CN205154962U

CN205154962U - Hydrodynamic clutch

Info

Publication number: CN205154962U
Application number: CN201520629675.2U
Authority: CN
Inventors: 海莫·布雷格勒; 赫尔穆特·弗勒绍斯; 奥利弗·瑙恩多夫; 哈拉尔德·霍费尔德
Original assignee: Voith Patent GmbH
Current assignee: Voith Patent GmbH
Priority date: 2014-08-19
Filing date: 2015-08-19
Publication date: 2016-04-13
Anticipated expiration: 2025-08-19
Also published as: DE202014006626U1; CN105370755A; CN105370755B

Abstract

The utility model relates to a hydrodynamic clutch, its turbine (2) that have pump impeller (1) of taking the blade and take the blade, they construct toroidal working chamber (3) together, this working chamber fills and maybe can fill with working medium, so that constitute hydrodynamic circuit stream, wherein, bear by revoluting moving axis line pivoted drive shaft (6) pump impeller (1), and bear by revoluting moving axis line pivoted output shaft (5) turbine (2), and hydrodynamic clutch has casing (7) of transfixion, this casing surrounds pump impeller (1) and turbine (2), its characterized in that, support with the help of the bearing with grease lubrication (13, 14, 15, 16) that at least one has lubricating arrangement (28) again respectively drive shaft (6) and/or output shaft (5).

Description

Fluid coupling

Technical Field

The utility model relates to a hydraulic coupling.

Background

Fluid couplings of this type have long been known. As can be realized with the fluid couplings according to the invention, they are used, for example, for heavy-duty machines such as crushers, chain conveyors, mills, belt conveyors, in particular in open-pit mining or underground mining, in order to start and operate the working machine without wear and with vibration damping. In combination with an electronic starting control, a starting time of up to several minutes can be achieved. In this case, the belt tension can be minimized when the belt conveyor is started.

In a conventional manner, such fluid couplings are usually designed as externally mounted (freedgenger) couplings, i.e. their drive shaft and output shaft are mounted on the connected machine, i.e. on the drive machine on the drive shaft side and the working machine on the output shaft side or on an intermediate transmission. In this way, although a low-cost and particularly compact construction of the fluid coupling is possible, the connected machines must be designed such that their bearing points can also absorb the operating forces acting on the drive shaft and output shaft of the fluid coupling.

SUMMERY OF THE UTILITY MODEL

The object of the invention is to provide a fluid coupling, in particular for the application areas mentioned at the outset, which avoids the disadvantages mentioned.

The object of the invention is achieved by a fluid coupling having a pump wheel with blades and a turbine wheel with blades, which together form an annular working chamber, which is filled or can be filled with a working medium in order to form a hydraulic circuit; wherein the pump impeller is carried by a drive shaft which rotates about an axis of rotation and the turbine wheel is carried by an output shaft which rotates about an axis of rotation, and the fluid coupling has a stationary housing which surrounds the pump impeller and the turbine wheel; characterized in that the drive shaft and/or the output shaft are each supported by means of at least one grease-lubricated bearing having a relubrication device.

The hydrodynamic clutch according to the invention has a bladed impeller and a bladed turbine, which together form an annular working chamber, which is filled or can be filled with a working medium in order to form a hydrodynamic circulation flow. The hydraulic coupling is in particular designed as a controlled-fill coupling, i.e. a fill control device is provided, by means of which the amount of working medium in the working chamber can be varied in a targeted manner between a minimum fill level and a maximum fill level of the working chamber, advantageously steplessly.

The fluid coupling has a pump impeller carried by a drive shaft that rotates about an axis of rotation. Furthermore, the fluid coupling has a turbine wheel which is carried by an output shaft rotating about an axis of rotation. Typically, the axis of rotation of the drive shaft and the axis of rotation of the output shaft are aligned with one another.

Furthermore, it is also possible for the hydrodynamic coupling to have more than one impeller and/or more than one turbine, for example two impellers, which enclose the two turbines between them in the axial direction, or two turbines, which enclose the two impellers between them in the axial direction. It is then advantageous to position the wheels enclosed in the axial direction on a common shaft in a back-to-back arrangement.

