DE102017106942A1 - Hydrodynamic coupling - Google Patents

Abstract

The invention relates to a hydrodynamic coupling having at least one bladed impeller and at least one bladed turbine wheel, which together form at least one working space filled or fillable with a working medium in which a hydrodynamic circulation flow for driving the turbine wheel can be formed by driving the impeller; which carries the impeller at least indirectly, integrally or as a separate component, with an output shaft which carries the turbine wheel integrally or at least indirectly as a separate component, with a housing which encloses the impeller and the turbine wheel; wherein the drive shaft and the output shaft are each supported by at least one bearing in the housing. The hydrodynamic coupling according to the invention is characterized in that the drive shaft and / or the output shaft are additionally supported by at least one relative bearing against the respective other shaft.

Description

The present invention relates to a hydrodynamic coupling according to the preamble of claim 1.

A generic hydrodynamic coupling is in DE 20 2014 006 629 U1 disclosed. The hydrodynamic coupling has at least one bladed impeller and at least one bladed turbine wheel, which together form at least one working space that can be filled with a working medium. The impeller is supported by a drive shaft rotating about an axis of rotation and the turbine wheel is supported by a revolving over an axis of rotation output shaft. Impeller and turbine wheel are enclosed by a stationary housing of the hydrodynamic coupling.

Such a coupling may be designed as a monocoupling with a single working space or as a double clutch, in which two working spaces are provided side by side. The one or more work spaces are filled with the working fluid to form a hydrodynamic circulation flow therein and so to transmit torque or drive power from the impeller to the turbine wheel or from the pump wheels to the turbine wheels and thereby drive the output shaft hydrodynamically by means of the drive shaft.

The drive shaft and the output shaft were initially stored externally, as in the DE 20 2014 006 629 U1 is pictured. The beats, however DE 20 2014 006 629 U1 Now, to store both the drive shaft and the output shaft by own rolling bearings in the housing.

DE 20 2014 006 625 U1 proposes a hydrodynamic coupling in which the drive shaft indirectly carries the impeller as a separate component and the output shaft indirectly carries the turbine wheel as a separate component, wherein the drive shaft and / or the output shaft is / are formed by a connection shaft extending up to the housing out or accessible from outside the housing for a non-rotatable connection of a drive train. At least one connecting shaft has a bearing in the housing, the other may be externally mounted.

Although various bearings for hydrodynamic clutches, which are designed as a mono- or double clutch, have been proposed, there is a need to improve the storage of such a hydrodynamic coupling in that on the one hand a compact design is achieved and on the other hand, the life of the bearings and thus the hydrodynamic coupling is lengthened by reducing the bearing load.

The present invention is therefore the object of developing a hydrodynamic coupling of the type described above such that in a compact design, the bearing load and concomitant wear are reduced, so that the life is extended. The hydrodynamic coupling should be characterized advantageously by low bearing forces and high smoothness.

The object of the invention is achieved by a hydrodynamic coupling with the features of claim 1. In the dependent claims advantageous and particularly expedient embodiments of the invention are given.

A hydrodynamic coupling according to the invention has at least one bladed pump wheel and at least one bladed turbine wheel, which together form at least one working space filled or fillable with a working medium in which a hydrodynamic circulation flow for driving the turbine wheel can be formed by driving the impeller. Further, a drive shaft is provided, which carries the impeller, at least indirectly, integrally or as a separate component, and an output shaft which carries the turbine wheel, at least indirectly, integrally or as a separate component.

It is a housing or stationary housing is provided, which encloses the impeller and the turbine wheel. If a plurality of pump wheels and turbine wheels are provided for forming a plurality of working spaces, in particular for forming two work spaces, then the housing encloses all pump wheels and turbine wheels. The work spaces are advantageously arranged side by side in the axial direction.

According to the invention, the drive shaft and the output shaft are mounted in the housing by means of at least one bearing. The bearing in the housing is referred to herein as a housing bearing. Furthermore, the drive shaft and / or the output shaft is / are additionally supported by means of at least one relative bearing against the respective other shaft. This means that according to one embodiment, the drive shaft is mounted with a relative bearing against the output shaft, whereas the output shaft is mounted exclusively in the housing. According to another embodiment, the drive shaft is mounted exclusively in the housing and the output shaft is mounted in addition to its storage in the housing in addition by means of at least one relative bearing against the drive shaft. According to another embodiment two relative bearings are provided, one to support the drive shaft against the output shaft and the other to support the output shaft against the drive shaft.

Both the bearings in the housing and the at least one relative bearing are advantageously designed as rolling bearings.

According to one embodiment of the invention, the drive shaft and the output shaft are each supported by a bearing in the region of one end face in the housing and in each case by means of a relative bearing against each other.

Preferably, a relative bearing is provided in the region of one end face of the housing, whereas the other relative bearing is positioned in the region of an axial center between the two end faces of the housing.

According to a particularly advantageous embodiment of the invention, the relative bearing in the region of the end face of the housing radially within the bearing in the housing, with which the corresponding shaft - drive shaft or output shaft - is stored, provided and is completely enclosed in particular by this bearing in the housing. For example, the drive-side relative bearing is located directly within the drive-side housing bearing. By such nesting of the bearings by positioning the axial bearing centers in a common radial plane or in the axial direction at least close to each other undesirable tilting moments can be avoided or reduced to the shaft.

