WO1993011027A1 - Systeme hydraulique d'entrainement et de freinage - Google Patents

Systeme hydraulique d'entrainement et de freinage Download PDF

Info

Publication number
WO1993011027A1
WO1993011027A1 PCT/EP1992/002765 EP9202765W WO9311027A1 WO 1993011027 A1 WO1993011027 A1 WO 1993011027A1 EP 9202765 W EP9202765 W EP 9202765W WO 9311027 A1 WO9311027 A1 WO 9311027A1
Authority
WO
WIPO (PCT)
Prior art keywords
connecting rod
hydraulic
axis
base body
cylinder
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP1992/002765
Other languages
German (de)
English (en)
Inventor
Tanja Vorsteher
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP92924627A priority Critical patent/EP0630335A1/fr
Publication of WO1993011027A1 publication Critical patent/WO1993011027A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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

Definitions

  • Hydraulic systems which consist of two interconnected hydraulic machines, one of which acts as a pump and one as a motor, are known for a wide variety of uses, including for driving
  • Hydraulic drives have also already been provided for bicycles.
  • Such hydraulic systems can be switched from driving to brakes by simple reversing measures, an advantage of which is that Braking energy does not necessarily have to be converted into heat energy to be dissipated and lost, but can at least partially be recovered with the aid of an appropriate energy store.
  • Equipping the hydraulic drive system with a stepless adjustment of the conveying capacity avoids a step-by-step manual transmission for adapting the transmission in vehicles, especially in bicycles, which requires a relatively high level of design and cost, especially for bicycles, and makes a not insignificant contribution to the overall weight of the bicycle.
  • this short-circuit valve When this short-circuit valve is in the normal, ie closed, position and the vehicle is braked, the previous pump becomes the driven motor and the motor becomes the pump, so that work is being done on the hydraulic machine that now acts as the motor - and which is usually located on the pedal crank axis of a bicycle can be done.
  • This work can be done in a working memory can be collected, which is either a gas storage with variable volume, the content of which is compressed by the work of the engine, or a mechanical element equipped with high spring force, which is also by “The work of the hydraulic motor is compressed.
  • the energy stored in this working memory can be withdrawn at a later point in time, when the hydraulic machine arranged on the pedal crank axis is to work again as a pump, via an infinitely controllable valve and thereby offer additional acceleration of the vehicle.
  • a further hydraulic machine which is connected to it in a rotationally fixed manner and which is to be referred to below as an accelerator machine, is arranged, which at. Thrust operation of the vehicle is mechanically driven by the hydraulic motor and feeds the working memory. In the event of later acceleration, the energy can be removed from the working memory via this accelerator machine and mechanically fed to the first hydraulic machine, which then functions as a pump.
  • This accelerator machine also has a short-circuit valve to enable a driving state in which there is neither braking nor additional acceleration from the main memory.
  • Controls for example from the handlebar of the bicycle using a manual switch, are used to choose whether energy is drawn from the working memory or supplied to it or whether the accelerator machine is switched to short-circuit, and on the other hand if necessary the stroke volume of the pump of the first hydraulic circuit is switched on. ⁇ , or the short-circuit valve of this first
  • Hydraulic circuit opened if the short circuit valve of the accelerator machine is also open.
  • the feed line into the working memory should contain a non-return valve in order to avoid, at a relatively high pressure inside the working memory, that when a desired loading with low output takes place, instead of a loading, removal from the working memory and thus an undesired acceleration effect take place.
  • the accelerator machine can be connected to the main memory via essentially only one line, a gas store preferably being accommodated in the cavities of the bicycle frame, so that this line does not branch into the feed line and discharge line until directly in front of the accelerator machine by means of a reversing valve located there. which combines the function of the two individual valves required in separate lines.
  • the check valve must then be arranged only in the individual line of the accelerator machine to the reversing valve, which serves as a feed line to the working memory.
  • the short circuit valve assigned to the accelerator machine is coupled to the two individual valves in the feed and extraction line to the working memory or to the functionally combined individual valve in such a way that the short circuit valve is automatically opened when the other two valves are both closed.
  • the other two valves can only be opened alternatively, but not at the same time.
  • the pedal cranks are not fixed mechanically on the pedal crank axle on which the first hydraulic machine and the accelerator machine are located, but by means of an interposed mechanical freewheel device in order to ensure that the pedal cranks come to a standstill, and thus, when the pedal crank axle rotates or is braked, despite the rotation of the pedal crank axle of the pedals.