According to the invention, the drive shaft and/or the output shaft are each supported by means of at least one grease-lubricated bearing having a relubrication device. The respective bearing is embodied, for example, as a rolling bearing, for example, a deep groove ball bearing, a cylindrical roller bearing or a tapered roller bearing.

According to the fluid coupling of the invention, the drive shaft and/or the output shaft are supported in the housing by means of a first rolling bearing in the form of a fixed bearing and a second rolling bearing in the form of a floating bearing, respectively. As is known to the person skilled in the art, the fixed bearing here means that it can absorb both radial and axial forces, whereas the floating bearing cannot absorb axial forces but only radial forces.

According to one embodiment of the invention, the one or more first rolling bearings and/or the one or more second rolling bearings are embodied as deep groove ball bearings, cylindrical roller bearings or tapered roller bearings.

Preferably, the relubrication device has at least one grease feed and at least one grease discharge, which open in each case at the bearing-side end in at least one bearing and at the opposite end on the housing exterior.

Advantageously, the relubrication device has, for each bearing, in each case at least one grease feed or a plurality of grease feeds which, in particular, each open with a respective opening in the bearing and on the outside of the housing.

Preferably, the relubrication device has at least one common grease outlet for each of the plurality of bearings, in particular for each of the two bearings, which has at least one opening in the bearing on the bearing-side end and a common opening on the housing exterior on the opposite end.

It is particularly advantageous if the relubrication device has a plurality of grease inlets for each bearing, which have a plurality of openings, in particular two openings, wherein the openings for each bearing are arranged offset from one another, in particular 180 ° from one another, over the circumference of the bearing.

According to the utility model discloses an embodiment is directed against every bearing. The relubrication device has a plurality of grease inlets with a plurality of openings, in particular two openings, which open on the housing exterior, in particular on opposite housing sides. For example, one of the two openings, viewed in the direction of the end face of the housing or in the direction of the rotational axis of the fluid coupling, is positioned to the left of a plane which runs perpendicular to and along the rotational axis, and the other of the two openings is positioned to the right of this plane, it being advantageous if the two openings each have a distance to the mentioned plane, for example approximately the maximum lateral extent of the housing. In addition or alternatively, corresponding openings can also be provided on the housing on both end sides.

In one embodiment, it is provided that the at least one grease inlet and/or grease outlet comprises a hose, in particular a hose which bridges an interior space in the housing. The at least one hose or the plurality of hoses can thus be mounted, for example, with one end on a flange of the housing, which surrounds the drive shaft or the output shaft with one or more associated bearings, and with its other end radially outside the flange on an outer carrier or a housing of the housing, so that the at least one grease inlet and the at least one grease outlet are accessible from the outside.

In the region of the external connection of the at least one hose or, in general, in the region of the opening of the grease inlet and/or the grease outlet outside the housing, a valve and/or a lubricant nipple can be provided, through which grease can be introduced into the grease inlet or grease can be discharged from the grease outlet.

In the case of an advantageous supply and discharge of grease, it is preferred if the opening of the grease inlet on the housing and/or the opening of the grease outlet on the housing are positioned above the respective other opening in the bearing and/or if the grease inlet and/or the grease outlet extend at least partially above the respective opening in the bearing. For this purpose, geodetic height differences can be used to facilitate the pressing of the grease into the bearing or to prevent an undesired outflow of grease.

A check valve may be provided in the grease inlet and/or the grease outlet, which check valve is acted upon in the closing direction by a spring force against which the grease counteracts when flowing through the grease inlet or through the grease outlet. This may also help to avoid undesirable flow of grease. Furthermore, a pressure can be built up in the grease by the non-return valve, which pressure facilitates the distribution of the grease.

The grease inlets and grease outlets can be connected to the respective bearings, in particular rolling bearings, in such a way that grease is introduced into the grease inlets, so that it pushes out the grease located in the bearings into the grease outlets, so that the used grease is pushed out of the bearings and replaced by grease. This can be achieved particularly advantageously by the flow restriction of the grease, for example by a flow restriction in the grease inlet and/or the grease outlet, and/or by a check valve in the grease inlet and/or the grease outlet.

