US20140007766A1 - Hydraulic device - Google Patents

Hydraulic device Download PDF

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Publication number
US20140007766A1
US20140007766A1 US13/823,992 US201113823992A US2014007766A1 US 20140007766 A1 US20140007766 A1 US 20140007766A1 US 201113823992 A US201113823992 A US 201113823992A US 2014007766 A1 US2014007766 A1 US 2014007766A1
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Prior art keywords
contact
friction surface
assembly
assemblies
parts
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US13/823,992
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English (en)
Inventor
Stéphane Vidal
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Poclain Hydraulics Industrie
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Poclain Hydraulics Industrie
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Assigned to POCLAIN HYDRAULICS INDUSTRIE reassignment POCLAIN HYDRAULICS INDUSTRIE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: VIDAL, STEPHANE
Publication of US20140007766A1 publication Critical patent/US20140007766A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • F03C1/002—Reciprocating-piston liquid engines details; components parts
    • 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
    • F03C1/0403—Details, component parts specially adapted of such engines
    • 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
    • F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders
    • 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
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/061—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F03C1/0623—Details, component parts
    • F03C1/0628—Casings, housings
    • 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
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0663—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/145—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/128—Crankcases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49236—Fluid pump or compressor making

Definitions

  • the present invention relates to a hydraulic device such as a motor or a pump comprising a first assembly of parts comprising a housing part wherein a cylinder block is arranged, and a second assembly of parts fixed to said first assembly, said assemblies having respectively a first and a second contact face, the two contact faces being stressed towards each other and placed in mutual contact by means exerting axial stress.
  • the means exerting axial stress are here means exerting stress tending to bring the two contact faces towards each other, along an axis perpendicular to these faces.
  • the housing In hydraulic motors or pumps, the housing generally comprises several parts which are machined individually and which are assembled together. This assembly must allow the passage of torque.
  • the housing of a hydraulic motor has a cam part whereof the internal periphery is corrugated to cooperate with the pistons of the cylinder block and a part known as a distribution cover, arranged around the internal distributor which distributes fluid to the cylinders of the cylinder block.
  • a fixed housing In the case of a fixed housing, it is generally the distribution cover part which is fixed to a fixed part such as the chassis of a vehicle, and the cam part must be perfectly well fixed to this cover part without being capable of turning, since it is the rotation of the cylinder block relative to the cam which conditions the functioning of the motor.
  • the torque which is transmitted between the distribution cover and the cam part is the torque resisting the motor torque.
  • some hydraulic motors are provided with braking systems which are arranged in a housing part called a brake cover. This part is fixed to another housing part, for example the distribution cover and it must be perfectly well connected thereto to transmit braking torque.
  • the motor torque or the braking torque must also be transmitted between the different housing parts assembled together.
  • a contact face is usually provided on each of the assemblies.
  • Means screws, for example
  • exerting axial stress perpendicularly to the contact faces push the two contact faces towards each other and place them in mutual contact.
  • rotation relative to the other rotation of the two assemblies is generally blocked by means for fastening the two assemblies in fixed rotational position, generally screws.
  • screws serve as shearing element, that is, they transmit some of the torque between the two assemblies. Also, in addition to screws and when the torque to be transmitted is substantial, extra shearing elements, such as balls, pins, etc., can also be used if necessary.
