EP3359428A1

EP3359428A1 - Force transmission device and brake assembly

Info

Publication number: EP3359428A1
Application number: EP16781707.1A
Authority: EP
Inventors: Peter Wolfsteiner
Original assignee: Hochschule fuer Angewandte Wissenschaften Muenchen
Current assignee: Hochschule fuer Angewandte Wissenschaften Muenchen
Priority date: 2015-10-09
Filing date: 2016-10-05
Publication date: 2018-08-15
Also published as: DE102015219626A1; WO2017060282A1

Abstract

The invention relates to a force transmission device (100) comprising a first and a second spring energy accumulator (10, 20) and a mechanical coupling (30) of the first and the second spring energy accumulator (10, 20). The mechanical coupling (30) has a lever element (33) which has a first end (31) connected to the first spring energy accumulator (10) and a second end (32) connected to the second spring energy accumulator (20) such that when the movement of the first and second end (31, 32) of the lever element (30) is coupled, energy can be transmitted via a force coupling between the first and second spring energy accumulators (10, 20). For movement purposes, the first end (31) of the rod element (31) is coupled to a first guide (41), and the second end (32) of the rod element (31) is coupled to a second guide (42). The first and second linear guides (41, 42) lie on a plane and extend in non-parallel directions.

Description

Power transfer device and brake assembly

description

The present invention relates to a power transmission device and a brake assembly. More particularly, the present invention relates to a power transmission device using spring energy storage devices and a brake assembly using the power transmission device.

When using mechanical power transmission devices, for example in tensioning devices, such as e.g. When friction brakes are used, a certain amount of mechanical work must be performed when operating. The work done is the reverse operation, for example, the relaxation of the corresponding fixture, partially or completely lost. While various mechanisms using spring energy storage devices are known that at least partially enable storage of the performed mechanical work and its reentry in a reverse operation, the power transmission and energy storage mechanisms used are comparatively complex and self-lossy.

The invention is therefore based on the object to provide a power transmission device and a brake assembly, which allow a particularly simple means reversible and energy-conserving transmission of mechanical forces as possible.

The object underlying the invention is in a power transmission device according to the invention with the features of independent claim 1 and in a brake assembly according to the invention with the features of independent claim 10 solved. Advantageous developments are the subject matter of the dependent claims. According to a first aspect of the present invention there is provided a power transmission device having first and second spring energy stores and mechanical coupling of the first and second spring energy stores with each other, the mechanical coupling having a lever member having a first end in communication with the first spring energy store and a second end in conjunction with the second spring energy storage such that when coupled movement of the first and second ends of the lever element via power coupling between the first and second spring energy storage energy is transferable.

In particular, the first end of the lever element are coupled to a first guide and the second end of the lever element to a second guide for movement. The first and second guides preferably lie in one plane and / or have non-parallel extension directions.

The power transmission device according to the invention has for mechanical coupling to a lever element through which a particularly simple mechanical means a force coupling and an energy exchange between the first and second spring energy storage can be achieved. As a result, a particularly lossless power and energy transfer between the spring energy storage is possible. Due to the simplified structure of the power transmission device is relatively robust and therefore reliable in operation. Also, assembly and maintenance due to the simplification of the mechanical structure can be done with less effort than would be possible with the use of mechanically mutually movable parts for the power coupling.

A particularly high efficiency arises in the power and energy transmission between the first and second spring energy storage in that, according to the force transmission device according to the invention, the first and second guides lie in particular in one plane and / or have non-parallel extension directions.

The lever element can also be designed as a lever, rod element or rod. In the following, the terms lever element, lever, rod element and rod are used interchangeably unless a particular application requires special distinction.

The second spring energy storage can also be referred to simply as the second and elastic energy storage and in particular be formed by that device which is operated or operated with the power and energy coupling and which is also generally referred to as a power receiving unit. That is, in this case, no additional components are formed in the second and elastic energy storage other than those of the power unit. For the purposes of the invention, the first and the second guide may be separate and in particular physically separate units. However, this is not mandatory. Rather, according to the invention, embodiments are also included in which the first and second guides are formed as materially non-separate units, e.g. in materially one-piece form. Thus, the guides and / or the lever element may be incorporated as part of a higher-level mechanical unit and e.g. be formed as part of a transmission, in particular a planetary gear or planetary gear of a planetary gear.

In a further development of the force transmission device according to the invention, the first and second guides are designed as linear guides or substantially linear guides and / or have mutually perpendicular or substantially perpendicular extension directions.

