WO2015071349A2 - Dispositif de transmission de puissance - Google Patents

Dispositif de transmission de puissance Download PDF

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Publication number
WO2015071349A2
WO2015071349A2 PCT/EP2014/074467 EP2014074467W WO2015071349A2 WO 2015071349 A2 WO2015071349 A2 WO 2015071349A2 EP 2014074467 W EP2014074467 W EP 2014074467W WO 2015071349 A2 WO2015071349 A2 WO 2015071349A2
Authority
WO
WIPO (PCT)
Prior art keywords
adjusting
power transmission
planetary gear
ring
transmission device
Prior art date
Application number
PCT/EP2014/074467
Other languages
German (de)
English (en)
Other versions
WO2015071349A3 (fr
Inventor
Reinhard Kernchen
Rainer Schips
Hartmut Graf
Hans Schirle
Bernhard Ludas
Original Assignee
Voith Patent Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE102014213295.9A external-priority patent/DE102014213295A1/de
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Priority to JP2016530890A priority Critical patent/JP6538681B2/ja
Priority to US15/036,853 priority patent/US10113626B2/en
Priority to EP14799138.4A priority patent/EP3069050B1/fr
Priority to CN201480062555.7A priority patent/CN105745475B/zh
Priority to KR1020167012619A priority patent/KR20160084393A/ko
Publication of WO2015071349A2 publication Critical patent/WO2015071349A2/fr
Publication of WO2015071349A3 publication Critical patent/WO2015071349A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
    • F16H47/085—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion with at least two mechanical connections between the hydraulic device and the mechanical transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H41/26—Shape of runner blades or channels with respect to function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/48—Control of exclusively fluid gearing hydrodynamic
    • F16H61/50—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit
    • F16H61/52—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades
    • F16H61/56—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades to change the blade angle

Definitions

  • the invention relates to a power transmission device having the features of the preamble of claim 1.
  • Devices for power transmission to drive a variable-speed machine are already known in different versions of the prior art.
  • the embodiment according to DE 34 41 877 A1 consists of a transmission with planetary gears, wherein the power is transmitted via a mechanical and a hydrodynamic power branch.
  • the hydrodynamic power branch runs via a hydrodynamic converter in the form of a synchronous converter and can be regulated by the converter by adjusting the blading of the stator in its speed.
  • This is reunited with the mechanically transmitted power branch in a planetary gear and thus drives the machine at the desired speed, although the drive unit, which drives the power unit to the input shaft, runs at a constant speed.
  • DE 10 2008 034 607 describes a similar structure, which replaces the hollow shaft by parallel to the central axis of the power transmission unit running coupling shafts.
  • the inventive solution with adjustment of at least individual adjusting vanes and / or adjustable blade segments on the pump and / or turbine wheel offers the advantage of the controllability of the recording power and an increase in the possible operating range of the converter within the power transmission device.
  • the converter of the power transmission device according to the invention may be designed as a synchronous converter according to a first basic embodiment of the power transmission device. In this case, impeller and turbine run in the same direction.
  • the coupling possibilities with the planetary gearing result from the assignment of the individual components as follows:
  • the first element of the planetary gear is the sun gear, the second element of the planetary gear from the ring gear and the third element of the planetary gear
  • Planetary gear formed by the planetary carrier. d)
  • the first element of the planetary gear is formed by the sun gear, the second element of the planetary gear from the planet carrier and the third element of the planetary gear from the ring gear.
  • Planetary gear made of sun gear.
  • the structure in which the ring gear is connected to the output shaft directly or via another gear, preferably a spur gear, and in which the hydrodynamic power branch is registered via the sun gear, has the decisive advantage that the planetary gear due to the low rotational speeds very compact can be executed.
  • the device thus receives a total of a very compact design, which can dispense with a coupling sleeve. He can also dispense with additional stationary transmission in the form of planetary gears and so can be very small, compact with a small number of components and, accordingly, simple and inexpensive in the Manufacture and assembly are performed.
  • the structure may be performed according to an advantageous development with exactly one planetary gear, so that can be dispensed with further relatively complex planetary gear.
  • the turbine of the hydrodynamic counter-rotating converter is connected via a hollow shaft with the sun gear of the planetary gear and extending through the hollow shaft input shaft is connected on the side facing away from the hydrodynamic reverse converter side with the planet carriers.
  • the hollow shaft according to this structure is of comparatively small diameter and not nearly as complex and complex as, for example, the coupling sleeve in the structure according to the prior art.