  • the reservoir in the form of an oil reservoir which is required to supply the hydraulic system with hydraulic medium, is preferably accommodated in the cavities of the bicycle frame, with only partitions having to be tightly inserted in the tubular pieces of the bicycle frame in order to create closed cavities with a defined volume.
  • additional devices such as diaphragms, pistons etc. must be provided.
  • the hydraulic machines have the following common features:
  • the hydraulic machine is a piston machine, in which the individual pistons are radially axially displaced radially in a radial manner in a cylinder base body and the corresponding cylinder spaces introduced therein, in which they lie tightly, so that between the outer end face of the piston, the inner wall of the cylinder spaces and the surrounding lateral surface from the housing or intermediate ⁇ components is limited, the variable volume
  • the piston spaces unite in the middle of the cylinder base body to form a central space through which the axis extending coaxially to the cylinder base body extends.
  • the connecting rods connected to the inner end face of the pistons are guided eccentrically with respect to the cylinder body in a manner known per se, in that the connecting rods have a connecting rod eye at the end facing away from the piston encloses the connecting rod axis eccentrically to the cylinder body.
  • each piston rod Since each individual piston and thus each individual piston rod has a different deflection from the center of the cylinder space compared to the other piston rods, each piston rod must be able to be changed in its rotational position independently of the other piston rods with respect to the connecting rod axis.
  • the individual connecting rod eyes are dimensioned so short in their axial extent that the individual connecting rod eyes can be accommodated one behind the other in the axial direction on the connecting rod axis within the axial extension of the entire cylinder body.
  • the connecting rod eyes preferably do not run directly on the connecting rod axle, but on an intermediate sleeve arranged between the two, which compensates for the individual radial forces of the individual connecting rod eyes and converts them into a surface pressure that is uniform over the axial extension relative to the connecting rod axle and can therefore also serve as a wearing part.
  • the connecting rods are made as narrow as possible in the axial direction in order to form the lowest possible resistance to the hydraulic fluid in the central space.
  • the central space is filled with hydraulic fluid despite the tight contact of the pistons in the cylinder spaces, since it can never be completely sealed for long periods, which does not mean a disadvantage, however, since the areas of the central space delimited by the pistons do not change during operation of the hydraulic machine Enclose volume.
  • the connecting rods can not be articulated to the rear sides of the piston, but fixed, preferably in one piece, so that inclined positions of the pistons relative to the surrounding cylinder walls result from the deflection of the connecting rods which are fixedly connected to the pistons.
  • the pistons in this case - which are of course adapted in cross-sectional shape to the cross-sectional shape of the cylinder chambers - are provided with an outer contour in the side view in the direction of view of the axis, which part at least in the central region of the piston a spherical or circular contour.
  • the first hydraulic machine which generally acts as a pump, is to be driven by means of the axis extending centrally through the base body and, in addition, the delivery capacity can be adjusted to change the transmission ratio.
  • the housing and also the connecting rod axis are designed to be stationary, the connecting rod axis being able to be manually adjusted in its radial position, as a result of which the eccentricity of the hydraulic machine and thus the delivery volume and the translation of the overall system are changed.
  • the connecting rod axis extends out of the main housing on at least one end face and is radially adjusted there by means of a push rod which is guided radially along the housing, preferably in the form of a plate.
  • a push rod which is guided radially along the housing, preferably in the form of a plate.
  • Another solution is an adjusting element which rotates axially into the housing and which only adjusts the connecting rod axis within the housing via an eccentric, as a result of which fewer sealing problems occur.
  • the star-shaped cylinder base body on the other hand, due to the cylinder bores introduced, is non-rotatably connected to the drive axle, this radial connection preferably taking place on the end face of the hydraulic base body facing away from the connecting rod for the connecting rod axis.
  • the free inner diameter of the connecting rod axis must be chosen so large that even with maximum radial adjustment of the connecting rod axis no obstruction by
  • the drive axis extends centrally to the base body through the connecting rod axis.
  • the connecting rod axis can also be adjusted beyond the zero position, which reverses the direction of delivery and thus the direction of drive of the hydraulic system.
