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
  • 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
  • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
• • 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
  • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
  • F16H2037/0873—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft with switching, 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
  • F16H37/0833—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
  • F16H2037/108—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 four or more 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
• • 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
  • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
  • F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T74/00—Machine element or mechanism
  • Y10T74/19—Gearing
  • Y10T74/19149—Gearing with fluid drive

Definitions

• the present invention relates to the field of transmission technology. It relates to a (continuously variable) hydrostatically power-split transmission according to the preamble of claim 1.
• Such a transmission is e.g. known from DE-A1-26 33 718.
• 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 fixed ratio and a second, infinitely variable in translation power branch split and then rejoined to be available at 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 be the case especially for the high driving speeds that are used in road traffic over a longer period of time.
• the gear should be compact, 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
• 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, size, complexity, the covered speed range, type and number of speed stages and the like .
• Examples of such hydrostatic axial piston machines are in the DE-A1-198 33 711 or DE-A1-100 44 784 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 parts of the transmission (hydrostats, clutches, shafts, planetary gears, gears, etc.) are incorporated in a specially geared to the housing, which consists of a plurality of housing segments. If now such a transmission to be installed in a corresponding agricultural or construction vehicle, either the vehicle must be tuned in its construction to the already prefabricated gear, or the gearbox must be adapted to the conditions of an existing vehicle and thus redesigned. In both cases, the special adaptation of the vehicle or entire transmission results in considerable additional expenditure.
• the housing with the input and output shafts can be installed early in the vehicle, while only later can be decided by placing a lid with a corresponding gear unit, whether a mechanical or a hydrostatic transmission should be used. Accordingly, in the already finished vehicle transmission can be easily replaced.
• a characteristic feature of the new transmission is that the control for the adjustment or pivoting of the at least one
• Hydrostat is disposed on the top of the lid and acts through the lid on the at least one hydrostat.
• a preferred embodiment of the transmission according to the invention is characterized in that both hydrostats can be adjusted or pivoted by means of the control through the cover, that for controlling the glossverze Trent a plurality of clutches are provided, and that for summing the branched services a stepped planetary drive is provided.
• Another embodiment of the invention is characterized in that both hydrostats for controlling the hydraulic power in each case at least about +/- 45 ° about a pivot axis are pivotable that the lid is substantially in a plane that the pivot axes of the hydrostat perpendicular to Level of the lid are arranged, that the control comprises hydraulically operated reciprocating piston, which pivot via a lever mechanism, the Hydrostaten about its pivot axis, and that for controlling the reciprocating piston within the control, a control hydraulic is provided, which is controlled by an electric control motor.
• the hydrostats are arranged with their axes of rotation parallel to each other and to the plane of the lid, and have the inner drive and output shafts and the outer drive and output shafts on a common axis which is oriented parallel to the axes of rotation of the hydrostatic and between the axes of rotation of the Hydrostat is arranged.
• a further development is characterized in that a total of two or four clutches are provided, which are assigned in pairs to the hydrostat and arranged in the axis of rotation of the associated Hydrostaten, and that the stepped planetary gear is arranged in the common axis of the inner and outer input and output shafts.
• a lower-lying pan is formed on the lower housing part, and a hydraulic pump is arranged and fixed on the underside of the lid, which dips into the tub in the assembled state of the transmission with an intake.
• an electronic control system is provided for the transmission, and that the control electronics is arranged on the top of the lid.
• both hydrostats for controlling the hydraulic power are each pivotable about a pivot axis at least in a range between -45 ° and + 45 °.
• this transmission can be provided for a hybrid drive and coupled with an electric motor.
• the electric motor is coupled with the inner drive shaft via a transmission.
• the electric motor is arranged directly on the inner drive shaft.
• a known disk-shaped three-phase machine is suitable.
• the electric motor is connected via a control electronics with a battery in connection, from which he draws energy or in which he can store energy.
• the electric motor can be used as a generator and / or starter and / or retarder.
• a second electric motor may be provided which drives a PTO, wherein the second electric motor is connected via a second control electronics with a battery.
