EP3055565B1 - Machine à plateau incliné - Google Patents

Machine à plateau incliné Download PDF

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Publication number
EP3055565B1
EP3055565B1 EP14771229.3A EP14771229A EP3055565B1 EP 3055565 B1 EP3055565 B1 EP 3055565B1 EP 14771229 A EP14771229 A EP 14771229A EP 3055565 B1 EP3055565 B1 EP 3055565B1
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EP
European Patent Office
Prior art keywords
bearing
bearing block
housing
swashplate machine
fastened
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.)
Not-in-force
Application number
EP14771229.3A
Other languages
German (de)
English (en)
Other versions
EP3055565A1 (fr
Inventor
Matthias Greiner
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3055565A1 publication Critical patent/EP3055565A1/fr
Application granted granted Critical
Publication of EP3055565B1 publication Critical patent/EP3055565B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles

Definitions

  • the present invention relates to a swashplate machine according to the preamble of claim 1 and a drive train according to the preamble of claim 11.
  • Swash plate machines serve as axial piston pumps for converting mechanical energy into hydraulic energy and as axial piston motor for converting hydraulic energy into mechanical energy.
  • a cylinder drum with piston bores is rotatably or rotatably mounted and pistons are arranged in the piston bores.
  • the cylinder drum is fixedly connected to a drive shaft and a hydraulic fluid acts temporarily on a first part of the rotating piston bores under high pressure and a hydraulic fluid acts temporarily on a second part of the rotating piston bores at low pressure.
  • a pivoting cradle is pivotally mounted about a pivot axis and on the pivoting cradle are on a flat support surface sliding shoes, which are attached to a retaining disc. The pistons are attached to the sliding shoes.
  • the retaining disc with the sliding shoes together with the cylinder drum performs a rotational movement about an axis of rotation and a flat bearing surface of the pivoting cradle is at an acute angle, for example between 0 ° and + 20 ° and between 0 ° and -20 ° as a swivel angle aligned with the axis of rotation of the cylinder drum.
  • the pivoting cradle is by two hydraulic pivoting devices, each of which is formed by an adjusting piston and an adjusting cylinder to a Swivel axis pivots.
  • the pivoting cradle is pivotally supported by a pivot bearing about the pivot axis.
  • two fixed, teilzylindermantelförmige bearing shells are indirectly attached to the housing by the bearing shells are attached to a bearing block and the bearing block is attached directly to the housing.
  • At the two bearing shells are each pivotable, formed on the pivoting cradle part cylinder shell-shaped counter-cups on.
  • the weighing storage is designed as a sliding bearing between the bearing and counter bearing shells.
  • the partially cylindrical bearing shell is attached to two part-cylindrical partial surfaces of the bearing block and for the production of partially cylindrical partial surfaces of the one-piece bracket is a complex and difficult spanabwede machining due to the overall geometry of the one-piece bracket necessary.
  • a large axial length of the one-piece bracket in the direction of the axis of rotation of the drive shaft is required so that a small bending occurs during machining with the machining tool.
  • This large axial length leads disadvantageously to a greater axial length of the entire swash plate machine.
  • the EP 1 013 928 A2 shows an axial piston pump in a swash plate design with a driven circumferential and a plurality of piston bores arranged therein cylinder barrel, wherein in each separated by webs piston bores linearly between a bottom dead center and a top dead center movable pistons are arranged and a Niederchristan gleichniere and a Hochbuch Hochtik kidney having control disc provided is.
  • the CH 405 934 shows a Schrägusionnaxialkolbenpumpe whose non-rotating cylinder block for varying the flow rate in dependence on the delivery pressure is longitudinally displaceable, wherein on the pressed by a spring in the direction of increasing the delivery cylinder block a control slide unit is fixed with a spool.
