EP0357698B1 - Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur - Google Patents

Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur Download PDF

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Publication number
EP0357698B1
EP0357698B1 EP89901264A EP89901264A EP0357698B1 EP 0357698 B1 EP0357698 B1 EP 0357698B1 EP 89901264 A EP89901264 A EP 89901264A EP 89901264 A EP89901264 A EP 89901264A EP 0357698 B1 EP0357698 B1 EP 0357698B1
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EP
European Patent Office
Prior art keywords
spring
cylinder block
hydraulic
axial piston
machine according
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EP89901264A
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German (de)
English (en)
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EP0357698A1 (fr
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Michael Meyerle
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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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/303—Control of machines or pumps with rotary cylinder blocks by turning the valve plate
    • 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
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining 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
    • F04B1/20—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
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure

Definitions

  • the invention relates to a hydrostatic axial piston machine, in particular for motor vehicle transmissions with power split according to the preamble of claim 1.
  • Hydrostatic axial piston machines of this type are widely known for their predominant use in construction machine gearboxes. For the demanding use in transmissions for passenger vehicles, these known hydrostatic transmissions are almost unsuitable because of their unfavorable efficiency and the excessive noise.
  • a known hydrostatic axial piston machine according to DE-A-2 341 106 has a fixed pressing device of the rotating hydrostatic elements designed via spring elements.
  • a variable contact pressure of the contact pressure device, which can be adapted to the different operating states, is not possible with this known axial piston machine.
  • the object of the invention is to develop a hydrostatic axial piston machine, in particular for use in power split transmissions for cars or bus transmissions, in which the efficiency is improved and, moreover, the noise level is reduced.
  • the invention is explained using exemplary embodiments with reference to drawings. Show it Hydrostatic circuit-related high-pressure oil of the hydrostatic sliding bearing between the sliding shoes 4 and the swash plate is lost to an increased extent, which leads to relatively high and uncontrollable leakage losses.
  • the invention has a hydraulic hold-down device 75, FIG. 2a, designed as a separate or additional hold-down device and / or a spring-elastic hold-down device in order to ensure the leakage oil losses between the sliding shoes 4 and the sliding plane of the inclined surface or Lower the pressure plate 11 to a minimum.
  • the known hydrostatic axial piston machines have, for the axial pressing of the cylinder block against its control disk, depending on the embodiment, internal springs which have a sufficiently high spring force for the entire speed range.
  • the spring force is dependent on the maximum permissible speed and is adjusted with a correspondingly high value. This means that the spring force is unnecessarily high for lower engine speeds, which are approximately one third of the maximum engine speed in the main operating area, for example. The consequence of this is that unnecessarily high friction losses or power losses occur in the main operating area.
  • the invention provides for a specific adaptation of the contact forces of the cylinder block to its control disk by the cylinder block 2 by means of a spring 24 with a constant spring force designed for low speed and an additional variable hydraulic contact pressure is pressed in a targeted manner onto its control surface 37.
  • the variable hydraulic contact pressure is essentially dependent on the speed of the drive motor. In special cases, it is possible to modulate or correct this pressure as a function of the hydrostatic pressure or the tensile force using a corresponding control device.
  • annular piston 20 For the hydraulic cylinder block pressure, an annular piston 20 is used, which is supported against the drive shaft 10 and contains a sealing ring 21 or 28 for sealing against the cylinder block, which is seated in a corresponding groove in the annular piston.
  • a further annular piston 22 is provided, which is connected to the cylinder block 2 and is axially fixed via a locking ring 27.
  • This annular piston 22 has a sealing ring, which is expediently directed inwards to the shaft 10 and is designed as an O-ring 23 or as a shaped ring 28 with a radially elastic sealing lip 29 or as a piston ring with radial play to the groove base.
