EP1368574A1 - Verfahren zum druckaufbau in verbindungskupplungen und verbindungskupplung - Google Patents
Verfahren zum druckaufbau in verbindungskupplungen und verbindungskupplungInfo
- Publication number
- EP1368574A1 EP1368574A1 EP02704739A EP02704739A EP1368574A1 EP 1368574 A1 EP1368574 A1 EP 1368574A1 EP 02704739 A EP02704739 A EP 02704739A EP 02704739 A EP02704739 A EP 02704739A EP 1368574 A1 EP1368574 A1 EP 1368574A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- coupling
- eccentric
- connection
- pressure medium
- 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.)
- Withdrawn
Links
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
- F16D25/00—Fluid-actuated clutches
- F16D25/04—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube
- F16D25/042—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch
- F16D25/046—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch and causing purely radial movement
-
- 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
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
- F16D1/0805—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to deformation of a resilient body or a body of fluid
-
- 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
- F16D25/14—Fluid pressure control
-
- 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
- F16D43/00—Automatic clutches
- F16D43/28—Automatic clutches actuated by fluid pressure
- F16D43/284—Automatic clutches actuated by fluid pressure controlled by angular speed
-
- 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
-
- 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
- F16D2048/0203—Control by fluid pressure with an accumulator; Details thereof
-
- 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
- F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
- F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
-
- 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
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0263—Passive valves between pressure source and actuating cylinder, e.g. check valves or throttle valves
Definitions
- the invention relates to a method for building up pressure in an intermediate space of a connecting coupling, which is delimited by at least one partially elastically deformable wall, for the non-positive connection of two machine elements which are arranged coaxially to one another and can be coupled with one another without play - a first drive-side and a second drive-side machine element, specifically with the features from the preamble of claim 1; also a connection coupling.
- Couplings are known in a variety of designs. These are used for torque transmission between two coaxial machine parts.
- a generic backlash-free, non-positive and quick-release and releasable connection coupling for realizing a shaft-hub connection is known, for example, from the publication Voith-Druck G 1578 SV / MSW
- a pressure medium supply system is assigned to the annular chamber. This is usually followed by a channel arrangement, which is used to fill and empty the annular chamber or the intermediate space.
- Such couplings are used, for example, in rolling mill drives.
- the invention is therefore based on the object of further developing a connection coupling for realizing a backlash-free connection of the type mentioned at the outset, so that the disadvantages mentioned are avoided, in particular that service personnel for implementing the positive connection by means of pressure medium supply and for relief can be dispensed with.
- Machine elements - a first on the drive side and a second output-side machine element - takes place according to the invention by conveying operating or pressure medium during the rotation of the connecting coupling by means of at least one conveying device arranged in the area of the outer circumference of the connecting coupling from a co-rotating pressure medium tank into the intermediate space.
- the conveying device is preferably arranged in the region of the outer circumference of the connecting coupling and is driven by an eccentric which acts directly or indirectly on the conveying device via a cam element in such a way that it is moved alternately into and out of the conveying position.
- the pressure medium is automatically conveyed into the intermediate space during the rotation of the connecting coupling by means of the conveying device or conveying devices arranged in the area of the outer periphery of the connecting coupling, the drive of the conveying device using a
- the conveying device is driven as a function of a speed difference between the connecting clutch and those that can be directly connected to it
- connection elements in particular the machine element on the drive side.
- the drive is then designed or controlled in such a way that the pressure in the pressure chamber is automatically adjusted when a relative speed occurs.
- the delivery rate is preferably directly proportional to the speed difference.
- the conveyor is assigned a drive device, which is designed, for example, in the form of an annular eccentric element, in particular an eccentric ring, and which is supported on the drive or output-side machine element and is effective at different speeds in relation to the speed of the conveyor on the conveyor elements, that is to say this drives. It is thereby achieved that, in the case of such a connection coupling, the system is automatically filled when the system in which the coupling is integrated, depending on the current relative speeds between the connection coupling and the machine elements to be coupled to one another.
- the filling takes place via means for pressure medium supply assigned to the connection coupling, in particular a pressure medium supply system, which comprise at least one delivery device and a pressure medium source or storage unit, the drive of the delivery device, in particular the delivery element or the individual delivery elements, due to the relative speeds between the connection clutch and the with this to be coupled elements.
