CN101939567A - Adjusting unit for a continuously variable hydrostatically branched transmission - Google Patents
Adjusting unit for a continuously variable hydrostatically branched transmission Download PDFInfo
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- CN101939567A CN101939567A CN2008801263219A CN200880126321A CN101939567A CN 101939567 A CN101939567 A CN 101939567A CN 2008801263219 A CN2008801263219 A CN 2008801263219A CN 200880126321 A CN200880126321 A CN 200880126321A CN 101939567 A CN101939567 A CN 101939567A
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- fluid pressure
- control valve
- pivot
- regulon
- pressure governor
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Fluid Gearings (AREA)
- Friction Gearing (AREA)
- Fluid-Pressure Circuits (AREA)
- Motor Power Transmission Devices (AREA)
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
Technical field
The present invention relates to the drive technology field.It relates to the regulon that is used for the hydrostatic branch of continuous variable transmission device according to claim 1 preamble.
Background technique
Power branch transmission device is particularly useful for agricultural or building field with in the vehicle, tractor for example, for a long time cicada just.In this power branch transmission device, the power (it is generally by internal-combustion engine output) that input shaft or live axle place are available, in the first mechanical power branch with have between the second power branch of continuous variable velocity ratio and cut apart, and reconfigure then so that available at output shaft or driven shaft place with fixed drive ratio.The second power branch generally is designed to hydrostatic branch, and wherein two tilt axis that hydraulically connect each other or the hydrostatic axial piston unit (fluid pressure governor hydrostat) of wobbler type are operating as pump or motor alternatively.Here, velocity ratio can be revised by the pivoting angle that changes cylinder block or wobbler.Power between these two power branches is cut apart with the combination of branch power section and is generally carried out by means of planetary drive arrangement.The power branch transmission device of described type is described in each embodiment of 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 12386, DE-A1-43 43 401, DE-A1-43 43 402, EP-B1-0 249 001 and EP-A2-1273 828.
For can be in practice working power branch transmission device successfully, generally should have following characteristic:
-transmission device should have high efficiency in whole velocity range.Especially the long-time relatively high-speed driving of using is especially should be like this in road traffic.
-transmission device should be compactly designed so that it can be installed in the vehicle of very broad variety as much as possible under not having structural limitations.
-transmission device should allow to transmit high power.
The structure of-transmission device should be as far as possible simply with restricted power loss and increase operational reliability.
-transmission device should allow the complete electronic control that is connected with engine control, and sufficient urgent working procedure is provided, even some control unit fault.
The DE-A1-43 43 402 that mentions during beginning has described a kind of power branch transmission device that is called " SHL Getriebe " (the hydrostatic power of SHL=Stufenloses HydrostatischesLeistungsverzweigungsgetriebe=continuous variable branch's transmission device or CVHPST) in Germany, described transmission device is characterised in that the fluid pressure governor that the hydraulic pressure of two same tilt axis types connects, its can by means of clutch to or selector element K1/K2 and K3/K4 be connected to the planetary differential device by different way.Known CVHPS transmission device uses with type identification SHL-Z on urban transit bus and tests.Employed two fluid pressure governors have just in time 0-25 ° range of pivot.For advancing forward, provide 3 driving stages or driving scope: in first driving scope, transmit power hydrostatic mark for a little being 100% starting, and the mode that increases with linearity along with speed then approaches zero.Second driving scope, it is from zero extremely maximum about 27% and fall after rise extremely zero then.The 3rd driving scope, it is from zero maximum value 13% to the highest forward velocity.
The hydrostatic power transmission branch of this transmission device comprises two hydrostatic axial piston units that hydraulically connect to each other, and in all cases, one of them is operating as pump and another is operating as motor.These two mechanical energy are according to driving the stage exchange interaction.