  • the DE 27 33 870 C2 shows a control device for a Schrägeninaxialkolbenpumpe, in which on both sides of the cradle for Pivoting the swash plate ever engages a hydraulically actuated swing wing on the engine, both motors are controllable by means of a pivotable about the pivot axis of the cradle arranged plate-shaped control valve spool and are used to adjust the flow rate of the pump.
  • a swivel-bearing of an axial machine is known with a housing, a pivoting cradle and formed by the housing and the pivoting cradle pivotal bearing area.
  • the pivoting cradle and / or the housing and / or a bearing element arranged in the pivotal rolling bearing area are designed to be deformable such that a deflection of the pivoting cradle can be compensated.
  • Another swashplate machine is off US 2009/0120279 known. This has a one-piece storage for the cradle.
  • Swash plate machine as axial piston pump and / or axial piston motor, comprising a cylinder drum rotatable about a rotation axis and having piston bores, pistons movably mounted in the piston bores, a pivoting cradle mounted pivotably about a pivot axis, a housing, a cradle support for the pivot cradle with at least one fixed cradle Bearing shell on a bearing block and with at least one pivotable counter-bearing shell on the pivoting cradle, wherein the bearing block is formed in several parts.
  • the partially cylindrical partial surfaces for the attachment of the bearing shells can be machined with high accuracy with a small axial length in the direction of the axis of rotation of the drive shaft.
  • a part of the bearing block can be clamped in a tool and then made particularly accurate at a low bending due to a machining tool.
  • a very small axial length of the multi-part bearing block is possible and still an evasive accurate machining of part-cylindrical surfaces on the multi-part bracket possible.
  • the swash plate machine overall advantageously has a small axial length.
  • the bearing block is formed in three parts and / or the fixed bearing shell is indirectly attached to the multi-part bearing block to the housing and / or the multi-piece bracket is, in particular directly attached to the housing.
  • the fixed bearing shell is fixed to the multi-part bearing block and the bearing block is fixed to the housing.
  • the stationary bearing shell is indirectly fixed by means of the bearing block on the housing, in particular a flange of the housing.
  • the weighing bearing has two stationary bearing shells and a first bearing shell is fastened to a first bearing block part and the second bearing shell is fastened to a second bearing block part and / or the multi-part bearing block is designed as an additional component in addition to the housing.
  • the first and second bearing block part in particular directly, attached to a third bearing block part and / or on the first and / or second bearing block part depending on a fixed bearing shell, in particular directly attached.
  • the partly cylindrical partial surfaces on the first position block part and on the second position block part can thus be produced particularly simply with high accuracy, since the first and second bearing block parts are simply fastened in a processing machine and then machined by a machining tool on the partial surfaces can be, with a slight bending of the first and second Lübockmaschines.
  • the three-part bearing block has a total of a small axial length in the direction of the axis of rotation of the drive shaft.
  • the first and second bearing block part each have a partially cylindrical partial surface on which each of the partially cylindrical bearing shell is attached.
  • the third bearing block part in particular directly, is preferably fastened to the housing, in particular to a flange of the housing.
  • the third bearing block part as a ring, in particular a disc-shaped ring formed.
  • the third bearing block part is formed a disk-shaped ring and the ring has an opening for the passage of the drive shaft.
  • the inner end sides of the multi-part bearing block have a small distance from the axis of rotation of the drive shaft at or a small distance to the outside of the drive shaft.
  • the distance of the two bearing shells from each other is small and the bending of the pivoting cradle due to the force applied by the shoes on the support surface of the pivoting cradle pressure forces is low in an advantageous manner.
  • the distance between the two bearing shells is independent of the outer diameter of a bearing for the drive shaft at the opening of the housing. Only by using, for example, geometrically different first and second bearing block parts with an identical third bearing block part, can the two bearing shells be fastened to different bearings for the drive shaft.
  • the first and second bearing block part are fastened to the third bearing block part with a fastening bolt or fastening pin.
