Classifications

• • 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
  • F16D48/00—External control of clutches
  • F16D48/02—Control by fluid pressure
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
  • B29C45/16—Making multilayered or multicoloured articles
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
  • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
  • F15B13/027—Check valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
  • F15B21/008—Reduction of noise or vibration
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
• • 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
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
• • 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
  • F16D25/088—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members being distinctly separate from the axis of rotation
• • 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
  • F16D25/12—Details not specific to one of the before-mentioned types
• • 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
  • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
  • F16L37/00—Couplings of the quick-acting type
  • F16L37/08—Couplings of the quick-acting type in which the connection between abutting or axially overlapping ends is maintained by locking members
• • 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
  • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
  • F16L37/00—Couplings of the quick-acting type
  • F16L37/08—Couplings of the quick-acting type in which the connection between abutting or axially overlapping ends is maintained by locking members
  • F16L37/12—Couplings of the quick-acting type in which the connection between abutting or axially overlapping ends is maintained by locking members using hooks, pawls, or other movable or insertable locking members
  • F16L37/14—Joints secured by inserting between mating surfaces an element, e.g. a piece of wire, a pin, a chain
  • F16L37/142—Joints secured by inserting between mating surfaces an element, e.g. a piece of wire, a pin, a chain where the securing element is inserted tangentially
  • F16L37/144—Joints secured by inserting between mating surfaces an element, e.g. a piece of wire, a pin, a chain where the securing element is inserted tangentially the securing element being U-shaped
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29L—INDEXING SCHEME ASSOCIATED WITH SUBCLASS B29C, RELATING TO PARTICULAR ARTICLES
  • B29L2031/00—Other particular articles
  • B29L2031/24—Pipe joints or couplings
• • 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
• • 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
  • F16D48/00—External control of clutches
  • F16D48/02—Control by fluid pressure
  • F16D2048/0215—Control by fluid pressure for damping of pulsations within the fluid system
• • 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
  • F16D48/00—External control of clutches
  • F16D48/02—Control by fluid pressure
  • F16D2048/0224—Details of conduits, connectors or the adaptors therefor specially adapted for clutch control

Definitions

• the present invention relates to a hydraulic system; in particular for motor vehicles; comprising a master cylinder, a slave cylinder, a damping device and a pressure medium line connecting them.
• a generic hydraulic system is known from DE 101 06 958 A1.
• Such hydraulic systems are used in particular in motor vehicles as a device for actuating brakes, as a steering aid and as a device for actuating friction clutches, for example in the power flow between an internal combustion engine and a transmission, or an electric machine and a drive train.
• a disadvantage of a hydraulic system according to the prior art is the high manufacturing effort.
• the present invention is therefore based on the problem of providing a hydraulic system which is simpler and less expensive to produce.
• the hydraulic system comprises at least one hydraulic plug connection with a plug and a socket and that the plug have an abutment and a sealing element, which consist of different materials and are integrally connected to one another.
• An abutment is understood here to mean a part of the plug that can be at least partially inserted into a corresponding socket.
• the abutment itself has no sealing function, but rather serves to transmit mechanical forces, for example buckling forces or the like, between the plug and the socket by means of an essentially positive connection with the socket.
• the actual sealing function is performed by the sealing element.
• the abutment and sealing element are made of different materials, the different materials being cohesively connected.
• the plug is preferably produced by injection molding from a plastic, the abutment and the sealing element consisting of another material being produced in one or two successive work steps. This can be done in one and the same injection mold or in different injection molds.
• a positive connection between the abutment and the sealing element can be provided.
• the positive connection can, for. B. by a partial penetration of the different materials in the form of bulges and pockets or by a tongue and groove design.
• the abutment is preferably made of an injection-moldable plastic, for example an elastomer.
• the sealing element is preferably made of a thermoplastic elastomer, a liquid silicone rubber or a general elastomer or a combination of these materials. Such plastics have optimal material properties with regard to their elasticity and surface quality for producing a tight connection.
• An outer bead is preferably formed on the sealing element.
• the bead is dimensioned so that its outer circumference is larger than the inner circumference of the corresponding part of the socket. In this way, the outer bead of the sealing element, when connected to the plug element, exerts a surface pressure on parts of the inner surface of the plug element, so that a sealing connection is established.