Hydrostatic axial piston unit is represented the vitals of hydrostatic power branch transmission device, and the characteristic for transmission device has decisive influence, such as velocity range and the type in the stage of driving and the number etc. of its efficient, overall dimensions, complexity, covering.The example of this hydrostatic axial piston unit is open in DE-A1-198 33 711, DE-A1-100 44784 and US-A1-2004/0173089.Hydrostatic axial piston unit and with it the title of the operation of the power branch tractor transmission device of assembling and theoretical H.Bork Munich Polytechnics in 2000 etc. be to describe in the publication of " Modellbildung; Simulation und Analyseeines stufenlosen leistungsverzweigten Traktorgetriebes[Modeling, Simulation and Analysis of a Continuously Variable Power SplitTractor Transmission] ".
The main feature of this transmission device function is to regulate or the pivot fluid pressure governor in wide angular range, to regulate the power transmission in the hydraulic branch or switch fluid pressure governor between motor function and pumping function.Simultaneously, controlling mechanism will be compactly designed, work reliably and allow to operate with enough precision.And for the maintenance purpose, controlling mechanism is easy to reach.
Summary of the invention
The objective of the invention is to describe in detail the regulon that satisfies these demands.
This purpose is realized by the feature of claim 1 generally.But the actuator that key of the present invention is to be arranged at controlling device, the control valve of the hydraulic actuating in the regulon and is used for the actuator control valve should directly be arranged between two fluid pressure governors.Thereby especially realize compact structure.
One embodiment of the present of invention are characterised in that the pivot axis of fluid pressure governor aims in parallel with each other, be that control valve has many longitudinal axis, corresponding valve slider can move along every longitudinal axis wherein so that brake control valve, be that control valve is arranged as distance of each interval in mode so, so that many longitudinal axis are aimed in parallel with each other and are vertical with the pivot axis of fluid pressure governor, and be that actuator comprises adjustment (adjusting) lever, control valve activates by means of it, and it can pivot in the pivot plane of vertically locating with the pivot axis of fluid pressure governor.
Especially, actuator also comprises compensation roll, it is arranged between the control valve and can be around the spin axis rotation of aiming at abreast with the longitudinal axis of control valve, and compensation roll has the guide rail of the pivot movement that is used for the regulating and controlling lever on periphery, and adjustment (adjusting) lever contacts with guide rail on the compensation roll with one of end.
Adjustment (adjusting) lever preferably is supported on the valve slider pivotally, and engage with fluid pressure governor by means of its other ends, so that, when fluid pressure governor during around its pivot axis, adjustment (adjusting) lever pivots in its pivot plane in a predetermined manner, and the connection between adjustment (adjusting) lever and the fluid pressure governor preferably includes in all cases can be around the crank mechanism of pivot axis rotation.
Especially, compensation roll is by motor driving.For the manual rotation of compensation roll, the urgent actuator that is arranged between motor and the compensation roll can be set, if make other system failure also can keep the instant operation of associated vehicle.
An alternative embodiment of the invention is characterised in that, but the controlling device that is used for the hydraulic actuating of each fluid pressure governor comprises at least one adjusting cylinder, it is engaged in by means of regulating piston on the pivot rotaring lever of fluid pressure governor, and described lever can be around pivot axis.
Especially, two of effect adjusting cylinders can be provided for each fluid pressure governor in the opposite direction, and described cylinder preferably is engaged on the identical pivot rotaring lever.
But the actuator that an alternative embodiment of the invention is characterised in that the control valve of the controlling device that is used for controlling hydraulic actuating and is used for the actuator control valve is contained in the housing of upward opening that can the usefulness covering palte seal, be that control valve and selected actuator are installed on the bottom side of cover plate, but and be that control valve is by being integrated into cover plate and having the controlling device that the pressure distribution system of hydraulic tubing separately is connected to hydraulic actuating.
Especially, fluid pressure governor is operating as pump or motor alternatively, and its range of pivot is in all cases at least+/-45 °.