  • Blade Segments Basically, a distinction can be made between the axial adjustment of the setting blades (in particular parallel to the rotation axis of the impeller and / or turbine wheel) and / or adjustable blade segments and the rotation about a theoretical axis of rotation.
  • the terms "axis of rotation” and “axis of rotation” are to be understood functionally and are not limited to a specific structural design.
  • These realizing components can be used for the axis of rotation of the blades of pins, bolts or be formed other rotationally symmetric components.
  • the components realizing the axis of rotation of the pump wheel and / or of the turbine wheel can be formed by the impeller itself, a component rotatably connected to the impeller in the form of a shaft, hollow shaft or other rotationally symmetric component.
  • the adjusting device comprises an actuator, which is connected via a transmission mechanism with the adjusting blade and / or at least one adjustable blade segment of a multi-membered blade, wherein the adjusting force applied via the actuator is introduced according to one of the following possibilities or a combination of these in the transmission mechanism:
  • the impeller or turbine wheel to a pump or turbine shell.
  • the at least one adjusting blade and / or at least one adjustable blade segment of a multi-membered blade is mounted so as to be displaceable in the axial direction in the blade wheel shell, parallel to the axis of rotation of the pump wheel or turbine wheel.
  • This embodiment offers the advantage of removability of at least some or all blades or blade segments from the working cycle.
  • a second basic variant is characterized in that the pump or turbine wheel comprises a Schaufelradschale and the at least one adjusting blade and / or at least one adjustable blade segment of a multi-membered blade is rotatably mounted about a theoretical axis in the Schaufelradschale.
  • the pump or turbine wheel comprises a Schaufelradschale and the at least one adjusting blade and / or at least one adjustable blade segment of a multi-membered blade is rotatably mounted about a theoretical axis in the Schaufelradschale.
  • These torsion vanes or rotatable blade segments whose angular position relative to a through the extent that can be described in the radial direction can be changed by turning about a defined axis of rotation.
  • the initial position describes a first functional position, each further from this deflected position another functional position.
  • the axis of rotation may according to a particularly advantageous embodiment in the blade plane but also outside this. This type of adjustability offers the advantage of free adjustability of
  • the adjusting device in both basic designs is preferably arranged outside the working space and in the axial direction next to the respective impeller - impeller and / or turbine wheel. This offers the advantage of easy accessibility and, in particular in the case of a countercurrent converter and hydraulic generation of the actuating force, a simple connection to a pressure sink / pressure source with regard to the type of generation of the required actuating force.
  • the actuator is executed in a development as an actuator or a combination of the following group of actuators:
  • an adjusting device with introduction of the adjusting force in the circumferential direction about the axis of rotation of the actuator ring elements, which are each arranged coaxially to the axis of rotation of the impeller, wherein a first ring element with the at least one adjusting blade and / or the at least one adjustable blade segment for Transmission of a force or a parking torque is connected by the transmission mechanism and the first ring member is rotatable relative to a second ring member in the circumferential direction of the drive shaft.
  • the first and second ring element form in a particularly advantageous manner at least two arranged in the circumferential direction of the drive shaft pressure chambers, which are each acted upon by pressure for the relative rotation between the first and second ring member.
  • the transmission mechanism in this case preferably has an adjusting ring, which is arranged coaxially to the drive shaft and non-rotatably connected to the first ring element, wherein the adjusting ring is coupled to the at least one adjusting blade and / or adjustable blade segment for transmitting a restoring force or a setting torque.
  • the adjusting ring can be designed according to one of the following possibilities:
  • the adjusting ring has at least one cam, which cooperates with a crank mechanism, in particular a radially arranged lever element, wherein the crank mechanism is coupled to the adjusting blade -
  • the adjusting ring has an outer toothing, which meshes with the external toothing of a pin of the adjusting blade, which extends parallel to the central axis of the adjusting ring.
  • the actuator has at least one movable in the axial direction of adjusting piston, which are arranged coaxially or eccentrically to the axis of rotation of the impeller, wherein the actuating piston with the at least one Adjusting bucket and / or the at least one adjustable blade segment for transmitting a force or a setting torque is connected by the transmission mechanism and relative to the impeller in the axial direction is displaceable.
  • the transmission mechanism can be formed, for example, by an adjusting ring coupled to the adjusting piston or in one piece.
  • the individual adjusting blades and / or adjustable blade segments are controlled by these measures either individually and / or in groups and / or together.
