their ends are "spherical". Under spherical "is an embodiment in which the two ends of the rollers are arched outwards.
  • the rollers are arranged in the rotary piston engine, that they are limited in the longitudinal direction on the one hand by the bearing flange and on the other hand by the distributor plate, wherein a tilting movement is executable, without causing leaks.
  • the game which is due to the length of the role in relation to the stator thickness, allows the role in their seat can tilt to compensate for any angular deviations.
  • the roller must be able to move as described, but the resulting gaps must still be so small that the volumetric efficiency is maintained.
  • the supply holes of the tooth chambers are arranged on their pitch circle, that the compression between the Zahnschvolumen at the time when the teeth of the rotor covering the supply holes entirely (mainly left and right of the roller fulcrum) and the smallest resulting chamber volume is kept small.
  • the supply holes are arranged close to the internal toothing of the stator, that is to say offset in the direction of the root circle of the internal toothing of the stator to the outside.
  • the trapped working fluid in the tooth chamber may additionally utilize the volume of the supply bore in the distributor plate, as far as the shut-off rotary valve, to reduce compression.
  • FIG. 1 shows a hydrostatic rotary piston engine according to the invention with a centrally mounted continuous shaft (4), acting as an output power unit with a Centric stationary stator (1) and a rotary piston as a rotor (3).
  • the stator (1) has an internal toothing
  • the rotor (3) has an external toothing (8) which partially engages in the internal toothing of the stator (1) and an internal toothing (9).
  • the shaft (4) meshes with its external toothing (10) partially the internal toothing (9) of the rotor (3).
  • the rotor (3) is so eccentrically arranged for performing an orbital motion and dimensioned accordingly that form with dental fluid ver ⁇ and disposable tooth chambers between the inner toothing of the stator (1) and the outer toothing (8) of the rotor (3).
  • the teeth of the internal toothing of the stator (1) are designed as rollers (2).
  • the rotary valve (6) as a commutator the toothed chambers through the supply holes of the distributor plate (5), the working fluid at the pressure (p 1 ) is supplied.
  • the expanded working fluid is discharged with the pressure (p 2 ) through the disposal holes in the same way through the distributor plate (5) and the rotary valve (6) again.
  • the division high pressure - low pressure is likewise in FIG. 1 shown along the vertical machine centerline. Due to its eccentric position, the rotor (3) is pressed by the resulting pressure force (Fp) of the working fluid in the tooth chambers at high pressure around the roller pivot with the supporting force (FS) with its internal teeth against the external teeth of the shaft (4) and generates the shaft torque forming force (FM).
  • FIG. 2 is a schematic representation of a roller seat shown.
  • the roller seats (7) has a geometric shape, which comprises a circular arc (KB) with circular arc ends (K 1 , K 2 ), with the radius (R KB ) and a center (M KB ).
  • An angle ( ⁇ ) of the circular arc is selected here with 195 °.
  • the arc ends at points (K 1 ) and (K 2 ).
  • the points (K 1 ) and (K 2 ) lie on a circular line (d 0 ), which connects all centers (M KB ) of the roller seats (7).
  • a straight line connects on both sides in such a way that the circular arc ends are extended tangentially in a straight line.
  • a geometric shape sets in, which is referred to below as "trumpet-shaped".
  • the rectilinear extension extends from the circular arc ends (K 1 , K 2 ) to the points (P 1 , P 2 ).
  • the points (P 1 , P 2 ) correspond to the points of intersection of the respective other geometric shape deviating from the shape of the circular arc (KB) (in this case the straight line) with a boundary surface (d f ) of the internal toothing.
  • the distance (A) from the center (M KB ) to points (P 1 , P 2 ) is greater than the radius (R KB ) of the circular arc (KB).
  • the points (P 3 , P 4 ) correspond to the ideal point of intersection of the circular arc (KB) with the boundary surface (d f ) of the internal toothing of the stator (1).
  • a distance ( ⁇ P1P3 ) between the point (P 1 ) and the point (P 3 ) and a distance ( ⁇ P2P4 ) between the point (P 2 ) and the point (P 4 ) is present accordingly.
  • the distance ( ⁇ P1P3 , ⁇ P2P4 ) is at least the difference between the distance (A) and the radius (R KB ) of the circular arc (KB).
  • an angle ( ⁇ 1 ) between the intersections (P 1 , P 2 ) and the circular arc ends (K 1 , K 2 ) is included. The angle occurs on both sides and amounts to approx. 25 ° each.
  • FIG. 3 is a schematic representation of a detail X from the FIG. 1 the device of the invention shown
  • the roller (2) has a diameter which is dimensioned so that the roller (2) in your seat in the respective stator (1) has a suitable clearance.
  • the roller seat (7) in the stator (1) is as in FIG. 2 represented, executed "trumpet-shaped".
  • the rotor (3) is dimensioned such that when the rollers (2) are in contact with the tooth tip circle of the rotor (3), the center of the roller diameter is eccentric (e) before the center of the roller seat diameter and the roller outer diameter does not touch the trumpet hole of the roller Roller seat (7) closes, so that always a suitable gap (s) remains.
  • the length of the rollers (2) has a suitable play to the stator thickness and has the same dimensions as the rotor thickness.
  • the high-pressure working fluid of the supply chamber can penetrate through the open gap (s) between the roller (2) and its trumpet-shaped seat in the stator (1) and the roller (2) eccentrically sealing against its stator seat (sealing position Pk2) and the rotor tooth ( Pk1).
  • roller sealing position (Pk) can vary within the abovementioned conditions and compensate for the existing tolerances and other position deviations. This is always a seal between high pressure and low pressure and an occurrence of oversize is thereby avoided.
  • the rotor (3) applies an additional force to the roller (2), which presses it into its sealing position (Pk 2 ) in a stator seat, since the roller (2) is eccentric (e) in front of it theoretical “Abrollpostion” is located in the stator seat.
  • the geometry of the contact surface (11, 12) in the Rollenabdichtposition (Pk2) in the stator is executed "trumpet-shaped".
  • a corresponding shaping can e.g. through a curve, through circular arcs, through straight lines or other geometric shapes.
  • the execution is to be executed left and right (because of left and right rotation of the machine).
  • a tangent contact point on the roller seat (7) in the stator (1) is determined and the remaining distance from this to the root of the stator internal teeth executed as a straight line.
  • FIG. 4 (Detail Y) is the Tangentenberlickddling (TP) on the roller seat (7) in the stator (1) at the intersection of the pitch circle (d 0 ) of Statorrollensitze with the circumference of the roller seat (7) in the stator (1), wherein the angle ( ⁇ ) between -15 ° and + 15 °.
  • the pitch circle (d 0 ) runs through all centers (M KB ) of the roller seats.
  • roller (2) just (yet) can not slide out of their seat.
  • the possible eccentric position (s) is sufficient large to compensate for the existing tolerances and other positional deviations.
  • the gap (s) is always present. (As an alternative to the straight line with the angle ( ⁇ ) is also a curve and a circular arc in FIG. 4 shown.)
  • the play allows, due to the length of the rollers (2) relative to the stator thickness, that the corresponding roller (2) in its seat (7) can tilt to compensate for any angular deviations.
  • the roller (2) must be able to move, but the resulting gaps (s) must still be so small that the volumetric efficiency is nevertheless maintained.
  • FIG. 1 it is advantageous for a very constant torque output of the machine when in the distributor plate (5) the supply holes (13.1, 13.2, 13.3, etc.) of the tooth chambers are arranged on their pitch circle that the compression between the Zahnwaitvolumen at the time when the Teeth of the rotor (3) cover the supply holes completely and the smallest resulting chamber volume is kept small.
  • the trapped working fluid (VT) in the tooth chamber may additionally utilize the volume of the supply bore in the distributor plate (5) to the shut-off rotary valve (6) to reduce compression so as to minimize pressure fluctuations.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
EP20120008506 2011-12-22 2012-12-20 Moteur hydrostatique à pistons rotatifs Withdrawn EP2607683A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110122027 DE102011122027B3 (de) 2011-12-22 2011-12-22 Hydrostatischer Kreiskolbenmotor
DE102012017745 2012-09-07