- the conveying process is generally only maintained during a relative speed to the other coupling parts, while at a relative speed
- the drive is designed according to a particularly advantageous embodiment as an eccentric, comprising a weight and a cam element, the output of which is directly or indirectly via a further transmission element on the conveyor element
- the eccentric is preferably an eccentric ring executed, the weight and curve element form an integral unit, that is, they are formed by one component.
- the weight and curve element can be formed by one component.
- the curve element is preferably designed in the form of an annular element with a correspondingly designed outer surface in the form of a curve contour. However, this surface on the outer circumference, when the conveying element moves relative to the latter, causes a force on the conveying element which, when implemented as a tappet pump, is converted into a pressure stroke and thus promotes
- Coupling parts equal to zero, there is no further conveyance, since no more force is applied to the tappet of the conveying device via the cam disc.
- the pressure medium storage space is designed to be pressure-tight with respect to the surroundings, and a slight excess pressure is impressed on the operating or pressure medium in the pressure medium storage.
- the variant a) represents a particularly preferred embodiment, since it is characterized by a very small space requirement and a low manufacturing cost. It is irrelevant whether the structural unit was assembled from individual components or whether it was created as an integral structural unit.
- the solution mentioned under b) has the advantage that there are no limits with regard to the design of the eccentric from weight and curve element, that is to say any possible combination with regard to the size of the weight and the design of the curve element can be provided very quickly since the functional unit is first is created by merging.
- the conveying element is prestressed with respect to the eccentric via one or more spring devices. If the force on the conveyor element, especially when trained as a ram pump
- the conveying device is designed as a pump device.
- the pump device, in particular the conveying elements are to this Purpose non-rotatably connected to the connecting coupling, the relative speeds between the connecting coupling and, for example, an eccentric being used to drive the conveying elements.
- this is achieved in that the conveying elements of the conveying device are actuated via corresponding actuating elements which are arranged on the eccentric ring which is supported on one of the two machine elements to be coupled.
- an actuation is triggered by bringing the conveying elements and the actuating elements into operative connection, this triggering being in each case due to the different circumferential speeds between the conveying devices arranged on the connecting coupling and thus conveying elements and the actuating elements.
- means for relieving the clutch are provided. Since the pressure is usually through a check valve in the
- a targeted discharge can be achieved by means of a relief valve with external actuation or a constant throttle relief.
- connection coupling which, in addition to a small number of components, has the advantage that it can be used as an independently encapsulated structural unit for any purpose, can be arranged on any components and can generally be dispensed with by service personnel on site, with automatic filling of the Space between
- a connecting coupling for the non-positive connection of two coaxial machine elements to be coupled with one another without play - a first machine element on the drive side and a second machine element on the output side - with at least one of at least one at least partially elastic deformable wall-limited space and a pressure medium supply system assigned to the space, comprising at least one pressure medium storage device, at least one conveying device and means for coupling the conveying device to the intermediate space, are three according to a further embodiment of the solution according to the invention
- Pressure medium storage device and the conveying device are arranged on the connecting coupling, the conveying device being assigned at least one drive which is connected to one of the two machine elements to be coupled - first machine element or second machine element ⁇ at least indirectly, i.e. indirectly via additional transmission elements or directly, i.e. is directly connectable.
- the drive is over
- the conveying device is also designed as a pump device in the simplest case.
- the pump device in particular the conveying elements, are connected in a rotationally fixed manner to the connecting coupling, the relative speeds between the connecting coupling and, for example, an eccentric being used to drive the conveying elements.
- this is achieved in that the conveying elements of the conveying device are actuated via corresponding actuating elements which are arranged on the eccentric ring which is supported on one of the two machine elements to be coupled. Doing so
- Actuation is triggered by bringing the conveying elements and the actuating elements into operative connection, this triggering being due to the different circumferential speeds between the conveying devices arranged on the connecting coupling and thus conveying elements and the actuating elements.
- These preferably comprise at least one delivery device in the form of a pump device, which is connected to the connecting coupling in a rotationally fixed manner, which in the simplest case is a reciprocating piston pump unit. This is arranged in relation to the coupling base body of the connecting coupling in such a way that the possible piston stroke is realized essentially in the radial direction in the installed position.
- a corresponding actuating device is assigned to the conveying elements for actuation.
- This is preferably designed in the form of an annular eccentric element.