  • a first aim of the invention is to overcome the above disadvantages using a device of the type presented in the introduction but comprising improved fastening means, for transmitting considerable torque between two parts of a hydraulic device without the need to multiply the screws or shearing elements connecting these two parts.
  • These means must especially enable sealing to be maintained relative to leaks of hydraulic fluid, at the level of the junction between the two assemblies of parts.
  • At least one of said first and second contact faces has a rough friction surface so it can allow transmission of high torque between the two assemblies.
  • the contact faces are capable of transmitting considerable torque between the two assemblies, and perhaps even more significant than with earlier known embodiments. In this way in a device according to the invention, the need to use shearing elements for transmission of torque is reduced, or even eliminated.
  • the invention particularly specifies the assembly of contact faces which are both metallic, the metals enabling transmission of high stress.
  • the invention can be implemented especially in a hydraulic device comprising a rotor and a stator, a hydraulic device of this type generally requiring the transmission of high torque, in particular if the device comprises braking means.
  • the invention can also be implemented in particular in devices wherein the second assembly of parts also comprises a housing part, the means exerting axial stress serving to secure the two housing parts to each other.
  • the rough friction surface can be arranged on all or part of the contact face.
  • the first assembly also comprises a fastening plate; the first and second contact faces are formed respectively on walls opposite said fastening plate and said second assembly; also, a third and a fourth contact face are formed respectively on walls opposite said housing part and said fastening plate.
  • this embodiment is fairly easy to execute.
  • the specific operations specifically especially those operations for preparing the rough friction surface, can relate to the fastening plate only.
  • fastening plate is (generally) smaller and less complex than the other parts making up the first or the second assembly (such as the housing part), it remains relatively easy to undertake the previously mentioned specific operations on the fastening plate.
  • the fastening plate can be made by common processes: the plate can be made by being cut from sheet metal, followed by peening and surface treatment increasing the surface hardness of the plate. So in this case, neither the housing part nor the second assembly needs any specific additional operation. Simple machining allowing them to receive the fastening plate may be necessary however.
  • one of said third and fourth contact face has a rough friction surface for increasing the value of maximal torque transmissible between the housing part and the fastening plate.
  • the two rough friction surfaces are arranged on the two opposite sides of the fastening plate, and the principle of securing in rotation according to the invention is implemented on each side of the fastening plate.
  • the friction surface must be roughened such that the device is capable of transmitting high torque between the two assemblies.
  • said friction surface or one of said friction surfaces has a roughness index Ra greater than 12 ⁇ m and preferably greater than 18 ⁇ m, or a roughness index Rz greater than 80 ⁇ m (roughness parameters Ra and Rz being defined by the standard ISO 4287).
  • Ra and Rz being defined by the standard ISO 4287.
  • said friction surface or at least one of said friction surfaces can be the object of surface treatment for increasing roughness, peening for example.
  • Such treatment or grit blasting not only cleans the contact face of the part, but also ensures that the relevant contact face has adequate roughness.
  • Other processes, for example grooving, are feasible for increasing the roughness of this contact face.
  • the surface treatment for increasing roughness is surface treatment without material input (in the sense where materials used are not intended to be incorporated into the friction surface).
  • treatments comprising input of grains of material are to be avoided, as such grains would be likely to flake off from the friction surface and could damage the hydraulic device if they were to be disseminated in the latter.
  • the friction surface occupies the major part of the contact face on which it is arranged, for example at least 80%, or even 95% of this surface.
  • said or at least one of said friction surfaces has a Vickers hardness greater than 450 Hv (Vickers hardness being measured as per standard EN ISO 6507-1).
