EP1368574A1

EP1368574A1 - Method for building up pressure in connection couplings, and respective connection coupling

Info

Publication number: EP1368574A1
Application number: EP02704739A
Authority: EP
Inventors: Ernst Elsner; Hans Lindenthal; Curt Falk; Bo Appell
Original assignee: Voith Turbo Safeset AB
Current assignee: Voith Turbo Safeset AB
Priority date: 2001-03-12
Filing date: 2002-03-08
Publication date: 2003-12-10
Also published as: WO2002073055A1

Abstract

The invention relates to a method for building up pressure in connection couplings for coupling two coaxial machine elements a first machine element on the drive side and a second machine element on the output side especially a shaft-hub connection in a rotationally fixed manner. The invention is further characterized in that the connection coupling establishes a zero play, force-fit connection between the machine elements and comprises an intermediate space filled with a pressure medium. Said intermediate space is defined by a wall that faces a machine element to be coupled and comprises an elastic section. Said elastic section is deformed in the direction of the machine elements to be braced against each other when acted upon by the pressure medium. The invention is further characterized in that the pressure medium is conveyed by at least one conveying means from a co-rotating pressure medium reservoir to the intermediate space during rotation of the connection coupling.

Description

Process for building up pressure in connecting couplings and connecting coupling

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

4.99 2000 known. This has at least one thin-walled sleeve, which forms an axially extending wall of an essentially annular chamber, which is also referred to as an intermediate space and which can be acted upon by pressure medium in order to deform the sleeve essentially in the radial direction and at least indirectly with a surface of an element to which the coupling is to be fastened. 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. There is a desire for a play-free connection between a roller and a shaft train, for example in the form of a cardan shaft, in order to improve the quality of the rolling stock or to avoid wear and tear in the usual flat pin hits. In the case of the generic connecting couplings used to date, these have been inflated manually, i.e. that this

Operators on the clutch had to work to release pressure when loosening drain and then inflate the connection coupling to close again by introducing pressure medium into the annular chamber. Depending on the application, however, this is only in the rarest of cases an acceptable procedure, in particular since each of these actions requires the system to come to a standstill and the presence of

Service personnel. Remote controls with automatic oil connections were considered, but were not implemented in practice, since the effort for such connections is considerable. As a solution, therefore, a large part of the rolling mill systems today is carried out with flat pin hits with play, which are only pushed into the roller with its flat profile without

Service personnel at the corresponding hit is necessary. A major disadvantage of such positive connections, however, is the considerable play, which can thus have a negative influence on the mode of operation of the machine element on the output side in processing machines of the processing result.

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.

The solution according to the invention is characterized by the features of claims 1 and 7. Advantageous configurations are given in the subclaims.

The pressure build-up in an intermediate space of a connecting coupling delimited by at least one at least partially elastically deformable wall for the non-positive connection of two coaxial couplings to be coupled with one another without play

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.

Preferably, 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

Relative speed, including zero speed to the other clutch parts rotates. The following modifications can be made to this mode of operation:

1) continuous, i.e. uninterrupted rotation of the drive with relative speed to the speed of the coupling parts or with zero speed and keeping the pressure in the space above one

Pressure limiting device

2) Rotation of the drive with relative speed to the speed of the coupling parts or with zero speed and the possibility of optional decoupling from the conveyor 2a) automatically or

2b) controlled.

In a further aspect of the invention, 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 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. For this purpose, 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. Specifically, this means that, at least as long as there is a relative speed between the drive device and the two elements to be connected in a rotationally fixed manner, the pressure medium supply into the intermediate space is maintained. 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

0 the conveying process is stopped. In order to allow this process to run automatically, that is to say without additional measures to be taken from the outside, 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

Pump device takes effect. 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. However, it is also conceivable to form the weight and curve element of separate components and to combine them in terms of their function to form a unit, while maintaining their independence as a 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

Pressure medium from the pressure medium storage space. A pressure builds up on the side of the connecting coupling as the delivery process increases, which at the same time determines the reaction moment to the delivery process caused by the pressure stroke. If this pressure reaches a certain predefined limit value, which corresponds to the optimal working pressure in the intermediate space or a maximum permissible pressure in the intermediate space, the reaction moment causes the cam element to be carried along with weight, that is to say the eccentric ring. This breaks away and rotates with it. For this purpose, the eccentric ring is rotatably mounted in the pressure medium chamber. Is the relative speed between drive and conveyor element or the rest

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 solution according to the invention offers the advantage of automatic filling of the

Intermediate space with operating or pressure medium during the starting process and with torque transmission, that is, in continuous operation. In a further aspect of the invention, 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. This solution has the advantage that the conveyor at Starting process can be self-priming, which means that no additional aids are required.