  • the sealing ring 28 is designed as a special shaped ring with an elastic sealing lip 29, which has a corresponding radial, largely lateral force-free displacement of the cylinder block 2 allows. This also applies to the ring pistons
  • the hydraulic oil pressure is expediently supplied to the piston chamber 25 centrally through a shaft 55 or 10 via a bore 26.
  • This device results in a specifically metered pressing of the cylinder block 2 against its control surface 37 and thus an optimization of the efficiency within this functional area.
  • the hydraulic hold-down device 75 provides for a hydraulic pressing of the perforated disc 6 against the sliding shoes 4.
  • this hold-down device 75 is equipped with a hold-down ring 7, which is non-rotatably but axially movable against the perforated disk 6 in the swashplate or in the swashplate 5.
  • the hold-down ring 7 is supported against a locking ring 8 and optionally a washer 76, which serves as an adjusting washer.
  • a spring element 77 is located between the locking ring or disk 76 and the hold-down ring 7 arranged.
  • This spring element 77 is preferably designed as a rubber element or elastomer element which is inserted in an annular groove of the hold-down ring 7.
  • the spring element 77 acts against the hold-down ring 7 with a certain spring force.
  • the pressure oil required for generating the hydraulic contact pressure is guided into the hold-down ring 7 via oil lines 79, the oil pressure acting against the sealing and spring element 77.
  • an axial force is exerted on the hold-down ring 7 against the perforated disk 6.
  • a targeted oil pressure is generated which, for example, is dependent on a speed signal or / and a load-dependent signal or / and a feed or supply pressure for the hydrostatic transmission and the control and regulating device.
  • the required contact forces are usually dependent on the speed.
  • a targeted contact pressure can be generated with this device via a speed-dependent pressure, which is already present in this way in the automatic car transmission of this type.
  • the hold-down forces are thus relatively low in the main operating area, for example in the case of a passenger car, as a result of which the friction losses between the perforated disk 6 and the hold-down ring 7 can be substantially reduced.
  • the hold-down ring 7 has additional recesses on the sliding surface opposite the perforated disk 6, for example in the form of an annular groove 80 and a transverse groove 81, which are connected to the hydraulic system of the hydraulic hold-down device and for lubricating the sliding surfaces between the hold-down ring 7 and the perforated disk 6 to serve.
  • the quantity of lubricating oil can be metered through a throttle bore 84 in the inflow to the lubrication system.
  • the sealing and spring element 77 when used in the hydraulic hold-down device 75, is expediently designed as a rubber element or elastomer element which, as shown, has one or two sealing lips projecting in the axial direction to support the axial spring force and at the same time seal of the hydraulic oil. A circumferential oil space is created between the two sealing lips, which guarantees an even hydraulic pressure.
  • the hydraulic hold-down device 75 in the form shown, can be produced relatively inexpensively, since no high manufacturing accuracy of the height dimensions for the hold-down device 7 and the perforated disk 6 is required, since even larger dimensional deviations can be compensated for by the sealing or spring element 77.
  • a relatively simple dimension setting can be implemented very economically by means of the disc 76, which is designed as an adjusting disc in various thickness dimensions, even for very high production quantities. This also applies to the positive plus spring-loaded hold-down device 40 in connection with this shim 76, which is not shown in the drawings.
  • the oil feed pipe 78 for the hydraulic hold-down device 75 is connected to the hold-down ring 7 and at the same time serves to prevent rotation relative to the inclined body or swivel body 5.
  • the form-fitting hold-down device 40 essentially consists of a perforated disc 6 which is held in place with a small axial play "B" via the hold-down ring 7 and a locking ring 8.
  • the perforated disc 6 rotates with the cylinder block 2 and the piston 3, with the hold-down ring 7 being secured against rotation in the inclined or swiveling body 5.
  • Protruding drivers 14, which engage in recesses 15 of the inclined body 5, serve to prevent rotation on the holding-down ring 7.
  • the swash plate or pressure plate 11 also has drivers 12 which engage in recesses in the swivel body 5 to prevent rotation. These recesses 13 and 15 to prevent rotation of the pressure plate 11 and the hold-down ring 7 are preferably cast in the pivot body 5 to save costs.
