EP0223656A1 - Mechanismus, Motor oder Pumpe mit mindestens zwei verschiedenen aktiven Hubvolumen - Google Patents

Mechanismus, Motor oder Pumpe mit mindestens zwei verschiedenen aktiven Hubvolumen Download PDF

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Publication number
EP0223656A1
EP0223656A1 EP86402276A EP86402276A EP0223656A1 EP 0223656 A1 EP0223656 A1 EP 0223656A1 EP 86402276 A EP86402276 A EP 86402276A EP 86402276 A EP86402276 A EP 86402276A EP 0223656 A1 EP0223656 A1 EP 0223656A1
Authority
EP
European Patent Office
Prior art keywords
orifices
pairs
cylinders
cam
communication
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
EP86402276A
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English (en)
French (fr)
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EP0223656B1 (de
Inventor
Louis Bernard Bigo
Bernard René Allart
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.)
Poclain Hydraulics France SA
Original Assignee
Poclain Hydraulics France SA
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Publication date
Application filed by Poclain Hydraulics France SA filed Critical Poclain Hydraulics France SA
Publication of EP0223656A1 publication Critical patent/EP0223656A1/de
Application granted granted Critical
Publication of EP0223656B1 publication Critical patent/EP0223656B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel

Definitions

  • Mechanism motor or pump, with at least two separate active displacements.
  • Hydraulic motors are already known, and more generally pressurized fluid mechanisms, which, by means of a displacement selector, are capable of operating with at least two distinct displacements, therefore also of rotating at distinct rotational speeds. .
  • a fluid distributor linked in rotation to the cam, distributes the fluid to the cylinders, in which the pistons are slidably mounted: such a distributor can, among other embodiments, be either cylindrical in shape or have a face plane (distributor known as "plan").
  • a displacement selector has the primary effect of grouping the cylinders of a mechanism into several distinct sets of cylinders, or alternatively of grouping the supplies corresponding to the undulations of the cam according to several distinct groups of undulations.
  • the invention belongs to the field of these various mechanisms, the descriptions of some of which are revealed in French patents FR-A- 1 411 047 (engine with several displacements, provided with a cylindrical distributor and a selector grouping the cylinders into several sets); FR-A-1 563 866 (engine similar to the previous one, but with a selector grouping the power supplies according to several groups of corrugations of the cam), and FR-A- 2 365 041 (engine with several displacements comprising a flat distributor).
  • the subject of the invention is therefore a first type of hydraulic mechanism, motor or pump, constituted by a cylinder block, a plurality of cylinders, which are formed in the cylinder block, inside each of which slides a piston, each cylinder being provided with an orifice for communication with the exterior of the cylinder, a cam, relative to which the cylinder block is rotatably mounted about an axis of rotation, on the surface of which the pistons are capable of being supported, and, which comprises a plurality of ramps succeeding each other in pairs of ramps, a first ramp of a pair moving away from the cylinder block with respect to the general direction of sliding of a piston, while pressing on said cam, and, the second ramp of said pair bringing the cylinder block closer to said general direction of sliding of the piston, two chambers capable of containing one a high pressure fluid, the other a low pressure fluid, a fluid distributor which is held integral in rotation with the cam, and, which has as many pairs of orifices as the cam has pairs of ramps, the two or
  • the invention also relates to a second type of hydraulic mechanism, motor or pump, consisting of a cylinder block, a plurality of cylinders, which are formed in the cylinder block, inside each of which slides.
  • a piston each cylinder being provided with an orifice for communication with the outside of the cylinder
  • a cam with respect to which the cylinder block is rotatably mounted about an axis of rotation, on the surface of which the pistons are likely to be in support, and, which comprises a plurality of ramps succeeding each other by pairs of ramps, a first ramp of a pair moving away from the cylinder block relative to the general direction of sliding of a piston, then in support on said cam, and, the second ramp of said pair approaching the cylinder block with respect to said general direction of sliding of the piston, two chambers capable of containing one a high pressure fluid, the other a low fluid pressure, a distributor fluid which is kept integral in rotation with the cam, and, which comprises as many pairs of orifices as the cam comprises pairs of ramps
  • the first additional arrangement consisted in having chosen the profiles of the cams in such a way that each of the operating displacements remains constant: it is said that the mechanism is "constant velocity" and this arrangement has the advantage of making it possible to obtain a speed constant rotation of the mechanism for the displacement concerned and for a determined fluid flow.
