EP2250404A1 - Adjusting unit for a continuously variable hydrostatically branched transmission - Google Patents

Adjusting unit for a continuously variable hydrostatically branched transmission

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Withdrawn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)
French (fr)
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/en
Withdrawn legal-status Critical Current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.

Abstract

The invention relates to an adjusting unit (16) for a continuously variable hydrostatically branched transmission, said transmission comprising two hydrostats (H1, H2), which are disposed next to each other at a distance from each other and each are supported pivotally about a pivot axis (27 or 28). In particular a compact design is achieved in that the adjusting unit (16) comprises hydraulically actuatable adjusting means (VZ1, VZ1'; VZ2) for pivoting the hydrostats (H1, H2) about the pivot axes thereof, that control valves (SV1, SV2) for controlling the hydraulically actuatable adjusting means (VZ1, VZ1'; VZ2) and actuating means (30; 42,...,46) for actuating the control valve (SV1, SV2) are provided, and that the control valves (SV1, SV2) and the actuating means (30; 42,..., 46) are disposed between the two hydrostats (H1, H2).

Description

BESCHREIBUNG DESCRIPTION
VERSTELLEINHEIT FÜR EIN STUFENLOSES HYDROSTATISCHADJUSTING UNIT FOR A CONTINUOUS HYDROSTATIC
VERZWEIGTES GETRIEBEBRANCHED GEAR
TECHNISCHES GEBIETTECHNICAL AREA
Die vorliegende Erfindung bezieht sich auf das Gebiet der Getriebetechnik. Sie betrifft eine Verstelleinheit für ein stufenloses hydrostatisch verzweigtes Getriebe gemäss dem Oberbegriff des Anspruchs 1.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.
STAND DER TECHNIKSTATE OF THE ART
Leistungsverzweigungsgetriebe, insbesondere für den Einsatz bei land- oder bauwirtschaftlich genutzten Fahrzeugen wie z.B. Traktoren, sind seit langem bekannt. Bei solchen Leistungsverzweigungsgetrieben wird die an einer Eingangswelle bzw. Antriebswelle anliegende, üblicherweise von einem Verbrennungsmotor abgegebene Leistung auf einen ersten mechanischen Leistungszweig mit fester Übersetzung und einen zweiten, in der Übersetzung stufenlos veränderbaren Leistungszweig aufgeteilt und anschliessend wieder zusammengeführt, um an einer Ausgangswelle bzw. Abtriebswelle zur Verfügung zu stehen. Der zweite Leistungszweig ist meistens als hydrostatischer Zweig ausgebildet, bei dem zwei hydrostatische Axialkolbenmaschinen (Hydrostaten) von Schrägachsen- oder Schrägscheibentyp, die hydraulisch miteinander verbunden sind, wahlweise als Pumpe oder Motor arbeiten. Die Übersetzung kann dabei durch die Veränderung des Schwenkwinkels des Zylinderblocks bzw. der Schrägscheibe verändert werden. Die Aufteilung der Leistung auf die beiden Leistungszweige und die Zusammenführung der verzweigten Leistungen erfolgt üblicherweise mittels eines Planetengetriebes. Leistungsverzweigungsgetriebe der beschriebenen Art sind in unterschiedlicher Ausgestaltung in der DE-A1-27 57 300, der DE-C2-29 04 572, der DE-A1-29 50 619, der DE-A1-37 07 382, der DE- A1-37 26 080, der DE-A1-39 12 369, der DE-A1-39 12 386, der DE-A1-43 43 401 , der DE-A1-43 43 402, der EP-B1-0 249 001 und der EP-A2-1 273 828 offenbart.Power split transmissions, especially for use in agricultural or construction-related vehicles such as tractors, have long been known. In such power split transmissions, 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 division of the power to the two power branches and the merger of the branched services is usually carried out by means of a planetary gear. Power split transmissions of the type described are described in different embodiments in DE-A1-27 57 300, DE-C2-29 04 572, DE-A1-29 50 619, DE-A1-37 07 382, DE-A1- 37 26 080, DE-A1-39 12 369, DE-A1-39 12 386, DE-A1-43 43 401, DE-A1-43 43 402, EP-B1-0 249 001 and the EP-A2-1 273 828 discloses.
Um ein Leistungsverzweigungsgetriebe mit Erfolg in der Praxis einsetzen zu können, sollte es sich generell durch die folgenden Eigenschaften auszeichnen:In order to successfully use a power split transmission in practice, it should generally have the following characteristics:
Das Getriebe sollte einen hohen Wirkungsgrad über den ganzen Geschwindigkeitsbereich aufweisen. Dies sollte insbesondere bei den hohen Fahrgeschwindigkeiten, die im Strassenverkehr über einen längerenThe 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
Zeitraum gefahren werden, der Fall sein.Be driven period, the case.
Das Getriebe sollte kompakt aufgebaut sein, um den Einbau in die unterschiedlichsten Fahrzeuge möglichst ohne konstruktive Einschränkungen zu ermöglichen.The gear should be compact in order to allow installation in a variety of vehicles as possible without constructive restrictions.
Das Getriebe sollte die Übertragung von hohen Leistungen ermöglichen.The transmission should allow the transmission of high power.
Das Getriebe sollte zur Begrenzung der Leistungsverluste und Erhöhung der Funktionssicherheit möglichst einfach aufgebaut sein.The gear should be as simple as possible to limit the power losses and increase the reliability.
Das Getriebe sollte eine vollumfängliche elektronische Steuerung im Zusammenhang mit dem Motormanagement ermöglichen und auch beiThe transmission should enable full electronic control in conjunction with the engine management and also at