In another preferred embodiment of the power transmission device according to the invention a particularly simple construction is achieved in that the first spring energy storage has a first spring element having a first end and a second end, the first end of the first Spring element is arranged stationary and the second end of the first spring element is movable and attached to the first end of the lever element.

By selecting certain degrees of freedom for the movement of the movable second end of the first spring element, a further simplification of the structure can be achieved. For this purpose, it is provided according to a preferred embodiment of the force transmission device according to the invention, that the movable second end of the first spring element, in particular via the first mediating rotary push joint, is coupled to a first guide.

In another development of the power transmission device according to the invention, the second spring energy storage has a power receiving unit or is formed thereof. Alternatively or additionally, the second end of the lever element for power transmission can be coupled or coupled directly or indirectly to the power take-up unit.

To further simplify the power transmission device, it is provided in an advantageous development that the second spring energy storage has a second spring element having a first end and a second end, the first end of the second spring element is movable and attached to the second end of the lever element and the second end of the second spring element for transmitting power to a power receiving unit is coupled or coupled formed.

Again, certain degrees of freedom of movement of the movable first end of the second spring element can be selected, namely, according to another preferred embodiment of the force transmission device according to the invention, the movable first end of the second spring element, in particular via the second mediating rotary push joint, is coupled to a second guide.

In accordance with another aspect of the present invention, a balanced one is provided between the first and second spring energy stores Provide interaction in the power and energy transfer. This is achieved according to an advantageous development of the force transmission device according to the invention in that the first spring element has a first spring constant c1 and the second spring element has a second spring constant and the first and second spring constants c1 and c2 in particular the relationship (1).

(1) c l c 2 C satisfy, where c1 the first spring constant and c2 denote the second spring constant and C is representative of elastic properties of a power unit to which the second spring element is formed with its second end coupled or coupled. Parameter C describes the coupled power unit as an externally coupled device, e.g. a device is performed on the mechanical work, in the manner of a spare spring with the spring constant C and in series with the second spring energy storage.

In order to adapt the power and energy transmission from the power transmission device to an externally coupled device in a suitable manner, it is provided in another embodiment of the power transmission device according to the invention that for coupling to a power receiving unit, the second end of the second spring element with an input of a mechanical power transmission is connected, in particular a lever transmission, preferably with controlled variable transmission ratio.

Alternatively or additionally, the force transmission device according to the invention with an actuator for impressing at least one driving force and / or a driving torque or torque may be formed, which indirectly or directly coupled to a - eg arbitrary - point of the lever element and in particular with the first end of the second spring element is. In this case, a mediacy by interposition or use of additional mechanical Components are achieved, for example using a transmission, such as a planetary gear.

For mechanical control of the power transmission device, it is provided that the actuator is designed to impart a driving force and is coupled to the first end of the second spring element and the second end of the rod element, preferably via the second rotary push joint to move along the second guide ,

For a particularly stable construction of the power transmission device according to the invention this is formed according to another preferred embodiment with a housing to which the first end of the first spring element fixed, the first and second guides formed and the rotary thrust joints - are mounted - in particular linear - movable on the linear guides.

According to another aspect, the present invention provides a brake assembly having a braking device and more particularly a disc brake operable by applying a force and having a power transmission device formed according to the present invention, the power transmission device being coupled to the braking device as a force receiving unit for power transmission to operate these. In order to adapt the brake arrangement according to the invention to the respective application, a compensating means for wear and / or clearance is formed in a preferred embodiment, in particular as part of the underlying power transmission device.

BRIEF DESCRIPTION OF THE FIGURES Further details, features and advantages of the invention will become apparent from the following description and the figures. Show it:

FIG. 1 shows a schematic side view for the illustration of FIG

Basic principles of the present invention a Embodiment of the invention

Power transmission device.

Figures 2A-E show details of the power transmission device of FIG

1. Figures 3, 4A-B show in a schematic side view and in the form of schematic force-displacement diagrams basic principles of the operation of the present invention.

Figure 5 shows another embodiment of the power transmission device according to the invention and its application in a disc brake.

Figures 6 and 7 show a schematic side view of embodiments of the power transmission device according to the invention with a lever coupling in application to a disc brake. Figure 8 shows a schematic side view of another

Embodiment of the invention

Power transmission device when used in a disc brake with wear compensation.

Figures 9A and 9B show in schematic side view two states of another embodiment of the invention

Power transmission device in use in a disc brake with Lüftspielkompensation.

