Hydrodynamic converter and adjustment device for a converter of this type

Abstract

A hydrodynamic converter has a working chamber through which an operating medium can flow. A pump wheel is connected to a drive shaft and a turbine wheel is connected to a driven shaft. At least one positioning blade can be adjusted by an adjustment device. In order to provide a compactly formed and robust hydrodynamic converter of this type, having a hard-wearing adjustment device for adjusting at least one positioning vane, the adjustment device includes an actuating drive with ring elements. Each ring element is disposed coaxially in relation to the drive shaft. A first ring element is connected to the at least one positioning blade for transmitting a positioning force or a positioning torque via a diverting device. The first ring element can be rotated relative to a second ring element in the circumferential direction of the drive shaft.

Claims

1. A hydrodynamic converter, comprising: a working space, through which an operating medium can flow, a drive shaft and a pump wheel connected to said drive shaft; a driven shaft and a turbine wheel connected to said driven shaft; a stator; at least one adjustable blade being a pump wheel blade; and an adjustment device for adjusting said adjustable blade; said adjustment device having an actuator with a plurality of ring elements disposed coaxially with respect to said drive shaft, wherein a first ring element of said plurality of ring elements is connected to said at least one adjustable blade at least indirectly by way of a deflection device for transmitting an actuating force or an actuating torque, and wherein said first ring element is rotatable relative to a second ring element of said plurality of ring elements in a circumferential direction of said drive shaft; and wherein said first and second ring elements form at least two pressure chambers, which are arranged in the circumferential direction of the drive shaft and which can each be subjected to pressure for a relative rotation between said first and second ring elements.

2. The hydrodynamic converter according to claim 1, wherein said deflection device is formed by said actuator.

3. The hydrodynamic converter according to claim 1, wherein said second ring element is connected for conjoint rotation to said drive shaft and configured to take said first ring element along during a rotation of said drive shaft.

4. The hydrodynamic converter according to claim 1, wherein said first ring element forms a cylindrical housing, and said second ring element is arranged in said cylindrical housing.

5. The hydrodynamic converter according to claim 1, wherein each of said first and second ring elements has radially extending vanes arranged in mirror-image fashion and delimiting said pressure chambers in the circumferential direction.

6. The hydrodynamic converter according to claim 5, wherein said vanes have radially arranged sealing elements to seal off said pressure chambers.

7. The hydrodynamic converter according to claim 1, wherein said pressure chambers have stops for limiting a relative rotation between said first and second ring elements, said stops being arranged in the circumferential direction of said drive shaft.

8. The hydrodynamic converter according to claim 1, wherein at least one of said ring elements is formed with bores opening into said pressure chambers for an application of pressure.

9. The hydrodynamic converter according to claim 8, wherein said second ring element has said bores formed in a region of an outer diameter thereof.

10. The hydrodynamic converter according to claim 1, wherein said deflection device includes an adjusting ring, which is arranged coaxially with respect to said drive shaft and is connected for conjoint rotation to said first ring element, wherein said adjusting ring is coupled to said at least one adjustable blade for transmitting an actuating force or an actuating torque.

11. The hydrodynamic converter according to claim 1, wherein said adjustable blade comprises a pivoted blade or a multi-element blade having at least one pivoted segment.

12. The hydrodynamic converter according to claim 1, wherein said hydrodynamic converter is embodied as a counterrotating converter and the adjustment device is arranged outside said converter in the axial direction.

13. The hydrodynamic converter according to claim 12, wherein said adjustment device is arranged adjacent said pump wheel.

14. The hydrodynamic converter according to claim 1, which comprises a sensor for detecting an angular position between said first and second ring elements.

15. An adjustment device for a hydrodynamic converter, the hydrodynamic converter having a pump wheel connected to a drive shaft, the adjustment device comprising: an actuator with concentrically arranged ring elements; said ring elements including a first ring element to be connected to at least one adjustable blade of a pump wheel of the hydrodynamic converter for transmitting an actuating force or an actuating torque by way of a deflection device, and wherein said first ring element is rotatable relative to a second ring element in a circumferential direction thereof; wherein said first and second ring elements form at least two pressure chambers, which are arranged in the circumferential direction of a drive shaft of the pump wheel and which can each be subjected to pressure for a relative rotation between said first and second ring elements.