Ausfall bestimmter Steuerungselemente ausreichende Notfahrprogramme zur Verfügung stellen. In der eingangs genannten DE-A1-43 43 402 ist bereits ein als SHL-Getriebe (Stufenloses Hydrostatisches Leistungsverzweigungsgetriebe) bezeichnetes Leistungsverzweigungsgetriebe beschrieben worden, das sich durch zwei hydraulisch gekoppelte gleichartige Hydrostaten in Schrägachsenbauweise auszeichnet, die über Kupplungspaare bzw. Wechselschaltelemente K1/K2 bzw. K3/K4 auf unterschiedliche Weise mit einem Planetendifferentialgetriebe koppelbar sind. Das bekannte SHL-Getriebe ist unter der Typbezeichnung SHL-Z bei Stadtbussen eingesetzt und getestet worden. Die beiden eingesetzten Hydrostaten haben einen Schwenkbereich von lediglich 0-25°. Für die Vorwärtsfahrt ergeben sich dabei 3 Fahrstufen bzw. Fahrbereiche: Im ersten Fahrbereich ist im Anfahrpunkt der hydrostatische Anteil der übertragenen Leistung 100% und geht dann linear mit der Geschwindigkeit gegen Null. Im zweiten Fahrbereich geht er von Null auf ein Maximum von etwa 27% und dann wieder zurück auf Null. Im dritten Fahrbereich geht er von Null auf einen Maximalwert von 13% bei der höchsten Vorwärtsgeschwindigkeit.Failure of certain control elements provide sufficient emergency driving programs. In the aforementioned DE-A1-43 43 402 already described as SHL transmission (continuously variable hydrostatic power split transmission) power split transmission has been described, which is characterized by two hydraulically coupled similar hydrostatic in Schrägachsenbauweise, via clutch pairs or changeover elements K1 / K2 or K3 / K4 can be coupled in different ways with a planetary differential gear. 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 °. For forward travel, there are 3 speed ranges or driving ranges: In the first driving range, the hydrostatic component of the transmitted power at the starting point is 100% and then linearly approaches zero speed. In the second driving range, it goes from zero to a maximum of about 27% and then back to zero. In the third driving range, it goes from zero to a maximum value of 13% at the highest forward speed.
Der hydrostatische Leistungsübertragungszweig eines solches Getriebes umfasst üblicherweise zwei hydrostatische Axialkolbenmaschinen, die hydraulisch miteinander in Verbindung stehen und von denen die eine jeweils als Pumpe und die andere als Motor arbeitet. Je nach Fahrstufe können die beiden Maschinen dabei ihre Rollen vertauschen.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.
Die hydrostatischen Axialkolbenmaschinen stellen einen wesentlichen Bestandteil des hydrostatischen Leistungsverzweigungsgetriebes dar und prägen massgeblich die Eigenschaften des Getriebes wie z.B. den Wirkungsgrad, die Baugrösse, die Komplexität, den überdeckten Geschwindigkeitsbereich, Art und Anzahl der Fahrstufen und dgL Beispiele für derartige hydrostatische Axialkolbenmaschinen sind in der DE-A1-198 33 711 oder der DE-A1-10044 784 oder der US-A1- 2004/0173089 offenbart. Funktionsweise und Theorie von hydrostatischen Axialkolbenmaschinen sowie eines damit ausgerüsteten leistungsverzweigten Traktorgetriebes sind in einer Veröffentlichung der TU München aus dem Jahr 2000 von H. Bork et al., „Modellbildung, Simulation und Analyse eines stufenlosen leistungsverzweigten Traktorgetriebes", beschrieben.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 Munich from the year 2000 by H. Bork et al., "Modeling, Simulation and Analysis of a Continuously Variable Power Tractor Drive".
Wesentlich für die Funktion derartiger Getriebe ist die Verstellung bzw. Verschwenkung der Hydrostaten in einem weiten Winkelbereich, um dieEssential for the function of such transmission is the adjustment or pivoting of the hydrostat in a wide angular range to the
Leistungsübertragung im hydraulischen Zweig zu verändern bzw. die Funktion der Hydrostaten zwischen Motorfunktion und Pumpenfunktion umzuschalten. Die Verstellmechanik soll dabei kompakt im Aufbau, sicher in der Funktion und mit ausreichender Genauigkeit betreibbar sein. Darüber hinaus ist es wünschenswert, die Verstellmechanik für Wartungszwecke leicht zugänglich zu gestalten.To change power transmission in the hydraulic branch or to switch the function of the hydrostat between motor function and pump function. 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.
DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION
Es ist Aufgabe der Erfindung, eine Verstelleinheit anzugeben, welche diese Forderungen erfüllt.It is an object of the invention to provide an adjustment that meets these requirements.
Die Aufgabe wird durch die Gesamtheit der Merkmale des Anspruchs 1 gelöst. Wesentlich für die Erfindung ist, dass die innerhalb der Verstelleinheit vorgesehenen hydraulisch betätigbaren Verstellmittel, Steuerventile undThe object is solved by the entirety of the features of claim 1. Essential for the invention is that provided within the adjustment hydraulically actuated adjusting means, control valves and
Betätigungsmittel zum Betätigen der Steuerventile direkt zwischen den beiden Hydrostaten angeordnet sind. Hierdurch wird insbesondere ein kompakter Aufbau erreicht.Actuating means for actuating the control valves are arranged directly between the two Hydrostaten. As a result, in particular a compact construction is achieved.
Eine Ausgestaltung der Erfindung ist dadurch gekennzeichnet, dass dieAn embodiment of the invention is characterized in that the
Schwenkachsen der Hydrostaten parallel zueinander ausgerichtet sind, dass die Steuerventile Längsachsen aufweisen, entlang derer zum Betätigen der Steuerventile jeweils ein Ventilschieber verschiebbar ist, dass die Steuerventile mit Abstand voneinander derart angeordnet sind, dass Ihre Längsachsen parallel zueinander und senkrecht zu den Schwenkachsen der Hydrostaten ausgerichtet sind, und dass die Betätigungsmittel Verstellhebel umfassen, über welche die Steuerventile betätigt werden, und welche in einer senkrecht zu den Schwenkachsen der Hydrostaten liegenden Schwenkebene verschwenkbar sind.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.