With regard to the design of the eccentric, there are a number of possibilities: a) structural unit consisting of weight and curve element, in particular non-rotatable connection between weight and curve element b) coupling between weight and curve element via interposed bearing arrangements.

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.

In a further aspect of the invention, 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

Tappet, higher than the spring preload, the spring device will continue to thread, the preload increases and the tappet stroke decreases until the conveying device or the pumping device no longer delivers.

In the simplest case, 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. In the simplest case, 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. In this case, 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.

In a further aspect of the invention, means for relieving the clutch are provided. Since the pressure is usually through a check valve in the

If space is kept, a targeted discharge can be achieved by means of a relief valve with external actuation or a constant throttle relief.

This solution enables a particularly compact unit

To create a 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

Connection coupling takes place.

In the case of 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

a) a standing eccentric b) a swash plate or c) a gear.

In this solution, the conveying device is also designed as a pump device in the simplest case. For this purpose, 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. In the simplest case, 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. There are a multitude of possibilities for both solutions with regard to the design of the means for supplying pressure medium. 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. Furthermore, designs of the drive of the conveying element by means of a swash plate or a gearwheel are conceivable.

In both solutions, 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

Direction can build smaller. 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.

In general, with regard to the concrete designs of the drive of

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.

In the case mentioned under a), the actuating element for the conveying element, for example the eccentric ring, 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

Torque arm. In this case, 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. For this purpose, 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. An advantage of such an embodiment is that with a corresponding arrangement of the devices for holding the eccentric ring on the connecting coupling, the connecting coupling can be designed as an encapsulated unit, regardless of other local conditions.

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. In the case of a mechanical solution, for example, 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.

To maintain the pressure in the intermediate space after filling, means are required 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. In the simplest case, only a closure element is provided, which connects the connecting channel between the space and the outer circumference of the

Clutch body closes.

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. The

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. When this state is reached, 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. Here too, 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.

The versions as a constant pump with automatic switchability offer the advantage that the 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.

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.

In a further aspect of the invention, 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

a) a relief valve with external actuation or b) constant throttle relief.

These solutions make it possible to create a particularly compact structural unit of a connecting coupling which, in addition to a small number of components, has the advantage that service personnel are not required on site and enables the space to be filled automatically.

The basic function is as follows: When the connection coupling begins to rotate, the pumping process begins according to the invention, and pressure medium is pressed into the intermediate space of the connection coupling. When the required pressure is reached, in

Depending on the conveyor used, several options are conceivable, limit or maintain the pressure. Examples of these are: a) pressure limiting valve b) throttle in the pump suction line to achieve higher speeds and limitation of the delivery rate c) provision of a special valve in the pressure supply line to the space that can be filled with pressure medium.

In this latter possibility, the pressure medium flows to the pressure gap via a check valve. One branches after the 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.

The pressure in the pressure gap is kept by the check valve. However, if this drops below a predefined minimum value as a result of a leak, the relief valve is deactivated again and the pressure gap is increased again to the required pressure. Funding ends when both

Rotate machine parts at the same speed.

With regard to the specific design of the conveyor, the drive of the conveyor and the means for realizing the limitation or

Holding the pressure, the solution according to the invention is not limited to the ones shown. The specific selection of one of these measures and the design depends on the specific application and is at the discretion of the person responsible

Professional.

The solution according to the invention is explained below with reference to figures.

The following is shown in detail:

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;

2a-2c illustrate various embodiments of an example

eccentric;

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.

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. In the illustrated case, 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

Elements - shaft 2 and hub 3. The connection coupling is thereby brought into engagement, in particular frictionally, in operative connection with the outer circumference A _{3 of} the hub 3. For this purpose, 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. These comprise a pressure medium supply system 10 with at least one pressure medium reservoir 1, a conveying device 12 for the pressure medium and means 13 for coupling the conveying device 12 to the intermediate space 4 which can be filled with pressure medium. 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

Arrangements of pumping devices on different diameters. 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

Connect the pump device 14a to 14n to the pressure space, which is formed by the intermediate space 4. After filling the space 4 which can be filled with pressure medium, it is necessary to maintain the pressure in the space 4. For this purpose, means 18 are provided for maintaining the pressure in the intermediate space 4.