  • the second complementary arrangement was to make the smallest of the operating cubic capacities by eliminating the alternative communication of some of the cylinders with the high and low pressure chambers of the mechanism, by choosing these cylinders distributed angularly in a regular manner around the axis of rotation. : for example, during a rotation around the axis of rotation, by isolating one cylinder out of two, successively, from at least one of the two said enclosures.
  • the invention consisted in overcoming the technical prejudice relating to the abovementioned obtaining of the weak or zero resultant of the forces along the axis of rotation or "axial forces", in choosing a priori a bad solution from this point of view, know a solution leading to the generation of a non-zero resultant of these efforts and therefore to a certain imbalance of the corresponding mechanism by its very design, and, then, to highlight the possible realization of "homokinetic” mechanisms, having several ( at least two) separate operating displacements and satisfactory cam profiles with regard to their radii of curvature.
  • the aforementioned serious drawback of the previously known mechanisms is eliminated, making this type of mechanism industrially usable, certainly at the cost of generating a parasitic resultant force on the axis of rotation.
  • the invention therefore relates to the adoption, for a mechanism of the aforementioned first type, of the arrangements according to which, in the second configuration, the pairs of ramps of the cam corresponding to the pairs of orifices in the first group of pairs of distributor orifices are angularly distributed around the axis of relative rotation of the cylinder block with respect to the cam in an irregular manner.
  • the pairs of ramps of the cam are in even number
  • the number of pairs of orifices of the first group of pairs of orifices of the distributor is at most equal to half the total number of pairs of orifices
  • said pairs of orifices of the first group are distributed along an arc of a circle representing said relative rotation greater than 180 °.
  • the subject of the invention is a mechanism of the aforementioned second type, it relates to the adoption in this mechanism of the arrangement according to which, in the second configuration, the cylinders of said first group are angularly distributed around said axis of relative rotation irregularly, that is to say with angular intervals between the axes of two consecutive cylinders of this first group of cylinders which are unequal with regard to the angular intervals corresponding to at least some of the pairs of two consecutive cylinders of the first group of cylinders.
  • the cylinders are in even number, and on the other hand, in the second configuration, the number of cylinders of the first group is at most equal to half of the total number of cylinders, in this second configuration said cylinders of the first group are distributed along an arc representing said rotation relative greater than 180 °.
  • the advantage of the invention is the new possibility of producing "homokinetic" mechanisms, having several displacements and having satisfactory mechanical strength. A number is enough to measure the progress made: the lifespan of these new mechanisms compared to previous mechanisms, has simply been multiplied by a factor between 4 and 10.
  • the hydraulic motor in Figure 1 includes: - a casing in two parts 1 a and 1 b ; - A cam 2, wavy, disposed between the joint planes of parts 1 a and 1 b of the housing, this cam 2 and these two parts 1 a and 1 b being made integral by screws 3; - an output shaft 4, which is rotatably mounted, relative to the casing 1 a -1 b , about an axis of rotation 5, by means of roller bearings 6, the inner end of the shaft 4 being further provided with grooves 7; - A cylinder block 8, which has a central bore provided with grooves 9, which is rotatably mounted relative to the housing 1 a -1 b , by cooperation of its grooves 9 with the grooves 7 of the shaft 4, which is therefore therefore integral in rotation with said shaft 4, and which has a flat face 10 perpendicular to the axis of rotation 5; - Cylinders 11, which are arranged radially in the cylinder block 8 and angularly spaced regularly; - pistons 12 sliding
  • the spring 38 pushes the slide 35 to the right (FIG. 1) and places the grooves 24 and 25 in communication, isolating from these two grooves, the third groove 26
  • the slide 35 is pushed to the left (FIG. 4) and puts the grooves 25 and 26 into communication, isolating from these two grooves, the groove 24.
  • This is the known prior provision.
  • the orifices 41 a and 42 have been tinted differently, on the one hand, to be distinguished, the orifices 42 has orifices 41 a , on the other hand to show that they contain the fluid of the source of fluid under pressure 29. On the contrary, the orifices 43 a have not been tinted, because they are in communication with the pressureless fluid reservoir 30.
  • a profile of the cam 2 such as that of FIG. 3, to which corresponds a constant overall displacement of the motor ("constant velocity" motor), and which, moreover, has radii of curvature large enough to guarantee satisfactory mechanical endurance.
  • this cam is constituted by a succession of pairs of ramps 2 a -2 b , the ramps 2 a corresponding to the sliding of a piston 12 which tends to come out of its cylinder 11, and the ramps 2 b corresponding to the reverse sliding of a piston, which tends to return to its cylinder, when the cylinder block effectively rotates in the direction of the arrow R.
  • ramps 2 a corresponds either an orifice 41 a , or an orifice 42 a
