WO2016066359A1 - Module de transmission pour un train d'entraînement comprenant un machine à plateau oscillant et une transmission mécanique - Google Patents

Module de transmission pour un train d'entraînement comprenant un machine à plateau oscillant et une transmission mécanique Download PDF

Info

Publication number
WO2016066359A1
WO2016066359A1 PCT/EP2015/072358 EP2015072358W WO2016066359A1 WO 2016066359 A1 WO2016066359 A1 WO 2016066359A1 EP 2015072358 W EP2015072358 W EP 2015072358W WO 2016066359 A1 WO2016066359 A1 WO 2016066359A1
Authority
WO
WIPO (PCT)
Prior art keywords
swash plate
transmission
transmission module
plate machine
axial distance
Prior art date
Application number
PCT/EP2015/072358
Other languages
German (de)
English (en)
Inventor
Armin Merz
Dirk Vahle
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2016066359A1 publication Critical patent/WO2016066359A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • 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

Definitions

  • the present invention relates to a transmission module according to the
  • Swash plate machines serve as axial piston pumps for the conversion of mechanical energy into hydraulic energy and as axial piston motor for
  • mechanical drive sub-string includes the hydraulic drive sub-string
  • the mechanical drive sub-string includes, inter alia, a mechanical transmission.
  • First and second swash plate machine is generally by means of
  • the transmission module leads with the
  • Swashplate machine facing away from the gearbox first ends of the screws have a smaller axial distance from the transmission than the center of mass of the swashplate machine.
  • the center of gravity of the swash plate machine thus has a large axial distance to the first ends of the screws, so that the transmission module forms a vibration prone system.
  • the vibrations can also lead to mechanical wear and damage to the transmission module.
  • a stiffening of the transmission housing to shift the natural vibration frequencies in non-critical areas is a high cost and the disadvantage of a larger mass of
  • Transmission module connected, so that the transmission module for mobile applications in a motor vehicle would no longer be suitable.
  • EP 1 013 928 A2 shows an axial piston pump in a swashplate design with a driven circumferential and a plurality of piston bores having cylinder bores, wherein in each separated by webs piston bores are arranged linearly between a bottom dead center and a top dead center pistons and a low pressure connection kidney and a Hochdruckin kidney having control disk is provided.
  • the CH 405 934 shows a Schrägusionnaxialkolbenpumpe whose non-rotating cylinder block for varying the flow rate in dependence on the delivery pressure is longitudinally displaceable, wherein at the pressed by a spring in the direction of increasing the delivery cylinder block a
  • Control slide unit is attached with a spool.
  • DE 27 33 870 C2 shows a control device for a
  • Oblique disk axial piston pump on each side of the cradle for pivoting the swash plate, each a hydraulically acted upon
  • both motors by means of a pivotable about the pivot axis of the cradle arranged plate-shaped Control valve spool are controllable and are used to adjust the flow rate of the pump.
  • Transmission module for a drive train, comprising a transmission, a swash plate machine with a drive shaft and the
  • Swash plate machine has a center of gravity, at least one connecting element with the swash plate machine is fixed to the transmission and the at least one connecting element each having a first, the swash plate machine opposite end and a second, the swash plate machine facing end, wherein in the direction of a longitudinal axis of the drive shaft of the swash plate machine the axial distance of the at least one first end of the at least one
  • Connecting element to a fictitious plane is greater than the axial distance of the center of mass of the swash plate machine to the fictitious plane and the fictitious plane perpendicular to the longitudinal axis of the drive shaft
  • the center of gravity of the swashplate machine is thus arranged between the first end of the at least one connecting element and the transmission.
  • the at least one connecting element with the swash plate machine in particular the connection plate of the swash plate machine or the housing of
  • Transmission module are significantly reduced.
  • the airborne and structure-borne noise emissions of the transmission module can be reduced in the arrangement in a motor vehicle and, in addition, the mechanical wear on the transmission module is reduced, thereby extending the service life of the transmission module.
  • the gearbox is in the arrangement the transmission module to the motor vehicle generally connected to an internal combustion engine, so that the transmission and thus also the transmission module at least partially carries out the vibrations of the internal combustion engine, that is from the vibrations of the
  • the transmission is a mechanical transmission with a transmission housing and / or the notional plane intersects the transmission or the fictitious plane intersects at an end of the transmission opposite the swashplate engine
  • Mass center of gravity of the transmission and / or the longitudinal axis corresponds to the axis of rotation of the drive shaft.
  • the fictional level can also be at the
  • the swash plate machine is attached to the transmission housing.
  • the swash plate machine is in particular positive and / or non-positively attached to the transmission, in particular the transmission housing.
  • Mass center of the swash plate machine to the fictitious plane.
  • the transmission module comprises a plurality of connecting elements and the axial distance of a plurality of first ends of the connecting elements is greater, in particular by 10%, 20% or 30% greater than the axial distance of the center of mass