• An inner bead can also be molded onto the sealing element. This is used for the sealing connection of the plug with a hydraulic line inserted into it.
• the inner diameter of the inner bead is smaller than the outer diameter the hydraulic line.
• Both the inner and the outer bead are arranged essentially rotationally symmetrically over the entire circumference of the sealing element.
• the plug comprises an annular groove into which a clamping spring can engage, a non-positive and / or positive connection between the plug and a socket being able to be established by means of the clamping spring.
• the clamping spring is usually attached to the socket, for example in a groove or in one or more holes.
• the connection between the plug and the socket is made by simply pushing the plug into the socket.
• the connection can be released, for example, by pulling the clamping spring out of the socket.
• a non-circumferential groove can be provided in the plug, so that the clamping spring is pressed outward by axially rotating the plug, thus enabling the connection between plug and socket to be released.
• the abutment and the sealing element are made of differently colored materials. This measure enables different designs of the connector to be identified, for example the identification of different connector diameters or different test pressures or different seal designs.
• the hydraulic system comprises at least one hydraulic plug connection with a plug and a socket and that the plug connection has an arrangement of a clamping spring and at least one groove for the positive and / or form-fitting connection between the plug and the socket comprises and that the clamping spring is corrugated and / or bent.
• the clamping spring is consequently not flat in the side view, but bent in the manner of an angle, a semicircle or a wave shape.
• the clamping spring lies in the groove in the installed position when the plug connection is made between the plug and socket so that the plug is fixed without play in the axial direction.
• the groove is preferably an annular groove.
• the groove can also consist of individual grooves, which are attached, for example, on opposite sides of the plug. An annular groove is easier to produce than individually made grooves.
• the height of the annular groove is preferably greater than the height of the clamping spring, so that the clamping spring lies in the groove under axial tension. This means that the clamping spring, if it were flat and not bent according to the invention, would be fixed in the groove with a clear play. Due to the corrugated or arcuate design of the clamping spring, it lies below in the installed position
• the clamping spring creates an axially backlash-free connection between the plug and socket.
• the hydraulic system comprises at least one hydraulic plug connection with a plug and a socket, the plug connection being an arrangement of a clamping spring and at least one groove for the non-positive and / or positive connection between the plug and of the socket, and that a spring element is arranged between an end face of the plug and a bottom surface of the socket.
• the spring element presses the plug and the socket apart in the axial direction against the movement of the clamping spring. In this way, an essentially backlash-free connection between the socket and the plug can be established.
• the spring element is preferably a corrugated washer.
• a corrugated washer is particularly easy to manufacture and particularly easy to handle when establishing the connection between the plug and socket.
• the two initially alternative embodiments of the hydraulic plug connection can also be used in combination, in that both the clamping tongue and groove and the spring element are designed in accordance with the present invention.
• a hydraulic system which comprises a damping device and in which the damping device comprises a hose mandrel for connection to the pressure medium line.
• the damping device With the help of the hose dome, the damping device can be connected directly to the pressure medium line. This measure also reduces the installation space required for the damping device.
• the mandrel is located on the damping device in place of one of the connectors.
• the hose mandrel is preferably connected in one piece to the damping device.
• the hose mandrel can be connected in one piece to a housing element of the damping device.
• Hose mandrel can be manufactured together with the housing element in one operation, for example.
• a welded connection is an example of a one-piece connection.
• the hose mandrel can be cast in one piece with a housing part of the damping device.
• the hose mandrel is detachably connected to the damping device.
• the hose mandrel can be screwed to the damping device or have a connection in the manner of a bayonet lock.
• a hydraulic system in that the hydraulic system comprises a damping device and in that the damping device comprises a switchable diaphragm.
• a switchable orifice means here that it is only effective in one direction of flow.
• the function of a diaphragm that acts only in one direction as an independent component and the function of the Damping device are combined in this way in one component.
• the manufacturing costs can be reduced compared to two individual components.
• the damping device comprises both a first and a second valve.
• the first valve opens when the damping device flows through from the master cylinder side to the slave cylinder side and the second valve opens when the damping device flows through from the slave cylinder side to the master cylinder side.