By this special arrangement, no additional radial load, for example, from the radial force of the coupling connecting the two bearings, that is, the component to which the bearing inner ring of the housing bearing and the bearing outer ring of the relative bearing is connected. Such a radial load would result from a lever effect, which causes an axially offset, in particular drive-side bearing assembly.

Particularly preferred is a relative bearing, in particular the relative bearing in the region of the end face of the housing, designed as a movable bearing, whereas the other relative bearing, which is provided for example in the axial center between the two end sides of the housing, is designed as a fixed bearing.

A bearing in the housing, for example, as a floating bearing and a bearing in the housing can be performed for example as a fixed bearing.

According to one embodiment of the invention, the drive shaft or the output shaft is mounted with two axially spaced bearings in the housing, whereas the other shaft - output shaft or drive shaft - by means of a single bearing in the housing and one, in particular a single, relative bearing corresponding to the other shaft is stored. Preferably, the relative bearing is designed as a fixed bearing in this case.

It is favorable if the bearings in the housing and the at least one relative bearing or all relative bearings are lubricated with the working medium of the hydrodynamic coupling.

According to one embodiment of the invention, the hydrodynamic coupling is designed as a double clutch with two, in particular axially juxtaposed work spaces. Another embodiment provides that the hydrodynamic coupling has a single working space to form a so-called mono-coupling.

Preferably, the hydrodynamic coupling is designed as a filling-controlled clutch, with an external working medium circuit, which is connected via a working medium and a Arbeitsmediumabfuhr to the at least one working space, wherein in the external working medium circuit a working medium cooler is provided and the external working medium advantageously via a filling valve and an emptying valve a working medium supply for adjusting the located in the at least one working space working medium quantity is connected. The working medium supply can be provided, for example, within the housing, in particular of the stationary housing. However, according to an alternative embodiment, it is provided outside the housing of the hydrodynamic coupling.

Instead of the filling valve and / or the emptying valve and a dynamic pressure pump may be provided to vary by means of this located in the working space working fluid quantity. For example, both valves can be replaced by an increasing filling and emptying of the working space is made possible by reversing the direction of rotation of the dynamic pressure pump, depending on the load condition.

By changing the working medium filling in the working space, the torque transmission is advantageously infinitely adjusted. For example, pressure medium is transferred to a gutter via the working medium inlet and flows through centrifugal force, in particular via bores, into the working space. By filling wedges, the inflow into the working medium circuit can be favored in the working space, the filling wedges an injector effect exercise. Via nozzles, the working fluid according to an embodiment of the invention can flow into a circulating pumping channel, from where it is taken up by a dynamic pressure pump projecting counter to the direction of rotation and guided via the working fluid outlet into the external working medium circuit. There it can then be passed through the cooler, thereby being cooled, and reintroduced into the hydrodynamic coupling again via the inlet.

About valves, in particular solenoid valves, or via the dynamic pressure pump shown above, it can be determined how much working fluid from the external working fluid circuit flows into the working fluid reservoir and how much working fluid flows from the working fluid reservoir into the external working fluid circuit. This can be done with working fluid alone with these valves, the regulation of the degree of filling of the at least one working space.

The bearing lubrication with the working fluid, in particular oil being used as the working medium, can take place from a sump at the bottom of the housing of the hydrodynamic coupling and / or from the working medium circuit in the working space or a working medium flow to or from the working space.

According to one embodiment of the invention, at least the drive-side relative bearing, wherein the terms drive side and output side refer to the positions of the drive shaft and the output shaft - the drive shaft is the drive side and the output shaft is positioned on the output side, by means of oil pressure against the rotational pressure of the working medium flow in the working space works, lubricated. In order to obtain a sufficient pressure difference, preferably two gap seals between the housing and the drive shaft, provided on both sides of an oil supply hole to promote the oil to the relative bearing. The gap seals may for example comprise piston rings or be formed by them.

Preferably, on both axial sides of the relative bearing, at least on the side facing away from the oil supply bore in the housing of the relative bearing, a radially inwardly projecting projection, for example formed by a pressure ring for screwing the impeller, is provided which has a smaller inner diameter than the inner diameter of the outer ring of the Relativlagers has. By this measure, a permanent lubrication of the relative bearing is ensured, even if for a short time no oil is conveyed through the oil supply hole in the housing. About such a projection is advantageously carried out the ongoing oil drain, so that the warehouse is not flooded.

In particular, when the bearing is designed as a floating bearing, the bearing inner ring can abut against a collar of the output shaft. The bearing outer ring abuts in particular on a radially inwardly projecting collar of the at least in the region of the relative bearing designed as a hollow shaft drive shaft. This can be dispensed with a further assurance of the bearing inner ring and / or the bearing outer ring.