  • first and / or second bearing block part is positively and / or non-positively and / or materially secured to the third bearing block part, for example by means of a recess form-fitting manner on the third bearing block part and / or with a screw connection and / or with a press connection and / or with a welded connection and / or non-positively due to the pressure force between the first and second bearing block part and the third bearing block part.
  • the third bearing block part is positively and / or non-positively and / or materially attached to the housing, in particular a flange of the housing, for example by means of a screw and / or a rivet and / or positively due to a recess in the housing and / or with a welded joint and / or non-positively due to the compressive force in the direction of the axis of rotation of the drive shaft between the housing and the third bearing block part.
  • the housing and the bearing block parts made of metal, for. As steel or aluminum, and / or the housing and the bearing block parts are made of an identical material.
  • the first and / or second and / or third bearing block part has at a radial inner side a smaller minimum distance, in particular by 10%, 20%, 30% or 40% smaller distance to the axis of rotation of the cylinder drum than the housing, in particular a flange, at an opening with a bearing for the drive shaft.
  • the first and second bearing block part thus have a small distance from each other, so that thereby a slight bending on the pivoting cradle occurs.
  • the swash plate machine is designed such that the at least one bearing surface and / or the at least one counter-bearing surface in the region of an inner end side facing the drive shaft has a smaller rigidity in a direction parallel to the pivot axis of the pivoting cradle than in the region of an outer end side facing away from the drive shaft , Due to the smaller rigidity of the at least one bearing surface in the region of the inner end side compared to the outer end side and due to the larger bends of the bearing surface in the region of the inner end side in comparison to the region on the outer end side occurs between the bearing surface and the counter surface advantageously a substantially same Surface pressure on.
  • the area preferably comprises less than 10%, 20% or 30% of the total extent of the bearing surface and / or the abutment surface in the direction parallel to the pivot axis.
  • the bearing surface and / or the abutment surface is formed in a section, in particular in all sections, perpendicular to the pivot axis as a circular segment with an identical distance to the pivot axis.
  • the longitudinal axis of a fictitious cylinder on the circle segment preferably corresponds to the pivot axis of the pivoting cradle.
  • the swash plate machine comprises two bearing shells and two counter-bearing shells and the two bearing shells and two counter-bearing shells are arranged in a, in particular identical, distance from the axis of rotation of the drive shaft.
  • the at least one bearing shell is formed by a separate bearing shell part, which is attached directly or indirectly to the first and second bearing block part of the swash plate machine.
  • the bearing shell part is a separate component and consists of a different material than the housing and / or the bearing block, for example plastic, PEEK or brass.
  • the counter-bearing shell is formed directly from the pivoting cradle made of steel, so that thereby the bearing surface and the counter-bearing surface are formed of a different material or material to reduce the friction loss at the weighing storage.
  • the at least one counter bearing shell is formed by the pivoting cradle.
  • the swashplate machine on the housing and / or the pivoting cradle and / or on at least one bearing block part and / or on a bearing for the drive shaft and / or on the at least one bearing shell and / or on the at least one counter-bearing shell in the area the inner end side of a recess and / or a cavity and / or a relief.
  • the pivot axis of the pivoting cradle is aligned perpendicular to the axis of rotation of the drive shaft and the cylinder drum.
  • the bearing shell of a different material than the anvil shell.
  • the bearing switching part made of PEEK or brass and the counter bearing shell made of steel.
  • Drive train for a motor vehicle, comprising at least one swash plate machine for converting mechanical energy into hydraulic energy and vice versa, at least one pressure accumulator, wherein the swash plate machine is designed as a swash plate machine described in this patent application.
  • the drive train includes two swash plate machines, which are hydraulically connected to each other and act as a hydraulic transmission and / or the drive train comprises two pressure accumulator as high-pressure accumulator and low pressure accumulator.
  • the swashplate machine comprises a drive shaft which is connected at least in a rotationally fixed manner to the cylinder drum and which is mounted rotatably or rotatably about the rotation axis.
  • the swash plate machine comprises at least one pivoting device for pivoting the pivoting cradle.