• Figure 1 is a schematic representation of the basic structure of a continuously variable hydraulic power split transmission with a total of four clutches, which is particularly suitable for the realization of the invention.
• Fig. 1 a comparable to Fig. 1 representation of a comparable continuously variable hydraulic power transmission with only two couplings, which is particularly suitable for the realization of the invention
• Fig. 2 shows the various speed stages of the power split transmission of Fig. 1 with a first
• FIGS. 1 and 2 shows the swivel angle SW1.2 of the two hydrostats and the hydraulic power component HL over the speed v in both forward driving stages for the transmission according to FIGS. 1 and 2;
• Fig. 4 is a perspective view (seen from obliquely above) of a
• Fig. 5 is a perspective view (viewed obliquely from below) of a transmission according to Fig. 4;
• Fig. 6 is a bottom view of the transmission of Fig. 4;
• FIG. 7 is a rear view of the transmission of FIG. 4; FIG.
• Fig. 8 is a front view of the transmission of Fig. 4; Fig. 9-11 two side views of a matching to the transmission of Figure 4 housing base.
• FIG. 12 shows the view from above into the housing lower part according to FIGS. 9-11;
• FIG. 13 shows a transmission according to FIG. 1 with additional electric motors for a hybrid drive or an electrically driven power take-off shaft;
• Fig. 14 shows a transmission according to FIG. 1 with a seated directly on the drive shaft additional electric motors for a hybrid drive.
• 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 is formed by a stepped planetary gear 12 with a large sun gear Z1 and a small sun gear Z1 ', the double planetary gears Z2, Z2', the ring gear Z3 and the planetary gear 13 rotationally fixed to a gear Z8, and two hydrostatic axial piston machines or hydrostatic units 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 12th 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.
• 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 namely a mechanical power branch and a hydraulic power branch and later recombined on the output shaft W7.
• Power branch runs from the input shaft W1 via the rotatably connected to the input shaft W1 larger sun gear Z1, 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 °.
• Fig. 2 The circuit of the clutches K1, .., K4 and the pivot position of the hydrostatic units H1, H2 for the various operating states of the transmission 10 are shown in Fig. 2, wherein the Fig. 2 (a1) to 2 (a3), the first forward drive, the Fig. 2 (b1) to 2 (b3), the second forward driving stage, and Fig. 2 (c1) to 2 (c3) Show reverse drive.
• Hydrostat H1 which operates as a pump in the first forward drive stage, is initially unshifted (swivel angle 0 °), while the second hydrostat H2 operating as the engine is fully swung out (maximum swivel angle 45 °). Due to the zero position of the first hydrostatic power H1, no pressure medium is pumped to the second hydrostatic power H2 and thus also no power is transmitted hydraulically. The starting process is initiated by the fact that the first hydrostat H1 is gradually pivoted, wherein increasingly volume is pumped to the second hydrostatic H2 and the second hydrostat begins to rotate with high torque and increasing speed.
• the hydrostatic pump (now the second hydrostat H2) operating as a pump is gradually swung out to the maximum swivel angle to the other side in a first phase, starting from the swivel angle 0 ° (FIG. 2 (b2)), during the Engine working Hydrostat (now the first Hydrostat H1) on the same side fully swung out.
• the first hydrostat H1 is then pivoted back into the zero position.
• the hydraulically transmitted power again approaches zero; the entire power is transmitted via the mechanical power branch.
• the diagram of the swivel angle SW1,2 of the two hydrostatic units and the percentage of the hydrostatically transmitted power HL as a function of the vehicle speed v resulting for a power split transmission according to FIGS. 1-8 is reproduced in FIG. Due to the 45 ° hydrostatic drive used in the transmission 10, the entire driving range ranging from 0 to the final speed can be subdivided into only two driving steps, the first driving step ranging from 0 to about 33% and the second driving step from 33% to 100%. In the first speed step, the hydrostatic transmitted power ratio decreases linearly from 0% to 100% initially. In the second gear, the proportion of hydrostatically transmitted power increases from 0 to a maximum of about 30% at about 50% of the max. Driving speed and then drops back to 0%. As a result, the efficiency at the end of the second gear does not drop again. This results in high
• Fig. 1 During the reverse drive (FIGS. 2 (c1) to 2 (c3)), starting from the situation of FIG. 2 (a1), the clutch K3 switches over to the clutch K4 (in the configuration operating without the clutches K3 and K4) Fig. 1 'is a switched power split reverse).