According to one embodiment of the invention, a retaining ring for the bearing outer ring of the relative bearing, in particular the output side relative bearing, is provided, which is screwed into the turbine wheel or generally a rotating with output speed component. The bearing retainer is made, for example, of a ferrous material, the component in which it is screwed, made of aluminum. In order for an undesirable change in position of the relative bearing is avoided by thermal expansion. The bearing retainer ring can be sealed against the component in which it is screwed.

The bearing retainer preferably has a collar whose inner diameter is smaller than the inner diameter of the outer ring of the relative bearing. By this measure a permanent lubrication of the bearing is ensured, even if for a short time no oil is conveyed. The ring can also be used for running oil drainage so that the bearing is not flooded.

Lubrication preferably takes place via an axial nozzle in the housing, which injects into the bearing close to the shaft. The bearing can be designed as a fixed bearing and in particular fix the turbine wheel axially on the output shaft.

The drive-side housing bearing is designed in particular as a floating bearing, the lubrication preferably takes place via an axial nozzle in the housing. The same oil passage provided for the lubrication of this bearing can also serve for the lubrication of the drive-side relative bearing. The required amounts of oil for the housing bearing and the relative bearing can be matched to each other by means of orifices and / or nozzles. The oil drain advantageously takes place via the housing bearing or the relative bearing into the housing in the direction of the turbine wheel.

The output-side housing mounting is preferably lubricated by at least one axial nozzle. Again, the same oil passage can be used for lubrication for the output side relative bearing and preferably the required quantities with orifices and / or nozzles are matched. According to one Embodiment, a lubrication ring is provided for the output side housing mounting.

The oil drainage preferably takes place through holes located further down, which prevent the bearing from being flooded. The holes are offset according to an embodiment of the invention at an angle to the radial plane, so that a small oil sump is present and the bearing does not remain without lubrication. The housing bearing may preferably be designed as a fixed bearing and fix the output shaft and thus the turbine wheel in the housing.

The invention will be described by way of example with reference to exemplary embodiments and the figures.

• 1 eine mögliche Füllungssteuerung für eine erfindungsgemäße hydrodynamische Kupplung;
• 2 eine erfindungsgemäß ausgeführte hydrodynamische Kupplung mit zwei Lagern im Gehäuse (Gehäuselagern) und zwei Relativlagern;
• 3 eine Ausführungsform entsprechend der 2, jedoch mit Ausführungsform der hydrodynamischen Kupplung als Doppelkupplung;
• 4 eine erfindungsgemäß ausgeführte hydrodynamische Kupplung mit drei Gehäuselagern und einem Relativlager;
• 5 eine mögliche Gestaltung der Abdichtung zwischen Läufer und Gehäuse, hier auf der Abtriebsseite;
• 6 einen Axialschnitt durch den Bereich der Dichtung zwischen der Abtriebswelle und dem Gehäuse;
• 7 einen gegenüber der 6 in Umfangsrichtung versetzen Axialschnitt;
• 8 eine mögliche Gestaltung der Abdichtung zwischen Läufer und Gehäuse, hier auf der Antriebsseite;
• 9 einen Axialschnitt durch den Bereich der Dichtung zwischen der Antriebswelle und dem Gehäuse;
• 10 einen gegenüber der 9 in Umfangsrichtung versetzen Axialschnitt.

Show it:

• 1 a possible filling control for a hydrodynamic coupling according to the invention;
• 2 an inventively designed hydrodynamic coupling with two bearings in the housing (housing bearings) and two relative bearings;
• 3 an embodiment according to the 2 , but with embodiment of the hydrodynamic coupling as a double clutch;
• 4 an inventively designed hydrodynamic coupling with three housing bearings and a relative bearing;
• 5 a possible design of the seal between rotor and housing, here on the output side;
• 6 an axial section through the region of the seal between the output shaft and the housing;
• 7 one opposite the 6 offset in the circumferential direction axial section;
• 8th a possible design of the seal between rotor and housing, here on the drive side;
• 9 an axial section through the region of the seal between the drive shaft and the housing;
• 10 one opposite the 9 in the circumferential direction offset axial section.

In the 1 is a hydrodynamic coupling with an external working fluid circuit 15 shown. The external working medium circuit 15 serves to cool the in the work space 3 the hydrodynamic coupling heated working medium, as well as the setting of a predetermined degree of filling in the working space 3 that is the setting of a given in the work space 3 located and there circulating in a hydrodynamic circulation flow amount of working fluid. The in the workroom 3 The amount of working fluid in turn determines that of the impeller 1 on the turbine wheel 2 transmitted torque.

In the external working medium circuit 15 is a working medium cooler 18 arranged. The external working medium circuit 15 is via a working fluid supply 16 and a work medium discharge 17 connected to the hydrodynamic coupling.

In the case 6 the hydrodynamic coupling is a working medium reservoir 21 provided by a filling valve 19 and an emptying valve 20 on the external working medium circuit 15 connected.

The supply of the working medium from the external working medium circuit 15 in the workroom 3 via the working medium supply 16 , here by introducing the working medium into a gutter 16a , from which the working medium promoted by centrifugal force through holes 16b in the workroom 3 or the prevailing circulation flow of the working medium flows there. In the holes 16b For example, nozzle screws may be provided which the amount of working medium passing through and thus together with the degree of filling of the working space 3 the circulating volume in the external working medium circuit 15 determine.

