阅读说明：本技术 液力机械、尤其是液力偶合器 (Hydraulic machine, in particular hydraulic coupling ) 是由 赫尔穆特·弗勒绍斯 斯特凡·布鲁纳 海莫·布雷格勒 于 2020-09-24 设计创作，主要内容包括：本发明涉及液力机械、尤其是液力偶合器。液力偶合器具有至少一个第一叶轮作为泵轮(20)并且具有分别配属于泵轮(20)的第二叶轮作为涡轮(23)。通过泵轮(20)和涡轮(23)来形成工作腔(10)。为了传递转矩,工作腔(10)被填充或能被充填工作介质。在其中至少一个叶轮(20、23)中设置有至少一个溢流通道(30)、优选多个溢流通道(30),用以将工作介质从至少一个工作腔(10)中排出。优选地,该至少一个溢流通道(30)穿过相应的叶轮(20)的叶轮壳(21)。(The present invention relates to a hydraulic machine, in particular a hydraulic coupling. The hydrodynamic coupling has at least one first impeller as a pump wheel (20) and second impellers, each associated with a pump wheel (20), as turbines (23). A working chamber (10) is formed by a pump wheel (20) and a turbine wheel (23). For transmitting torque, the working chamber (10) is filled or can be filled with a working medium. At least one overflow channel (30), preferably a plurality of overflow channels (30), is provided in at least one of the impellers (20, 23) for discharging the working medium from at least one working chamber (10). Preferably, the at least one overflow channel (30) passes through an impeller shell (21) of the respective impeller (20).)

1. Fluid coupling (4) having at least one first impeller as pump impeller (20), wherein each pump impeller (20) is assigned a second impeller as turbine wheel (23), wherein a working chamber (10) is formed by the pump impeller (20) and the turbine wheel (23) and the working chamber (10) is filled or can be filled with a working medium for transmitting torque,

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

at least one overflow channel (30), preferably a plurality of overflow channels (30), is provided in at least one of the impellers (20, 23) for discharging the working medium from at least one working chamber (10), and preferably the at least one overflow channel (30) passes through an impeller shell (21) of the respective impeller (20).

2. A fluid coupling according to claim 1,

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

the at least one overflow channel (30) has an inflow opening (41) pointing towards the axis of rotation, wherein the opening (41) is preferably arranged in the region of the radially inner half, preferably the radially inner third, of the blades (22) of the impeller (20).

3. A fluid coupling according to claim 1 or 2,

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

the overflow channel (30) is integrated into a blade (35) of the impeller (20) and preferably opens into a recess (36) of the blade (22).

4. A fluid coupling according to any one of the preceding claims,

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

the overflow channel (30) is at least partially cast into a blade of the pump wheel (20) or the turbine wheel (23).

5. A fluid coupling according to any one of the preceding claims,

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

the at least one overflow channel (30) is integrated in the pump wheel (20).

6. A fluid coupling according to any one of the preceding claims,

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

the at least one overflow channel (30) is integrated into an impeller designed as an outer rotor (33).

7. A fluid coupling according to any one of the preceding claims,

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

the length (31) of the overflow channel (30) exceeds 70% of the radial length (31) of the vanes, wherein the overflow channel (20) is a small tube that can be inserted from the outside, wherein the length of the small tube (40) is adjustable.

8. A fluid coupling according to any one of the preceding claims,

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

the overflow channel (40) can be closed at its radially outer end, preferably in the region through the impeller shell (21), by a closure (32) and can thereby be deactivated.

9. A fluid coupling according to any one of the preceding claims,

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

a receptacle (42) for receiving a closure (32, 34) for partially and/or completely closing the overflow channel (40) is formed in the connecting flange (17) of the impeller.

10. A fluid coupling according to any one of the preceding claims,

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

the overflow channel (40) is arranged in at least one impeller having an XL profile (11).