• the switchable orifice is preferably arranged such that it flows through from the slave cylinder side to the master cylinder side when the damping device flows through it.
• the switchable orifice is preferably arranged behind the second valve when the damping device flows through from the slave cylinder side to the master cylinder side.
• valves are formed from passage openings and at least one hose sleeve, the hose sleeve being able to close the passage openings in one flow direction and open in the other flow direction.
• the damping device preferably comprises both a first and a second housing part, the second housing part having a valve section with a first channel and a second channel.
• the essential functional elements of the damping device are integrated in the second housing part in this way, so that complex production is only necessary for the second housing part and the first housing part is a comparatively simple housing component.
• the hose cuff comprises a
• other sealants such. B. a separate seal between the housing parts is omitted, so that the assembly of the damping device is simplified.
• the hydraulic system comprises a pressure line connection with means for venting the hydraulic actuation system, and that the pressure line connection has an axially rotatable sleeve with a first vent hole, which together with at least a closable valve forms a second vent hole.
• the hydraulic actuation system can now be vented by means of the lockable valve.
• no further valves are required in the hydraulic actuation system for ventilation.
• the valve located directly on the pressure line connection is easily accessible in the installed position.
• a second vent hole is made in a hollow spigot, a hose seal with a third vent hole is arranged on the spigot, the second and the third vent hole being arranged approximately axially to one another and a rotatable sleeve on the hose seal a first vent hole is arranged, the first vent hole being in a first position of the rotatable sleeve approximately axially to the second vent hole and in a second position outside an overlap area of the second vent hole.
• Both the hose seal and the sleeve designed as a plastic ring are commercially available components.
• the breather can be opened or closed by rotating the sleeve around the longitudinal axis by 180 °, which is ensured by an anti-rotation device with an end stop. Possible leakage is prevented by applying a bead around the vent hole on the adapter plug. Twisting of the hose seal is prevented by applying the tenon and groove in the respective parts. The possible twisting and / or slipping of the plastic ring is prevented by attaching one Snap-in function on the adapter plug and simultaneous clamping protection achieved by wire form spring.
• the first position of the cuff is preferably moved into the second position by axial rotation of the cuff.
• a displacement of the sleeve in the axial direction would also be possible here.
• the cuff is preferably in by means of a detent spring on the pin
• the cuff is preferably locked in the closed rotational position.
• latching definition it is meant here that an initial resistance must first be overcome in order to twist the cuff. This measure prevents unintentional opening of the vent valve and, at the same time, indicates that the closed position has been reached by means of the latching function. In addition, this measure prevents unwanted opening during operation, for example due to vibrations or the like.
• the problem mentioned at the outset is also solved by a hydraulic system in which it is provided that the hydraulic system comprises a pressure line connection and that at least parts of the pressure line connection have been produced by means of a gas or fluid injection method.
• This measure also makes it possible to produce curved or curved molded parts.
• the pressure line connection comprises at least one plug and / or a socket, the cavity of which has been produced by means of a mold core. In this way, the shape accuracy and surface quality of the plugs or sockets can be improved.
• F Fiigg .. 2 2 is a schematic diagram of a hydraulic connector in longitudinal section
• FIG. 3 shows a longitudinal section through a first embodiment of a plug according to the invention
• FIG. 4 shows a longitudinal section through a second embodiment of a connector according to the invention
• FIG. 5 5 shows a longitudinal section through a third embodiment of a connector according to the invention
• FIG. 7 shows a clamping spring for use in an arrangement according to FIG. 6,
• FIG. 8 8 shows a second fastening arrangement of a hydraulic plug connection
• FIG. 11 is an exploded view of a pressure line connection according to the invention.
• FIG. 12 a top view of a pressure connection according to the invention according to FIG. 11, FIG. 1 133 a section according to A-A in FIG. 12 in a first position,
• FIG. 14 shows a section according to A-A in FIG. 12 in a second position
• FIG. 15 shows a section through a first embodiment of a pressure line connection according to the invention
• Fig. 16 is a partial section through a second embodiment of an inventive
• Fig. 1 shows a schematic representation of a possible embodiment of a hydraulic system with a pressure relief valve 90 using a clutch release device 91 with a master cylinder 92 and a slave cylinder 93.