  • one or each hydraulic machine which will preferably work as a motor, is to be provided on the wheels of the vehicle to be driven, in which the axis extending centrally through the basic cylinder body remains at rest and is therefore fixed to the fixed parts of the vehicle can be connected.
  • the motor the housing rotates, on which the rim, either a front or rear wheel or both, is driven via spokes or similar radial elements.
  • the cylinder base body as well as the individual pistons with their connecting rods and the connecting rod eyes, and the possible intermediate sleeve, rotate with the housing, while the connecting rod axis stands together with the central axis.
  • the housing is mounted and sealed on the central axis, and this axis is preferably designed as a hollow axis in order to serve as a supply and discharge line for the hydraulic medium to the motor.
  • the partitioning into a high-pressure side and a low-pressure side space is achieved by means of a partition in the cross-section of the hollow, central axis that is arranged on the symmetry line of the hydraulic machine and that also extends tightly up to the inner wall of the eccentric connecting rod axis.
  • a partition in the cross-section of the hollow, central axis that is arranged on the symmetry line of the hydraulic machine and that also extends tightly up to the inner wall of the eccentric connecting rod axis.
  • ⁇ O There is preferably a manually adjustable short-circuit valve in the partition, which enables this hydraulic machine to run freely.
  • the supply of the hydraulic oil to the desired areas is achieved in that in the axial direction between the two end faces of the cylinder body and the housing inner wall, radially sealingly connected to the hollow central axis, disc-shaped elements are arranged which have recesses in the area of defined sectors, which Allow the corresponding hydraulic medium to be forwarded to the lateral surface of the cylinder base body in a specific sector by means of corresponding radial openings in the hollow central axis.
  • the cutouts of the two opposite disks are offset from one another in order to ensure the desired motor operation of the hydraulic machine.
  • Appropriate recesses must therefore be provided above each piston in the inside of the outer surface of the housing, which have a connection to the open spaces on the front side, these open spaces on the front side being filled to approximately 2/3 by partial discs that are fixed on the front side and connected to the central axis, and only closed about 1/3, offset in their rotational position against each other, allow the connection of the free spaces in the jacket surfaces to the corresponding negative pressure or positive pressure line in the central space of the hydraulic machine.
  • the constructive solution of such hydraulic machines can also be used as an internal combustion engine, in which the hydraulic work spaces become the combustion spaces or compression spaces, with corresponding modifications such as the provision of an ignition element etc. being necessary in each combustion space. However, this makes it possible to adjust the ignition timing and, if necessary, also the compression ratio in a simple manner.
  • Fig. 1 shows a schematic diagram of the hydraulic
  • Fig. 2 is an end view of the invention
  • Hydraulic machine as a pump in the version provided on the pedal crank axis
  • FIG. 3 is a sectional view of the pump of FIG. 2 along the line III-III,
  • FIG. 4 a representation similar to FIG. 2 for a hydraulic motor
  • FIG. 5 is a sectional view of FIG. 4 along the line V-V,
  • Fig. 6 is a sectional view of FIG. 4 along the line VI-VI and
  • FIG. 1 shows a basic illustration of the arrangement of the drive and brake system according to the invention on the frame of a bicycle.
  • the physically drawn parts of the bicycle are shown hatched, namely the bicycle frame 22, the fork 43 and the handlebar 24.
  • bottom bracket 41 is present at the normal position, ie the meeting point of the seat post and the beam, through which the bottom bracket axis 19 extends.
  • the pump 1 is arranged in a rotationally fixed manner on this bottom bracket axis, as is the accelerator machine 5, which are thus connected to one another mechanically in a rotationally fixed manner by the pedal crank axis 19.
  • the pedal cranks 20 are fastened to the ends of the pedal crank axis 19 by means of a mechanical freewheel device 21.
  • a hydraulic motor 2 is arranged both at the location of the front wheel and at the location of the rear wheel of the bicycle, which hydraulic motors are fed by the pump 1 by means of hydraulic lines 27, 28.
  • Both motors 2 have a short-circuit valve 12, 13, whereby both motors can be switched over to a freewheel.
  • each of the short-circuit valves 12, 13 would have to be able to be moved back and forth manually between the two switching positions, as a result of which a hydraulic braking operation of the Bicycle is controlled, provided that the return line 28th AI to the pump 1 is completely closed by a valve, not shown in Fig. 1.
  • Fig. 1 in addition to the pump 1, there is a hydraulic machine running, the accelerator machine 5, which, when the bicycle is braked hydraulically, feeds hydraulic medium into a gas pressure accumulator 3, which is accommodated in a cavity of the lower tube, and thereby collecting energy in this gas storage.
