EP1074740B1 - Machine hydrostatique à piston rotatif - Google Patents

Machine hydrostatique à piston rotatif Download PDF

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Publication number
EP1074740B1
EP1074740B1 EP19990115295 EP99115295A EP1074740B1 EP 1074740 B1 EP1074740 B1 EP 1074740B1 EP 19990115295 EP19990115295 EP 19990115295 EP 99115295 A EP99115295 A EP 99115295A EP 1074740 B1 EP1074740 B1 EP 1074740B1
Authority
EP
European Patent Office
Prior art keywords
teeth
rotary valve
hydrostatic
tooth system
machine 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.)
Expired - Lifetime
Application number
EP19990115295
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German (de)
English (en)
Other versions
EP1074740A1 (fr
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
Hermann Härle
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Individual
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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
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Application filed by Individual filed Critical Individual
Priority to DE59900601T priority Critical patent/DE59900601D1/de
Priority to DK99115295T priority patent/DK1074740T3/da
Priority to EP19990115295 priority patent/EP1074740B1/fr
Priority to EP00116469A priority patent/EP1074739A1/fr
Publication of EP1074740A1 publication Critical patent/EP1074740A1/fr
Application granted granted Critical
Publication of EP1074740B1 publication Critical patent/EP1074740B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C2/105—Details concerning timing or distribution valves
    • 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

Definitions

  • the invention relates to a hydrostatic rotary piston machine according to the preamble of claim 1.
  • Such a rotary piston machine is for example in the EP-A1-761 968.
  • the advantage of this arrangement is that a Large bearing distance arises, resulting in additional radial forces at the outer end of the shaft e.g. by belt or tooth forces or through wheel contact forces the bearing loads be reduced.
  • Another advantage of this machine is the much better mechanical-hydraulic Starting efficiency compared to other known systems of the so-called orbit slow-speed, mostly with a cardan shaft the torque from the rotary piston to the output shaft transfer.
  • the object of the invention is to improve this machine so that it is higher than the known version Working pressures and therefore higher torques and outputs are possible with a reduced number of components.
  • the aim is a so-called "high torque motor” for a maximum pressure of approx. 400 bar and for a continuous pressure of 350 bar.
  • This demand hangs together with the fact that such hydraulic motors with today's Axial and radial piston pumps must be operated as adjustable hydrostatic power units in many cases be used. That means the machine is essential more robust and at the same time the volumetric Efficiency can be improved.
  • an eccentric internal gear is available as the gear transmission at which the disc-shaped rotary valve executes the eccentric movement (orbit movement).
  • the two Internal gears that form the eccentric gear have differences in the number of teeth between one and two teeth, making one There is multiple tooth engagement, similar to the positive toothing on the displacer.
  • Cycloid internal gears can be used as tooth shapes, especially trochoid gears, be used, or with a difference in the number of teeth of two teeth also involute splines according to DIN 5480 with 30 ° pressure angle if it is ensured that no tooth head interference disorders occur.
  • a is the number of teeth of the external teeth on the shaft
  • b the number of teeth of the internal teeth on the rotary piston
  • c the number of teeth of the external teeth on the rotary piston
  • d the number of teeth of the internal teeth on the rigid housing part
  • w the number of teeth on the first sun gear on the shaft
  • x the number of teeth the internal teeth on the rotary valve
  • y is the number of teeth on the external teeth on the rotary valve
  • z is the number of teeth on the second sun gear designed as a fixed ring gear.
  • the stepped piston hydraulically compensates for the axial forces on disc-shaped rotary valve, so that in both directions of rotation the leakage gap between the rotary valve and the control plate on the one hand and the rotary valve and the end face the stepped piston on the other hand to a lubricating film thickness of is reduced by a few micrometers. That way stays the volumetric efficiency of the machine even at high Pressures and low speeds very high.
