EP2205887A2

EP2205887A2 - Clutch-brake combination

Info

Publication number: EP2205887A2
Application number: EP08802653A
Authority: EP
Inventors: Herbert Seeger
Original assignee: Ortlinghaus Werke GmbH
Current assignee: Ortlinghaus Werke GmbH
Priority date: 2007-09-27
Filing date: 2008-09-26
Publication date: 2010-07-14
Also published as: WO2009043544A2; WO2009043544A3; DE102007046104A1; DE102007046104B4

Abstract

The invention relates to a clutch-brake combination (1) in which both the clutch disks (2) and the brake plates (3) run wet. The fluid reservoir of the closed fluid circuit is disposed within an oil-tight housing, inside which the closed circuit is also enclosed. The lubricating-cooling fluid is delivered via drawing pipes (5) which at least temporarily plunge into the lubricating-cooling fluid.

Description

Kupplunqs-brake combination

The present invention relates to a clutch-brake combination according to the preamble of the main claim.

Such a clutch-brake combination are known, see e.g. www.ortlinq.com .com.

Clutch / brake combinations with wet clutch and brake discs have the advantage of unmeasurable wear.

It is by the wet run to a practically permanent system.

However, since the fluid necessary for this always has to be guided from the inside to the outside through the slats, a relatively high construction cost must be operated for the closed fluid circuit.

In this respect, it is known to pump the fluid via the central shaft by means of a rotary feedthrough or the like into the system and after it has left the clutch or brake disks via its outer diameter via a communicating line system again via the rotary inlet to the inner diameter of the slats to pump etc. ,

The lubrication-cooling circuit which is necessary in this respect therefore requires an external pump unit, possibly a heat pump.

BESTÄT1GUNGSKOPIE exchanger and above all a closed line system, which is connected via the rotary inlet with the central shaft of the clutch-brake combination.

It is therefore an object of the present invention to reduce the construction cost of the necessary lubricating-cooling circuit in a clutch-brake combination of the known type with wet-running clutch and brake plates.

This object is achieved by the invention with the features of the main claim.

What is essential is the arrangement of a self-contained circuit of the lubricant or coolant within an oil-tight housing, which also encloses the clutch and the brake plates.

It is therefore a self-contained system within which the central shaft is arranged so that no sealing of the pipe system to the environment is required.

The closed system is completely oil-tight to the environment and the lubrication-cooling circuit is completely housed within the closed system within the oil-tight housing.

Of particular advantage is the arrangement of the scoop lines so that a relative rotation takes place between the scoop lines and the inner wall of the housing.

The Realtivrotation therefore provides a pumping function to pump the lubricating coolant within the closed housing for the purpose of flow through the slats, so that the required wear-free operation is ensured. The scoopers dive with theirs for this purpose

Jam openings ahead in the lubricating cooling fluid, wherein the

Relative movement between the jam openings and the lubricating cooling fluid for promoting the same in the

Creation lines provides.

Only the rotational speed of the scoop lines must be so low that the fluid pressure in the direction of the central shaft is greater than the centrifugal forces acting on the fluid, as long as the reservoir openings dive through the fluid.

By thus forced promotion of the lubricating-cooling fluid via the scoop lines for communicating

Channel system, via which the clutch and brake plates are then supplied from the inside to the outside with the fluid, the lubricating-cooling circuit is closed in itself, so that a constant supply of the fins is ensured with the fluid.

The scoop lines can dive intermittently or continuously through the fluid.

In the case of intermitierendbeaufschlagung is additionally proposed to provide self-closing check valves in the scoop pipes, preferably just behind the jam openings, so that the scoop lines can not be thrown empty as soon as the jam openings no longer dive through the fluid.

On the other hand, constructive measures are conceivable, so that the scoop lines permanently dive through the fluid. Check valves would then have the function of ensuring the emergency running properties of the system for a certain period of time.

