WO2009037151A1 - Entraînement hydraulique - Google Patents

Entraînement hydraulique Download PDF

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Publication number
WO2009037151A1
WO2009037151A1 PCT/EP2008/061918 EP2008061918W WO2009037151A1 WO 2009037151 A1 WO2009037151 A1 WO 2009037151A1 EP 2008061918 W EP2008061918 W EP 2008061918W WO 2009037151 A1 WO2009037151 A1 WO 2009037151A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
pressure medium
drive according
piston
hydraulic drive
Prior art date
Application number
PCT/EP2008/061918
Other languages
German (de)
English (en)
Inventor
Stefan Matuzic
Original Assignee
Stefan Matuzic
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 Stefan Matuzic filed Critical Stefan Matuzic
Publication of WO2009037151A1 publication Critical patent/WO2009037151A1/fr

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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M19/00—Transmissions characterised by use of non-mechanical gearing, e.g. fluid gearing
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft

Definitions

  • the invention relates to a hydraulic drive, in particular for driving a muscle-powered vehicle, electric or alternative types of drive having a hydraulic pumping means for providing a hydraulic pressure fluid flow and at least one hydraulic motor, wherein the hydraulic pumping means and the hydraulic motor via at least one Pressure medium line are connected to each other and the hydraulic pumping means comprises at least two cylinders and at least two radially movable piston therein.
  • chain drives can be used for vehicles such as bicycles or other vehicles driven either by muscle power or by a motor.
  • Such chain drives with a variety of chainrings and arranged in a cassette sprockets are adjustable to fixed switching stages, so that a continuous conversion of the torque can not be done, which is not feasible, for example, with a planetary gear in the rear hub. Also, only with the bottom bracket fixedly spaced rear wheel can be driven via a chain drive, as a transmission of a rotary motion on a hinged front not is feasible. To maintain the necessary chain tension chain tensioning devices must be used for the corresponding chain tension in different gear pairs, which are also prone to failure and maintenance.
  • An-drive device known which comprises a rotatably driven by means of a pedal drive hydraulic pump and the rear wheel of the bicycle, in turn, by the funded by the hydraulic pump pressure medium flow rotatably drivable hydraulic motor.
  • the pump is designed as an axial piston pump which comprises at least eight pump elements, wherein each pump element operates within one revolution of the pump rotor at least three times in the delivery mode. It is provided as a valve control device switching stage selector means by means of which, with the exception of a permanently exploited in the pump operation, the other pump elements are switched individually or to several in increasing or decreasing number in the circulation mode. With this arrangement of eight pump elements, which are individually switched on and off, the switching stages are stepped against each other and thus Fixed in the transmission ratio of speed and displacement of the pressure medium.
  • a stepless selection of the speed of the pedal drive at the same delivery volume or a continuously selectable delivery volume at a constant speed with the arrangement disclosed herein is not given. Rather, the disclosed device is limited to predetermined transmission levels between speed and displacement and thus the torque or the vehicle speed.
  • a hydraulic drive unit wherein the hydraulic pumping means is designed as Zweiringaxialkolbenpumpe.
  • the hydraulic pumping means is designed as Zweiringaxialkolbenpumpe.
  • the unavoidable oscillation of this Zweiringaxialkolbenpumpe following disadvantages brings:
  • the piston reversal points are standstill points.
  • the three to the stroke adjustment radially adjustable roller bearing rollers cause energy losses with increasing speed, as these spinning rollers must perform permanently changing rotational movement.
  • optimal efficiency is given only at low speeds. Also the manufacturing costs are to be estimated in comparison to high.
  • the hydraulic pumping means is designed as a radial compound piston pump, wherein the stroke length of the piston pair via a radially adjustable adjusting bearing, which is formed as Wälzoder ball bearings, is adjustable to regulate the hydraulic pressure fluid flow continuously.
  • the designed as Radialverbundkolbenpumpe pump means has an extremely compact design, which offers a minimum space and high weight-specific power throughput.
  • the piston and cylinder assembly are in pairs, with all pairs of pistons produce a common flow. Thus, a space limited by a housing space can be optimally utilized. Due to the paired design of the piston assembly of the adjustment and thus the piston stroke is structurally fixed and the adjustment for both sides of the piston pairs has an equal amount.
  • the radial adjustment of the adjustment of the hydraulic pumping means by the adjusting is variable in its radial position by means of a hydraulic piston from the crankshaft ago.
