EP0491398B1 - Radialkolbenmotor - Google Patents

Radialkolbenmotor Download PDF

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Publication number
EP0491398B1
EP0491398B1 EP91121810A EP91121810A EP0491398B1 EP 0491398 B1 EP0491398 B1 EP 0491398B1 EP 91121810 A EP91121810 A EP 91121810A EP 91121810 A EP91121810 A EP 91121810A EP 0491398 B1 EP0491398 B1 EP 0491398B1
Authority
EP
European Patent Office
Prior art keywords
bearing surface
guide body
housing
ball
relief
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
EP91121810A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0491398A1 (de
Inventor
Mattias Dr.-Ing. Szewczyk
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.)
Paul Pleiger Maschinenfabrik GmbH and Co KG
Original Assignee
Paul Pleiger Maschinenfabrik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Paul Pleiger Maschinenfabrik GmbH and Co KG filed Critical Paul Pleiger Maschinenfabrik GmbH and Co KG
Publication of EP0491398A1 publication Critical patent/EP0491398A1/de
Application granted granted Critical
Publication of EP0491398B1 publication Critical patent/EP0491398B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0644—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0658—Arrangements for pressing or connecting the pistons against the actuating or actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • F01B15/005—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 having cylinders in star or fan arrangement, the connection of the pistons with the actuated or actuating element being at the inner ends of the cylinders