This function can be realized by the system, because the amount of fluid delivered between each pair of open lamellae is exposed to a secure pressure potential, which causes a flow to the outside.

The pressure decreasing from the inside outwards therefore allows a certain suction effect, which makes emergency running properties possible at least for a certain period of time.

The operation of such clutch-brake combinations takes place alternately so that in each case only the disk set of the brake or the disk set of the clutch is opened.

However, the open lamella pact must also be lubricated only. The communicating duct system, which is connected to both the clutch and brake disks, ensures that at least the respectively open disk pack is supplied with the fluid.

The resulting between the jam openings and the scooping lines towards the communicating channel system back pressure thus promotes the amount of lubricating cooling fluid required in the respective open plate pack.

Appropriately, the dimensioning of the jam openings and the scoop lines is such that the communicating channel system always an oversupply of lubricating cooling fluid is available, so that the entire clutch-brake combination can be operated permanently and wear-free. Another advantage is that the achievable delivery rate is dependent on the respective speed.

Since the resulting friction power increases with increasing speed, more lubricating cooling fluid must be pumped as the speed increases.

This is ensured by the lubricating system according to the invention, because by the faster dipping of the scoop and the conveyable amount of fluid increases.

In particular, the invention thus ensures that the operation of the clutch-brake combination can be carried out in a wide speed range, without having to fear a lack of lubricant.

The supply of the lubricating-cooling fluid on a diameter in the communicating channel system, which is smaller than the inner diameter of the lamellae, takes place against the centrifugal forces on the fluid in the scoop lines and avoids a dry running of the lamellae as a result of the conveying action.

Consequently, the system according to the invention always provides the safety of a wear-free operation, although the centrifugal forces acting on the fluid within the respective open lamellae would lead to a lubricant depletion from the inner diameter to the outer diameter of the lamellae.

The nachgeförderte amount of fluid through the scoop always takes place with an oversupply, which is present at the communicating channel system and is released depending on the respective open lamellae state exactly between these slats. The effort for the invention, measured by the advantage, is very low.

The scoop pipes may, for example, be designed as simple pipelines provided with back pressure holes on the side with which they advance into the fluid, e.g. a lubricating oil, dip.

Assuming suitable dimensioning, then sets within the scoop lines a promotion function, which to supply the slats to the

Inner diameter via the communicating channel system, wherein the closed circuit due to the

Centrifugal forces in the rotating blades always results of its own accord.

In that regard, the storage openings of the scoop pipes must be arranged on a radius which is outside the maximum radius of the slats to form the lubricant supply system in a closed circuit.

Considering that due to the rotational movement of clutch or. Brake fins the lubricating cooling fluid is always conveyed from the inside to the outside under the influence of centrifugal force, comes to the feature of only a partial filling of the oil-tight housing with the fluid, a special inventive quality.

By the invention, namely, it is ensured that the lubricating-cooling fluid is subjected within the closed housing, in particular, only a small splashing work when the oil-tight housing is only partially filled. This advantage is achieved in that the scoop pipes with their storage openings in advance dive into the fluid and convey it in the direction of the central axis of the clutch-brake combination, where it is needed between the inner diameter and the outer diameter of the slats. Although the flow towards the central shaft, which takes place exclusively within the oil-tight housing, requires a certain excess amount of lubricating cooling fluid, but not after a complete filling of the oil-tight housing.

The oil-tight housing has as far as a tank function, which, depending on the arrangement and a lubricating oil sump is considered.

However, if the oil-tight housing rotatably connected to the drive of the clutch-brake combination and the discharge lines to the brake stator, with a correspondingly measured amount of fluid under all operating conditions on the inner wall of the housing, a liquid jacket form, which rotates together with the housing.

The scoop pipes with their storage openings ahead then dive continuously into the liquid jacket, so that a continuous delivery of lubricating cooling fluid in the direction of the central shaft and from there via the communicating duct system is ensured in the slats.