Hereinafter, embodiments of the invention will be described in detail with reference to FIGS. 1 to 9B. Identical and equivalent as well as equivalent or equivalent elements and components are designated by the same reference numerals. Not in every case of their occurrence, the detailed description of the designated elements and components is reproduced. The illustrated features and other properties can be isolated in any form of each other and combined with each other, without departing from the gist of the invention.

FIG. 1 shows, in a schematic side view in connection with a first embodiment of the force transmission device 100 according to the invention, the principles on which the invention is based.

The power transmission device 100 consists of the core of a first spring energy storage 10 and a second spring energy storage 20, which are mechanically connected by a coupling 30 with each other by means of power coupling and transmission of energy. The mechanical coupling 30 consists of a rod member 33, which is also referred to as a rod, is linear and has a first end 31 and a second end 32.

The spring energy accumulators 10 and 20 are formed in the embodiment of FIG. 1 by a first spring element 13 and by a second spring element 23, respectively. The first spring element 13 has a first end 1 1, which is attached to the surface 74-1 of a wall 74 of an underlying housing 70. Thus, the first end 1 1 of the first spring element 13 is stationary and immovable. The second end 12 of the first spring element 13, however, is movable and not formed stationary. The second end 12 of the first spring element 13 is connected to a hinge point 81 of a first rotary push joint 80, together with the first end 31 of the rod element 33 of the mechanical coupling 30.

The first rotary thrust joint 80 has a joint body 83, one side of which acts as a thrust surface 82 is attached to a surface 71-1 of a wall 71 of the housing 70 such that a first linear guide 41 is present. This means that the joint body 83 of the first rotary push joint 80 can move linearly in the first linear guide 41 and in that case the first end 31 of the rod element 33 of the mechanical coupling 30 and the second end 12 of the first spring element 13 of the first spring energy store 10 Reason whose rotation at the pivot point 81 of the first rotary push joint 80 are linearly moved.

The embodiment of the power transmission device 100 according to the invention according to FIG. 1 furthermore has a second rotary thrust joint 90. The second rotary thrust joint 90 consists of a joint body 93, whose underside serves as a thrust surface 92 and is attached to a surface 72-1 of a housing wall 72 of the housing 70 such that a second linear guide 42 is formed. Along this second linear guide 42, the second thrust joint 90 can thus move linearly. This means that the first thrust joint 80 can move in the z direction in FIG. 1 and that the movement of the second thrust joint 90 takes place perpendicular to it in the x direction. However, these orientations are not mandatory, although mutually perpendicular directions of movement for the linear guides 41 and 42 and correspondingly for the sliding joints are preferred.

The joint body 93 of the second rotary push joint 90 also has a hinge point 91 on which on the one hand a first end 21 of the second spring element 23 of the second spring energy storage 20 and the second end 32 of the rod element 33 of the mechanical coupling 30 are mounted. Due to the rotatability at the hinge point 91, both the second end 32 of the rod element 33 and the first end 21 of the second spring element 23 can be moved with movement of the hinge body 91 with the sliding surface 92 along the second linear guide 42 with the movement of the hinge point 91. Because of the rigidity of the rod element 33, the movements of the hinge point 81 of the first thrust joint 80 with the connected ends 12 and 31 on the one hand and the hinge point 91 of the second thrust joint 90 with the connected ends 32 and 21 on the other hand are forcibly coupled together.

In the embodiment according to FIG. 1, the second end 22 of the second spring element 23 of the second spring energy store 20 is provided with a Power receiving coupling 62 of a power input 60 for coupling to a power unit 61 is connected. Thus, the force absorption 60 can be, for example, a device that is to be used for mechanical work and that is put into operation by transmission of force; it can be, for example, a brake assembly 200, as will be described below , or the like act.

To drive the power transmission device 100 according to the invention, even with highly low-loss interaction mechanisms, for example, the rotary thrust joints 80 and 90 in the linear guides 41 and 42, a certain energy input and effort from the outside be helpful or necessary.

This is achieved in the embodiment of Figure 1 by actuation by means of an actuator 50. This consists of the actual actuator unit 51, which by means of an actuator coupling 52 - in the case of Figure 1 - exerts a force on the second rotary thrust joint 90 to move it along the second linear guide 42. By this displacement, a compression or expansion of the second spring element 23 of the second spring energy storage and - coupled via the mechanical coupling 30 with the rod member 33 - each of the first spring element 13 causes a corresponding force and energy transfer. At the same time there is a force and energy transfer with respect to the power 60. This means that the device underlying the power 60 is driven accordingly.

