Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
  • B60K23/02—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for main transmission clutches
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D25/00—Fluid-actuated clutches
  • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D25/00—Fluid-actuated clutches
  • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
  • F16D2025/081—Hydraulic devices that initiate movement of pistons in secondary cylinders for actuating clutches, i.e. primary cylinders

Definitions

• the present invention relates to an arrangement for pressurizing a hydraulic system, in particular a hydraulic system for actuating a clutch in the drive train of a motor vehicle, comprising an actuating means which is mechanically connected to a hydraulic master cylinder.
• the present invention further relates to a master cylinder.
• the clutch pedal In a hydraulic clutch actuation in a motor vehicle, the clutch pedal is generally connected by means of a piston rod directly to the piston of the master cylinder. This results depending on Schwenkwinkei the pedal a nearly constant translation.
• the US 2,315,632 discloses a variable pedal ratio, in which a roller attached to the pedal rolls on a link plate. On the link disk, the piston rod of a hydraulic cylinder is attached.
• a disadvantage of this arrangement is that the entire pedal force must be transmitted through a single role. This results in high stresses in the role and the slide track.
• this mechanism is designed as a separate component and not integrated into the master cylinder. From WO 87/03344 a master cylinder is known, which is integrated in a pedal. When pressing the pedal rolls while a role that is attached to the piston rod, on a curved path.
• the disadvantage here is that an oblique force is exerted on the piston rod, which generates a large frictional force on the lateral guide.
• the object of the present invention is to provide an arrangement for pressurizing a hydraulic system, which provides a variable ratio while avoiding the disadvantages of the prior art.
• an arrangement for pressurizing a hydraulic system in particular a hydraulic system for actuating a clutch in a drive train of a motor vehicle, comprising an actuating means which is mechanically connected to a hydraulic master cylinder, wherein the hydraulic master cylinder comprises at least two pressure generating units are connected to the same hydraulic output of the hydraulic pressure generating unit.
• a hydraulic pressure is generated or hydraulic fluid is forced out of the master cylinder into a downstream hydraulic system in which a slave cylinder is usually arranged.
• the pressure generating units are a first hydraulic cylinder with a first master cylinder piston and a second hydraulic cylinder with a second master cylinder piston.
• the first hydraulic cylinder and the second hydraulic cylinder preferably act on a common pressure chamber.
• the first master cylinder piston is preferably connected via a transmission means with the actuating means.
• the transmission means is preferably a push rod which is pivotally connected to the actuating means and / or the first master cylinder piston.
• the second master cylinder piston is preferably coupled via a gear arrangement with the actuating means.
• the gear arrangement preferably comprises a coupling gear, which preferably comprises a lever, which is arranged with a rotary joint between the second master cylinder piston and a pivot point of the actuating means.
• the articulation point is preferably a roller assigned to the actuating means.
• the lever preferably has a link on its side facing the articulation point.
• the role of the articulation point sweeps over the guide in a deflection of the actuating means and thus turns the lever.
• the scenery is preferably arranged on a link module, which is firmly connected to the lever.
• Lever and link module are made separately and then connected together, for example, welded together or bolted.
• the lever preferably has a crank, which makes it possible to arrange the fulcrum on a directly connected to the master cylinder housing flange.
• a master cylinder comprising a first master cylinder piston and a second master cylinder piston, which act on a common pressure chamber.
• the first master cylinder piston and the second master cylinder piston are arranged approximately at right angles to each other.
• FIG. 1 shows an embodiment of a pedal / master cylinder arrangement according to the invention in a first pedal position.
• FIG. 2 shows the pedal / master cylinder arrangement according to FIG. 1 in a second pedal position
• Fig. 4 shows another embodiment of a master cylinder according to the invention together with lever.
• FIG. 1 shows a pedal / master cylinder assembly 1 with a hydraulic master cylinder 2.