Drawings

The invention shall be elucidated below by way of example with reference to the embodiments and the accompanying drawings. Wherein:

fig. 1 shows an exemplary embodiment of a fluid coupling in which the present invention can be applied;

FIG. 2 shows an end side view, partially broken away, of the end side of the coupling of FIG. 1;

fig. 3 shows a possible connection of the external openings of the grease inlet and grease outlet to the housing;

fig. 4 shows a schematic cross-sectional view of the passage of the grease inlet inside the housing;

fig. 5 shows a schematic cross-sectional view of the channels for the grease outlet of the two bearings of the impeller.

Detailed Description

Fig. 1 shows a fluid coupling which is designed as a double coupling with two working chambers 3. Each working chamber 3 is formed by a pump wheel 1 and a turbine wheel 2, respectively, wherein, in the embodiment shown, the fluid coupling is provided with a so-called outer wheel drive, i.e. the two pump wheels 1 are connected to each other via a pump wheel housing 4 and enclose between them two turbine wheels 2 positioned in a back-to-back arrangement on an output shaft 5. The pump wheel housing 4 surrounds the two turbines 2 in the circumferential direction.

The two pump wheels 1 are driven via a drive shaft 6 which carries the two pump wheels 1 in each case, wherein a counter-bearing of the pump wheels 1 facing the output shaft 5 can also be provided on the output shaft 5 or on the turbine wheel 2.

The two pump wheels 1 and the turbine wheel 2 are surrounded by a stationary housing 7 together with the pump wheel housing 4. The housing 7 has a working medium inlet 8, via which a working medium is introduced into the hydrodynamic coupling from an external working medium circuit 9, in particular having a storage tank 10. In the exemplary embodiment shown, the working medium is conducted into the working chamber 3 after it has flowed through the rotary feedthrough 11 via nozzles 12 which extend in the radial direction or in the radial axial direction.

The drive shaft 6 is supported in the housing 7 via a first rolling bearing 13 and a second rolling bearing 14. As shown, the first rolling bearing 13 can be dimensioned considerably larger than the second rolling bearing, for example, that is to say it has relatively large rolling bodies and a larger-diameter bearing outer ring. The first rolling bearing 13 is designed as a fixed bearing, i.e. it absorbs both radial and axial forces and, as a result, the drive shaft 6 is held in the desired position inside the housing 7. The second rolling bearing 14 is designed as a floating bearing, i.e. it cannot absorb axial forces.

The output shaft 5 is positioned in the housing 7 by means of a first rolling bearing 15 and a second rolling bearing 16. The same applies to the two rolling bearings 15, 16 described for the two rolling bearings 13, 14 of the drive shaft 6.

Each rolling bearing 13, 14, 15, 16 has a bearing inner ring 17 and a bearing outer ring 18. The bearing inner race 17 is positioned on the drive shaft 6 or the output shaft 5, while the bearing outer race 18 is positioned in the housing 7. The bearing cones 17 for supporting the drive shaft 6 are braced against one another via an intermediate sleeve 19 on the drive shaft 6 and are therefore held in their axial position relative to one another. The bearing cones 17 for supporting the output shaft 5 are braced against one another on the output shaft 5 by means of sleeves 19 and are therefore held in their axial position on the output shaft 5. In addition, an inner sleeve 20 is provided on the side of the respective second rolling bearing 14, 16 facing away from the respective first rolling bearing 13, 15, and the respective inner bearing ring 17 is tensioned relative to this inner sleeve 20.

The inner sleeve 20 simultaneously forms part of a shaft seal 21, by means of which the interior of the hydrodynamic coupling, or the drive shaft 6 and the output shaft 5, are sealed off from the housing 7. In the embodiment shown, the inner sleeve forms the active surface for the sealing ring 22 of the shaft seal 21.