- designs of the drive of the conveying element by means of a swash plate or a gearwheel are conceivable.
- a plurality of conveying devices are preferably provided, which in the circumferential direction of the
- Connection coupling are arranged at certain preferably uniform distances from each other. If several conveying devices are provided, there are also several possibilities for the configuration and arrangement of the actuating elements on the drive-side machine element. It is conceivable to use a single actuating element, which the individual
- Drives conveying elements one after the other depending on the relative speed between the connecting coupling and the drive device.
- Another possibility is to provide a plurality of actuating elements, which preferably corresponds to the number of conveying devices and also to arrange them at regular intervals in the circumferential direction, for example of the machine element on the drive side, so that all conveying devices can be driven simultaneously.
- This solution offers the advantage that the individual conveying devices can be made smaller, and thus the entire device connection coupling with means for supplying pressure medium, also with regard to the required installation space in a radial manner
- the individual actuators can an actuating device can be summarized, for example in the form of an eccentric ring and a plurality of projections aligned in the radial direction.
- Conveying element pumping devices can be realized with different modes of operation. A distinction is made between the following: a) Constant pump - not switchable b) Constant pump with external switchability c) Constant pump can be switched automatically d) Control pump.
- the pump devices mentioned under a) and b) are used for the second solution, while the one mentioned under c) is used for the first solution.
- the actuating element for the conveying element for example the eccentric ring
- the connecting coupling or the part of the connecting coupling which realizes the frictional connection is led out in the axial direction beyond the housing of the pressure medium storage unit and thus the connecting coupling or the part of the connecting coupling which realizes the frictional connection.
- the outstanding part serves as a link to one
- the conveying process of the conveying device can never be interrupted, so that after the pressure has built up in the space which can be filled with pressure medium, means are to be provided which limit the pressure in the space and thus the contact pressure for the elements to be coupled to one another to a maximum value.
- a pressure limiting device in the simplest case a pressure limiting valve, is assigned to the connecting coupling, in particular the space that can be filled with pressure medium.
- the eccentric ring is used to implement the mode of operation of a constant delivery device according to b), in particular a constant pump with external switchability also extended in the axial direction and means for optional braking or realization of a freewheel are provided.
- the holding function can be implemented, for example, a) mechanically b) hydraulically c) electromagnetically or by combining these options.
- Drive devices are preferably used which enable the delivery device, in particular the pump device, to function as an automatically switchable constant delivery device according to c).
- Different solutions are also differentiated here. These can be implemented mechanically, hydraulically or electrically.
- the eccentric ring which acts as a drive or actuating device for the conveying element, is provided with an eccentric weight.
- the reaction moment from the pump device is applied by a swinging weight on the eccentric ring.
- the maximum possible pump drive torque is precisely determined by the eccentric weight and the lever arm. When the limit torque, which corresponds to the maximum permissible torque, is reached, the eccentric ring begins to rotate with the weight and due to the reduction in the
- Relative speed is set by the pumping device until the pressure in the space in the connecting coupling drops again and a relative speed can be recorded.
- means which preferably comprise at least one check valve which is located in a Connection line between the space and relief device is arranged.
- the relief device is used for quick emptying of the intermediate space, that is, for releasing if necessary, and is operated manually.
- only a closure element is provided, which connects the connecting channel between the space and the outer circumference of the
- a further embodiment for realizing the constant pump function with automatic switchability can be implemented by providing a magnetic brake device with a set magnetic force.
- Magnetic force acts on a magnetizable part of the eccentric ring and holds it in place until the pump force becomes greater than the magnetic force.
- the eccentric ring breaks free and begins to rotate. Since the relative speed between the pump device and the eccentric is almost zero, it no longer delivers.
- means for maintaining the pressure in the space that can be filled with pressure medium are required, which in the simplest case also comprise a check valve.
- Another alternative embodiment for realizing the function of a constant pump with automatic switchability consists in the provision of a hydraulic valve device in the supply line to the intermediate space, which lowers the pump pressure to almost zero when the maximum pressure is reached. Means for maintaining the clutch pressure are also required here. This solution is a particularly compact version.
- connection coupling and the equipment supply system assigned to it can be created as a modular, pre-assembled structural unit, which must be coupled with the respective elements to be connected in a corresponding manner depending on the application. There are no additional devices on the machine parts to be coupled provided. These solutions are therefore particularly versatile in terms of their range of use.