FIGS. 2A to 2E show, in isolated form, structural details of the first spring energy store 10 with the first spring element 13, the second spring energy store 20 with the second spring element 23, the first and second rotational thrust joints 80 and 90 and the mechanical coupling 30 with the rod element 33.

It should also be noted with reference to FIG. 1 that the second spring energy store 20 represents both the interaction with the second spring element 23 and the interaction with the force take-up 60. In Figures 3, 4A, 4AB and 4B, this unified view is based on the second spring energy storage 20 as a basis. This means that details relating to the energy and power extraction to an external power 60 are not considered in detail here. The illustration of FIG. 3 essentially corresponds to the illustration from FIG. 1, omitting the actuator 50 and the force absorption 60. The second spring energy store 20 is thus representative of the effects which are developed by the second spring element 23 and the force receiving device 60 thus represents a substitute spring representative of the second spring element 23 and the power receptacle 60 and is with its opposite end 21 in the first end 21 fixed to a surface 73-1 of a wall 73, for example, the housing 70, mounted. The illustration of FIG. 3 serves here only to consider the energetic conditions, as explained in detail in connection with the following FIGS. 4A, 4AB and 4B.

From the relationships of FIGS. 1 to 4B, it can be seen that the energetic and force ratios of the second spring energy store 20 can advantageously be chosen so that they correspond to those of the first spring energy store 10. This means, in particular, that the second spring element 23 of the second spring energy store 20 must be designed so that in cooperation with the force absorption 60 and its elastic behavior just the forces and energy moderate ratios of the first spring energy storage device 10 is met. With respect to the spring constants or spring stiffnesses c1 for the first spring element 13, c2 for the second spring element 23 and C representative of the force absorption 60, as will be explained later in detail, the following relationship results

(1 )

^■ (1) clc 2 C

The columns of FIGS. 4A, 4AB and 4B represent different positions A, AB and B of the arrangement of the force-generating device according to the invention 100 and thus various stages with regard to acting forces and the available energies of the power transmission device 100 according to the invention from FIG. 2.

In Figure 4A and the first state A, the first spring element 13 is maximum compressed, whereas the second spring element 25 - as imaginary combination of the second spring element 23 of the second spring energy storage 20 and the power 60 - is relaxed.

In the figure 4B and the second state B is the opposite case. The first spring element 13 is relaxed, whereas the second spring element 25 is compressed to the maximum. FIG. 4AB shows an intermediate state AB, in which the first spring element 13 and the second spring element 25 are each in an intermediate state.

The situations corresponding to states A, B and AB are shown in the uppermost subfigures of Figs. 4A, 4AB and 4B. The respective underlying figures give in the form of force-displacement diagrams respectively acting on the first spring element 13 force F1 and force acting on the second spring element 25 force F2 on the ordinate again, wherein on the abscissa of the way in the sense of compression or extension x or y of the respective spring 13, 25 is applied, and thus the area under the graphs in each case represent the work performed on the springs 13, 25 in the sense of a compression of the spring 13, 25.

These aspects are further explained in detail below.

FIG. 5 shows a schematic side view of another embodiment of the force transmission device 100 according to the invention in connection with its use in a brake assembly 200 with a brake device 150 in the form of a disc brake, which acts as a force receiver 60.

By means of an actuator 50 with an actuator unit 51 and an actuator coupling 52 is by movement of the second rotary push joint 90 via the second spring 23 of the second spring energy storage 20 and the Force receiving coupling 62 to the power 60 in the form of a braking device 150 transmitted power and thus the brake assembly 200 operated. The braking device 150 as a power take-up 60 consists of a pair of brake shoes 61 -1 and 61 -2, which receive between them a brake disc 61 -3, in order to reduce or inhibit in conjunction with this rotation about the axis 61 -4.

During operation of the brake assembly 200, at least a portion of the work done is stored in the first and second spring energy stores 10 and 20 and profitably employed during the reversing process, so that any necessary energetic and force expenditure by the actuator 50 is less than that achieved by the actuator 50 conventional procedure without the power transmission device 100 according to the invention.

The spring element shown schematically in Figure 5 in the region of the braking device 150 schematically shows the elastic properties of the brake shoes 61 -1, 61 -2 and the brake disc 61 -3 as a replacement spring 24 with a spring constant C again, which together with the elastic properties of the first and second spring elements 13 and 23, namely the spring constants c1 and c2, advantageously satisfies the above relationship (1). Figure 6 shows another embodiment of the power transmission device 100 according to the invention used in a brake assembly 200 with a brake device 150 in the form of a disc brake with a brake disc 61-3, which is arranged between a pair of brake shoes 61 -1 and 61 -2, in the rubbing Effect of reducing rotation about the axis of rotation 61 -4.