By means of a in the housing 6 the hydrodynamic coupling projecting dynamic pressure pump 22 becomes working medium from an adjoining room 23 , its level with the level in the working space 3 corresponds, because a corresponding connection is provided, skimmed off and on the Arbeitsmediumabfuhr 17 discharged from the hydrodynamic coupling.

To working medium from the working medium supply 21 in the external working medium circuit 15 To promote is a pump 25 intended.

The housing bearings 7 and 8th as well as the relative bearings 10 and 11 are lubricated with working fluid. For this branching a lubricant line 53 from the external working medium circuit 15 or from the pressure side of the pump 25 from. About this lubricant line 53 become the bearings 7 . 8th . 10 and 11 supplied with working fluid as a lubricant, wherein oil supply holes 24 , 27 in the housing 6 are provided. From the camps 7 . 8th . 10 and 11 the working medium flows into the working medium circuit in the working area 3 ,

When the degree of filling of the work space 3 is to be increased, via the filling valve 19 additional working medium from the Working medium supply 21 in the external working medium circuit 15 directed as shown above. In particular, the drain valve is 20 closed. When the degree of filling of the working space 3 is to be reduced, is via the drain valve 20 more working fluid from the external working fluid circuit 15 derived as over the filling valve 19 from the working medium supply 21 is supplied. In this case, the filling valve 19 be closed or on tank, that is in the direction of the working medium supply 21 , be connected.

In the 2a is a cross section through a hydrodynamic coupling according to the invention shown, in which the with the impeller 1 connected drive shaft 4 about a camp 7 in a frontal side 12 the housing 6 and a relative bearing 11 , which is in the area of the free end of the impeller 1 or with this revolving impeller shell 26 is arranged on the output shaft 5 is stored. The output shaft 5 carries the turbine wheel 2, wherein impeller 1 and turbine wheel 2 only each with their radially inner connection areas are shown, so that the working space 3 forming bladed areas are not recognizable.

The type of clutch shown is a so-called external-wheel drive, since the turbine wheel 2 from the impeller 1 together with the impeller shell 26 , which forms, so to speak, an inner casing of the hydrodynamic coupling, which rotates, is enclosed.

The output shaft 5 and with it the turbine wheel 2 are at the output end with a bearing 8th in the case 6 stored, namely in the front 13 , At the opposite end is the output shaft 5 with the relative bearing 10 on the drive shaft 4 , here inside the drive shaft 4 , which is designed as a hollow shaft at its output end, stored. The other relative bearing 11 between the drive shaft 4 and the output shaft 5 on the other hand, it is preferably located in the axial direction between the two end faces 12 . 13 of the housing, here in the area of the axial center 14 ,

Also in the design according to the 2a gets inside the impeller shell 26 an adjoining room 23 formed, from which the working fluid can be skimmed by means of a dynamic pressure pump, not shown here. Especially comes in the 1 contemplated filling control, also in the other embodiments described below.

The two rotor parts - drive shaft 4 with all with these rotating components and output shaft 5 with all with these rotating components - thus have together two relative bearings. At the same time, the complete rotor, that is to say the unit consisting of all circulating components, is in the two housings fixed in the housing 7 . 8th stored. Such storage occurs both in the 2a embodiment shown as a monocoupling as well as in the in 3 embodiment shown as a double clutch into consideration.

All bearings 7 . 8th in the case 6 and the relative bearings 10 . 11 can be lubricated with working fluid. These are corresponding oil supply holes 24 . 27 in the case 6 intended. In the 2 B are the oil supply holes 27 in the case 6 for the warehouse 8th and the camp 11 (see the 2a ). With 54 and 55 are in the 1 Drain holes for the emerging from the corresponding bearings working medium referred.

The drive-side relative bearing 10 lies directly radially inside the drive-side housing bearing 7 that is the camp 7 and the relative bearing 10 lie in a common radial plane. In the embodiment shown, the relative bearing 10 completely over its entire axial length from the bearing 7 in the case 6 enclosed. By this arrangement, no additional radial loads, in particular no tilting moment on the drive shaft 4 because there is no leverage in the connection of the bearing inner ring of the bearing 7 and the bearing outer ring of the relative bearing 10 results.

To also the relative bearing 10 with working fluid or lubricating oil from the oil supply hole 24 to be able to supply, is also in the drive shaft 4 at least one oil supply hole 28 provided a conductive connection between the oil supply hole 24 and the relative bearing 10 manufactures.

For sealing the oil supply holes 24 . 28 are preferred gap seals between housing 6 and drive shaft 4 in the axial direction on both sides of the mouth of the oil supply hole 24 or the oil supply hole 28 provided, for example in the form of piston rings.

The impeller 1 is by means of a pressure ring 29 screwed on the front side of the drive shaft 4. The pressure ring 29 has a smaller inner diameter than the inner diameter of the outer ring of the relative bearing 10 , By this measure is a permanent lubrication of the relative bearing 10 ensured, even if no oil is pumped for a short time. About this pressure ring 29 the running oil drain also takes place so that the relative bearing 10 not flooded.