- the conveyor For certain purposes, it is advisable not to operate the conveyor as a constant pump, but as a control pump. This means that when the required pressure is reached in the space that can be filled with pressure medium, the pump automatically goes back to zero stroke.
- This function is implemented, for example, when the delivery device is designed as a radial piston pump with a spring-loaded adjustable eccentric ring or a radial piston pump with a spring-loaded spring assembly in front of the tappet or an axial piston pump with a spring-loaded adjustable swash plate.
- means for relieving the clutch are provided for both solutions. Since the pressure is usually kept in the intermediate space by the check valve, a targeted discharge can be carried out
- connection coupling begins to rotate
- pumping process begins according to the invention, and pressure medium is pressed into the intermediate space of the connection coupling.
- the pressure medium flows to the pressure gap via a check valve.
- Control line to a relief valve, which lowers the pump pressure to almost zero bar after reaching the required pressure in the pressure gap.
- Figure 1 illustrates in a schematically simplified representation the basic structure and the basic principle of an invention designed particularly advantageously used connection coupling with automatic filling;
- FIG. 3 illustrates a further embodiment of a connecting coupling designed according to the invention with an eccentric consisting of a plurality of individual components
- Figure 4 illustrates an embodiment of a connecting coupling designed according to the invention with a non-switchable constant pump function of the conveyor.
- 5a and 5b illustrate an embodiment of a connecting coupling designed according to the invention with a switchable constant pump function of the conveying device
- FIG. 6 shows an embodiment of a connecting coupling with a separate relief valve
- Figure 7 illustrates a particularly compact embodiment of the
- Means for maintaining and / or limiting the pressure in the space Means for maintaining and / or limiting the pressure in the space.
- FIG. 1 illustrates, by way of example, a preferred embodiment of a connecting coupling 1 designed according to the invention.
- This acts as a coupling for the play-free connection between two machine elements to be coupled coaxially to one another - for example a shaft 2 and a hub 3.
- the bracing can be caused by the direct effect of the connecting coupling 1 on the two elements to be coupled together by means of intermediate connections the coupling 1 viewed in the radial direction between the shaft 2 and the hub 3 take place.
- Another possibility is the indirect realization of the bracing, in which the connection coupling 1 is only in direct operative connection with the hub 3, that is to say in direct contact and causes bracing with the other second element of the shaft 2 via the contact pressure on one of these elements.
- the connecting coupling 1 is designed such that it surrounds the elements to be coupled - shaft 2 and hub 3 - in the circumferential direction and is therefore characterized in the radial direction by a larger diameter than the outer diameter of the elements to be coupled
- connection coupling is thereby brought into engagement, in particular frictionally, in operative connection with the outer circumference A 3 of the hub 3.
- the connecting coupling 1 comprises at least one space 4 which can be filled with pressure medium, one of which, preferably the one to the outer surface 5 of the one with the
- Connection coupling 1 frictionally directly to be coupled element, here the hub 3, directed wall 6 has at least one elastic portion 7, which experiences a deformation in the direction of the elements to be braced when the pressure medium acts.
- the space 4 is formed, for example, by a double-walled pressure sleeve 8 and is designed in a ring shape. This extends in the installed position of the connecting coupling 1, viewed in the axial direction, preferably in the axial direction and essentially parallel to the axis of rotation R 2, 3 of the shaft 2 and hub 3.
- Means 9 for supplying pressure medium are assigned to the connecting coupling 1.
- the conveying device 12 comprises at least one pump device 14, in the illustrated case two of which can be seen in the axial section Pumping devices, the pumping device 14a and the pumping device 14b, which in the area of the
- Outer circumference 15 or on the end faces aligned in the axial direction 16a or 16b of the connecting coupling 1 are arranged.
- a plurality of pump devices 14 are preferably always provided, which are arranged at certain predefinable distances from one another in the circumferential direction, preferably at uniform distances from one another, on a certain diameter dp of the connecting coupling. Versions with are also conceivable
- the means 13 for coupling the conveying device 12 to the intermediate space 4 which can be filled with pressure medium each comprise at least one connecting channel 17, in the case of designs with a plurality of pumping devices 14 a plurality of connecting channels 17, each of which is the individual one
- the pressure medium supply system 10, in particular the pressure medium reservoir 11, is also arranged on the connection coupling 1 according to the invention.
