DE102016204918A1 - Integrated rotor brake - Google Patents

Abstract

Rotor brake device for a hydrodynamic transmission unit with a brake pad (1, 1a, 1b, 1c) and a contact pressure element (5, 5a, 5b, 5c, 5d), designed such that upon activation of the rotor brake, the contact pressure element (5, 5a, 5b, 5c , 5d) presses the brake pad (1, 1a, 1b, 1c) against a rotational element (13) of the hydrodynamic gear unit and thus the rotational element (13) can be braked, wherein the contact pressure element (5, 5a, 5b, 5c, 5d) Hydraulic cylinder (5, 5a, 5b, 5c, 5d) which is at least partially integrated in a channel plate (3), wherein at least one supply line (33, 33a) for controlling the hydraulic cylinder (5, 5a, 5b, 5c, 5d) is present, which is at least partially integrated into the channel plate (3), and wherein the channel plate (3) further channels (30, 31, 32), which serve to control and / or supply of further transmission elements.

Description

The invention relates to a rotor brake device for a hydrodynamic transmission unit with a brake lining and a pressure element designed so that the pressing element presses the brake pad against a rotational element of the hydrodynamic gear unit upon activation of the rotor brake and thus the rotational element can be braked.

In addition, the invention relates to a hydrodynamic transmission unit with a corresponding rotor brake device, wherein the transmission unit has a hydrodynamic coupling and / or a hydrodynamic converter, as well as at least one mechanical transmission stage

A hydrodynamic transmission with a rotor brake device and a corresponding rotor brake device are for example made DE 4226665 A1 known. It shows a hydrodynamic transmission with a hydrodynamic coupling, a hydrodynamic converter and several mechanical gear stages, as used in particular for rail vehicles. The hydrodynamic torque transmission takes place by the rotation of a primary-side impeller is transferred via the oil filling to a secondary-side impeller. If no torque transmission take place, the oil is discharged from the intermediate space. However, even with an empty space through the turbulence of the air between the two rotor wheels transmit a certain torque, so that the secondary side connected part of the transmission would rotate. In order to avoid this, for example in order to enable interference-free switching in a downstream mechanical gear stage, the secondary side must be able to be braked in certain operating states. For this purpose, the described rotor brake is provided, which in this case is indirectly connected to the secondary shaft of the hydrodynamic transmission component and thus can decelerate and hold the secondary side.

Rotor brakes are particularly known which can be activated electromagnetically or which are designed as a gear pump with controllable filling.

A disadvantage of the known rotor brakes is that they cause great additional construction and assembly costs and are relatively expensive, because they are needed only rarely and in a few operating conditions. In addition, they require additional space.

The object of the invention is to develop a suitable and reliable rotor braking device for a hydrodynamic transmission unit, which is designed simpler and cheaper and which avoids the aforementioned disadvantages.

The object is achieved by an embodiment according to claim 1. In this embodiment, the pressing member is a hydraulic cylinder which is at least partially integrated in a channel plate, wherein at least one supply line for controlling the hydraulic cylinder is present, which is at least partially integrated in the channel plate, and wherein the channel plate has further channels, which are for driving and / or supply of other transmission elements serve. The use of a hydraulic cylinder as a contact element for the rotor brake offers the enormous advantage that the already existing oil circuit can be used for control. This eliminates the separate and complex electromagnetic control of the rotor brake, as well as the separate cable harness for it. By the hydraulic control, a larger displacement and a greater contact pressure of the brake pad is possible, in particular, the two parameters are independent of the design of the magnet. Thus, only a standard solenoid valve for control and no specially adapted solenoid for the contact pressure is more necessary. At the same time the required space is significantly reduced. There are no components mounted on the outside of the gear unit and no separate housing for the rotor brake. Another advantage results from the integration of the supply line of the hydraulic cylinder in the channel plate, which is already designed so that other transmission elements can be supplied with control pressure or lubricant or equipment. This eliminates extra oil lines for controlling the hydraulic cylinder. Only further lines or channels in the channel plate are needed. The channel plate is connected to the transmission housing. It is designed so that a connection to the oil passage in the gear housing is produced, thus ensuring a continuous supply of hydraulic fluid and a corresponding return. On the channel plate shut-off, metering or control valves, such as solenoid valves, for the various channels, for example, control channels, or sub-circuits may be appropriate. The channel plate may be provided with a cover plate which covers and tightly seals channels and supply lines. Due to this multi-part design, the channel plate is easier to manufacture.