Definitions

  • the invention relates to a radial piston motor according to the preamble of claim 1.
  • FIG. 1 shows schematically the known construction according to the above-mentioned FR-OS.
  • the pressure p B present in the pressure chamber 1 above the guide body 2 at the diameter de of this pressure chamber of the pressure medium supplied, for example, through passages in the cylinder cover exerts a force F H which occurs during the pivoting movement of the guide body 2, which engages in a hollow piston 3, remains stationary.
  • F H the force which occurs during the pivoting movement of the guide body 2, which engages in a hollow piston 3
  • the invention has for its object to design a radial piston engine of the type mentioned so that the effective degree of relief can be designed to a maximum.
  • the spherical ring-shaped bearing surface on the housing is dimensioned in relation to the spherical ring-shaped bearing surface on the guide body in such a way that when the guide body is pivoted, the bearing surface on the housing is partially released with respect to the pressure medium and not the bearing surface on the guide body, as is the case with the above prior art Case is, the relief diameter de on the guide body, on which the relief force F H acts, the pendulum movement of the guide body, so that a constant high relief can be achieved in any pivot position, which can also be interpreted precisely due to the constant alignment of the forces acting against each other.
  • the spherical ring bearing surface 4 on the guide body 2 is approximately the same width as the corresponding spherical ring bearing surface 5 on the housing or cylinder cover 6, so that in the illustrated maximum pivoting position of the guide body 2, its bearing surface 4 has the bearing surface 5 on one side Housing 6 covers, while on the opposite side, the bearing surface 5 on the housing 6 is partially released.
  • the width of the ball ring bearing surface 4 can be designed as desired. In theory, it can reach the extreme value zero, as shown in Fig. 2a. There is therefore no relationship between the width of the ball ring bearing surface 4 and the ball bearing surface 5 on the cylinder cover.
  • the ball bearing surface in the cylinder cover must have a certain minimum width, because the ball ring bearing surface 4, if the degree of relief is not 100%, only has to transmit the resulting residual force.
  • the relief surface on the end face of the guide body 2 is not partially formed by the bearing surface 4 on the guide body, but only by the straight end face 8, the edges of which during the pivoting movement Brush over the bearing surface 5 on the housing 6.
  • a portion of the bearing surface 4 on the guide body 2 is always acted upon by the pressure of the pressure medium, so that the relief force F H cannot follow the pivoting movement of the guide body 2.
  • the relief surface de is defined by the approximately cylindrical pressure chamber 1 in the housing 6, while in the construction according to the invention the relief surface de is fixed on the guide body 2.
  • FIGS. 1a and 2a This is illustrated by the schematic representations in FIGS. 1a and 2a.
  • the bearing surface on the housing is reduced to a circular sealing edge 5 ', on which the ball ring bearing surface 4 of the guide body 2 rests.
  • the pressure chamber 1 above the guide body is essentially fixed by a cylindrical recess Diameter de formed.
  • the sealing edge 5 ' determines the size of the pressure field p B and thus also its stationary position, because the sealing edge 5' does not change during the pivoting movement of the guide body 2.
  • the pressure chamber 1 is formed above the guide body 2 by an approximately spherical cap-shaped recess, the bearing surface 4 of the guide body 2 reduced to a peripheral edge 4 'being present as a sealing edge in this spherical cap-shaped recess.
  • the diameter de of this circular sealing edge 4 ' determines the pressure field p B acting on the guide body 2 according to size and position, so that the orientation of the pressure field inevitably follows the orientation of the sealing edge 4', which in this illustration forms the upper end face 8 of the guide body 2.
  • Characterized in that the cylindrical element 2 in Fig. 2a is movable relative to the fixed element 5 with a concave ball bearing surface, the sealing line 4 'between these two elements and the associated pressure field is movable.
  • the plane of the relief surface de or its projection in the axial direction intersects the spherical ring bearing surface 5 on the housing 6 in the construction according to the invention.
  • the width of the bearing shell 5 on the housing 6 is essentially determined by the pivoting range of the relief surface de running perpendicular to the longitudinal axis of the guide body 2 certainly. This applies to the determination of the minimum height of the upper edge of the bearing shell 5.
  • the lower edge of the bearing shell 5 is designed so that even in the maximum pivoting position according to FIG. 2, there is sufficient bearing surface for the guide body 2 at the bottom right.
  • Fig. 2 shows in the maximum swivel position of the guide body 2 the minimum height of the upper edge of the bearing surface 5 on the housing. As FIG. 2a shows, this upper edge can also be higher.
  • the width of the bearing surface 4 on the guide body corresponds to the width of the bearing surface 5 on the housing, so that the two bearing surfaces completely overlap on one side in the maximum pivoting position. However, this width of the bearing surface 4 is not necessary, as stated above.
  • This design of the bearing area between the guide body and the housing or cylinder cover ensures that the hydraulic relief field and the resulting relief force F H is connected to the pivoting guide body.
  • the hydraulic relief force acts in the same plane or orientation against the reaction force on the radially inner side of the guide body, so that there is no critical position in which lifting of the piston is to be feared because the same friction torque is present in every pivot position.
  • Fig. 3 shows a construction according to the invention, in which the guide body 2 'overlaps the piston 3'.
  • the plane of the relief surface de can only be pivoted in the area of the bearing shell 5 on the housing 6 and not beyond.
  • the frictional torque on the guide body 2 'can thereby be reduced to a minimum value, that due to a high degree of relief only low friction forces N. »Occur.
  • a relatively large ball radius R K is provided in this construction, which is larger than the piston radius, because the piston is immersed in the guide body, the frictional torque can nevertheless be kept very small.
  • the upper part of the guide body 2 ' is spherical, with a support ring 10 supported by springs 9 is provided in the lower region of the ball, which is supported in the housing or in the cylinder cover.
  • the eccentric is indicated in Fig. 3, on the circumference of which the pistons 3 'or 3 abut.
  • Fig. 3 designates an annular groove formed on the bearing surface 4, which is formed near the end face of the guide body 2 'on its circumference and is continuously connected via an oblique bore 13 to the leakage oil chamber of the radial piston motor.
  • the annular groove 12 is therefore formed near the end face of the guide body 2 'in the ball ring bearing surface 4.
  • the pressure surface on the end face 8 of the guide body 2 ' is precisely defined, since the annular groove 12 via the oblique bore 13 reduces the operating pressure PB to the leakage oil pressure between the end face 8 and the annular groove 12. Without this annular groove 12 with relief bore 13, the pressure reduction in the bearing area and thus the pressure relief field would not be precisely defined.
  • the convex spherical ring bearing surface 4 lying below the annular groove 12 in FIG. 3 serves only for reducing the surface pressure and for better ball guidance in the cylinder cover.
  • the effective degree of relief can on the one hand be designed to a maximum and on the other hand the degree of relief can be clearly and precisely predetermined, because in every pivot position the pressure force acts on the guide body in the direction of the axis of the guide body.
  • the piston 3 is designed as a hollow piston and the guide body 2 corresponding to a fully cylindrical component which is immersed in the hollow piston, in the construction according to FIG. 3, the guide body 2 'is provided with a cylindrical recess in which the fully cylindrical piston 3 'is guided so that the guide body 2' overlaps the piston 3 'in this construction.
  • elevations or the like can also be formed in the central region. It is essential that the hydraulically effective relief surface determined by the diameter de is present, which cuts the bearing surface 5 on the housing during the pivoting movement of the piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Hydraulic Motors (AREA)
  • Compressor (AREA)
  • Medicines Containing Plant Substances (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Medicines Containing Antibodies Or Antigens For Use As Internal Diagnostic Agents (AREA)
  • Medicines That Contain Protein Lipid Enzymes And Other Medicines (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP91121810A 1990-12-19 1991-12-19 Radialkolbenmotor Expired - Lifetime EP0491398B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4040738 1990-12-19
DE4040738 1990-12-19

