KR20090046937A - Clutch - Google Patents

Abstract

The present invention relates to a clutch having an input side connection for a drive motor and an output side connection for an output shaft and a set of disks disposed therebetween, the disk set being sent in friction through the piston-cylinder unit. . Importantly, the disc set is operated through two piston-cylinder-units which complement each other additionally.

Description

Clutch {CLUTCH}

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

Such clutches are generally known.

Typically such a clutch is arranged between the drive motor, for example the combustion engine and the output, and the output as long as the clutch disc is in a state of sliding friction in order to transmit only a portion of the drive side torque to the output side. The negative rotational motion must be coupled with the rotational motion of the drive motor via the clutch or must be separated from the rotational motion of the drive motor.

In such a clutch, for example, the output side is formed as a shaft, preferably as a hollow shaft, while the drive side is coupled to rotate integrally with the coupling housing.

There is a set of discs between the drive side and the output side, in which case the number of discs used each affects the torque to be transmitted and the thermal performance of the clutch.

Higher torque also requires a larger number of disks.

In each clutch state (open, closed, synchronized or trolling), the disc set delivers no torque at all, or delivers maximum torque, depending on the pressing force acting individually according to the basic law of sliding friction. Alternatively, the compression force must be adjustable to deliver only a portion of the maximum torque.

Furthermore, there are also applications such as in the field of marine clutches where the speed of the ship propeller has to be slower than the minimum possible speed caused by the engine, for example.

This operating state appears, for example, when the position of the ship must be fixed in case of inflow, so that the speed of the ship propeller must be adjustable independent of the speed of the motor.

Such requirements can be fully met through conventional clutches for the purpose of use in the field of shipping industry, but the object of the present invention is to reduce the control cost of such clutches.

The problem is solved by the features of the main claims according to the invention.

The advantage obtained from the present invention is that higher torque can be transmitted without actually varying the overall size of such clutch.

In particular for the purpose of use as a marine clutch, it is preferred that if the pressure level inside the pressure chamber of the second piston-cylinder-unit is relatively higher, preferably via a control circuit acting on a relatively smaller piston face It is recommended to implement the trolling state.

The present invention starts from the following content:

In principle, each clutch is loaded by two different operating states.

In the first operating state the clutch is in the engaged state, that is, the rotational motion of the drive engine is transmitted to the rotational motion of the output shaft without sliding.

In the case of a marine clutch the operating state corresponds, for example, to sailing from Hamburg to New York.

Another operating state appears when, for example, the ship clutch is forced to perform a predetermined sliding action in order to fix the position of the ship.

Therefore, in the first operating state, a high compressive force is required to operate the disk set without sliding.

In the second operating state, there is a need for a sensitive adjustment operation that must be performed in a pressing force state that causes the clutch to slide.

Such operating states are implemented according to the invention, on the one hand, by means of which the second piston-cylinder-unit can use a relatively smaller pressure application surface, and on the other hand a relatively higher pressure 2 piston-cylinder-unit is provided.

The relatively higher pressure level is naturally more precisely regulated, while the relatively smaller working surface of the piston-cylinder-unit limits the upper limit of the pressing force in sliding even though the pressure level is relatively higher.

Thus, another feature of the invention is that in the sliding operation the clutch is preferably operated by a second piston-cylinder-unit, which is preferably designed to be relatively smaller in size while in the inserting operation, ie a fixed engagement between the drive side and the output side. In this case, it is a fact that additional clamping force is provided to the two piston-cylinder-units by this fixed engagement.

However, if the compressive force necessary for the static friction due to the associated pressure surface can be realized even with a relatively smaller pressure level, the clutch is designed to be of a corresponding size in the fixedly inserted operating state, irrespective of the above. It may be operated only by the piston cylinder unit.

However, an important aspect of the invention is the advantage that a slipless clutch operation can be realized by providing two piston-cylinder-units.

This advantage is achieved by the compression force acting on the disc set appearing as a result of adding up the compression force of the first piston-cylinder-unit and the compression force of the second piston-cylinder-unit in consideration of the relevant aspects.

The pressing force of the two piston-cylinder-units is added by the present invention.

Thus, the power acting on the disc set appears additionally from the sum of the two individual powers formed from the individual piston-cylinder-units, taking into account the geometric situation.

However, when the installation sizes of the clutches are the same, the torque that can be transmitted also increases correspondingly.

The compressive force of the disc set, which can be achieved entirely from the available pressure levels, is correspondingly enlarged and described above in particular with respect to the relatively smaller piston face of the second piston-cylinder-unit, to use the clutch in the marine sector. For use purposes it can be better set even when the first piston-cylinder unit is not operated.