  • the swash plate machine comprises a low-pressure opening for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores.
  • the swash plate machine comprises a high-pressure opening for discharging and / or introducing hydraulic fluid out of and / or into the rotating piston bores.
  • swash plate machine 1 serves as axial piston pump 2 for conversion or conversion of mechanical energy (torque, speed) in hydraulic energy (volume flow, pressure) or as axial piston 3 for conversion or conversion of hydraulic energy (flow, pressure) into mechanical energy ( Torque, speed).
  • a drive shaft 9 is mounted rotatably or rotatably about a rotation axis 8 by means of a bearing 10 on a flange 21 of a housing or multi-part housing 4 and with a further mounting 10 on the housing 4 of the swash plate machine 1 ( Fig. 1 ).
  • the drive shaft 9 is a cylinder drum 5 rotatably and connected in the axial direction, wherein the drive shaft 9 and the cylinder drum 5 are formed in one or two parts and the boundary between the drive shaft 9 and the cylinder drum 5 in Fig. 1 is shown in dashed lines.
  • the cylinder drum 5 carries out the rotational movement of the drive shaft 9 with due to a rotationally fixed connection.
  • a plurality of piston bores 6 with an arbitrary cross section, for example square or circular, incorporated.
  • the longitudinal axes of the piston bores 6 are aligned substantially parallel to the axis of rotation 8 of the drive shaft 9 or the cylinder drum 5.
  • In the piston bores 6 each have a piston 7 is movably mounted.
  • a pivoting cradle 14 is mounted pivotably about a pivot axis 15 on the housing 4.
  • the pivot axis 15 is perpendicular to the plane of Fig. 1 and parallel to the drawing plane of Fig. 2 aligned.
  • the axis of rotation 8 of the cylinder drum 5 is parallel to and in the plane of Fig. 1 arranged and perpendicular to the drawing plane of Fig. 2 ,
  • the housing 4 defines an interior space 44 which is filled with hydraulic fluid.
  • the pivoting cradle 14 has a flat or planar bearing surface 18 for the indirect support of a retaining disk 37.
  • the retaining plate 37 has bores (not shown), within which a respective sliding shoe 39 is arranged.
  • the sliding blocks 39 are located directly on the support surface 18 of the pivoting cradle 14.
  • Each shoe 39 is connected to a respective piston 7.
  • the sliding block 39 has a bearing ball 40 (FIG. Fig. 1 ), which is fixed in a bearing cup 59 on the piston 7, so that a piston joint 22 between the bearing ball 40 and the bearing cup 59 is formed on the piston 7.
  • the partially spherical trained bearing ball 40 and bearing cup 59 are both complementary or spherical, so characterized in a corresponding possibility of movement between the bearing ball 40 and the bearing cup 59 on the piston 7, a permanent connection between the piston 7 and the shoe 39 is present. Due to the connection of the piston 7 with the rotating cylinder drum 5 and the connection of the bearing cups 59 with the sliding blocks 39, the sliding blocks 39 perform a rotational movement about the axis of rotation 8 with and due to the arrangement of the sliding blocks 39 in the holes of the retaining plate 37 also performs the retaining disc 37 a rotational movement about the rotation axis 8 with out.
  • the retaining plate 37 is in constant indirect contact with the support surface 18 of the pivoting cradle 14, this is by a compression spring 41 under a Pressing force on the support surface 18 is pressed so that the sliding shoes 39 are pressed by the compression spring 41 on the support surface 18 directly.
  • the pivoting cradle 14 is - as already mentioned - pivotally mounted about the pivot axis 15 and further comprises an opening 42 (FIG. Fig. 1 ) for the implementation of the drive shaft 9.
  • a weighing storage 20 is formed on the housing 4.
  • two counter bearing shells 23 are formed on the pivoting cradle 14.
  • the two pivotable counter bearing shells 23 on the pivoting cradle 14 are each on a bearing shell 17, so that the two bearing shells 17 and two counter-bearing shells 23 form the weighing storage 20.