11. A fluid coupling according to any one of the preceding claims,

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

the coupling has two pump wheels (20) and two turbine wheels, and the overflow channel (40) is provided in only one of the impeller wheels (20).

12. A fluid coupling according to any one of the preceding claims,

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

at least four overflow channels (40) are provided, and at most one overflow channel (40) is associated with every fourth vane of at least one of the impellers.

13. Drive train, in particular for a chain conveyor with a drive and a dynamic coupling,

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

the drive train (1) has at least one fluid coupling (4) according to one of the preceding claims, which has at least one overflow channel (40).

14. A goods conveyor or chain conveyor having a plurality of drive trains,

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

at least one of said drive trains having a fluid coupling (4) according to any one of claims 1 to 12.

Technical Field

The invention can in principle be applied to any type of hydraulic machine and thus to a torque converter, a fluid coupling or a hydrodynamic retarder. However, this application is particularly advantageous in fluid couplings having a so-called impeller, which is usually driven by the input shaft, as the primary impeller with vanes and a so-called turbine, which is driven by the impeller by a circulating flow in the working chamber, as the secondary impeller. The turbine is typically carried by or in driving connection with a driven shaft of this kind.

Background

DE 202014006630 discloses a hydraulic machine, which is embodied in particular as a hydraulic coupling. The coupling has a bladed primary wheel and a bladed secondary wheel. The impellers form an annular working chamber which is filled or can be filled with a working medium for generating a hydrodynamic circulating flow of the working medium. By means of the hydrodynamically circulating fluid, torque or drive power can be transmitted from the primary wheel (also referred to as pump wheel) to the secondary wheel (also referred to as turbine wheel) without losses and with damped rotational vibrations. A fixed throttle disk which projects into the working chamber can be arranged in the separating gap between the primary wheel and the secondary wheel. The torque limitation of the coupling can be achieved by the extension and position of the throttle disk.

It is also known that: the power data are predefined or set by setting the distance between the primary wheel and the secondary wheel.

A charge-controlled coupling is known from DE 102016215739 a1, in which the possible power transmission can be controlled by the amount of fluid in the working chamber of the coupling.

A fluid coupling for transmitting force from a drive motor to a work machine is known from EP 1127231B 1. Preferably, a work machine, such as a conveyor belt, having a large mass or transporting a large mass is concerned. The hydraulic coupling realizes that: the drive motor can be started only at low load. The work machine is moved only when the drive motor reaches its rated rotational speed, or even after the drive motor has reached the rated rotational speed. During the starting process of the working machine, the fluid coupling automatically limits the torque transmitted by it to a certain value, so that the drive motor and the working machine are protected. The invention relates only to a fluid coupling of the type which is operated with a constant quantity of working fluid. In other words, when the coupling is stopped, the inner space of the coupling is filled with a defined amount of operating fluid, which remains constant during operation. However, in addition to the bladed working chamber, the coupling has at least one reduction chamber rotating together with the primary wheel. In particular, when the coupling is stopped, a portion of the working fluid accumulates in the reduction chamber. Through this design, realized: the bladed working chamber is only partially filled with working fluid at the beginning of the starting process and the filling level in the working chamber is only gradually taken to the maximum possible value. It can be said that: to a coupling having an internal influence on the filling level of a working chamber. There are also fluid couplings with external influence on the filling level of the working chamber, for example by means of a scoop tube. This type of coupler has similar characteristics. However, the additional expenditure of means for external influencing is mostly only worthwhile if the power density is high.

A fluid coupling is also known, for example from DE 102016118588, which has an increased surface at the impeller and is thus able to transmit a greater drive power.

There are drive devices, for example for driving conveyor belts in the mining industry, in which a plurality of fluid couplings are arranged in parallel for power transmission. It happens that these fluid couplings must be replaced. If only one of the two couplings, for example, which are arranged on the drive location, such as the driven drum, has to be replaced, a new embodiment with a greater drive output is proposed on one side, but this is often dispensed with, since for reasons of cost it is not necessary to replace a plurality of, in particular two, fluid couplings arranged on the driven drum at the same time. On the other side, couplings of the same drive power are usually used.