  • the accelerator machine 5 which, when the bicycle is braked hydraulically, feeds hydraulic medium into a gas pressure accumulator 3, which is accommodated in a cavity of the lower tube, and thereby collecting energy in this gas storage.
  • the accelerator machine is equipped with a 3/3-way valve 14, 15, 44 which, via the hydraulic line 6, 7, connects the oil-carrying areas of the gas reservoir 3, which contains a compressible gas volume, optionally with the High pressure or with the low pressure side of the accelerator machine.
  • the work stored in the gas accumulator 3 can be used by removing hydraulic medium from the gas accumulator 3 for additional acceleration by means of supply to the high-pressure side of the accelerator machine 5, or for braking with simultaneous energy storage, which can be done by manually adjusting the 3/3-way valve 14, 15, 44, and a suitable setting of the push rod on the pump 1 and the short-circuit valves 12, 13 by means of the hand switch 23 from the handlebar 24.
  • the 3/3-way valve 14, 15, 44 has a short-circuit position 44 with respect to the accelerator machine 5 for the freewheeling of the bicycle. Furthermore, a check valve 16 is arranged in the feed line 6, 7 to the gas storage device in order to avoid an undesired acceleration process when the pressure in the gas pressure storage device 3 is already high and the working storage device is further charged with low pressure.
  • the oil reservoir 4 is provided, which is provided without pressure as a reservoir for supplying the hydraulic system with hydraulic medium and is connected to the pump 1 via a check valve 16 and to the accelerator machine 5.
  • FIGS. 2 For a better understanding, the stationary parts of the hydraulic machine are shown hatched in FIGS. 2 and the following, while the rotating parts are unshaded.
  • FIG. 3 The pump according to FIG. 2 is shown in FIG. 3 in a cut-away side view, that is to say in the viewing direction III-III of FIG. 2.
  • the cylinder base body 31 with its radially circular cylinder spaces 36 runs in a housing 140.
  • the cylinder base body 31 is driven by the central axis 141, to which it is connected in a rotationally fixed manner by means of an end plate 142 arranged on one end face is, as can be seen better in FIG. 3.
  • the central axle 141 which corresponds to the pedal crank axle 19 when installed in a bicycle, is mounted relative to the housing 140 by means of the bearings 42.
  • the individual pistons 32 move up and down once in their cylinder space due to their eccentric bearing on the likewise stationary eccentric connecting rod axis 35, as a result of which an intake and a compression phase are achieved by rotating one in the direction of the arrow
  • the hydraulic medium unit is supplied via the supply line 27 on the low-pressure side - that is to say the working space 29 in the cylinder space 36 outside the pistons 32 - and is discharged via the line 28 on the high-pressure side.
  • the eccentricity and thus the stroke volume of the pump 1 can be changed in that the stationary, eccentric connecting rod axis 35 can be adjusted in its eccentricity with respect to the central axis 141 by means of a radially movable push rod 34, which extends outside the housing 140, as can be seen in Fig. 3.
  • FIG. 2 shows how each piston 32 is connected to its connecting rod eye 33 by means of at least one connecting rod 30, which tightly but rotatably surrounds the eccentric, stationary connecting rod axis 35.
  • each connecting rod and thus each piston 32 must have at least one separate connecting rod eye 33 assigned to it To allow deflections of the piston 32 with respect to the cylinder space 36 occurring during the rotation.
  • the individual connecting rod eyes 33 are arranged one behind the other in the axial direction and are designed so narrow that the number of connecting rod eyes required for the corresponding number of pistons is within the axial extent of the basic cylinder body, that is to say between the cylinder spaces 36 persistent intermediate segments 39, can be accommodated.
  • Some pistons 32 are connected to only one connecting rod 33 via only one connecting rod 30, while other pistons, as shown in the lower half of the figure in FIG. 3, are supported on two in the same way by two one-piece connecting rods 30 arranged at an axial distance from one another Distance from the connecting rod eyes 33 to ensure a uniform introduction of the radial piston forces in the stationary, eccentric connecting rod axis 35 in the axial direction.
  • the connecting rod eyes 33 preferably do not run directly on the connecting rod axis 35, but on an appropriately dimensioned intermediate sleeve 38 arranged between them, which rotates with the connecting rod eyes 33 and fulfills the function of a wearing part.
  • the pistons In order to enable the changes in the inclined position of the pistons 32 relative to the cylinder spaces 36, as seen in FIG. 2, the pistons have a spherical outer contour in the side view of FIG. 2, that is to say in the direction of view of the axes, which corresponds to a central region of a circle, and thus - with a cylindrical cross section of the cylinder spaces 36 - the central region of a sphere.