Therefore, it is important in the present invention that two piston-cylinder-units are arranged so as to be in communication with one pressure source, respectively, each piston-cylinder-unit acting on the disc set in the insertion direction.

Pressure is provided to the two piston-cylinder-units from only one pressure source or pressure is provided to the two piston-cylinder-units from each unique pressure source.

In this way, the pressing force of the two piston-cylinder-units acting on the disc set additionally overlaps, without the need to increase the overall size of the clutch as described above.

The power density of the clutch is a characteristic value in the form of a quote, which increases in proportion to the total volume from the deliverable power.

It should be noted that for the sake of completeness, the additional arrangement of two or more piston-cylinder-units may also be included in the present invention.

In this case, the above-described embodiments apply correspondingly.

In this case the two piston-cylinder-units can use separate pressure sources.

However, two piston-cylinder-units can also be connected to the same pressure source.

Furthermore, in the case where it is desired to use a wear-free clutch, especially for trolling operations in the maritime sector, a solution is proposed to allow the disk set to pass through an oil bath.

In the present invention, an improvement suited specifically to the field of shipping is addressed, in which the clutch disposed between the drive motor and the output shaft is intentionally moved to the grinding mode in order to reach the ship propeller speed less than the engine minimum speed. do.

In this case, the speed of the ship propeller required for the standstill in the flow is set through the pressing force of the disc set using only one piston-cylinder-unit of the two piston-cylinder-units. This is achieved because of the better regulating properties of the relatively smaller piston-cylinder-unit.

If the pistons of the two piston-cylinder-units are mutually coupled, and at the time of displacement only one piston of each of the pistons of the other piston-cylinder-unit is displaced together in a forcedly coupled state, the two pressure chambers are simultaneously filled The additional compressive force derived from the two piston-cylinder-units is immediately applied to the disc set without time delay, while only the filling operation of the relatively smaller piston-cylinder-unit can improve the grinding mode.

Such a combination also allows the two pistons to be displaced essentially simultaneously and in the same direction in the extraction direction as well.

As in the insertion direction, the two pistons must be firmly engaged with each other in the withdrawal direction.

Such a coupling can be realized through a simple axial screw coupling in an embodiment.

The invention also found that two piston-cylinder-units can be arranged in the same clutch housing.

As such, the overall size of such a clutch does not exceed the overall size of the clutch with only one unique piston-cylinder-unit.

In other words, in the case of an improvement of the invention as described above, the installation space available at any time in the clutch housing is provided by mounting a second piston-cylinder-unit, and in some cases an additional piston-cylinder-unit, and in this manner. It is better used for the purpose of increasing the compressive force applied to the disk set.

Basically, the present invention deals with the parallel connection of two piston-cylinder-units, and the intention of such parallel connection is to supplement the second piston-cylinder-type while additionally supplementing the piston face provided with pressurized oil to form a pressing force. To operate the relatively smaller piston face of the unit by itself.

Another proposed solution to reduce the overall size is to arrange two piston-cylinder-units in an axial direction, ie two piston-cylinder-units can be arranged on the same side of the disc set, It is applied to the compression ring jointly by using the compression ring, the pressing force is provided to the disk set.

In this case the two piston-cylinder-units can be provided with pressurized oil jointly through a pressurized oil channel provided typically in the hollow shaft.

For this purpose, two piston-cylinder-units are provided with radial channels in communication with the compression chamber, respectively, which may in some cases be supplied with compressed oil by the same pressurized oil source.

Such an improvement of the present invention requires a minimum configuration cost, since only the elements necessary for the present invention need to be complemented.

In this case, like the first piston-cylinder-unit, the second piston-cylinder-unit with the piston face acting in the direction of insertion of the clutch may also have a total size which is relatively relatively smaller in size.

In that case the piston face of the piston of the second piston-cylinder-unit may lie in the piston face set by the piston of the first piston-cylinder-unit to keep the housing diameter of the clutch small.

As such, by simply displacing the two piston faces in the axial direction, two piston-cylinder units can be provided in the same clutch housing without any problem.

Further preferred structural features are provided for each of the two piston-cylinder-units, one support flange fixed firmly on the inner actuator, in which each cylinder is tightly coupled axially with the clutch shaft.

Also, for structural reasons, the support flange of the second piston-cylinder-unit between the first piston-cylinder-unit and the second piston-cylinder-unit can also be used as a support surface for the power generator responsible for the pull-out operation of the clutch. Can be.

Embodiments for such operations are presented.

The invention is described in detail below with reference to embodiments.