The relative bearing 10 is designed as a floating bearing. The federal government in the output shaft 5 serves to fix the bearing inner ring. The bearing outer ring is on an opposite collar of the drive shaft 4 fixed. Thus, no further fixation is necessary.

The output side relative bearing 11 , however, for supporting the drive shaft 4 on the output shaft 5 serves, has a Lagerhaltering 30 on, in the output side end of the rotor, that is in the impeller shell 26 is screwed. If the bearing retainer 30 is made of a ferrous material and screwed into the runners made of aluminum, a secure fit is achieved even with thermal expansion.

The storage ring 30 preferably has an inner diameter which is smaller than the inner diameter of the outer ring of the relative bearing 11 , By this measure is a permanent lubrication of the relative bearing 11 ensured, even if no oil is pumped for a short time. About this storage ring 30 The running oil drain also takes place so that the warehouse is not flooded.

The lubrication of the relative bearing 11 via an axial nozzle 56 in the case 6 who are well-close to the relative camp 11 injected.

Such an axial nozzle 57 can also in the shown oil supply hole 27 for lubrication of the warehouse 8th in the front side 13 of the housing 6 be provided. Both axial nozzles 56 . 57 can be operated from the same oil channel. The required quantities of oil can be matched by means of diaphragms.

The oil drain from the warehouse 8th in the housing is through one or more holes 31 running below the camp 8th in the case 6 are positioned. The holes 31 are offset at an angle to the radial plane, so that a small oil sump is present and the bearing is not without lubrication. The warehouse 8th is designed as a fixed bearing and fixes the output shaft 5 and with it the turbine wheel 2 in the case 6 ,

The drive-side bearing 7 in the housing is designed as a floating bearing, also here is an axial nozzle for lubrication 32 in the case 6 intended. As shown, the same oil channel (oil supply hole 24 ) also for lubrication of the drive-side relative bearing 10 , Again, the required quantities of oil can be matched by means of screens / nozzles.

The oil drain is mainly on the camp 7 in the overflow channel 58 of the impeller 1 , For partial filling of the work space 3 the working medium flows out of the warehouse 7 in the workroom 3 (the overflow trough 58 is via holes 59 with the workspace 3 connected). In nominal operation, the working medium runs out of the overflow channel 58 in the designated 60 part of the housing 6 ,

The embodiment according to the 3 corresponds to that of 2a with the only difference being that two work spaces 3 are provided to form a dual clutch. Accordingly, two turbine wheels 2 on the output shaft 5 attached. Furthermore, there are two pump wheels 1 on the drive shaft 4 attached. Incidentally, on the zur 2a Executed referenced.

In the embodiment according to the 4 the corresponding reference numerals are used for the corresponding components. Deviating from the previous embodiments is a single relative bearing 10 intended. With the relative bearing 10 is the output shaft 5 in the drive shaft 4 is stored. The relative bearing 10 is designed as a paired angular contact ball bearings in X-arrangement, but this is not mandatory. The relative bearing 10 is via a nozzle that enters a gutter of the drive shaft 4 injects, supplied with working medium, in particular oil. The nozzle is preferably supplied from the same oil passage as the nozzle for the lubrication of the drive-side housing mounting, that is, the bearing 7. Again, the required quantities can be matched by means of diaphragms and / or nozzles.

A bearing retainer ring is preferred 30 with the drive shaft 4 screwed. The storage ring 30 is made of an iron material, for example, the drive shaft 4 made of aluminum, or preferably also made of a ferrous material such as steel. Thus, a change in the seat of the bearing can be avoided even with thermal expansion.

The oil drain preferably takes place from the relative bearing 10 on the side facing away from the supply into the work space 3 the hydrodynamic coupling.

The relative bearing 10 can be designed as a fixed bearing and the relatively rotating rotor parts, that is, the drive shaft 4 and the output shaft 5 or fix them with these rotating components, axially.

The impeller 1 and the turbine wheel 2 can, as shown, axially with a pressure ring 29 on the drive shaft 4 or the output shaft 5 fastened, in particular screwed be. The pressure ring 29 of the impeller 1 can at the same time the stock holder ring 30 form.

The drive shaft 4 gets through the bearings 7 and 9 in the case 6 stored, the output shaft 5 through the camp 8th , Thus, two housing bearings and thus a housing bearing are provided more than in the previous embodiments.

The additional warehouse 9 in the case 6 is here in the area of the axial center 14 between the two end faces 12 . 13 of the housing 6 intended. The bearings 7, 8 are in turn in the end faces 12 . 13 intended.

About the camp 9 in the case 6 the rotor is supported by the impeller 1 or the impeller shell 26 on a radially outer surface of the housing 6 from. The warehouse 9 is executed in the illustrated embodiment as a cylindrical roller bearing and as a floating bearing.

The bearing ring of the bearing 9 can be made of a ferrous material and with the impeller shell 26 and thus the drive shaft 4 be bolted. The impeller shell 26 is again preferably made of aluminum. The various materials again avoid unwanted effects of thermal expansion, which is the seat of the camp 9 could change.