• the hydraulic master cylinder 2 comprises a first master cylinder 3 and a second master cylinder 4, which are arranged approximately at right angles to each other.
• the first hydraulic cylinder 3 and second hydraulic cylinder 4 act together on a common pressure chamber 5.
• the first hydraulic cylinder 3 comprises a first master cylinder piston 6, the piston crown side with a joint 7 and designed as a push rod mechanical transmission 8 via a pedal attachment 9 with a foot pedal 10 as the actuating means connected is.
• the foot pedal is rotatably mounted about a body-mounted pedal pivot 17.
• the pedal attachment 9 may for example be designed in the form of a ball head, so that the mechanical transmission 8 is rotatably connected to the pedal attachment 9 as a fulcrum with the foot pedal 10.
• the first hydraulic cylinder 3 is arranged approximately at right angles to the foot pedal 10
• the second hydraulic cylinder 4 extends approximately at right angles to the first hydraulic cylinder 3 in a plane spanned by the first master cylinder 3 and the foot pedal.
• the pressure chamber 5 is, for example, via a arranged on the first piston 6 not shown here sniffing groove or bore with a follow-up space 33 which is connected via a follow-up line 18 with a follower tank, not shown.
• the pressure chamber 5 is connected to a hydraulic output 19, which is a hydraulic connection via a pressure line, not shown, to a non-illustrated hydraulic slave cylinder of a hydraulic system, e.g. forms for actuating a clutch in the drive train of a motor vehicle.
• the second hydraulic cylinder 4 comprises a second master cylinder piston 11, which is also referred to as an auxiliary piston.
• the second master cylinder piston 11 acts on the same pressure chamber 9 as the first master cylinder piston 6.
• the second master cylinder piston 11 is actuated by a lever 12 which at a fulcrum 13, for example, the body or directly on the master cylinder, for example by means of a receptacle provided on this can be arranged, is rotatably mounted.
• the lever 12 comprises a shell-like recess 22 which engages around an actuating cam 15 of the second master cylinder piston 11 and thus forms a ball joint for transmitting a compressive force between the lever 12 and the second master cylinder piston 11.
• the second master cylinder piston 11 Upon rotation of the lever 12, the second master cylinder piston 11 is moved in this way.
• On the shell-like recess 14 side facing away from the lever 12, a link 15 is arranged, which cooperates with a roller 16 of the foot pedal 10.
• the lever 12 forms with its link 15 in cooperation with the roller 16 a gear arrangement which transmits the pedal travel with variable ratio to the second master cylinder piston 11.
• the gear arrangement here is a planar coupling mechanism.
• the pedal attachment 9 Upon rotation of the foot pedal 10 about the pedal pivot point 17, the pedal attachment 9 is displaced on a circular path about the pedal pivot point 17, so that via the mechanical transmission 8 of the first master cylinder piston 6 is moved. If, for example, the foot pedal is displaced on a pedal surface 20 in the direction of an arrow 21, for example by foot operation of a driver of a vehicle, the first master cylinder piston 6 is displaced in the direction of the pressure chamber 5. At the same time, the roller 16 also moves in a circular path about the pedal pivot point 17.
• the lever 12 is fastened in the shown embodiment body-fixed to the fulcrum 13, thereby pushing the roller 16 via the gate 15 upon rotation of the foot pedal 10 thereby performs a rotational movement about the fulcrum 13 and presses on the second Geberzyiinderkolben 11th
• the path of the first master cylinder piston 6 is essentially determined by the distance between the pedal attachment 9 to the pedal pivot 17 and the angular relationship between the straight line through the pedal pivot 17 and the pedal attachment 9 and a second straight line through the pedal attachment 9 and the joint 7.
• FIG. 1 shows the pedal / master cylinder arrangement in a first position of the foot pedal 10
• FIG. 2 shows a foot pedal 10 actuated by a distance x1, as can be seen.
• the roller 16 moves along the guide 15, thereby deflecting the lever 12 off.
• the second master cylinder piston 11 is compressed.
• Fig. 3 shows an example of a pedal force via the pedal travel.
• the sizes of the pedal force in N or the pedal travel in mm are only to be understood to clarify the relation between the pedal force curve according to the invention and the pedal force curve according to the prior art.
• Plotted in Fig. 3 is the pedal force in Newtons over the pedal travel in mm.
• the hydraulic master cylinder 2 is connected via a slave cylinder, not shown, with a vehicle clutch.
• the vehicle clutch generates an opposing force via the slave cylinder depending on the actuation path.