  • the rotary piston machine shown in the figures has an input or output shaft 2, in which the bearing 10 directly are arranged on both sides of a rigid housing part 4.
  • the Shaft 2 is in the area of the rigid housing part 4 with a - second - external toothing 9 with a number of teeth a, with a - second - Internal teeth 8 with a number of teeth b on the rotary piston 6 combs.
  • the rotary piston 6 circles eccentrically around the shaft 2 and meshes with a - first - external toothing 7 with a Number of teeth c in the - first - internal toothing 6 with one Number of teeth d of the rigid housing part 4.
  • Rotary piston 6 and housing part 4 can - the first - internal teeth 5 on the housing part 4 in an advantageous manner Be designed in the form of rotatably sliding rollers 28.
  • a gear transmission is used to transmit the rotary piston rotation provided in the form of an eccentric gear 12, 13, whereby a translation is generated via this gear transmission is through which the translation in the rotation transmission is compensated by the rotary piston 6 on the shaft 2.
  • the such driven control part in the form of a rotary valve 3 is disc-shaped. Comparing the invention Training according to the present Fig.1 and FIG. 5 with that known from EP-A1-0 761 968, FIG. 5 Training, it is easy to see that the inventive Training with fewer components (so could on the transmission piston 15 ', the transmission sleeve 42 and also the housing part 9 of the known training can be dispensed with) is, thereby reducing the manufacturing cost.
  • the size of the motor can also be chosen to be smaller become.
  • the shaft 2 is designed as the first - sun gear 14 with a number of teeth w, into which the disk-shaped rotary valve has an - third - internal toothing 15 with a number of teeth x with an eccentricity 20 engages in rotation.
  • the rotary valve 3 now meshes with its - third - external toothing 16 with a number of teeth y with a - fourth - internal toothing 17, which is formed in the connection housing 18 on a second sun gear 18 1 in the form of a ring gear fixed to the housing.
  • the number of teeth of this - fourth - internal toothing 17 on the second sun gear 18 1 is given by z.
  • the internal toothing provided on the second sun gear can also be arranged directly on the connection housing, as a result of which the sun gear as a separate component, although fixed to the housing, can be dispensed with.
  • Step piston 23 is a new version of the step piston 23 shown.
  • the stepped piston 23 must be prevented from rotating be secured in the connection housing 18. It serves according to the design of Figure 1 a pin 53. However can then no connection bore 36 at this point Step piston 23 are attached, which is the flow resistance enlarged for the oil.
  • the ring gear-shaped, second sun gear 18 1 is made slightly wider. In this way, a toothing 37 provided on the stepped piston 23 can engage in the stepped piston 23, so that the stepped piston 23 can be prevented from rotating against lateral forces.
  • the stepped piston 23 can be manufactured together with its toothing 37 and the connecting bores 36 in the sintering process. This version is very easy to install, since the stepped piston 23 can be used if the 0-rings 33 and 34 are arranged in the connection housing 18.
  • the anti-rotation device for the second sun gear 18 1 is done via pins 38 and its axial securing device via a snap ring 39.
  • An initial spring 40 is designed as a corrugated spring and keeps the stepped piston 23 in contact with the rotary valve 3 even at zero pressure.
  • the fourth internal toothing 17 can also be arranged directly in the connection housing 18, as shown in FIG. This will prove to be particularly advantageous from the point of view if the manufacturer of such circular piston machines has sufficient capacity for gear-butting machines.
  • Such an arrangement has the advantage that the internally toothed sun gear 18 1 and small parts such as pins 38 and locking ring 39 can be saved. This also reduces the effort involved in assembly.
  • the relative twist phase position of the toothing 17 with respect to the second internal toothing 5 (which can be designed in the form of rollers according to FIG. 2) is exactly observed, which task in the training according to FIG. 1 and 5 is fulfilled by the correct positioning of the pin 38.
  • the slight eccentric movement of the rotary valve 3 has a tribological effect very advantageous because it causes scoring Dirt and abrasion particles in the oil film is avoided, such as when polishing smooth surfaces.
  • the inevitable Wear due to erosion and corrosion on these surfaces is by the hydrostatically pressed stepped piston 23 automatically readjusted. This keeps the leakage current always small at these points.