  • the Ubertragungsmodul comprises a plurality of connecting elements and the axial distance of all first ends of the connecting elements is greater, in particular by 10%, 20% or 30% greater than the axial distance of the center of mass of the swash plate machine to the fictitious plane.
  • the axial distance between the at least one first end of the at least one connecting element and the notional plane is substantially equal to the maximum axial distance of the swashplate machine in the region of the at least one first end to the notional plane.
  • the axial distance of the at least one first end of the at least one connecting element to the fictitious plane with a deviation of less than 20%, 10%, 5% or 3% of the maximum axial distance of the swash plate machine in the region of at least one first End to the fictitious level.
  • the transmission module comprises a plurality of connecting elements and the axial distance of a plurality of first ends, in particular all first ends of the connecting elements is substantially the maximum axial distance of the swash plate machine in the region of the at least one first end to the fictitious plane.
  • the transmission module comprises a plurality of connecting elements and the axial distance between a plurality of first ends, in particular all first ends of the connecting elements is with a deviation of less than 20%, 10%, 5% or 3% of the maximum axial distance of the swash plate machine in the range of the at least one first end to the fictitious plane.
  • the at least one connecting element is designed as a screw or a bolt and preferably each screw or bolt comprises a head, which forms the first end.
  • connecting elements can also be used, for example, a rivet.
  • the swash plate machine comprises a housing as a main housing and a connection plate and the first end of the at least one connecting element is in the region or on the
  • Arranged terminal plate in particular is depending on a head of at least one
  • the main housing consists at least partially, in particular completely, of light metal, in particular aluminum
  • the connection plate consists at least partially, in particular completely, of
  • the head rests on the connecting plate and applies a compressive force as a holding force on the connecting plate, so that thereby pressed by the pressing force, the connecting plate and thus the swash plate machine in the direction of the transmission.
  • connection plate one each on the connection plate
  • the connecting element is arranged and / or on the transmission, in particular gear housing, is ever a bore, in particular
  • Connecting element arranged and / or fixed, in particular with a screw connection.
  • the bore has an internal thread and the at least one connecting element, in particular the screw, has an external thread, and the external thread of the connecting element is screwed into the internal thread on the bore, so that the connecting element is connected to the screw connection with the transmission.
  • a Zentrierstutzen is formed on the housing, in particular the main housing, the swash plate machine and the Zentrierstutzen is within a centering on the transmission, in particular gear housing arranged or vice versa for centering, in particular radial centering, the swash plate machine with respect to the transmission and / or Transmission module includes two
  • Swash plate machines and the two swash plate machines are each connected to the at least connecting element on the transmission according to the
  • the centering nozzle has a radial outer surface which rests against the centering opening, thereby centering the swashplate machine with respect to the gearbox.
  • the transmission module comprises two
  • powertrain with a hydraulic drive sub-string and a mechanical drive sub-strand for a motor vehicle comprising a transmission module with a first and second swash plate machine for converting mechanical energy into hydraulic energy and vice versa and with a mechanical transmission, at least one pressure accumulator, wherein the transmission module as a in this patent application described transmission module is formed.
  • the drive train comprises two swash plate machines, which are hydraulically connected to each other and act as a hydraulic transmission and / or the drive train comprises two pressure accumulator ais
  • 1 is a longitudinal section of a swash plate machine
  • Fig. 2 shows a cross section A-A of FIG. 1 a valve disc of
  • FIG. 3 is a greatly simplified longitudinal section of a transmission module in a first embodiment
  • 4 is a greatly simplified longitudinal section of the transmission module in a second embodiment
  • 5 is a greatly simplified longitudinal section of the transmission module in a third embodiment
  • FIG. 6 shows a drive train for a motor vehicle.
  • a swashplate machine 1 shown in a longitudinal section in FIG. 1 serves as axial piston pump 2 for conversion or conversion of mechanical energy (torque, speed) into hydraulic energy (volume flow, pressure) or as axial piston motor 3 for conversion or conversion of hydraulic energy (volume flow, pressure ) into mechanical energy (torque,
  • a drive shaft 9 is by means of a bearing 10 at a
  • a cylinder drum 5 is rotationally fixed and connected in the axial direction, wherein the drive shaft 9 and the cylinder drum 5 are formed in one or two parts and the boundary between the drive shaft 9 and the cylinder barrel 5 is shown in Fig. 1 by dashed lines.
  • the cylinder drum 5 carries out the rotational movement of the drive shaft 9 with due to a rotationally fixed connection.
  • a plurality of piston bores 6 with an arbitrary cross section, for example square or circular, incorporated.
  • Piston bores 6 are aligned substantially parallel to the axis of rotation 8 of the drive shaft 9 or the cylinder drum 5.
  • Piston holes 6 are each a piston 7 movably mounted.
  • Pivoting cradle 14 is pivotable about a pivot axis 15 on the
  • the pivot axis 15 is aligned perpendicular to the plane of Fig. 1 and parallel to the plane of Fig. 2.