Integration of the hydraulic cylinder into the channel plate is understood to mean that the braking force applied when the brake is activated is picked up by the channel plate, since the pressure element is supported thereon. The channel plate serves as a support structure for the brake components. Accordingly, the channel plate must be sufficient dimensioned and securely attached to the transmission housing. The rotor brake device can be preassembled on the channel plate and mounted as a unit with the channel plate, which is a great simplification. For the control of the rotor brake, a solenoid valve is preferably present, which controls the supply of hydraulic fluid into the pressure chamber or the pressure therein.

By the hydraulic cylinder, a higher Anpress- and thus braking force can be generated as with previously usual rotor brakes. Hydraulic cylinders are known per se. This has a piston and a housing in which the piston can move back and forth. The hydraulic cylinder is controlled via a pressure chamber into which hydraulic fluid can be supplied via the supply line, so that a pressure is exerted on the piston in order to displace it and apply the contact pressure. Hydraulic cylinders and solenoid valves are available as standard and standard parts, resulting in lower costs than individually designed and manufactured components.

The pressing element can act directly or indirectly on one or more force-transmitting intermediate elements, such as levers, connecting parts or the like, on the brake pad.

There are basically two different ways of operating the rotor brake:
On the one hand, the closing principle: The rotor brake is not activated when the rotation element is at a standstill. That is, the brake pad is not in contact with the rotary member, the rotor brake is open. This principle is particularly suitable for systems in which a pressure for the hydraulic system is built up only during operation by the transmission dynamics. On the other hand, the opening principle: Here, the rotor brake is closed when the rotation element is stationary, the brake pad is against the rotating element and holds it firmly. If you want to switch to traction, the pressure on the hydraulic cylinder is reduced to move the brake pad away from the rotating element and to open the rotor brake. This principle requires a system that can generate pressure in the hydraulic system independently of the transmission dynamics.

Further advantageous features of the embodiment according to the invention, which make the rotor brake device even easier and cheaper, can be found in the dependent claims.

Preferably, the hydraulic cylinder has a housing which is completely or at least partially formed by the channel plate. That is, the piston is guided in the channel plate and / or the pressure chamber is at least partially formed by the channel plate. This offers the advantage of a very simple design.

Additionally or alternatively, the hydraulic cylinder may comprise a sliding bush, which is completely or at least partially integrated in the channel plate. In this sliding bush, the piston of the hydraulic cylinder is guided. By using a sliding sleeve, the surface quality for the guidance and sealing of the piston can be made easier than if the recess in the channel plate itself must be machined so accurately.

Furthermore, there may be a support which is part of the hydraulic cylinder and forms at least a part of the housing in which the piston can move back and forth, and which is connected to the channel plate. As a result, a hydraulic cylinder with a longer piston can be used without the channel plate must be made particularly thick at the installation point.

It can be advantageous if the supply line for controlling the hydraulic cylinder is completely integrated in the channel plate. In this case, both the supply of the hydraulic fluid and the pressure chamber is arranged on the piston of the hydraulic cylinder in the channel plate. This results in a particularly simple design without too many attachments.

The brake lining, which comes into contact with the rotary element during braking, may preferably be arranged on a lever which is pivotable about a pivot point and which has an engagement point for the hydraulic cylinder. As a result, the braking force exerted on the rotating element and the path of movement that the brake pad can perform are specifically influenced constructively. In addition, a simple way to reset the brake can be realized.

In particular, the lever may be designed so that the point of attack of the hydraulic cylinder is farther from the fulcrum than the brake pad. As a result, the braking force is increased with respect to the force exerted on the lever by the pressing element. Alternatively, the lever may be designed so that the point of attack is located closer to the pivot point than the brake pad. As a result, a larger movement of the brake pad towards the rotational element is possible, as it corresponds to the pure displacement of the piston in the hydraulic cylinder.