  • the adjusting bearing can advantageously be designed so that this can be offset in eccentric position due to its radial adjustability and with increasing offset drives the piston radially outward.
  • the piston pairs are firmly connected to each other with a ring pair, pumping the pressure medium on the one hand and suck on the other hand, the pressure medium.
  • the connecting rings ensure a precise distance, which creates a free play between the respective suction piston and adjusting bearing. Furthermore, a uniform suction power is ensured even at high speeds.
  • This solution is more advantageous over a spring bias of the piston, since friction between the piston and the adjusting bearing is avoided, and at higher speeds compared to a spring solution, ensures continuous suction.
  • the connecting rings are structurally designed so that they can not touch and the crankshaft can rotate without contact in any adjustment.
  • the adjustment and thus the piston stroke have an immediate effect on the delivery volume, torque and transmission ratio.
  • the displacement of the pressure medium can be adjusted continuously, without a switching operation assumes fixed predetermined switching stages.
  • the adjustment which is determined constructively in the design of the adjustment bearing with respect to the diameter and the radial displacement can be easily adapted in the application of the bicycle to the ergonomic and thus physiological needs of the user.
  • the difference of the extreme gear ratios can thus be determined or even changed and adjusted by an exchange of the adjustment.
  • the change in the radial position of the adjusting bearing is vorappelbar via an actuatable outside the hydraulic pumping cable, which by means of a external small cylinder / piston device performs the hydraulic adjustment.
  • the extremely compact adjustment mechanism consists of the following components, starting from the cable end: A cylinder / piston device mounted externally on the pump housing, which presses the pressure medium through the pressure medium line arranged radially in the cylinder block.
  • the pressure medium line discharges into a pressure medium coupling which is sealed on the crankshaft with two sets of rotor seals and guides the pressure medium through the hollow crankshaft to the adjusting bearing piston, which drives the adjusting bearing into the eccentric position.
  • the return adjustment is done without pressure and automatically, because the adjusting bearing by pressure resistance of the piston tends automatically to the central position. An adjustability is easily possible under load. Alternatively, a stepped adjustment on the handlebar is also feasible, in which case only realistic gears arise.
  • crankshaft not only fulfills the very own role, but is responsible as an additional pressure medium flow function and as a cylinder body for the stepless adjustment and freewheel device.
  • the freewheel is also solved hydraulically according to the invention. This sits on the crankshaft, consisting of main body (freewheel ring), two moving pistons, two Nockenschnappern rotatable on two cylinder pins and two leaf springs for each Nockenschnapper. In the cylinder block a toothing is incorporated, which is responsible for the conversion of the two Nockenschnapper in return or pre-emergence.
  • the adjusting pistons are in the retracted position, the cams at the maximum point, and the adjustment of the adjusting bearing is ready for propulsion.
  • the cam latches tip over, the adjusting cylinders extend and the adjusting bearing is forced to the center to the O position. To ensure trouble-free operation, care must be taken to ensure accurate dimensioning of all mechanical movement parts.
  • the check valves provide by an exhaust and an intake valve per cylinder are allocated. All intake valves are on one side with exhaust valves always are arranged opposite. Pressure line channels are incorporated in the cylinder block, each having a collecting channel on the front side, which is then connected to the housing cylinder with the oil outlet or oil inlet. In order to allow the high pressure on the housing covers, both lids are provided with synchronous thread.
  • the housing inlet and outlet lines for an external connection of the hydraulic pressure medium flow via pressure medium lines.
  • These include the supply and return, wherein the pressure lines and the return lines of both radial pump assemblies are connected via a pressure port and return port, so that the housing has only two ports in total.
  • a line branching is provided in the cylinder block, and the external connection of the pressure medium connections via inlet and outlet lines to the hydraulic motor.
  • the hydraulic drive primarily serves as a drive of a bicycle and the hydraulic pumping means is arranged in the bottom bracket of the bicycle, wherein the crankshaft is driven by pedals with muscle power.
  • the advantages of the invention can be used optimally, since in bicycle construction drive units should be as small as possible, and according to the requirement of the physiology of the user a continuous circuit is considered to be optimal.