Insbesondere umfassen die Betätigungsmittel weiterhin eine Verstellwalze, welche zwischen den Steuerventilen angeordnet und um eine Drehachse drehbar ist, die parallel zu den Längsachsen der Steuerventile ausgerichtet ist, und welche an ihrem Umfang Führungsbahnen zur Steuerung der Schwenkbewegung der Verstellhebel aufweisen, die mit ihren einen Enden die Führungsbahnen auf der Verstellwalze abtasten.In particular, 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.
Bevorzugt sind die Verstellhebel an den Ventilschiebern schwenkbar gelagert und stehen mit ihren anderen Enden mit den Hydrostaten in Eingriff, derart, dass bei einem Verschwenken der Hydrostaten um ihre Schwenkachsen die Verstellhebel) in vorbestimmter Weise in ihrer Schwenkebene verschwenkt werden, wobei die Kopplung zwischen den Verstellhebeln und den Hydrostaten vorzugsweise jeweils einen um die Schwenkachsen drehbaren Kurbeltrieb umfasst.Preferably, 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.
Die Verstellwalze wird insbesondere von einem elektrischen Motor angetrieben. Zur manuellen Drehung der Verstellwalze kann eine zwischen Motor und Verstellwalze angeordnete Notbetätigung vorgesehen sein, mit der es möglich ist, bei Ausfall anderer Systeme einen Notfahrbetrieb des zugehörigen Fahrzeugs aufrechtzuerhalten.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.
Eine andere Ausgestaltung der Erfindung zeichnet sich dadurch aus, dass die hydraulisch betätigbaren Verstellmittel für jeden Hydrostaten wenigstens einen Verstellzylinder umfassen, welcher mit einem Verstellkolben an einem um die Schwenkachse verschwenkbaren Schwenkhebel des Hydrostaten angreift.Another embodiment of the invention is characterized in that the 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.
Insbesondere können für jeden Hydrostaten zwei in entgegengesetzte Richtungen arbeitende Verstellzylinder vorgesehen sein, welche vorzugsweise an demselben Schwenkhebel angreifen. Eine weitere Ausgestaltung der Erfindung ist dadurch gekennzeichnet, dass die Steuerventile zum Steuern der hydraulisch betätigbaren Verstellmittel und die Betätigungsmittel zum Betätigen der Steuerventile in einem nach oben offenen Gehäuse untergebracht sind, welches mit einem Deckel verschliessbar ist, dass die Steuerventile und ausgewählte Betätigungsmittel auf der Unterseite des Deckels angebracht sind, und dass die Steuerventile mit den hydraulisch betätigbaren Verstellmitteln über ein im Deckel integriertes Druckverteilsystem mit einzelnen Hydraulikkanäle in Verbindung stehen.In particular, two adjusting cylinders operating in opposite directions can be provided for each hydrostat, which preferably engage on the same pivoting lever. 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.
Die Hydrostaten arbeiten insbesondere wahlweise als Pumpe und als Motor arbeiten, wobei ihr Schwenkbereich jeweils wenigstens +/- 45° beträgt.In particular, the hydrostats operate selectively as a pump and as a motor, their pivoting range being at least +/- 45 ° in each case.
KURZE ERLÄUTERUNG DER FIGURENBRIEF EXPLANATION OF THE FIGURES
Die Erfindung soll nachfolgend anhand von Ausführungsbeispielen im Zusammenhang mit der Zeichnung näher erläutert werden. Es zeigenThe invention will be explained in more detail with reference to embodiments in conjunction with the drawings. Show it
Fig. 1 in einer schematisierten Darstellung den prinzipiellen Aufbau eines beispielhaften stufenlosen hydraulischenFig. 1 in a schematic representation of the basic structure of an exemplary continuously variable hydraulic
Leistungsverzweigungsgetriebes, das zur Verwirklichung der Erfindung geeignet ist;Power split transmission suitable for realizing the invention;
Fig. 2 eine perspektivische Darstellung (von schräg unten gesehen) eines Getriebes nach dem in Fig. 1 dargestellten Prinzip, wobei nur der Deckel mit dem darunter angeordneten Getriebe und der darüber angeordneten Steuerung gezeigt ist;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 eine perspektivische Darstellung (von schräg unten gesehen) der beiden Hydrostaten aus Fig. 2 mit der zugehörigen Verstelleinheit gemäss einem bevorzugten Ausführungsbeispiel der Erfindung; Fig. 4 die Anordnung aus Fig. 3 in perspektivischer Darstellung schräg von oben gesehen;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 die Verstelleinheit aus Fig. 4 ohne Deckel und ohne zwei der Verstellzylinder;5 shows the adjusting unit of FIG. 4 without a cover and without two of the adjusting cylinders; FIG.
Fig. 6 schräg von unten gesehen den Deckel der Verstelleinheit aus Fig.Fig. 6 seen obliquely from below the lid of the adjusting unit of FIG.
3 mit den angebauten Steuerventilen, der Verstellwalze und den3 with the attached control valves, the adjusting roller and the
Verstellhebeln; undadjusting levers; and
Fig. 7 die Verstelleinheit der Fig. 3 bzw. 4 ohne Deckel von oben gesehen, wobei einer der Verstellzylinder weggelassen ist.Fig. 7, the adjusting unit of Fig. 3 and 4 seen without cover from above, wherein one of the adjusting cylinder is omitted.
WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS FOR CARRYING OUT THE INVENTION
In Fig. 1 ist in einer schematisierten Darstellung der prinzipielle Aufbau eines stufenlosen hydraulischen Leistungsverzweigungsgetriebes dargestellt, das zur Verwirklichung der Erfindung besonders geeignet ist. Das Getriebe 10 überträgt die Leistung eines Verbrennungsmotors 11 , der in Fig. 1 durch einen auf einer Kurbelwelle sitzenden Kolben symbolisiert ist. Das Getriebe 10 ist mit einer Eingangswelle (Antriebswelle) W1 mit dem Verbrennungsmotor 11 verbunden. Es gibt die übertragene Leistung über eine Ausgangswelle (Abtriebswelle) W7 ab. Durch das Getriebe 10 hindurch erstreckt sich bei Bedarf eine Zapfwelle W8, die eine direkte Fortsetzung der Eingangswelle W1 ist.In 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.