For both shaft seals 21, so-called relief sections are provided, to which a ventilation line 23 is connected, via which the working medium reaching the interior of the shaft seal 21 is discharged from the hydrodynamic coupling in a targeted manner. A vent line 23 extends inside the housing 7. Corresponding to these ventilation lines 23, ventilation lines 25 are provided for shaft seals 24, by means of which shaft seals 24 the drive shaft 6 or the output shaft 5 is sealed off from the housing outside the first rolling bearings 13 and 15.

The bearing outer rings 18 of the second rolling bearings 14 and 16 are each prestressed against the housing 7 via one or more spring elements 26. Accordingly, an annular recess or axial bore is provided in the housing 7. On the side facing away from the spring element 26, the bearing outer ring 18 can be held by an outer ring 27 of the respective shaft seal 21. The outer ring 27 can in particular be screwed onto the housing 7.

Now, with reference to the illustration of the bearing in fig. 1, fig. 2 shows by way of example how the first rolling bearings 13, 15 and the second rolling bearings 14, 16 are maintained by means of the relubrication device 28, in that: the grease located in the bearings 13 to 16 is replaced at advantageously regular intervals. For this purpose, in the region of each axial end of the hydrodynamic coupling, a grease feed 29 is provided for the first rolling bearing 13, 15, respectively, and a grease feed 30 is provided for the second rolling bearing 14, 16, respectively. Furthermore, a common grease outlet 31 is provided for each of the first rolling bearing 13, 15 and the second rolling bearing 14, 16, i.e. in the region of each axial end of the hydrodynamic coupling, a grease outlet 31 is provided for each of the rolling bearings 13 and 14 or 15 and 16 respectively arranged there.

In the exemplary embodiment shown, each rolling bearing 13 to 16 is provided with two grease inlets 29.1 and 29.2 or 30.1 and 30.2, but this is not mandatory. This has the advantage, however, that two openings 32, which are positioned offset from one another along the circumference, can be provided for each grease inlet 29, 30, via which openings 32 the grease inlets 29, 30 open in the bearings 13 to 16. Thus, a better distribution of new grease over the circumference of the respective bearing 13 to 16 can advantageously be achieved. Furthermore, in the embodiment shown, for this purpose, see also fig. 3, all the rolling bearings 13 to 16 are lubricated with new grease from both sides of the hydrodynamic coupling separately, which is advantageous because access from both sides is not always ensured.

The openings of the grease inlets 29, 30 on the outside of the housing 7 are marked with 33, and the openings of the grease outlet 31 on the outside of the housing 7 are marked with 34. The opening of the grease outlet 31 in the bearing is marked 40.

At the openings 33 and 34 located on the housing 7, a hose 35 is connected to the grease inlet 29, the grease inlet 30 and the grease outlet 31, respectively, which hose bridges the free space between a flange 36 on the end side, which surrounds the respective bearing 13 to 16 (see also fig. 1 for this purpose), and the region outside the housing 7 having the openings 33 and 34. In the embodiment shown, the hoses 35 are connected to the housing 7 via valves for forming the openings 33 and 34, respectively.

Fig. 4 shows channels 37 inside the flange 36, which form the final sections of the grease inlets 29.1 and 29.2 to the first rolling bearing 15 and the final sections of the grease inlets 30.1 and 30.2 to the second rolling bearing 16. These channels 37 open in the respective rolling bearing 15, 16 and are connected on the other side to the hose 35 shown in fig. 2 and 3. In the embodiment shown, the channel 37 is introduced through a hole in the flange 36 of the housing 7 and sealed on the outer end with a closing bolt or other closure. The connection for the hose 35 forms the only free entry opening.

Fig. 5 shows a corresponding channel 38 for the common grease outlet 31, which extends within the flange 36. In addition, the vent line 23 is again seen.

In the hose connection for the channel 38, a check valve 39 can be provided, for example, to avoid an undesired overflow of grease. In addition or alternatively, such a non-return valve can also be provided in the region of the external opening of the grease outlet 31 or the grease inlets 29, 30 on the housing 7. For this purpose, reference is again made to fig. 3, where there is the outer end of the hose 35.