  • the transverse extent of the piston 32 is always the same, even when deflected from alignment with the cylinder space 36, as a result of which a sealing contact is made Piston outer surfaces on the cylinder chamber inner surfaces is given despite angular deflection.
  • FIG. 4 shows the hydraulic machine 2 of FIG. 1, which is usually operated as Mo ⁇ .or, namely FIG. 4 in a middle section through the plane of symmetry 247 in the direction of view of the axes with the graduated disk 242 drawn in front thereof, and FIG 5 in the viewing direction of the section VV in FIG. 4, and the illustration in FIG. 6 in the viewing direction of the section VI-VI in FIG.
  • the enclosing housing 240 is not shown in FIG. 4.
  • FIG. 4 - similar to FIG. 2 - shows the piston base body 31 or its intermediate segments 39 between individual cylinder spaces 36, and the pistons 32 moving in the cylinder grooves together with connecting rods 30 and a connecting rod eye 33.
  • the housing 240 rotates with the cylinder body 31 and the piston 32.
  • the zentra.® axis 241 is designed as a hollow axis with an Absctio.i_ung 244 in the middle of the motor 2, so that the Cavities on both sides serve to supply the hydraulic medium to the high and low pressure sides.
  • the bulkhead 244 extends radially beyond the cross section of the fixed central axis 241 to close to the inner surfaces of the eccentric, also stationary connecting rod axis 35, so that the central space 37 outside the central axis 241 and inside the connecting rod axis 35 into a high pressure and a Low pressure side is divided.
  • the short-circuit valve 12 is arranged in the partition 244, which can establish a connection between the two pressure sides and thus enable the wheel to run freely. The control of the short-circuit valve 12 is not shown.
  • At least one radial opening 250 is opened on each side of the central space 37.
  • the forwarding of the pressure medium on the high-pressure and low-pressure side via the end faces of the cylinder body 31 to the peripheral surfaces and thus the working spaces 29 of the cylinder spaces 36 depends on whether the corresponding piston 32 is in the high-pressure or low-pressure range according to FIG. 4 is located.
  • An inflow or outflow of the hydraulic medium is only possible via appropriately designed pockets 251, 252 if the corresponding partial disk 242, 243 does not close off the axial free space between the front-side inner wall of the housing 240 and the front-end outer wall of the cylinder base body 31 5 and 6 have curves 253, 254, in order to enable a laminar flow of the hydraulic medium with the least possible resistance.
  • the two outer surfaces of the pockets 251, 252 meet in an elevation 255 approximately in the center of the bottom of the piston 32, which, as shown in FIG. 7, is at an angle of approximately 45 ° to the plane of symmetry 247 and to the direction of the axes.
  • the shape of the partial disk 242 on the right and left in FIG. 6 can be seen from FIG. 4, in which this partial disk 242 is drawn with a thick-edged contour.
  • the large, approximately semicircular, left-hand area of the indexing disk 242 corresponds to the thicker area of the indexing disk which is graduated on the dashed, thick line, that is to say the axial distance between the inside of the housing 240 and the central space 37 or the front-side outer surface of the basic cylinder body 31
  • This thin, crescent-shaped part 242a seals the distance between the cylinder body 31 and the outside of the eccentric connecting rod axis 35.
  • FIG. 7 shows, in the viewing direction T x and T 2 of FIG. 4 and T ⁇ of FIG. 5, a development of the peripheral surface of the inside of the housing approximately at the section line VII-VII of FIG. 5.
  • FIG. 7 is in the high-pressure area according to FIG. 4, so that the high-pressure side access, that is to say the sectoral cutout 248 (dotted in FIG. 4) of the left-hand partial disk 243 to the left of the center of the illustration in FIG. 7 can be seen . 7 - in the top view of FIG. 7 - via pockets 251, 252, which are arranged parallel to each other and each separated by the inclined elevation 255, to the two free spaces on both sides of the end face of the cylinder base body 31, which through the two partial disks 242, 243 partially are filled.
  • this work space which is located at the transition between the low-pressure sector and the high-pressure sector, has just no connection with the beginning of the high-pressure region and is therefore not yet part of the high-pressure side Hydraulic medium supplied, but with increasing rotation of the machine, this top pocket 252 in FIG. 7 is fully opened in its connection to the sectoral recess 248.
  • this uppermost working space 29 of FIG. 7 no longer has any connection via the pocket 251 to the free space to the right of the basic cylinder body, since that in FIG. 7 The upper end of the pocket 251 already runs into the beginning of the thick part of the right part 242.
  • the ends of the pockets 251, 252 are bent in the form of a quarter circle 246 towards the elevations 255 and thus promote a laminar, swirl-free inflow of the hydraulic medium into the working spaces 29 of the hydraulic machine, which are additionally shown by the curves 253 and 254 in the direction of view in FIG. 5 and 6 are supported.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Motors (AREA)
  • Control Of Fluid Gearings (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