• the first hydrostat H1 operating as a pump is now driven directly by the input shaft W1 and, starting from 0 °, is gradually swung out to the other side.
• the fully swung-out second hydrostat H2 is swung back (Fig. 2 (c3)) and thus continues to increase speed.
• a transmission of the type shown in Fig. 1 or 1 ' according to the invention, the incorporation into a housing consisting of a cover and a housing base made so that the actual transmission with the hydrostat, the shafts, the clutches, the gears and the stepped planetary gear is arranged on the underside of the lid and forms a structural unit with the lid, while the electrical, electronic, mechanical and hydraulic control is arranged on the top of the lid and also forms a structural unit with the lid.
• FIGS. 4 to 8 Power split transmission according to a preferred embodiment of the invention is shown in FIGS. 4 to 8 seen from different angles, wherein only the lid is shown with the underlying transmission and the control disposed above.
• Housing base can be configured differently depending on requirements.
• a (non-limiting) example of such a lower housing part is shown in FIGS. 9 to 12 seen from different angles.
• the transmission 10 of Fig. 4 to 8 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 housing lower part 31 of FIG. 9 to 12, 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.
• the third, middle axis includes W2, W7 and W10, the stepped planetary gear 12, and the gears Z4, Z6, Z8 and Z10.
• the bottom shelf 27 limits the gear core 17 on the bottom. It is screwed to the support posts 26, 26 'and the bearing walls 28, 28'.
• the shafts W9 and W3 coming from the clutches K1 / K2 and K3 / K4 are mounted in the front bearing wall 28.
• the associated bearings are each executed as a structural unit with a control hydraulic 29 and 30, which is in communication with the control on the top of the lid and actuated via axial bores 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 22, the oil via a downward
• Intake manifold 23 sucks from the oil sump forming in a sump 32 of the lower housing part 31 (FIGS. 9-11) and transmits it to the control system via channels integrated in the bearing wall 28.
• the transmission control necessary for the operation of the transmission core 17 is accommodated so that the intervention in the transmission initiated by the transmission control 16 takes place directly through the cover 14.
• One type of intervention is the control of the hydrostat H1 and H2, on the one hand, a pivoting of the swivel housing by max. +/- 45 ° and on the other hand affects the hydraulic connection between the two hydrostat.
• a control hydraulic system 20 in the form of control blocks is provided on the top side of the cover directly above the two hydrostats H1, H2.
• Each of the two Hydrostaten H1, H2 are two opposite, hydraulically actuated reciprocating SK1, SK2 or SK3, SK4 associated, the a lever located in the control block 20 lever mechanism to pivot the associated hydrostatic H2 or H1.
• the hydraulic control of the reciprocating pistons SK1, .., SK4 and the hydraulic connection between the hydrostats H1, H2 is controlled by a rotatable control piston in the control block 20, which is driven by an electric control motor 21. Due to the direct connection between the control block 20 and the underlying Hydrostaten H1, H2 an extremely compact design is achieved, which allows easy accessibility to the individual components of the control from above and at the same time allows a high adaptability to the vehicle environment on the housing base 31.
• control electronics 18 Compact design, good accessibility and short distances are also due to the arrangement of the control electronics 18 in a box directly on the lid 14.
• the control electronics 18 evaluates physical measures from the transmission and commands from the engine control and controls of the vehicle and indicate control commands the control motor 21 and arranged around the control electronics 18 around on the lid 14 hydraulic valves, with the help of the clutches K1, .., K4 are actuated.
• the control electronics 18 to the necessary microprocessors and power outputs are housed.
• a closable filling opening 19 for the oil which is needed in the transmission for the hydraulic tasks.
• the lower housing part 31 only has the functions of protecting the gear core 17, holding the oil for the transmission, and decoupling the power into and out of the transmission .
• the coupling and uncoupling can - as in the example of FIGS. 9 to 12 shown - done by simple coaxial shafts 39, 40, which are rotatably mounted in the lower housing part 31.