  • a spring element 9 or 46, 41 is, as shown in Figure 3, 3a, formed as an elastomer in the form that inwardly directed resilient segments 41 with the dimension "F" are connected to a closed ring 46 as possible, the engage in recesses 43 of the hold-down ring 7 and are resiliently supported against the retaining ring 8 and the hold-down ring 7.
  • These resilient subsegments 41 have a special profile 52, which is designed such that, at a relatively high spring rate, a fairly exact axial force is generated on the hold-down ring 7 of the perforated disc 6 and the sliding shoes 4 against the swash plate or pressure plate 11.
  • the spring profile 52 is comb-shaped, the spring rate depending on the comb shape and the degree of softness of the elastomer.
  • the recesses 43 for the spring segment 41 can be cut inexpensively without cutting, for example when using the sintering or die-casting technique for the hold-down ring 7 or it can also be milled, all recesses being able to be produced very efficiently in one operation. When using milling technology, however, it is advisable to design the spring segment 41 in a radius-like manner, as in FIG. 4, and to adapt the recess 19 accordingly.
  • the hold-down ring 7 has a peripheral edge 47 which lies in the diameter range of the inner diameter 48 for the locking ring 8 or is only slightly smaller.
  • the spring element according to FIG. 4 is made in the form of a flat spring or from flat material and has inwardly directed spring parts 16 with projecting resilient tongues 17 which engage in recesses 19 of the hold-down ring 7 and are supported against the hold-down ring 7 and the retaining ring 8.
  • the spring parts 16 can be connected to one another via a circumferential ring 18 and thus be formed in one piece, or can be loosely inserted into the recesses 19 as separate individual members (FIGS. 4, 4a).
  • FIG. 5 and 5a show a form-fitting hold-down device with a spring element, which is designed as an elastomer in the form of an O-ring or profile ring 72 and lies in an annular groove 44 or 73 of the hold-down ring 7.
  • the profile ring 72 like the spring elements 9; 6, 17 have the advantage of higher spring elasticity compared to the O-ring 45 and a lower spring force-related tilting moment on the locking ring 8.
  • the O-ring 45 or profile ring 72 there is also a steel spring made of flat material or steel wire with a cylindrical or square cross-section, as in the drawings not shown, applicable.
  • the invention provides for the cylinder block 2 to be formed with cast-in sleeves 35 and for the end face 54 of the cylinder block 2 to be conical with an angle ⁇ which approximately corresponds to the maximum swivel angle, the piston running surface 57 being flush with the conical end face 54 of the cylinder block 2 is. It is thereby achieved that a longer effective piston guidance is achieved with the same overall length of the axial piston machine compared to the prior art, whereby the lateral force-related frictional forces of the piston 3 are reduced in favor of a further improvement in efficiency.
  • the cylinder base 36 of the cylinder block 2 is also metallically connected to the cylinder block material, ie it is cast on and consists of a special, low-friction and very resistant alloy known per se, which also has special emergency running properties.
  • This special sliding layer on the cylinder base 36 and on the piston running surface 35 can also be applied in a metal-bonding manner by other methods, for example by a spraying process.
  • control disk 31 is not arranged in a fixed manner, as is known, but can be rotated automatically as a function of specific operating values.
  • the valve disk 31 is connected to an adjusting piston 32 which, depending on the speed of the drive motor or / and depending on the load condition or the hydrostatic pressure, can be rotated to a limited extent within an angular range ⁇ .
  • the control disk 31 is provided with kidney-shaped recesses 38 for the two high-pressure lines and additional damping slots 34. Depending on the operating state, the control disk 31 is rotated with regard to noise optimization.
  • control disk 31 is hydrostatically supported axially on both pressure sides.
  • control disk 31 is inexpensively designed as a sheet metal body, the kidney-shaped recesses 38 and the damping slots 34 being stamped out.
  • FIG. 8 shows an axial piston machine which has a hydraulically effective hold-down device or hold-down device 71 for the piston sliding shoes 4.
  • This hold-down device 71 can be used as an alternative or in addition to the hold-down devices 40 described so far. It is characterized in that the perforated disk 68, which depresses the sliding shoes 40 of the pistons 3, is pressed axially against the sliding shoes 40 by a hydraulic force on the inside diameter.
  • This hold-down device 71 consists of a spherical cap 66, which is pressed axially with its spherical outer surface 67 onto the likewise spherical surface of a perforated disk 68.
  • the axial contact pressure is generated by a pressure medium in the piston chamber 70, which acts on an axially displaceable piston 64.
