EP0038372A1 - Moteur hydraulique - Google Patents

Moteur hydraulique Download PDF

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Publication number
EP0038372A1
EP0038372A1 EP80102148A EP80102148A EP0038372A1 EP 0038372 A1 EP0038372 A1 EP 0038372A1 EP 80102148 A EP80102148 A EP 80102148A EP 80102148 A EP80102148 A EP 80102148A EP 0038372 A1 EP0038372 A1 EP 0038372A1
Authority
EP
European Patent Office
Prior art keywords
piston
rotor
pistons
chamber
control pin
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.)
Granted
Application number
EP80102148A
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German (de)
English (en)
Other versions
EP0038372B1 (fr
Inventor
Rudolf Bock
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
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP80102148A priority Critical patent/EP0038372B1/fr
Priority to AT80102148T priority patent/ATE4001T1/de
Publication of EP0038372A1 publication Critical patent/EP0038372A1/fr
Application granted granted Critical
Publication of EP0038372B1 publication Critical patent/EP0038372B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
    • F03C1/2407—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders

Definitions

  • the invention relates to a hydraulic motor with the features mentioned in the preamble of the main claim.
  • a hydraulic motor is previously known from GB-PS 12 42 381.
  • the invention has for its object to make such hydraulic motors, which allow a compact design, by a simple displacement adjustment in each cylinder speed switchable.
  • the displacement can be adjusted in each cylinder, but this is only achieved by a very complex construction with separable piston heads in conjunction with a rotatable valve block .
  • the invention relates to a constructive solution that is favorable in terms of production technology, a high level of operational safety is guaranteed and the motor can be switched easily.
  • these properties are particularly important when using such hydraulic motors in vehicles exposed to vibrations, for example when installing such motors in wheel hubs.
  • the hydraulic motor designed according to the invention allows switching between more than two speeds.
  • FIG. 1 shows a central longitudinal section through the hydraulic motor 10.
  • Its stationary housing consists of two identical cylindrical housing halves 11 and 12, in each of which a control curve 13.1 and 13.2 shown in FIG. 2 is formed.
  • a rotor 14 is mounted in the housing via a ball bearing 15.1 and 15.2 in each housing half 11 and 12.
  • the rotor has a tubular central area, one end of which is closed by a flange wall 16, to which an output shaft, not shown, can be flanged coaxially.
  • a cylindrical control pin 18 with a widened outer connection head 19 is inserted from its open end face, via which the pressure medium is supplied and discharged to the hydraulic motor and which will be described in more detail below.
  • a star is formed by hollow radial pistons 22 distributed uniformly over the circumference of the rotor 14.
  • the radial pistons 22 can expediently be formed separately and then fastened to the tubular central part of the rotor 14 by brazing.
  • 4 and 5 show such a separately producible individual radial piston 22 of the piston star of the rotor. It has two concentric ring walls, an outer ring wall 35 and an inner ring wall 36, and is divided into two, each radially open to the outside chambers.
  • the first chamber is formed by the annular space 37 between the two concentric annular walls 35 and 36, while the second chamber 38 is formed by the cylindrical inner space 38 of the radial piston 22 enclosed by the inner annular wall 36.
  • the outer chamber 37 has an inner opening 39 and a corresponding opening in the tubular part of the rotor 14, while the second chamber 38 has an inner connection opening 40 which is offset in relation to the opening 39 in the axial direction of the hydraulic motor 10.
  • two driver stars consisting of individual driver webs 24.1 or 24.2 are formed on the outside of the rotor 14 symmetrically to the piston star and at the same distance from it.
  • the webs 24.1 and 24.2 of the two entraining stars are shaped in a manner which cannot be seen from the drawing, such that the spaces between the individual entraining webs have edges which run parallel to one another.
  • the cup-shaped cylinder 25 cooperating with the divided radial piston 22 is shown individually in FIG. 6. It has radial stepped journals 26 and 27 on two opposite sides, which are formed in one piece with it. In addition, it is provided on the inside with an annular groove 28 for receiving a narrow sealing ring 29 with a small coefficient of friction. In its cup-shaped part it has a concentric cylindrical piston shoulder 41, which at the level of the inner annular groove 28 of the cylinder also has an annular groove 42 for receiving a narrow sealing ring 43 (FIG. 1) is provided with a low coefficient of friction. The piston shoulder 41 projects with play into the cylindrical chamber 38 of the radial piston 22.
  • a needle-bearing control roller 30.1 or 30.2 is arranged on the inner step of the two axle journals 26 and 27, which is supported in abutment against the control cam 13.1 or 13.2 of the stationary housing.
  • a support roller 31.1 or 31.2 is arranged, which each protrude into an intermediate space between two driver webs 24.1 and 24.2 of the two driver stars of the rotor 14 and abut there against the parallel flanks of these driver webs .
  • the control pin 18 of the motor 10 is displaceable in the axial direction between a total of four different control positions, but is secured against rotation.
  • FIG. 7 and the two cross sections according to FIGS. 8 and 9 show, for each of its six inner longitudinal channels 44.1-44.6 it has four openings offset in the axial direction, for example 45.1-45.4, 46.1-46.4 and 47.1- 47.4.
  • the control pin 18 has two annular grooves 48 and 49.