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

16a or at least part of the side surfaces of the coupling coupling 1 formed by the end faces and of the shaft 2 or hub 3 to be coupled. When 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. In order to implement a pressure medium supply system 10 for the connection coupling 1 that is completely autonomous during the operation of a drive system with an integrated connection coupling 1, a drive 21 is assigned to the conveying element 20. According to the invention, 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. The

Curve body 22 and the weight 26 form an eccentric 27. There is the possibility of executing the cam body 22 and weight 26 in one piece or as two separate elements by means of corresponding connecting means for the rotationally fixed connection. The structural unit of cam body 22 and weight 26, which forms an eccentric, can also be referred to as an eccentric ring 27. This forms the drive 21. 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. Furthermore, in the case shown, 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

14 and the eccentric ring 27 realized with a low reaction torque of the conveyor 12. 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

Interspace 4 of the connecting coupling 1 pressed. If, in the case shown, the drive takes place, for example, via the shaft 2 or the hub 3, the connecting coupling 1 and thus also the pressure medium storage space 18 rotates together with the housing 9 of the pressure medium accumulator 11. Furthermore, the inner rings 31a and 31b of the two bearings 32a and 32b rotate the bearing assembly 28.

Forces to rotate the eccentric 27 are not transmitted. Because of the Weight 26 remains in its position. The surface on the outer circumference 24, which can be described by a curved contour, however, when the conveying element 20 moves relative to the latter, causes a force on the conveying element 20 which is converted into a pressure stroke and thus carries out pressure medium from the pressure medium storage space 18. In order to ensure simple self-priming by the pump device 14, the pressure medium in the pressure medium storage space 18 is preferably held with a slight excess pressure. As a result, a pressure builds up on the side of the connecting coupling 1 as the conveying process increases, which pressure is simultaneously responsible for the reaction moment of the conveying device 12 to the conveying process caused by the pressure stroke. If this pressure reaches a certain predefined limit value, which corresponds to the optimal working pressure in the intermediate space 4 or a maximum permissible pressure in the intermediate space 4, the reaction moment causes the cam element 22 to be entrained with weight, ie the eccentric ring 27. This breaks free and rotates with it. For this purpose, the eccentric ring 27 is rotatably mounted in the pressure chamber 18, preferably via the bearing arrangement 28.

In order to ensure the function, in particular during the commissioning of the suction process, 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. For this purpose, 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

Lever arm precisely determined. When this limit torque is reached, the Eccentric ring 27 then rotate with the weight 26 and the pump no longer delivers until the pressure drops again. In a further aspect of the invention, 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. 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.

In a further aspect of the solution according to the invention, 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.

There are a multitude of options with regard to the design of the eccentric ring 27. Three examples are shown in FIGS. 2a to 2c. 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. With regard to the design of the curve contour 25.2a, reference is made to the different radial dimensions on the outer surface 24.2a. The eccentric 27.2a clarifies a sectional view according to a section 1-1 according to FIG. 1. In contrast, 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. According to a further, particularly advantageous embodiment of the part of the eccentric 27.2b that forms the weight 26, according to the embodiment in FIG. 2c for flow and weight optimization, 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. In this case, 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. In this embodiment, 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

Plane, but in several planes arranged side by side in the axial 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. The second

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. To implement the function, 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

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. In this case, the pressure stroke is not transmitted directly from the cam element 22.3 to the conveying element 20.3, but via an intermediate element. In this version of the eccentric 27.3 from several individual elements, the

Execution of the weight 26 carrying part according to one of the possibilities shown in Figure 2a to 2c. In a further aspect of the invention, 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

Enable shutdown when a certain pressure p is reached in the intermediate space by lowering the pressure in the pump device 14.3a or 14.3b to 0.

According to a further possible embodiment, 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. However, 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. When the means for limiting the pressure in the intermediate space are designed in the form of pressure limiting valves, 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

Provided area of the outer circumference of the connecting coupling. 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 , The combinations shown in the figures, the design of the conveyor

12.4 or their connection and mode of operation as well as the means 18.4 for holding and / or limiting the pressure in the intermediate space 4.4 do not represent any restriction to the concrete option presented, but can be freely combined with one another. The basic structure of the connecting coupling 1.4 and the means 9.4 for supplying pressure medium and the means 18.4 for

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.