  • said friction surface or at least one of said friction surfaces can follow surface treatment for increasing surface hardness, nitriding for example.
  • At least one contact face placed opposite a friction surface has a surface hardness of less than that of said friction surface.
  • the surface hardness HV contact of the relevant contact face is less by at least 20%, and if possible by at least 30%, than that HV friction of the friction surface opposite it.
  • HV contact is preferably less than HV friction * 0.8 (or even HV friction * 0.7).
  • the invention is particularly adapted to securing housing parts made of metals of relatively low hardness, for example cast iron, molten steel or even forged steel.
  • the fastening plate when a fastening plate is used, the fact that the fastening plate is a part separate from the parts which it secures allows relatively free choice of the material of the plate and surface treatments applied to the latter. It is possible to select particularly hard material for the plate; it is also relatively easy to apply treatments to the plate, whether for roughening the plate or for boosting its surface hardness. By comparison, it would generally be more complicated to apply such treatments to an entire housing part, these housing parts comprising zones machined with precision, which are relatively fragile and have to be preserved.
  • the invention offers an effective solution in terms of torque transmission, and is particularly simple to implement and inexpensive on an industrial scale.
  • a second aim of the invention is to propose a process for producing a hydraulic device of the type presented in the introduction, allowing a link for transmission of considerable torque between these two assemblies of parts to be made between the two assemblies of parts making up the device.
  • a first and a second assembly of parts are provided, such as:
  • step b) for formation of the rough friction surface can be made while step a) for providing the different assemblies of parts of the device is not yet complete.
  • the rough friction surface can be formed by applying to the relevant contact face one of the surface treatments for increasing roughness presented previously.
  • the production process also comprises, after step b), the following step c):
  • FIG. 1 is an axial sectional view of a hydraulic motor according to the invention
  • FIG. 2 is an exploded perspective view of part of the motor of FIG. 1 , in a first embodiment
  • FIG. 3 is an exploded perspective view of part of a motor similar to that of FIG. 1 but comprising a fastening plate, and constituting a second embodiment of the invention;
  • FIG. 3A is a section of a detail extracted from FIG. 3 , locally showing the form (in section) of the fastening plate;
  • FIG. 4 is an axial section of part of the motor of FIG. 3 ;
  • FIG. 5 is a section of a detail extracted from FIG. 4 , showing the arrangement of the fastening plate
  • FIG. 6 is an exploded local axial section of the part of the motor illustrated in FIG. 3 , showing the arrangement of the fastening plate;
  • FIG. 7 is an exploded perspective view of part of a motor similar to the motor of FIG. 3 , showing the fastening plate, in a third embodiment;
  • FIG. 8 is a section of a detail of the motor of FIG. 7 , showing the arrangement of the fastening plate.
  • FIGS. 9A and 9B are axial sections of a detail of a motor according to the invention in a fourth and a fifth embodiment, showing two other possible arrangements for the fastening plate.
  • the hydraulic motor 100 of FIG. 1 is a motor with radial pistons. It has a housing in four parts 1 A, 1 B, 1 C and 1 D.
  • the part 1 B has an undulating internal periphery and forms the cam against which the pistons of the cylinder block 2 react.
  • the cylinder block 2 illustrated in this case comprises two rows of offset cylinders and whereof the respective cylinders 2 ′ are offset angularly. Pistons 2 ′′ are arranged and slide in these cylinders.
  • the motor shaft 3 is arranged non-rotatably with respect to the cylinder block 2 by splines and extends in the part 1 A of the housing, which bears the bearings 4 of the motor.
  • the latter comprises an internal fluid distributor 5 whereof the distribution conduits 6 are connected alternatively to the cylinder conduits 7 of the cylinder block 2 .
  • the distributor extends inside the part 1 C of the housing, called a distribution cover.
  • a brake shaft 8 also extends inside the distributor, which, as for the shaft 3 , is fixed in rotation with the cylinder block 2 .
  • the end of this shaft opposite the cylinder block 2 extends in the part 1 D of the housing, called a brake cover.