For this purpose, it is additionally proposed to arrange the scoop pipes essentially radially to the central shaft and to dimension them so that they stay ahead with their stowage openings in the surrounding liquid jacket, as long as the clutch-brake combination rotates. In the following the invention will be explained in more detail with reference to an exemplary embodiment:

Show it:

Fig.l. an inventive clutch-brake combination in axial section

2 shows the clutch-brake combination according to Fig.l in radial section

Unless otherwise stated below, the following description applies to all figures.

The figures show a clutch-brake combination 1. It is such a combination with safety brake.

For this purpose, the brake disks 3, which can be seen in the left-hand part of FIG. 1, are acted upon in the closing direction by a spring-loaded piston 15. The springs 16 are compression springs which displace the piston 15 in the direction of the brake disks 3 as soon as the pressure chamber located to the left of the piston 15 is depressurized.

However, if this pressure chamber is filled with pressurized fluid via the corresponding channel system, the brake opens because the springs 16 are compressed and the piston 15 then acts on the clutch plates 2 in the closing direction, so that the rotational movement originating from the drive 11 is transmitted to the central shaft 14.

With regard to the unspecified details of such clutch-brake combinations with safety brake reference is made to the prior art. See eg www. ortlinghaus. com. It is essential that both the clutch plates 2 and the brake plates 3 run wet in a lubricant-cooling fluid and are supplied for this purpose from a fluid reservoir via a closed circuit, at least if necessary, with fluid. If necessary in the scope of the present application means that the respective open lamellae are flowed through by the lubricating-cooling fluid, so that there is fluid friction between the adjacent friction partners.

Due to the centrifugal forces between the inner diameter and the outer diameter of the respective lamellae, therefore, the lubricating cooling fluid must be conveyed from inside to outside through the lamellae.

This must be done in a closed circuit.

For this purpose, both the clutch plates 2 and the brake plates 3 are enclosed by an oil-tight housing 4, within which also the closed circuit is included.

This means that the entire supply of lubricating cooling fluid takes place exclusively within the closed housing 4, which in turn is very easy to seal with the environment.

In particular, it does not require the supply of lubricating cooling fluid any costly rotary input into the housing 4, because the entire amount of lubricating cooling fluid is within the housing 4.

In this case, the heat generated during the rubbing process, which is initially absorbed by the fluid, can be released via the outer surface of the housing 4 to the environment. The oil-tight housing 4 therefore serves as a fluid container on the one hand and on the other hand as a cooling unit.

For conveying the lubricating-cooling fluid are scoop pipes 5, which are arranged such that between them and the inner wall 6 of the housing takes place a relative rotation.

To the lubricating-cooling fluid as a result of this relative rotation as needed to the minimum diameter of the clutch or. In addition, to promote brake disks, 5 stowage openings 7 are provided on the scoop pipes, so that the scoop pipes 5 with their stowage openings 7 dive ahead in the relative rotation in the fluid.

In this case, the fluid is conveyed into the scoop pipes 5 as a result of the pending at the jam openings 7 back pressure. The scoop pipes 5 in turn open in the vicinity of the central shaft 14 in a communicating duct system 9, from where the lubricating cooling fluid is conveyed to the inner diameters of the clutch disks 2 and brake disks 3.

From there, the fluid can then always flow over the respective open plate pairings to ensure the state of liquid friction.

In this case, the scoop lines-depending on the arrangement within the oil-tight housing 4- only temporarily dive through the fluid.

To throw out the scoop pipes in this case

5 to prevent during that time in which they do not drive with their storage openings 7 through the fluid are in Direction to the jam openings 7 self-closing check valves 10 are provided.

These self-closing check valves 10 may also be provided for the case that the scoop pipes 5 continuously dive through the fluid.

In the exemplary embodiment shown, this is achieved in that the oil-tight housing is rotatably connected to the drive 11 of the clutch-brake combination 1 via the indicated left on the housing 4 located threaded joint.