Den Kern des Getriebes 10 bilden ein Stufenplanetentrieb 12 mit einem grossen Sonnenrad Z1 und einem kleinen Sonnenrad ZV, den Doppelplanetenrädern Z2, Z2', dem Hohlrad Z3 und dem mit einem Zahnrad Z8 drehfest verbundenen Planetensteg 13, und zwei hydrostatische Axialkolbenmaschinen oderThe 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
Hydrostaten H1 und H2, deren Abtriebswellen W6 bzw. W12 jeweils über ein Paar von Kupplungen K3, K4 bzw. K1 , K2 auf unterschiedliche Weise mit der Eingangswelle W1 , der Ausgangswelle W7 und dem Stufenplanetentrieb 12 gekoppelt werden können. Die Hydrostaten H1 und H2, die wahlweise als Pumpe und Motor arbeiten, sind hydraulisch über nicht dargestellte Hochdruckleitungen miteinander verbunden. Der erste Hydrostat H1 kann mit seiner Abtriebswelle W6 mittels der Kupplung K3 über ein Vorgelege aus dem Zahnrad Z5 und einem mit dem Hohlrad Z3 drehfest verbundenen Zahnrad Z4 mit dem Hohlrad Z3 gekoppelt werden. Er kann aber auch mittels der Kupplung K4 über das Zahnrad Z11 , das Zwischenrad Z12 und das auf der Eingangswelle W1 drehfest angeordnete Zahnrad Z10 mit der Eingangswelle W1 gekoppelt werden.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. However, 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.
Der zweite Hydrostat H2 kann mit seiner Abtriebswelle W12 einerseits mittels der Kupplung K1 über die Hohlwelle W11 und das darauf drehfest angeordnete Zahnrad Z9, welches mit dem Zahnrad Z8 kämmt, mit dem Planetensteg 13 und damit mit der Ausgangswelle W7 gekoppelt werden. Er kann andererseits mittels der Kupplung K2 über das Zahnradpaar Z7, Z6 und die Hohlwelle W2 mit dem kleineren Sonnenrad ZV des Stufenplanetentriebs 12 gekoppelt werden.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. On the other hand, 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.
Die an der Eingangswelle W1 anstehende Leistung wird im Getriebe 10 durch den Stufenplanetentrieb 12 auf zwei Leistungszweige, nämlich einen mechanischen Leistungszweig und einen hydraulischen Leistungszweig aufgeteilt und später an der Ausgangswelle W7 wieder zusammengeführt. Der mechanische Leistungszweig läuft von der Eingangswelle W1 über das mit der Eingangswelle W1 drehfest verbundene grossere Sonnenrad Z1 , die Doppelplanetenräder Z2, den Planetensteg 13 und das Zahnrad Z8. Der hydraulische Leistungszweig läuft über die beiden hydraulisch verbundenen Hydrostaten H1 und H2 und ist je nach Schaltung der Kupplungen K1 ,..,K4 unterschiedlich ausgebildet. Wie in der Fig. 1 zeichnerisch angedeutet ist, können die beiden Hydrostaten H1 und H2 jeweils um +/- 45° geschwenkt werden.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 °.
Ein nach dem Getriebeschema aus Fig. 1 realisiertesA realized according to the transmission scheme of Fig. 1
Leistungsverzweigungsgetriebe ist in Fig. 2 aus der Sicht schräg von unten wiedergegeben, wobei nur der Deckel mit dem darunter angeordneten Getriebe und der darüber angeordneten Steuerung gezeigt ist. Das dazugehörige Gehäuseunterteil kann je nach Anforderung unterschiedlich konfiguriert werden.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.
Das Getriebe 10 der Fig. 2 umfasst als tragendes Teil einen im Wesentlichen rechteckigen Deckel 14, der von einem in einer Ebene liegenden, mit Bohrungen für die Verschraubung mit dem Gehäuseunterteil versehenen, umlaufenden Flansch 15 berandet ist. Auf der Unterseite des Deckels 14 sind im eigentlichen Getriebekern 17 in drei zueinander parallelen, ein gleichschenkliges Dreieck bildenden Achsen die in Fig. 1 schematisch dargestellten Getriebekomponenten (Hydrostaten, Kupplungen, Zahnräder und Wellen) angeordnet und gelagert. In der einen Achse befindet sich der erste Hydrostat H1 mit den Wellen W3, W5 und W6, den Zahnrädern Z5 und Z11 , sowie den Kupplungen K3 und K4. In der zweiten Achse befindet sich der zweite Hydrostat H2 mit den Wellen W9, W11 und W12, den Zahnrädern Z7 und Z9, sowie den Kupplungen K1 und K2. Die dritte, mittlere Achse umfasst W2, W7 und W10, den Stufenplanetentrieb 12, und die Zahnräder Z4, Z6, Z8 und Z10.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. On the underside of the cover 14, the transmission components (hydrostats, clutches, gears and shafts) 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. In the second axis, there is the second hydrostat H2 with the shafts W9, W11 and W12, the gears Z7 and Z9, and the clutches K1 and K2. The third, middle axis includes W2, W7 and W10, the stepped planetary gear 12, and the gears Z4, Z6, Z8 and Z10.
Für die Lagerung und Halterung des Getriebekerns 17 auf der Unterseite des Deckels 14 sind als wesentliche Komponenten ein parallel zum Deckel 14 orientierter Lagerboden 22, zwei senkrecht vom Deckel 14 nach unten abgehende, seitliche Tragpfosten 20, 21 , und zwei ebenfalls senkrecht vom Deckel 14 nach unten abgehende, Lagerwände vorgesehen, von denen nur die eine Lagerwand 23 zu sehen ist. Der Lagerboden 22 begrenzt den Getriebekern 17 auf der Unterseite. Er ist mit den Tragpfosten 20, 21 und den Lagerwänden 23 verschraubt. Im Lagerboden 22 sind die unteren Schwenklager 18, 19 für die jeweils um eine vertikale Achse (Schwenkachsen 27, 28 in Fig. 3) schwenkbaren Gehäuse der Hydrostaten H1 und H2 angeordnet. Die oberen Schwenklager sind nicht sichtbar im Deckel 14 selbst untergebracht. Die zueinander parallelen, senkrecht zu den drei Achsen des Getriebekerns 17 stehenden Lagerwände 23 dienen der Lagerung der zu den Achsen gehörenden Wellen. Insbesondere sind in der vorderen Lagerwand 23 die von den Kupplungen K1/K2 und K3/K4 kommenden Wellen W9 und W3 gelagert. Die zugehörigen Lager sind jeweils als bauliche Einheit mit einer Steuerhydraulik 24 bzw. 25 ausgeführt, die mit der Steuerung auf der Oberseite des Deckels in Verbindung steht und über axiale Bohrungen im inneren der Wellen W3 und W9 die Kupplungen K1 ,..,K4 betätigt. Der für die Steuerhydraulik benötigte Öldruck wird von einer Hydraulikpumpe 26 erzeugt, die Öl über einen nach unten gerichteten Ansaugstutzen aus dem in einer Wanne des Gehäuseunterteils sich bildenden Ölsumpf ansaugt und über in der Lagerwand 23 integrierte Kanäle zur Steuerung weiterleitet.For the storage and mounting of the gear core 17 on the underside of the lid 14 are as essential components 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. In the bearing bottom 22, 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. In particular, 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.