To increase the force of the actuator 50, the force-receiving coupling 62 is formed here by a lever 62-3 having a first end 62-1 and a second end 62-2 and a pivot point 62-5, on a support 62-4 on a wall 73 of a underlying housing 70 is supported. At the first end 62-1 of the lever 62-3, the second spring element 23 is at its second end 22 attached. To the second end 62-2 of the lever 62-3, the first brake shoe 61 -1 is coupled. Thus, during operation of the actuator 50 and thus when moving the first and second rotary thrust joints 80 and 90, a corresponding displacement and thus force transmission to be ensured. The embodiment according to FIG. 7 also shows the application of a force transmission device 50 according to the invention in connection with a brake arrangement 200 which has a brake device 150 in the form of a disc brake. Again, a power transmission by means of a lever 62-3 is provided as in Figure 6. However, here the hinge point 62-5 is slidably formed within a slot 62-6 of the lever 62-3. The hinge body 62-4 can be displaced in the z-direction along the wall 73 of the housing 70 so as to change the pivot point 62-5 about which the lever 62- 3 can be tilted, and thus the lever lengths, and thus a force or To achieve stiffness adjustment during operation of the disc brake as a braking device 150.

In the embodiment for the brake assembly 200 according to the invention according to FIG. 8, the force-receiving coupling 62 has a wear adjustment 62-7 in order to be able to take account of the wear of the brake shoes 61 -1 and 61-2 as well as the brake disk 61 -3. As a result, the correct setting of the kinematics and thus the spring strokes is achieved with a modified lining thickness. This wear adjustment leads to a change in the length of the connection between the right end of the spring 20 and the left pivot point of the friction lining 61 -1. The change in length is controlled by the stroke of 62-7 compared to the housing. This is effected by the pin in Fig. 8, which projects from the housing 70 in the wear adjuster.

In the embodiment according to FIG. 9, in a brake arrangement 200 with a brake device 150 in the form of a disc brake as a force receiving means 60 in the region of the first rotary push joint 80, a so-called Lüftspielanordnung 84 with a pin 85 and a recess 86 in the region of the first linear guide 41 for engaging Spigot 85 is provided. As a result, the correct coordination of the kinematics and thus the spring strokes is achieved when closing and opening the clearance of the pads.

These and other features and characteristics of the present invention will be further elucidated with reference to the following statements: When using mechanical tensioning devices, as described e.g. be used in friction brakes, mechanical work must be performed during clamping, which is usually lost when relaxing again.

As an example, here is a typical vehicle brake called whose interpretation is carried out so that the driver with his foot - with limited power and limited stroke - can press the brake. Due to the elasticity of the installed components, this can not be done without the use of additional energy sources, e.g. of brake boosters.

The mechanical work that has to be done to tension the brake is lost due to the design when loosening again.

A comparable problem is with spring brakes. Here, the work required to clamp the brake is stored in a spring. To release the brake, however, this work is again to spend.

In addition, if it is required that the period of tensioning or loosening of the clamping device must be very short, for example in ABS or ESP systems, very high powers are required for a short time. In the field of vehicle construction are therefore usually energy storage, for example in the form of pressure accumulators, are used, which allow short-term rapid energy consumption. Conventional pneumatic or hydraulic brake systems used in conjunction with ABS and ESP systems require considerable technical effort (hydraulic or pneumatic brake actuator, pipes, brake cylinders, accumulators, pressure generators, electromagnetic valves), so that the use of electromechanical Force generator was examined. The aim of these developments is to use an electromechanical actuator directly on the caliper and then be able to dispense with the other (hydraulic or pneumatic) components. The already explained short positioning times together with the high mechanical work, however, lead to the fact that the dimensioning of the actuators quickly reaches its limits due to the very short time very high performance.

The invention presented here solves this problem by mechanically storing the mechanical work that is implemented as a power transmission device when clamping or releasing the tensioning device and thus does not have to expend new energy with each cycle.

Assuming a frictionless design with ideal design so that clamping and releasing without any operating force would be possible. This applies in the case of a static analysis. In a fast operation also occur inertial forces. In Figure 1, the basic structure of the device according to the invention is described with reference to an embodiment.