- the pressure medium reservoir 11 is designed such that it forms at least one tight pressure medium storage space. This is delimited by a housing 19 and an end face 16 oriented in the axial direction, here the end face
- the coupling coupling 1 rotates, the pressure medium in the pressure medium storage space 18 also rotates.
- the pump device 14 is arranged in relation to the liquid level that is set in the pressure medium storage space 18 in such a way that its conveying element 20 extends into the operating medium.
- a drive 21 is assigned to the conveying element 20.
- this comprises at least one curved body 22, which is in the form of an annular element 23 with a correspondingly curved shape designed surface 24 is formed on the outer circumference in the form of a curved contour 25, which is designed such that it acts on the conveying element 20 with relative movement like a cam and causes a movement of the conveying element 20 in the conveying position and out of it.
- An imbalance in the form of a weight 26 is assigned to the cam body 22.
- Curve body 22 and the weight 26 form an eccentric 27.
- the structural unit of cam body 22 and weight 26 which forms an eccentric can also be referred to as an eccentric ring 27.
- the eccentric ring 27 is supported via a floating bearing arrangement 28 on the hub 3 which can be brought into a frictional engagement directly with the connecting clutch 1.
- a further bearing 30, also in the form of floating bearings is provided between the outer circumference 29 of the eccentric ring 27 and the conveying element 20.
- the pump devices 14 used are preferably piston pumps, for example in the form of tappet pumps.
- the plungers act as the conveying element 20.
- the funding is realized via the pressure stroke. This is at a relative speed between the connecting clutch 1 and thus the conveyor device 12 coupled to it in the form of the pump devices
- connection coupling 1 When the connection coupling 1 begins to rotate, the pumping process is initiated on the conveying element 18 due to the pressure stroke generated by the eccentric 27. Via the connecting channels 17, pressure medium can be filled with pressure medium
- the reaction moment causes the cam element 22 to be entrained with weight, ie the eccentric ring 27.
- the eccentric ring 27 is rotatably mounted in the pressure chamber 18, preferably via the bearing arrangement 28.
- the pressure medium storage space 18 is designed to be pressure-tight with respect to the surroundings. This is caused by the sealing of the housing 19 from the environment.
- sealing devices 33 and 34 are provided, for example, which are arranged between the housing 19 and the end face 16a of the connecting coupling and furthermore between the housing 19 and the end face 35 of the hub 3.
- the reaction moment from the pump device 14 is applied to the eccentric 27 by the swinging-out weight 26.
- the maximum possible pump drive torque, in particular the pressure stroke which characterizes this, is thus determined by the eccentric weight 26 and the
- means 18 can be provided in this case for holding the pressure in the intermediate space 4 in the form of so-called check valves 36, which are arranged in the connecting line or the connecting lines 17 to the intermediate space 4.
- check valves 36 which are arranged in the connecting line or the connecting lines 17 to the intermediate space 4.
- Another possibility, not shown here, is to provide a hydraulic valve that lowers the pump pressure to almost zero when the maximum pressure is reached. In this case, the reaction torque is also set to 0 and the eccentric 27 is returned to its original starting position without further rotation.
- the conveying element 20 is prestressed with respect to the eccentric ring 27 via one or more spring devices 37. If the force on the conveying element 20, in particular the tappet, is higher than the spring preload, then the
- Compress spring device 37 further and the ram stroke decreases, preferably down to 0. Pump device 14 then also no longer delivers.
- FIG. 2a illustrates in a plan view of an eccentric ring 27.2a the annular element 23 with the curved outer surface 24 and the weight 26.
- the part carrying the weight 26 is designed as a projection 38.
- the eccentric 27.2a clarifies a sectional view according to a section 1-1 according to FIG. 1.
- FIG. 2b illustrates a further embodiment of the weight-forming part 26 of an eccentric 27.2b.
- the part of the eccentric forming the weight 26 is formed by a ring element 39, which has two segments, a first segment 40 and a second segment 41, which differ in terms of their inner circumference 42a and 42b differentiate.
- the individual segments 40 and 41 can be made of different materials.
- the second half, i.e. the first segment 40 for alignment with the inner circumference 42b of the second segment 41, for example poured out a plastic or other potting compound.
- an essentially smooth inner contour is realized on the inner circumference 42a and 42b, in which the hydrodynamic inclination is considerably minimized.