16. A hydrodynamic converter assembly, comprising: a counter-rotating hydrodynamic converter having a working space through which an operating medium can flow, a drive shaft and a pump wheel connected to said drive shaft, a driven shaft and a turbine wheel connected to said driven shaft, a stator and at least one adjustable blade; an adjustment device for adjusting said at least one adjustable blade; said adjustment device being arranged outside said converter in an axial direction and adjacent said pump wheel of said converter; said adjustment device having an actuator with a plurality of ring elements disposed coaxially with respect to said drive shaft, wherein a first ring element of said plurality of ring elements is connected to said at least one adjustable blade at least indirectly by way of a deflection device for transmitting an actuating force or an actuating torque, and wherein said first ring element is rotatable relative to a second ring element of said plurality of ring elements in a circumferential direction of said drive shaft.

17. The hydrodynamic converter according to claim 16, wherein said deflection device includes an adjusting ring, which is arranged coaxially with respect to said drive shaft and is connected for conjoint rotation to said first ring element, wherein said adjusting ring is coupled to said at least one adjustable blade for transmitting an actuating force or an actuating torque.

18. The hydrodynamic converter according to claim 17, wherein the adjusting ring has at least one cam, which interacts with a crank mechanism that is coupled to said adjustable blade.

19. The hydrodynamic converter according to claim 18, wherein said adjustable blade comprises a pivoted blade or a multi-element blade having at least one pivoted segment.

20. The hydrodynamic converter according to claim 18, wherein said at least one cam interacts with a radially arranged lever element.

21. The hydrodynamic converter according to claim 20, wherein said adjusting ring is formed with external toothing configured to mesh with an external toothing of a journal of said adjustable blade, which extends parallel to a central axis of said adjusting ring.

22. The hydrodynamic converter according to claim 17, wherein said hydrodynamic converter is embodied as a counterrotating converter and the adjustment device is arranged outside said converter in the axial direction.

23. The hydrodynamic converter according to claim 16, which comprises a sensor for detecting an angular position between said first and second ring elements.

Description

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

(1) The invention is described in greater detail below together with further details with reference to the attached drawings, in which:

(2) FIG. 1: shows a longitudinal section through a converter according to the invention along the drive shaft;

(3) FIG. 2: shows a cross-section through the actuator of the converter according to FIG. 1; and

(4) FIG. 3: shows a cutaway portion of the actuator according to FIG. 2.

DESCRIPTION OF THE INVENTION

(5) FIG. 1 shows a longitudinal section through a hydrodynamic converter according to an illustrative embodiment according to the invention. Converters of this kind are used in the control of pumps or compressors, for example, and can be coupled to mechanical gear units, e.g. planetary gear units. Different modes of use are conceivable here. Speed-controlled drives in a power range of from 1 to over 50 MW, for example, in the oil and gas industry and in thermal power plants are possible. The invention is not restricted to such modes of use but relates to hydrodynamic converters in general.

(6) The converter shown by way of example in FIG. 1 is specifically a single-phase counterrotating converter having a pump wheel 11, a turbine wheel 13 and a stator 14. In the counterrotating converter shown, the pump wheel 11 and the turbine wheel 13 rotate in opposite directions. The stator 14 is connected in a fixed manner to the stator housing 32 (single-phase converter). In the illustrative embodiment according to FIG. 1, the stator 14 forms a reversing stator, which is arranged between the pump wheel 11 and the turbine wheel 13.

(7) The invention is not restricted to the counterrotating converter shown. All the features described with reference to FIGS. 1-3 are disclosed and claimed in connection with a hydrodynamic converter in general.

(8) For example, multi-stage counterrotating converters can be designed in accordance with the invention. It is also possible to employ the invention with corotating converters, in which the pump wheel 11 and the turbine wheel 13 rotate in the same direction. It is also conceivable to employ the invention with multi-phase hydrodynamic converters, where, once again, single-stage or multi-stage designs are likewise possible.