  • This axial force is transmitted from the annular piston 64 to the spherical cap 66 by intermediate members - preferably bolts 65 which are loosely mounted in corresponding recesses in the cylinder block 2.
  • a spring 24 for generating a constant axial force of the cylinder block 2 on the control surface or control disk 31; 37 provided which is fixed axially against the drive shaft 10 via a support ring 62 and on the other side against the cylinder block 2 via a support ring or piston ring 22.
  • A, preferably speed-dependent, pressure is generated in the piston chamber 25 or 70 via the oil line 26, which on one side presses the cylinder block 2 against the control surface 37 or 31, depending on the speed, in addition to the spring force of the spring 24 and on the other side via the annular piston 64 and the intermediate links - bolts 65, dome 66 - press the perforated disk 68 against the sliding shoes 4 of the pistons 3.
  • the piston ring 64 is additionally acted upon by the spring force of the spring 24, the support ring 62 being omitted and the spring 24 and the piston 64 being adapted accordingly.
  • the spring force of the spring 24 acts in this embodiment with the same spring force on the cylinder block 2, and the hold-down device 71 via the calotte 66.
  • the spring 24 can be designed for a relatively low spring force in favor of lower frictional forces between the piston crown 36 and the control surface 37 or 31 and in favor of correspondingly lower frictional forces in the hold-down device 71.
  • the higher contact forces required for higher speeds are generated by the speed pressure in the piston chamber 70, 25, which is supplied via the oil line 26.
  • the contact pressure for the holding-down device 71, as well as the stabilizing force for the cylinder block 2 is automatically modulated depending on the operating speed, which in particular reduces the frictional losses in all operating states
  • the minimum dimension is reduced, and the leakage-related losses on the slide shoes 4 and on the control surface 37 are also minimized to an optimal degree.
  • the hold-down device 71 with hydraulic pressure in the various embodiments, as described and partially not shown in the drawings, can also be used very effectively as an independent hold-down device.
  • the prerequisite for this is that the calotte 66 is additionally spring-loaded, e.g. by a separate spring in the piston chamber 70 or by direct support of the spring 24 on the annular piston 64, the support ring 62 being omitted, or by a spring between the cylinder block 2 and the calotte 66.
  • the perforated disk 68 is made correspondingly thicker.
  • FIG. 9 Another embodiment shown in FIG. 9, similar to the embodiment according to FIG. 8, sees two piston surfaces of different sizes, e.g. an annular piston 64 with a small piston area and an annular piston 22 with a large piston area, the hydraulic pressure force of the cylinder block 2 against the control surface 37 and the hydraulic pressure force against the holding-down device 71 being of different sizes.
  • the determining factors for the effective hydraulic forces for holding down the sliding shoes 4 are the outer diameter 69 of the annular piston 64 and its inner diameter 86 and for the pressing of the cylinder block 2 in the opposite direction, the outer diameter 69 of the inner annular piston 64 and the inner diameter 87 of outer annular piston 22. This allows an optimal adaptation to different conditions.
  • the cylinder block 2 is rotatably connected to the drive shaft 10 and axially free.
  • one of the components - perforated disc 6, hold-down ring 7 or locking ring 8 - is designed as a dimension compensation element according to the system of a sorting process. That means it will be rational in terms of economic.
  • the holding-down device e.g. the locking ring 8
  • the retaining ring 8 with the suitable setting dimension "E” selected.
  • the determination of the given dimensions "A” and “C” and the setting of the adjustment dimension "E” can be carried out electronically very efficiently for mass production.
  • the axial play "B” is almost “zero" when new, ie free of play.
  • the use of the known axial piston units is almost impossible due to their unfavorable efficiency. Even when used in a power split transmission, which only partially load the hydrostatic transmission, the efficiency is often unsatisfactory.
  • the details of the invention allow a significant improvement in the overall efficiency of the hydrostatic axial piston machine despite the applicability of rational and inexpensive production methods.
  • the individual components are designed according to the invention so that they allow economical modern production for mass production; this is an essential aim of the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Arrangement Of Transmissions (AREA)
  • Hydraulic Motors (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Actuator (AREA)
  • Gear-Shifting Mechanisms (AREA)