Claims (9)

  1. Machine hydrostatique à piston rotatif, avec une partie refoulement (1), agissant en tant que partie menante ou partie menée, et avec une soupape rotative (3) servant à l'alimentation et à l'évacuation en fluide de travail de la partie refoulement (1), la partie refoulement (1) présentant une première partie de carter (4) rigide, munie d'une première denture intérieure (5), présentant un nombre de dents (d), qui coopère avec une première denture extérieure (7) présentant un nombre de dents (c), réalisée sur un piston circulaire (6) susceptible de tourner, monté de façon excentrique, le piston circulaire (6) présentant une deuxième denture intérieure (8), présentant un nombre de dents (b), s'engrenant avec une deuxième denture extérieure (9), présentant un nombre de dents (a), réalisée sur un arbre (2) monté de façon centrée, et dans lequel d - c = 1 et b - a = 2, les paliers d'arbre (10, 11) étant disposés directement voisins à gauche et à droite sur la partie refoulement et une soupape rotative (2), en forme de disque, et une transmission à roue dentée pour son entraínement étant prévues, caractérisée en ce que la transmission à roue dentée est une transmission intérieure à excentrique (12, 13), pour laquelle la soupape rotative (3) en forme de disque effectue le mouvement d'excentricité en orbite autour de l'axe de machine.
  2. Machine hydrostatique à piston rotatif selon la revendication 1, caractérisée en ce que les nombres de dents (a, b, c, d) de la partie refoulement (1) et les nombres de dents (w, x, y, z) de la transmission intérieure à excentrique (12, 13) satisfont à l'égalité : ba . d - cd - c = xw . z - yz - y et cette expression d'égalité étant un nombre positif entier, w étant le nombre de dents d'une première roue solaire (14) disposée sur l'arbre (2), x étant le nombre de dents de la troisième denture intérieure (15) sur la soupape rotative (3) en forme de disque, y étant le nombre de dents de la troisième denture extérieure (16) sur la soupape rotative (3) et z étant le nombre de dents de la quatrième denture intérieure (17) sur le carter de raccordement (18).
  3. Machine hydrostatique à piston rotatif selon la revendication 2, caractérisée en ce que le nombre entier positif est égal à 3.
  4. Machine hydrostatique à piston rotatif selon l'une des revendications 1 à 3, caractérisée en ce que la valeur de l'égalité yy - z prend des valeurs négatives entières, entre -33 et -55, lorsque, sur la transmission excentrique (12, 13), y désigne le nombre de dents de la denture extérieure (16) sur la soupape rotative (3) en forme de disque et z désigne le nombre de dents de la denture intérieure (17) sur le carter de raccordement (18) ou sur une deuxième roue solaire (181) dans le carter de raccordement (18).
  5. Machine hydrostatique à piston rotatif selon l'une des revendications 2 à 4, caractérisée en ce que pour les nombres de dents a = 12, b = 14, c = 11, d = 12 ou a = 13, b = 15, c = 12, d = 13 de la partie refoulement (1), les nombres de dents de la transmission à excentrique (12, 13) de la soupape rotative (3) peuvent prendre les valeurs suivantes :
    pour (x - w) = 1 : x = 16 à 24; y = 29 à 45 dents
    pour (x - w) = 2 : x = 31 à 49; y = 18 à 46 dents.
  6. Machine hydrostatique à piston rotatif selon l'une des revendications 1 à 5, caractérisée en ce que l'excentricité commune (20) de la transmission à excentrique (12, 13) sur la soupape rotative (3) en forme de disque est de 0,01 à 0,017 fois le diamètre moyen du cercle partiel des fentes ou lumières de commande (21) dans une plaque de commande (22).
  7. Machine hydrostatique à piston rotatif selon l'une des revendications 1 à 5, caractérisée en ce que l'excentricité commune (20) des deux transmissions intérieures (12, 13) est de 0,011 à 0,015 fois le diamètre moyen de cercle partiel des fentes ou lumières de commande (21) dans la plaque de commande (22).
  8. Machine hydrostatique à piston rotatif selon l'une des revendications 1 à 7, caractérisée en ce qu'un piston étagé (23) est prévu pour assurer la compensation axiale des interstices de fuite (24 et 25) sur la soupape rotative (3) en forme de disque.
  9. Machine hydrostatique à piston rotatif selon les revendications 1 à 8, caractérisée en ce que la première denture intérieure (5) est formée par des rouleaux (28) montés à rotation dans la partie de carter (4).
EP19990115295 1999-08-03 1999-08-03 Machine hydrostatique à piston rotatif Expired - Lifetime EP1074740B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE59900601T DE59900601D1 (de) 1999-08-03 1999-08-03 Hydrostatische Kreiskolbenmaschine
DK99115295T DK1074740T3 (da) 1999-08-03 1999-08-03 Hydrostatisk rotationsstempelmaskine
EP19990115295 EP1074740B1 (fr) 1999-08-03 1999-08-03 Machine hydrostatique à piston rotatif
EP00116469A EP1074739A1 (fr) 1999-08-03 2000-07-29 Machine hydrostatique à piston rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19990115295 EP1074740B1 (fr) 1999-08-03 1999-08-03 Machine hydrostatique à piston rotatif

Publications (2)

Publication Number Publication Date
EP1074740A1 EP1074740A1 (fr) 2001-02-07
EP1074740B1 true EP1074740B1 (fr) 2001-12-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19990115295 Expired - Lifetime EP1074740B1 (fr) 1999-08-03 1999-08-03 Machine hydrostatique à piston rotatif

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EP (1) EP1074740B1 (fr)
DE (1) DE59900601D1 (fr)
DK (1) DK1074740T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011122027B3 (de) * 2011-12-22 2013-04-11 Böhm + Wiedemann Feinmechanik AG Hydrostatischer Kreiskolbenmotor
EP2607683A2 (fr) 2011-12-22 2013-06-26 Böhm+Wiedemann AG Moteur hydrostatique à pistons rotatifs

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH701073B1 (de) * 2004-07-22 2010-11-30 Siegfried A Dipl-Ing Eisenmann Hydrostatischer Kreiskolbenmotor.
DE102013111098B3 (de) * 2013-10-08 2014-11-13 4-QM hydraulics GmbH Strömungsmaschine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH679062A5 (fr) * 1988-10-24 1991-12-13 Siegfried Eisenmann
EP0761968A1 (fr) * 1995-09-08 1997-03-12 Siegfried A. Dipl.-Ing. Eisenmann Soupape pour moteur à engrenage à denture intérieure avec palier hydrostatique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011122027B3 (de) * 2011-12-22 2013-04-11 Böhm + Wiedemann Feinmechanik AG Hydrostatischer Kreiskolbenmotor
EP2607683A2 (fr) 2011-12-22 2013-06-26 Böhm+Wiedemann AG Moteur hydrostatique à pistons rotatifs

Also Published As

Publication number Publication date
DK1074740T3 (da) 2002-04-15
DE59900601D1 (de) 2002-01-31
EP1074740A1 (fr) 2001-02-07

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