(9) To be specific, the converter shown in FIG. 1 has a working space 10, through which an operating medium can flow. The converter has a pump wheel 11, which is connected to a drive shaft 12, and a turbine wheel 13, which is connected to a driven shaft (not shown). The turbine wheel 13 is rotatably mounted on the drive shaft 12, for example. In the illustrative embodiment shown in FIG. 1, the stator housing 32 with the stator 14 is arranged in a fixed manner. Revolving stator housings 32 are possible. Together with the housing of the turbine wheel 13 and with the housing of the pump wheel 11, the stator housing 32 forms a working space 10 which is enclosed in the form of a shell and in which the flow circuit forms during operation.

(10) The pump wheel 11 is connected for conjoint rotation to the drive shaft 12. For this purpose, a shaft shoulder is formed in the drive shaft 12, and the pump wheel 11 is screwed axially to said shoulder. Other shaft-hub connections are possible.

(11) The pump wheel 11 has at least one adjustable blade 15. The other pump blades of the pump wheel 11 can likewise be designed in a corresponding manner as adjustable blades 15. As an alternative, the remaining pump blades can be of rigid design.

(12) The adjustable blade 15 is assigned an adjustment device 16, which rotates with the pump wheel 11 during the operation of the converter. The adjustment device 16 has a deflection device 20 and an actuator 17. The deflection device 20 couples the actuator 17 to the adjustable blade 15.

(13) The actuator 17 has ring elements 18, 19, which are each arranged coaxially with respect to the drive shaft 12, i.e. the two ring elements 18, 19 are also arranged concentrically (see also FIG. 2).

(14) The first ring element 18 can be turned relative to the second ring element 19 in the circumferential direction of the drive shaft 12. The turning movements of the first ring element 18 actuate the deflection device 20, which transmits the turning motion of the ring element 18 to the adjustable blade 15 and changes the angle of attack of the adjustable blade 15.

(15) To be specific, in the illustrative embodiment shown in FIG. 1 the second ring element 19 is arranged on the inside and connected for conjoint rotation to the drive shaft 12. This can be accomplished by screwing the second ring element 19 axially to a shaft shoulder of the drive shaft 12, for example. The second ring element 19 rotates with the drive shaft 12. The rotatably mounted first ring element 18 forms a cylindrical housing 23 which encloses the second ring element 19. In other words, the second ring element 19 is arranged in the housing 23 of the first ring element 18. For this purpose, the first ring element 18 has a first end wall 33, which is arranged on the outside in the axial direction, and a second end wall 34, which is arranged on the inside in the axial direction, said walls delimiting the housing 23 in the axial direction. The housing 23 has an outer ring 35, which delimits the housing 23 in the radial direction and is arranged between the two end walls 33, 34. The counterpart to the outer ring 35 is formed by the inner ring 36 of the second ring element 19, which is seated directly on the drive shaft 12 and is screwed to the shaft shoulder, as described above. As can be seen in FIG. 1, the two end walls 33, 34 fit over the inner ring 36 in such a way that an annular space is formed between the first and the second ring element 18, 19. The first end wall 33 forms a sealing surface with respect to the outer circumference of the drive shaft 12.

(16) FIG. 2 shows a cross section through the two mounted ring elements 18, 19, from which the annular space and the internal fittings arranged therein can be seen. The two ring elements 18, 19 each have radially arranged vanes 24, 25, which act as rotary vanes by virtue of the relative rotation between the first and the second ring element 18, 19. To be specific, the first ring element 18 has first vanes 24, which are secured on the outer ring 35 and extend radially inward. The second ring element 19 has second vanes 25, which are formed on the inner ring 36 and extend radially outward. The vanes 24, 25 of the two ring elements 18, 19 are thus arranged mirror-image fashion.

(17) Pressure chambers 21, 22, the volume of which can be varied by means of the position of the respective vane 24, 25, are formed between the vanes 24, 25 of the two ring elements 18, 19. In other words, the distance between the vanes 24, 25 in the circumferential direction can be varied by turning the first ring 18.

(18) In each case one vane 24 of the first ring element 18 and a further vane 25 of the second ring element 19 together delimit a first pressure chamber 21. For this purpose, the first vane 24 of the first ring element 18 rests sealingly on the inner ring 36 of the second ring element 19. The same applies in a corresponding manner to the second vane 25 of the second ring element 19, which rests sealingly on the inner circumference of the outer ring 35 of the first ring element 18. The two vanes 24, 25 furthermore extend in the axial direction between the end walls 33, 34, on which the vanes 24, 25 likewise rest sealingly, with the result overall that a closed pressure chamber 21 is formed, which is delimited in the circumferential direction by the vanes 24, 25 and in the radial direction by the outer ring 35 and the inner ring 36.