  • the latter option offers the advantage of a relatively small constructive and control technical effort, while the former possibility allows a very accurate and sensitive adjustment.
  • devices for controlling for example, valve devices are conceivable.
  • the stator can be designed to be adjustable, in particular adjusting blades or at least comprise an adjustable blade segment.
  • the power transmission device is particularly for use in drive trains between a prime mover, which is operable at a constant speed, in particular electric motor or turbine (eg gas or steam turbine) and a variable-speed machine can be used, as by the adjustability of the arrangement in an optimal manner to the requirements
  • a prime mover which is operable at a constant speed, in particular electric motor or turbine (eg gas or steam turbine) and a variable-speed machine can be used, as by the adjustability of the arrangement in an optimal manner to the requirements
  • This application is customizable.
  • a particularly advantageous and described below embodiment of an adjusting or adjusting device with introduction of the adjusting force parallel to the axis of rotation of the impeller has a sleeve, a manifestenzyl inder and an axially movable sliding element, which are each arranged coaxially to the drive shaft.
  • the sliding element connects the sleeve and the outer cylinder such that the sleeve can be rotated by an axial movement of the sliding element relative to the outer cylinder in the circumferential direction of the drive shaft.
  • the sleeve is connected to the at least one adjusting blade for transmitting a setting force or a setting torque, in particular by a deflection device.
  • a sleeve, a Outer cylinder and a sliding element are provided, which form the adjusting device.
  • the sleeve and the outer cylinder are rotatable relative to each other in the circumferential direction of the drive shaft.
  • the sliding element Upon activation of the adjusting device, the sliding element performs a superimposed translational / rotational movement.
  • the translational movement of the sliding element represents an axial displacement of the sliding element along the drive shaft, wherein the sliding element simultaneously rotates about this.
  • the relative rotation between the sleeve and the outer cylinder is generated.
  • the sleeve is coupled by the deflection with the adjusting blade.
  • the actuating torque generated by the relative rotation of the sleeve relative to the outer cylinder or the actuating force is introduced by the deflecting device in the adjusting blade and brings them to the desired setting position.
  • the sliding element means for applying a force wherein the respective connection between the sliding element and the outer cylinder and the sliding element and the sleeve is formed and arranged to superimpose the effects of the compounds during transmission of a force, wherein the individual connection between the sliding element and the outer cylinder and / or sliding element and sleeve takes place in each case directly or via further intermediate elements.
  • the connection between the sliding element and the outer cylinder and the connection between the sliding element and the sleeve is in each case formed as a toothing, in particular a thread.
  • a first variant of the compounds is in each case one of the compounds of the sliding element with the connection components - the connection between the sliding element and outer cylinder or the connection between the sliding element and sleeve - designed as a thread and the other connection - connection between the sliding element and sleeve or connection between Sliding element and Au JOzyl inder - as a straight toothing with an orientation of the tooth flanks parallel to the axis of rotation of the transducer.
  • one of the compounds of the sliding element with the connection components - the connection between the sliding element and outer cylinder or the connection between the sliding element and sleeve - is designed as a thread and the other connection - connection between the sliding element and sleeve or connection between Sliding element and outer cylinder - as helical gearing with an orientation of the tooth flanks at an angle to the axis of rotation of the transducer.
  • thread and helical toothing are characterized by a common directional component.
  • the design as helical gearing is particularly easy to produce.
  • the sleeve and the outer cylinder form two pressure chambers arranged in the axial direction of the drive shaft, which are separated from one another by the sliding element and each can be pressurized such that the sliding element is axially displaceable along the drive shaft.
  • the actuation of the sliding element is hydraulically, in particular hydraulically in both axial directions of the sliding element.
  • mechanical Stellgl ieder, such as. Return springs are avoided.
  • the provision or generally the change in position of the sliding element is hydraulically.
  • the sliding element can be generally understood as an axially displaceable annular piston whose stroke acts axially along the drive shaft.
  • a simple and robust design is provided, with which the hydraulically generated axial movement of the sliding element introduces a restoring force or a setting torque in the sleeve, so that the sleeve rotates relative to the drive shaft.
  • the coupling element comprises an internal thread of the outer cylinder, with an external thread of the sliding element in Intervention is.
  • the internal thread can be understood as a nut thread.
  • the coupling element may comprise an outer thread of the sleeve, which is in engagement with an internal thread of the sliding element.
  • a translational displacement of the sliding element relative to the sleeve is made possible, wherein the sleeve is rotated by the thread relative to the sliding element or to the drive shaft.