  • a bearing surface 33 on the two bearing shells 17 is thus on an abutment surface 34 on the counter-bearing shells 23.
  • the counter-cups 23 are integrally formed by the pivoting cradle 14 made of steel.
  • the pivoting cradle 14 is thus pivotally mounted about the pivot axis 15 by means of a plain bearing 20 as a pivot bearing.
  • a pivot angle ⁇ of approximately + 20 °.
  • the pivoting angle ⁇ is present between a fictitious plane perpendicular to the axis of rotation 8 and a plane spanned by the flat bearing surface 18 of the pivoting cradle 14 according to the sectional formation in FIG Fig. 1 ,
  • the pivoting cradle 14 can be pivoted between two pivoting angles ⁇ between + 20 ° and -20 ° by means of two pivoting devices 24.
  • the first and second pivoting means 25, 26 as pivoting means 24 has a connection point 32 between the pivoting device 24 and the pivoting cradle 14.
  • the two pivoting devices 24 each have an adjusting piston 29, which is movably mounted in an adjusting cylinder 30.
  • the adjusting piston 29 or an axis of the adjusting cylinder 30 is aligned substantially parallel to the axis of rotation 8 of the cylinder drum 5.
  • At one in Fig. 1 On the left end region of the adjusting piston 29, this has a bearing socket 31, in which a bearing ball 19 is mounted. In this case, the bearing ball 19 on a pivoting arm 16 ( Fig. 1 to 2 ) of the pivoting cradle 14 is present.
  • the first and second pivoting means 25, 26 is thus connected to a respective pivot ball 19 on a respective pivot arm 16 with the pivoting cradle 14.
  • the pivoting cradle 14 By opening one of the two valves 27, 28 as the first valve 27 on the first pivoting device 25 and the second valve 28 on the second feed device 26 as shown in FIG Fig. 1 can the pivoting cradle 14 are pivoted about the pivot axis 15, as this is applied to the adjusting piston 29 at the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30, a force.
  • an opening 63 is formed with the bearing 10 and a second side 65 has a recess for supporting the drive shaft 9 with a further storage 10.
  • a mechanical seal 74 is also arranged, so that the hydraulic fluid can not flow out of the inner space 44 to the outside.
  • the bearing surface 33 of the two bearing shells 17 rests on the abutment surface 34 on the pivoting cradle 14, respectively.
  • the bearing shell 17 is formed by two separate components, namely a first bearing shell 77 and a second bearing shell 78.
  • the three-part bearing block 79 comprises a first bearing block part 70, a second bearing block part 71 and a third bearing block part 72, wherein the third bearing block part 72 is formed as a disk-shaped ring 73.
  • the first and second bearing block part 70, 71 each have a partially cylindrical partial surface, on each of which the first bearing shell 77 and the second bearing shell 78 is attached.
  • the first and second bearing block parts 70, 71 and the first and second bearing shells 77, 78 are in a projection direction in the plan view of FIG Fig. 3 rectangular shaped.
  • the annular third bearing block part 72 is positively secured by means of a recess 75 on the flange 21 of the housing 4. Due to the compressive force between the flange 21 and the third bearing block part 72 is thus a positive and non-positive connection between the flange 21 and the third bearing block portion 72.
  • the third bearing block portion 72 has two separate recesses 76, each for positive reception of the first Bearing part 70 and the second bearing block part 71.
  • the first and second bearing part 70, 71 positively and non-positively connected to the third bearing block part 73.
  • the first and second bearing block parts 70, 71 are additionally fastened in a form-fitting manner to the third bearing block part 72 by means of a plurality of fastening bolts 61 or fastening pins 68.
  • the two bearing shell parts 62 as the first and second bearing shell 77, 78 are made of a different material, for.
  • PEEK or brass such as the abutment surface 34 of the pivoting cradle 14 and the flange 21 made of steel and the first, second and third bearing block part 70, 71, 72.