(19) In the circumferential direction of the two ring elements 18, 19, a further pressure chamber 22 is formed, which is delimited in a corresponding manner by the vanes 24, 25 of the two ring elements 18, 19.

(20) In other words, a first vane 24 of the first ring element 18 is arranged between two second vanes 25 of the second ring element 19, with the result that a respective pressure space 21, 22 is formed on each side of the first vane 24.

(21) As can be seen in FIG. 2, a plurality of pressure chambers 21, 22 is formed in a corresponding manner on the circumference of the two ring elements 18, 19, wherein in each case a first vane 24 of the first ring element 18 and a second vane 25 of the second ring element 19 are arranged alternately. As a result, pressure chambers 21, 22 arranged in a manner distributed over the circumference are formed, said chambers extending on both sides of the first vane 24 of the first ring element 18.

(22) To produce the relative rotation between the two ring elements 18, 19, the pressure chambers 21, 22 can each be subjected to pressure. In the illustrative embodiment shown in FIG. 2, the pressure is produced hydraulically. In the operating state shown in FIG. 2, the pressure prevailing in the first pressure chamber 21 is higher than that in the second pressure chamber 22, with the result that the first vane 24 and hence ring element 18 is rotated clockwise. By changing the pressure ratios in the two pressure chambers 21, 22, adjustment of the first ring element 18 in the counterclockwise direction is possible.

(23) The first ring element 18 thus acts as an annular piston.

(24) To limit the stroke motion of the first ring element 18 in the circumferential direction, stops 27 are provided, against which the first vane 24 of the first ring element 18 strikes (see FIG. 2). The stops 27 can, for example, be designed as replaceable adjustment blocks which are screwed to the second vanes 25 of the second ring element 19 or secured in some other way.

(25) As shown in FIG. 2, the stops 27 are arranged on both sides of a first vane 24 of the first ring element 18 in order to limit the adjusting movement in both circumferential directions. Moreover, further stops 27 are arranged in point symmetry on the opposite side of the first ring element 18. The stops 27 can be seen in longitudinal section in FIG. 1.

(26) Further details of the actuator 17 can be seen in the detail view according to FIG. 3. Thus it can be seen from FIG. 3, for example, that bores 28 are formed in the second ring element 19, said bores serving as pressure channels for the supply of the hydraulic fluid. To be specific, the pressure channels are formed in the inner ring 36 and extend radially outward through the second vane 25. The bores 28 open into the respective pressure chambers 21, 22 in the region of the outside diameter of the pressure chambers 21, 22 (see also FIG. 1). In other words, the clearance at the outlet openings of the bores 28 with respect to the outer ring 35 is very much smaller than the clearance with respect to the inner ring 36. As a result, a scavenging effect is achieved, by means of which accumulation of contaminants on the outer ring 35 is to a large extent prevented.

(27) The feed channels which connect the bores 28 of the second ring element 19 to a feed device (not shown) are formed directly in the drive shaft 12 or in a component associated with the drive shaft 12. To be specific, a sleeve 37, in which the feed channels for supplying the pressure chambers 21, 22 with hydraulic fluid are formed, is arranged between the inner ring 36 of the second ring element 19 and the drive shaft 12. The connection between the inner ring 36 and the sleeve 37 can be made nonpositively, for example.

(28) To transmit the rotary motion of the first ring element 18 to the adjustable blade 15, the deflection device 20 described below is provided. The deflection device 20 is connected for conjoint rotation to the first ring element 18. As a result, it is possible to introduce a torque into the deflection device 20, which is transmitted to the adjustable blade 15. Transmission by the deflection device 20 can be accomplished by a superimposed translational/rotary motion or by an exclusively rotary motion. The torque introduced by the first ring element 18 imparts a pivoting motion to the adjustable blade 15, as a result of which the angle of attack of the adjustable blade 15 is changed.