In the embodiment of the connecting coupling 1.4 and the means 9.4 for supplying pressure medium shown in FIG. 4, the only difference is in the embodiment of the actuating device 46 for the pump device 14.4. The design of the means 18.4 for limiting and / or for maintaining the pressure in the intermediate space 4.4 corresponds to that described in FIG. 1. The actuating device 46 for the pump device 12.4 is shown in FIG

Shape of at least one eccentric, preferably an eccentric ring 27.4, executed. This is supported by a bearing arrangement 28.4 on the shaft 2.4 or hub 3.4. 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. This eccentric ring 27.4 is preferably also designed for a speed of n = 0. This is made possible by leading the eccentric 27.4 out, since support can be provided in the protruding area via a torque arm 47. 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. A particularly advantageous embodiment is in the case of electromagnetic hard braking of the eccentric ring 27.4 in a fully encapsulated version of the connecting coupling 1.4, the magnetic force transmission also being possible through an aluminum housing 19.4. 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

27.5a from the housing 19.5a, which means can be assigned for optional braking. The embodiment according to 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

Continue to compress the spring and the tappet stroke decreases, preferably to zero. The pump 12.5a or 12.5b then no longer delivers. In this case, an internal flap valve is preferably provided in the pump device 12.5a or 12.5b, which maintains the pressure. To limit 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

Figures 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 summarized. 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. The pressure in

Space 4.7 is held by the check valve 36.7. If, however, the pressure drops below a set minimum as a result of a leak, the relief valve 55 is deactivated again, and the intermediate space 4.7 is increased again to the required pressure. In addition to the particularly compact design, 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.

LIST OF REFERENCE NUMBERS

1, 1.2, 1.3, 1.4, 1.5a 1.5b, 1.6, 1.7 connecting coupling 2, 2.3 shaft

3, 3.3 hub 4, 4.4, 4.5a, 4.5b,

4.6, 4.7 space which can be filled with pressure medium

5 outer surface 6 wall

7 elastic section

8 double-walled pressure sleeve

9, 9.4 Means for supplying pressure medium

10, 10.3, pressure medium supply system 11 _, 11.3, 11.4;

11.5a, 11.5b, 11.6;

11.7 Pressure fluid reservoir

12, 12.3, 12.4; 12.5A,

12.5b, 12.6; 12.7 conveyor 13, 13.4; 13.5A; Means for coupling the conveyor

13.5b, 13.6, 13.7 with the one that can be filled with pressure medium

gap

14a, 14b, 14.3a,

14.3b, 14.4, 14.5,

14.6, 14.7 pumping device

15 outer circumference

16a, 16b end face of the connecting coupling

17 connecting channel

18, 18.3, 18.4, means for holding and / or limiting the

18.5a, 18.5b, pressure in the space

18.6, 18.7 19, 19.3, 19.4; 19.5a; 19.5b, 19.6, 19.7 housing 20a, 20b, 20.3a, 20.3b, 20.4, 20.5a, 20.5b, 20.6, 20.7 conveyor elements

21, 21.3 drive

22, 22.3, curve element

23, 23.3 annular element

24, 24.2a, 24.2b, 24.2c outer surface

25, 25.2a, 25.2b 25.2c curve contour

26, 26.2a, 26.2b, 26.2c, 26.3 weight 27, 27.2a, 27.2b, 27.2c,

27.3, 27.4, 27.5a,

27.5b, 27.6, 27.7 eccentric

28 floating bearing arrangement

29 Outer circumference 30, 30.4 storage

31a, 31b inner ring

32a, 32b bearings of the bearing arrangement 28

33 sealing device

34 sealing device 35 end face

36, 36.7 check valve

37 spring device

38 head start

39 ring element 40 first segment

41 second segment 42a inner circumference

42b inner circumference

43 partial element

44 partial element 45 floating bearing

46 actuating device

47, 47.5b torque arm

48 outstanding part of the eccentric

49 Pressure relief valve 50.5a, 50.5b spring device

51 relief valve

52 structural unit

53 connecting line

54 Control line 55 Relief valve

A ₃ outer circumference dp arrangement diameter of the pumping devices

Claims

claims

1. Method for building up pressure in connecting couplings (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7) for the rotationally fixed coupling of two coaxial machine elements - a first machine element on the drive side and a second machine element on the drive side - especially in a shaft (2; 2.3) - Hub (3; 3.3) connection, where