For example, the drive is a flywheel of a press driven by the clutch / brake combination.

The oil-tight housing therefore carries along the rotational movement of the drive 11 constantly, so that at a corresponding partial filling of the housing 4, a circumferential liquid jacket 13 is formed on the inner wall 6 of the housing 4, which rotates in principle with the rotating housing 4 with.

In this case, the jam openings 7 of the scoop pipes 5 immerse permanently into the liquid casing 13, so that the scooping pipes 5 are constantly filled to their smallest diameter with the lubricating cooling fluid.

In this case, the smallest diameter to which the scoop lines 5 lead into the communicating channel system 9 lies on a smaller diameter than the smallest diameter 8 of the coupling 2 or brake plates 3.

Thus, after the lubricating cooling fluid has left the scoop pipes 5 at its inner end to enter the communicating duct system 9, the fluid will pass through there centrifugal force automatically to the and then promoted by the slats.

In this development of the invention with the rotating housing 4 there is in particular the advantage of increased convection on the rotating surface of the housing 4.

The improved convection leads to a good cooling effect, which also increases with increasing speed of the housing 4 also.

These features are therefore system compatible, since with increasing speed of the clutch-brake combination and the dissipated frictional heat increases.

In addition, FIG. 1 shows, in conjunction with FIG. 2, the arrangement of the scoop lines 5 with respect to the central shaft 14.

On the one hand, the scoop lines are provided diametrically in pairs and on the other hand they are firmly connected to the brake stator 12.

The brake stator 12 is thus, as well as the scoop lines 5, within the housing 5, which rotates with the drive 11, rigid.

The present invention is therefore characterized by an easy to implement construction in the usual

Clutch-brake combinations, regardless of whether the

Drive 11 is operated with flywheel or without

Flywheel with appropriately dimensioned servomotors. Reference character list:

I Clutch / brake combination 2 clutch plates

3 brake discs

4 oil-tight housing

5 scoops

6 inner wall 7 Jam opening

8 small diameter

9 channel system

10 check valve

II drive 12 brake stator

13 liquid coat

14 central shaft

15 pistons

16 spring

Claims

Claims;

1. clutch-brake combination (1) in which both the

Clutch and the brake plates run wet and are supplied for this purpose from a fluid reservoir via a closed circuit with fluid, characterized in that both the clutch (2) - and the brake plates (3) enclosed by an oil-tight housing (4) within which the closed circuit is also enclosed, wherein the oil-tight housing (4) serves as a fluid container and wherein scoop lines (5) are provided and arranged such that between the scoop lines (5) and the inner wall (6) of the housing (4 A relative rotation takes place, wherein the scoop lines (5) have stowage openings (7) with which they at least temporarily dive into the fluid during the relative rotation and wherein the scoop lines (5) on a smaller than the smallest diameter (8) of the coupling (2 ) - or brake plates (3) open into a communicating with this channel system (9).

2. clutch-brake combination according to claim 1, characterized in that the scoop pipes (5) only temporarily dive through the fluid and in the direction of the Jam openings (7) self-closing check valves (10).

3. clutch-brake combination according to claim 1, characterized in that the scoop pipes (5) dive continuously through the fluid.

4. clutch-brake combination according to one of claims 1 to 3, characterized in that the oil-tight housing (4) is only partially filled with the fluid.

5. clutch-brake combination according to one of claims 1 to 4, characterized in that oil-tight housing (4) rotatably with the drive (11) of the clutch-brake combination (1) and the scoop lines (5) with the brake stator ( 12) are connected.

6. clutch-brake combination according to claim 5, characterized in that the amount of fluid is so dimensioned that under the operating conditions on the inner wall (6) of the housing (4) here a liquid jacket (13) is formed.

7. clutch-brake combination according to claim 6, characterized in that the scoop lines (5) with respect to the central shaft (14) of the clutch-brake combination (1) are arranged radially.