Claims (16)

  1. Machine hydrostatique à pistons axiaux avec un barillet, dans lequel travaillent des pistons (3) coulissants en direction axiale comprenant des patins (4) qui sont actionnés au moyen d'un dispositif de maintien (40; 75) sur un plateau oblique inclinable ou fixe, le barillet (2) étant appliqué en di-rection axiale contre une surface portante ou de distribution (37) au moyen d'un element de ressort,
    caractérisé en ce que
       la machine à pistons axiaux fait partie d'une transmission hydrostatique-mécanique à division de puissance, et en ce que le barillet (2) est applique axialement en plus au moyen d'un dispositif hydraulique, la force d'application hydraulique étant une force d'application hydraulique variable, dont la grandeur depend de la vitesse de rotation du moteur d'entraînement ou/et de la pression de la transmission hydrostatique, la force d'application hydrostatique étant créée dans une chambre pressurisée de piston (25) à l'intérieur du barillet (2).
  2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce qu'elle comprend un moyen de maintien (71) pour les patins (4) agencé de manière à ce qu'un element d'appui (calotte 66) placé à l'intérieur, supporté par l'arbre d'entraînement (10) et déplacé axialement par une pression hydraulique pour s'appuyer sur un disque à trous (68) coopérant avec les patins (4).
  3. Machine hydrostatique à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que
    a) le moyen de maintien (75; 71, 85) est réalisé sous forme d'un moyen de maintien hydraulique, une force hydraulique agissant sur une bague de maintien (7) immobilisée en rotation dans une pièce oblique ou inclinable (5) et sur un disque à trous (6), de manière à ce que les patins (4) des pistons (3) soient appliqués contre une surface oblique (plateau de poussée 11);
    b) et/ou un dispositif de ressort (9; 41; 72, 16, 17; 46; 45; 77) est prévu pour appliquer élastiquement les pistons (3) contre une surface oblique (plateau de poussée 11) par l'intermédiaire de leurs patins (4), d'un disque à trous (6) et d'un élément de maintien (bague de maintien 7), le dispositif à ressort étant logé dans la pièce oblique ou inclinable (5), à l'intérieur d'un moyen de maintien de préférence avec blocage et avantageusement combiné avec un moyen de maintien hydraulique (75).
  4. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 3, caractérisée en ce que le ressort (24) appliquant axialement le barillet (2) contre la surface de distribution (37) est placé sur l'arbre d'entraînement (10) dans l'alésage central du barillet (2) et en ce que des pistons annulaires (20, 22) sont agencés sous forme de bagues d'appui pour la force du ressort et sous forme de pistons de poussée pour créer de la force supplémentaire, de la force hydraulique, entre l'arbre d'entraînement (10) et le barillet (2) et en ce que le ressort (24) est logé dans la chambre de pression du piston (25).
  5. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 4, caractérisée en ce que la chambre du piston (25) est limitée par un piston annulaire (20) comportant un joint annulaire (21), qui est arrêté contre l'arbre (10) et un second piston annulaire (22) avec un joint annulaire (23), qui est fixé dans le barillet (2) et en ce que les joints annulaires sont réalisés soit en élastomère sous la forme d'un joint torique (21, 23) ou d'un joint moulé (28) avec des lèvres d'étanchéité (29) élastiques radialement, soit constitués de segments de piston de forme connue par exemple en fonte ou en matière synthétique avec du jeu radial dans la gorge annulaire (figures 1 et 6).
  6. Machine à pistons axiaux selon la revendication 1 et 2, caractérisée en ce que le barillet (2) est appliqué contre un disque de distribution (31), qui comporte des ouvertures (38) en forme de croissant avec des fentes d'amortissement (34) et en ce que ledit disque de distribution (31) peut être tourné d'un angle β autour de son axe central en fonction d'un signal de vitesse de rotation ou/et d'un signal de pression (Figure 7).
  7. Machine à pistons axiaux selon une des revendications 1 à 6, caractérisée en ce que le disque de distribution (31) coopère avec un piston (32), qui est déplacé hydrauliquement ou électriquement contre la pression d'un ressort (33) (figures 7 et 8).
  8. Machine à pistons axiaux selon une des revendications 1 à 7, caractérisée en ce que le disque de distribution (31) à déplacement automatique est réalisé en tôle avec des découpés (38) en forme de croissant et des fentes d'amortissement (34) embouties.
