EP2250404A1 - Unite de reglage pour une transmission ramifiee hydrostatique continue - Google Patents

Unite de reglage pour une transmission ramifiee hydrostatique continue

Info

Publication number
EP2250404A1
EP2250404A1 EP08872255A EP08872255A EP2250404A1 EP 2250404 A1 EP2250404 A1 EP 2250404A1 EP 08872255 A EP08872255 A EP 08872255A EP 08872255 A EP08872255 A EP 08872255A EP 2250404 A1 EP2250404 A1 EP 2250404A1
Authority
EP
European Patent Office
Prior art keywords
adjusting
control valves
adjusting unit
unit according
pivot
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.)
Withdrawn
Application number
EP08872255A
Other languages
German (de)
English (en)
Inventor
Robert KÖPF
Manfred Kirchhoff
Josef HÄGLSPERGER
Rudolf Hempel
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.)
Mali Holding AG
Original Assignee
Mali Holding AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mali Holding AG filed Critical Mali Holding AG
Publication of EP2250404A1 publication Critical patent/EP2250404A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/433—Pump capacity control by fluid pressure control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/02—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motors at a distance from liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/08—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/423—Motor capacity control by fluid pressure control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/105—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing
    • F16H2037/107—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing with switching means to provide three variator modes or ranges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H2039/005—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution comprising arrangements or layout to change the capacity of the motor or pump by moving the hydraulic chamber of the motor or pump