- FIG. 3 illustrates, by way of example, a further particularly advantageous embodiment of a connecting coupling 1.3 designed according to the invention with an eccentric ring 27.3.
- the basic structure and the basic function of the connecting coupling 1.3, the connecting elements shaft 2 and hub 3 and the pressure medium supply system 10.3 correspond to that described in FIG. 1, which is why the same reference numerals are used for the same elements with the addition of the figure number.
- the coupling between the conveying element 20.3 of the pump device 1 .3a or the pump device 14.3b with the curve element 22.3 or the drive 21.3 does not take place in a radial direction essentially as in FIG. 1 in a common direction
- the eccentric ring 27.3 is supported on the connecting coupling 1.3 via a floating bearing 28.3. Furthermore, the eccentric 27.3 is divided into two sub-elements 43 and 44, the sub-element 43 being directly connected to the weight 26.3 or forming a structural unit with it.
- Part element 44 is supported via a further second floating bearing arrangement 45 with respect to the part forming the weight 26.3 and the conveying element 20.3.
- sub-element 43 is designed as curve element 22.3, i.e. this has an outer surface 24.3, which is characterized by a curved contour 25.3
- the sub-element 44 exposed to a corresponding pressure stroke, which is proportional to Pressure stroke of the conveying element 20 is.
- the sub-element 44 is designed such that it can transmit the pressure stroke to the conveying element 20.3.
- the pressure stroke is not transmitted directly from the cam element 22.3 to the conveying element 20.3, but via an intermediate element.
- the eccentric 27.3 In this version of the eccentric 27.3 from several individual elements, the
- this figure provides the possibility of integrating the means 18.3 for holding the pressure in the intermediate space 4 in the form of check valves arranged in the pump device 14.3a or 14.3b, which automatically
- means are provided for limiting the pressure.
- the means for limiting the pressure in the space which can be filled with pressure medium, in particular a pressure-limiting valve, and the means for holding the pressure in the space are preferably combined in one structural unit.
- This structural unit then preferably includes the check valve in addition to the pressure relief valve.
- the structural unit is arranged in the area of the outer circumference of the connecting coupling, in particular the double-walled pressure sleeve.
- a plurality of structural units are preferably viewed in the circumferential direction of the connecting coupling at certain predefined distances from one another on the circumference, in particular in the region of the
- the outer circumference of the connecting coupling is arranged, which are each connected via a connecting line to the intermediate space which can be filled with pressure medium.
- a connecting line to the intermediate space which can be filled with pressure medium.
- designs with only one structural unit are also conceivable, which, however, is then to be designed accordingly, while the size can be considerably reduced when using several structural units.
- a cooling jacket (not shown here) on the circumference, preferably in the whole, is used to reduce the energy loss and thus to avoid an inadmissibly high heating of the pressure medium
- the pressure medium is guided in a circuit from the pressure medium store to the pressure medium store and can then dissipate thermal energy.
- FIGS. 4 to 7 illustrate further possible designs of a connecting coupling 1.4 designed according to the invention, which differ in terms of the way in which the conveying devices, in particular the pumping devices 14.4 and / or the means 18.4 for holding or limiting the pressure in the intermediate space 4.4 are implemented ,
- Limiting the pressure in the intermediate space 4.4 corresponds essentially to that described in FIG. 1.
- the same reference numerals are used for the same elements.
- the conveying element 20.4 is supported on the actuating device 46 via a bearing 30.4.
- the eccentric 27.4 is constructed in such a way that, viewed in the axial direction, it extends beyond the means for supplying pressure medium 9.4.
- Corresponding sealing devices are provided in the passage area through the housing 19.4 between the eccentric 27.4 and the housing 19.4.
- the torque arm 47 can be designed differently. For example in the form of a rope or a rod which is articulated out of the housing 19.4 in the region of the projecting part 48 of the eccentric 27.4.
- the embodiment according to FIG. 4 enables the mode of operation of the
- Pump device 12.4 as a constant pump, ie as a non-switchable pump.
- the eccentric ring 27.4 is held on the outside with a torque arm 47. Since the pumping process of the conveying device 14.4 cannot be interrupted, a pressure limiting valve 48 is required as a means for limiting the pressure. If, according to FIG. 4, there is no fixed connection via a rod or a rope, the pumping device 12.4 can be implemented with an optional hard braking or free-running of the eccentric ring 27.4, the functionality of a constant pump with externally possible switchability. With regard to the possibilities of braking, the protruding part 48 of the eccentric 27.4 from the housing 19.4 is then assigned means for braking. These can act mechanically or electromagnetically on the eccentric ring 27.4.