The rod member 33 is connected as at its ends 31, 32 respectively with the rotary thrust joints 80 and 90, which are held in the linear guides 41, 42 as straight guides. Both guides 41, 42 are perpendicular to each other and are, for example part of a housing 70. At the two rotary thrust joints 80, 90 each engage the springs 13 and 23, which are each supported by the housing 70. Both springs 13 and 23 are linearly elastic and have the stiffnesses c1 and c2, which may be the same or adapted to the coupled force absorption 60. Furthermore, by way of example, a force 53 fan - for example, an actuator 50 - located, with the aid of the rod member 33 can be pivoted as a lever. Design and function will be explained with reference to Figures 3, 4A, 4B and 4B. Figures 4A, 4AB and 4B show three positions A, AB and B of the proposed power transmission device 100:

Left column - position A - Figure 4A:

In this position, spring 13 is biased by its length I relative to its relaxed length. This corresponds to their maximum preload force Fmax. Spring 25 is relaxed, as shown in the force diagrams below.

Right column - position B - Figure 4B:

In this position, spring 25 is biased by its length I relative to its relaxed length. This corresponds to their maximum preload force Fmax. Spring 13 is relaxed, as shown in the force diagrams below.

Middle column - transition from A to B - Figure 4AB:

In this intermediate position, both springs 13, 25 are only partially tensioned. Due to the kinematics of the rod element 33 as a lever, there is a fixed relationship between the displacement x of the rotary thrust joint 80 and the displacement y of the rotary thrust joint 90. This relationship is described by equation (2): 1 ² = X ² + y ² . (2)

When using linearly elastic springs 13, 25 with the same stiffness c, this kinematic relationship leads to the fact that, when the rod element 33 is pivoted, the amount of tension energy released from the spring 13 is exactly picked up by the spring 25.

If one adds the clamping energies W1 (x) and W2 (y) indicated in the following equation (3) and furthermore uses the kinematic relationship from equation (2), this results in the sum of a constant tension energy Wges for both springs 13, and 25 together, regardless of the position of the rod element 33, see equation (4). This constant tension energy thus corresponds to the tensioning energy of the spring 13 in the position A as well as the tensioning energy of the spring 25 in the position B.

W ₁ () = - x ² ; W ₂ (y) = - y ² (3) 2 2 ff = W ^ + W ^ y) = - _X ² + - y ² = - (/ ² -) + - = - / ² (4)

2 2 2 2 2 This means that the work released by the pivoting of the rod element 33 by the spring 13 is resumed by the spring 25 according to the hatched area in the diagram for F1 (x), corresponding to the hatched area in the diagram for FIG F2 (y).

The consequence of this is that the rod element 33 as a lever - with an exact design of the arrangement - in any position in equilibrium and consequently only a negligible force 53 fan has to be used according to Figure 1 for its displacement.

In a real implementation of the proposed arrangement is to be expected that both friction in the rotary thrust joints 80 and 90 occur and also an exact design of the springs 13 and 25 only within certain unavoidable tolerances is possible.

As a consequence, the force 53 fan, which must be used to pivot the rod element 33 as a lever, not negligible.

Despite this restriction, however, it can be expected that the arrangement has significant advantages compared to the known procedure. In particular, the services that are needed for a quick tightening or loosening can be kept very small. Furthermore, it is conceivable to incorporate the proposed arrangement including drive directly into a caliper or a brake caliper so as to be able to dispense completely with the above-mentioned additional devices. Figure 5 shows an example of a possible use of the proposed spring accumulator as a force generator of a disc brake. In addition to the components contained in FIG. 1, in addition to the actuator 50, the brake disk 61 -3 with rotation axis 61 -4 and the two brake linings or brake shoes 61-1 and 61-2 are shown.

The spring 23 has a modified stiffness compared to the spring 25. The actuator 50 accomplishes the adjustment of the rod element 33 as a lever by exerting the force 53 fan shown in FIG. 1 on the joint 90. The spring 23 is now supported on the brake disk 61 -3 and the two brake pads 61 -1, 61-2. The pressure force in the spring 23 presses the brake pads 61-1, 61 -2 on the brake disc 61 -3. The stiffness of the brake disc 61 -3 and the brake pads 61 -1, 61 -2 are summarized in Figure 5 model in the spare spring 24.