Definitions

  • the present invention relates to the field of transmission technology. It relates to an adjusting unit for a continuously variable hydrostatically branched transmission according to the preamble of claim 1.
  • Power split transmissions especially for use in agricultural or construction-related vehicles such as tractors, have long been known.
  • the power applied to an input shaft or drive shaft usually delivered by an internal combustion engine power to a first mechanical Power branch with a fixed ratio and a second, infinitely variable in translation power branch split and then rejoined to stand on an output shaft or output shaft available.
  • the second power branch is usually designed as a hydrostatic branch, in which two hydrostatic axial piston machines (hydrostatics) of sloping axis or swashplate type, which are hydraulically connected to each other, optionally operate as a pump or a motor.
  • the translation can be changed by the change in the pivot angle of the cylinder block or the swash plate.
  • the transmission should have high efficiency over the entire speed range. This should especially be the case at the high driving speeds, over a longer road
  • the gear should be compact in order to allow installation in a variety of vehicles as possible without constructive restrictions.
  • the transmission should allow the transmission of high power.
  • the gear should be as simple as possible to limit the power losses and increase the reliability.
  • the transmission should enable full electronic control in conjunction with the engine management and also at
  • SHL transmission continuously variable hydrostatic power split transmission
  • SHL transmission continuously variable hydrostatic power split transmission
  • the well-known SHL transmission has been used and tested under the type designation SHL-Z in city buses.
  • the two hydrostats used have a swivel range of only 0-25 °.
  • the hydrostatic component of the transmitted power at the starting point is 100% and then linearly approaches zero speed.
  • the second driving range it goes from zero to a maximum of about 27% and then back to zero.
  • the third driving range it goes from zero to a maximum value of 13% at the highest forward speed.
  • the hydrostatic power transmission branch of such a transmission usually comprises two hydrostatic axial piston machines, which are hydraulically connected to each other and of which one operates as a pump and the other as a motor. Depending on the driving level, the two machines can swap their roles.
  • the hydrostatic axial piston machines represent an essential part of the hydrostatic power split transmission and significantly shape the characteristics of the transmission such as the efficiency, the size, the complexity, the covered speed range, type and number of speed steps and dgL
  • Examples of such hydrostatic axial piston machines are in DE A1-198 33 711 or DE-A1-10044 784 or US-A1- 2004/0173089.
  • the mode of operation and theory of hydrostatic axial piston machines as well as a power-split tractor system equipped with them are published in a publication of the TU Kunststoff from the year 2000 by H. Bork et al., "Modeling, Simulation and Analysis of a Continuously Variable Power Tractor Drive".
  • the adjustment mechanism should be compact in construction, safe in operation and operable with sufficient accuracy. In addition, it is desirable to make the adjustment mechanism easily accessible for maintenance purposes.
  • Essential for the invention is that provided within the adjustment hydraulically actuated adjusting means, control valves and
  • Actuating means for actuating the control valves are arranged directly between the two Hydrostaten. As a result, in particular a compact construction is achieved.
  • Pivot axes of the hydrostats are aligned parallel to each other, that the control valves have longitudinal axes along which a valve spool is displaceable for actuating the control valves, that the control valves are spaced apart such that their longitudinal axes are aligned parallel to each other and perpendicular to the pivot axes of the hydrostatic in that the actuating means comprise adjusting levers over which the Control valves are actuated, and which are pivotable in a plane perpendicular to the pivot axes of the Hydrostaten pivot plane.
  • the actuating means further comprise an adjusting roller, which is arranged between the control valves and rotatable about an axis of rotation, which is aligned parallel to the longitudinal axes of the control valves, and which have on its circumference guideways for controlling the pivoting movement of the adjusting lever, with its one ends the Scan guideways on the adjusting roller.
  • the adjusting levers are pivotally mounted on the valve spools and are at their other ends with the hydrostatic engaged, such that upon pivoting of the hydrostatic about their pivot axes, the adjusting lever are pivoted in a predetermined manner in its pivoting plane, wherein the coupling between the adjusting levers and the hydrostat preferably each comprises a crank drive rotatable about the pivot axes.
  • the adjusting roller is driven in particular by an electric motor.
  • For manual rotation of the adjusting can be provided between the engine and adjusting roller emergency operation, with which it is possible to maintain an emergency driving operation of the associated vehicle in case of failure of other systems.
  • hydraulically actuable adjusting means for each hydrostatic comprise at least one adjusting cylinder which engages with an adjusting piston on a pivotable about the pivot axis pivoting lever of the hydrostatic.
  • a further embodiment of the invention is characterized in that the control valves for controlling the hydraulically actuatable adjusting means and the actuating means for actuating the control valves are housed in an upwardly open housing, which is closable with a lid, that the control valves and selected actuating means on the underside the cover are mounted, and that the control valves with the hydraulically actuated adjusting means are connected via a pressure-distribution system integrated in the cover with individual hydraulic channels.
  • the hydrostats operate selectively as a pump and as a motor, their pivoting range being at least +/- 45 ° in each case.