  • Other coupling elements are conceivable, with which the rotational movement of the sleeve with the translational movement of the sliding element can be coupled.
  • the sliding element has a toothing which is in engagement with a complementary toothing of the sleeve or of the outer cylinder.
  • the external toothing of the sleeve is straight teeth or helical teeth.
  • the helical design leads to an increase in the angle of rotation, since the pitch of the toothing and the pitch of the thread are added.
  • Both versions are particularly suitable for the nut thread of the outer cylinder.
  • This complementary toothing may generally comprise a single tooth which is fixedly connected to the sleeve or the outer cylinder and engages in a corresponding guide groove in the sliding element. This guide groove of the sliding element transmits both the rotary drive movement of the drive shaft, as well as during the adjustment, the relative displacement of the sliding element.
  • the individual tooth can thus be guided during the axial displacement of the sliding element and, at the same time, the adjusting force or the adjusting torque can be transmitted to the sleeve in every position of the sliding element.
  • the teeth may comprise a plurality of teeth, for example a sprocket segment or a complete sprocket.
  • the toothing in the engaged components is designed to be complementary.
  • the single tooth can be arranged on the sliding element and engage in a guide groove in the sleeve or the outer cylinder.
  • the teeth may comprise a plurality of teeth, for example a sprocket segment or a complete sprocket.
  • the toothing in the engaged components is designed to be complementary.
  • the guide groove extends parallel to the central axis of the drive shaft. In the helical version, the guide is adapted accordingly.
  • the outer cylinder can form a cylindrical housing in which the sliding element and the sleeve are arranged.
  • the outer cylinder represents - seen from the drive shaft - the outer boundary of the pressure chambers.
  • the inside of the pressure chambers can be limited both by the drive shaft itself and by the shell.
  • both pressure chambers each form a radially symmetrical pressure chamber, wherein these are arranged coaxially to the drive shaft.
  • the two pressure chambers are separated from each other by the sliding in the axial direction sliding element, so that pressure chambers are formed with variable volume.
  • the sliding element in each case forms an end face of the two radially symmetrical pressure chambers.
  • the respective opposite end face of the two pressure chambers is formed by the redesignenzyl inder.
  • the sliding element By acting on the pressure chambers at different pressures, the sliding element can be displaced axially in both directions along the drive shaft.
  • the axial displacement of the sliding element causes by the coupling element between the outer cylinder and the sliding element an additional rotational movement of the sliding element relative to the outer cylinder. This relative movement in the circumferential direction to the drive shaft ermögl icht through the teeth between the sliding element and sleeve adjustment of the adjusting blade in different directions.
  • the sliding element and / or the outer cylinder and / or the sleeve may have radially arranged sealing elements for sealing the pressure chambers.
  • bores are preferably further formed in the adjusting device according to the second alternative embodiment, in particular in the outer cylinder, which open for pressurization in the pressure chambers, in particular in the region of the outer diameter.
  • Training the holes in the outer cylinder has the advantage that the supply channels may be formed in the drive shaft, which are fluidly connected to the bores formed in the outer cylinder.
  • the mouth of the bores in the region of the outer diameter of the pressure chambers has the advantage that this rinsing of the pressure chambers is achieved. Any adhering to the outer diameter impurities that accumulate during operation there are solved or avoided by the introduction of the working medium in the range of the outer diameter.
  • the formation of the feed channels in the drive shaft can, for example, be done by a rotary feedthrough.
  • the rotary feedthrough can be, for example, a hydraulic sleeve in which channels are formed, ie, which are fluid-connected to the bores in the outer cylinder.
  • the hydraulic sleeve is rotatably connected to the drive shaft.
  • the deflection device has an adjusting ring, which is arranged coaxially to the drive shaft and rotatably connected to the sleeve.
  • the adjusting ring is coupled to the at least one adjusting blade for transmitting a control force or a setting torque.
  • the adjusting ring contributes to the compact design of the converter, since this, like the adjusting device, is arranged coaxially to the drive shaft. Due to the rotationally fixed connection of the adjusting ring with the sleeve any mechanical coupling components are avoided. Rather, the adjusting torque required for the adjustment of the adjusting blade is introduced directly from the sleeve into the adjusting ring.
  • the rotationally fixed connection between the adjusting ring and the sleeve can be achieved for example by a material connection such as a welded joint, or by positive or non-positive connections.
  • the coupling of the adjusting ring with the adjusting blade can be effected in a further embodiment in that the adjusting ring Has at least one cam or at least one driver, in particular a rad ial arranged lever element and / or crank mechanism, cooperates.