Description of drawings
To connect accompanying drawing below and explain the present invention in more detail with reference to exemplary embodiment.In the accompanying drawings:
Fig. 1 is schematically illustrated to be suitable for implementing exemplary continuous variable hydraulic power branch transmission device of the present invention;
Fig. 2 illustrates based on the perspective view of the transmission device of principle shown in Figure 1 (from obliquely following), only shows and is furnished with the cover plate that transmission device and its top are furnished with control system below it;
Fig. 3 illustrates the preferred illustrative embodiment according to the present invention, has the perspective view (from obliquely following) of two fluid pressure governors among Fig. 2 of associated adjustment unit;
Fig. 4 illustrates layout among Fig. 3 from top perspective view when seeing obliquely;
Fig. 5 illustrates the regulon among Fig. 4, does not have cover plate and does not regulate in the cylinder two;
Fig. 6 illustrates the cover plate of regulon among Fig. 3, has the control valve, compensation roll and the adjustment (adjusting) lever that adhere to, from obliquely following; And
Fig. 7 illustrates the regulon in Fig. 3 and 4, does not have cover plate, from the top, omits one and regulates cylinder.
Embodiment
Fig. 1 is schematically illustrated to be particularly suitable for implementing the basic structure of continuous variable hydraulic power of the present invention branch transmission device.The power that transmission device 10 transmits from internal-combustion engine 11, internal-combustion engine 11 is represented with the piston that is installed on the crankshaft in Fig. 1.Transmission device 10 is connected to internal-combustion engine 11 by input shaft (live axle) W1.The power that it is transmitted via output shaft (driven shaft) W7 output.If desired, can have the pto W8 that extends through transmission device 10, described axle is the direct continuation of input shaft W1.
The core of transmission device 10 is by having big sun gear Z1, small sun gear Z1`, dual planetary gear Z2, the planetary step change mechanism 12 of Z2`, ring wheel Z3 and planet carrier 13, be connected to gear Z8 with the rotation rigid manner, two hydrostatic axial piston units or fluid pressure governor H1 and H2, driven shaft W6 and W12, each can be respectively be connected to input shaft W1, output shaft W7 and planetary step change mechanism 12 by different way via a pair of clutch K3, K4 and K1, K2.Be operating as the fluid pressure governor H1 and the H2 of pump or motor alternatively, hydraulically be connected to each other by the high pressure line (not shown).The driven shaft W6 of the first fluid pressure governor H1 can be connected to the gear Z5 of ring wheel Z3 and the center tooth wheels of gear Z4 are connected to ring set Z3 via comprising with the rotation rigid manner by means of clutch K3.Yet described fluid pressure governor also may be connected to input shaft W1 via gear Z11, idler gear Z12 and with the gear Z10 that is arranged on the input shaft W1 of rotation rigid manner by means of clutch K4.
On the other hand, the driven shaft W12 of the second fluid pressure governor H2 can rigid manner be arranged thereon and the gear Z9 that engages with gear Z8 is connected to planetary carrier 13 via hollow shaft W11 with to rotate by means of clutch K1, and therefore is connected to output shaft W7.On the other hand, described fluid pressure governor can be connected to the small sun gear Z1` of planetary step change mechanism 12 by means of clutch K2 via gear mesh Z7, Z6 and hollow shaft W2.
In transmission device 10, the available power in input shaft W place is shunted between two power branches (just machine power branch and hydraulic power branch) by planetary step change mechanism 12, and subsequently in output shaft W7 place recombinant.Machine power branch transmits via big sun gear Z1, the dual planetary gear Z2, planet carrier 13 and the gear Z8 that are connected to input shaft W1 with the rotation rigid manner from input shaft W1.Hydraulic power branch transmits via fluid pressure governor H1 and the H2 that two hydraulic pressure connect, and according to clutch K1 .., the joint of K4 is differently constructed.Illustrated as Fig. 1, these two fluid pressure governor H1 and H2 each can pivot+/-45 °.
Represent obliquely from following in Fig. 2 according to the power branch transmission device that the diagram of gears among Fig. 1 is implemented, only show transmission arrangements is arranged in its top in its below and control system lid.Relevant housing bottom can be constructed as required by different way.