  • the crankshaft can take over pedals the pedals and used as a bottom bracket.
  • the constructive embodiments of the present invention in terms of space, the cylindrical housing design and the required torques are optimized for this application. Other applications with minimal structural changes are very well conceivable when the individual properties require special solutions.
  • a further advantageous embodiment of the invention provides that the hydraulic motor is designed as a radial composite piston engine, with piston pairings are decisive here as well.
  • the advantage of the execution The hydraulic motor as a radial composite piston engine is superficially in the small size with a correspondingly high power throughput.
  • Another advantage here is that the radial composite piston engine can be optimally integrated in a wheel hub due to the flat design. Also, the ratio of delivery volume of the pressure medium for driving the radial piston motor and the torque that can be generated is very well adapted to the requirements of a bicycle drive.
  • the internal piston control comes without valves, on both sides of the cylinder block two segment sealing seals of about 50% of the peripheral surface and 180 ° offset seal the ring star wires so that the corresponding pairs of pistons are filled and emptied simultaneously.
  • the star ring lines are attached to the cylinder ring, sealed and connected to the cylinder chambers with exhaust or intake ports. On the hub shaft, the star ring lines are radially sealed.
  • the hydraulic pressure medium flow via a hub shaft, wherein the bore of the hub shaft has an internal pitch, so that the end of the hub shaft, the pressure medium on the releasably connected pressure medium lines and is discharged.
  • the division on half of the hub axle forms an inner wall, so that the hydraulic pressure medium can not flow from the pressure side directly to the return side.
  • the already necessary axis is designed as a pressure medium-supplying hub shaft and advantageously takes over three functions simultaneously. These are on the one hand the wave function of the wheel or the radial piston motor, on the other hand, the supply and removal of the pressure medium and pressure medium control.
  • the central division of the hub axle prevents flow through the pressure medium from the pressure side to the return side.
  • the pressure medium line is connected and supplies the radial piston motor with the pressure medium, thus external connections for the supply and discharge of the pressure medium, for example in the area of the housing superfluous and can be saved.
  • the housing is firmly bolted together with the cylinder ring, whereby the motor housing can be separated from the hub shell.
  • the invention provides that in a cylinder ring at least one pair of pistons is arranged connected to a double-sided rack, wherein the cylindrical spaces arranged in the cylinder chambers are pressurized so mutually that over the working stroke of the respective working piston, a torque between the toothed rack and a pinion can be generated on the hub shaft.
  • the pressure medium can be performed directly in the region of the inner star ring control, wherein the star ring control takes place via an interaction with the hub shaft such that the hub shaft has internally radially arranged holes through which the two Star ring controls are mutually acted upon by pressure medium and the relaxed pressure medium can also be discharged according to the rotation angle of the star ring control assembly on the hub axle again.
  • the working piston are pressurized via the inlet star ring control such that it performs a lifting movement via a double rack, wherein the working stroke takes place by the action of the working piston in the pitch circle segment, in which a "circular motion" of the drive wheel on the hub shaft arranged motor takes place and the rotational movement
  • the torque thus generated thus serves to drive the wheel, which is connected via the housing with the double rack and the pinion.
  • the piston pairs are connected to an annular double-toothed rod.
  • the toothed ring rod has from the inside adjusting teeth with a nose and return spring. If the toothed rack rod is pressed from one side, the negative inclined pin teeth automatically engage, whereby on the opposite side the pin teeth are pressed in with very little spring resistance. This process happens alternately, with resulting in a rotational movement.
  • An advantageous embodiment of the invention provides that the hydraulic motor is arranged on at least one hub of a bicycle to drive the releasably connected to a housing wheel of the vehicle.
  • the hydraulic motor is arranged on at least one hub of a bicycle to drive the releasably connected to a housing wheel of the vehicle.
  • only one wheel of a bicycle can be driven, wherein for reasons of simpler design, the rear wheel is preferably driven, but it can also be driven both wheels with the hydraulic motor according to the invention, which only requires the appropriate use of pressure medium lines.
