• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A stepless hydrostatic transmission (10) with power distribution for a vehicle, comprising a first hydrostat (H1) acting as a pump and a second hydrostat (H2) acting as an engine, as well as a planetary gear (12), a first shaft (W1) arranged on the drive side and a summing means (W6), the power abutting on the first shaft (W1) being divided via the planetary gear unit (12) into a mechanical transmission branch (Z9, W2, Z1, Z2) and a hydrostat (H1, H2) connected by the two hydraulically ) formed hydraulic transmission branch (Z7, W3, Z4, Z5, Z6, H1, H2) and reassembled at the summing means (W6). In such a transmission, a compact and simplified construction is achieved and a great flexibility in use, so that the power transfer between the first shaft (W1) and the summing means (W6) is controllable exclusively by a change in the stroke volumes of the hydrostats (H1, H2).
    公开号:SE1150793A1
    申请号:SE1150793
    申请日:2010-01-25
    公开日:2011-09-01
    发明作者:Markus Liebherr；Peter Dziuba；Josef Haeglsperger
    申请人:Mali Holding Ag；
    IPC主号:
    专利说明:

    15 20 25 30 0 The transmission must have a high efficiency over the entire speed range. This should be especially the case at high driving speeds, which occurs over a longer period of time in street traffic. 0 The transmission must be compact in order to enable installation in the most varied vehicles, if possible without design restrictions. 0 The transmission shall enable full electronic control in connection with engine management, and in the event of the absence of certain control elements, make sufficient emergency operation programs available. 0 The transmission must enable the transmission of high powers 0 The transmission must for limiting power losses and. increase 'of functional safety. be. so simple. built up as possible.
    The above-mentioned DE-Al-43 43 402 has already described a power transmission (in German called SHL-Getriebe (ëtufenloses äydrostatisches ëeistungs- verzweigungsgetriebe)), which is characterized by two hydraulically coupled similar oblique shaft type hydrostats, which via The known SHL transmission has been used and tested in city buses under The two hydrostats used have a type of rotation SHL-Z. O-25 ° For forward travel, driving modes or driving ranges are achieved In the first driving range, at the starting point, the hydrostatic proportion of the transmitted power is 100% zero and then decreases linearly with the speed towards In the second driving range it moves from zero to a maxi- In the mum of about 27% and then back again to zero.
    H: DOCWORK Applicationtext.d0ox, 2011-08-31 110036EN 10 15 20 25 30 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 one of which acts as a pump and the other as a motor. Depending on the driving position, the two machines can then change their roles.
    The hydrostatic axial piston machine 'constitutes * an essential' component of the hydrostatic power-splitting transmission and characterizes the characteristics of the transmission such as e.g. efficiency, design size, complexity, the covered speed range, type and number of driving modes and the like. described in DE-A1-198 33 711 or DE-A1-100 44 784 or US-Al-2004/0173089.
    Examples of such hydrostatic axial piston machines are Functions and theories for hydrostatic axial piston machines as well. one thus. equipped power-divided tractor transmission is described in a publication at the Technical University of Munich in 2000 by H. Bork et al., entitled “Model formation, simulation and analysis of a stepless performance-enhanced tractor assembly”.
    Finally through. WO-A1-2006 / 042434 discloses a stepless hydrostatic power splitting transmission operating with two large angle hydrostats with a range of up to 500. The total speed range of the transmission is divided into two sections, in which the two hydrostats. switches its functions as pump and motor. For switching between the two sections, two double couplings are provided, with which the hydrostats are connected in different ways to the power-dividing planetary drive. With this transmission, a large speed range can be covered steplessly during a simultaneously high-efficiency H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30 degree. However, it is quite large, as space is needed for the switchable connections with. the double couplings.
    It is therefore an object of the invention to provide a comparable transmission which is particularly compactly built, which is characterized by a simplified construction and which can be modularly adapted to different requirements of the vehicle, and also to provide a method for its operation. The object of the invention is achieved in its entirety with the features of claims 1 and 16. The transmission according to the invention comprises * one which. pump-operating first hydrostat and a motor-operating second hydrostat, as well as a planetary gear, a first shaft on the driving side and a summing member, the power acting on the first shaft via the planetary gear being divided into a mechanical transmission branch and a hydraulically coupled the hydrostats formed hydraulic transmission branch and reunited to the summing means. It is characterized in that the power transfer between the first shaft and the summing means is controllable exclusively by a change in the stroke volumes of the hydrostats.