  • each ramp 2 b corresponds an orifice 43 a of the distributor 16. Subsequently, we will not distinguish the ramps 2 a and 2 b , to name a few than cam 2.
  • the ports 42 a are brought into communication with the pressureless fluid reservoir 30, by introducing the pilot fluid (37) into the operating chamber 36 , and thus pushing the drawer 35 to the left ( Figure 4).
  • FIG. 5 The diagram of the fluid supply to the cylinders is shown in FIG. 5, in which the orifices 42 a are shown to be untinted, since they contain the same fluid as the exhaust orifices 43 a . It is understood that the result of the forces due to the pressure in the active chambers of the cylinders communicating with the orifices 41 a is zero or substantially zero on the axis of rotation 5.
  • a "constant velocity" motor we observe l impossibility of designing a better profile for cam 2 than that of FIG. 6: however, this profile, different from that of FIG. 3 and achieving the constancy of the overall displacement of the engine (large and small displacements), is poor from the mechanical point of view, because some of its radii of curvature are too small.
  • the orifices 41 a , 42 a , 43 a are still angularly, regularly spaced, one of the following (angles A), an orifice 43 a being interposed between two other consecutive holes 41 a or 42 a ; on the other hand, what is new is the fact of having disposed all the orifices 41 a on the same side of a diameter L and, consequently, all the orifices 42 a on the other side of the diameter L . thus, about the axis 5, there is a hole 41 has angularly spaced from the next 2A, or 10A, so a very irregular distribution.
  • FIG. 7 the orifices 41 a , 42 a , 43 a are still angularly, regularly spaced, one of the following (angles A), an orifice 43 a being interposed between two other consecutive holes 41 a or 42 a ; on the other hand, what is new is the fact of having disposed all the orifices 41 a on the same side of
  • FIG. 8 It amounts to replacing one of the orifices 41 a , constantly supplied with pressurized fluid, by the orifice 42 a diametrically opposite.
  • the motors of FIGS. 1 to 9 are two-displacement motors with displacement selection by selection of cams opposite which the cylinders are or are not supplied with pressurized fluid.
  • the hydraulic motor in Figure 10 includes: - a casing in four parts 1 a , 1 b ; 1 c and 1 d assembled with screws 3 and bolts 31; - a double cam 2, wavy; - An output shaft 4, which is rotatably mounted relative to the housing about an axis of rotation 5, by means of bearings 6, the inner end of the shaft 4 being further provided with grooves 7; - A cylinder block 8, which has a central bore provided with grooves 9, which is rotatably mounted relative to the casing, by cooperation of its grooves 9 with the grooves 7 of the shaft 4, which is therefore thereby integral in rotation of said shaft 4, and which has a planar face 10 perpendicular to the axis of rotation 5; - Cylinders 11, which are arranged radially in the cylinder block 8, and angularly spaced regularly; - pistons 12 slidingly mounted in said cylinders 11, one per cylinder; - cylindrical rollers 13, rotatably mounted in pairs, one of each pair at the end of a beam 44
  • FIG. 14 is a section showing the regular distribution of the orifices 41 a , 43 a and showing, on the one hand, that the cam is constituted by a succession of pairs of ramps 2 a -2 b , on the other hand, that to each ramp 2 a corresponds an orifice 41 a , and to each ramp 2 b corresponds an orifice 43 a ;
  • Two grooves 45 and 46 which are formed in the cylinder block 8 and which open into a bore 47 of this cylinder block;
  • the cylinders 11 are therefore divided into two groups, the chambers 40 of which communicate with the face 10 of the cylinder block 8 by conduits
  • the orifices 49 a and 50 a through which the conduits 49 and 50 open into the flat face 10 of the cylinder block 8, are capable of being in periodic communication with the orifices 41 a and 43 a of the distributor 48.
  • Figures 12 and 13 show, for the engine of Figure 11, the distribution of the holes 49 a and 51a, which are in the XII-XII section of conduits 49 and 51.
  • only orifices 49 a (colored) can be placed in communication with the pressurized fluid source 29, the orifices 51a never being in communication with the source 29.
  • the configuration of figures 11, 12 and 13 show the small engine displacement, in which only half of the cylinders (those corresponding to the conduits 49) are periodically supplied with pressurized fluid.
  • the section corresponding to the selection of the large displacement has not been shown: in fact, in this section, all the orifices 49 a and 51 a are liable, successively, to be placed in communication with the source of pressurized fluid 29.
  • Such a known motor can be designed to be "constant velocity": in this case, it can be seen that the profile of the cams imposed is bad from the mechanical point of view, because some of its radii of curvature are too small, unlike the motors according to the invention ( Figures 12 and 13).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
EP86402276A 1985-10-16 1986-10-14 Mechanismus, Motor oder Pumpe mit mindestens zwei verschiedenen aktiven Hubvolumen Expired - Lifetime EP0223656B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8515352 1985-10-16
FR8515352A FR2588616B1 (fr) 1985-10-16 1985-10-16 Mecanisme, moteur a pompe, a au moins deux cylindrees actives distinctes.