The lubrication of the warehouse 9 takes place preferably via an axial nozzle in the housing 6 who are close to the camp 9 injected. The oil drain from the warehouse 9 takes place again on the opposite side.

The warehouse 7 in the front side 12 of the housing 6 is executed in the illustrated embodiment as a floating bearing and also here, the lubrication again via an axial nozzle in the housing 6 respectively. The same oil passage can also be used to lubricate the relative bearing 10 serve and the required quantities of oil can be matched by means of diaphragms. See also the 8th ,

The oil drain or generally lubricant or working fluid outflow from the warehouse 7 This is done via a labyrinth seal and an oil drain hole that goes from the labyrinth seal back into the housing 6 leads.

The warehouse 8th in the front side 13 is preferably designed as a double-row angular contact ball bearing, also referred to as a paired angular contact ball bearings executed. In the present case, an X arrangement of the two rows of bearings is again selected. The bearing lubrication can be done radially via an intermediate ring between the outer rings of the angular contact ball bearings.

The oil drainage is preferably carried out by bores located further down, which are positioned on both sides outside the opposite axial ends of the angular contact ball bearings and prevent the bearing is flooded. The bores are preferably offset at an angle to the radial plane, so that a small oil sump is ensured and the bearing 8th does not remain without lubrication.

The warehouse 8th can be designed as a fixed bearing and the output shaft 5 and the associated runner in the housing 6 fix axially.

In the 5 are advantageous details of the sealing of the passage of the output shaft 5 through the housing 6 shown, namely on the basis of the design of the hydrodynamic coupling according to the 4 ,

However, corresponding features could also be made in other designs, for example, in an embodiment according to the 2 and 3 ,

The 6 and 7 show in the circumferential direction of the output shaft 5 offset to 5 arranged sectional views with further details.

The 8th shows an advantageous seal of the drive shaft 4 through the housing 6 , as well as the lubricant supply to the bearing 8th , The 9 and 10 show corresponding advantageous details, again in axial sections, compared to the sectional view in the 8th positioned offset in the circumferential direction, the labyrinth reliefs are recognizable.

In the 5 to 10 For themselves corresponding components, the reference numerals from the 1 to 4 used.

The sealing of the drive shaft 4 and the output shaft 5 through the housing 6 takes advantage of multi-level labyrinths. Preferably, each stage has its own pressure relief, so that the working medium, in particular oil, can be removed without the pressure conditions of one stage of the labyrinth influencing the pressure of the next stage of the labyrinth.

Based on 5 is for the frontal sealing of the bearing 8th in the case 6 in the area of the front side 13 of the housing 6 a three-stage labyrinth seal shown. The first labyrinth stage is designated 33, the second labyrinth stage is designated 34, and the third labyrinth stage is designated 61. The corresponding labyrinth levels 33 . 34 and 61 one recognizes also in the 6 and 7 ,

In all three labyrinth levels 33 . 34 and 61 there is a deflection of the passing working medium flow of more than 180 °. As can be seen from the following illustration, this deflection is in the first labyrinth stage 3 but only by a slinger 35 achieved without further sealing tips are provided in this stage. In the second labyrinth stage 34 and in the third labyrinth stage 61 however, not just one is each Slider provided, but there are also sealing tips provided which cause a cross-sectional reduction of the gap to be sealed, in particular to zero or almost to zero, and further a deflection of the working medium flow. In that sense, the first labyrinth level could 33 also referred to as a precursor, the second labyrinth stage 34 then set the first maze level and the third maze level accordingly 61 the second labyrinth step, if only steps with sealing tips are considered a complete labyrinth stage. In the following, however, the "precursor" is already referred to as the first labyrinth stage.

The first labyrinth stage 33 takes out of the warehouse 8th emerging working medium. The first labyrinth stage has a first slinger 35 on, immediately adjacent to the output end of the bearing 8th is positioned on the output shaft 5 and with the output shaft 5 circulates. Between the front of the bearing 8th and the first centrifugal disc 35 there remains a gap that leaves the warehouse 8th Exiting working fluid is able to absorb, so that the working fluid from the centrifugal disc 35 is detected. In another embodiment, instead of the centrifugal disc 35 a fixed, that is non-rotating disc can be provided, which the Arbeitsmediumabfluss from the camp 8th reduced. In particular, such a disc is then adjacent to the bearing outer ring of the bearing 8th provided, since this stationary in the housing 6 is positioned, and with distance to the circumferential bearing inner ring.

In dargestellen case, for example, the first centrifugal disc 35 through one on the output shaft 5 screwed nut 36 or another suitable element.

Working medium, which is from the warehouse 8th in the axial direction on the first centrifugal disc 35 impinges, is thrown radially outwardly and may be in the radially opposite first gutter 37 be caught. This first gutter 37 is for example in the 6 and 7 seen. In the embodiment shown, it is in one in the housing 6 inserted, in particular screwed, cover 38 that drives the output shaft 5 in the area of the front side 13 encloses, introduced. To relieve the first labyrinth stage 33 is a process 62 provided from the 4 is apparent. The sequence 62 is as a hole in the housing 6 introduced and leads the working medium back into the interior of the housing 6 ,

Also the mother 36 or a corresponding retaining element on the bearing 8th opposite side of the first centrifugal disc 35 can be a covenant or radial projection 39 have, over the first centrifugal disc 35 overflowing working fluid radially outward to the first gutter 37 passes.