  • This end and this brake part support braking members constituted in this case by discs 9 interposed between each other.
  • a brake piston 10 is stressed by a spring 11 to push the discs 9 into braking contact and can be controlled in reverse by pressurising fluid in a braking chamber 12 .
  • the motor 100 is of the type with rotating shaft, since its housing is fixed, the housing part 1 A comprising fastening elements not illustrated with for example the chassis of the vehicle.
  • Such a motor needs transmission of substantial torque, mainly in two operating modes: motor mode, and braking mode.
  • braking torque Inversely during braking, braking torque must be transmitted between the part 1 D of the housing and the parts 1 A, 1 B and 1 C.
  • the motor 100 comprises first of all contact faces for attaching these parts in pairs to the parts 1 A, 1 B and 1 C. These faces are flat and perpendicular to the axis of rotation A of the motor; these are faces 1 A′ and 1 B′ between parts 1 A and 1 B, 1 B′′ and 1 C′′ between parts 1 B and 1 C, 1 C′ and 1 D′ between parts 1 C and 1 D.
  • fastening screws 14 ensure that the parts 1 A, 1 B and 1 C are joined together, as is known.
  • the motor 100 first comprises screws 15 . These pull towards each other parts 1 C and 1 D and consequently, the contact faces 1 C′ and 1 D′, which constitute the first and second contact faces in terms of the invention.
  • the screws 15 are means exerting axial stress along axis A of the motor 100 , and press the contact faces 1 C′ and 1 D′ against each other.
  • the screws 15 are capable of transmitting a certain torque between the parts 1 C and 1 D.
  • the contact face 1 C′ has been the object of a particular arrangement. It has undergone peening followed by surface-hardening treatment. As a result of these treatments the face 1 C′ has become rough and is a friction surface capable of transmitting considerable torque between the parts 1 C and 1 D.
  • FIG. 3 A motor part illustrating a second embodiment of the invention is illustrated in FIG. 3 .
  • the first assembly in terms of the invention comprises not only the part 1 C, but also an additional part, specifically a fastening plate 22 .
  • the latter serves to transmit torque between the parts 1 C and 1 D.
  • This plate 22 is a washer arranged about an axis A of rotation of the device (motor 100 ).
  • washer designates a substantially flat part, pierced by a hole wherein another part enters.
  • the fastening plate can take the form of a washer also in the embodiments wherein the fastening plate comprises a rough surface on one side only).
  • Each of the two sides opposite the plate 22 has a rough friction surface ( 24 , 25 ).
  • the plate 22 is interposed between the contact faces 1 C′ and 1 D′ such that the friction surfaces 24 and 25 are respectively in contact with the contact faces 1 C′ and 1 D′.
  • the surfaces 24 and 1 D′, at the level of which the first assembly (part 1 C and plate 22 ) and the second assembly (part 1 D) are in contact constitute the first and second contact faces in terms of the invention.
  • the surfaces 1 C′ and 25 constitute the third and fourth contact faces in terms of the invention.
  • the friction surfaces 24 and 25 are aligned axially on either side of the fastening plate 22 .
  • the friction surfaces 24 and 25 extend exactly to the right of each other, in the axial direction, on either side of the plate 22 .
  • FIG. 2A shows the form of the friction surfaces 24 , 25 .
  • the projecting parts are pointed; they form peaks or points 26 (viewed in a section perpendicular to the plane of the plate).
  • the points 26 are pressed into the opposite contact surface (in this case, surfaces 1 C′ and 1 D′); they prevent any rotation, any relative sliding between the parts 1 C, 22 and 1 D.
  • the parts 1 C and 1 D present a surface hardness less than that of the plate 22 .
  • the plate is clamped by means of the screws 15 between the contact faces 1 C′ and 1 D′.
  • a specific pressing system can optionally be used to impose particularly strong pressure on the fastening plate, if necessary. Under the effect of this pressure, the points 26 penetrate therefore (superficially) the parts 1 C and 1 D.
  • the thickness really occupied by the plate 22 between the contact faces is substantially less than its initial thickness and is around the minimal thickness of the plate measured at the base of the reliefs of the friction surfaces (thickness e, FIG. 2A ). In practice, for a washer having a thickness of around 1 mm, a loss in thickness of the order of 0.1 to 0.3 mm during assembly can be confirmed.