  9. Machine à pistons axiaux selon la revendication 2, caractérisée en ce que le moyen de maintien (71) est constitué d'une calotte (66) avec une surface de contact sphérique (67), qui est appliquée contre une surface sphérique correspondante d'un disque à trous (68), et en ce qu'un piston (64) coulissant axialement par une pression d'huile est appliqué axialement contre la calotte (66) par des entretoises (cheville 65) (figure 8).
  10. Machine à pistons axiaux selon une des revendications 1 à 9, caractérisée en ce que le moyen de maintien (71) logé à l'intérieur actionné hydrauliquement ou/et par ressort est combiné avec un moyen de maintien (40) logé à l'extérieur actionné par blocage ou/et par blocage et par ressort ou/et un moyen de maintien (75) logé à l'extérieur actionné hydrauliquement (figure 8, 9, 2a).
  11. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 9, caractérisée en ce qu'un piston (64) coulissant axialement vers la calotte (66) est actionné hydrauliquement et par un ressort (83), où, dans la chambre de piston (25) sont logés un ressort (24) plus fort, qui pousse contre le barillet (2) axialement en direction de la surface de distribution (37) et dans l'autre direction axiale contre l'arbre d'entraînement (10), et un ressort (83) plus faible qui s'appuie contre le disque à trous (68) au moyen d'entretoises (64, 65, 66) et dans l'autre direction axiale contre le ressort (62) plus fort ou un élément (rondelle d'appui 62) de l'arbre d'entraînement (10) (figure 9).
  12. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 11, caractérisée en ce qu'un ressort (24) s'appuie d'un côté contre le disque à trous (68) du dispositif de maintien au moyen d'entretoises (64, 65, 66) et de l'autre coté contre le barillet (2) au moyen d'une pièce intermédiaire (22) correspondante, de manière à ce que le barillet (2) soit pressé élastiquement en direction de sa surface de distribution (31; 37) et les mêmes forces de ressort maintiennent les patins (4) des pistons (3) appliqués et en ce que les forces de maintien et d'application sont en plus renforcées par une pression dans la chambre de piston (25; 70) qui dépend de la vitesse de rotation ou/et de la charge (comme figure 8, mais sans bague d'appui (62) ), le ressort (24) s'appuyant sur le piston (64).
  13. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 12, caractérisée en ce qu'au moins deux pistons annulaires (22, 64) avec des surfaces d'action de grandeur différente sont agencés entre l'arbre d'entraînement (10) et le barillet (2) de manière à créer des forces de pression hydrauliques de grandeur différente sur le moyen de maintien (71) des patins (4) et entre le barillet (2) et le disque de distribution (37; 31).
  14. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 13, caractérisée en ce que la pression hydraulique pour le dispositif de maintien (40; 75; 71) ou/et le dispositif pour appliquer le barillet (2) contre le disque de distribution (37) est une pression dépendante de la vitesse de rotation ou/et une pression dépendante de la charge ou/et une pression provenant de l'alimentation et du gavage de la transmission hydrostatique ou de la commande/régulation.
  15. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 14, caractérisée en ce que le moyen de maintien (75, 71, 85) hydraulique pour les patins (4) comme le dispositif hydraulique pour le dispositif de stabilisation (88; 89; 90) sont alimentés simultanément par la même pression hydraulique, qui est par exemple une pression dépendante de la vitesse de rotation ou/et une pression dépendante de la charge.
  16. Machine à pistons axiaux selon une ou plusieurs des revendications 1 à 15, caractérisée en ce que le disque de distribution (31) comporte une position de base déterminée d'après le critère du bruit minimal et est ajustable à l'intérieur du domaine d'angle β en fonction de la charge ou/et de la vitesse de rotation par exemple au moyen d'une pression de commande.
EP89901264A 1988-01-16 1989-01-16 Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur Expired - Lifetime EP0357698B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3801144 1988-01-16
DE3801144 1988-01-16
PCT/DE1989/000017 WO1989006750A1 (fr) 1988-01-16 1989-01-16 Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur

Publications (2)

Publication Number Publication Date
EP0357698A1 EP0357698A1 (fr) 1990-03-14
EP0357698B1 true EP0357698B1 (fr) 1995-06-28

Family

ID=6345413

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89901264A Expired - Lifetime EP0357698B1 (fr) 1988-01-16 1989-01-16 Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur

Country Status (4)

Country Link
EP (1) EP0357698B1 (fr)
AT (1) ATE124498T1 (fr)
DE (1) DE58909319D1 (fr)
WO (1) WO1989006750A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3904782A1 (de) * 1989-02-17 1990-08-23 Linde Ag Axialkolbenmaschine
DE4237506C2 (de) * 1992-11-06 1995-04-06 Danfoss As Axialkolbenmaschine
JPH10176655A (ja) * 1996-12-13 1998-06-30 Zexel Corp 可変容量型斜板式圧縮機
JPH10213062A (ja) * 1997-01-31 1998-08-11 Zexel Corp 可変容量型斜板式圧縮機
US5941159A (en) * 1998-01-09 1999-08-24 Sauer Inc. Integral holdown pin mechanism for hydraulic power units

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2546583A (en) * 1945-02-10 1951-03-27 Denison Eng Co Hydraulic apparatus
GB934851A (en) * 1960-01-23 1963-08-21 Council Scient Ind Res Improvements in swash plate pumps and motors
DE1226418B (de) * 1962-07-12 1966-10-06 Unipat A G Einrichtung zum Andruecken der winkelbeweglichen Kolbengleitschuhe an die Schiefscheibe oder Taumelscheibe einer Axialkolbenmaschine (Pumpe oder Motor)
US3783743A (en) * 1972-11-16 1974-01-08 Abex Corp Axial piston hydraulic transducer shoe retainer structure
US4111103A (en) * 1977-02-14 1978-09-05 Commercial Shearing, Inc. Thrust rings for swash plate pumps and motors
DE2849772A1 (de) * 1978-11-16 1980-05-29 Linde Ag Axialkolbenmaschine in triebflanschbauform

Also Published As

Publication number Publication date
DE58909319D1 (de) 1995-08-03
WO1989006750A1 (fr) 1989-07-27
ATE124498T1 (de) 1995-07-15
EP0357698A1 (fr) 1990-03-14

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