The lid 38 preferably has a radially inwardly projecting collar 40 which also retains escaping oil, so this through the first gutter 37 or another suitable drain opening (here the drain 62 in the 4 ) can expire.

The second labyrinth level 34 and the third labyrinth level 61 be through a stepped sealing ring 41 on the output shaft 5 formed, which rotates with the output shaft 5 and against the lid 38 which is stationary, seals. Also the stepped sealing ring 41 can be a slinger, the second slinger 42 , and further radially and / or axially aligned sealing tips 43 . 44 , 45, with corresponding radially and / or axially opposite sealing tips 46, 47 in the stationary lid 38 a labyrinth for gap sealing between the output shaft 5 and the housing 6 or form the lid 38 used. The circumferential radially inward standing sealing tip 44 the stepped sealing ring 41 , which could also be referred to as a slinger due to its rotation, also acts as a slinger, as a slinger of the third labyrinth stage 61 , All circumferential sealing tips or centrifugal discs of the second labyrinth stage 34 and the third labyrinth level 61 can be integrally formed by the stepped sealing ring 41.

In the flow direction of the working medium behind the second centrifugal disc 42 is a gutter 48 in the lid 38 provided, via which on the second centrifugal disc 42 Passing working medium can drain and a corresponding hole 49 in the lid 38 or housing 6 back into the housing or the sump or working fluid supply below in the housing 6 can be directed.

The drainage of the lubricant (working fluid) via the drainage channel 48 is through the in the 6 and 7 special design of the contour of the lid 38 with a collar 50 and a first in the axial direction and then radially outward sealing tip 46 favored.

Even if lubricant over this sealing tip 46 flows away, so is in front of the last sealing tip 47 another covenant 51 in the lid 38 provided, the lubricant into the hole 49 passes. Behind the last sealing tip 47 Therefore, the sealing gap should be dry in any operating condition.

The output side of the last sealing tip 47 provided felt ring 52 serves as dust protection. This felt ring 52 is preferably not circumferential in the lid 38 or housing 6 used.

Thus, in the embodiment shown in the 4 to 7 in every labyrinth level 33 . 34 and 61 or - when viewed with a preliminary stage - in the preliminary stage ( 33 ) and the first labyrinth stage ( 34 ) as well as the second labyrinth stage ( 61 ) each provided a slinger, followed by a baffle against which the working fluid is passed. This achieves a particularly reliable seal.

The inlet of the working fluid to the bearing 8th is in the 5 again by means of an oil supply hole 27 in the case 6 shown. The relevant process, that is the main process for the working medium from the warehouse 8th , gets through the drain hole 55 ensured, here again in the axial direction next to the camp 8th empties.

Also in the in the 8th to 10 illustrated drive-side bearings 7 is a multi-stage, here again two-stage labyrinth seal with precursor or three-stage labyrinth seal provided with a first labyrinth stage 33 and a second labyrinth step following the vicinity of the hydrodynamic coupling 34 , as well as a subsequent third labyrinth stage 61 , Each labyrinth level 33 . 34 . 61 has a centrifugal disc, see the first centrifugal disc 35 in the axial direction immediately next to the bearing 7 at the beginning of the second labyrinth stage 34 provided second centrifugal disc 42 and those through the sealing tip 44 trained third slinger of the third labyrinth stage 61 ,

Again, there is a mother 36 , preferably with a radial projection 39 , analogous to the execution in the 5 to 7 , intended.

According to the previous illustrations, the first centrifugal disc hurls 35 Working medium in the first gutter 37 whereas on the second centrifugal disc 42 transgressing working fluid in the gutter 48 and over the hole 49 in the lid 38 and housing 6 is derived.

The stepped sealing ring 41 in turn has corresponding axially and / or radially aligned sealing tips 43 . 44 . 45 on, with axially and / or radially aligned sealing tips 46 . 47 in the lid 38 work together to form a labyrinth. The radially aligned sealing tip 44 , with or as part of the sealing ring 41 revolves, as set forth, the third centrifugal disc.

Regarding fret 50 , Federation 51 and felt ring 42 Reference is made to the above illustrations.

From the representation in the 2 and 3 shows that here on the drive side of the labyrinth no further drainage possibility for the working fluid from the bearing or from the oil supply is provided, since here, as described above, a gap seal throttles the working fluid access into the labyrinth, so that the relatively small entering working fluid through the labyrinth steps can be removed.

On the output side, the exiting working fluid is throttled by a stationary disc and returned to the housing in a separate drain, wherein the radially located inside the disc snap ring, which is preferably provided, also acts as a centrifugal disc and reduces the flow.

The labyrinth seals have the advantage that they work reliably and wear-free.