  • the lever element and / or the crank mechanism is coupled to the adjusting blade.
  • the control of the adjusting blade by a crank mechanism is known per se, so that in this regard can be made of existing designs.
  • the formation of the cam or driver on the adjusting ring has the advantage over the prior art that no separate mechanical components are required for the introduction of force into the crank mechanism. Rather, the crank mechanism is operated directly by the driver.
  • the crank mechanism forms a radially arranged lever element, which converts the rotational movement of the adjusting ring in a superimposed translational / rotational movement.
  • the lever element By the coupling of the lever element with the adjusting blade, the adjusting movement is achieved in a conventional manner.
  • the adjusting ring has an outer toothing, which meshes with the outer toothing of a pin of the adjusting blade.
  • the pin extends parallel to the central axis of the adjusting ring.
  • the adjusting blade may comprise a rotating blade or a multi-membered blade with at least one twisting segment.
  • Rotary blades and multi-membered blades are known per se, wherein a rotating blade means a one-piece adjusting blade, which is adjustable as a whole.
  • a blade segment is fixed. At least one other blade segment is rotatable.
  • the drive for the rotatable blade segment is effected by the adjusting device.
  • the preferred embodiment according to which a sensor for detecting the angular position between the sleeve and the Jardinenzyl indians is provided, is particularly suitable for systems in which the receiving power is controlled. For this purpose, the angle signal output by the sensor is used.
  • the adjusting device comprises an axially movable sliding element, a sleeve and an outer cylinder with concentric arrangement.
  • the sleeve is at least connected to a control blade of the transducer for transmitting a restoring force or an actuating torque, in particular by a deflecting device.
  • the sleeve is rotatable by an axial movement of the sliding element relative to the outer cylinder in the circumferential direction of the drive shaft.
  • FIG. 1 shows by way of example a first basic embodiment of a
  • FIG. 2 shows by way of example a second basic embodiment of a
  • FIGS. 5a and 5b show, by way of example, different views of one
  • Power transmission device 1 for transmitting power from an input shaft E connected at least indirectly to a drive assembly 31 to an output shaft A at least indirectly connected to a driven machine 32, according to a first and second basic design in an advantageous embodiment with adjustability of the impeller blades. At least indirectly means either directly or via other intermediate components, which may also include facilities for speed / torque conversion.
  • the arrangement of the adjusting device 15 preferably takes place outside of the working space formed by the paddle wheels 9, 10, 1 1 and viewed in the axial direction next to the impeller 9.
  • adjusting devices 15 there are a variety of ways. These can be carried out in various ways and differ with respect to the implementation of a plurality of sub-functions, including the type of generation of the adjusting force, the direction of introduction for the adjustment, the type of adjustment of the individual adjusting vane or the adjustable blade segment and the Type of bucket control belong. These possibilities are shown by way of example in a table in FIG. It can with regard to the type of control in central control, ie adjustment of all adjusting blades and / or adjustable blade segments or but the individual or group control of the adjusting blades and / or adjustable blade segments are distinguished.
  • a further embodiment according to the first basic type consists in the formation of at least one individual blade with deformable regions.
  • a second basic type consists in the axial displaceability of individual adjusting blades 13 or blade segments 14, i. the displaceability of the effective range of the individual blades out of the working cycle, preferably parallel to the axis of rotation R of the impeller.
  • the position of the impeller 9 is fixed in the vane space.
  • the adjustability of one or more blades or blade areas is variable.
  • the shaft end on the drive side is accessible and on the output side only conditionally.
  • FIG. 4a illustrates the axial introduction of the adjusting force F, ie parallel in the direction of the rotational axis R of the impeller 9.
  • the adjusting force F is transmitted to the blade 13 via at least one transmission mechanism 19 of the adjusting device 15 for realizing a change of direction of the force.
  • the transmission mechanism 17 can be coupled directly or via further intermediate elements either with a component describing the rotational axis RS of the blade 13 or a blade region eccentrically with respect to the latter in order to generate a torque about the rotational axis RS.
  • FIG. 4b schematically shows in simplified form the rotational introduction of the adjusting force F, i. in the circumferential direction about the axis of rotation R of the impeller 9.
  • Figures 5 and 6 illustrate advantageous structural embodiments of possible adjusting devices 15 for rotating vanes, in which case all blades of the blading of a pump wheel 9 are preferably adjusted in the same way. The adjustment of all coupled with the adjusting device 15 adjusting blades is carried out at the same time by the same angle of rotation.