  • Rotation axis 8 of the cylinder drum 5 is arranged parallel to and in the plane of Fig. 1 and perpendicular to the plane of Fig. 2.
  • the housing 4 is liquid-tight, an interior space 44 which with
  • the pivoting cradle 14 has a flat or planar support surface 18 for the indirect support of a retaining disk 37 and for the direct support of sliding shoes 39.
  • the retaining disc 37 is provided with a plurality of sliding shoes 39 and each sliding block 39 is connected to a respective piston 7.
  • the sliding block 39 has a bearing ball 40 (FIG. 1), which is fastened in a bearing socket 59 on the piston 7, so that a piston connection point 22 between the bearing ball 40 and the bearing socket 59 is formed on the piston 7.
  • Bearing ball 40 and bearing cup 59 are both complementary or spherical, so characterized in a corresponding possibility of movement between the bearing ball 40 and the bearing cup 59 to the piston 7, a permanent connection between the piston 7 and the shoe 39 is present. Due to the connection of the piston 7 with the rotating cylinder drum 5 and the connection of the bearing cups 59 with the
  • Pressing force on the support surface 18 is pressed.
  • the pivoting cradle 14 is - as already mentioned - pivotally mounted about the pivot axis 15 and further comprises an opening 42 (Fig. 1) for
  • the pivoting cradle 14 is thus by means of a
  • Swivel axis 15 pivotally mounted.
  • the illustration in Fig. 1 the
  • Support surface 18 according to the sectional formation in Fig. 1 a pivot angle ⁇ of approximately + 20 °.
  • the pivot angle ⁇ is present between a fictitious plane perpendicular to the axis of rotation 8 and a plane spanned by the flat bearing surface 18 of the pivoting cradle 14 according to the
  • the pivoting cradle 14 can be between two Pivoting limit angle ⁇ between + 20 ° and -20 ° by means of two pivoting devices 24 are pivoted.
  • the first and second pivoting means 25, 26 as pivoting means 24 has a connection point 32 between the pivoting device 24 and the
  • the two pivoting devices 24 each have an adjusting piston 29, which is movably mounted in an adjusting cylinder 30.
  • the adjusting piston 29 or an axis of the adjusting cylinder 30 is aligned substantially parallel to the axis of rotation 8 of the cylinder drum 5.
  • Adjusting piston 29 has this a bearing cup 31, in which a
  • Bearing ball 19 is mounted.
  • the bearing ball 19 on a pivot arm 16 (Fig. 1 to 2) of the pivoting cradle 14 is present.
  • Pivoting device 25, 26 is thus connected to a respective pivot ball 19 on a respective pivot arm 16 with the pivoting cradle 14.
  • the pivoting cradle 14 can be pivoted about the pivot axis 15, as a result Adjustment piston 29 to the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30, a force is applied.
  • this pivotal movement of the pivoting cradle 14 from.
  • a valve disk 1 1 is located on the end of the cylinder drum 5 shown on the right in FIG. 1, with a kidney-shaped high-pressure opening 12 and a kidney-shaped
  • the piston bores 6 of the rotating cylinder drum 5 are thus fluidly connected in an arrangement on the high-pressure opening 12 with the high-pressure opening 12 and in an arrangement on the
  • Low-pressure port 13 fluidly connected to the low pressure port 13. At a swivel angle ⁇ of 0 ° and during operation of the
  • Swash plate machine 1 for example, as axial piston 2, despite a rotational movement of the drive shaft 9 and the cylinder drum 5 no hydraulic fluid conveyed by the axial piston pump 2, since the piston 7 perform no strokes in the piston bores 6.
  • the piston bores 6, which are temporarily in fluid-conducting connection with the high-pressure opening 12 have a greater pressure on hydraulic fluid than the piston bores 6 which are temporarily in fluid-conducting connection with the low-pressure opening 13.
  • An axial end 66 of the cylinder drum 5 rests on the valve disc 1 1.
  • a first side 64 of the housing 4 and the flange 21 of the housing 4 an opening 63 is formed with the bearing 10 and a second side 65 has a recess for supporting the drive shaft 9 with a further storage 10.
  • the housing 4 on the second side 65 is formed by a connecting plate 73 made of steel and in the connecting plate 73 hydraulic channels for the pivoting devices 24 and hydraulic channels (not shown) for conducting hydraulic fluid to the high-pressure and low-pressure ports 12, 13 incorporated.
  • the remaining part of the housing 4 without the terminal plate 73 is formed by a main housing 72 made of aluminum.
  • the main housing 72 includes the flange 21 and a radial main housing 62 for radial
  • connection plate 73 is fastened to the radial main housing 62 by screws (not shown). In Fig. 1, a transmission 35 is not shown.
  • the retaining disc 37 is formed annularly as a flat disc and thus has an opening 38 for the passage of the drive shaft 9.
  • Retaining disc 37 sliding shoes 39 are fixed with bearing balls 40.
  • the retaining disc 37 has eight holes within which the sliding shoes 39 are arranged, so that the sliding shoes 39 in the radial direction, d. H.
  • a powertrain 45 shown in FIG. 6 has first and second
  • Swash plate machine 50, 51 and the mechanical transmission 35 on.
  • the two swash plate machines 50, 51, 1 and the mechanical transmission 35 are connected to a transmission module 17 with each other.
  • Fig. 3 is a longitudinal section of a first embodiment of the
  • Transmission module 17 shown. Two swashplate machines 1 are fastened to the transfer module 17, wherein only one swashplate machine 1 is shown due to the sectional formation in FIG. Both
  • Swash plate machines 1 are connected in an analogous and identical manner to the transmission 35 as the mechanical transmission 35.
  • Swash plate machine 1 is connected to a transmission housing 36 of the transmission 35 with a total of four connecting elements 61. Due to the
  • the connecting elements 61 are designed as screws 67 or bolts 68.