    A first embodiment of the invention is characterized in that the stroke volumes of the two hydrostats are changeable by an oscillation process, and that the two hydrostates are designed as large-angle hydrostats with an oscillation range of at least about 450. As a result, a speed range of about 50 km / h can be realized.
    Preferably, the second hydrostat is pivotable at least on one side by at least about 450 and on the other hand by at least about 300. This easily facilitates a stepless reverse travel.
    H: DOCWORK Ansökstext.d0ox, 2011-08-31 110036EN 10 15 20 25 30 Suitably the hydrostats are designed as axial piston oblique shaft hydrostats.
    Another the second hydrostat has a significantly larger stroke volume than the first hydrostat. A particularly high traction force of the vehicle can be achieved in that the maximum displacement of the other hydrostat is approximately twice the maximum displacement. in the first hydrostat. In particular, * the maximum stroke volume of the first. the hydrostat to about 160 cm3.
    According to another embodiment of the invention, the summing means is a summing axis.
    Yet another embodiment of the invention is characterized in that the hydrostats are arranged parallel to each other and to the first axis. In particular, the two hydrostats, in relation to the direction of the first axis, can be arranged next to each other, preferably in a horizontal plane.
    However, it is also conceivable that the two hydrostats, in relation to the direction of the first axis, are arranged coaxially one after the other and mutually mirror-image-like, so that the planetary gear. is arranged. in the axial direction 'before the two hydrostates and. the summing means in the axial direction after the two hydrostats, and that the planetary gear and the summing means are operatively connected by an axis extending above the two hydrostates in the axial direction. This special arrangement makes it possible, especially during use. of the transmission in snow. traction vehicle, to realize a low-lying cab floor, which between the planetary gear and the summing means slides down to near the axis between the planetary gearbox and the summing means. H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30
    Another embodiment of the invention is characterized in that the planetary gear comprises a central sun gear and a sun wheel concentric surrounding ring gear as well as between both arranged planetary wheels rotatably mounted on a planet carrier, so that the planet carrier is rotatably connected to a first shaft, and that the ring gear is in effective communication with the first hydrostat, and that the sun gear is in effective communication with the second hydrostat.
    According to a further embodiment, the first shaft extends through the planetary gear and is designed as a socket shaft on the side opposite the drive.
    According to another embodiment of the invention, the summing means is in operative connection with a second shaft for the drive and / or rear shaft, the ring. of forward- thereby. especially the drive of the front axle can be connected via a coupling.
    The method according to the invention for driving the transmission is characterized in that in order to realize a stepless forward travel area, before the start, the stroke volume of the first and first hydrostat is set to zero, the stroke volume of the second hydrostat at a maximum, and in a first phase the stroke volume of the the second hydrostat at maximum while the stroke volume of the first hydrostat is increased in the forward direction until it reaches its maximum in the forward direction, and that in a second phase the stroke volume of the first hydrostat is kept at the maximum while the stroke volume of the second hydrostat is reduced from maximum to zero.
    H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30 An embodiment of the method according to the invention is characterized in that in order to realize a stepless reverse travel area, the stroke volume of the first hydrostat is first set to zero. and the stroke volume of the second hydrostat at maximum, and that in a first phase the stroke volume of the second hydrostat is kept at maximum while the stroke volume of the first hydrostat is increased in that reverse direction until it reaches its maximum in reverse direction, and that in a second phase the stroke volume of the first hydrostat at maximum while the stroke volume of the second hydrostat is lowered from maximum to zero.
    The invention will be explained in more detail below with the aid of exemplary embodiments in connection with the drawing. There, Fig. 1 shows the principle diagram for a stepless transmission with power division according to a first embodiment of the invention, to (c) Fig. 2 in several sub-figures (a) the conversion of the hydrostats over the forward travel area of the transmission according to Fig. 1, Figs. 3 in several sub-figures (a) to (c) the conversion of the hydrostats over the reverse travel area of the transmission according to Fig. 1, Fig. 4 the curves for traction (ZK), efficiency (n) and the hydrostatic power ratio (HL) for the transmission according to Fig. Fig. 5 shows the velocity of a first magnitude of the hydrostats, Fig. 5 the curves for the * traction (ZK), the efficiency (n) and the hydrostatic power ratio (HL) of the transmission according to Fig. Fig. 6 in several views a first complete transmission of the type shown in Fig. 1, Fig. 7 in several views a second complete transmission of the type shown in Fig. 1, Fig. 7a the internal structure of the transmission. in Fig. 7 in exploded perspective view, Fig. 7b the exemplary structure of the hydrostat H2 connected to the shaft W6 in Fig. 7a, Fig. 8 the principle diagram for a stepless hydrostatic transmission with power division 'for small H: DOCWORK Application text .docx, 2011-08-31 110036EN 10 15 20 25 30 towed vehicle with lowered cab floor according to a second preferred embodiment of the invention, and Fig. 9 the principle diagram for a stepless hydrostatic transmission with power division for small towing vehicles with lowered cab floor according to Fig. 8 in module - your execution.