  • the bearing shell part 62 has the bearing surface 33.
  • the bearing surface 33 is formed teilzylindermantelelförmig.
  • an abutment shell 23 is provided, wherein the abutment shell 23 is also formed teilzylindermantelelförmig with an abutment surface 34 of the abutment shell 23.
  • a fictitious cylinder on the bearing surface 33 and the counter-surface 34 has a longitudinal axis which corresponds to the pivot axis 15 of the pivoting cradle 14.
  • the abutment surface 34 on the pivoting cradle 14 rests on the bearing surface 33 on the bearing shell part 62.
  • the bearing shell 17 and the counter bearing shell 23 thus form the weighing support 20 for the pivoting cradle 14.
  • the bearing block parts 70, 71, 72 are made of steel as the housing 4th
  • a bearing 10 for the drive shaft 9 and the mechanical seal 74 are arranged within the opening 63 of the flange 21, a bearing 10 for the drive shaft 9 and the mechanical seal 74 are arranged.
  • a circular cross-sectional boundary surface of the flange 21 thus limits the opening 63 and the minimum distance 38 between the axis of rotation 8 of the drive shaft 9 and this boundary surface of the flange 21 for the opening 63 is substantially greater than the minimum radial distance 43 between the axis of rotation 8 and a Radial inside 80 of the bearing block 79, in particular of the third bearing block part 72 as well as the first and second bearing block part 70, 71.
  • the two bearing block parts 70, 71 and thus resting thereon the first and second bearing shells 77, 78 and thus the two bearing surfaces 33 point it a small distance to the radial outer side of the drive shaft 9.
  • the pivoting cradle 14 has a slight bend.
  • the large required diameter of the opening 63 for the bearing 10 and the mechanical seal 74 can thus be compensated by the opening 63 projecting over the bearing block 79.
  • the drive train 45 has an internal combustion engine 46, which drives a planetary gear 48 by means of a shaft 47. With the planetary gear 48 two shafts 47 are driven, wherein a first shaft 47 is connected to a clutch 49 with a differential gear 56. A second or other shaft, which is driven by the planetary gear 48 drives a first swash plate machine 50 through a clutch 49 and the first swash plate machine 50 is hydraulically connected by means of two hydraulic lines 52 with a second swash plate machine 51. The first and second swash plate machines 50, 51 thereby form a hydraulic gear 60, and from the second swash plate machine 51, the differential gear 56 can also be driven by means of a shaft 47.
  • the differential gear 56 drives the wheels 57 with the wheel shafts 58.
  • the drive train 45 has two pressure accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55.
  • the two accumulators 53 are hydraulically connected by means not shown hydraulic lines with the two swash plate machines 50, 51, so that mechanical energy of the engine 46 in the high-pressure accumulator 54 can be hydraulically stored and also in a recuperation of a motor vehicle with the drive train 45 also kinetic energy of the motor vehicle in the high-pressure accumulator 54 can be stored hydraulically.
  • the differential gear 56 can additionally be driven with a swash plate machine 50, 51.
  • the bearing block 79 made of steel is designed in several parts, namely in three parts with the first bearing block part 70, the two bearing block part 71 and the third bearing block part 72.
  • the first and second bearing block part 70, 71 each have partially cylindrical part surfaces, on each of which the first and second bearing shell 77th , 78 are attached.
  • these partially cylindrical partial surfaces on the separate components of the first and second bearing block part 70, 71 can be produced particularly easily by a machining tool, for example a lathe or a milling cutter.