• the pressure relief valve 90 is built into the line parts 99 and 100 and does not separate them open state from each other.
• the pressure limiting valve 90 can be integrated in the master cylinder 92 or in the slave cylinder 93 and can be integrated in a functional component in other hydraulic systems, for example brake systems, power steering systems and the like.
• a pressure relief valve according to the invention can be advantageously used in each hydraulic line system as a pressure relief valve and / or as a vibration filter, for example as a so-called “prickle filter”.
• the clutch release system 91 actuates the clutch 95 hydraulically by acting on the master cylinder 92 by means of an actuating element 102, which can be a foot pedal, an actuator, for example an electric actuator, or the like.
• an actuating element 102 which can be a foot pedal, an actuator, for example an electric actuator, or the like.
• pressure is built up in the master cylinder 92 by means of a mechanical transmission 101, which builds up a pressure in the slave cylinder 93 via the line line 100, via the pressure limiting valve 90 and the power line 99.
• the slave cylinder 93 can, as in the example shown, be arranged concentrically around the transmission input shaft 98 and be axially supported on a transmission housing (not shown) and apply the necessary release force via a release bearing on the clutch 95 or on its release elements, such as a plate spring.
• exemplary embodiments can provide a slave cylinder 93, which actuates a releaser via a disengaging mechanism and is arranged outside the clutch bell, said axially acting on the disengaging mechanism by means of a piston which is hydraulically connected to the master cylinder and is accommodated in the slave cylinder housing.
• the slave cylinder is attached to the transmission housing, which is not shown here, or to another component fixed to the housing. With the clutch 95 closed, the transmission input shaft 98 does not transmit the torque of the internal combustion engine 96 to Gearbox shown in detail and then on the drive wheels
• the crankshaft 97 experiences, depending on the design of the internal combustion engine 96, for example depending on the number of cylinders, non-uniform loads which are expressed in axial and / or wobble vibrations and which are transmitted to the slave cylinder via the disengaging mechanism 94 93, the line system 99, 100 are transmitted to the master cylinder 92 and from there via the mechanical connection 101 to the actuator 102.
• these vibrations are perceived as unpleasant.
• an actuator as actuator 102 for example, a reduced control accuracy or a shortened service life can be the result of the vibrations.
• the pressure relief valve 90 is therefore switched on for damping in the lines 99, 100 and tuned for damping the vibrations entered by the crankshaft 97.
• the frequency range of such vibrations is typically 50 to 200 Hz.
• Fig. 2 shows a longitudinal section through a hydraulic connector 1, which comprises a plug 2 and a socket 3.
• Fig. 2 is used first to explain the purpose and interaction of the plug and socket.
• Both the plug 2 and the socket 3 are each connected to pressure medium lines 99, 100, not shown in FIG. 2, according to FIG. 1.
• the plug 2 has a circumferential annular groove 4 into which a clamping spring 6, which is introduced into a recess 5, engages in the installed position.
• FIG. 3 shows a longitudinal section with a first embodiment of a plug 2 according to the invention.
• This consists of an abutment 7 and a sealing element 8 arranged on the end face of the abutment 7.
• Both the abutment 7 and the sealing element 8 are made of a plastic, but from a different plastics in each case.
• the abutment 7 can consist of any plastic of sufficient strength, preferably of a thermoplastic, so that the component can be injection molded or the like. driving is manufacturable.
• the sealing element preferably consists of thermoplastic elastomer (TPE), liquid silicone rubber (LSR) or any other elastomer.
• the plug 2 is preferably produced by injection molding, the abutment 7 and the sealing element 8 consisting of a different material being produced in one or two successive work steps. This can be done in one and the same injection mold or in different injection molds. Two different plastics are thus introduced into the injection mold at the same time or in succession, the different plastics being introduced in such a way that the abutment 7 is produced from one plastic, the sealing element 8 from the other plastic. Abutment 7 and sealing element 8 are integrally connected to one another at their contact point.
• Fig. 4 shows a further embodiment of a connector 2 according to the invention, in which the connection between the abutment 7 and the sealing element 8 is made material and form-fitting.
• an annular extension 9 is formed on the end face of the abutment 7, on which a sealing element 8 provided with a corresponding bead 10 is arranged.