- FIGS. 5a and 5b illustrate further embodiments of the implementation of the pump function as a regulating pump by appropriately designing the eccentric 27.5a or 27.5b and actuating the delivery elements 20.5a and 20.5b.
- FIG. 5a illustrates an embodiment with an outstanding eccentric
- FIG. 5b illustrates a possibility of realizing the functioning of the pump device 12.5b as a non-switchable constant pump, in that the eccentric ring 27.5b is held from the outside with a torque support 47.5b, here in the form of a rope.
- Both versions have in common that the eccentric ring 27.5a or 27.5b is biased at least by one or more spring devices.
- the spring devices are designated 50.5a and 50.5b. If the pump force on the conveying element 20.5a or 20.5b, in particular on the tappet, is higher than the spring preload, then the
- an internal flap valve is preferably provided in the pump device 12.5a or 12.5b, which maintains the pressure.
- a throttle point in the pump or suction line is preferably the
- Pump device provided to limit the stroke and thus the delivery rate at higher speeds.
- FIG. 6 illustrates an embodiment 1.6 with a separate relief valve 51 for the targeted release of the pressure, which is also used for the embodiments according to FIG. 6
- FIGS 1 to 5 can be used.
- FIG. 7 illustrates a particularly compact design of the means 18.7 for holding and / or limiting the pressure in the space 4.7 and the means 22.5 for limiting the pressure in the space 4.7. Both are structural
- Unit 52 This forms a kind of special valve and is in the Pressure supply line, ie the connecting line 53, arranged between the pump device 12.7 and the intermediate space 4.7.
- the pressure oil comes through the check valve 36.7 and branches off into a control line 54 to a relief valve 55 which, after reaching the required pressure in the space 4.7, lowers the pump pressure to almost zero bar.
- this valve device has the advantage that, once the required pressure in the intermediate space 4.7 has been reached, the pressure generated by means of the pump device 12.7 (not shown here) is reduced, so that there is only little power loss.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10112087 | 2001-03-12 | ||
DE10112088A DE10112088A1 (de) | 2001-03-12 | 2001-03-12 | Verfahren zum Druckaufbau in Verbindungskupplung und Verbindungskupplung |
DE10112088 | 2001-03-12 | ||
DE10112087A DE10112087A1 (de) | 2001-03-12 | 2001-03-12 | Verfahren zum Druckaufbau in Verbindungskupplungen und Verbindungskupplung |
PCT/EP2002/002537 WO2002073055A1 (de) | 2001-03-12 | 2002-03-08 | Verfahren zum druckaufbau in verbindungskupplungen und verbindungskupplung |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1368574A1 true EP1368574A1 (de) | 2003-12-10 |
Family
ID=26008756
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02704739A Withdrawn EP1368574A1 (de) | 2001-03-12 | 2002-03-08 | Verfahren zum druckaufbau in verbindungskupplungen und verbindungskupplung |
Country Status (2)
Country | Link |
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EP (1) | EP1368574A1 (de) |
WO (1) | WO2002073055A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE530706C2 (sv) * | 2006-12-27 | 2008-08-19 | Hudiksvalls Teknik Ct Ab | Koppling |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE423566B (sv) * | 1973-01-25 | 1982-05-10 | Foerenade Fabriksverken | Tryckmedieunderstott friktionsorgan for sammankoppling av atminstone tva detaljer foretredesvis for vridmomentoverforing |
SE425515B (sv) * | 1978-06-15 | 1982-10-04 | Metalform Safeset Ab | Tryckmediepaverkad koppling |
DE4112484C2 (de) * | 1991-04-17 | 1997-07-03 | Renk Tacke Gmbh | Hydraulische Sicherheitskupplung |
-
2002
- 2002-03-08 WO PCT/EP2002/002537 patent/WO2002073055A1/de not_active Application Discontinuation
- 2002-03-08 EP EP02704739A patent/EP1368574A1/de not_active Withdrawn
Non-Patent Citations (1)
Title |
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See references of WO02073055A1 * |
Also Published As
Publication number | Publication date |
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WO2002073055A1 (de) | 2002-09-19 |
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