1 is a cross-sectional view of a clutch according to the present invention cut along an axis;

2 is a detailed view of two piston-cylinder-units;

3 is a detailed view illustrating the manner in which lubricating oil is provided to the disk set.

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

The figures show the clutch 1.

The clutch 1 has an input side connection for the drive motor and an output side connection for the output shaft.

In this case, there is no difference between the input side connection and the output side connection.

Typically one of the two connections is connected to the clutch housing 3 and the other is connected to the internal actuator 2.

In this case individual discs of the disc set 4 are arranged between the clutch housing 3 and the inner actuator 2, of which the outer tooth wheel of every second disc has a corresponding inner tooth of the clutch housing 3. The inner toothed wheels of the different disks are arranged on the outer toothed wheels of the inner actuator 2.

The pressure is applied to the disk set 4 in the insertion direction (Einruckrichtung) 5, whereby a frictional force acting in the circumferential direction is generated between each of the neighboring disks of the disk set, and the magnitude of the frictional force is equal to the neighboring disk. Depending on the individual friction value of the disks, the friction force is an axial force acting in the insertion direction 5.

In the drawing direction (Ausruckrichtung) 6 a power generator 12 acting separately to open the disc set was provided.

In the insertion direction there is one piston-cylinder-unit 7 which can be supplied with pressurized fluid through the channel system.

In this case the channel system consists of, for example, an axial channel 17 installed in the inner actuator 2 and a radial channel 18 which leads out of the axial channel, which radial channel is the piston-cylinder unit. In communication with the interior of the pressure chamber 9 of (7), the piston-cylinder-unit is also designated as a "first" piston-cylinder-unit.

Thus, the radial channel 18 is in communication with the interior of the first pressure chamber 9 and actuates the piston face 10 of the piston 8 of the piston-cylinder-unit 7 in the insertion direction 5.

Thereby, the piston 8 of the piston-cylinder-unit 7 has an outer surface with the impingement surface 25 of the piston 8 facing towards the disk set 4 facing the disk set 4. Displaced in the direction of the disk set 4 until it hits.

The additional pressure then builds up the disk set more and more, creating a friction force necessary to transfer torque between the input side and the output side of the clutch 1.

It is important at this time that a separate second piston-cylinder-unit 13 is provided in addition to the first piston-cylinder-unit 7.

The further piston-cylinder-unit 13 likewise has a piston 14, but the piston closes the second pressure chamber 15 and, if filled with a suitable pressurized fluid, likewise displaces the piston 14. It can be displaced in the direction of the set 4.

For this purpose, the second pressure chamber 15 is likewise in communication with the pressure source via the channel system.

In a first embodiment of the invention the channel system consists of an axial channel 17 inserted into the hollow shaft 2, from which the radial channel 18a is led and the radial channel is finally In communication with the second pressure chamber 15.

This embodiment means that the radial outer end of the radial channel 18a is coupled directly with the second pressure chamber 15 through a suitable channel system.

Alternatively, the radial channel 18a used to fill the second piston-cylinder-unit 13 may be in communication with the pressure sources 11, 11a through the inherent axial channel 17a. In this case, a unique pressure source 11a can be used which preferably has a higher pressure level than the pressure source 11 of the first piston-cylinder-unit 7.

When filling the first piston-cylinder-unit 7 it can be realized that the piston 8 is displaced in the direction of the disc set 4. However, the same applies to the case where the piston face 16 of the piston 14 of the second piston-cylinder-unit 13 is operated, so that the front face 25 is left of the disk set 4 to the left. If it is sufficiently displaced in the direction, it will collide in front of the corresponding mating surface of the outermost disk, and the pressure additionally created in this way compresses the entire set of disks correspondingly.

Since the clutch 1 according to the invention is particularly suitable for operation in the grinding state, the disk set 4 additionally passes through an oil bath.

For this purpose a small number of additional radial channels 26a-g are provided in the axial longitudinal region of the disc set 4, which likewise carries an axial channel 17 installed in the rotary actuator 2. Lubrication is supplied through.

In this way the lubricating oil is reached via the radial channels 26a-g to the very region of the clutch 1 where the individual discs to be lubricated of the disc set 4 are present.

As can be seen further in FIG. 1, the pistons 8 and 14 of the two piston-cylinder-units 7 and 13 are mutually coupled so that only one piston 8 or 14 is the only one of the two pistons. In case of displacement, the different pistons 14 or 8 are displaced together in the insertion direction 5, respectively.

In this case the two pistons 8 and 14 are fixed to each other via the coupling screw 27, so that the two pistons 8 and 14 can move simultaneously as a unit.

