EP1074739A1 - Machine hydrostatique à piston rotatif - Google Patents

Machine hydrostatique à piston rotatif Download PDF

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Publication number
EP1074739A1
EP1074739A1 EP00116469A EP00116469A EP1074739A1 EP 1074739 A1 EP1074739 A1 EP 1074739A1 EP 00116469 A EP00116469 A EP 00116469A EP 00116469 A EP00116469 A EP 00116469A EP 1074739 A1 EP1074739 A1 EP 1074739A1
Authority
EP
European Patent Office
Prior art keywords
teeth
rotary valve
rotary piston
gear
piston machine
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Withdrawn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
EP00116469A
Other languages
German (de)
English (en)
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
Hermann Haerle
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
Priority claimed from EP19990115295 external-priority patent/EP1074740B1/fr
Application filed by Individual filed Critical Individual
Priority to EP00116469A priority Critical patent/EP1074739A1/fr
Publication of EP1074739A1 publication Critical patent/EP1074739A1/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Withdrawn legal-status Critical Current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
    • 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

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 straps 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 requirement is related to the fact that such hydraulic motors have to be operated with today's axial and radial piston pumps, which are widely used as adjustable hydrostatic power units. That means that the machine can be made much 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.
  • the number of teeth on the toothing of the equation should correspond, where 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, and z is the number of teeth on the second sun gear designed as a fixed ring gear.
  • this expression of the equation should be an integer.
  • 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 O-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.
EP00116469A 1999-08-03 2000-07-29 Machine hydrostatique à piston rotatif Withdrawn EP1074739A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00116469A EP1074739A1 (fr) 1999-08-03 2000-07-29 Machine hydrostatique à piston rotatif

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP19990115295 EP1074740B1 (fr) 1999-08-03 1999-08-03 Machine hydrostatique à piston rotatif
EP99115295 1999-08-03
EP00116469A EP1074739A1 (fr) 1999-08-03 2000-07-29 Machine hydrostatique à piston rotatif

Publications (1)

Publication Number Publication Date
EP1074739A1 true EP1074739A1 (fr) 2001-02-07

Family

ID=26071236

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00116469A Withdrawn EP1074739A1 (fr) 1999-08-03 2000-07-29 Machine hydrostatique à piston rotatif

Country Status (1)

Country Link
EP (1) EP1074739A1 (fr)

Citations (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

Patent Citations (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

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