As load-bearing component, the transmission device 10 among Fig. 2 has essentially rectangular cover plate 14, and it determines borders by surrounding flange 15, surround flange 15 be on the plane in and be provided with the hole so that its energy spiral to housing bottom.Arranging and be supported on the bottom side of practical transmission core 17 cover plate 14, forming on three axis that are parallel to each other of isosceles triangle is the schematically illustrated transmission component of Fig. 1 (fluid pressure governor, clutch, gear and axle).The first fluid pressure governor H1 and axle W3, W5 and W6, gear Z5 and Z11 and clutch K3 and K4 are positioned on the axis.The second fluid pressure governor H2 and axle W9, W11 and W12, gear Z7 and Z9 and clutch K1 and K2 are positioned on second axis.The 3rd, central axis comprises W2, W7 and W10, planetary step change mechanism 12 and gear Z4, Z6, Z8 and Z10.
Provide be used in the bottom side of cover plate 14 upper support and to keep the critical piece of transmission device core 17 are support base 22 of being parallel to cover plate 14 orientations, from 20,21 and two on outstanding vertically downward two cross-brace posts of cover plate 14 equally from the outstanding vertically downward abutment wall of cover plate 14, only an abutment wall 23 can be seen.Support base 22 limits transmission device core 17 on the bottom side.Its bolt is to supporting post 20,21 and abutment wall 23.Being arranged on the support base 22 is the lower part of frame pivot bearings 18,19 that is used for fluid pressure governor H1 and H2, and each housing can pivot around vertical axis ( pivot 27,28 among Fig. 3).The top pivot bearings is contained in the cover plate 14 itself in the mode that can not see.The abutment wall that is parallel to each other 23 of aiming at three axis normal ground of transmission device core 17 is used for supporting the axle relevant with axis.
Especially, axle W9 and the W3 from clutch K1/K2 and K3/K4 is supported in the anterior abutment wall 23.Each is embodied as the element of construction that has hydraulic control system 24 and 25 respectively relevant bearing, and hydraulic control system is connected to the control system on the cover plate upside, and activates clutch K1 .., K4 via the axial aperture in axle W3 and the W9.The required oil pressure of hydraulic control system is produced by oil hydraulic pump 26, oil hydraulic pump 26 via downwards towards the oil groove oil suction of the root of attracting deposits (suction stub) from the dish that is formed at housing bottom, and transmit it to control system via the pipeline that is integrated into abutment wall 23.
The 3rd, on the central axis from anterior abutment wall 23 outstanding be input shaft or interior live axle W1, it is provided with spline and connects into transmission device by means of the outer driving shaft that is supported in the housing bottom thus from the power of motor.The interior driven shaft W7 that is provided with spline equally can operate by the rear support wall, and is sent to outside via described axle by means of the outer driven shaft that is supported in the housing bottom from the kinetic force of transmission device.
The necessary transmission control system of the operation of transmission device core 17 is contained on the upside of cover plate 14, and its mode is that the intervention that is brought by transmission control system 16 in the transmission device directly takes place by cover plate 14.A kind of pattern of intervening is regulator solution voltage regulator H1 and H2, and described adjusting needs pivoted maximum+/-45 ° and influence two hydraulic pressure connections between the fluid pressure governor of pivoting housing.Adjusting (pivot) for fluid pressure governor H1 and H2 provides according to regulon of the present invention, and its exemplary embodiment is shown in Fig. 3 to 7.
Being arranged between two control valve SV1, the SV2 is compensation roll (cam rollers) 42, and it is supported for and can rotates in two supporting brackets 43,44 of bolt below cover plate 29 around spin axis 41 in mode so.The spin axis 41 of compensation roll 42 extends abreast with the longitudinal axis 56,57 of control valve SV1, SV2.Compensation roll 42 is driven by motor 30 via clutch plate 53 (Fig. 6), and motor 30 is given prominence in the outside of housing 60 and controlled by the electronics or the electric control system of transmission device 10.Being arranged between motor 30 and the compensation roll 42 is urgent actuator 31 laterally projecting, that can operate from the outside, and by means of this, compensation roll 42 can manually rotate so that instant operation (if hydraulic system still works).