• the force curve is also dependent on the coupling used.
• a force curve A according to the prior art and a force curve B with a pedal / master cylinder arrangement 1 according to the invention are shown in FIG. 3.
• the pedal force curve A according to the prior art has a pronounced maximum. This can be changed by a pedal / master cylinder assembly 1 according to the invention to a flatter course according to the curve B.
• the first master cylinder piston 6 is sealed by means of a primary seal 23 and a secondary seal 24 with respect to a follow-up conduit 18 connected to the follower space or the environment.
• the primary seal 23 seals the common pressure chamber 5 with respect to the overflow chamber which is connected to the overflow line 18.
• sniffer position this is the fully unloaded position, in which therefore the first master cylinder piston 6 is in as far as possible pulled out of the pressure chamber 5 end position, Schnüffelnute, sniffing hole or the like are released, the connection between the common pressure chamber 5 and the make with the caster line 18 connected overflow space 33.
• the secondary seal 24 ensures a sealing of the follow-up space 33 and the pressure chamber 5 with respect to the environment.
• the secondary seal 24 is arranged in a cup-shaped front part 25 of a piston carrier 26.
• the piston carrier comprises an annular groove 27, in which a sealing ring 28 is arranged to seal against the master cylinder housing 29.
• the piston carrier 26 may for example be pressed or glued to the master cylinder housing 29 or fastened by means of a bayonet connection.
• the piston carrier 26 is covered in the direction of the foot pedal 10 by a cover 30. In the axial direction in the direction of the pressure chamber 5, the piston carrier 26 presses a spacer 31, which is substantially annular, on the primary seal 23.
• the primary seal 3 is pressed in a seal seat 32, which is essentially a stepped bore with a diameter greater than that Diameter of the pressure chamber 5 is.
• the bore of the spacer element 31 or the piston carrier 26 in the master cylinder housing 29 has a slightly larger diameter than the bore for the primary seal 23.
• the second master cylinder piston (auxiliary piston) 11 has a cylindrical base body 34, which has a movable seat (play-bearing seat) with a bore forming the second master cylinder 4.
• the cylindrical base body 34 has a cross-sectionally T-shaped front part 35, which carries a sealing ring 35.
• the sealing ring 35 is positively connected by the T-shaped front part 35 with the second master cylinder 11 and seals the pressure chamber 5 from the environment.
• Seal ring 36 may be, for example, a rubber ring or a rubberized steel ring or the like.
• the actuating cam 14 is arranged, which is actuated via the shell-like recess 22 of the lever 12.
• the lever 12 has a crank 37 on the foot pedal 10 facing side of the fulcrum 13. Due to the offset 37, which is inclined substantially in relation to the plane formed by the mechanical transmission 8 in FIG. 4, the distance a between a slide receptacle 38 and the mechanical transmission 8 is increased, so that the fulcrum 13 thereby closer to the master cylinder housing 29 can be moved.
• the fulcrum 13 is mounted for example as a shaft or the like on a flange 39 of the master cylinder housing 29.
• the gate 15 is arranged on a separate from the lever 12 independent module 40.
• the link module 40 is connected to the lever 12 cohesively, positively or the like, ie, for example, screwed, welded, or the like.
• the gate module 40 is made separately from the lever 12, since in this way 40 different requirements can be effected on the characteristics of the hydraulic master cylinder for various applications by replacing the link module.
• FIG. 4 While other components of the illustration of FIG. 4 remain the same, by simply replacing the link module 40 and another gate 15 introduced therein, ie a different surface shape, a different hydraulic characteristic is obtained, this being the relationship between the pedal travel X according to FIG and 2 and the measurable at the hydraulic output 19 pressure and flow, causes.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Actuator (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=38269503

Family Applications (1)

Country Status (5)

Families Citing this family (4)

Family Cites Families (4)

• 2007
  • 2007-02-15 EP EP07711193A patent/EP1996426A1/de not_active Withdrawn
  • 2007-02-15 WO PCT/DE2007/000290 patent/WO2007104277A1/de not_active Ceased
  • 2007-02-15 BR BRPI0708674-1A patent/BRPI0708674A2/pt not_active Application Discontinuation
  • 2007-02-15 CN CNA2007800087041A patent/CN101400540A/zh active Pending
  • 2007-02-15 DE DE112007000402T patent/DE112007000402A5/de not_active Withdrawn

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events