    Fig. 1 shows the principle diagram for a stepless hydrostatic transmission with power division according to a first preferred embodiment of the invention. The transmission 10 transmits the power from an internal combustion engine 11, which is symbolically shown in the form of a piston, to a shaft W7 which, as the driving input shaft, leads the power to the rear axle and / or front axle of a vehicle. The transmission comprises two power branches, namely a mechanical power branch and a hydraulic power branch.
    The power applied at the entrance is divided depending on the driving style in different ways to the two branches, whereby the mechanical branch is unchangeable and the hydrostatic branch can be changed.
    Essential parts of the transmission 10 are a planetary gear 12 with. central sun gear Z9, rotating planet gear Z8 and a concentric planet gear Z8 enclosing ring gear Z7, a first large angle hydrostat H1 having a turning range of about 450 and a negative turning area of about 30 °, a second large angle hydrostat H2 having a one-sided turning range of about 450, to which the effects and a summing axis W6, from the two branches are reunited. The two hydrostats H1 and H2 are to the left and to the right of a first axis W1 with its axes of rotation arranged parallel to this axis. The first shaft W1, as the driving input shaft, engages the power from the internal combustion engine 11 in the transmission 10. It extends through the planetary gear l2 and is available as an output shaft W5 on the other side of the transmission for the drive of external units.
    H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30 On the first shaft W1 there is a planet holder 13 which rotates the planet gears Z8. The central sun gear Z9 is rotatably connected via a first hollow shaft W2 to a gear Z1, which via a first intermediate gear Z2 transmits the rotation to a gear Z3 on the summing shaft W6. The summing shaft W6 is directly connected to the other hydrostat H2. The ring gear Z7 is connected via a second hollow shaft W3 in a rotationally fixed manner to a gear wheel Z4, which via a second intermediate gear wheel Z5 transmits the rotation to a gear wheel Z6 on the shaft W4. The shaft W4 is directly connected to the first hydrostat H1. The two hydrostats H1 and H2 are - which is not shown in the drawing - hydraulically connected to each other, so that the hydraulic fluid pumped by the son1 pump operating the first hydrostat H1 comes to the motor and the second hydrostat H2 operating as motor.
    In the planetary gear 12, the power connected to the transmission 10 is divided: the mechanical power branch is formed by the sun gear Z9, the first hollow shaft W2 and the gears Z1, Z2 and Z3. The hydraulic power branch is formed by the ring gear Z7, the second hollow shaft W3, the gears Z4, Z5 and Z6 and the two hydraulically connected hydrostats H1 and H2. The power of the two branches summed on the summing shaft W6 is transmitted via the gear drive to the driven shaft W7.
    With the transmission 10 according to Fig. 1, a stepless forward travel area and a stepless reverse travel area can be realized. The associated adjustments of the hydrostats are shown in Fig. 2 (forward travel range or step V) both and Fig. 3 (reverse travel range or step R). In the cases, the driving area begins with that in Fig. 2a) resp. Fig. 3a) showed the still state, in which the first hydrostat H1 is unsteady and thus. shows a disappearing stroke volume while the other H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30 10 The hydrostat H2 is fully flared (with approximately 450) and has the maximum stroke volume. To start, turn when driving forward (Fig. 2) to the upper side corresponding to the forward movement, whereby the vehicle picks up speed. The maximum oscillation of the second hydrostat H2 thereby ensures a high torque (high tensile force) at a low rotational speed. If the first hydrostat H1 is fully swung out (Fig. 2b), it is kept there and the second hydrostat H2 is swung back inwards (Fig. 2c) to the zero position (disappearing stroke volume). The decreasing stroke volume in the second hydrostat H2 ensures an ever-increasing rotational speed with decreasing torque. In Fig. 4, for a transmission according to Fig. 2 according to Fig. 2, the traction force ZK, the hydrostatic power ratio HL at the transmission and the efficiency n of the transmission over the speed v are plotted. The exemplary transmission transmits a power of 90 kW. The vehicle reaches a speed of 50 km / h at a speed of the internal combustion engine ll of 2200 rpm. The pumping hydrostat H1 then has a maximum stroke volume of 160 cmê, the motor-operated hydrostat H2 has a maximum stroke volume of 233 cmê. It can be seen that the efficiency in the important driving range of 5 to 50 km / h is clearly above 80% and at. low speeds a maximum traction ZK of over 60kN is achieved. The proportion of the hydraulic power branch. at. the power transmission then decreases. from 10% at. stationary linear to 0% km / h. at. an velocity of 40 An even higher maximum tensile force ZK of more than 80 kN can be achieved under otherwise equal conditions according to Fig. 5 when the second hydrostat H2 has an even larger maximum displacement of 325 cm the volume of the first hydrostat Hl.