On its periphery, compensation roll 42 has guide rail 51,52, and adjustment (adjusting) lever 45,46 contacts with it at one (interior) end place.Another (outward) end place, adjustment (adjusting) lever engages with the top axle journal of fluid pressure governor H1, H2 via crank mechanism KT1 and KT2 (Fig. 7) respectively in all cases, and the connection between adjustment (adjusting) lever 45,46 and crank mechanism KT1, the KT2 realizes via being in the slide block 48 that moves in the fork 47 in the end of lever.Crank mechanism KT1, KT2 are the parts at the pivot plate 49,56 of fluid pressure governor H1, H2 upper process, it pivots around its pivot axis 27,28 with fluid pressure governor H1, H2, and regulating piston VK1, VK1` and VK2, the VK2` of adjusting cylinder VZ1, VZ1` and VZ2, VZ2` engage thereon respectively.
Fluid pressure governor H1, H2 do not pivot if compensation roll 42 is rotated, adjustment (adjusting) lever 45,46 pivots around the spin axis of the crank mechanism KT1, the KT2 that pass slide block 48, according to the shape of guide rail 51,52 and the valve slider 58,59 of correspondingly mobile control valve SV1, SV2.If fluid pressure governor is by pivot and not rotation of compensation roll 42, the valve slider 58,59 of control valve SV1, SV2 equally also moves.Thereby just exist the machine feedback of the pivot movement of fluid pressure governor H1, H2 to the control of adjustment process.Valve slider 58,59 by spring preload on the direction of the longitudinal axis 56,57, thereby guarantees that adjustment (adjusting) lever 45,46 does not lean against on the side of guide rail 51,52 of compensation roll 42 with having play in control valve SV1, SV2.Control valve SV1, SV2 are arranged in the symmetrical relative to each other point, only need to guarantee one type valve.
Guaranteed the operability that structure is compact, control is accurate and good according to the regulon of the embodiment of the invention.Especially, the parallel alignment of the longitudinal axis of control valve and the spin axis of compensation roll perpendicular to the straight line of the pivot axis that connects fluid pressure governor, and perpendicular to self pivot axis, has the effect of controlling mechanism for very short structure.
The reference identification tabulation:
10 transmission devices (continuous variable, hydrostatic, power branch)
11 internal combustion engines
12 planetary step change mechanisms
13 planetary carriers (planetary step change mechanism)
14 cover plates (transmission device)
15 flanges (cover plate)
16 regulons
17 transmission device cores
18,19 pivot bearings
20,21 supporting posts
22 support base
23 abutment wall
24,25 hydraulic control systems (clutch)
26 oil hydraulic pumps
27,28 pivot axis (fluid pressure governor)
29 cover plates (regulon)
30 motors (control)
31 urgent actuators (manually)
32 .., 35 hydraulic tubings (pressure distribution system)
36 pressure distribution systems
37,38 hydraulic tubings (adjusting cylinder)
39,40 control valve ports
41 spin axiss (compensation roll)
42 compensation rolls (cam rollers)
43,44 supporting brackets
45,46 adjustment (adjusting) levers
47 forks
48 slide blocks
49,56 pivot plates
50 sensor roll
51,52 guide grooves
53 clutch plate
54,55 pressure port
56,57 longitudinal axis (control valve)
58,59 valve sliders
60 housings (regulon)
H1, the H2 fluid pressure governor
K1 .., K4 clutch
KT1, the KT2 crank mechanism
SK1 .., SK4 reciprocating piston
SV1, the SV2 control valve
SW pivoting angle (%)
VK1, VK1 ' regulating piston
VK2, VK2 ' regulating piston
VZ1, VZ1 ' adjusting cylinder
VZ2, VZ2 ' adjusting cylinder
W1 .., W12 axle
Z1 .., Z12 gear
Claims (11)
1. regulon (16) that is used for the hydrostatic branch of continuous variable transmission device (10), described transmission device (10) comprises two fluid pressure governor (H1, H2), they are arranged as contiguous with a distance to each other, and each all supports so that can pivot around pivot axis (27 or 28) in mode so, it is characterized in that: regulon (16) comprises and is used to make fluid pressure governor (H1, H2) around its pivot axis (27,28) but controlling device (VZ1, the VZ1 ' of the hydraulic actuating that pivots; VZ2, VZ2 '), but be to be provided for controlling controlling device (VZ1, the VZ1 ' of hydraulic actuating; Control valve VZ2, VZ2 ') (SV1, SV2) and be used for actuator control valve (SV1, actuator (30 SV2); 42 .., 46), and control valve (SV1, SV2) and actuator (30; 42 .., 46) be arranged in these two fluid pressure governors (H1, H2) between.