  • FIG. 1 in a schematic representation of the basic structure of an exemplary continuously variable hydraulic
  • Fig. 2 is a perspective view (seen obliquely from below) of a transmission according to the principle shown in Figure 1, wherein only the lid is shown with the underlying transmission and the control above.
  • FIG. 3 is a perspective view (seen from obliquely below) of the two hydrostat of FIG. 2 with the associated adjusting unit according to a preferred embodiment of the invention;
  • FIG. 4 shows the arrangement from FIG. 3 in a perspective view obliquely from above;
  • FIG. 5 shows the adjusting unit of FIG. 4 without a cover and without two of the adjusting cylinders
  • Fig. 6 seen obliquely from below the lid of the adjusting unit of FIG.
  • Fig. 1 is a schematic representation of the basic structure of a continuously variable hydraulic power split transmission is shown, which is particularly suitable for the realization of the invention.
  • the transmission 10 transmits the power of an internal combustion engine 11, which is symbolized in FIG. 1 by a piston seated on a crankshaft.
  • the transmission 10 is connected to the engine 11 with an input shaft (drive shaft) W1. It outputs the transmitted power via an output shaft (output shaft) W7. If necessary, a power take-off shaft W8 extends through the transmission 10, which is a direct continuation of the input shaft W1.
  • the core of the transmission 10 form a stepped planetary gear 12 with a large sun Z1 and a small sun gear ZV, the double planetary gears Z2, Z2 ', the ring gear Z3 and the planet gear 13 non-rotatably connected to a gear Z8, and two hydrostatic axial piston or
  • Hydrostates H1 and H2 whose output shafts W6 and W12 in each case via a pair of clutches K3, K4 and K1, K2 in different ways with the Input shaft W1, the output shaft W7 and the stepped planetary gear 12 can be coupled.
  • the hydrostats H1 and H2, which optionally operate as a pump and motor, are hydraulically connected to each other via high pressure lines, not shown.
  • the first hydrostat H1 can be coupled with its output shaft W6 by means of the clutch K3 via a countershaft from the gearwheel Z5 and a gearwheel Z4 connected in a rotationally fixed manner to the ring gear Z3 with the ring gear Z3.
  • it can also be coupled to the input shaft W1 by means of the clutch K4 via the gearwheel Z11, the intermediate gear Z12 and the gearwheel Z10 arranged in a rotationally fixed manner on the input shaft W1.
  • the second hydrostat H2 can be coupled with its output shaft W12 on the one hand by means of the clutch K1 via the hollow shaft W11 and the gear rotatably mounted thereon Z9, which meshes with the gear Z8, with the planet carrier 13 and thus with the output shaft W7.
  • it can be coupled to the smaller sun gear ZV of the stepped planetary drive 12 via the gear pair Z7, Z6 and the hollow shaft W2 by means of the clutch K2.
  • the power applied to the input shaft W1 is divided in the transmission 10 by the stepped planetary gear 12 on two power branches, namely a mechanical power branch and a hydraulic power branch and later recombined on the output shaft W7.
  • the mechanical power branch runs from the input shaft W1 via the larger sun gear Z1 rotatably connected to the input shaft W1, the double planetary gears Z2, the planetary gear 13 and the gear Z8.
  • the hydraulic power branch runs over the two hydraulically connected hydrostats H1 and H2 and is designed differently depending on the circuit of the clutches K1, .., K4. As indicated in the drawing in FIG. 1, the two hydrostats H1 and H2 can each be pivoted by +/- 45 °.
  • Power split transmission is shown in Fig. 2 from the perspective obliquely from below, with only the lid with the underlying transmission and the controller arranged above it is shown.
  • the associated lower housing part can be configured differently depending on the requirement.
  • the transmission 10 of Fig. 2 comprises as a supporting part a substantially rectangular cover 14 which is bounded by a lying in a plane, provided with holes for screwing to the lower housing part, circumferential flange 15.
  • the transmission components shown schematically in FIG. 1 are arranged and supported in the actual transmission core 17 in three mutually parallel axes forming an isosceles triangle. In one axis there is the first hydrostat H1 with the shafts W3, W5 and W6, the gears Z5 and Z11, and the clutches K3 and K4.
  • the third, middle axis includes W2, W7 and W10, the stepped planetary gear 12, and the gears Z4, Z6, Z8 and Z10.
  • a parallel to the lid 14 oriented bearing bottom 22 two vertically from the lid 14 downgoing outgoing side support posts 20, 21, and two also perpendicular to the cover 14 after downgoing outgoing, bearing walls provided, of which only the one bearing wall 23 can be seen.
  • the bearing bottom 22 limits the gear core 17 on the underside. It is bolted to the support posts 20, 21 and the bearing walls 23.
  • the lower pivot bearings 18, 19 are arranged for each about a vertical axis (pivot axes 27, 28 in Fig. 3) pivotable housing of the hydrostatic H1 and H2.
  • the upper pivot bearings are not visible housed in the lid 14 itself.
  • the mutually parallel, perpendicular to the three axes of the gear core 17 bearing walls 23 are used to support the belonging to the axes of waves.
  • the shafts W9 and W3 coming from the clutches K1 / K2 and K3 / K4 are supported in the front bearing wall 23.
  • the associated bearings are each designed as a structural unit with a control hydraulics 24 and 25, which is in communication with the controller on the top of the lid and actuated via axial holes in the interior of the shafts W3 and W9 the clutches K1, .., K4.
  • the oil pressure required for the control hydraulics is generated by a hydraulic pump 26, which draws oil via a downwardly directed intake from the formed in a trough of the housing base oil sump and passes on integrated in the bearing wall 23 channels for control.
  • Bearing wall through which is also provided with a serration inner output shaft W7 accessible, via which the power from the transmission can be delivered by means of an outer output shaft mounted in the lower housing part to the outside.