    When reversing according to Fig. 3, start from the same stationary configuration (Fig. 3a) as when driving forward. The first H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30 ll the hydrostat H1 is, however, swung for start in the opposite direction, until it has reached '3b). its maximum oscillation (in the example of 300) (Fig. The fully flared second hydrostat H2 is then swung back to the zero position (Fig. 3c).
    In Fig. 6 different views of a complete transmission 10 'with the basic structure according to Fig. 1 are depicted. The transmission 10 'is mounted in a housing 14, from which the driving shaft. W1 protrudes' forward and. the driven shaft W7 forwards and backwards. The two hydrostats H1 and H2 are arranged lying on both sides of the driven shaft W7, and pivotable in an area visible as bulges 21 in the housing 14. On the upper side of the housing 14 is a switching unit 15 with two pairs of opposite hydraulic cylinders 16, 17 and 18, 19, through which the hydrostats H1, H2 pivotable about a vertical pivot axis can be adjusted. The hydraulic adjustment is controlled by a control unit 20, which is arranged next to the adjustment unit 15.
    Due to the simple and compact construction of the transmission according to the invention, it is possible to also arrange the driven one. axeln. W7 in another position to adjust. to different needs of the different vehicles. Fig. 7 shows a transmission 10 ”in which the driving shaft W1 on the rear side is designed as an outlet shaft W5 with built-in side drive 22, and in which the driven shaft W7 for driving the rear and front axles is displaced considerably downwards. If necessary, however, this shaft can also be displaced to the side.
    The internal structure of the transmission. 10 ”according to Fig. 7 is shown in an exploded perspective view in Fig. 7a. The housing 14 is here slightly changed in relation to Fig. 7. In a central block, the planetary gear 12 and the two horizontally pivotable rotary axes 27 and 28 are hydrostats H1 and H2 H: DOCWORK Application text.d0ox, 2011-08- 31 110036EN 10 15 20 25 30 l2 as well as additional transmission parts arranged. The pairs of co-operating pistons 29 of the hydraulic cylinders 16, 19, 19 of the conversion unit 15, which are in effective connection with the pivot shafts 27 and 28 via a rake arm, can also be seen on the outside at the side drive, the electronic guide 26 arranged in a square housing, in which the signals from the different food care sensors distributed in the transmission for temperature, pressure and temperature converge.
    The hydrostat H2 illustrated in Fig. 7b comprises a one-piece swing housing 31 in which the cylinder block 34 with the pistons slidably arranged therein is rotatably mounted. At the swing housing 3l, bearing pins 32 and at the bottom are formed. 33. The upper bearing pin. 32 also contains inlet and outlet openings for high-pressure ducts, which extend inside the hinge housing 31 between the upper bearing pin 32 and the bearing surface of the cylinder block 34 formed in the interior of the housing housing 31. The pistons 35 are versatile in a pivotal bearing 36 which merges with the shaft W6 .
    A special design of the transmission according to the invention enables the use in, for example, small towing vehicles with a lower cab floor. A corresponding transmission scheme is shown in Fig. 8. The transmission. Fig. 8 shows the general arrangement of the two hydrostats H1 and H2 in the axial direction one after the other and in a mirror image-like manner. The cylinder blocks of the hydrostats H1 and H2 are then opposite each other. The planetary gear l2 and the summing shaft W6 are in the axial direction far inwardly drawn. The one who. the shaft axis W2 extends from the sun gear Z9 to the summing axis, W6 above the two hydrostats H1 and H2 past the hydrostats H1, H2 and backwards and via the gears Z10 and Z11 coupled to the summing axis W6. Thereby space is gained at the top for a lowered cab. floor 23, as indicated in Fig. 8 by a dotted line.