Since the correct function of the proposed power transmission device 100 with spring actuators 10 and 20 with the smallest possible actuation force 53 Fan identical spring stiffness c of the springs 13 and 23, 24 requires, in this embodiment, the sum stiffness of the series-connected springs 23 with spring stiffness c2 and 24 with Spring stiffness C to be adjusted accordingly so that the relationship (1) -1 ₌ -L ₊ -L ₍₁₎ c1C2C is satisfied, c1 denotes the rigidity of the spring 13.

In the same way, this applies to the stiffnesses of other components not considered here.

The invention relates to a very general power transmission device and e.g. a clamping device, as described exemplarily in Figure 1. An application on brakes is possible, but not mandatory.

There are a number of variants are conceivable, which may relate to an application as a brake actuator. 1. Conceivable is the use of a translation device - for example by means of a lever 62-3 - with the help of the forces in the described arrangement can be reduced. This results in a more compact design of springs 13, 23 and lever 62-3 according to Figures 6 and 7. 2. It is also possible to use a translation device with variable ratio, with the help of the overall stiffness of the spring 23 and 24 to the spring Can be adjusted, as shown in Figure 7: Due to the wear of the pads 61 -1, 61 -2 in a friction brake, the overall stiffness of the springs 23 and 24 change. An adjustable rigidity allows adaptation to be achieved. By way of example, an arrangement is proposed here starting from the lever 62-3 illustrated in FIG. 6, which is supplemented by a displaceable mounting 62-4.

3. Furthermore, various variants of the drive can be thought of by the actuator 50: - First, a linear drive at the hinge points 81 or 91 as shown in Figure 1 or at any other point on the rod member 33 attack as a lever, in which case possibly still another pivoting mechanism could be helpful as the other points do not shift linearly.

- It can be constructed of a linear electric motor, a linear drive.

- Furthermore, a linear drive can be constructed from an electric rotary motor and a spindle drive with or without self-locking.

- Furthermore, a linear drive from an electric rotary motor and a spindle drive and with an additional gear conceivable. - The motor can be designed with or without brake.

- The motor can be equipped with a sensor that measures the angular position or displacement of the motor. Thus, the position of the brake actuator and thus the tensile stress of the brake can be measured. 4. It is also conceivable to receive a wear adjuster 62-7 according to FIG. 8: To compensate for the wear of the brake linings 61 -1, 61 -2 and the brake disc 61 -3, a device 62-7 is possible which adjusts the lost thickness. 5. Alternatively or additionally, the provision of a mechanism 84 for the clearance of the brake pads 61 -1, 61 -2 can be thought of according to Figures 9A and 9B: When a brake is released, the brake pads 61-1, 61 -2 not only relieved, but actually lifted off the brake disc 61 -3. Between the pads 61 -1, 61 -2 and the brake disc 61 -3 then creates a clearance. Since the mechanism 84 proposed here is based on a precise coordination of the spring forces and the kinematics, appropriate compensation must be provided. There are, among others, the following solution options:

(i) A particularly soft tuning of the two springs 13 and 23 is used, so that the influence of the deviation on the operating force 53 Fan due to the clearance can be kept small.

(ii) An additional device 84 according to FIGS. 9A and 9B is provided, which enables the compensation of the clearance. By way of example, here is an arrangement in which the first rotary thrust joint 80 has been extended by an additional function with a recess 86 and a pin 85.

6. Furthermore, in addition or alternatively, the failure of the power supply can be considered: In order to achieve a defined behavior (release or application of the brake) in case of power failure of the brake, additional measures can be taken, eg (i) a targeted unequal design of the springs 13 and 23 and / or (ii) the use of additional springs on the drive which cause the brake to open or close (torsion spring on the rotating part of the motor, linear spring on the linearly displaced part of the drive). LIST OF REFERENCE NUMBERS

10 first spring energy storage 1 1 first end

12 second end

13 first spring element

20 second spring energy storage 21 first end

22 second end

23 second spring element

24 spare spring

25 spare spring

26 second end

30 coupling, mechanical coupling

31 first end

32 second end

33 rod element

41 first linear guide

42 second linear guide 50 actuator

51 Actuator unit

52 Actuator coupling

53 Actuator power fan

60 power input

61 power unit 61 -1 brake shoe, brake pad

61 -2 Brake shoe, brake pad

61 -3 brake disc

61- 4 axis, axis of rotation of the brake disc 61-3 62 power receiving coupling

62- 1 first end

62-2 second end

62-3 lever

62-4 edition

62-5 pivot point

62-6 slot

62-7 wear adjustment

70 housing

71 wall

71 - 2 surface

72 wall

72- 2 surface

73 wall

73-2 surface

74 wall

74-2 surface

80 first rotary push joint

81 pivot point, pivot point

82 thrust surface

83 joint body

84 clearance arrangement

85 cones

86 recess

90 second rotary push joint

91 pivot point, pivot point pushing surface

Articulated body Power transmission device Brake device, disc brake Brake arrangement

spatial direction

Claims

claims:

1. Power transmission device (100),

With:

- A first and a second spring energy storage (10, 20) and

a mechanical coupling (30) of the first and second spring energy stores (10, 20) with each other,

in which:

- the mechanical coupling (30) has a lever element (33) with a first end (31) in connection with the first spring energy store (10) and a second end (32) in connection with the second spring energy store (20),

for movement, the first end (31) of the lever element (33) is coupled to a first guide (41) and the second end (32) of the lever element (33) is coupled to a second guide (42),

- The first and second guides (41, 42) lie in a plane and have non-parallel directions of extension and

- When coupled movement of the first and second ends (31, 32) of the lever element (30) via power coupling between the first and second spring energy storage (10, 20) energy is transferable.

2. Power transmission device (100) according to claim 1,

in which the first and second guides (41, 42):

- Linear guides or substantially linear guides are and / or

- Have mutually perpendicular or substantially vertical directions of extension.

3. A power transmission device (100) according to any one of the preceding claims, wherein: - The first spring energy storage (10) comprises a first spring element (13) having a first end (1 1) and a second end (12),

- The first end (1 1) of the first spring element (13) is arranged stationary and

- The second end (12) of the first spring element (13) is movable and at the first end (31) of the lever element (33) is mounted.

Power transmission device (100) according to claim 2 or 3,

in which the movable second end (12) of the first spring element (13), in particular via a first mediating rotary thrust joint (80), is coupled to the first guide (41).

Power transmission device (100) according to one of the preceding claims,

in which:

- The second spring energy storage (20) has a power receiving unit (60) or is formed thereof and

- The second end (32) of the lever element (33) for transmitting power directly or indirectly to the power receiving unit (60) is coupled or coupled.

A power transmission device (100) according to any one of the preceding claims, wherein:

the second spring energy store (20) has a second spring element (23) with a first end (21) and a second end (22),

- The first end (21) of the second spring element (23) is movably mounted on the second end (32) of the lever element (33) and

- The second end (22) of the second spring element (23) for transmitting power to a power receiving unit (60) is formed coupled or coupled.

7. A power transmission device (100) according to claim 6, in which the movable first end (21) of the second spring element (23), in particular via a second mediating rotary thrust joint (90), is coupled to the second guide (42).

Power transmission device (100) according to one of the preceding claims, when dependent on claims 3 and 6, in which

- The first spring element (13) has a first spring constant (c1) and the second spring element (23) has a second spring constant (c2) and

the first and second spring constants (c1, c2), in particular the relationship (1)

^■ J-! - ^ (1) clc 2 C

where c1 is the first spring constant and c2 is the second spring constant and C is representative of elastic properties of a force receiving unit (60) to which the second spring element (23) is coupled or coupled to its second end (22).

Power transmission device (100) according to one of the preceding claims, when dependent on claim 6,

in which for coupling to a force-receiving unit (60) the second end (22) of the second spring element (23) is connected to an input of a mechanical power transmission (62-3), in particular a lever transmission, preferably with controlled variable transmission ratio.

Power transmission device (100) according to one of the preceding claims,

with an actuator (50) for impressing at least one driving force, which is indirectly or directly coupled to a point of the lever element (33) and in particular to the first end (21) of the second spring element (23). Power transmission device (100) according to claim 10,

wherein the actuator (50) is coupled to the first end (21) of the second spring element (23) and the second end (32) of the lever element (33), preferably via the second rotary push joint (90), along the second guide (42) to move.

Power transmission device (100) according to one of the preceding claims,

with a housing (70) on which (i) the first end (1 1) of the first spring element (13) is fixed, (ii) the first and second guides (41, 42) are formed and (iii) the rotary thrust joints (80, 90) - in particular linear

- Are movably attached to the guides (41, 42).

Brake assembly (200),

With:

- A braking device (150), in particular a disc brake, which is operable by impressing a force and

a power transmission device (100) according to one of claims 1 to 12,

wherein the power transmission device (100) is coupled to the braking device (150) as a power receiving unit (60) for power transmission to operate the same.

Brake assembly (200) according to claim 13,

in which compensating means (84, 62-7) are designed for wear and / or clearance, in particular as part of the underlying power transmission device (100).