• deflecting and / or conversion gear can be provided to change the position and orientation of the axes. In this way, a plurality of drive solutions in different vehicles can be realized with the same transmission block, that only the housing base 31 is adapted to the vehicle.
• a corresponding flange 36 is formed on the housing lower part 31.
• the shafts 39 and 40 are rotatably mounted in the end walls of the housing base 31 by means of corresponding bearings 37, 38.
• a longitudinally extending, recessed trough 32 is formed, in which a sump of the hydraulic oil collect and can be sucked by the hydraulic pump 22 on the gear core 17.
• a side walls of the lower housing part 31 can be arranged by means of lids lockable access openings 33, through which one can have access to the interior with the gearbox closed.
• the stepped planetary gear acts as a power split and summation gearbox and is used as the optimal solution for the basic setup.
• the hydrostatic power range is realized with the large angle technology +/- 45 ° with big advantages regarding efficiency and spreading in this gearbox.
• the gearbox is built according to a modular principle. - It is hydrostatic branched.
• the power transmission is stepless throughout the operating range.
• the transmission has a high overall efficiency without break-ins. - Only when starting the full hydrostatic power is required.
• the output speed is infinitely variable between 0 to 3000 rpm without interruption of traction
• the control is via an actuator.
• the electronics have a modular structure.
• FIG. 13 A first embodiment of such a hybrid drive is shown in FIG. 13 in a greatly simplified schematic: A first electric motor E1 acting as a drive motor is fixedly coupled via a gear Z13 to the gear Z11 and thus to the input shaft W1.
• the first electric motor E1 is supplied via a first control electronics 41 from a suitable battery 42 with the necessary electrical energy.
• the first control electronics 41 cooperates with the engine and transmission control (not shown in FIG. 13).
• the first electric motor E1 may drive the vehicle alone in certain cases (e.g., a city bus). But he can also support the engine 11.
• the first electric motor E1 is used as an electrodynamic retarder, or if the electric motor E1, in particular as part of regenerative braking, operates as a generator and stores energy back into the battery 42 (see the double arrows between the first control electronics 41 and first electric motor E1 and the battery 42).
• the battery 42 is preferably a lithium-ion battery is used, which combines a high storage capacity with great performance.
• a second control electronics 43 is provided between the battery 42 and the second electric motor E2.
• the second control electronics 43 can operate largely independently of the engine and transmission control, but must take at least on the current load and the state of charge of the battery 42 consideration.
• the type of electric motor E1 can be selected largely freely, because the electric motor E1 can be arranged laterally on the transmission, for example, where the overall length only plays a minor role ,
• battery e.g., lithium ion

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Arrangement Of Transmissions (AREA)
• Motor Power Transmission Devices (AREA)
• Agricultural Machines (AREA)

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• 2008
  • 2008-02-08 DE DE102008008236A patent/DE102008008236A1/de not_active Withdrawn
• 2009
  • 2009-01-21 CN CN200980104336XA patent/CN101939568A/zh active Pending
  • 2009-01-21 MX MX2010008704A patent/MX2010008704A/es not_active Application Discontinuation
  • 2009-01-21 KR KR1020107019935A patent/KR20110015508A/ko not_active Application Discontinuation
  • 2009-01-21 WO PCT/CH2009/000024 patent/WO2009097701A2/de active Application Filing
  • 2009-01-21 JP JP2010545340A patent/JP5339306B2/ja not_active Expired - Fee Related
  • 2009-01-21 BR BRPI0908821-0A patent/BRPI0908821A2/pt not_active IP Right Cessation
  • 2009-01-21 AU AU2009212076A patent/AU2009212076A1/en not_active Abandoned
  • 2009-01-21 CA CA2711967A patent/CA2711967A1/en not_active Abandoned
  • 2009-01-21 EP EP09708091A patent/EP2240707A2/de not_active Withdrawn
  • 2009-01-21 EA EA201070939A patent/EA020999B1/ru not_active IP Right Cessation
  • 2009-01-21 US US12/735,690 patent/US8915812B2/en active Active

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