2. regulon as claimed in claim 1, it is characterized in that: fluid pressure governor (H1, H2) pivot axis (27,28) aim in parallel with each other, (SV1 SV2) has the longitudinal axis (56,57) to be control valve, corresponding valve slider (58,59) can along each longitudinal axis (56,57) move so that brake control valve (SV1, SV2), be control valve (SV1, SV2) be arranged as distance of each interval so that its longitudinal axis (56,57) is parallel to each other and with fluid pressure governor (H1, pivot axis (27 H2), 28) vertically aim at, and be actuator (30; 42 .., 46) comprise adjustment (adjusting) lever (45,46), (SV1 SV2) activates by means of adjustment (adjusting) lever (45,46) control valve, and it can be in that (H1 pivots in the pivot plane that pivot axis H2) (27,28) is vertically located with fluid pressure governor.
3. regulon as claimed in claim 2 is characterized in that: actuator (30; 42 .., 46) also comprise compensation roll (42), its be arranged in control valve (SV1, SV2) between, and can around with control valve (SV1, SV2) the longitudinal axis (56,57) spin axis of aiming at abreast (41) rotates, and has the guide rail (51 of the pivot movement of the regulating and controlling of being used for lever (45,46) on compensation roll (42) periphery, 52), adjustment (adjusting) lever (45,46) contacts with one of end and guide rail (51,52) on the compensation roll (42).
4. regulon as claimed in claim 3, it is characterized in that: adjustment (adjusting) lever (45,46) is supported on the valve slider (58,59) pivotally, and by means of other ends and fluid pressure governor (H1, H2) engage, so that, as fluid pressure governor (H1, H2) around its pivot axis (27, when 28) pivoting, adjustment (adjusting) lever (45,46) pivots in its pivot plane in a predetermined manner.
5. regulon as claimed in claim 4 is characterized in that: adjustment (adjusting) lever (45,46) and fluid pressure governor (H1, the H2) connection between, comprise in all cases can around the crank mechanism of pivot axis (28,29) rotation (KT1, KT2).
6. regulon as claimed in claim 3 is characterized in that: compensation roll (42) is driven by motor (30).
7. regulon as claimed in claim 6 is characterized in that: be arranged in the urgent actuator (31) between motor (30) and the compensation roll (42), be provided for the manual rotation of compensation roll (42).
8. regulon as claimed in claim 1 is characterized in that: be used for each fluid pressure governor (H1, but the controlling device of hydraulic actuating H2) comprises that at least one regulates cylinder (VZ1, VZ1 '; VZ2, VZ2 '), it is by means of regulating piston (VK1, VK1 '; VK2, VK2 ') (H1, on pivot rotaring lever H2) (49,50), pivot rotaring lever (49,50) pivots around pivot axis (27,28) to be engaged in fluid pressure governor.
9. regulon as claimed in claim 8 is characterized in that: provide two to regulate cylinder (VZ1, VZ1 '; VZ2, VZ2 ') act on each fluid pressure governor in an opposite direction, described cylinder preferably is engaged on the identical pivot rotaring lever (49,50).