In the case of chain conveyors, a plurality of drives are usually provided, which drive the chain at spatially different positions. Due to the connection to the chain, the rotational speed is predefined on the output side of the respective fluid coupling connected to the chain. In this way, different transmitted powers are obtained for different fluid couplings. Thus, for example, a fluid coupling with a large blade profile (also referred to as an XL profile) can have a higher power than a fluid coupling with a smaller blade size at the same slip ratio. If the two couplings are now arranged together on the chain conveyor, an overload of the fluid coupling with the XL profile may result as a result.

Disclosure of Invention

The object on which the invention is based is to provide a fluid coupling whose power and operating capacity can be reduced. Preferably, the operating capacity can be reduced due to the structure of the fluid coupling.

According to the invention, this object is achieved by the embodiment according to claim 1. Further advantageous features of the embodiments according to the invention are found in the dependent claims.

This task is solved by: the drive power of the new hydraulic machines used, in particular of the hydraulic couplings, is deliberately reduced. At a later point in time, the reduction can be cancelled again. Thus, if one or more other fluid couplings are also converted to a coupling with increased drive power, the conversion to a fluid coupling with increased drive power can be accomplished.

The cost and cost of such a change should be as low as possible. It is particularly desirable to make the changeover without disassembling the coupling.

Through the overflow channel, the power curve of the coupling can be changed, in particular the transmissible torque can be reduced. The working medium can be discharged from the working chamber via an overflow channel. This reduces the torque that can be transmitted by the coupling.

If, for example, several drive trains are provided on a chain conveyor and one of the fluid couplings may already be transmitting a high torque to the chain at a high slip rate, there is the danger of just overloading the drive train. The reason for this is that: the drive power of the coupling is caused by the torque and the drive train is connected with other drive trains via a chain. In such a configuration, it is advantageous to reduce the transferable drive power or to coordinate the transferable drive power with other drive trains. The coordination or reduction can be carried out in particular by means of a fluid coupling.

It has proven advantageous: the overflow channel has an opening through the blade shell.

In a preferred embodiment, the overflow channel has a branch, wherein the branch preferably has an opening towards the scoop. In this way, the working medium can be fed directly from the working chamber to the scoop tube.

In a preferred embodiment, provision is made for: at least one overflow channel has an opening directed toward the axis of rotation for receiving a working medium. This allows the working medium to be discharged when the working medium flows into the impeller. It has proven advantageous: the opening is arranged in the region of the radially inner half of the impeller, preferably in the region of the radially inner third.

In a preferred embodiment, provision is made for: the overflow channel is integrated into the blades of the impeller. The arrangement of the overflow channel in the vane has a favorable effect on the stability. The overflow channel can be supported in particular by vanes. It is also conceivable to arrange directly in front of the blade. Another advantage brought about by direct integration into the blade is: the relative movement of the vanes and the overflow channel is prevented, which can also have a favorable effect on noise development, in particular.

In a preferred embodiment, provision is made for: the overflow channel is at least partially cast. The production costs can thereby be kept low.

In a preferred embodiment, provision is made for: at least one overflow channel is provided in the pump wheel or even integrated into the vanes of the pump wheel. It has been shown that: arranging the overflow channel in the pump wheel is particularly efficient.

In a further embodiment, provision is made for: at least one overflow channel is integrated into the impeller, which is designed as an outer rotor. The radially outwardly directed opening of the impeller is thereby particularly easily accessible. In particular, it is possible to subsequently close the overflow channel via a closable installation opening, which is usually provided in the housing. It is not necessary to disassemble the fluid coupling for this purpose.

In a preferred embodiment, provision is made for: the length of the overflow channel exceeds 70% of the radius of the blades of the respective impeller. It has proven advantageous: a small tube which can be inserted from the outside in the radial direction is used as an overflow channel, wherein the length of the small tube is adjustable and the power data of the fluid coupling can be adjusted by selecting the length.