Aus der vorderen Lagerwand 23 ragt in der dritten, mittleren Achse die mit einer Kerbverzahnung versehene Eingangswelle bzw. innere Antriebswelle W1 heraus, über welche die Leistung vom Motor mittels einer im Gehäuseunterteil gelagerten äusseren Antriebswelle in das Getriebe eingekoppelt wird. Durch die hintereFrom the front bearing wall 23 protrudes in the third, central axis provided with a serration input shaft or inner drive shaft W1, via which the power from the engine is coupled by means of an outer drive shaft mounted in the housing lower part in the transmission. Through the rear
Lagerwand hindurch ist die ebenfalls mit einer Kerbverzahnung versehene innere Abtriebswelle W7 zugänglich, über welche die Leistung vom Getriebe mittels einer im Gehäuseunterteil gelagerten äusseren Abtriebswelle nach aussen abgegeben werden kann.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.
Auf der Oberseite des Deckels 14 ist die zum Betrieb des Getriebekerns 17 notwendige Getriebesteuerung so untergebracht, dass der von der Getriebesteuerung 16 veranlasste Eingriff in das Getriebe direkt durch den Deckel 14 hindurch erfolgt: Eine Art des Eingriffs ist die Verstellung der Hydrostaten H1 und H2, die ein Verschwenken der Schwenkgehäuse um max. +/-45° erfordert und die hydraulische Verbindung zwischen den beiden Hydrostaten beeinflusst. Zur Verstellung (Verschwenkung) der Hydrostaten H1 und H2 ist eine Verstelleinheit nach der Erfindung vorgesehen, deren Ausführungsbeispiel in den Fig. 3 bis 7 dargestellt ist.On the top of the cover 14, 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. For adjusting (pivoting) of the hydrostats H1 and H2, an adjusting unit according to the invention is provided, the embodiment of which is shown in FIGS. 3 to 7.
Die Verstelleinheit 16 ist zu einem Teil in einem auf der Oberseite des Deckels 14 angeordneten, nach oben offenen Gehäuse 60 (Fig. 2) untergebracht, dass mit einem (zweiten) Deckel 29 verschlossen werden kann. An das Gehäuse 60 sind an gegenüberliegenden Längsseiten paarweise gegenüberliegend insgesamt vier hydraulische arbeitende Verstellzylinder VZ 1 , VZV und VZ2, VZ2' aussen angeflanscht, deren zugehörige Verstellkolben VK1 , VKV und VK2, VK2' in das Gehäuse 60 hineinreichen und dort verschwenkend auf die Hydrostaten H1 und H2 einwirken (siehe Fig. 7). Die in entgegengesetzte Richtungen arbeitenden Verstellzylinder eines Zylinderpaares VZ1 , VZV bzw. VZ2, VZ2' erhalten den für ihre Betätigung notwendigen Druck über seitlich angeordnete Hydraulikkanäle 37, 38 (Fig. 4), die über nicht dargestellte Verbindungskanäle im Gehäuse 60 mit Hydraulikkanälen 32,.., 35 eines in den zweiten Deckel 29 integriertenThe 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). The working in opposite directions adjusting cylinder of a pair of cylinders VZ1, VZV or VZ2, VZ2 'receive the pressure necessary for their operation via laterally disposed hydraulic channels 37, 38 (Fig. 4), not shown via connecting channels in the housing 60 with hydraulic channels 32,. ., 35 of an integrated in the second cover 29
Druckverteilsystems 36 in Verbindung stehen. Der Druck in den Hydraulikkanälen 32, ..,35 des zweiten Deckels 29 und damit der Einsatz der mit dem Druck beaufschlagbaren Verstellzylinder VZ1 , VZV bzw. VZ2, VZ21 wird durch hydraulische Steuerventile (Servoventile) SV1 und SV2 gesteuert, die auf der Unterseite des zweiten Deckels 29 mit ihren Längsachsen 56, 57 parallel liegend angeflanscht sind und mit Druckanschlüssen 54, 55 (Fig. 7) über entsprechende vertikale Bohrungen im Deckel 29 mit den Hydraulikkanälen 32,..,35 in Verbindung stehen.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.
Der Deckel 29 erstreckt sich in einer Ebene, die senkrecht zu den parallelen Schwenkachsen 27, 28 der beiden Hydrostaten H1 , H2 orientiert ist. In einer parallelen Ebene unterhalb des Deckels verschwenkbar sind zwei Verstellhebel 45, 46 angeordnet, mittels derer die Ventilschieber 58, 59 der beiden Steuerventile SV1 , SV2 in den Längsachsen 56, 57 verschoben werden können. Dazu sind die Ventilschieber 58, 59 in einem Mittelabschnitt der Steuerventile SV1 , SV2 von oben frei zugänglich. Die Verstellhebel 45, 46 sind jeweils an den Ventilschiebern 58, 59 verschwenkbar gelagert, wobei sie mit etwa einem Drittel der Hebellänge in den Zwischenraum zwischen den beiden voneinander beabstandeten Steuerventilen SV1 , SV2 hineinragen und sich mit etwa zwei Dritteln der Hebellänge in entgegengesetzter Richtung bis zu den Hydrostaten H1 , H2 erstrecken. Zwischen den beiden Steuerventilen SV1 , SV2 ist eine Verstellwalze (Kurvenwalze) 42 angeordnet, die um eine Drehachse 41 drehbar in zwei Lagerböcken 43, 44 gelagert ist, die unter den Deckel 29 geschraubt sind. Die Drehachse 41 der Verstellwalze 42 verläuft parallel zu den Längsachsen 56, 57 der Steuerventile SV1 , SV2. Angetrieben wird die Verstellwalze 42 über eine Kupplungsscheibe 53 (Fig. 6) von einem elektrischen Motor 30, der aussen am Gehäuse 60 angeflanscht ist und von der Steuerelektronik bzw. -elektrik des Getriebes 10 angesteuert wird. Zwischen dem Motor 30 und der Verstellwalze 42 ist eine seitlich abgehende, von aussen zugängliche Notbetätigung 31 vorgesehen, mittels derer die Verstellwalze 42 (bei noch funktionierender Hydraulik) für den Notfahrbetrieb manuell verdreht werden kann.The cover 29 extends in a plane which is oriented perpendicular to the parallel pivot axes 27, 28 of the two Hydrostaten H1, H2. In a parallel plane below the lid pivotally 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. For this purpose, 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. Between the two control valves SV1, SV2, 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. 