Particularly preferred is a restoring element, in particular a return spring, present, which acts on the lever such that it can act in the opposite direction to the hydraulic cylinder. As a result, the brake pad is moved away from the rotational element when the pressure in the Pressure chamber of the hydraulic cylinder falls below a certain threshold (NO principle). Thus, a targeted control of the brake with a single-acting hydraulic cylinder is possible. Equally well, a return element may be present, which is arranged so that it can move the lever in the direction of the rotary member and thereby cause the brake to close. When the pressure in the pressure chamber exceeds a certain threshold, the brake pad is moved away from the rotating member, whereby the brake is opened (NC principle). In the version described first, the brake is open without applied pressure and in the second version, the brake is closed without applied pressure.

Even if no lever is present, a return element may be present, which acts on the piston of the hydraulic cylinder, so that the brake pad is moved away from the rotating element when the pressure in the pressure chamber falls below a certain threshold. In an embodiment according to the second version described above, the return element acts so that the brake pad is moved away from the rotating member when the pressure exceeds a certain threshold.

Alternatively to the arrangement on a lever, the hydraulic cylinder may be designed with a piston on which the brake lining is arranged. The piston thus presses the brake pad directly onto the rotating element. So a particularly space-saving design is possible.

In order to get a larger contact surface between brake pad and rotating element, it may be advantageous if two brake pads are present, which can be pressed against the rotary member. As a result, the wear is distributed over more area; so a longer service life is possible.

The provision of the brake can be realized in an advantageous manner with a hydraulic cylinder which is designed as a double-acting cylinder. Such a hydraulic cylinder has a second pressure chamber, which can be filled with hydraulic fluid, so that the piston is moved in the opposite direction. Depending on the pressure chamber in which the higher pressure is present, the brake can be activated or opened. Preferably, two solenoid valves or a suitable switching valve are used to control in this case.

Brake lining is generally understood to mean an area which can be brought into contact with the rotating element and is suitable for generating a braking frictional force. As the material for the brake lining, for example, an impregnated fabric of non-magnetic metal or resin-bonded magnetic metal or sintered friction material is particularly suitable.

Particularly advantageously, a hydrodynamic transmission unit can be equipped with the rotor brake device according to the invention. The invention therefore also relates to a hydrodynamic gear unit with a hydrodynamic coupling and / or a hydrodynamic converter, as well as with at least one mechanical gear stage. The object is achieved by an embodiment according to claim 13, that is, characterized in that a rotor brake device according to the invention is provided. The corresponding rotor wheel associated with the rotor brake can be retained when there is no oil in the space, and thus shifting in the mechanical gear stage is possible.

In particular, the mechanical gear stage may be a reverse gear to reverse the direction of rotation at the same ratio or a mechanical transmission or a combination of both. Particularly preferably, the mechanical gear stage to a neutral position, which is located between two to be switched gear positions.

It is advantageous if the rotor brake with its brake pad can act directly on the impeller of the hydrodynamic coupling or the hydrodynamic converter. For this purpose, the embodiment may be designed such that the rotation element, on which the rotor brake can act, is formed by the rotor wheel on the secondary side of the hydrodynamic coupling or of the hydrodynamic converter.

Alternatively, it may be advantageous that the rotation element, on which the rotor brake can act, is non-rotatably connected via a shaft and / or a gear stage with the impeller on the secondary side of the hydrodynamic coupling or the hydrodynamic converter. As a result, the braking force of the rotor brake is transmitted indirectly to the rotor wheel.

By way of embodiments, further advantageous embodiments of the invention will be explained with reference to the drawings. The features mentioned can not only be implemented advantageously in the illustrated combination, but also individually combined with each other. The figures show in detail:

1 Cross section of a hydrodynamic transmission unit according to the invention with rotor brake device

2a an embodiment of an integrated into the channel plate hydraulic cylinder for a rotor braking device according to the invention

2 B further embodiment of an integrated into the channel plate hydraulic cylinder for a rotor brake device according to the invention

2c another embodiment of an integrated into the channel plate hydraulic cylinder for a rotor brake device according to the invention

3a Section of a rotor brake device according to the invention

3b Section of another rotor brake device according to the invention

3c Detail of still a rotor brake device according to the invention

4a Another variant of a hydraulic cylinder for a rotor brake device

4b Another variant of a hydraulic cylinder for a rotor brake device

4c Another variant of a hydraulic cylinder for a rotor brake device

The figures are described in more detail below.