  • the actuator 17 according to FIG. 5a is formed by an annular piston.
  • This has ring elements 20 and 21, which are each arranged coaxially to the axis of rotation R of the impeller 9, wherein a first ring member 21 with the at least one adjusting blade 13 and / or the at least one adjustable Blade segment 14 is connected to transmit a restoring force or a setting torque by the transmission mechanism 19 and the first ring member 21 is rotatable relative to a second ring member 20 in the circumferential direction of the drive shaft.
  • the first and second ring element 20, 21 form at least two pressure chambers 22 which are arranged in the circumferential direction of the drive shaft and can each be subjected to pressure for the relative rotation between the first and second ring elements 20, 21.
  • FIG. 6a shows, in an axial section, a design with axial adjustment force introduction into the transmission mechanism 19.
  • the actuator comprises at least one adjusting piston 28, which can be displaced in the axial direction and which is coaxial or eccentric to the axis of rotation R of FIG Impeller 9 are arranged, wherein the adjusting piston 28 is connected to the at least one adjusting blade 13 and / or the at least one adjustable blade segment 14 for transmitting a force or a setting torque by the transmission mechanism 19 and relative to the pump 9 in the axial direction is displaceable.
  • the transmission mechanism comprises an adjusting ring 23 which engages via a thread with a thread of the adjusting piston 28, wherein an axial movement of the adjusting piston 28 is converted into a rotational movement on the adjusting ring 23.
  • the adjusting ring 23 in the remote from the actuating piston 28 end portion with the adjusting blade 13, in particular a the axis of rotation RS descriptive and the adjusting blade 13 supporting element, for example, a crank mechanism 49 is coupled.
  • the converter 2 shown in Figure 6a has a working space, which can be flowed through by an operating medium.
  • the transducer 2 has an impeller 9, which is connected to a drive shaft 1 8 and an input shaft E, and a turbine wheel 1 0, which is connected to an output shaft (not shown).
  • the turbine wheel 1 0 is mounted relatively rotatably on the drive shaft 1 8.
  • the stator housing 29 is arranged stationarily with the stator 1 1.
  • the Leitradgepur 29 together with the housing of the turbine wheel 1 0 and with the housing of the pump 9 a cup-shaped enclosed working space in which forms during operation of the flow circuit.
  • the impeller 9 has at least one adjusting blade 1 3.
  • the other pump blades of the impeller 9 can also be designed as adjusting blades 1 3 accordingly. Alternatively, the remaining pump blades may be rigid.
  • the adjusting blade 1 3 is associated with an adjusting device 1 5, which co-rotates with the impeller 9 during operation of the converter 2.
  • the adjusting device 1 5 has a deflecting device 33 and a, the adjusting piston corresponding sleeve 28, a sliding element 34 and an outer cylinder 35.
  • the deflecting device 33 couples the sleeve 28, the sliding member 34 and the outer cylinder 35 with the adjusting blade 1 3.
  • the sleeve 28, the sliding member 34 and the outer cylinder 35 are each coaxial with the drive shaft 1 8.
  • the housing has an outer ring 38 which limits the housing in the radial direction and which is arranged between the two end walls 36, 37.
  • the counterpart to the outer ring 38 forms the inner ring of the sleeve 28.
  • the two end walls 36, 37 engage over the outer ring 38 and inner ring so that between the outer cylinder 35 and the sleeve 28, two annular spaces 41, 42 are formed.
  • the annular spaces 41, 42 are arranged axially one behind the other and separated by the sliding element 34 pressure-tight from each other.
  • the annular spaces 41, 42 act as a displacement.
  • the first end wall 36 forms a sealing surface to the outer periphery of the drive shaft 1 eighth
  • a bolt 50 is attached to the lower end of the crank mechanism 49.
  • the axis of rotation of the bolt 50 extends parallel to the central axis of the drive shaft 1 8.
  • the upper end of the crank mechanism 49 engages the adjusting blade 1 3, specifically on an eccentrically arranged pin of the adjusting blade 1 3, which protrudes axially from the housing of the impeller 9.
  • the driver forms together with the bolt a swivel k, by which the crank mechanism 49 is pivotable.
  • the pivoting movement takes place in the circumferential direction of the drive shaft 1 8.
  • the driver acts as a sliding bearing in which the bolt is rotatably mounted.
  • adjusting torque is transmitted to the crank mechanism 49 via the bolt which is supported in the driver of the adjusting ring 23.