6) by an electric motor 30, which is flanged on the outside to the housing 60 and is controlled by the control electronics or electrics of the transmission 10. Between the motor 30 and the adjusting roller 42 a laterally outgoing, externally accessible emergency operation 31 is provided, by means of which the adjusting roller 42 (at still functioning hydraulic) for emergency operation can be manually rotated.
Die Verstellwalze 42 hat an ihrem Umfang Führungsbahnen 51 , 52, die von den Verstellhebeln 45, 46 mit den einen (inneren) Enden abgetastet werden. Mit den anderen (äusseren) Enden stehen die Verstellhebel mit den oberen Lagerzapfen der Hydrostaten H1 , H2 jeweils über einen Kurbeltrieb KT1 bzw. KT2 (Fig. 7) in Eingriff, wobei die Kopplung zwischen Verstellhebel 45, 46 und Kurbeltrieb KT1, KT2 über einen in einer Gabel 47 am Hebelende verschiebbaren Gleitstein 48 erfolgt. Der Kurbeltrieb KT1 , KT2 ist Teil einer am Hydrostaten M 1 H2 angeflanschten Schwenkplatte 49, 56, die mit dem Hydrostaten H1 , H2 um dessen Schwenkachse 27, 28 schwenkt, und an der die Verstellkolben VK1 , VK1' bzw. VK2, VK2' der Verstellzylinder VZ1 , VZ11 bzw. VZ2, VZ2' angreifen.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. The 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 '.
Wenn bei nicht schwenkenden Hydrostaten H1 , H2 die Verstellwalze 42 verdreht wird, schwenken die Verstellhebel 45, 46 je nach Verlauf der Führungsbahnen 51 , 52 um die durch die Gleitsteine 48 gehenden Drehachsen der Kurbeltriebe KT1 , KT2 und verschieben entsprechend die Ventilschieber 58, 59 der Steuerventile SV1 , SV2. Wenn bei nicht drehender Verstellwalze 42 die Hydrostaten verschwenkt werden, verschiebe sich ebenfalls die Ventilschieber 58, 59 der Steuerventile SV1 , SV2. Hierdurch wird eine mechanische Rückkopplung der Schwenkbewegung der Hydrostaten M 1 H2 auf die Steuerung des Verstellvorgangs bewirkt. Die Ventilschieber 58, 59 sind innerhalb der Steuerventile SV1 , SV2 durch Federn in Richtung der Längsachsen 56, 57 vorgespannt, so dass die Verstellhebel 45, 46 an den einen Seiten der Führungsbahnen 51 , 52 der Verstellwalze 42 spielfrei anliegen. Die Steuerventile SV1 , SV2 sind punktsymmetrisch zueinander angeordnet, so dass nur ein Ventiltyp benötigt wird.If 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. The 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.
Durch die erfindungsgemässe Ausgestaltung der Verstelleinheit wird ein kompakter Aufbau, eine präzise Steuerung und eine gute Zugänglichkeit erreicht. Insbesondere die parallele Ausrichtung der Längsachsen der Steuerventile und der Drehachse der Verstellwalze senkrecht zur Verbindungslinie zwischen den Schwenkachsen der Hydrostaten und senkrecht zu den Schwenkachsen selbst führt dazu, dass der Verstellmechanismus sehr kurz baut.The inventive design of the adjustment a compact design, precise control and good accessibility is achieved. In particular, 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.
BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS
10 Getriebe (stufenlos, hydrostatisch, leistungsverzweigt)10 gearboxes (stepless, hydrostatic, power split)
11 Verbrennungsmotor11 internal combustion engine
12 Stufenplanetentrieb12 stepped planetary gears
13 Steg (Stufenplanetentrieb) 14 Deckel (Getriebe)13 Bridge (stepped planetary gear) 14 Cover (gear)
15 Flansch (Deckel)15 flange (cover)
16 Verstelleinheit16 adjustment unit
17 Getriebekern 18,19 Schwenklager 20,21 Tragpfosten17 gear core 18,19 pivot bearing 20,21 support post
22 Lagerboden22 storage floor
23, Lagerwand23, storage wall
24,25 Steuerhydraulik (Kupplungen)24.25 control hydraulics (clutches)
26 Hydraulikpumpe 27,28 Schwenkachse (Hydrostat)26 hydraulic pump 27,28 swivel axle (hydrostat)
29 Deckel (Verstelleinheit)29 cover (adjusting unit)
30 Motor (Steuerung) 31 Notbetätigung (manuell)30 motor (control) 31 emergency operation (manual)
32,..,35 Hydraulikkanal (Druckverteilsystem)32, .., 35 Hydraulic channel (pressure distribution system)
36 Druckverteilsystem36 pressure distribution system
37,38 Hydraulikkanal (Verstellzylinder)37,38 hydraulic channel (adjusting cylinder)
39,40 Steuerventilanschluss39.40 Control valve connection
41 . Drehachse (Verstellwalze)41. Rotary axis (adjusting roller)
42 Verstellwalze (Kurvenwalze)42 adjusting roller (cam roller)
43,44 Lagerbock43,44 bearing block
45,46 Verstellhebel45.46 adjusting lever
47 Gabel47 fork
48 Gleitstein48 sliding block
49,56 Schwenkplatte49.56 swivel plate
50 Tastrolle50 sensing rollers
51 ,52 Führungsrille51, 52 guide groove
53 Kupplungsscheibe53 clutch disc
54,55 Druckanschluss54.55 pressure connection
56,57 Längsachse (Steuerventil)56.57 longitudinal axis (control valve)
58,59 Ventilschieber58.59 valve spool
60 Gehäuse (Verstelleinheit)60 housing (adjustment unit)
H1 ,H2 HydrostatenH1, H2 hydrostatics
K1....K4 KupplungK1 .... K4 clutch
KT1.KT2 KurbeltriebKT1.KT2 crank drive
SK1....SK4 HubkolbenSK1 .... SK4 reciprocating piston
SV1.SV2 SteuerventilSV1.SV2 control valve
SW Schwenkwinkel (in %)SW swivel angle (in%)
VK1.VK1' VerstellkolbenVK1.VK1 'adjusting piston
VK2.VK21 VerstellkolbenVK2.VK2 1 adjusting piston
VZ1.VZ1' VerstellzylinderVZ1.VZ1 'adjusting cylinder
VZ2.VZ2' VerstellzylinderVZ2.VZ2 'adjusting cylinder
W1 ,..,W12 WelleW1, .., W12 shaft
Z1 ,..,Z12 Zahnrad Z1, .., Z12 gear