Publications (2)

Publication Number Publication Date
EP0491398A1 EP0491398A1 (de) 1992-06-24
EP0491398B1 true EP0491398B1 (de) 1994-06-22

Family

ID=6420771

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91121810A Expired - Lifetime EP0491398B1 (de) 1990-12-19 1991-12-19 Radialkolbenmotor

Country Status (13)

Country Link
US (1) US5209155A (ko)
EP (1) EP0491398B1 (ko)
JP (1) JP3335655B2 (ko)
KR (1) KR920012701A (ko)
CN (1) CN1023825C (ko)
AT (1) ATE107739T1 (ko)
CA (1) CA2057933A1 (ko)
DE (1) DE59102013D1 (ko)
DK (1) DK0491398T3 (ko)
ES (1) ES2055956T3 (ko)
FI (1) FI915895A (ko)
PT (1) PT99868A (ko)
RU (1) RU2069794C1 (ko)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6622706B2 (en) 2000-05-30 2003-09-23 Robert H. Breeden Pump, pump components and method
WO2012063119A2 (en) 2010-11-10 2012-05-18 R. & D. S.R.L. Radial cylinder hydraulic machine with improved oscillating radial cylinder
ITMO20110001A1 (it) * 2011-01-10 2012-07-11 R & D Srl Macchina idraulica a cilindri radiali con cilindro oscillante perfezionato
CN107559047A (zh) * 2016-06-30 2018-01-09 埃克索埃斯公司 活塞型轴向膨胀器

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2674196A (en) * 1951-10-10 1954-04-06 Oilgear Co Piston assembly for axial type hydrodynamic machines
DE1453433C3 (de) * 1962-06-20 1975-05-28 Breinlich, Richard, Dr., 7120 Bietigheim Hyraulische Radialkolbenmaschine
US3789741A (en) * 1971-07-26 1974-02-05 Fmc Corp Hydrostatic bearing for radial piston pump
GB1468658A (en) * 1974-03-06 1977-03-30 Lucas Ltd Piston for use in a radial piston pump or motor
US4926744A (en) * 1974-11-29 1990-05-22 Karl Eickmann Radial piston hydraulic machine with piston having twelve circumferential fluid bearing pockets
US4776258A (en) * 1974-11-29 1988-10-11 Karl Eickmann Radial piston machine with pistons and piston shoes between faces
US4478133A (en) * 1977-02-03 1984-10-23 Karl Eickmann Arrangement on members which oscillate or pivot
FR2307985A1 (fr) * 1975-04-14 1976-11-12 Leduc Gerard Perfectionnements aux pompes hydrauliques a excentrique
US4366747A (en) * 1980-08-11 1983-01-04 J. I. Case Company Slipper arrangement for hydraulic pump
DE3046753C2 (de) * 1980-12-12 1986-02-27 Mannesmann Rexroth GmbH, 8770 Lohr Hydrostatische Radialkolbenpumpe

Also Published As

Publication number Publication date
JPH0579348A (ja) 1993-03-30
DK0491398T3 (da) 1994-11-07
RU2069794C1 (ru) 1996-11-27
ATE107739T1 (de) 1994-07-15
JP3335655B2 (ja) 2002-10-21
CN1023825C (zh) 1994-02-16
US5209155A (en) 1993-05-11
EP0491398A1 (de) 1992-06-24
CN1063741A (zh) 1992-08-19
FI915895A (fi) 1992-06-20
FI915895A0 (fi) 1991-12-13
DE59102013D1 (de) 1994-07-28
PT99868A (pt) 1993-11-30
ES2055956T3 (es) 1994-09-01
KR920012701A (ko) 1992-07-27
CA2057933A1 (en) 1992-06-20

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