Publications (1)

Publication Number Publication Date
EP2607683A2 true EP2607683A2 (fr) 2013-06-26

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ID=47598556

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20120008506 Withdrawn EP2607683A2 (fr) 2011-12-22 2012-12-20 Moteur hydrostatique à pistons rotatifs

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EP (1) EP2607683A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111997893A (zh) * 2020-09-10 2020-11-27 杭州智笙生物技术有限公司 一种机器手臂柔性低线速度齿式型线啮合穿戴泵
RU2825493C1 (ru) * 2023-12-19 2024-08-26 Общество с ограниченной ответственностью "ДРГ-НМ" Гидромотор-колесо

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1074740B1 (fr) 1999-08-03 2001-12-19 Siegfried A. Dipl.-Ing. Eisenmann Machine hydrostatique à piston rotatif
WO2006010471A1 (fr) 2004-07-22 2006-02-02 Eisenmann Siegfried A Moteur a piston rotatif hydrostatique

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1074740B1 (fr) 1999-08-03 2001-12-19 Siegfried A. Dipl.-Ing. Eisenmann Machine hydrostatique à piston rotatif
WO2006010471A1 (fr) 2004-07-22 2006-02-02 Eisenmann Siegfried A Moteur a piston rotatif hydrostatique

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111997893A (zh) * 2020-09-10 2020-11-27 杭州智笙生物技术有限公司 一种机器手臂柔性低线速度齿式型线啮合穿戴泵
CN111997893B (zh) * 2020-09-10 2022-10-14 中国计量大学 一种机器手臂柔性低线速度齿式型线啮合穿戴泵
RU2825493C1 (ru) * 2023-12-19 2024-08-26 Общество с ограниченной ответственностью "ДРГ-НМ" Гидромотор-колесо

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