  • the transmission control necessary for the operation of the transmission core 17 is accommodated so that the intervention initiated by the transmission control 16 intervention in the transmission takes place directly through the cover 14:
  • One type of intervention is the adjustment of the hydrostatic H1 and H2, the pivoting of the swivel housing by max. +/- 45 ° and affects the hydraulic connection between the two hydrostats.
  • an adjusting unit according to the invention is provided, the embodiment of which is shown in FIGS. 3 to 7.
  • the adjusting unit 16 is to a part in a arranged on the top of the lid 14, upwardly open housing 60 (Fig. 2) housed that with a (second) cover 29 can be closed.
  • To the housing 60 are on opposite longitudinal sides in pairs opposite a total of four hydraulic working adjusting VZ 1, VZV and VZ2, VZ2 'flanged outside, their corresponding adjusting VK1, VKV and VK2, VK2' extend into the housing 60 and there pivoting on the hydrostatic H1 and H2 act (see Fig. 7).
  • Pressure distribution system 36 are connected.
  • the pressure in the hydraulic channels 32, .., 35 of the second cover 29, and thus the use of the pressure actuated adjusting cylinder VZ1, VZV or VZ2, VZ2 1 is controlled by hydraulic control valves (servo valves) SV1 and SV2 on the bottom of the second cover 29 with their longitudinal axes 56, 57 are flanged parallel and with pressure ports 54, 55 (Fig. 7) via corresponding vertical holes in the lid 29 with the hydraulic channels 32, .., 35 in connection.
  • the cover 29 extends in a plane which is oriented perpendicular to the parallel pivot axes 27, 28 of the two Hydrostaten H1, H2.
  • two adjusting levers 45, 46 are arranged, by means of which the valve spool 58, 59 of the two control valves SV1, SV2 in the longitudinal axes 56, 57 can be moved.
  • the valve slide 58, 59 in a central portion of the control valves SV1, SV2 freely accessible from above.
  • the adjusting levers 45, 46 are each pivotally mounted on the valve slides 58, 59, wherein they protrude with approximately one third of the lever length in the space between the two spaced control valves SV1, SV2 and with about two thirds of the lever length in the opposite direction up to the hydrostatic H1, H2 extend.
  • an adjusting roller (cam roller) 42 is arranged, which is rotatably mounted about a rotation axis 41 in two bearing blocks 43, 44, which are screwed under the cover 29.
  • the axis of rotation 41 of the adjusting roller 42 runs parallel to the longitudinal axes 56, 57 of the control valves SV1, SV2.
  • the adjusting roller 42 is driven via a coupling disk 53 (FIG.
  • the adjusting roller 42 has at its periphery guideways 51, 52 which are scanned by the adjusting levers 45, 46 with the one (inner) ends. With the other (outer) ends, the adjusting levers are in engagement with the upper bearing journals of the hydrostats H1, H2 via a crank drive KT1 or KT2 (FIG. 7), wherein the coupling between the adjusting levers 45, 46 and the crank drive KT1, KT2 is via a sliding in a fork 47 at the lever end sliding block 48 takes place.
  • crank mechanism KT1, KT2 is part of a swivel plate 49, 56 flanged to the hydrostatic unit M 1 H 2, which pivots with the hydrostatic drive H 1, H 2 about its pivot axis 27, 28, and at which the adjusting pistons VK 1, VK 1 'or VK 2, VK 2' Actuate adjusting cylinder VZ1, VZ1 1 or VZ2, VZ2 '.
  • the adjusting roller 42 is rotated in the case of non-pivoting hydrostatic drives H1, H2, the adjusting levers 45, 46 pivot about the axes of rotation of the crank mechanisms KT1, KT2 passing through the sliding blocks 48, depending on the course of the guide tracks 51, 52 and displace the valve slides 58, 59 accordingly Control valves SV1, SV2. If the hydrostats are pivoted when the adjusting roller 42 is not rotating, the valve slides 58, 59 of the control valves SV1, SV2 also move. As a result, a mechanical feedback of the pivoting movement of the hydrostats M 1 H2 is effected on the control of the adjustment process.
  • valve spools 58, 59 are within the Control valves SV1, SV2 biased by springs in the direction of the longitudinal axes 56, 57, so that the adjusting lever 45, 46 abut on one side of the guideways 51, 52 of the adjusting roller 42 without play.
  • the control valves SV1, SV2 are arranged point-symmetrical to each other, so that only one valve type is needed.
  • the inventive design of the adjustment a compact design, precise control and good accessibility is achieved.
  • the parallel alignment of the longitudinal axes of the control valves and the axis of rotation of the adjusting roller perpendicular to the connecting line between the pivot axes of the hydrostat and perpendicular to the pivot axes themselves causes the adjustment builds very short.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Fluid Gearings (AREA)
  • Friction Gearing (AREA)
  • Motor Power Transmission Devices (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne une unité de réglage (16) pour une transmission ramifiée hydrostatique continue, ladite transmission comprenant deux hydrostats (H1, H2) qui sont disposés à distance l'un de l'autre, et qui sont montés, chacun pivotant autour d'un axe de pivotement (27 ou 28). En particulier, en vue d'obtenir une construction compacte, l'invention est caractérisée en ce que l'unité de réglage (16) comprend des moyens de réglage actionnés hydrauliquement (VZ1, VZ1'; VZ2) pour le pivotement des hydrostats (H1, H2) autour de leurs axes de pivotement (27, 28), en ce qu'il est prévu des soupapes de commande (SV1, SV2) pour la commande des moyens de réglage actionnés hydrauliquement (VZ1, VZ1'; VZ2), et des moyens de commande (30; 42,..., 46) pour la commande des soupapes de commande (SV1, SV2), et en ce que les soupapes de commande (SV1, SV2) et les moyens de commande (30; 42,..., 46) sont disposés entre les deux hydrostats (H1, H2).
EP08872255A 2008-02-08 2008-12-05 Unite de reglage pour une transmission ramifiee hydrostatique continue Withdrawn EP2250404A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810008234 DE102008008234A1 (de) 2008-02-08 2008-02-08 Verstelleinheit für ein stufenloses hydrostatisch verzweigtes Getriebe
PCT/CH2008/000520 WO2009097700A1 (fr) 2008-02-08 2008-12-05 Unité de réglage pour une transmission ramifiée hydrostatique continue