10. regulon as claimed in claim 1 is characterized in that: but be used to control controlling device (VZ1, the VZ1 ' of hydraulic actuating; Control valve VZ2, VZ2 ') (SV1, SV2) and be used for actuator control valve (SV1, actuator (30 SV2); 42, .., 46) be contained in the housing (60) of the upward opening that can use cover plate (29) sealing, be control valve (SV1, SV2) and selected actuator (42, .., 46) be installed on the bottom side of cover plate (29), and be control valve (SV1, SV2) by being integrated into cover plate (29) and having hydraulic tubing (32 separately, .., pressure distribution system (36) 36) but be connected to controlling device (VZ1, the VZ1 ' of hydraulic actuating; VZ2, VZ2 ').
11. regulon as claimed in claim 1 is characterized in that: (H1 H2) is operating as pump or motor to fluid pressure governor alternatively, and is that its range of pivot is in all cases at least+/-45 °.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008008234.1 | 2008-02-08 | ||
| 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 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101939567A true CN101939567A (en) | 2011-01-05 |
Family
ID=40560307
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008801263219A Pending CN101939567A (en) | 2008-02-08 | 2008-12-05 | Adjusting unit for a continuously variable hydrostatically branched transmission |
Country Status (11)
| Country | Link |
|---|---|
| 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) |
| MX (1) | MX2010008520A (en) |
| WO (1) | WO2009097700A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194584A (en) * | 2015-05-27 | 2016-12-07 | 罗伯特·博世有限公司 | Hydrostatic linear actuator and there is the device of hydrostatic linear actuator |
Families Citing this family (3)
| 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 |
| 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 |
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| 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 |
| DE3912386C2 (en) | 1989-04-14 | 1993-10-28 | Man Nutzfahrzeuge Ag | Infinitely variable hydrostatic-mechanical power split transmission |
| DE3912369C2 (en) | 1989-04-14 | 1996-02-22 | Man Nutzfahrzeuge Ag | Stepless 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 |
| WO2006042434A1 (en) * | 2004-10-20 | 2006-04-27 | Markus Liebherr International Ag | Power-branched transmission and method for the operation of such a transmission |
-
2008
- 2008-02-08 DE DE200810008234 patent/DE102008008234A1/en not_active Withdrawn
- 2008-12-05 KR KR1020107019936A patent/KR20110007098A/en not_active Application Discontinuation
- 2008-12-05 WO PCT/CH2008/000520 patent/WO2009097700A1/en active Application Filing
- 2008-12-05 BR BRPI0822293-2A patent/BRPI0822293A2/en not_active IP Right Cessation
- 2008-12-05 CA CA2711954A patent/CA2711954A1/en not_active Abandoned
- 2008-12-05 AU AU2008350228A patent/AU2008350228A1/en not_active Abandoned
- 2008-12-05 CN CN2008801263219A patent/CN101939567A/en active Pending
- 2008-12-05 EA EA201070938A patent/EA201070938A1/en unknown
- 2008-12-05 MX MX2010008520A patent/MX2010008520A/en not_active Application Discontinuation
- 2008-12-05 EP EP08872255A patent/EP2250404A1/en not_active Withdrawn
- 2008-12-05 JP JP2010545339A patent/JP2011512493A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194584A (en) * | 2015-05-27 | 2016-12-07 | 罗伯特·博世有限公司 | Hydrostatic linear actuator and there is the device of hydrostatic linear actuator |
| CN106194584B (en) * | 2015-05-27 | 2020-03-17 | 罗伯特·博世有限公司 | Hydrostatic linear actuator and device having a hydrostatic linear actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| EA201070938A1 (en) | 2011-02-28 |
| EP2250404A1 (en) | 2010-11-17 |
| CA2711954A1 (en) | 2009-08-13 |
| DE102008008234A1 (en) | 2009-08-13 |
| BRPI0822293A2 (en) | 2015-06-30 |
| AU2008350228A1 (en) | 2009-08-13 |
| KR20110007098A (en) | 2011-01-21 |
| WO2009097700A1 (en) | 2009-08-13 |
| MX2010008520A (en) | 2010-10-25 |
| JP2011512493A (en) | 2011-04-21 |
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Legal Events
| Date | Code | Title | Description |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Open date: 20110105 |