  • the crank mechanism 49 converts the rotational movement of the adjusting ring 23 in a superimposed translational / rotational movement of the crank mechanism 49, which causes a tilting movement of the adjusting blade 1 3, so that the desired angle of attack of the adjusting blade 1 3 can be adjusted.
  • An alternative transmission of the rotational movements of the sleeve 28 on the adjusting blade 1 3 can be done by an external toothing, which is formed at the axially inner end of the adjusting ring 23.
  • the axially inner end of the adjusting ring 23 form a gear or gear segment, which meshes with a corresponding external toothing of a pin of the adjusting blade 1 3.
  • the pin extends parallel to the central axis of the adjusting ring 23.
  • Other mechanical couplings of the adjusting ring 23 with the adjusting blade 1 3 are possible.
  • the adjusting blade 1 3 form a Verdandschaufel, as shown in Figure 6a, which is rotated as a whole.
  • the blade 1 3 may be a multi-membered blade 1 3, which has at least one adjustable torsion segment.
  • the converter according to Figure 1 operates as follows: To adjust the blading of the impeller 9, the adjusting device 1 5 is actuated. For this purpose, the pressure chambers 41, 42 are acted upon by different pressures, so that the sliding element 34 is axially displaced along the drive shaft 1 8 and rotated by the internal thread 40. Since the sliding element 34 is toothed with the sleeve 28, the sleeve 28 is relative to the outer cylinder 35 in the circumferential direction mechanically, or if the actuation of the sliding element 34 is taken into account, indirectly hydraulically twisted. By the rotational movement of the sleeve 28 of the adjusting ring 23 is rotated in the circumferential direction, whereby the crank mechanism 49 is actuated.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Retarders (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne un dispositif de transmission de puissance présentant un convertisseur hydrodynamique. Selon l'invention, l'aubage (12) de la roue de pompe (9) et/ou de la roue de turbine (10) présente au moins une aube réglable (13) pouvant être actionnée via un dispositif de réglage (15) et/ou au moins une aube à plusieurs éléments présentant au moins un segment d'aube réglable (14).
PCT/EP2014/074467 2013-11-14 2014-11-13 Dispositif de transmission de puissance WO2015071349A2 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2016530890A JP6538681B2 (ja) 2013-11-14 2014-11-13 動力伝達装置
US15/036,853 US10113626B2 (en) 2013-11-14 2014-11-13 Power transmission device
EP14799138.4A EP3069050B1 (fr) 2013-11-14 2014-11-13 Dispositif de transmission de puissance
CN201480062555.7A CN105745475B (zh) 2013-11-14 2014-11-13 功率传输装置
KR1020167012619A KR20160084393A (ko) 2013-11-14 2014-11-13 동력 전달 장치

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE102013223213 2013-11-14
DE102013223213.6 2013-11-14
DE102014213295.9 2014-07-09
DE102014213295.9A DE102014213295A1 (de) 2013-11-14 2014-07-09 Hydrodynamischer Wandler und Verstelleinrichtung für einen solchen Wandler
DE102014216066.9A DE102014216066A1 (de) 2013-11-14 2014-08-13 Leistungsübertragungsvorrichtung
DE102014216066.9 2014-08-13

Publications (2)

Publication Number Publication Date
WO2015071349A2 true WO2015071349A2 (fr) 2015-05-21
WO2015071349A3 WO2015071349A3 (fr) 2015-07-23

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015226638A1 (de) * 2015-12-23 2017-06-29 Voith Patent Gmbh Hydrodynamischer Wandler
DE102015226640A1 (de) * 2015-12-23 2017-06-29 Voith Patent Gmbh Unterwasser-Antriebseinheit
CN107504151A (zh) * 2017-10-12 2017-12-22 中国船舶重工集团公司第七0三研究所 一种功率多分支液力行星调速装置
CN107504150A (zh) * 2017-10-12 2017-12-22 中国船舶重工集团公司第七0三研究所 一种新型液力行星调速机构