1.1 a play-free, non-positive connection between the machine elements (2; 2.3; 2.4; 3; 3.3; 3.4) is established by means of the connecting coupling (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7) and

1.2 the connecting coupling (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7) comprises an intermediate space (4; 4.4; 4.5a; 4.5b; 4.6; 4.7) which can be filled with a pressure medium, which is limited, which is directed in the direction of one of the machine elements to be coupled and has an elastic portion (7), wherein

1.3 the elastic portion (7) experiences a deformation in the direction of the machine elements to be braced when the pressure medium acts, characterized in that

1.4 the pressure medium during the rotation of the connecting coupling (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7) by means of at least one conveyor device (12;

12.3; 12.4; 12.5A; 12.5b; 12.6; 12.7) from a rotating pressure medium reservoir (11; 11.3; 11.4; 11.5a; 11.5b; 11.6; 11.7) into the intermediate space (4; 4.4; 4.5a; 4.5b; 4.6; 4.7).

2. The method of claim 1, wherein

2.1 the conveyor (12; 12.3; 12.4; 12.5a; 12.5b; 12.6; 12.7) is arranged in the area of the outer circumference of the connecting coupling (1; 1.2; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7), and

2.2 the conveyor (12; 12.3; 12.4; 12.5a; 12.5b; 12.6; 12.7) driven by an eccentric (27; 27.2a; 27.2b; 27.2c; 27.3; 27.4; 27.5a; 27.5b; 27.6; 27.7) is directly or indirectly via a curve element (22; 22.3) acts on the conveying device (12; 12.3; 12.4; 12.5a; 12.5b; 12.6; 12.7) in such a way that it is moved alternately out of the conveying position.

3. The method according to claim 1 or 2, characterized in that the

Pressure medium is automatically conveyed into the intermediate space (4; 4.4; 4.5a; 4.5b; 4.6; 4.7) during the rotation of the connecting coupling (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7), whereby the drive (21 ; 21.3) of the conveyor (12; 12.3; 12.4; 12.5a; 12.5b; 12.6; 12.7) rotates at a relative speed to the other coupling parts.

4. The method according to claim 3, characterized in that the drive always has a relative speed to the speed of the coupling parts and the pressure in the space (4.4; 4.5a; 4.5b; 4.6; 4.7) via a pressure limiting device (18.4; 18.5a; 18.5b ; 18.6; 18.7) is held.

5. The method according to claim 3, characterized in that the drive (27.5a; 27.5b) has a relative speed to the speed of the coupling parts and can optionally be decoupled from the conveyor (12.5a; 12.5b).

6. The method according to claim 1 to 3, characterized in that the drive (21; 21.3) is designed such that at a relative speed of zero between the drive-side machine element (2; 2.3) and the output side

Machine element (3; 3.3) which is automatically taken out of operation.

7.Connecting couplings (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7) for the non-positive connection of two coaxial, without play to each other coupling machine elements - a first drive-side and a second output-side machine element -;

7.1 with an intermediate space (4; 4.4; 4.5a; 4.5b; 4.6; 4.7) bounded by at least one at least partially elastically deformable wall (6);

7.2 with a pressure medium supply system (10; 10.3) assigned to the intermediate space (4; 4.4; 4.5a; 4.5b; 4.6; 4.7); characterized by the following features:

7.3 the pressure medium supply system (10; 10.3) comprises at least one rotating pressure medium tank (11; 11.3; 11.4; 11.5a; 11.5b; 11.6;) arranged on the connecting coupling (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7). 11.7);

7.4 with at least one conveyor device (12; 12.3; 12.4; 12.5a; 12.5b; 12.6; 12.7) arranged in the area of the outer circumference (15) of the connecting coupling (1; 1.3; 1.4; 1.5a; 1.5b; 1.6; 1.7), comprising at least one conveying element (20a, 20b, 20.3a, 20.3b, 20.4, 20.5a, 20.5b, 20.6, 20.7) for conveying pressure medium from the co-rotating pressure medium tank (11; 11.3; 11.4; 11.5a; 11.5b; 11.6; 11.7) in the space (4; 4.4; 4.5a; 4.5b; 4.6; 4.7); 7.5 with a drive (27; 27.2a; 27.2b; 27.2c; 27.3; 27.4; 27.5a; 27.5b; 27.6; 27.7) assigned to a conveyor device (12; 12.3; 12.4; 12.5a; 12.5b; 12.6; 12.7) ,

8. Connection coupling (1; 1.2; 1.3) according to claim 7, characterized by the following features:

8.1 with a drive (21;

21.3), comprising an eccentric (27; 27.2a; 27.2b; 27.2c; 27.3) with a weight (26, 26.2a, 26.2b, 26.2c, 26.3) and a cam element (22; 22.3) coupled to it, which is effective directly or indirectly via further transmission elements on the conveyor element (20a, 20b, 20.3a; 20.3b).