    H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 25 30 l3 The rear axle 24 is in this case driven by the summing shaft W6 via a gear drive. Genonl hollow shaft. W2, the drive shaft W1 is guided backwards and can, via a first clutch K2 and a two-speed gearbox 25, if necessary drive a socket shaft WIO. A shaft W9 for a clutchable front-wheel drive is connected via a second clutch and the pair of gears Z11, ZI2 also to the summing shaft W6.
    Fig. 9 shows the modular basic form of the transmission in Fig. 8. The transmission 30 'makes with the axes W2, W6 and W9 three alternative possibilities available for the drive, which in Fig. 9 are shown by arrows and the Roman numerals I, II and III. The drive shaft W1 guided through the hollow shaft W2 can at the other end again also be used as a socket shaft. The shaft W9 extending to the left is used for driving the front axle at. an all-wheel drive. It appears that a transmission. with this transmission structure can be flexibly adapted to the most varied cases of use, takes up little space and can be used to advantage especially for narrow small towing vehicles with low-lying cab floors, finds such as. for example, use in vineyards.
    A simple planetary gearbox functions as a power-sharing transmission and is thereby regarded as an optimal solution for the basic construction. The hydrostatic power range with large-angle technology and turning ranges of +/- 450 in terms of efficiency and oscillation are considered to be the best system. If you use this basic mechanical structure and combine it with the large-angle technology and, if necessary, supplement it with a socket shaft and all-wheel drive, you achieve an affordable transmission concept that can be right for many vehicle uses.
    Overall, the transmission according to the invention is characterized by the following characteristic features and advantages: H: DOCWORK Application text.d0ox, 2011-08-31 110036EN 10 15 20 l4 Modular principle Hydrostatic power division Simple planetary gear for power division One driving range forwards and one rear 2 large angle hydrostats with + -450 swivel angle Stepless power transmission in the entire operating range High overall efficiency without declines Full hydrostatic power only necessary at start-up Always full traction available at start-up No travel coupling necessary, function available Speed up to 50 km / h nblig ü_ special case up to 65 km / h) Lower speeds possible with reduced speed Outgoing speed adjustable between 0 and ß4000 rpm Torque spread input to output l to 25.9 Different driving strategies possible Control via changeover unit In case of disturbance of electrical system or electronics it is possible to continue working with mechanical emergency function H: DOCWORK Application text. d0ox, 2011-08-31 110036SE
    权利要求:
    Claims (17)
    [1]
    A stepless hydrostatic transmission with power distribution for a vehicle, which transmission 10 ', 10 "; 30, 30') comprises a first hydrostat (H1) acting as a pump and a second hydrostat (H2) operating as a motor, as well as a planetary gear ( 12), a first axis (W1) on (W6), the on the (12) (Z9, W2, Z1, Z2 input side and a summing member first axis (W1) abutting the power via the planetary gear being divided on a mechanical transmission branch Z10) a genon1 the two hydraulically connected hyd- (Z7, respectively and the rostats (H1, H2) formed hydraulic transmission branch W3, Z4, Z5, Z6, H1, H2 respectively Z7, W3, Z4, Z6, H1, H2) And reunited at the summing means (W6), characterized in that the power transfer between the first shaft (W1) and the summing means (W6) is controllable exclusively by a change in the stroke volumes of the hydrostats (H1, H2).
    [2]
    Stepless hydrostatic transmission according to claim 1, characterized in that the displacement volumes of the two hydrostates (H1, H2) are changeable by a pivotal movement, and that the two hydrostates (H1, H2) are designed as large-angle hydrostats with a pivot range of at least about 450. claim 2, (H2)
    [3]
    Stepless hydrostatic transmission according to characterized in that the second hydrostat is pivotable at least on one side by at least about 450, and that the first hydrostat (H1) is pivotable on one side by at least about 450 and on the other side by at least about 300 H: DOCWORK Ansökstext.d0ox, 2011-08-31 110036SE 10 15 20 25 30 l6
    [4]
    A stepless hydrostatic transmission according to claim 2 or 3, characterized in that the hydrostats (H1, H2) are designed as axial piston oblique shaft hydrostats. transmission requirement 4, (H2)
    [5]
    5. Stepless hydrostatic according to k a n n e t e c k n a d in that the second hydrostat has a significantly larger maximum stroke volume than the first hydrostat (H1).