Publications (1)

Publication Number Publication Date
EP2250404A1 true EP2250404A1 (fr) 2010-11-17

Family

ID=40560307

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08872255A Withdrawn EP2250404A1 (fr) 2008-02-08 2008-12-05 Unite de reglage pour une transmission ramifiee hydrostatique continue

Country Status (11)

Country Link
EP (1) EP2250404A1 (fr)
JP (1) JP2011512493A (fr)
KR (1) KR20110007098A (fr)
CN (1) CN101939567A (fr)
AU (1) AU2008350228A1 (fr)
BR (1) BRPI0822293A2 (fr)
CA (1) CA2711954A1 (fr)
DE (1) DE102008008234A1 (fr)
EA (1) EA201070938A1 (fr)
MX (1) MX2010008520A (fr)
WO (1) WO2009097700A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010053012A1 (de) * 2010-12-02 2012-06-06 Claas Industrietechnik Gmbh Hydromechanisches Getriebe
DE102010062951A1 (de) * 2010-12-13 2012-06-14 Zf Friedrichshafen Ag Stellvorrichtung eines Hydrostatmoduls
DE102015209644A1 (de) * 2015-05-27 2016-12-01 Robert Bosch Gmbh Hydrostatischer linearer Aktuator und Anordnung mit hydrostatischen linearen Aktuatoren
EP4249769A1 (fr) 2022-03-22 2023-09-27 Fuss Spezialfahrzeugbau GmbH Transmission à dérivation de puissance pour un véhicule automobile à faible puissance réactive et à large plage de vitesses

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2956407A (en) * 1956-10-09 1960-10-18 Daimler Benz Ag Hydrostatic transmission
GB1129534A (en) * 1965-07-15 1968-10-09 Lucas Industries Ltd Hydraulic transmission systems
DE2757300C2 (de) 1977-12-22 1982-08-12 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Leistungsverzweigtes hydrostatisch-mechanisches Verbundgetriebe
DE2904572C2 (de) 1979-02-07 1984-04-05 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe
DE2950619A1 (de) 1979-12-15 1981-06-19 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Leistungsverzweigungsgetriebe mit einem planetendifferentialgetriebe
FR2562627B1 (fr) * 1984-04-09 1989-06-30 Chapuis Laurent Procede et dispositif de commande d'un ensemble hydrostatique
JPS62224770A (ja) * 1986-03-24 1987-10-02 Honda Motor Co Ltd 静油圧式無段変速機の変速制御装置
DE3619640A1 (de) 1986-06-11 1987-12-17 Man Nutzfahrzeuge Gmbh Instationaer betriebenes nutzfahrzeug mit ueber eine arbeitshydraulik betaetigbaren nutzeinrichtungen
DE3707382A1 (de) 1987-03-07 1988-09-15 Fendt & Co Xaver Hydrostatisch-mechanischer radantrieb
DE3726080A1 (de) 1987-08-06 1989-02-16 Man Nutzfahrzeuge Gmbh Hydromechanisches leistungsverzweigungsgetriebe fuer ein fahrzeug
DE3912386C2 (de) 1989-04-14 1993-10-28 Man Nutzfahrzeuge Ag Stufenlos hydrostatisch-mechanisches Leistungsverzweigungsgetriebe
DE3912369C2 (de) 1989-04-14 1996-02-22 Man Nutzfahrzeuge Ag Stufenloses hydrostatisch-mechanisches Leistungsverzweigungsgetriebe
JPH0747232Y2 (ja) * 1989-07-12 1995-11-01 株式会社神崎高級工機製作所 Ｈｓｔ式車軸駆動装置
DE4343402A1 (de) 1993-12-18 1994-04-28 Voith Gmbh J M Stufenloses hydrostatisches Leistungsverzweigungsgetriebe
DE4343401C2 (de) 1993-12-18 1995-06-01 Voith Gmbh J M Stufenloses hydrostatisches Leistungsverzweigungsgetriebe
DE19833711A1 (de) 1998-07-27 2000-02-10 Brueninghaus Hydromatik Gmbh Hydrostatische Axialkolbenmaschine mit einer Nachführvorrichtung für eine Zwischenscheibe
DE10044784B4 (de) 2000-09-11 2006-03-23 Sauer-Danfoss (Neumünster) GmbH & Co OHG Schrägachsenverstelleinheit
GB2377260B (en) 2001-07-03 2005-09-21 Agco Gmbh & Co Torque split power transmission
US7014429B2 (en) 2003-03-06 2006-03-21 The United States Of America As Represented By The Administrator Of The U.S. Environmental Protection Agency High-efficiency, large angle, variable displacement hydraulic pump/motor
ATE388353T1 (de) * 2004-10-20 2008-03-15 Markus Liebherr Internat Ag Leistungsverzweigungsgetriebe sowie verfahren zum betrieb eines solchen getriebes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009097700A1 *