  • the connecting elements 61 have a first end 69 which is connected to the
  • Gear 35 is turned away and a second end 70, which to the
  • Gear 35 faces. In the area of the first end 69 of the
  • a head 79 is formed and the head 79 has a larger diameter than the shaft of the screw 67.
  • a bore 80 is incorporated as a through hole 81.
  • Into the transmission housing 36 is a bore 82 as a
  • the screw 67 has at the end portion of the shaft in the region of the second end 70 on an external thread and the external thread of the screw 67 is screwed into an internal thread on the blind hole 83, thereby characterized a screw 84 between the screw 67 and the gear housing 36 in the blind hole 83 exists.
  • the connecting elements 61 as the screws 67 are subjected to a tensile force, so that each head 79 of the screws 67 applies a compressive force as a holding force on the connection plates 73, thereby an axial bearing surface 87 on the housing 4 of the swash plate machine 1 on an axial counter-bearing surface 88 at the transmission housing 36 is pressed with a compressive force.
  • On the transmission 35, in particular the transmission housing 36 is also a
  • Centering opening 86 is formed and within the centering opening 86 is a Centering 85 of the housing 4 of the swash plate machine 1 is arranged.
  • the centering stub 85 and the centering opening 86 are aligned complementary to each other, so that a radial outer side of the centering stub 85 rests against the boundary of the centering opening 86 on the gear 85 and thereby in the radial direction, the swash plate machine 1 is aligned with respect to the transmission 35.
  • the transmission 35 has an end 77, which is facing away from the swash plate machine 1.
  • a notional plane 43 is oriented perpendicular to the longitudinal axis 8 or axis of rotation 8 of the drive shaft 9 and the notional plane 43 intersects the transmission housing at the end 77.
  • An axial distance 75 in the direction of the longitudinal axis 8 of a center of mass 71 of the swash plate machine 1 has a smaller distance to the notional plane 43 than the axial distances 76 of the first ends 69 of the connecting elements 61.
  • a maximum axial distance 78 of the swash plate machine 1 to the fictitious plane 43 that is, the maximum axial distance 78 of the connection plate 73 at the extreme end of the connection plate 73 facing away from the transmission 35 substantially corresponds to the axial distance 76, because the heads 79 are arranged in the region of the relevant end of the connection plate 73.
  • the connecting elements 61 are preferably not considered.
  • the connection plate 73 is made of steel and the
  • Main housing 72 of the swash plate machine 1 is made of aluminum in an analogous manner as well as the transmission housing 36 made of aluminum as
  • the Gear housing 36 has a cylindrical or stutzenformigen extension 89, within which the main housing 72 of the swash plate machine 1 is arranged.
  • the axial bearing surface 87 is formed on the connecting plate 73 and the axial counter bearing surface 88 on the extension 89 of the gear housing 36.
  • the main housing 72 and the centering 85 is movable in the axial direction relative to the transmission housing 36.
  • the notional plane 43 is oriented perpendicular to the longitudinal axis 8 and intersects a center of mass 74 of the transmission 35.
  • Gear housing 36 and the connection plate 73 is an annular extension of the main housing 72 of the swash plate machine 1 is arranged.
  • the blind hole 83 is, as in the second embodiment shown in FIG. 4, incorporated in the cylinder or Stutzenformigen extension 89 on the gear housing 36.
  • Fig. 6 the drive train 45 according to the invention is shown.
  • Drive train 45 has internal combustion engine 46, which drives a planetary gear 48 by means of a shaft 47.
  • Planetary gear 48 two shafts 47 are driven, wherein a first shaft 47 is connected to a clutch 49 with a mechanical transmission 35 and the mechanical transmission 35 is connected to the first shaft 47 with a
  • Differential gear 56 connected so that the mechanical transmission 35 forms part of the mechanical drive sub-strand 33.
  • a second or other shaft 47 driven by the planetary gear 48 drives the first swash plate machine 50 through a clutch 49 and the first one
  • Swash plate machine 50 is hydraulically connected by means of two hydraulic lines 52 to the second swash plate machine 51.
  • the first and second swash plate machines 50, 51 thereby form a hydraulic gear 60 and are thus part of a hydraulic drive sub-string 34 and of the second swash plate machine 51 by means of a shaft 47 also the differential gear 56 are driven.
  • the differential gear 56 drives the wheels 57 with the wheel shafts 58.
  • the drive train 45 has two pressure accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55. The two accumulators 53 are not shown by means of
  • Hydraulic lines also hydraulically connected to the two swash plate machines 50, 51, thereby mechanical energy of the
  • Internal combustion engine 46 can be hydraulically stored in the high pressure accumulator 54 and also in a recuperation of a motor vehicle with the drive train 45 also kinetic energy of the motor vehicle in the high pressure accumulator 54 can be stored hydraulically.
  • the differential gear 56 can additionally be driven with a swash plate machine 50, 51.
  • a holding force is applied to the swashplate machine 1 on the heads 79 as a compressive force in the region of the first ends 69 of the connecting elements 61.
  • Place of application of the holding force on the swash plate machine 1 has a greater axial distance to the fictitious plane 43 than the
  • Mass system are positively influenced, so that the
  • Transmission module 17 executes vibrations with a lower amplitude.
  • the air and structure-borne noise emissions of the transmission module 17 can be reduced in the arrangement in a motor vehicle and also due to the smaller amplitudes of the vibrations of the mechanical