(29) To be specific, the deflection device 20 has an adjusting ring 29 for this purpose, said ring being arranged coaxially. The adjusting ring 29 is seated on the outside diameter of the drive shaft 12 and can be rotated relative to the latter. The adjusting ring 29 is supported in the axial direction on the housing of the pump wheel 11, for example. The connection of the adjusting ring 29 for conjoint rotation to ring element 18 is made by means of the second end wall 34, arranged on the inside, of ring element 18, said wall being connected firmly to the adjusting ring 29. The connection can be made materially (welded joint) or positively or nonpositively, for example. The effect of the connection consists in taking the adjusting ring 29 along during a rotation of the first ring element 18. The adjusting ring 29 has a cam or driver on the end arranged axially on the inside, said driver interacting with a crank mechanism 30. The crank mechanism 30 is coupled to the adjustable blade 15. To be specific, the crank mechanism 30 has a lever element 31 or a push and pull rod, on the lower end of which a pin 38 is secured. The pivoting axis of the pin extends parallel to the central axis of the drive shaft 12. The upper end of the lever element 31 engages on the adjustable blade 15, specifically on an eccentrically arranged journal 39 of the adjustable blade 15, which projects axially from the housing of the pump wheel 11.

(30) Together with the pin 38, the driver forms a pivot joint, about which the crank mechanism 30 can be pivoted. The pivoting motion takes place in the circumferential direction of the drive shaft 12. The driver acts as a sliding bearing in which the pin 38 is arranged with the ability for rotary motion.

(31) The adjusting torque introduced by the adjusting ring 29 is transmitted to the crank mechanism 30 via the pin 38, which is supported in the driver of the adjusting ring 29. The crank mechanism 30 converts the rotary motion of the adjusting ring 29 into a superimposed translational/rotary motion of the crank mechanism 30, which brings about a tilting motion of the adjustable blade 15, thus allowing the desired angle of attack of the adjustable blade 15 to be set.

(32) An alternative way of transmitting the rotary movements of the first ring element 18 to the adjustable blade 15 can be achieved by means of external toothing, which is formed on the axially inner end of the adjusting ring 29. To be specific, the axially inner end of the adjusting ring 29 can form a gearwheel or gearwheel segment, which meshes with corresponding external toothing on a journal of the adjustable blade 15. The journal extends parallel to the central axis of the adjusting ring 29. Other mechanical couplings of the adjusting ring 29 to the adjustable blade 15 are possible. The adjustable blade 15 can likewise form a pivoted blade, as shown in FIG. 1, which is pivoted as a whole. As an alternative, the blade 15 can be a multi-element blade 15 which has at least one adjustable pivoted segment.

(33) As shown in FIG. 1, the converter has a sensor 40 for detecting the angular position between the first and the second ring element 18, 19. The sensor 40 allows closed-loop control of the input power of the pump wheel.

(34) In summary, the converter according to FIG. 1 operates as follows:

(35) To adjust the blading of the pump wheel 11, the actuator 17 is actuated. For this purpose, the pressure chambers 21, 22 are subjected to different pressures, with the result that the first ring element 18 is turned in the circumferential direction relative to the second ring element 19. By means of the rotary motion, the adjusting ring 29 is turned in the circumferential direction, thereby actuating the crank mechanism 30. The crank mechanism 30 converts the rotary motion of the adjusting ring 29 into a superimposed translational/rotary motion, which brings about a tilting motion of the adjustable blade, thus allowing the desired angle of attack of the adjustable blade 15 to be set. The position of the adjustable blade 15 is held by means of the pressure ratios in the actuator 17.

LIST OF REFERENCE SIGNS

(36) 10 working space

(37) 11 pump wheel

(38) 12 drive shaft

(39) 13 turbine wheel

(40) 14 stator

(41) 15 adjustable blade

(42) 16 adjustment device

(43) 17 actuator

(44) 18 first ring element

(45) 19 second ring element

(46) 20 deflection device

(47) 21 pressure chamber

(48) 22 pressure chamber

(49) 23 cylindrical housing

(50) 24 vane

(51) 25 vane

(52) 26 sealing elements

(53) 27 stops

(54) 28 bores

(55) 29 adjusting ring

(56) 30 crank mechanism

(57) 31 lever element

(58) 32 stator housing

(59) 33 first end wall

(60) 34 second end wall

(61) 35 outer ring

(62) 36 inner ring

(63) 37 sleeve

(64) 38 pin

(65) 39 journal

(66) 40 sensor