In 1 is shown a schematic cross section through a hydrodynamic transmission unit. Of the various transmission elements, only the rotation element 13 shown. Other existing transmission elements such as hydrodynamic components or mechanical transmission stages are not shown. The rotation element 13 may preferably be the impeller on the secondary side of a hydrodynamic coupling or a hydrodynamic converter. However, it may also be a rotation element, which is rotatably connected to the secondary side of the aforementioned hydrodynamic component via a shaft and optionally one or more mechanical gear stages. It is important that the impeller can be held, in which the rotation element is braked.

The gearbox 10 is with an oil pan 14 completed. The channel plate 3 lies in the gearbox housing 10 and is so connected to it, that in the channel plate 3 existing channels and supply lines for hydraulic fluid 30 . 31 . 32 . 33 with the oil supply 40 . 41 and the oil removal 42 . 43 are connected in the transmission housing. So a continuous supply of hydraulic fluid and lubricant is possible. In the channel plate 3 There is a network of different channels, supply lines or hydraulic circuits. As a result, various transmission element can be supplied with lubricant, with control means or resources. For example, a retarder or a converter can be filled or emptied with hydraulic fluid or a hydraulic cylinder can be controlled with pressure. The in the channel plate 3 existing channels are through the cover plate 2 closed from below. This allows a simplified production for the channel plate 3 , To the channel plate 3 are different valve bodies 11 . 12 , for example, for solenoid valves, grown. There may also be other control elements.

As a pressing element for the rotor brake is a hydraulic cylinder 5 in the channel plate 3 integrated. The piston 55 the hydraulic cylinder is guided in the illustrated embodiment in a housing which is at least partially formed by the channel plate. There is also a holder 4 present from the bottom of the channel plate 3 is attached and the the lower portion of the housing for the hydraulic cylinder 5 forms. It's just as possible to have a hydraulic cylinder 5 with its own housing in the channel plate 3 use. The supply line for the control of the hydraulic cylinder 5 runs partly as a supply line 33 in the channel plate and partly as a supply line 34 in the holder. The supply line may be a channel or a bore or something similar. Through the supply lines 33 . 34 becomes the pressure chamber 50 under the piston 55 filled with hydraulic fluid or emptied.

The rotor brake device has a bearing block 9 on that on the channel plate 3 is attached and on which a lever 6 is rotatably mounted. On the lever 6 is a brake pad 1 appropriate. To activate the runner brake, the pressure chamber becomes 50 filled with hydraulic fluid to a certain pressure. This will cause the piston 55 out of the case and against the lever 6 , and thus the brake pad 1 against the rotation element 13 pressed The acting braking force is increased with respect to the contact force of the hydraulic cylinder, since the point of attack of the hydraulic cylinder on the lever 6 further from the fulcrum 7 is removed as the brake pad 1 , About a return element 8th - shown here as a spiral spring - is the brake pad 1 from the rotary element 13 pushed away when the pressure in the pressure chamber 50 falls below a corresponding value. Thus, the rotor brake can be activated and deactivated via the pressure control of the hydraulic fluid.

In the 2a . 2 B and 2c are different variants for the design of the hydraulic cylinder 5 and shown for the supply line to this. The different design features may also be different Compilation can be combined as presented. 2a shows a variant in which the piston 55 in a sliding bush 51 is guided. The sliding bush is partly in the channel plate 3 integrated and the other part in the holder 4 added. Due to the training with additional bracket 4 can be a longer piston 5 can be used without requiring a thicker channel plate 3 is necessary. Through the additional sliding bush 51 In addition, a particularly elaborate machining of the surfaces for the seat of the piston 55 in the channel plate 3 be waived. The supply line 33 gets the hydraulic fluid from the oil supply 40 in the gearbox 10 and directs it via the supply line 34 in the holder further into the pressure chamber 50 under the piston 55 ,

2 B shows a variant in which the supply line 33a completely as a hole in the channel plate 3 is formed and directly into the pressure chamber 50 which also flows within the channel plate 3 located. To cover other channels can still a cover plate 2 to be available.