  • the housing has features of a wheel hub as Radspeicheningn.
  • Fig. 1 is a front view with partial detail of a first embodiment of the hydraulic pumping means
  • FIG. 2 is an overall sectional view of the hydraulic pumping means according to FIG. 1, section A-A; FIG.
  • Fig. 3 is an overall view of a second embodiment of the hydraulic pumping means according to Fig. 1, section B-B;
  • FIG. 4 shows a further front view with partial section of the hydraulic pumping means.
  • FIG. 5 shows a detailed view of the hydraulic pumping means according to FIG. 6, detail C;
  • Fig. 6 is a further overall sectional view of the hydraulic pumping means according to Fig. 4, section A-A;
  • Fig. 7 is another overall sectional view of the hydraulic pumping means of Fig. 4, section B-B;
  • FIG. 8 is another front view of the hydraulic pumping means with covered housing and cylinder block;
  • FIG. 9 shows a further overall sectional illustration of the hydraulic pumping means according to FIG. 8, section CC;
  • FIG. 9 shows a further overall sectional illustration of the hydraulic pumping means according to FIG. 8, section CC;
  • FIG. 10 shows a detailed view of the hydraulic pumping means according to FIG. 8, detail D;
  • Fig. 11 is a front view of the hydraulic motor
  • Fig. 12 is an overall sectional view of the hydraulic motor, Fig. 11, section B-B;
  • Fig. 13 is another overall sectional view of the hydraulic motor, Fig. 11, section A-A;
  • FIG. 14 is another front view of the hydraulic motor
  • Fig. 15 is another overall sectional view of the hydraulic motor, Fig. 14, section A-A;
  • Fig. 16 is another overall sectional view of the hydraulic motor, Fig. 14, section B-B;
  • Fig. 17 is a detail view of the hydraulic motor of Fig. 16, detail C;
  • the hydraulic pumping means 100 shown in Fig. 1 to 3 has a housing 1, which has a hollow cylindrical portion for receiving the internal components, and further comprises two end-side housing cover 2, 2 '.
  • the housing cover 2, 2 ' have the task of screwing the cylinder block 10 and seal the pressure medium in the pressure medium collection channel frontally.
  • the two main ball bearings 4, 4 'in the housing cover 2, 2' fixed.
  • the cylinder block 10 has six slot-shaped star-shaped cylinder chambers, in which the working piston 22 in rows radially from Verstellicalzlager 17 after radial adjustment, are moved hydraulically outwards, wherein the pressure medium from the cylinder chambers through the incorporated in the cylinder block 10 pressure line channels only in the cylinder block 10 admitted Outlet valves 12 flows through and in the in the illustration in Fig. 2 on the front side shown on the right lying, not closer to recognizing pressure fluid collection channel, enters, then in the outlet channel and continues to lead through the connected to the housing 1 pressure line to the engine.
  • the six outlet valves 12 are located on the pressure side (Fig. 2 right) and open automatically under oncoming pressure.
  • the working piston 22 acting as a pressure piston which forms fixedly connected piston pairs with the opposite working piston 22, each having two connecting rings 7, 8, 9, the working pistons 22 operating as a suction piston simultaneously perform the suction work.
  • the paired working piston 22 permanently change its functional role as a pressure and suction piston.
  • the intake valves 11 open while the exhaust valves 12 close automatically. Since this is a closed circulation system, the pressure medium is guided back to the working cylinders through the ducts arranged symmetrically on the opposite side of the cylinder block.
  • the Verstellicalzlager 17 is located centrally on the both sides and secured against rotation flattened crankshaft 3, wherein the Verstellicalzlager 17 is secured even with a locking ring 24 against axial movement.
  • the adjusting roller bearing 17 can be infinitely adjusted radially on the crankshaft 3 with the aid of the adjusting piston 13, and thus the working pistons 22 can be moved in pairs.
  • the piston connecting rings 7, 8, 9 are arranged on the dimension width of the Verstellicalzlagers 17 on both sides of the working piston 22, the Verstellicalzlager 17 in each case rolls over the piston center in a circle. With increasing eccentricity of the variable pitch bearing 17, the flow rate and thus the transmission ratio increases continuously.
  • the housing 1 of the hydraulic pumping means 100 is cylindrical and fixed with four cylinder screws 16 on the cylinder block 10 (see FIG. 6), wherein along the longitudinal axis of the housing 1, a crankshaft 3 with adjusting and locking screw 14, which extends externally by means not shown, such as on pedal arms attached pedals, can be driven.
  • the external adjustment of the hydraulic pumping means 100 via a hydraulic pumping means 100 (see FIG. 7) attached, not shown cylinder / piston device.
  • a movement of the cable generates a pumping power at the cylinder / piston device via a lever arm, thereby causing a hydraulic radial adjustment of the adjusting roller bearing 17 (see FIG. 2) on the crankshaft.