DE102017101339A1 (de) 2017-01-25 2018-07-26 Voith Patent Gmbh Verfahren zum Betreiben eines Antriebsstranges zum drehzahlvariablen Antreiben einer Arbeitsmaschine und Antriebsstrang
DE102017114063A1 (de) 2017-06-26 2018-12-27 Voith Patent Gmbh Leistungsübertragungsvorrichtung und Verfahren zum Betreiben einer Leistungsübertragungsvorrichtung in einem Antriebsstrang zum drehzahlvariablen Antreiben einer Arbeitsmaschine
CN112576724A (zh) * 2021-01-08 2021-03-30 吉林大学 一种带有仿生缝隙的能容可调式液力变矩器
DE102020124864A1 (de) 2020-09-24 2022-03-24 Voith Patent Gmbh Monitoring von regelbaren Getrieben
WO2024056270A1 (fr) * 2022-09-14 2024-03-21 Voith Patent Gmbh Dispositif de transmission de puissance comprenant un convertisseur hydrodynamique à détection de point synchrone, et procédé de fonctionnement de ce dernier

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US2368279A (en) * 1942-10-05 1945-01-30 Ernest E Wemp Torque converter
US2640680A (en) * 1948-09-02 1953-06-02 Kenneth G Altheide Variable pitch hydraulic transmission
US2964976A (en) * 1956-12-10 1960-12-20 Gen Motors Corp Transmission
US2909034A (en) * 1957-05-13 1959-10-20 Ford Motor Co Hydrokinetic torque converter with adjustable reactor blades
US3073182A (en) * 1959-06-10 1963-01-15 Gen Motors Corp Transmission
US3151457A (en) * 1963-04-11 1964-10-06 Ford Motor Co Hydrokinetic torque transmitting mechanism
US3263522A (en) * 1963-10-02 1966-08-02 Ford Motor Co Dual range torque converter transmission
JPS5247168A (en) * 1975-10-13 1977-04-14 Komatsu Ltd Speed change gear
FR2662483A2 (fr) * 1990-02-28 1991-11-29 Antonov Roumen Dispositif de transmission a rapport variable en particulier pour l'automobile.
GB9620063D0 (en) * 1996-09-26 1996-11-13 Haidar Haidar M Variable speed transmission

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015226640A1 (de) * 2015-12-23 2017-06-29 Voith Patent Gmbh Unterwasser-Antriebseinheit
DE102015226638A1 (de) * 2015-12-23 2017-06-29 Voith Patent Gmbh Hydrodynamischer Wandler
US10876612B2 (en) 2017-01-25 2020-12-29 Voith Patent Gmbh Method for operating a drive train for driving a working machine with variable rotation speed and drive train
DE102017101339A1 (de) 2017-01-25 2018-07-26 Voith Patent Gmbh Verfahren zum Betreiben eines Antriebsstranges zum drehzahlvariablen Antreiben einer Arbeitsmaschine und Antriebsstrang
WO2018137916A1 (fr) 2017-01-25 2018-08-02 Voith Patent Gmbh Procédé pour faire fonctionner une chaîne cinématique servant à l'entraînement à vitesse variable d'une machine de travail, et chaîne cinématique
WO2019001953A1 (fr) 2017-06-26 2019-01-03 Voith Patent Gmbh Dispositif de transmission de puissance et procédé permettant de faire fonctionner un dispositif de transmission de puissance dans une chaîne cinématique pour l'entraînement d'une machine de travail à une vitesse de rotation variable
DE102017114063A1 (de) 2017-06-26 2018-12-27 Voith Patent Gmbh Leistungsübertragungsvorrichtung und Verfahren zum Betreiben einer Leistungsübertragungsvorrichtung in einem Antriebsstrang zum drehzahlvariablen Antreiben einer Arbeitsmaschine
CN107504150A (zh) * 2017-10-12 2017-12-22 中国船舶重工集团公司第七0三研究所 一种新型液力行星调速机构
CN107504151A (zh) * 2017-10-12 2017-12-22 中国船舶重工集团公司第七0三研究所 一种功率多分支液力行星调速装置
CN107504151B (zh) * 2017-10-12 2024-04-26 中国船舶重工集团公司第七0三研究所 一种功率多分支液力行星调速装置
DE102020124864A1 (de) 2020-09-24 2022-03-24 Voith Patent Gmbh Monitoring von regelbaren Getrieben
CN112576724A (zh) * 2021-01-08 2021-03-30 吉林大学 一种带有仿生缝隙的能容可调式液力变矩器
CN112576724B (zh) * 2021-01-08 2022-03-18 吉林大学 一种带有仿生缝隙的能容可调式液力变矩器
WO2024056270A1 (fr) * 2022-09-14 2024-03-21 Voith Patent Gmbh Dispositif de transmission de puissance comprenant un convertisseur hydrodynamique à détection de point synchrone, et procédé de fonctionnement de ce dernier

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