LIST OF REFERENCE NUMBERS

1

impeller

2

turbine

3

working space

4

drive shaft

5

output shaft

6

casing

7

Bearings in the housing

8th

Bearings in the housing

9

Bearings in the housing

10

relative bearing

11

relative bearing

12

front

13

front

14

center

15

external working medium circuit

16

Working medium supply

16a

gutter

16b

drilling

17

Working medium removal

18

Working medium cooler

19

filling valve

20

drain

21

Working medium supply

22

Dynamic pressure pump

23

Outbuildings

24

Oil supply hole

25

pump

26

pump wheel

27

Oil supply hole

28

Oil supply hole

29

pressure ring

30

Bearing retainer

31

drilling

32

axial nozzle

33

first maze level

34

second maze level

35

first centrifugal disc

36

mother

37

first gutter

38

cover

39

radial projection

40

Federation

41

stepped sealing ring

42

second centrifugal disc

43

sealing tip

44

sealing tip

45

sealing tip

46

sealing tip

47

sealing tip

48

gutter

49

drilling

50

Federation

51

Federation

52

felt ring

53

lubricant line

54

drain hole

55

drain hole

56

axial nozzle

57

axial nozzle

58

Spillway

59

drilling

60

housing part

61

third maze level

62

procedure

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 202014006629 U1 [0002, 0004]
• DE 202014006625 U1 [0005]

Claims (14)

Hydrodynamic coupling 1.1 with at least one bladed impeller (1) and at least one bladed turbine wheel (2), which together form at least one filled or filled with a working fluid working space (3), in which by driving the impeller (1) a hydrodynamic circulation flow to the drive the turbine wheel (2) can be formed; 1.2 with a drive shaft (4), which carries the impeller (1) integrally or as a separate component, at least indirectly; 1.3 with an output shaft (5), which carries the turbine wheel (2) integrally or as a separate component, at least indirectly; 1.4 with a housing (6) enclosing the impeller (1) and the turbine wheel (2); wherein 1.5 the drive shaft (4) and the output shaft (5) by means of at least one bearing (7, 8, 9) are mounted in the housing (6); characterized in that 1.6 the drive shaft (4) and / or the output shaft (5) in addition by means of at least one relative bearing (10, 11) against the respective other shaft (4, 5) are mounted. Hydrodynamic coupling according to Claim 1 , characterized in that the bearings (7, 8, 9) in the housing (6) and the at least one relative bearing (10, 11) are designed as rolling bearings. Hydrodynamic coupling according to one of Claims 1 or 2 , characterized in that the drive shaft (4) and the output shaft (5) in each case by means of a bearing (7, 8) in the region of one end face (12, 13) of the housing in the housing (6) and in each case by means of a relative bearing (10, 11) are mounted against each other. Hydrodynamic coupling according to Claim 3 , characterized in that a relative bearing (10) in the region of an end face (12) of the housing (6) and a relative bearing (11) in the region of an axial center (14) between the two end faces (12, 13) of the housing (6). is positioned. Hydrodynamic coupling according to Claim 4 , characterized in that the relative bearing (10) in the region of the end face (12) of the housing (6) radially within the bearing (7) in the housing (6), in particular completely enclosed by this is positioned. Hydrodynamic coupling according to one of Claims 3 to 5 , characterized in that a relative bearing (10), in particular the relative bearing (10) in the region of the end face (12) of the housing (6) as a movable bearing and a relative bearing (11) is designed as a fixed bearing. Hydrodynamic coupling according to one of Claims 3 to 6 , characterized in that a bearing (7) in the housing (6) as a movable bearing and a bearing (8) in the housing (6) is designed as a fixed bearing. Hydrodynamic coupling according to one of Claims 1 or 2 , characterized in that the drive shaft (4) or the output shaft (5) with two axially spaced bearings (8, 9) in the housing (6) is mounted and the other shaft (4, 5) by means of a single bearing (7 ) is mounted in the housing (6) and one, in particular a single, relative bearing (10). Hydrodynamic coupling according to Claim 8 , characterized in that the relative bearing (10) is designed as a fixed bearing. Hydrodynamic coupling according to one of Claims 1 to 9 , characterized in that the bearings (7, 8, 9) in the housing (6) and the at least one relative bearing (10, 11) are lubricated with the working medium. Hydrodynamic coupling according to one of Claims 1 to 10 , characterized in that the hydrodynamic coupling is designed as a double clutch with two, in particular axially juxtaposed work spaces (3). Hydrodynamic coupling according to one of Claims 1 to 10 , characterized in that the hydrodynamic coupling has a single working space (3). Hydrodynamic coupling according to one of Claims 1 to 12 , characterized in that the hydrodynamic coupling is designed as a filling-controlled coupling, with an external working medium circuit (15) which is connected via a working medium supply (16) and a Arbeitsmediumabfuhr (17) to the at least one working space (3), wherein in the external working medium circuit (15) a working medium cooler (18) is provided and the external working medium circuit (15) in particular via a filling valve (19) and an emptying valve (20) to a working medium supply (21) for adjusting the circulating in the external working medium circuit (15) working fluid quantity is connected. Hydrodynamic coupling according to Claim 13 , characterized in that the working medium supply (21) within the housing (6) is provided.

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