In a further embodiment, provision is made for: the overflow channel can be closed at its radially outer end, preferably in the region through the impeller shell, by a closure and can thereby be deactivated. For the purpose of sealing, a corresponding receptacle for the seal is formed in the housing of the respective impeller.

In a further embodiment, provision is made for: a receptacle for receiving a closure element for partially and/or completely closing off the overflow channel is formed in the connecting flange of the impeller. Preferably, the radial openings of the overflow channels are arranged between the axially arranged flange holes.

In a further embodiment, provision is made for: the overflow channel is arranged in at least one impeller with an XL profile. This expands the application possibilities of the fluid coupling. In particular, it may be used with other modules having different power curves.

It has proven advantageous: in the case of a coupling with two pump wheels and two turbine wheels, only one of the impeller wheels, preferably only one pump wheel, is equipped with an overflow channel. In this way, it is particularly simple to adjust the power data later by closing the overflow channel. Such an arrangement also has a favorable impact on manufacturing costs.

Preferably, the transfer channel is used only in fluid couplings with controlled filling. In the case of this coupling type, the working medium which is discharged via the overflow channel can be fed back by the already existing pump.

It has proven advantageous: at least four overflow channels are provided and at most one overflow channel is associated with every fourth vane of one of the impellers. Preferably, the overflow channels are integrated into the respective blade.

The fluid coupling described above is particularly suitable for use in a chain conveyor.

The fluid coupling described above can be operated particularly advantageously with water as the working medium.

Drawings

Further advantageous forms of realization of the invention are explained according to embodiments with reference to the drawings. The features mentioned can advantageously be implemented not only in the combinations shown but also individually in combination with one another. These drawings show in detail:

figure 1 shows a 3D representation of an impeller with an integrated overflow channel;

figure 2 shows the impeller in a 2D view;

FIG. 3 shows a segment of a fluid coupling having an overflow channel;

FIG. 4 shows a conveyor having a drive train;

fig. 5 shows a hydrodynamic double coupling with a closed transfer channel.

Detailed Description

These figures are described in more detail below.

First, a drive train 1 for driving a chain conveyor with a chain 7 is described according to fig. 4. By means of the conveyor chain, the goods to be conveyed can be transported in the conveying direction 12. For driving the chain, a drive train is provided, which drives the chain by means of a drive drum. For driving the chain 7, a plurality of drive trains, not shown, are provided distributed over the conveying path. The drive trains are kept connected via chains. If different drive lines are now introduced for the different drive trains, each drive train may be overloaded.

The drive train shown in fig. 4 has a motor 2, a fluid coupling 3 and a transmission 4. The driving power of the motor is transmitted to the shaft 5 of the drive drum 6 via the fluid coupling 3 and the transmission 4. In the case of chain conveyors, the coupling of the drive train is more pronounced, since the slipping of the chain star wheel may be less easy than the slipping of the drive drum in a goods conveyor.

The fluid coupling 3 has a housing 8, wherein the housing 8 is equipped with a housing cover 9. A possible arrangement of the fluid coupling is shown in fig. 5 in segments. The coupling 3 has first and second pump wheels 20. The two pump wheels 20 are connected to one another by a connecting element 18. These pump wheels are configured as outer rotors. A turbine is assigned to each pump wheel. The turbines are designed as internal rotors, i.e. the connection of the two turbines 23 is arranged radially within the connection of the two pump wheels.

Each of these pump wheels 20 has a pump wheel housing 21. The pump wheel housing is connected to the drive shaft and is driven by the drive shaft 15. The two turbines 23 also each have a turbine housing and a turbine blade 25 arranged in the turbine housing 24. These turbine blades are fixedly connected to the driven shaft 16. The torque is transmitted from the pump impeller 20 to the turbine wheel 23 by the working medium in the working chamber formed by the pump impeller 20 and the turbine wheel 23. The illustrated embodiment is a fillable fluid coupling which is filled with a working medium for torque transmission. For replacement, a scoop tube 14 is provided. The working medium escaping from the working chamber is conveyed away via the scoop tube 14.