Claims

PATENTANSPRÜCHE
1. Verstelleinheit (16) für ein stufenloses hydrostatisch verzweigtes Getriebe (10), welches Getriebe (10) zwei Hydrostaten (H1 , H2) umfasst, die mit Abstand nebeneinander angeordnet und jeweils um eine Schwenkachse (27 bzw. 28) verschwenkbar gelagert sind, dadurch gekennzeichnet, dass die Verstelleinheit (16) hydraulisch betätigbare Verstellmittel (VZ1 , VZ1 '; VZ2, VZ21) zum Verschwenken der Hydrostaten (H1 , H2) um ihre Schwenkachsen (27, 28) umfasst, dass Steuerventile (SV1 , SV2) zum Steuern der hydraulisch betätigbaren Verstellmittel (VZ1 , VZ1'; VZ2, VZ21) und Betätigungsmittel (30; 42,..,46) zum Betätigen der Steuerventile (SV1 , SV2) vorgesehen sind, und dass die Steuerventile (SV1 , SV2) und die Betätigungsmittel (30; 42,..,46) zwischen den beiden Hydrostaten (H 1 , H2) angeordnet sind.1. adjustment unit (16) for a stepless hydrostatically branched transmission (10), which transmission (10) comprises two hydrostats (H1, H2), which are arranged at a distance next to each other and each pivotable about a pivot axis (27 or 28), characterized in that the adjusting unit (16) comprises hydraulically actuatable adjusting means (VZ1, VZ1 ', VZ2, VZ2 1 ) for pivoting the hydrostats (H1, H2) about their pivot axes (27, 28), that control valves (SV1, SV2) for Controlling the hydraulically actuatable adjusting means (VZ1, VZ1 ', VZ2, VZ2 1 ) and actuating means (30; 42, .., 46) are provided for actuating the control valves (SV1, SV2), and in that the control valves (SV1, SV2) and the actuating means (30; 42, .., 46) are arranged between the two hydrostats (H 1, H 2).
2. Verstelleinheit nach Anspruch 1 , dadurch gekennzeichnet, dass die Schwenkachsen (27, 28) der Hydrostaten (H1, H2) parallel zueinander ausgerichtet sind, dass die Steuerventile (SV1 , SV2) Längsachsen (56, 57) aufweisen, entlang derer zum Betätigen der Steuerventile (SV1 , SV2) jeweils ein Ventilschieber (58, 59) verschiebbar ist, dass die Steuerventile (SV1 , SV2) mit Abstand voneinander derart angeordnet sind, dass Ihre Längsachsen (56, 57) parallel zueinander und senkrecht zu den Schwenkachsen (27, 28) der Hydrostaten (H1 , H2) ausgerichtet sind, und dass die Betätigungsmittel (30; 42, ..,46) Verstellhebel (45, 46) umfassen, über welche die Steuerventile (SV1, SV2) betätigt werden, und welche in einer senkrecht zu den Schwenkachsen (27, 28) der Hydrostaten (H1 , H2) liegenden Schwenkebene verschwenkbar sind.2. Adjusting unit according to claim 1, characterized in that the pivot axes (27, 28) of the hydrostats (H1, H2) are aligned parallel to each other, that the control valves (SV1, SV2) longitudinal axes (56, 57) along which to actuate the control valves (SV1, SV2) in each case a valve slide (58, 59) is displaceable, that the control valves (SV1, SV2) are spaced apart such that their longitudinal axes (56, 57) parallel to each other and perpendicular to the pivot axes (27 , 28) of the hydrostats (H1, H2) are aligned, and in that the actuating means (30, 42, .., 46) comprise adjusting levers (45, 46) via which the control valves (SV1, SV2) are actuated, and which a pivot plane lying perpendicular to the pivot axes (27, 28) of the hydrostat (H1, H2) are pivotable.
3. Verstelleinheit nach Anspruch 2, dadurch gekennzeichnet, dass die Betätigungsmittel (30; 42,..,46) weiterhin eine Verstellwalze (42) umfassen, welche zwischen den Steuerventilen (SV1 , SV2) angeordnet und um eine Drehachse (41) drehbar ist, die parallel zu den Längsachsen (56, 57) der Steuerventile (SV1 , SV2) ausgerichtet ist, und welche an ihrem Umfang Führungsbahnen (51 , 52) zur Steuerung der Schwenkbewegung der Verstellhebel (45, 46) aufweisen, die mit ihren einen Enden die Führungsbahnen (51 , 52) auf der Verstellwalze (42) abtasten.3. Adjusting unit according to claim 2, characterized in that the actuating means (30; 42, .., 46) further comprise an adjusting roller (42) which is arranged between the control valves (SV1, SV2) and about an axis of rotation (41) is rotatable , which is aligned parallel to the longitudinal axes (56, 57) of the control valves (SV1, SV2), and which at its periphery guideways (51, 52) for Control of the pivoting movement of the adjusting lever (45, 46) which scan with its one ends the guide tracks (51, 52) on the adjusting roller (42).
4. Verstelleinheit nach Anspruch 3, dadurch gekennzeichnet, dass die4. Adjusting unit according to claim 3, characterized in that the
Verstellhebel (45, 46) an den Ventilschiebern (58, 59) schwenkbar gelagert sind und mit ihren anderen Enden mit den Hydrostaten (H1 , H2) in Eingriff stehen, derart, dass bei einem Verschwenken der Hydrostaten (H1 , H2) um ihre Schwenkachsen (27, 28) die Verstellhebel (45, 46) in vorbestimmter Weise in ihrer Schwenkebene verschwenkt werden.Adjusting levers (45, 46) are pivotally mounted on the valve spools (58, 59) and with their other ends with the Hydrostaten (H1, H2) are engaged, such that upon pivoting of the Hydrostaten (H1, H2) about their pivot axes (27, 28) the adjusting levers (45, 46) are pivoted in a predetermined manner in its pivoting plane.
5. Verstelleinheit nach Anspruch 4, dadurch gekennzeichnet, dass die Kopplung zwischen den Verstellhebeln (45, 46) und den Hydrostaten (H1 , H2) jeweils einen um die Schwenkachsen (28, 29) drehbaren Kurbeltrieb (KT1 , KT2) umfasst.5. Adjusting unit according to claim 4, characterized in that the coupling between the adjusting levers (45, 46) and the Hydrostaten (H1, H2) each comprise a about the pivot axes (28, 29) rotatable crank mechanism (KT1, KT2).
6. Verstelleinheit nach Anspruch 3, dadurch gekennzeichnet, dass die Verstellwalze (42) von einem elektrischen Motor (30) angetrieben wird.6. Adjusting unit according to claim 3, characterized in that the adjusting roller (42) by an electric motor (30) is driven.
7. Verstelleinheit nach Anspruch 6, dadurch gekennzeichnet, dass zur manuellen Drehung der Verstellwalze (42) eine zwischen Motor (30) und Verstellwalze (42) angeordnete Notbetätigung (31) vorgesehen ist.7. Adjusting unit according to claim 6, characterized in that for manual rotation of the adjusting roller (42) between an engine (30) and adjusting roller (42) arranged emergency operation (31) is provided.
8. Verstelleinheit nach Anspruch 1 , dadurch gekennzeichnet, dass die hydraulisch betätigbaren Verstellmittel für jeden Hydrostaten (H 1 , H2) wenigstens einen Verstellzylinder (VZ1 , VZ1'; VZ2, VZ2') umfassen, welcher mit einem Verstellkolben (VK1 , VK1'; VK2, VK21) an einem um die Schwenkachse (27, 28) verschwenkbaren Schwenkhebel (49, 50) des Hydrostaten (H1 , H2) angreift.8. Adjusting unit according to claim 1, characterized in that the hydraulically actuatable adjusting means for each hydrostat (H 1, H2) comprise at least one adjusting cylinder (VZ1, VZ1 ', VZ2, VZ2'), which with an adjusting piston (VK1, VK1 '; VK2, VK2 1 ) on a about the pivot axis (27, 28) pivotable pivot lever (49, 50) of the Hydrostaten (H1, H2) engages.
9. Verstelleinheit nach Anspruch 8, dadurch gekennzeichnet, dass für jeden9. adjusting unit according to claim 8, characterized in that for each
Hydrostaten zwei in entgegengesetzte Richtungen arbeitende Verstellzylinder (VZ1 , VZ1'; VZ2, VZ2') vorgesehen sind, welche vorzugsweise an demselben Schwenkhebel (49, 50) angreifen.Hydrostat two working in opposite directions adjusting cylinder (VZ1, VZ1 ', VZ2, VZ2') are provided, which preferably act on the same pivot lever (49, 50).
10. Verstelleinheit nach Anspruch 1 , dadurch gekennzeichnet, dass die Steuerventile (SV1 , SV2) zum Steuern der hydraulisch betätigbaren Verstellmittel (VZ1 , VZT; VZ2, VZ2') und die Betätigungsmittel (30; 42, ...46) zum Betätigen der Steuerventile (SV1 , SV2) in einem nach oben offenen Gehäuse (60) untergebracht sind, welches mit einem Deckel (29) verschliessbar ist, dass die Steuerventile (SV1 , SV2) und ausgewählte Betätigungsmittel (42, ..,46) auf der Unterseite des Deckels (29) angebracht sind, und dass die Steuerventile (SV1 , SV2) mit den hydraulisch betätigbaren Verstell mittein (VZ1 , VZ1'; VZ2, VZ2') über ein im Deckel (29) integriertes Druckverteilsystem (36) mit einzelnen Hydraulikkanäle (32, ..,36) in Verbindung stehen.10. Adjusting unit according to claim 1, characterized in that the control valves (SV1, SV2) for controlling the hydraulically actuatable adjusting means (VZ1, VZT; VZ2, VZ2 ') and the actuating means (30; 42, ... 46) for actuating the Control valves (SV1, SV2) are housed in an upwardly open housing (60) which is closable with a cover (29) that the control valves (SV1, SV2) and selected actuating means (42, .., 46) on the underside the control valve (SV1, SV2) with the hydraulically actuatable adjustment (VZ1, VZ1 ', VZ2, VZ2') via a in the lid (29) integrated pressure distribution system (36) with individual hydraulic channels ( 32, .., 36).
11. Verstelleinheit nach Anspruch 1 , dadurch gekennzeichnet, dass die11. Adjusting unit according to claim 1, characterized in that the
Hydrostaten (H1 , H2) wahlweise als Pumpe und als Motor arbeiten, und dass ihr Schwenkbereich jeweils wenigstens +/- 45° beträgt. Hydrostat (H1, H2) either as a pump and as a motor work, and that their pivoting range is at least +/- 45 °.
EP08872255A 2008-02-08 2008-12-05 Adjusting unit for a continuously variable hydrostatically branched transmission Withdrawn EP2250404A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810008234 DE102008008234A1 (en) 2008-02-08 2008-02-08 Adjustment unit for a continuously variable hydrostatic branched transmission
PCT/CH2008/000520 WO2009097700A1 (en) 2008-02-08 2008-12-05 Adjusting unit for a continuously variable hydrostatically branched transmission