  • crankshaft 3 is shown cut in the hydraulic pumping means 100.
  • the following elements and functions can be seen from this sectional view: On the right side of the illustration is the adjusting and locking screw 14, with which the amount of pressure medium in the hydraulic adjusting mechanism can be adjusted exactly.
  • the crankshaft 3 not only performs its main task comparable to a standard bottom bracket, but also serves as a cylinder body for a continuous adjustment via an adjusting piston 13, includes a Freilaufverstell piston 6, 6 ', a line segment 20 between the external cylinder / piston pumping device on the Pressure medium connection line 21 (see Figure 7), via the intermediate line segment 20, and a crankshaft coupling 18th
  • the crankshaft coupling 18 of the hydraulic pumping means 100 (see FIG. 3) encloses the crankshaft 3, wherein three pressure medium inputs and outputs are arranged on the crankshaft 3 centrally below the pressure medium coupling 18 and are additionally connected to an incorporated groove and with two sets of rotor gaskets are sealed on both sides.
  • the pressure medium flows through in switching operation, the intermediate line segment 20 and the pressure medium connection line 21, while externally the cylinder / piston device is adjusted.
  • the freewheel device 5 (see FIG. 2) is located between the main ball bearing 4 and the adjusting roller bearing 17 on the crankshaft 3. This hydraulic device should completely interrupt the flow of pressure medium at each return operation. This happens in that in the freewheel device 5 opposite to two cylinder pins 15 in the corresponding rotation angle range are two adjustable cam latch 23, which can be overturned with light, caused by a leaf spring 25 spring preload in the lead / resignation, incorporated in a cylinder block 10 freewheel teeth 26 (see FIG. 5). During a return movement, the cam latches 23 rotate to the lowest point, allow the Freilaufverstellkolben 6, 6 'extend, wherein the pressure medium space is expanded so far that moves the Voreriever ein the Verstellicalzlagers 17 in the central position.
  • the hydraulic motor 200 is shown in section with a multi-part housing (with hub housing 30, left motor housing 31 and right motor housing 32).
  • the housing parts left motor housing 31 and right motor housing 32 connect with six screws 40 and locknuts 41 the inner cylinder ring 48 with six radially arranged cylinders.
  • the cylinder ring 48 has recesses, which cause a weight reduction.
  • the hub shell 30 (see FIG. 12) is connected six times with a screw 44 and slotted nut 43 to the left motor housing 31, and the motor 200 with the housing unit consisting of the left motor housing 31 and the right motor housing 32 can be unscrewed for possible repairs ,
  • hub shell 30 and right motor housing 32 On both sides in the housing parts hub shell 30 and right motor housing 32 are two ball bearings 28, 28 'on the hub shaft 53 with lock nuts 36, 36' attached.
  • the pressure medium supply of the hydraulic motor 200 via the hub shaft 53, at both ends of the inlet line and outlet line is connected, which are not explicitly shown.
  • the front side two star-shaped pressure fluid control rings 37, 38 are secured to the cylinder ring 48, wherein these enclose the hub shaft 53 and are each provided with two sets of rotor gaskets.
  • the hub shaft 53 is hollow but centrally closed in the region of the cylinder ring 48 from both sides.
  • a three-part pressure medium outlet is additionally arranged with a radial groove, wherein each one shaft segment seal 29, 29 'of 180 °, the pressure medium control rings 37, 38 semi-circumferentially seals.
  • the outlet side is sealed in exactly the opposite direction.
  • the two pressure medium control rings 37, 38 completely replace the valve control system.
  • the pressure medium channels lead the pressure medium from the six-part pressure medium control ring 37, 38 to the working piston 51, wherein these torque via the toothed ring rods 45, 46, 47, each of which a pair of pistons of two working pistons 51 fixedly connected via the arranged on the hub shaft 53 pinion 49 transmit and put the drive wheel of a bicycle in motion.
  • the pinion 49 itself is separated by ball bearing from the hub shaft 53, wherein three snapper 50 stop the piston activity in the hydraulic motor 200 at an interruption of the pressure medium flow. This feature is similar to a standard sprocket.
  • the middle rack bar 46 is shown in section.
  • the three toothed ring rods 45, 46, and 47 are connected in a staggered arrangement each with two working pistons 51, so that an independent and non-contact adjustment is possible.
  • pin teeth built in on both sides are arranged in such a way that each toothed rack rod 45, 46, 47 only engages the pinion 49 on one side and alternately. This is done a) by the inclination position of the pin teeth 54 on the one hand, b) by easy adjustability of the pin teeth 54 on the opposite side by the counter-acting pinion teeth, against the return spring 56, on the other.
  • the pin teeth 54 have a nose for hooking. In a torque transmission at least three to six pin teeth 54 are uniformly stressed.