The impeller facing the scoop tube is equipped with impeller blades 22 having overflow channels 30. The overflow channel 30 shown there comprises a small tube. If the small tube 40 is not integrated into the blade, an adjustment or change of the power curve of the coupling (Leistungsprofil) can be carried out by shortening the inserted small tube. The radial length of the small tubes is designated by 31 and relates to the radial extent of the respective impeller to which the overflow channel is assigned. The axial direction is denoted by 27 and coincides with the axis of rotation of the drive shaft 15/driven shaft 16.

If the small tube is fixedly connected to the blades, such as is shown in fig. 1 and 2, it cannot be shortened from the outside in this way simply. The adjustment can be performed by narrowing the range of the inflow opening 41 of the overflow passage 30.

The overflow channels integrated in the blades have the following advantages: the overflow channel 30 is supported by the vanes 22. The overflow channel is configured at its radial end with a branch 37. The branch has an opening 39 directed in the axial direction towards the scoop tube and a radial opening 38. By providing a closure, the radial opening 38 and the axial opening 39 can be closed, as shown in fig. 5. However, it is also possible to close only the radial opening 38, as is shown in fig. 3. In the embodiment shown in fig. 3, a screw plug 34 is provided as the closure 32. By opening the cover 9 in the housing, the overflow channel 30 can also be easily closed later in the pump wheel designed as an outer rotor. By closing, the maximum operating capacity of the fluid coupling 4 can be achieved.

In the illustration shown in fig. 1, the overflow channel is integrated into the blade of the impeller. The flow direction of the working medium is depicted by the arrow 26. If there is little working medium in the coupling, no working medium has yet reached the overflow channel 30. Full cranking torque is provided. As the filling increases, the opening 41 of the overflow channel 30 is traversed and a portion of the working medium is discharged, whereby the transferable power is reduced. If the overflow channel is now limited by a partial closure, for example by a partial closure that can be fastened in the receptacle 42, the amount of the working medium flowing out is changed and thereby the power data of the coupling is changed. A screw plug 34 for completely closing off the overflow channel can also be fastened in the receptacle. Thereby, the maximum operation capacity of the fluid coupling can be provided.

Although an overflow channel 30 is shown in the pump impeller 20, it is also possible to provide an overflow channel in the turbine 23 for power regulation of the fluid coupling.

If a coupling with a large blade profile, as is known from EP 2140161, is to be used together with other couplings with a smaller power transmission, an overload of the coupling with the XL profile can be prevented by an initial power reduction. Wherein the power characteristic of the other drive trains can be adjusted by closing some of the provided overflow channels when the power characteristic changes.

List of reference numerals

1 drive train

2, a driver; motor with a stator having a stator core

3 fluid coupling

4 speed variator

5-shaft driving drum wheel

6 drive drum

7 conveying chain

8 casing

9 casing cover

10 working chamber

11 XL Profile (EP 2140161)

12 direction of conveyance

13

14 spoon tube

15 drive shaft

16 driven shaft

17 connecting flange

18 coupling element for a pump wheel

19

20 pump wheel

21 pump wheel shell

22 impeller blade

23 turbine

24 turbine shell

25 turbine blade

26 flow direction of the working medium

27 axial direction of the shaft

29 radial direction

30 overflow channel

31 radial length of the overflow channel

32 closure of overflow channel

33 outer rotor (Pump impeller)

34 screw plug

35 vane with integrated overflow channel

36 emptying part of inlet of overflow channel

37 branch

38 radial opening of the overflow channel

39 axial opening of the overflow channel

40 small tube

41 inflow opening of the overflow channel

42 closure receiving portion