• the sealing element 8 and the abutment 7 can be produced, for example, as separate plastic parts and only afterwards e.g. can be connected to each other with an adhesive connection or latching snap connections.
• the connector 2 corresponding to the embodiment according to FIG. 4 similar to that described with reference to the embodiment of FIG. 3, can be produced in one or more work steps from different plastics.
• the abutment 7 can first be produced in an injection mold and its end face can be provided with the sealing element 8 made of a different plastic in another injection mold.
• the sealing element 8 is provided with an outer circumferential bead 10, which serves to seal the plug 2 with respect to the socket 3.
• an inner bead 11 can be arranged on the inside of the sealing element 8. This serves to seal the connector 2 against a hydraulic pipe 12 of a pressure medium line 99 or 100 according to FIG. 1, which is inserted into the connector 2.
• FIG. 5 shows a modified embodiment of the plug connection corresponding to FIG. 4.
• both the annular extension 9 and the associated sealing element 8 are provided with a circumferential bevel 13 for easier assembly.
• the plastic of the sealing element 8 can have a different color than the plastic of the abutment 7.
• the different colors can be used to identify the connector 2, for example.
• the abutment is preferably produced by injection molding, in which the abutment 7 has different physical and chemical properties than the sealing element 8.
• different plastics are chosen for the abutment 7 and the sealing element 8 in the present exemplary embodiment.
• Fig. 6 shows a schematic diagram of a hydraulic connector in partial section.
• the fastening arrangement roughly corresponds to the illustration in FIG. 2. Identical components are therefore identified identically.
• a plug 2 is detachably connected to a socket 3.
• a clamping spring 6 engages in an annular groove 4 of the plug 2.
• the ring groove can alternatively also be designed as a groove-like incision or in the form of two opposite individual grooves.
• the clamping spring 6 can be introduced into the socket 3 by means of a recess 5 or can be introduced into the socket 3 via a through hole (not shown here).
• the plug 2 is inserted axially into the socket 3.
• the clamping spring 6 Due to the essentially conical outer shape of the plug 2, the clamping spring 6 is pressed outwards and can snap into the annular groove 4 as soon as the plug 2 has been inserted far enough into the socket 3. In this way, there is a positive and / or non-positive connection of the plug 2 to the socket 3.
• An O-ring 14 is arranged in an O-ring groove 15 of the plug 2 and is in the installation position shown in FIG Inner wall of the socket 3, in which the plug connection is made sealing.
• the height D4 of the The annular groove 4 is larger than the height D6 of the clamping spring 6.
• the clamping spring 6 shown in a side view in FIG. 7 is angled.
• FIG. 8 shows an alternative embodiment of the plug connection according to the invention.
• a corrugated spring 18 is arranged between an end face 16 of the plug 2 and a bottom face 17 of the socket 3.
• 8 shows the sealingly produced hydraulic plug connection 1 between the plug 2 and the socket 3.
• FIG. 9 shows a damping device 20, a so-called prickle filter, which can be arranged in hydraulic systems for damping undesirable pressure fluctuations in a hydraulic line.
• the damping device 20 is provided with a plug connection 21 for connection to a clutch (not shown), for example a central clutch release, of a vehicle clutch.
• a hose mandrel 22 is flanged onto the side of the damping device 20 opposite the plug connection 21.
• a hose 23 can be attached to the hose mandrel 22 with the aid of a hose socket 24.
• the hose socket 24 is provided in a known manner with a press point 26, so that a frictional connection between the hose mandrel 22 and the hose 23 can be established.
• the hose mandrel 22 is connected in one piece to the damping device 20, for example by a welded connection, or in that the housing of the damping device and the hose mandrel 22 is manufactured in one piece, for example by casting, turning, forging or the like.
• the hose mandrel 22 can be detachably connected to the damping device 20, for example by a screw connection.
• a damping device 20 also referred to as a tingling filter, which can be inserted as an additional component in a pressure medium line 99, 100, which is not shown in more detail here.
• a plug 31 can be designed both according to the prior art and in one of the embodiments described above with reference to FIGS. 2 to 7.
• the plug socket 32 can correspond to the socket explained above with reference to FIGS. 2 to 7
• the plug 31 is connected to a slave cylinder 93, not shown here.