  • the equal-ranking openings of all six longitudinal channels 44 each lie in the same cross-sectional plane, so that - including the two ring grooves 48 and 49 - one can speak of six control levels of the axially displaceable control pin 18.
  • FIGS. 8 and 9 show, for each of its six inner longitudinal channels 44.1-44.6 it has four openings offset in the axial direction, for example 45.1-45.4, 46.1-46.4 and 47.1- 47.4.
  • the control pin 18 has two annular grooves 48 and 49.
  • the equal-ranking openings of all six longitudinal channels 44
  • the longitudinal channels 44 form partly feed lines and partly return lines.
  • Fig. 1 shows the control pin 18 in its innermost control position.
  • the chambers 37 and 38 of the radial piston 22 are connected to the same longitudinal channels.
  • the chamber 38 is above the inner opening 40 and the opening 45.1 of the control pin 18 in connection with the longitudinal channel 44, while the chamber 37 is also connected to the longitudinal channel 44.1 via the inner opening 39 of the rotor 14 and the opening 45.4 of the control pin 18. So that the entire effective area of the cylinder 25 is applied, and in the engine a torque in the same direction is generated with the full engine capacity.
  • FIG. 10 shows the control slide 18 in its third of four control positions, in which the piston chamber 37 shown communicates with the opening 47.4 and thus with the longitudinal channel 44.1, while the piston chamber 38 communicates with the opening 46.2 and thus with the adjacent longitudinal channel 44.6 of the control pin 18.
  • the effective cross section of the piston chamber 38 thus counteracts the effective ring cross section of the piston chamber 37.
  • the chamber 37 of the radial piston 22 shown is via the elongated opening 45.4 of the control pin 18 with the Longitudinal channel 44.1 connected, while the chambers 38 of all radial pistons are connected to one another via the annular groove 48 and are thus practically short-circuited.
  • the cylinders are therefore only exposed to part of their effective area.
  • the same picture emerges in the fourth Switch position of the control pin 18 when the chambers 37 of the radial piston are short-circuited by the annular groove 49 of the control pin and the chamber 38 of the radial piston shown is not connected to the longitudinal channel 44.1 via the opening 45.3 of the control pin 18.
  • the gap between the rotor 14 and the control pin 18 is sealed by a sealing ring 50 in the vicinity of the rotor opening.
  • the leakage oil occurring at the periphery of the control pin 18 can therefore not flow to the outside. Measures can be taken so that leakage oil can get into the intermediate space 51 between the flange wall 16 of the rotor and the inner end face of the control pin 18.
  • the control pin 18 secured against rotation is under the pretension of a compression spring 52, by means of which it is pressed into the first control position shown in FIG. 1.
  • the adjustment of the control pin 18 into the two control positions 2 and 3, in which it is fixed by a spring-loaded locking ball 53, which is fixed in locking notches 1, 2, 3, 4 designated by the numbers of the control positions, by introducing leakage oil into the intermediate space 51 causes where a build-up pressure acts on the entire cross-sectional area of the control pin 18.
  • the oil pressure built up in the intermediate space 51 is controlled by an adjustable pressure control valve 55, indicated schematically in FIG. 1, in a flexible leak oil line 54, which is connected downstream in the outflow direction.
  • the leakage oil line 54 is connected to the intermediate space 51 of the engine via a central longitudinal channel 56 of the control pin 18.
  • control pin 18 Given the large cross-sectional area of the control pin 18, a small change in the oil switching pressure is sufficient to produce a sufficiently large change in the thrust force on the control pin, so that sufficiently large forces for the axial displacement of the control pin 18 from a spring catch position into the next position against the force of the compression spring 52 are available and an exact switching is ensured.
  • the control pin 18 In the fourth control position and end position, the control pin 18 can also be held by a stop.
  • the holding force of the spring catches is designed so that its catch effect is only overcome by an increase in pressure in the intermediate space 51, which results in a change in force sufficient to move the control pin 18 against the force of the compression spring 52 until the next catch position.
  • a different design of the control pin also makes it possible to form other control variants, for example only two or three control stages or slow work steps forwards and a rapid return in reverse. If the effective cross-section of the piston chamber 38 and the corresponding cross-section of the piston shoulder 41 of the cylinder 25 are given an area which corresponds to a quarter of the total effective cylinder area, the following gradation of the effective cylinder areas results from the first to the fourth control stage of the control pin 18: starting of the area value four, which is present at the first control level and corresponds to the full effective cylinder area, there is an area value three at the second control level, the area value two at the third control level and the area value one at the fourth control level. With a constant supply of pressure oil, the following speed values result, starting from speed value 1 in the first control stage: in the second control stage the speed is 1.33 times the value 1, in control stage three twice and in Control level four finally four times the value.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP80102148A 1980-04-22 1980-04-22 Moteur hydraulique Expired EP0038372B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP80102148A EP0038372B1 (fr) 1980-04-22 1980-04-22 Moteur hydraulique
AT80102148T ATE4001T1 (de) 1980-04-22 1980-04-22 Hydraulischer motor.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP80102148A EP0038372B1 (fr) 1980-04-22 1980-04-22 Moteur hydraulique