9. Connection coupling (1; 1.2; 1.3) according to claim 8, characterized in that the eccentric (27; 27.2a; 27.2b; 27.2c; 27.3) is freely rotatable in the pressure medium reservoir (11; 11.3) and the intermediate space (4; 4.3) Means (18; 18.3) for holding and / or limiting the pressure are assigned.

10. Connection coupling (1; 1.2; 1.3) according to claim 9, characterized in that the means (18; 18.3) at least one check valve arranged in the feed line to the intermediate space (4; 4.3)

(36).

11. Connection coupling (1; 1.2) according to one of claims 9 or 10, characterized in that the cam element (22) and the weight (26, 26.2a, 26.2b, 26.2c) are formed by an integral structural unit.

12. Connection coupling (1.3) according to claim 9 or 10, characterized in that curve element (22; 22.3) and weight are formed by separate components which are combined to form a structural unit by means of a rotationally fixed connection.

13. Connection coupling (1.3) according to claim 12, characterized in that the cam element (22.3) and the weight (26.3) are supported against one another via a bearing arrangement (45).

14. Connection coupling (1; 1.2; 1.3)) according to any one of claims 9 to 13, characterized in that between the eccentric (27; 27.2a; 27.2b; 27.2c; 27.3) and the conveyor (12; 12.3) a prestressed Spring unit is provided.

15. Connection coupling (1.4) according to claim 7, characterized by the following features: 15.1 the conveyor (12.4) is designed as a non-switchable constant pump; 15.2 the drive is formed by an eccentric ring (27.4) assigned to the conveyor (12.4) and supported in a stationary manner; 15.3 the pressure chamber (4.4) are means (18.4) for holding the pressure or for

Pressure limitation assigned.

16. Connection coupling (1.5a; 1.5b) according to claim 7, characterized by the following features:

16.1 the conveyor (12.5a; 12.5b) is designed as a switchable constant pump;

16.2 the drive is driven by a freely rotatable and brakeable eccentric ring (27.5a;

27.5b) formed;

16.3 The pressure chamber (4.5a; 4.5b) is assigned means (18.5a; 18.5b) for maintaining the pressure or for limiting the pressure.

17. Connection coupling (1.5a) according to claim 16, characterized in that the eccentric (27.5a) is assigned a mechanical braking device.

18. Connection coupling (1.5a) according to claim 17, characterized in that the eccentric (27.5a) is associated with an electro-pneumatic braking device.

19. Connection coupling according to claim 18, characterized by the following features: 19.1 the drive is formed by an eccentric ring;

19.2 the eccentric is freely rotatable;

19.3 the eccentric can be coupled to a magnetic brake device with an adjusted braking force;

19.4 means for maintaining the pressure are assigned to the intermediate space.

20. Connection coupling (1) according to claim 7, characterized in that the conveying device is designed as an automatically switchable constant pump device.

21. Connection coupling according to claim 19, characterized by the following features:

21.1 the drive is formed by an eccentric with an eccentric weight;

21.2 the eccentric is freely rotatable;

21.3 means for maintaining the pressure or pressure limitation are assigned to the intermediate space.

22. Connection coupling according to one of claims 15 to 21, characterized in that the means comprise at least one check valve arranged in the inlet line to the intermediate space.

23. Connection coupling according to one of claims 7 to 22, characterized in that the conveying device is formed by a control pump.

24. Connection coupling according to claim 23, characterized in that the control pump is designed as a radial piston pump with a spring-loaded eccentric ring.

25. Coupling according to claim 23, characterized in that the control pump is designed as a radial piston pump with spring-biased delivery element.

6. Connection coupling according to claim 23, characterized in that the control pump is designed as an axial piston pump with spring-loaded adjustable swash plate.