  • the plate 22 When mounted in such a manner, the plate 22 is closely connected to the parts 1 C and 1 D and enables transmission of considerable torque to each other of these parts. Also, the invention can advantageously be implemented on novel devices during maintenance operation on devices, by retrofitting.
  • the second and/or the third contact face ( 1 C′, 1 D′) has an uptake recess 28 for the plate provided to receive the fastening plate 22 .
  • an uptake recess for the plate can be provided in an embodiment wherein the fastening plate has a rough surface on one side only).
  • the recess 28 is provided on the face 1 D′, the face 1 C′ remaining smooth. This is also the case in the variant presented in FIG. 9A .
  • only one ( 1 D′) of the second and the third contact faces comprises an uptake recess 28 for the plate, the other contact face 1 C′ being provided a recess.
  • uptake recesses 30 , 31 of the plate are made symmetrically on the two contact faces 1 C′ and 1 D′.
  • a sealing joint is positioned symmetrically between the two faces 1 C′ and 1 D′.
  • the plate 22 gives a clear gain in terms of torque transmission, generally specific arrangements must also be made to ensure sealing of the connection between the parts 1 C and 1 D. It can in fact be necessary to prevent any fluid leak from the inside to the outside of the motor 100 between the parts 1 C and 1 D.
  • the device 100 comprises sealing means 40 to prevent radial fluid passage between two contact faces ( 1 C′, 25 ; 24 , 1 D′) in mutual contact.
  • the sealing means 40 comprise two O-rings 42 , 43 arranged on either side of the washer 22 and coaxial with the latter. These joints extend continuously over the entire periphery of the motor to the right of the contact faces, and prevent any fluid going from the interior to the exterior of the motor, between the faces 1 C′ and 1 D′. They ensure continuous contact between the face 1 C′ and the plate 22 on the one hand, and between the plate 22 and the face 1 D′ on the other hand.
  • the plate 22 has sealing surfaces facing the joints 42 , 43 , that is, surfaces capable of creating sealing when the joints 42 , 43 are pressed on them.
  • these are smooth surfaces provided on the inner periphery of the plate 22 , on each side of the latter.
  • the sealing means 40 comprise two joints 44 , 45 fixed respectively on both sides of the washer 22 , overmoulded, for example. This embodiment simplifies installation of the plate 22 to the extent where the two joints are solid with the latter.
  • the sealing joint or sealing joints provided in the sealing means 40 can be arranged in different configurations.
  • the sealing means ( 40 ) comprise at least one sealing joint ( 42 , 43 , 46 ), arranged so as to create sealing between both a flat surface and also a groove 50 formed in the contact face 1 D′ and arranged to receive said sealing joint 46 and allow deformation of the latter.
  • the joint 46 is arranged to create sealing on the face 1 C′.
  • the face 1 D′ comprises a groove 50 provided to receive the joint 46 .
  • the plate 22 contributes to holding the joint 46 and the groove 50 is relatively shallow.
  • the term ⁇ flat surface>> signifies in particular that said flat surface against which the joint seals has no relief(s) likely to make contact with the joint so as to promote sealing. In this way advantageously creating sealing on this surface (said flat surface) requires no specific treatment, such as machining.
  • the sealing means 40 comprise a joint 46 , 47 interposed between the second contact face 1 D′ and the third contact face 1 C′ and placed directly in contact with each of these faces.
  • this joint can be placed radially inside or outside the washer. There is accordingly dissociation between the sealing function, ensured by the joint, and the torque transmission function, ensured especially by the plate 22 .
  • FIGS. 9A and 9B An exemplary embodiment is given in FIGS. 9A and 9B .
  • the sealing between the parts 1 C and 1 D of the housing is ensured conventionally by means of an O-ring arranged between the surfaces 1 C′ and 1 D′.
  • the joint in this case is placed radially inside the plate 22 , and is relatively independent of the latter.
  • the edge of the washer 22 is used to hold the joint ( 46 , 47 ).
  • the invention has been presented in the foregoing as a motor with radial pistons. Naturally, it can be implemented in numerous other types of hydraulic devices, especially pumps with axial pistons.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
US13/823,992 2010-09-17 2011-09-15 Hydraulic device Abandoned US20140007766A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR1057441 2010-09-17
FR1057441A FR2965020B1 (fr) 2010-09-17 2010-09-17 Dispositif hydraulique
PCT/FR2011/052124 WO2012035270A1 (fr) 2010-09-17 2011-09-15 Dispositif hydraulique