Publications (2)

Publication Number Publication Date
EP0223656A1 true EP0223656A1 (de) 1987-05-27
EP0223656B1 EP0223656B1 (de) 1990-01-03

Family

ID=9323888

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86402276A Expired - Lifetime EP0223656B1 (de) 1985-10-16 1986-10-14 Mechanismus, Motor oder Pumpe mit mindestens zwei verschiedenen aktiven Hubvolumen

Country Status (7)

Country Link
US (1) US4724742A (de)
EP (1) EP0223656B1 (de)
JP (1) JPS62168972A (de)
DE (1) DE3668037D1 (de)
FI (1) FI85179C (de)
FR (1) FR2588616B1 (de)
IN (1) IN169761B (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989006604A1 (en) * 1988-01-14 1989-07-27 Stahlgruber Otto Gruber Gmbh & Co. Apparatus for mounting tyres
FR2673684A1 (fr) * 1991-03-04 1992-09-11 Poclain Hydraulics Sa Ensemble d'un moteur a fluide sous pression a plusieurs cylindrees et d'un frein associe.
EP0526333A1 (de) * 1991-08-01 1993-02-03 POCLAIN HYDRAULICS, Société Anonyme Druckflüssigkeitsvorrichtung mit Ausgleichsräumen

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2611816B1 (fr) * 1987-02-25 1989-07-13 Poclain Hydraulics Sa Mecanisme a fluide sous pression, moteur ou pompe, a plusieurs cylindrees
IT1221428B (it) * 1988-05-18 1990-07-06 Corghi Elettromecc Spa Gruppo di comando pluricilindrico,azionato a fluido,particolarmente adatto per macchine smontagomme
FR2644210B1 (fr) * 1989-03-07 1994-06-03 Poclain Hydraulics Sa Dispositif d'immobilisation mutuelle de deux elements montes a rotation relative
FR2678322B1 (fr) * 1991-06-25 1993-10-29 Poclain Hydraulics Sa Mecanisme a fluide sous pression comportant au moins deux cylindrees distinctes de fonctionnement.
DE4311997C2 (de) * 1993-04-13 2001-07-12 Sauer Sundstrand Gmbh & Co Hydraulikmotor
DE4439648A1 (de) * 1993-11-11 1995-05-18 Luk Fahrzeug Hydraulik Hydraulikpumpe
FI104014B1 (fi) * 1994-05-18 1999-10-29 Valmet Voimansiirto Oy Radiaalimäntähydraulimoottori ja menetelmä radiaalihydraulimoottorin säätämiseksi
JP3127842B2 (ja) * 1996-11-01 2001-01-29 ダイキン工業株式会社 カムモータ装置
DE19832696A1 (de) * 1998-07-21 2000-01-27 Mannesmann Rexroth Ag Radialkolbenmaschine mit Rollenführungen
WO2001061186A1 (de) * 2000-02-17 2001-08-23 Mannesmann Rexroth Ag Hydraulische steuerschaltung für einen hydromotor mit mindestens zwei geschwindigkeiten
EP1272735B1 (de) * 2000-04-11 2004-11-10 Bosch Rexroth AG Radialkolbenmaschine
FR2819023B1 (fr) 2000-12-28 2003-04-04 Poclain Hydraulics Ind Circuit de prelevement comprenant une valve de prelevement pour echange et/ou balayage du carter d'un moteur hydraulique
FR2820186B1 (fr) 2001-01-31 2004-03-12 Poclain Hydraulics Ind Dispositif d'echange pour un circuit ferme
FR2904380A1 (fr) * 2006-07-26 2008-02-01 Hydro Leduc Soc Par Actions Si Perfectionnement aux pompes a barillet
DE102008006123A1 (de) 2008-01-25 2009-07-30 Robert Bosch Gmbh Radialkolbenmaschine