Abstract

L'invention concerne un entraînement hydraulique, en particulier pour entraîner un véhicule fonctionnant par la force musculaire, qui présente un moyen de pompage hydraulique pour fournir un flux de fluide hydraulique et au moins un moteur hydraulique. Le moyen de pompage hydraulique et le moteur hydraulique sont reliés entre eux via au moins une conduite de fluide hydraulique, et le moyen de pompage hydraulique présente au moins une paire de cylindres et au moins une paire de pistons composites qui y sont radialement mobiles. Selon l'invention, le moyen de pompage hydraulique est réalisé sous forme de pompe à pistons composites radiaux, la longueur de course du piston composite étant réglable au moyen d'au moins un palier mobile pouvant être déplacé radialement, afin de régler en continu le flux de fluide hydraulique. De plus, selon l'invention, le moteur hydraulique est réalisé sous forme de moteur à pistons composites radiaux avec une crémaillère et un pignon, sachant qu'au moins une paire de pistons composites présente une crémaillère qui roule par des dents de broche mobiles sur le pignon et accomplit chaque fois un mouvement constant.
PCT/EP2008/061918 2007-09-13 2008-09-09 Entraînement hydraulique WO2009037151A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710045014 DE102007045014B3 (de) 2007-09-13 2007-09-13 Hydraulischer Antrieb
DE102007045014.3 2007-09-13