Also Published As

Publication number Publication date
JP2011512493A (ja) 2011-04-21
EA201070938A1 (ru) 2011-02-28
MX2010008520A (es) 2010-10-25
BRPI0822293A2 (pt) 2015-06-30
KR20110007098A (ko) 2011-01-21
AU2008350228A1 (en) 2009-08-13
CN101939567A (zh) 2011-01-05
WO2009097700A1 (fr) 2009-08-13
CA2711954A1 (fr) 2009-08-13
DE102008008234A1 (de) 2009-08-13

Similar Documents

Publication Publication Date Title
DE102008008236A1 (de) Hydrostatisch leistungsverzweigtes Getriebe
EP1802896B1 (fr) Transmission a repartition de puissance et procede pour faire fonctionner cette transmission
EP0615077B1 (fr) Transmission équipée de deux moteurs hydrauliques
EP2381135B1 (fr) Transmission hydromécanique à division de puissance
EP2577097B1 (fr) Système de transmission
DE19522833A1 (de) Leistungsverzweigungsgetriebe
EP0939866A1 (fr) Transmission a reglage continu a branchement de puissance
EP2271861B1 (fr) Transmission à dérivation de puissance
EP2606259A1 (fr) Engrenage de branchement de couple pour un véhicule automobile
DE4206023C2 (de) Stufenloses hydrostatisch-mechanisches Leistungsverzweigungsgetriebe
EP2461073B1 (fr) Engrenage hydromécanique
EP2250404A1 (fr) Unite de reglage pour une transmission ramifiee hydrostatique continue
EP2122200A1 (fr) Engrenage
DE1065734B (de) Stufenlos verstellbares hydrostatisches Getriebe, insbesondere für schwere Fahrzeuge
WO2010091778A1 (fr) Transmission hydrostatique continue à dérivation de puissance
WO1990002893A1 (fr) Transmission hydromecanique a variation continue avec repartition de puissance, notamment pour vehicules a moteur
DE19510914C2 (de) Hydromechanisches Antriebsaggregat
EP1325250A1 (fr) Dispositif hydrostatique pour engrenage de derivation de puissance hydrostatique-mecanique
EP1574756A1 (fr) Transmission
DE102011118410A1 (de) Hydromechanisches Getriebe mit einem Hydromotor und einem mechanischen Zweigang- oder Dreigang-Stufenschaltgetriebe
DE3224968A1 (de) Hydrostatische kriechgang-antriebsanordnung fuer nutzfahrzeuge
DE1816069A1 (de) UEbersetzungsgetriebe,insbesondere zum Zapfwellenantrieb fuer landwirtschaftliche Schlepper od.dgl.
DE3817292A1 (de) Leistungsverzweigungsgetriebe
DE1530899C (de) Stufenlos einstellbares hydrostatisch mechanisches Fahrzeuggetriebe mit einer von der Antriebswelle angetriebenen hydrosta tischen Pumpe und mit zwei von der Pumpe mit Druckflüssigkeit beaufschlagbaren hydrostatischen Motoren
DE102007016517A1 (de) Hydrostatischer Fahrantrieb

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20100906

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20101027