• the socket 32 is connected to a master cylinder 92, not shown here.
• the damping device 20 comprises a first housing part 33 and a second housing part 34.
• the two housing parts 33, 34 are sealed against one another in a pressure-tight manner by means of a sealing ring 35.
• the second housing part 34 comprises a valve section 36 located within the first housing part 33. This comprises a first channel 37 which opens into an annular space 39 between the first housing part 33 and the second housing part 34 via a first passage opening 38.
• a second channel 40 is composed of a first area 40a and a second area 40b.
• the second region 40b extends essentially radially in the circumferential direction between the first and the second housing parts 33, 34 and forms an annular space there.
• the first and second regions 40a, 40b are connected to one another by a second passage opening 41.
• An aperture 42 establishes a connection between the second region of the second channel 40b and the first channel 37.
• the valve section 36 is surrounded by a hose cuff 43 which, together with the first passage opening 38 and the second passage opening 41, forms a valve which is only permeable in one direction.
• the hose sleeve 43 comprises a circumferential sealing bead 44 with which the second region of the second channel 40b is sealed off from the annular space 39.
• the first passage opening 38 forms a first valve 45 with the hose sleeve 43.
• the second passage opening 41 accordingly forms a second valve 46 with the hose sleeve 43.
• the flow from the slave cylinder 93 to the master cylinder 92 takes place via the annular space 39, the first region of the second channel 40a and the second valve 46 into the second region of the second channel 40b.
• the hydraulic fluid can then continue to flow through the orifice 42 into the first channel 37.
• An additional flow resistance which only acts in one flow direction, can thus be installed in the damping device 20 via the orifice 42.
• a plurality of first passage openings 38 and a plurality of second passage openings 41 can also be distributed over the circumference of the damping device 20, so that a plurality of valves are formed here.
• the diameter and shape of the passage openings as throttling channels are adapted to the throttling conditions and damping requirements.
• the hose sleeve 43 is made of an elastic plastic or rubber material.
• the hose cuff 43 can be reinforced in sections, constructed in multiple layers or in multiple layers. Reinforcement can be carried out, for example, with a fabric, with rings or spirals made of plastic or metal.
• the hose section 43 is preferably pulled onto the valve section 36 under prestress.
• FIGS. 12 and 13 show a top view and side view of a pressure line connection 50 according to the invention.
• the pressure line connection 50 comprises a first connector 51 and a second connector 52.
• the pressure line connection 50 is at an angle angled from about 90 °.
• the pressure connection 50 is hollow overall and forms an interior 68 so that hydraulic fluid or the like can flow through it.
• a hose seal 54 with a vent hole 55 is pushed over a pin 53.
• the hose seal 54 is provided with a groove-like recess 56 which can engage in a spring-like projection 57 and prevent rotation of the hose seal 54 relative to the pin 53 in the installed position.
• a sleeve 58 is slid over the hose seal 54 and is rotatably mounted on the hose seal 54 or the pin 53.
• the sleeve 58 is axially fixed on the pin 53 by a detent spring 59 which can be inserted into a recess 60 of the sleeve 58 and which engages in an installed position in an annular groove 61 of the pin 53.
• the sleeve 58 is in the installed position despite being axially fixed on this pin 53 arranged radially rotatable.
• On the cuff 58 is a
• Hose connection 62 is arranged, which is provided with a closure cap 63a.
• the hose connection 62 comprises a vent hole 67, which can be brought into alignment with the vent hole 55 of the hose seal 54 in a rotational position of the sleeve 58.
• a vent hole 64 is made in the pin 53 and is aligned with the vent hole 55 of the hose seal 54 in the installed position of the hose seal 54.
• a strap 65 is arranged on the pressure line connection 50, with which the pressure line connection 50 can be fastened to the clutch bell of a vehicle engine, not shown.
• a web 66 in the installation eye of the pressure line connection 50 covers a breakthrough made in the clutch bell (not shown here) for the passage of the pressure line connection 50 in a sealing manner.
• FIGS. 13 and 14 The function of the pressure line connection according to the invention is shown in FIGS. 13 and 14.
• FIG. 13 shows a section according to A-A in FIG. 12.
• a closed position of the pressure line connection is shown here.