  • the first and second bearing block portion 70, 71 a small axial length in the direction of the axis of rotation 8 of the drive shaft 9 and thus also the total bearing block 79, since the third bearing block portion 72 is formed as a disc-shaped ring 73 with a small extension in the direction of As a result, the swash plate machine 1 as a whole has a small axial length and is simple and inexpensive to manufacture in terms of the bearing block 79.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

  1. Machine à plateau incliné (1) en tant que pompe à pistons axiaux (2) et/ou moteur à pistons axiaux (3), comprenant
    - un tambour cylindrique (5) monté de façon rotative ou tournante autour d'un axe de rotation (8), avec des alésages de pistons (6),
    - des pistons (7) montés de façon mobile dans les alésages de pistons (6),
    - une bascule pivotante (14) montée de façon pivotante autour d'un axe de pivotement (15),
    - un corps (4),
    - un support de bascule (20) pour la bascule pivotante (14) avec au moins une coquille de coussinet fixe (17) sur un support de palier (79) et avec au moins une coquille de coussinet opposée pivotante (23) sur la bascule pivotante (14),
    caractérisée en ce que le support de palier (79) est réalisé en plusieurs parties.
  2. Machine à plateau incliné selon la revendication 1, caractérisée en ce que
    - le support de palier (79) est réalisé en trois parties,
    et/ou
    - la coquille de coussinet fixe (17) est fixée indirectement au corps (4) avec le support de palier en plusieurs parties (79),
    et/ou
    - le support de palier en plusieurs parties (79) est fixé, en particulier directement, au corps (4).
  3. Machine à plateau incliné selon la revendication 1 ou 2, caractérisée en ce que le support de bascule (20) présente deux coquilles de coussinet fixes (17) et une première coquille de coussinet (77) est fixée à une première partie de support de palier (70) et la deuxième coquille de coussinet (78) est fixée à une deuxième partie de support de palier (71), et/ou le support de palier en plusieurs parties (79) est réalisé sous forme de composant supplémentaire (79) en complément du corps (4).
  4. Machine à plateau incliné selon la revendication 3, caractérisée en ce que la première et la deuxième parties de support de palier (70, 71) sont fixées, en particulier directement, à une troisième partie de support de palier (72), et/ou en ce qu'une coquille de palier fixe (17) est chaque fois fixée, en particulier directement, à la première et/ou à la deuxième partie de support de palier (70, 71).
  5. Machine à plateau incliné selon la revendication 4, caractérisée en ce que la troisième partie de support de palier (73) est fixée, en particulier directement, au corps (4), en particulier à une bride (21) du corps (4).
  6. Machine à plateau incliné selon la revendication 4 ou 5, caractérisée en ce que la troisième partie de support de palier (72) est réalisée en forme d'anneau (73), en particulier d'anneau en forme de disque (73).
  7. Machine à plateau incliné selon une ou plusieurs des revendications 4 à 6, caractérisée en ce que la première et la deuxième parties de support de palier (70, 71) sont fixées à la troisième partie de support de palier (72) avec un boulon de fixation (61) ou une broche de fixation (68).
  8. Machine à plateau incliné selon une ou plusieurs des revendications précédentes, caractérisée en ce que le corps (4) et les parties de support de palier (70, 71, 72) sont constitué(e)s de métal, en particulier d'acier ou d'aluminium,
    et/ou
    le corps (4) et les parties de support de palier (70, 71, 72) sont constitué(e)s d'un matériau identique.
  9. Machine à plateau incliné selon une ou plusieurs des revendications précédentes, caractérisée en ce que chaque face d'appui (33) sur la coquille de coussinet (17) s'applique respectivement sur une face d'appui opposée (34) de la coquille de coussinet opposée (23), et/ou en ce que la première et/ou la deuxième et/ou la troisième parties de support de palier (70, 71, 72) présentent sur un côté radial intérieur (80) une plus petite distance minimale (43), en particulier une distance plus petite de 10 %, 20 %, 30 % ou 40 %, par rapport à l'axe de rotation (8) du tambour cylindrique (5) que le corps (4), en particulier une bride (21), à une ouverture (63) avec un appui (10) pour l'arbre d'entraînement (9).