As a result, the operation of the two pistons 8 and 14 is always performed in the same direction at the same time, so that the entire unit of the two piston-cylinder-units, even if only a small amount of pressurized fluid is introduced into the one or two pressure chambers Is displaced in the direction of the disc set 4.

Furthermore, the coupling screw 27 allows two pistons 8 and 14 to move simultaneously and in the same direction in the extraction direction 6 as well.

However, the embodiment shown so that two piston-cylinder-units 7 and 13 are arranged in the same clutch housing 3 also offers particular advantages.

In other words, in such a manner, the available installation space of the clutch housing is best utilized, and the output density of the clutch increases in accordance with the intention of the present invention without changing the external dimensions.

By arranging two piston-cylinder-units 7 and 13 continuously in the axial direction, the outer diameter of the conventional clutch housing 3 can also be simply dedicated.

In that case the piston-cylinder-units may be formed in an annular shape, but such a shape is a completely corresponding shape in the prior art, in which case a relatively low pressure level may be mentioned as a complementary advantage, but such a relative Lower pressures will result in correspondingly higher pressing forces due to the pressure side of the pistons 8 and 14 to be supplemented further.

Nevertheless, the adjustment characteristics in the grinding mode are improved because of the relatively smaller side of the second piston-cylinder-unit.

The two piston-cylinder-units can be combined with one pressure source or with each separate pressure source, corresponding to FIG. 1.

It is further revealed that the two piston faces of the first piston-cylinder-unit and the second piston-cylinder-unit can actually have the same size, so that each of the two piston-cylinder-units is connected to one unique pressure source. A connection scheme is proposed.

Each piston-cylinder-unit consists of a component part that is tightly coupled with the inner actuator 2, for example by means of suitable screwing, and a component part which is guided axially movable on the component part.

In order to support the piston-cylinder-units 7 and 13 to the inner actuator 2, support flanges 19 and 22 are used in the present invention, which support shafts have two axes so as not to be pushed on the inner actuator 2. Are arranged in the direction.

In particular, the support flange 19 can be firmly engaged with the internal actuator 2 via a screw connection.

The embodiment shown in the figures differs from the above variant solution.

In the case of the right support flange 19 a snap ring 20 is inserted into the corresponding circumferential groove of the inner actuator 2 for this purpose.

Thereby, the support flange 19 can be safely protected against the situation of slipping out in the direction away from the disk set 4.

A tension ring 21 is provided to fix the support flange 19 in the opposite direction, which is engaged with the other side of the snap ring 20 and is screwed against the support flange 19.

The second support flange 22 is supported against a diameter step in the inner actuator 2 in the direction of the disc set 4, in particular a screw against the inner actuator 2 as shown in FIG. 3. Combined.

In this case the second support flange forms an extension which extends in the direction of the disc set 4, the outer circumference of the extension running in a sealing manner in the front region.

In the present invention, the sealing zone is formed by the inner circumference of the ring tightly coupled with the second piston 14 and extending in a direction away from the disk set 4, thereby providing a piston () of the second piston-cylinder-unit 13. 14 actually proceeds in a sealed manner on the outer diameter of the support flange 22, in which case the tensioning screw 23, preferably dispensing around the support flange 22, is fixed in relation to the so-called inner actuator 2. The component parts of the second piston-cylinder-unit (13).

In the support flange 22 of the second piston-cylinder-unit 13, a guide bore 24 disposed circumferentially is formed in the axial direction, whereby in the axial direction of the second piston-cylinder-unit 13 It can be further confirmed that the power generator 12 may be installed in the non-movable component, the piston 8 of the first piston-cylinder-unit 7 as soon as the pressure supply is interrupted by the power generator. The drawing direction 6 is moved.

In this manner, the two pistons 8 and 14 are axially coupled by the coupling screw 27, whereby the piston 14 of the second piston-cylinder-unit 13 is also the first piston-cylinder- It is displaced in the same direction as the piston 8 of the unit 7 and simultaneously in the withdrawal direction 6.

Explanation of symbols on the main parts of the drawings

1: clutch 2: internal actuator

3: clutch housing 4: disc set

5: insertion direction 6: drawing direction

7: piston of first piston-cylinder-unit 8: 7

9: first pressure chamber 10: piston face in insertion direction 5

11, 11a: pressure source 12: power generator

13: piston of the second piston-cylinder unit 14: 13

15: second pressure chamber 16: piston face in the insertion direction (5)

17, 17a: axial channel 18, 18a: radial channel

19: first support flange 20: snap ring

21: tension ring 22: second support flange

23: tension screw 24: guide bore

25: front side 26a-g: radial channel

27: coupling screw

M: adjustment member GPS: global positioning system

Claims (18)