    [6]
    The stepless hydrostatic transmission according to claim 5, characterized in that the maximum stroke volume of (H2) is approximately twice as large as that of (H1). the second hydrostat maximum stroke volume of the first hydrostat
    [7]
    A stepless hydrostatic transmission according to claim 5 or 6, characterized in that the maximum displacement of the first hydrostat (H1) is approximately 160 cm 3.
    [8]
    A stepless hydrostatic transmission according to any one of the claims characterized in that the summing means is (W6). to 7, a summing axis
    [9]
    Stepless hydrostatic transmission according to one of Claims 1 to 8, characterized in that the hydrostats (H1, H2) are arranged parallel to one another and to the first axis (W1). lO. Stepless hydrostatic transmission according to claim 9, characterized in that the two hydrostats (H1, H2), in relation to the direction of the first axis (W1), are arranged next to each other, preferably in a horizontal plane. H: DOCWORK Ansökstext.d0ox, 2011-08-31 110036SE
    [10]
    10. 15 20 25 30 17
    [11]
    Stepless hydrostatic transmission according to claim 9, characterized in that the two hydrostats (H1, H2), in relation to the direction of the first axis (W1), are arranged coaxially one after the other and mutually mirror image-like, that the planetary axis (12) is arranged in the axial direction before the two hydrostats (H1, H2) and the summing means (W6) in the axial direction after the two hydrostats (H1, H2), and that the planetary shaft (12) and the summing means (W6) are in operative connection through an axis (W2) extending in the axial direction above the two hydrostats (H1, H2).
    [12]
    The stepless hydrostatic transmission according to any one of claims 1 to 11, (12) (Z9) may be a sun gear (Z9) (Z7) (13) (13) in that the planetary gear comprises a central and a sun wheel concentrically surrounding the ring gear as well as between both arranged, wheels (Z8), at a planet carrier rotatably mounted planets rotatably connected to (Z7) (H1) that the planet carrier the first shaft (W1), that the ring gear is in effective communication with the first hydrostat (Z9) (H2). and that the sun wheel is in 'effective. connection with. the other hydrostat
    [13]
    A stepless hydrostatic transmission according to any one of claims 1 to 12, (W1) in that the first shaft (12) extends through the planetary gear and is on the opposite side of the drive designed as a socket shaft (W5).
    [14]
    A stepless hydrostatic transmission according to any one of claims 1 to 13, (W6) characterized in that the summing means is in operative connection with a second shaft (W7, W9) for driving the rear and / or front axle. H: DOCWORK Ansökstext.d0ox, 2011-08-31 110036SE 10 15 20 25 18
    [15]
    A stepless hydrostatic transmission according to claim 14, characterized in that the drive of the front axle can be switched on by means of a coupling (K1).
    [16]
    Method for driving a stepless hydrostatic transmission according to one of Claims 1 to 15, characterized in that, in order to realize a stepless forward travel range, the stroke volume of the first hydrostat (H1) is first set to zero and the stroke volume of the second hydrostat (H2) at maximum, that in a first phase the stroke volume of the second hydrostat (H2) is kept at maximum and the stroke volume of the first hydrostat (H1) is increased in the forward travel direction until it reaches its maximum in forward travel and that in a second phase the stroke volume of the first hydrostat (H1) (H2) is kept in the direction of direction, at maximum and the stroke volume of the second hydrostat is reduced from maximum to zero.
    [17]
    Method according to claim 16, characterized in that in order to realize a stepless reverse travel area, the stroke volume of the first hydrostat (H2) (H1) is first set to zero and the stroke volume of the second hydrostat to a maximum, that in a first phase it is kept the stroke volume of the second hydrostat (H2) at Haximum and the stroke volume of the first hydrostat (H1) increase in the reverse direction until it reaches its maximum in the reverse direction, and in a second phase the stroke volume of the first hydrostat (H1) is kept at maximum1 and the stroke volume of the second hydrostat (H2) is reduced from maximum to zero. H: DOCWORK Ansökstext.d0ox, 2011-08-31 110036SE
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    同族专利:
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    JP2012517572A|2012-08-02|
    DE112010000699A5|2012-11-08|
    CH700414A1|2010-08-13|
    US8915813B2|2014-12-23|
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    WO2010091778A1|2010-08-19|
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    法律状态:
    2015-03-31| NAV| Patent application has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    CH00211/09A|CH700414A1|2009-02-12|2009-02-12|A continuously variable hydrostatic transmission with power branching and method for its operation.|
    PCT/EP2010/000404|WO2010091778A1|2009-02-12|2010-01-25|Continuously variable hydrostatic transmission having torque division|
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