Publications (1)

Publication Number Publication Date
US20140007766A1 true US20140007766A1 (en) 2014-01-09

Family

ID=43902891

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/823,992 Abandoned US20140007766A1 (en) 2010-09-17 2011-09-15 Hydraulic device

Country Status (5)

Country Link
US (1) US20140007766A1 (fr)
CN (1) CN103210210B (fr)
DE (1) DE112011103103T5 (fr)
FR (1) FR2965020B1 (fr)
WO (1) WO2012035270A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016153042A1 (fr) * 2015-03-26 2016-09-29 Ｋｙｂ株式会社 Moteur hydraulique et son dispositif de freinage, et procédé de fabrication de dispositif de freinage

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US4688805A (en) * 1985-10-31 1987-08-25 Italtractor Meccanica Itm S.P.A. Annular front-sealing gasket assembly
EP1247135A1 (fr) * 2000-01-03 2002-10-09 Wesley Jessen Corporation Lentilles de contact comprenant un colorant orange
US20020157530A1 (en) * 2001-04-30 2002-10-31 Sauer-Danfoss Inc. Axial servo control
US20040208759A1 (en) * 2003-04-18 2004-10-21 Eon-Pyo Hong Motor fixing structure of reciprocating compressor
US20060039801A1 (en) * 2004-07-15 2006-02-23 Xingen Dong Hydrostatic transmission
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US7866942B2 (en) * 2006-01-30 2011-01-11 Harvie Mark R Dry running flexible impeller pump and method of manufacture

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JPS58124002A (ja) * 1982-01-20 1983-07-23 Toyota Motor Corp タ−ボチヤ−ジヤのインペラ組み付け方法
CA2288462A1 (fr) * 1999-11-03 2001-05-03 Patrick Renaud Piece de liaison d'une pompe
GB0224727D0 (en) * 2002-10-24 2002-12-04 Holset Engineering Co Compressor wheel assembly
US20090056123A1 (en) * 2007-08-28 2009-03-05 Itt Manufacturing Enterprises Inc. Friction lock design for adjustable pump head to allow for 360° rotation

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US3279972A (en) * 1962-08-03 1966-10-18 Int Harvester Co High friction gasket and method of manufacturing same
US4688805A (en) * 1985-10-31 1987-08-25 Italtractor Meccanica Itm S.P.A. Annular front-sealing gasket assembly
EP1247135A1 (fr) * 2000-01-03 2002-10-09 Wesley Jessen Corporation Lentilles de contact comprenant un colorant orange
US20020157530A1 (en) * 2001-04-30 2002-10-31 Sauer-Danfoss Inc. Axial servo control
US20040208759A1 (en) * 2003-04-18 2004-10-21 Eon-Pyo Hong Motor fixing structure of reciprocating compressor
US20060039801A1 (en) * 2004-07-15 2006-02-23 Xingen Dong Hydrostatic transmission
US7866942B2 (en) * 2006-01-30 2011-01-11 Harvie Mark R Dry running flexible impeller pump and method of manufacture
US7695258B2 (en) * 2006-05-08 2010-04-13 White Drive Products, Inc. Gerotor motor and brake assembly

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016153042A1 (fr) * 2015-03-26 2016-09-29 Ｋｙｂ株式会社 Moteur hydraulique et son dispositif de freinage, et procédé de fabrication de dispositif de freinage
JP2016183621A (ja) * 2015-03-26 2016-10-20 Ｋｙｂ株式会社 液圧モータ、そのブレーキ装置及びブレーキ装置の製造方法

Also Published As

Publication number Publication date
CN103210210A (zh) 2013-07-17
FR2965020A1 (fr) 2012-03-23
CN103210210B (zh) 2015-12-02
FR2965020B1 (fr) 2012-10-12
WO2012035270A1 (fr) 2012-03-22
DE112011103103T5 (de) 2013-06-27

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Effective date: 20130923

STCB Information on status: application discontinuation

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