On peut réaliser de manière particulièrement simple un réglage en continu de la transmission de systèmes hydrauliques, notamment d'entraînement de véhicules, en construisant des machines hydrauliques, dans lesquelles des chambres de cylindre (36) radiales sont agencées en étoile dans un corps de base (31) du cylindre et se rejoignent dans une cavité centrale. Les pistons (32) sont montés excentriques par rapport au corps de base (31) du cylindre sur un axe (141) qui traverse cette cavité centrale, leur excentricité étant ajustable. En ajoutant au système hydraulique un accumulateur de pression (3) pour le fluide hydraulique, on peut stocker temporairement l'énergie à annihiler pendant le freinage pour l'utiliser lors d'accélérations ultérieures.
PCT/EP1992/002765 1991-11-29 1992-11-30 Systeme hydraulique d'entrainement et de freinage Ceased WO1993011027A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP92924627A EP0630335A1 (fr) 1991-11-29 1992-11-30 Systeme hydraulique d'entrainement et de freinage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4139422.4 1991-11-29
DE19914139422 DE4139422C2 (de) 1991-11-29 1991-11-29 Hydraulisches Antriebs- und Bremssystem

Publications (1)

Publication Number Publication Date
WO1993011027A1 true WO1993011027A1 (fr) 1993-06-10

Family

ID=6445930

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1992/002765 Ceased WO1993011027A1 (fr) 1991-11-29 1992-11-30 Systeme hydraulique d'entrainement et de freinage

Country Status (4)

Country Link
EP (1) EP0630335A1 (fr)
AU (1) AU3083492A (fr)
DE (1) DE4139422C2 (fr)
WO (1) WO1993011027A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19630447A1 (de) * 1996-07-27 1998-01-29 Eckhard Dr Ing Oster Hydrostatischer Antrieb mit Steuereinheit für Zweiräder
WO1999051486A1 (fr) * 1998-03-25 1999-10-14 Galina Grigoryevna Budkevich Procede d'entrainement d'un moyen de transport par le biais de l'energie musculaire d'un humain et transmission hydraulique permettant de mettre en oeuvre ce procede

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612519C2 (de) * 1996-03-29 1999-07-08 Helmut Goeb Hydraulisches Getriebe für Fahrräder
DE29612234U1 (de) * 1996-07-13 1996-12-19 Gauermann, Jörg, 70771 Leinfelden-Echterdingen Oelhydraulischer Fahrradantrieb
DE102007045014B3 (de) * 2007-09-13 2009-01-29 Stefan Matuzic Hydraulischer Antrieb