In the 2c is another variant without additional support for the hydraulic cylinder 5 to see. The supply line 33 is designed as a channel of the cover plate 2 is closed. The supply line 33 in turn flows directly into the pressure chamber 50 under the piston 55 ,

Both for the variants 2 B or 2c can as well as in 2a shown a sliding bush are provided, in which the piston 55 is guided and can form a part of the housing.

The 3a and 3b represent two further arrangements for the rotor brake device with lever. The execution in 3a differs from the according to 1 in particular in that the return element 8a is arranged at another location. The illustrated coil spring 8a pulls the lever 6a and the brake pad thereon 1 from the rotary element 13 away when the pressure in the pressure chamber 50 falls below a certain value. When the runner brake is activated, the piston pushes 55 due to the pressure in the pressure chamber 50 the lever 6a and thus the brake pad against the rotating element 13 , For receiving the hydraulic cylinder 5 in the channel plate 3 this is executed thickened at the appropriate place. The attachment of the lever 6a may alternatively be used with a separate bearing block, as in 1 is shown with a bearing block 9a take place, which is an integral part of the channel plate 3 is.

3b shows a variant in which the point of attack of the hydraulic cylinder 5a on the lever 6b closer to the fulcrum 7b lies as the brake pad 1 , This allows the brake lining to cover a larger path without the need for a longer piston 55a is necessary. To get a better contact between pistons 55a and levers 6b to achieve at the point of attack is the piston 55a obliquely executed at the point of attack, such that the slope of the inclination of the lever 6b when pressing the brake pad 1 to the rotation element 13 equivalent.

In 3c is the brake pad 1a directly on the piston 55b of the hydraulic cylinder 5b appropriate. Again, the hydraulic cylinder is so in the channel plate 3 integrated, that no additional bracket is needed, instead, the channel plate is designed in this area accordingly thicker. A reset element is not explicitly shown; but it may for example be designed as a spring and be provided so that it directly on the piston 55b acts.

The finishes in 4a and 4b show variants with double-acting hydraulic cylinders. These double-acting hydraulic cylinders 5c . 5d point next to the first pressure chamber 50 for pressing the brake pad 1 another second pressure chamber 52 on, over which the piston 55c . 55d in the opposite direction away from the rotating element 13 can be pressed. In 4a is additionally on the piston 55c a sealing element 53 shown, which seals the piston chamber and prevents oil leakage upwards. This requires the housing wall in the channel plate 3 be executed in this area not sealed to the piston. In 4b an embodiment is shown, which is a holder of the hydraulic cylinder 5d which is from the top of the channel plate 3 is attached and the piston 55d receives. On the side is a connection hole for a supply line for filling and emptying the pressure chamber 52 shown with hydraulic fluid. The channel plate 3 forms a boundary wall of the pressure chamber 50 of the hydraulic cylinder 5d and contains an integrated supply line to this pressure chamber 50 which is not explicitly shown.

The 4c represents again another inventive type of rotor brake device. For one, here are two brake pads 1c present, so that a larger braking surface can be used, and on the other a different return mechanism is applied. The two brake pads 1c are arranged on a support structure, with the channel plate 3 connected is. If now the runner brake is activated, the hydraulic cylinder presses 5 with the piston on the support structure, which is deformed by it and so the brake pads 1c to the rotation element 13 suppressed. Will the pressure in the pressure chamber 50 again reduced, the support structure deforms back to the starting position, so that the brake pads 1c no longer with the rotation element 13 are in contact.