Publications (1)

Publication Number Publication Date
WO2009037151A1 true WO2009037151A1 (fr) 2009-03-26

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PCT/EP2008/061918 WO2009037151A1 (fr) 2007-09-13 2008-09-09 Entraînement hydraulique

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WO (1) WO2009037151A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2520179A (en) * 2013-06-04 2015-05-13 Genius Ip Ltd A hydraulic or pneumatic drive system, and a motor and a pump therefor

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009060453A1 (de) * 2009-12-24 2011-06-30 Opitz, Hans-Joachim, 30916 Mit Muskelkraft betriebenes Fahrzeug, insbesondere Landfahrzeug
DE102012021554A1 (de) 2012-10-26 2014-04-30 Stefan Matuzic Hydrostatischer Antrieb
CN112503923B (zh) * 2020-11-27 2022-04-05 合肥三伍机械有限公司 一种用于谷物烘干机的双推动装置

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US2851952A (en) * 1957-06-27 1958-09-16 Lane Edwin Leonard Hydraulic pumps
JPS53109346A (en) * 1977-03-05 1978-09-25 Shimadzu Corp Hydraulically power transmitted bicycle
JPS61266869A (ja) * 1985-05-21 1986-11-26 Bridgestone Cycle Co 偏心カムの偏心制御装置
DE19749906A1 (de) * 1997-11-12 1999-05-20 Halm Peter Radialkolben-Hydromotor
FR2831221A1 (fr) * 2001-10-18 2003-04-25 Jean Yves Guittard Dispositif de pompe hydraulique basse pression pour l'alimentation d'au moins un moteur hydraulique, notamment destine a equiper une bicyclette a entrainement hydraulique

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DD221704A1 (de) * 1984-02-23 1985-05-02 Wismar Mechanisierung Hydro-antrieb
DE4015962A1 (de) * 1990-05-18 1991-11-21 Eckehart Schulze Fahrrad mit hydraulischer antriebseinrichtung
DE4139422C2 (de) * 1991-11-29 1994-02-03 Tanja Vorsteher Hydraulisches Antriebs- und Bremssystem
DE19630447A1 (de) * 1996-07-27 1998-01-29 Eckhard Dr Ing Oster Hydrostatischer Antrieb mit Steuereinheit für Zweiräder
US6055878A (en) * 1997-12-16 2000-05-02 Speed Control, Inc. Adjustable eccentric shift mechanisms
DE102005009821B3 (de) * 2004-11-16 2006-07-20 Stefan Matuzic Hydraulische Antriebseinheit

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2851952A (en) * 1957-06-27 1958-09-16 Lane Edwin Leonard Hydraulic pumps
JPS53109346A (en) * 1977-03-05 1978-09-25 Shimadzu Corp Hydraulically power transmitted bicycle
JPS61266869A (ja) * 1985-05-21 1986-11-26 Bridgestone Cycle Co 偏心カムの偏心制御装置
DE19749906A1 (de) * 1997-11-12 1999-05-20 Halm Peter Radialkolben-Hydromotor
FR2831221A1 (fr) * 2001-10-18 2003-04-25 Jean Yves Guittard Dispositif de pompe hydraulique basse pression pour l'alimentation d'au moins un moteur hydraulique, notamment destine a equiper une bicyclette a entrainement hydraulique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2520179A (en) * 2013-06-04 2015-05-13 Genius Ip Ltd A hydraulic or pneumatic drive system, and a motor and a pump therefor
GB2520179B (en) * 2013-06-04 2015-12-09 Genius Velo Ltd A hydraulic or pneumatic drive system, and a motor and a pump therefor

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