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un module de transmission (17), destinée à une chaîne cinématique, qui comprend : une transmission (35), une machine à plateau oscillant (1) pourvue d'un arbre d'entraînement (9), la machine à plateau oscillant (1) présentant un centre de gravité (71), et au moins un élément de liaison (61) qui permet de fixer la machine à plateau oscillant (1) à la transmission (35), l'au moins un élément de liaison (61) comportant une première extrémité (69) opposée à la machine à plateau oscillant (1) et une seconde extrémité (70) dirigée vers la machine à plateau oscillant (1), par référence à la direction d'un axe longitudinal (8) de l'arbre d'entraînement (9) de la machine à plateau oscillant (1), la distance axiale (76) de l'au moins une première extrémité (69) de l'au moins un élément de liaison (61) à un plan imaginaire (43) étant supérieure à la distance axiale (75) du centre de gravité (71) de la machine à plateau oscillant (1) au plan imaginaire (43), le plan imaginaire (43) étant orienté perpendiculairement à l'axe longitudinal (8) de l'arbre d'entraînement (9) et le plan imaginaire (43) coupant la transmission (35).
PCT/EP2015/072358 2014-10-27 2015-09-29 Module de transmission pour un train d'entraînement comprenant un machine à plateau oscillant et une transmission mécanique WO2016066359A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014221766.0 2014-10-27
DE102014221766.0A DE102014221766A1 (de) 2014-10-27 2014-10-27 Übertragungsmodul