• the ventilation hole 67 of the hose connection 62 is rotated axially by 180 ° with respect to the ventilation hole 55 of the hose seal 54 or the ventilation hole 64 of the pin 53. Therefore, no hydraulic fluid can escape from the interior 68 through the vent hole 67.
• a second vent hole 64 is made in the hollow pin 53.
• a hose seal 54 with a third vent hole 55 is arranged on the pin 53, the second vent hole 64 and the third vent hole 55 being arranged approximately axially to one another and a rotatable sleeve on the hose seal 54 is arranged with a first vent hole 67, wherein the first vent hole
• 67 lies in a first position of the rotatable sleeve 58 approximately axially to the second vent hole 64 and in a second position outside of an overlap area of the second vent hole 64.
• FIG. 15 shows a pressure line connection 70 which is provided with a plug 71 and two plug sockets 72.
• the pressure line connection is used to connect a hydraulic line, not shown here, for example to a hydraulic central release system of a motor vehicle.
• the pressure line connection 70 is hollow over its entire length. This is identified in FIG. 15 as cavity 73.
• a fluid for example a hydraulic fluid, flows through the pressure line connection.
• Pressure line connections like other housing parts, often contain long and thin hollow areas. Components of this type are generally produced by means of plastic injection molding. According to the prior art, cores within the injection mold are used to produce cavities. In the case of long and thin cavities, correspondingly long and thin cores must be used, which have low mechanical stability and the risk of deformation. In addition, heat dissipation is problematic with such cores. To allow demolding, the cores are designed with a straight core axis. The use of such cores limits the design options for the pressure line connection.
• the pressure line connection 70 is a comparatively long and slender component with an elongated cavity 73.
• a very long and thin core is usually to be attached in an injection mold or the like .
• the cavity is produced directly by blowing in a gas or a liquid.
• This gas or fluid injection method is such that a balloon-like plastic film is pressed into a negative form of the pressure line connection 70 by means of one or more spray nozzles.
• the balloon-like plastic film lies on the inside of the negative mold and fills out the bulges, as is the case with the present pressure line connection 70, for example a circumferential fastening web 74.
• the inner surface is essentially smooth with a relatively high roughness. This is designated as free surface 75 in FIG. 15. Areas in which more complicated surface shapes are to be produced, for example the area of the plug 71 or that of the sockets 72, are produced with mold cores 76, 77. As an example, only a first mold core 76 for producing the sockets 72 and a second mold core 77 for producing the plug 71 are shown here.
• FIG. 16 shows a clearly curved pressure line connection 80, which has a curvature 81 greater than 90 °.
• a first essentially straight region 82 and a second substantially straight region 83 are connected to the curvature 81.
• a hole had to remain in the area of an outer curve 84 in the extension of the second area 83 for introducing a mold core. This hole was subsequently closed with a stopper that was welded or glued, for example. The introduction of such a plug as an additional step can be omitted with the manufacturing process shown here.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Analytical Chemistry (AREA)
• Chemical & Material Sciences (AREA)
• Manufacturing & Machinery (AREA)
• Quick-Acting Or Multi-Walled Pipe Joints (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Valves And Accessory Devices For Braking Systems (AREA)
• Gasket Seals (AREA)
• Transmission Of Braking Force In Braking Systems (AREA)

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• 2003
  • 2003-05-13 CN CN038110253A patent/CN1653272B/zh not_active Expired - Fee Related
  • 2003-05-13 BR BR0304826-8A patent/BR0304826A/pt not_active IP Right Cessation
  • 2003-05-13 DE DE10321287A patent/DE10321287A1/de not_active Withdrawn
  • 2003-05-13 WO PCT/DE2003/001513 patent/WO2003095846A1/de not_active Ceased
  • 2003-05-13 US US10/514,400 patent/US7946630B2/en not_active Expired - Fee Related
  • 2003-05-13 KR KR10-2004-7018357A patent/KR20050013550A/ko not_active Ceased
  • 2003-05-13 DE DE10393287T patent/DE10393287D2/de not_active Expired - Fee Related
  • 2003-05-13 AU AU2003232622A patent/AU2003232622A1/en not_active Abandoned
  • 2003-05-13 JP JP2004503809A patent/JP2005525517A/ja not_active Withdrawn

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