  10. Machine à plateau incliné selon une ou plusieurs des revendications précédentes, caractérisée en ce que la machine à plateau incliné (1) est réalisée en ce sens que ladite au moins une face d'appui (33) et/ou ladite au moins une face d'appui opposée (34) présente dans la région d'un côté d'extrémité intérieur (36) tourné vers l'arbre d'entraînement (9), dans une direction parallèle à l'axe de pivotement (15) de la bascule pivotante (14), une rigidité moins élevée que dans la région d'un côté d'extrémité extérieur (35) détourné de l'arbre d'entraînement (9).
  11. Chaîne cinématique (45) pour un véhicule automobile, comprenant
    - au moins une machine à plateau incliné (1) pour la conversion d'énergie mécanique en énergie hydraulique et inversement,
    - au moins un accumulateur d'énergie (53),
    caractérisée en ce que la machine à plateau incliné (1) est réalisée selon une ou plusieurs des revendications précédentes.
  12. Chaîne cinématique selon la revendication 11, caractérisée en ce que la chaîne cinématique (45) comprend deux machines à plateau incliné (1), qui sont entraînées de façon hydraulique l'une avec l'autre et qui fonctionnent comme transmission hydraulique,
    et/ou
    la chaîne cinématique (45) comprend deux accumulateurs d'énergie (53) en tant qu'accumulateur d'énergie à haute pression (54) et accumulateur d'énergie à basse pression (55).
EP14771229.3A 2013-10-08 2014-09-10 Machine à plateau incliné Not-in-force EP3055565B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310220231 DE102013220231A1 (de) 2013-10-08 2013-10-08 Schrägscheibenmaschine
PCT/EP2014/069298 WO2015051965A1 (fr) 2013-10-08 2014-09-10 Machine à plateau incliné

Publications (2)

Publication Number Publication Date
EP3055565A1 EP3055565A1 (fr) 2016-08-17
EP3055565B1 true EP3055565B1 (fr) 2017-11-15

Family

ID=51582360

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14771229.3A Not-in-force EP3055565B1 (fr) 2013-10-08 2014-09-10 Machine à plateau incliné

Country Status (4)

Country Link
EP (1) EP3055565B1 (fr)
CN (1) CN105745442B (fr)
DE (1) DE102013220231A1 (fr)
WO (1) WO2015051965A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015212601A1 (de) 2015-07-06 2017-01-12 Robert Bosch Gmbh Verfahren zur Steuerung und Regelung eines Antriebsstranges
CN108150479A (zh) * 2016-12-05 2018-06-12 江苏汉力士液压制造有限公司 分体式摇摆
DE102019116250B4 (de) * 2019-06-14 2023-02-16 Schaeffler Technologies AG & Co. KG Schwenkwiegenlagerung und Verfahren zur Herstellung einer Schwenkwiegenlagerung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH405934A (de) 1962-07-26 1966-01-15 Weatherhead Co Schrägscheiben-Axialkolbenpumpe
US4076459A (en) 1976-09-14 1978-02-28 Abex Corporation Horsepower limiter control for a variable displacement pump
EP1013928A3 (fr) 1998-12-22 2000-11-08 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation
JP4298684B2 (ja) * 2005-07-19 2009-07-22 株式会社カワサキプレシジョンマシナリ 液圧装置の斜板支持台装着構造
KR20080067959A (ko) * 2007-09-11 2008-07-22 가부시키 가이샤 가와사키 프리시젼 머시너리 사판식 피스톤 펌프ㆍ모터
US7891285B2 (en) * 2007-11-08 2011-02-22 Caterpillar Inc. Bearing restricting device in swash plate hydraulic pump or motor
DE102008013010A1 (de) 2007-12-28 2009-07-02 Robert Bosch Gmbh Schwenkwiegenlagerung für Axialkolbenmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN105745442A (zh) 2016-07-06
CN105745442B (zh) 2017-12-15
DE102013220231A1 (de) 2015-04-09
EP3055565A1 (fr) 2016-08-17
WO2015051965A1 (fr) 2015-04-16

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