Publications (2)

Publication Number Publication Date
EP0038372A1 true EP0038372A1 (fr) 1981-10-28
EP0038372B1 EP0038372B1 (fr) 1983-06-29

Family

ID=8186665

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80102148A Expired EP0038372B1 (fr) 1980-04-22 1980-04-22 Moteur hydraulique

Country Status (2)

Country Link
EP (1) EP0038372B1 (fr)
AT (1) ATE4001T1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2250784A (en) * 1990-11-24 1992-06-17 Rexroth Mannesmann Gmbh Radial piston motor.
FR2836960A1 (fr) * 2002-03-08 2003-09-12 Poclain Hydraulics Ind Moteur hydraulique a cylindres radiaux etages
DE102017130723B4 (de) 2016-12-21 2022-10-06 Jin-Tian Huang Hydraulik- und Pneumatikmotor mit einem niedrigen Energieverbrauch und einem hohen Gasdruck

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191009402A (en) * 1910-04-18 1911-06-19 Henry Selby Hele-Shaw Improvements in Pumps and Motors.
DE1528541A1 (de) * 1964-06-03 1970-04-23 Poclain Sa Geschwindigkeitssteuereinrichtung fuer einen Hydraulikmotor
US3787147A (en) * 1972-12-26 1974-01-22 Owatonna Tool Co Two-stage air-hydraulic booster
US3799034A (en) * 1972-10-06 1974-03-26 Gen Motors Corp Rotary fluid device
DE2452725A1 (de) * 1974-11-06 1976-05-20 Pleiger Maschf Paul Radialkolbenmotor
DE2853552A1 (de) * 1978-12-12 1980-06-19 Rudolf Bock Hydraulischer motor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191009402A (en) * 1910-04-18 1911-06-19 Henry Selby Hele-Shaw Improvements in Pumps and Motors.
DE1528541A1 (de) * 1964-06-03 1970-04-23 Poclain Sa Geschwindigkeitssteuereinrichtung fuer einen Hydraulikmotor
US3799034A (en) * 1972-10-06 1974-03-26 Gen Motors Corp Rotary fluid device
US3787147A (en) * 1972-12-26 1974-01-22 Owatonna Tool Co Two-stage air-hydraulic booster
DE2452725A1 (de) * 1974-11-06 1976-05-20 Pleiger Maschf Paul Radialkolbenmotor
DE2853552A1 (de) * 1978-12-12 1980-06-19 Rudolf Bock Hydraulischer motor

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2250784A (en) * 1990-11-24 1992-06-17 Rexroth Mannesmann Gmbh Radial piston motor.
GB2250784B (en) * 1990-11-24 1994-06-15 Rexroth Mannesmann Gmbh Radial piston motor
FR2836960A1 (fr) * 2002-03-08 2003-09-12 Poclain Hydraulics Ind Moteur hydraulique a cylindres radiaux etages
WO2003076799A1 (fr) * 2002-03-08 2003-09-18 Poclain Hydraulics Industrie Moteur hydraulique a cylindres radiaux etages
GB2403513A (en) * 2002-03-08 2005-01-05 Poclain Hydraulics Ind Hydraulic engine with stepped radial cylinders
GB2403513B (en) * 2002-03-08 2005-07-06 Poclain Hydraulics Ind Hydraulic motor with radial multistage cylinders
DE10392363B4 (de) * 2002-03-08 2015-01-22 Poclain Hydraulics Industrie Hydraulikmotor mit gestuften Radialzylindern
DE102017130723B4 (de) 2016-12-21 2022-10-06 Jin-Tian Huang Hydraulik- und Pneumatikmotor mit einem niedrigen Energieverbrauch und einem hohen Gasdruck

Also Published As

Publication number Publication date
ATE4001T1 (de) 1983-07-15
EP0038372B1 (fr) 1983-06-29

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