Publications (1)

Publication Number Publication Date
WO2016066359A1 true WO2016066359A1 (fr) 2016-05-06

Family

ID=54199244

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/072358 WO2016066359A1 (fr) 2014-10-27 2015-09-29 Module de transmission pour un train d'entraînement comprenant un machine à plateau oscillant et une transmission mécanique

Country Status (2)

Country Link
DE (1) DE102014221766A1 (fr)
WO (1) WO2016066359A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110469478B (zh) * 2019-09-02 2024-02-20 南通华东油压科技有限公司 一种斜盘式轴向柱塞泵及其生产方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3235378A1 (de) * 1982-09-24 1984-03-29 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Antriebsvorrichtung
DE4201156A1 (de) * 1991-04-15 1992-10-22 Kubota Kk Schwingungs- und geraeuschdaemmungssystem zur anbringung am getriebegehaeuse eines hydrostatischen stufenlosen getriebes
JPH05330353A (ja) * 1992-06-02 1993-12-14 Kubota Corp トラクターの変速部構造
DE19933822A1 (de) * 1999-07-20 2001-02-01 Zahnradfabrik Friedrichshafen Leistungsverzweigungsgetriebe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH405934A (de) 1962-07-26 1966-01-15 Weatherhead Co Schrägscheiben-Axialkolbenpumpe
US4076459A (en) 1976-09-14 1978-02-28 Abex Corporation Horsepower limiter control for a variable displacement pump
EP1013928A3 (fr) 1998-12-22 2000-11-08 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3235378A1 (de) * 1982-09-24 1984-03-29 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Antriebsvorrichtung
DE4201156A1 (de) * 1991-04-15 1992-10-22 Kubota Kk Schwingungs- und geraeuschdaemmungssystem zur anbringung am getriebegehaeuse eines hydrostatischen stufenlosen getriebes
JPH05330353A (ja) * 1992-06-02 1993-12-14 Kubota Corp トラクターの変速部構造
DE19933822A1 (de) * 1999-07-20 2001-02-01 Zahnradfabrik Friedrichshafen Leistungsverzweigungsgetriebe

Also Published As

Publication number Publication date
DE102014221766A1 (de) 2016-04-28

Similar Documents

Publication Publication Date Title
EP2890892A1 (fr) Moteur à disque en nutation
DE102012215238A1 (de) Schrägscheibenmaschine
WO2016066359A1 (fr) Module de transmission pour un train d'entraînement comprenant un machine à plateau oscillant et une transmission mécanique
WO2015150043A1 (fr) Machine à plateau incliné sous la forme d'une pompe à pistons axiaux et/ou d'un moteur à pistons axiaux
WO2014187607A1 (fr) Machine à plateau incliné
WO2015193132A1 (fr) Module de transmission
WO2014187608A1 (fr) Machine à plateau incliné
DE102015226403A1 (de) Schrägscheibenmaschine
WO2015018648A1 (fr) Machine à plateau oscillant
DE102012220743A1 (de) Schrägscheibenmaschine
WO2015086260A1 (fr) Machine à plateau oscillant
WO2014195083A1 (fr) Machine à plateau oscillant
WO2016045849A1 (fr) Machine à plateau oscillant
WO2015140033A1 (fr) Machine à plateau oscillant servant de pompe à piston axial et/ou de moteur à piston axial
WO2016026691A1 (fr) Machine à plateau incliné
WO2015150045A1 (fr) Machine à plateau oscillant configurée en pompe à piston axial et/ou en moteur à pistons axiaux
WO2015193131A1 (fr) Module de transmission
WO2014206713A1 (fr) Machine à plateau oscillant comme pompe à pistons axiaux et/ou moteur à pistons axiaux
WO2015158477A1 (fr) Machine à plateau oscillant utilisée comme pompe à pistons axiaux et/ou comme moteur à pistons axiaux
DE102015220879A1 (de) Schrägscheibenmaschine
DE102014225935A1 (de) Schrägscheibenmaschine
DE102013215597A1 (de) Schrägscheibenmaschine
DE102014206243A1 (de) Schrägscheibenmaschine
DE102014212208A1 (de) Schrägscheibenmaschine
DE102013215672A1 (de) Schrägscheibenmaschine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15770913

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15770913

Country of ref document: EP

Kind code of ref document: A1