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4078816A (en) * 1976-05-24 1978-03-14 Michael Sean Smith Hydraulically driven two-wheeled pedicab
US4087105A (en) * 1977-05-12 1978-05-02 Amarantos John G Hydraulic powered bicycle
GB2102747A (en) * 1981-05-29 1983-02-09 Harold William Lamberth Hydraulic transmission for bicycle
US4684143A (en) * 1985-04-05 1987-08-04 Yasunori Sato Two-wheeled vehicle with hydraulic transmission
WO1991017913A1 (fr) * 1990-05-18 1991-11-28 Eckehart Schulze Cycle a commande hydraulique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4078816A (en) * 1976-05-24 1978-03-14 Michael Sean Smith Hydraulically driven two-wheeled pedicab
US4087105A (en) * 1977-05-12 1978-05-02 Amarantos John G Hydraulic powered bicycle
GB2102747A (en) * 1981-05-29 1983-02-09 Harold William Lamberth Hydraulic transmission for bicycle
US4684143A (en) * 1985-04-05 1987-08-04 Yasunori Sato Two-wheeled vehicle with hydraulic transmission
WO1991017913A1 (fr) * 1990-05-18 1991-11-28 Eckehart Schulze Cycle a commande hydraulique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19630447A1 (de) * 1996-07-27 1998-01-29 Eckhard Dr Ing Oster Hydrostatischer Antrieb mit Steuereinheit für Zweiräder
WO1999051486A1 (fr) * 1998-03-25 1999-10-14 Galina Grigoryevna Budkevich Procede d'entrainement d'un moyen de transport par le biais de l'energie musculaire d'un humain et transmission hydraulique permettant de mettre en oeuvre ce procede

Also Published As

Publication number Publication date
DE4139422C2 (de) 1994-02-03
DE4139422A1 (de) 1993-06-03
AU3083492A (en) 1993-06-28
EP0630335A1 (fr) 1994-12-28

Similar Documents

Publication Publication Date Title
DE2952839C1 (de) Anti-Roll System fuer ein Fahrzeug
DE2533095C2 (de) Taumelscheibentriebwerk mit verstellbarem Kippwinkel der Taumelscheibe insbesondere für Heißgaskolbenmaschinen
DE1555984B1 (de) Hydrostatisches Getriebe fuer Kraftfahrzeuge
DE10213156A1 (de) Aktive Federung für ein Kraftfahrzeug
DE19849334B4 (de) Hydrostatische Motoreinheit
DE4447129A1 (de) Hydraulischer Taumelscheiben-Trieb, hydromechanisches, stufenlos veränderbares Getriebe, Verfahren zum Steuern des hydromechanischen, stufenlos veränderbaren Getriebes
WO1993011027A1 (fr) Systeme hydraulique d'entrainement et de freinage
EP1299644B1 (fr) Transformateur hydraulique
DE3904944C2 (de) Hydrostatisches Getriebe
WO1994002334A2 (fr) Systeme hyraulique d'entrainement et de freinage
DE4224074A1 (de) Verbrennungsmotor
DE3627375C2 (fr)
DE3916444C1 (en) Car seat backrest hydraulic adjuster - has two cavities, each of two parts with first part annular segment chamber for separating piston
DE4428410C2 (de) Kompakte Regeleinheit für eine Flügelzellenpumpe
DE1628130A1 (de) Druckfluessigkeitsmotor bzw. Fluessigkeitspumpe
DE2733128A1 (de) Hydrostatische zweikreis-lenkanlage
DE2748455A1 (de) Hydro-rotationsmaschine
DE1680253A1 (de) Servo-Lenkung fuer Kraftfahrzeuge
DE19735979B4 (de) Hilfskraftlenkung
EP0433347A1 (fr) Direction assistee, notamment pour vehicles a moteur.
DE102008019993A1 (de) Leichtfahrzeug
DE19918123A1 (de) Kolbenpumpe
DE3902808A1 (de) Hydraulische hilfskraftlenkung
DE950431C (de) Stufenloses Fluessigkeitsgetriebe, insbesondere fuer Fahrzeuge, wie Fahrraeder, Motorraeder u. dgl. oder Kraftwagen
WO1987004761A1 (fr) Pompe a piston avec disque oscillant ou excentrique

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AU BR CA HU JP KR RU US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN ML MR SN TD TG

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)

Free format text: EUROPEAN PATENT(AT,BE,DE,DK,FR,GB,IE,IT,LU,MC,NL,PT,SE)

NENP Non-entry into the national phase

Ref country code: CA