DE102010034548A1 (de) 2010-08-17 2012-02-23 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
DE102012001365A1 (de) 2012-01-25 2013-07-25 Robert Bosch Gmbh Haltebremse für einen Antrieb
US20130205763A1 (en) 2012-01-31 2013-08-15 Mitsubishi Heavy Industries, Ltd. Method of controlling hydraulic machine to reduce torque ripple and/or bearing side load
DE102013217714A1 (de) 2013-09-05 2015-03-05 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
FR3030645B1 (fr) * 2014-12-17 2019-10-11 Poclain Hydraulics Industrie Appareil hydraulique a pistons radiaux
DE102016214967A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
DE102016214976A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine und Verfahren zum Betreiben einer hydrostatischen Radialkolbenmaschine
DE102016214978A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
EP4102051A1 (de) * 2021-06-07 2022-12-14 Robert Bosch GmbH Mehrkolbenmaschine mit mindestens drei schaltbaren verdrängungsvolumen

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1563866A (de) * 1968-02-07 1969-04-18
FR2365041A1 (fr) * 1976-09-21 1978-04-14 Poclain Hydraulics Sa Mecanisme hydraulique a plusieurs cylindrees
FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1411046A (fr) * 1964-06-03 1965-09-17 Poclain Sa Perfectionnements aux moteurs hydrauliques à bloc cylindre rotatif
US3760691A (en) * 1971-12-17 1973-09-25 Deere & Co Step variable displacement hydraulic motor
AU566382B2 (en) * 1982-12-24 1987-10-15 Renold Plc Cam driven piston pump with variable capacity control

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1563866A (de) * 1968-02-07 1969-04-18
FR2365041A1 (fr) * 1976-09-21 1978-04-14 Poclain Hydraulics Sa Mecanisme hydraulique a plusieurs cylindrees
FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989006604A1 (en) * 1988-01-14 1989-07-27 Stahlgruber Otto Gruber Gmbh & Co. Apparatus for mounting tyres
FR2673684A1 (fr) * 1991-03-04 1992-09-11 Poclain Hydraulics Sa Ensemble d'un moteur a fluide sous pression a plusieurs cylindrees et d'un frein associe.
EP0526333A1 (de) * 1991-08-01 1993-02-03 POCLAIN HYDRAULICS, Société Anonyme Druckflüssigkeitsvorrichtung mit Ausgleichsräumen
FR2679963A1 (fr) * 1991-08-01 1993-02-05 Poclain Hydraulics Sa Mecanisme a fluide sous pression muni d'enceintes d'equilibrage particulieres.
US5261318A (en) * 1991-08-01 1993-11-16 Poclain Hydraulics Pressure fluid mechanism provided with special balancing enclosures

Also Published As

Publication number Publication date
US4724742A (en) 1988-02-16
FI864184A0 (fi) 1986-10-16
JPS62168972A (ja) 1987-07-25
FR2588616A1 (fr) 1987-04-17
FI864184A (fi) 1987-04-17
EP0223656B1 (de) 1990-01-03
FI85179B (fi) 1991-11-29
FR2588616B1 (fr) 1988-01-08
FI85179C (fi) 1992-03-10
DE3668037D1 (de) 1990-02-08
IN169761B (de) 1991-12-21

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