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EP2250404A1 true EP2250404A1 (en) 2010-11-17

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EP (1) EP2250404A1 (en)
JP (1) JP2011512493A (en)
KR (1) KR20110007098A (en)
CN (1) CN101939567A (en)
AU (1) AU2008350228A1 (en)
BR (1) BRPI0822293A2 (en)
CA (1) CA2711954A1 (en)
DE (1) DE102008008234A1 (en)
EA (1) EA201070938A1 (en)
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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010053012A1 (en) * 2010-12-02 2012-06-06 Claas Industrietechnik Gmbh Hydromechanical transmission
DE102010062951A1 (en) * 2010-12-13 2012-06-14 Zf Friedrichshafen Ag Actuating device for e.g. hydrostatic axial piston machine, has coupling device that includes sliding block which is pivotally mounted on actuating piston about rotational axis
DE102015209644A1 (en) * 2015-05-27 2016-12-01 Robert Bosch Gmbh Hydrostatic linear actuator and arrangement with hydrostatic linear actuators
EP4249769A1 (en) 2022-03-22 2023-09-27 Fuss Spezialfahrzeugbau GmbH Power split transmission for a motor vehicle with low reactive power and a large speed range

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 (en) 1977-12-22 1982-08-12 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Power-split hydrostatic-mechanical compound transmission
DE2904572C2 (en) 1979-02-07 1984-04-05 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Hydrostatic-mechanical power split transmission
DE2950619A1 (en) 1979-12-15 1981-06-19 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München POWER BRANCHING GEARBOX WITH A PLANET DIFFERENTIAL GEARBOX
FR2562627B1 (en) * 1984-04-09 1989-06-30 Chapuis Laurent METHOD AND DEVICE FOR CONTROLLING A HYDROSTATIC ASSEMBLY
JPS62224770A (en) * 1986-03-24 1987-10-02 Honda Motor Co Ltd Speed change control device for static hydraulic type continuously variable transmission
DE3619640A1 (en) 1986-06-11 1987-12-17 Man Nutzfahrzeuge Gmbh INSTATIONAL COMMERCIAL VEHICLE WITH OPERATING HYDRAULIC OPERATING DEVICES
DE3707382A1 (en) 1987-03-07 1988-09-15 Fendt & Co Xaver Hydrostatic-mechanical wheel drive
DE3726080A1 (en) 1987-08-06 1989-02-16 Man Nutzfahrzeuge Gmbh HYDROMECHANICAL POWER BRANCHING GEARBOX FOR A VEHICLE
DE3912369C2 (en) 1989-04-14 1996-02-22 Man Nutzfahrzeuge Ag Stepless hydrostatic-mechanical power split transmission
DE3912386C2 (en) 1989-04-14 1993-10-28 Man Nutzfahrzeuge Ag Infinitely variable hydrostatic-mechanical power split transmission
JPH0747232Y2 (en) * 1989-07-12 1995-11-01 株式会社神崎高級工機製作所 HST type axle drive
DE4343402A1 (en) * 1993-12-18 1994-04-28 Voith Gmbh J M Infinite hydrostatic load distribution gear - has planetary differential gearing and adjustable hydro units set inside gearbox housing with oppositely directed drive and driven shafts
DE4343401C2 (en) 1993-12-18 1995-06-01 Voith Gmbh J M Stepless hydrostatic power split transmission
DE19833711A1 (en) 1998-07-27 2000-02-10 Brueninghaus Hydromatik Gmbh Hydrostatic axial piston machine with a tracking device for a washer
DE10044784B4 (en) 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
US7722493B2 (en) * 2004-10-20 2010-05-25 Mali Holding Ag Power-branched transmission and method for the operation of such a transmission

Non-Patent Citations (1)

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

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EA201070938A1 (en) 2011-02-28
AU2008350228A1 (en) 2009-08-13
BRPI0822293A2 (en) 2015-06-30
DE102008008234A1 (en) 2009-08-13
MX2010008520A (en) 2010-10-25
KR20110007098A (en) 2011-01-21
CA2711954A1 (en) 2009-08-13
JP2011512493A (en) 2011-04-21
CN101939567A (en) 2011-01-05
WO2009097700A1 (en) 2009-08-13

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