LIST OF REFERENCE NUMBERS

1, 1a, 1b, 1c

 brake lining

2

 cover

3

 channel plate

4

 bracket

5, 5a, 5b, 5c, 5d

 hydraulic cylinder

6, 6a, 6b

 lever

7, 7a, 7b

 pivot point

8, 8a

 Return element

9, 9a

 bearing block

10

 gearbox

11, 12

 valve housing

13

 rotating member

14

 oil pan

30, 31, 32

 Oil channel in channel plate

33

 Supply line in channel plate

34

 Supply line in holder

40, 41

 Oil supply in the gearbox

42, 43

 Oil removal in the gearbox housing

50

 pressure chamber

51

 bush

52

 further pressure chamber

53

 sealing element

54

 support structure

55, 55a, 55b, 55c, 55d

 Piston of the hydraulic cylinder

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 4226665 A1 [0003]

Claims (15)

Rotor brake device for a hydrodynamic transmission unit with a brake lining ( 1 . 1a . 1b . 1c ) and a pressing element ( 5 . 5a . 5b . 5c . 5d ), designed such that upon activation of the rotor brake, the pressing element ( 5 . 5a . 5b . 5c . 5d ) the brake pad ( 1 . 1a . 1b . 1c ) against a rotary element ( 13 ) presses the hydrodynamic transmission unit and thus the rotational element ( 13 ) can be braked, characterized in that the pressing element ( 5 . 5a . 5b . 5c . 5d ) a hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ), which at least partially into a channel plate ( 3 ), wherein at least one supply line ( 33 . 33a ) for controlling the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) is present, at least partially in the channel plate ( 3 ), and wherein the channel plate ( 3 ) other channels ( 30 . 31 . 32 ), which serve to control and / or supply of further transmission elements. Apparatus according to claim 1, characterized in that the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) has a housing which completely or at least partially through the channel plate ( 3 ) is formed. Device according to claim 1 or 2, that the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) a sliding bush ( 51 ), which completely or at least partially into the channel plate ( 3 ) is integrated. Device according to one of the preceding claims, characterized in that the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) a holder ( 4 ), which with the channel plate ( 3 ), wherein the holder ( 4 ) forms at least a part of the housing. Device according to one of the preceding claims, characterized in that the supply line ( 33a ) for controlling the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) completely into the channel plate ( 3 ) is integrated. Device according to one of the preceding claims, characterized in that the brake pad ( 1 . 1a . 1b ) on a lever ( 6 . 6a . 6b ) arranged around a fulcrum ( 7 . 7a . 7b ) is pivotable and the an attack point for the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) having. Device according to claim 6, characterized in that the lever ( 6 . 6a ) is designed so that the point of attack further from the fulcrum ( 7 . 7a ) is removed as the brake pad ( 1 . 1a ). Device according to claim 6, characterized in that the lever ( 6b ) is designed so that the point of attack closer to the fulcrum ( 7b ) is arranged as the brake pad ( 1b ). Device according to one of claims 6 to 8, characterized in that a return element ( 8th . 8a ), in particular a return spring ( 8th . 8a ), which is so at the lever ( 6 . 6a . 6b ) attacks it in the opposite direction to the hydraulic cylinder ( 5 . 5a . 5b . 5c . 5d ) can act. Device according to one of claims 1 to 5, characterized in that the hydraulic cylinder ( 5b . 5c . 5d ) a piston ( 55b . 55c . 55d ), on which the brake pad ( 1a . 1b . 1c ) is arranged. Device according to one of the preceding claims, characterized in that two brake pads ( 1c ) are present, which against the rotation element ( 13 ) can be pressed. Device according to one of the preceding claims, characterized in that the hydraulic cylinder ( 5c . 5d ) is designed as a double-acting cylinder. Hydrodynamic transmission unit with a rotor brake device according to one of the preceding claims, wherein the transmission unit has a hydrodynamic coupling and / or a hydrodynamic converter, as well as at least one mechanical transmission stage. Hydrodynamic transmission unit according to claim 13, characterized in that the rotation element ( 13 ), on which the rotor brake can act, is formed by the impeller on the secondary side of the hydrodynamic coupling or the hydrodynamic converter. Hydrodynamic transmission unit according to claim 13, characterized in that the rotation element ( 13 ), on which the rotor brake can act, is non-rotatably connected via a shaft and / or a gear stage with the impeller on the secondary side of the hydrodynamic coupling or the hydrodynamic converter.

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