Claims

1. A kind of fluid coupling is disclosed, which comprises a fluid coupling,

1.1 the hydrodynamic coupling has a bladed impeller (1) and a bladed turbine (2) which together form an annular working chamber (3) which is filled or can be filled with a working medium in order to form a hydrodynamic circulation flow; wherein,

1.2 the pump impeller (1) is carried by a drive shaft (6) rotating about an axis of rotation, and the turbine impeller (2) is carried by an output shaft (5) rotating about an axis of rotation, and

1.3 said fluid coupling has a stationary housing (7) which encloses said pump wheel (1) and said turbine wheel (2);

it is characterized in that the preparation method is characterized in that,

1.4 the drive shaft (6) and/or the output shaft (5) are each supported by means of at least one grease-lubricated bearing (13, 14, 15, 16) having a relubrication device (28).

2. Fluid coupling according to claim 1, characterised in that the relubrication means (28) has at least one grease inlet (29, 30) and at least one grease outlet (31) which open in at least one bearing (13, 14, 15, 16) and on the outside of the housing (7), respectively.

3. Fluid coupling according to claim 2, characterised in that the relubrication means (28) have, for each bearing (13, 14, 15, 16), respectively, at least one grease inlet (29, 30) which opens in the bearing (13, 14, 15, 16) and on the outside of the housing (7), respectively.

4. A fluid coupling according to claim 3, characterised in that the at least one grease inlet (29, 30) is open with a respective opening (32, 33) in the bearing (13, 14, 15, 16) and on the outside of the housing (7), respectively.

5. Fluid coupling according to claim 2, characterised in that the relubrication means (28) has at least one common grease outlet (31) for a plurality of bearings (13, 14, 15, 16) respectively, which grease outlet opens with at least one opening (40) in the bearings (13, 14, 15, 16) respectively and with a common opening (34) on the outside of the housing (7).

6. Fluid coupling according to claim 2, characterised in that the relubrication means (28) has at least one common grease outlet (31) for both bearings (13, 14, 15, 16), respectively, which grease outlet opens with at least one opening (40) in the bearing (13, 14, 15, 16), respectively, and with a common opening (34) on the outside of the housing (7).

7. A fluid coupling according to claim 3, characterised in that the relubrication means (28) has, for each bearing (13, 14, 15, 16), a plurality of grease inlets (29, 30) with a plurality of openings (32), wherein, for each bearing (13, 14, 15, 16), the openings (32) are arranged offset from each other on the circumference of the bearing (13, 14, 15, 16).

8. A fluid coupling according to claim 7, characterised in that the grease inlet (29, 30) has two openings (32) for each bearing (13, 14, 15, 16).

9. Fluid coupling according to claim 7, characterised in that for each bearing (13, 14, 15, 16) the openings (32) are arranged 180 ° offset from each other on the circumference of the bearing (13, 14, 15, 16).

10. A fluid coupling according to claim 3, characterised in that the relubrication means (28) has, for each bearing (13, 14, 15, 16), a plurality of grease inputs (29, 30) with a plurality of openings (33), which openings (33) open on the outside of the housing (7).

11. A fluid coupling according to claim 10, characterised in that the grease inlet (29, 30) has two openings (33) for each bearing (13, 14, 15, 16).

12. A fluid coupling according to claim 10, characterised in that the opening (33) is open on the opposite side on the outside of the housing (7).

13. The fluid coupling according to any one of claims 2 to 12, characterised in that the at least one grease inlet (29, 30) and/or grease outlet (31) comprises a hose (35) which bridges an inner space in the housing (7).

14. Fluid coupling according to any one of claims 2-12, characterised in that the opening (34) of the grease inlet (29, 30) and/or grease outlet (31) on the housing (7) is positioned above the opening (32, 40) in the bearing (13, 14, 15, 16) and/or that the grease inlet (29) and/or grease outlet (30) extends at least partially above the respective opening (32, 40) in the respective bearing (13, 14, 15, 16).

15. Fluid coupling according to any one of claims 2-12, characterised in that a non-return valve (39) is arranged in the grease inlet (29, 30) and/or the grease outlet (31), which non-return valve is loaded in the closing direction with a spring force against which the grease counteracts when flowing through the grease inlet (29, 30) or the grease outlet (31).