As the clutch 1, An input side connection (2; 3) for the drive motor and an output side connection (3; 2) for the output shaft and a set of disks (4) disposed therebetween, The disc set can be operated in the insertion direction 5 via the channel system 17, 18 using pressurized fluid by the piston 8 of the piston-cylinder-unit 7, and the piston-cylinder-unit ( With a clutch having a power generator 12 acting in the drawing direction 6 on the piston 8 of 7): A second piston-cylinder-unit 13 is provided, The piston 14 of the second piston-cylinder-unit has an additional second piston face 16 which can be actuated in the direction of insertion of the clutch 1 by pressurized fluid, The second piston face 16 closes the further second pressure chamber 15, The second pressure chamber (15) is characterized in that it is in communication with the pressure source (11; 11a) via a second channel system (17, 18; 17a, 18a). The method of claim 1, The disk set (4) is characterized in that it passes through an oil bath. The method according to claim 1 or 2, By the pistons 8, 14 of the two piston-cylinder-units 7, 13 being mutually engaged 27, the piston 14 of the second piston-cylinder-unit 13 is connected to the first piston-cylinder-unit A clutch, characterized in that it is displaced together at least in the insertion direction (5) by the piston (8). The method of claim 3, wherein By the pistons 8, 14 of the two piston-cylinder-units 7, 13 being mutually engaged 27, the piston 14 of the second piston-cylinder-unit 13 is connected to the first piston-cylinder-unit A clutch, characterized in that it is also displaced together in the drawing direction (6) by the piston (8). The method according to any one of claims 1 to 4, Clutch, characterized in that two piston-cylinder-units (7, 13) are arranged in the same clutch housing (3). The method of claim 5, wherein Clutch, characterized in that two piston-cylinder-units (7, 13) are arranged continuously in the axial direction. The method according to claim 5 or 6, The two piston-cylinder-units 7, 13 are arranged annularly on the inner actuator 2, The inner actuator 2 has a pressurized oil channel 17, through which the two piston-cylinder-units 7, 13 supply pressurized oil through separate radial channels 18, 18a. Clutch characterized in that. The method according to claim 5 or 6, The internal actuator 2 for each piston-cylinder-unit 7, 13 has a separate pressurized oil channel 17, 17a, respectively, and two piston-cylinder-units by means of said separate pressurized oil channel. A clutch, characterized in that one piston-cylinder-unit of each of (7, 13) is supplied with pressurized oil through separate radial channels (18, 18a). The method according to claim 7 or 8, Clutch, characterized in that two piston-cylinder-units (7, 13) are in communication with the same pressure source (11). The method of claim 8, Clutch, characterized in that a different pressure source (11, 11a) is provided for each piston-cylinder-unit (7, 13). The method of claim 10, Clutch, characterized in that the pressure source (11a) of the second piston-cylinder-unit (13) has a higher pressure level than the pressure source (11) of the first piston-cylinder-unit (7). The method according to any one of claims 5 to 11, The piston face 16 of the piston 14 of the second piston-cylinder-unit 13 is larger than the piston face 10 set by the piston 8 of the first piston-cylinder-unit 7. Clutch, characterized in that smaller. The method of claim 12, The two piston-cylinder-units 7, 13 are characterized in that they are closed by one support flange 19, 22 which is firmly fixed in two axial directions 5, 6 on the inner actuator 2. Clutch. The method of claim 13, The support flange 22 of the second piston-cylinder-unit 13 comprises the piston 8 of the first piston-cylinder-unit 7 and the piston 14 of the second piston-cylinder-unit 13. ) In between Withdrawal direction 6 of clutch 1 between side of said support flange 22 facing away from disk set 4 and side of said first piston-cylinder-unit 7 facing towards disk set 4. Clutch characterized in that the power generator 12 acting as a support. The method of claim 14, The power generator (12) is characterized in that it is formed by a compression spring distributed over the circumference of the support flange (22) of the second piston-cylinder-unit (13). The method of claim 15, The compression spring is arranged in the guide bore 24 of the support flange 22 of the second piston-cylinder-unit 13 or towards the first set of piston-cylinder-unit 7. Clutch, characterized in that disposed on the side of the piston (8). The method according to any one of claims 1 to 16, The second piston-cylinder-unit 13 is provided in an adjustment circuit, in the case of the adjustment circuit, the pressure provided serves as the adjustment member M, and the setting position of the adjustment member is a predetermined global globe. Clutch which can be changed according to the deviation of the vehicle setting position. The method according to any one of claims 1 to 17, Clutch, characterized in that the second piston face (16) of the second piston-cylinder-unit (13) is in the piston face (10) of the first piston-cylinder-unit (7).

Images