US20140050565A1 - Hydrodynamic component - Google Patents

Hydrodynamic component Download PDF

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Publication number
US20140050565A1
US20140050565A1 US13/983,284 US201213983284A US2014050565A1 US 20140050565 A1 US20140050565 A1 US 20140050565A1 US 201213983284 A US201213983284 A US 201213983284A US 2014050565 A1 US2014050565 A1 US 2014050565A1
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US
United States
Prior art keywords
shaft
magnetic field
component according
hydrodynamic component
hydrodynamic
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US13/983,284
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English (en)
Inventor
Markus Schlosser
Thursten Luhrs
Achim Menne
Dieter Laukmann
Ravi Schade
Bruno Foehl
Jürgen Kibler
Christian Ebert
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Voith Patent GmbH
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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
Application filed by Voith Patent GmbH filed Critical Voith Patent GmbH
Assigned to VOITH PATENT GMBH reassignment VOITH PATENT GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EBERT, CHRISTIAN, FOEHL, BRUNO, KIBLER, JURGEN, MENNE, ACHIM, SCHADE, RAVI, SCHLOSSER, MARKUS, LAUKEMANN, DIETER, LUHRS, THORSTEN
Publication of US20140050565A1 publication Critical patent/US20140050565A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/003—Arrangements for testing or measuring
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/18—Details
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D57/00—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
    • F16D57/04—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders with blades causing a directed flow, e.g. Föttinger type
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • 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
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/02—Rotary-transmission dynamometers
    • G01L3/04—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft
    • G01L3/10—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving electric or magnetic means for indicating
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/02—Rotary-transmission dynamometers
    • G01L3/04—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft
    • G01L3/10—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving electric or magnetic means for indicating
    • G01L3/101—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving electric or magnetic means for indicating involving magnetic or electromagnetic means
    • G01L3/102—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving electric or magnetic means for indicating involving magnetic or electromagnetic means involving magnetostrictive means
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/003—Position, angle or speed
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/005—Force, torque, stress or strain
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/18—Sensors; Details or arrangements thereof

Definitions

  • the invention relates to a hydrodynamic component having the features defined in detail in the preamble of claim 1 .
  • a generic hydrodynamic component is described in the German Patent Specification DE 10 2005 052 105 B4.
  • This patent is concerned with a hydrodynamic system which is configured with a device for detecting a torque or a variable characterizing this torque.
  • the structure is comparatively expensive since one of the two elements of the hydrodynamic system must be supported with respect to a positionally fixed element and the forces required for the support must be measured in the region of this support.
  • a comparatively high constructive expenditure must be accepted for this and in particular a rotational movement of the supporting element must be possible, which for example in the case of a hydrodynamic retarder causes a correspondingly high expenditure.
  • the supporting element must be in a non-rotating state since the measurement is only possible here. In the case of a hydrodynamic converter or a hydrodynamic coupling, this is correspondingly expensive or in some cases not even possible.
  • the solution of the object mentioned initially consists in that the shaft is formed at least in at least two sections which are at an axial distance from each other and which are made of a ferromagnetic material and is provided with a magnetic field configured to be rotationally fixed with the respective section. Magnetic field sensors are then arranged in areas corresponding to the at least two sections, for example, on a housing surrounding the shaft.
  • This structure allows a change in the magnetic fields in the respective sections to be detected by means of the physical effect of magnetostriction or the Joule effect having the most important component in the magnetostriction.
  • a slight twist of the magnetic field in the first section in the direction of the shaft can be detected with respect to the magnetic field in the second section.
  • the measurement always allows the rotational speed of the shaft to be determined when the magnetic field disposed in a rotationally fixed manner to one of the sections has a constant inhomogeneity in the circumferential direction.
  • Such an inhomogeneity can be achieved, for example, by a material variation, a mechanical variation of the material or a magnetic field coded accordingly in the circumferential direction, with which the shaft is provided.
  • the rotational speed of the shaft can also be detected.
  • both the rotational speed and the torque in the shaft are detected with a correspondingly high measurement frequency so that the rotational speed and/or torque are available quasi-continuously.
  • the measurement of the torque is in particular of interest here for a hydrodynamic retarder or a hydrodynamic coupling as a hydrodynamic component since the transmitted torque can be detected here by means of a suitable sensor system in one of the shafts.
  • it is also feasible in a hydrodynamic converter where as a result of the supporting moment of the vanes between the primary wheel and the secondary wheel, either the torque both of the input shaft and of the output shaft must be detected or in addition to the torque in one of the shafts, the supporting moment of the vanes in order to determine the torque transmitted by the component.
  • the magnetic fields disposed in a rotationally fixed manner to the respective section of the shaft can in principle be constructed in any manner provided that they are configured to be rotationally fixed and constant at least during a certain time interval for the measurement.
  • the magnetic fields or at least one of the magnetic fields according to a particularly favourable and advantageous embodiment of the hydrodynamic component according to the invention can be configured as a permanent magnetic field.
  • the shaft can accordingly be magnetized once, for example, prior to assembly or the expenditure for the structures required to build up the magnetic field in the region of the shaft is eliminated.
  • the magnetic field sensors are configured to be contact-free with respect to the shaft. As a result, the measurement of the torque and/or the rotational speed can be made without friction losses.
  • the shaft is configured as a hollow shaft, wherein at least one of the magnetic field sensors is disposed in the interior of the hollow shaft.
  • At least one of the magnetic field sensors is disposed in the region of a sealing element surrounding the shaft.
  • at least one sealing element is required in any case in order to seal with respect to the surroundings the working fluid located at high pressure in the working chamber between the elements, for example, the primary wheel and the secondary wheel during the transmission of torque.
  • Such a sealing element surrounding the shaft is ideally suitable for integrating the magnetic field sensor, which for example can be a coil surrounding the shaft, in this sealing element and thus providing a hydrodynamic component having corresponding sensors according to the invention in a neutral manner in terms of installation space with suitable magnetizations of at least two axially spaced-apart sections of the shaft and arrangement of the magnetic field sensors in the region of the sealing element around the shaft.
  • At least one of the magnetic field sensors can be disposed in a shaft sealing ring surrounding the shaft.
  • Such shaft sealing rings typically have a configuration in any case which allows sufficient space for the integration of a coil as a magnetic sensor. They are typically very readily accessible and connected to corresponding regions of the housing so that a lead can be guided from the region of the coil integrated in the shaft sealing ring, for example, to the outside of the housing to an electronic system or the like simply and without any problems.
  • At least one of the magnetic field sensors is disposed between the shaft sealing rings surrounding the shaft.
  • this region between two shaft sealing rings of a multistage seal of the shaft or the working chamber surrounding the shaft it is possible to dispose one or two magnetic field sensors between these shaft sealing rings. This has the advantage that abrasion from the working chamber will not enter into such a region to any extent and that contamination of the magnetic field sensors can thereby be largely avoided.
  • a shaft seal comprises at least one shaft sealing ring and a piston ring connected via a support element to the shaft sealing ring.
  • at least one of the magnetic field sensors can be disposed on the support element.
  • This structure with a piston ring placed between working chamber and first sealing chamber allows a reduction of the pressure in the first sealing chamber compared with the pressure in the working chamber to, for example, about 20% of the pressure in the working chamber.
  • the piston ring is frequently connected to a shaft sealing ring via a support element which ensures the sealing of the first sealing chamber with respect to the surroundings or optionally also with respect to a further second seating chamber.
  • Such a support is ideally suitable for carrying the magnetic field sensor since this is typically formed from a sheet metal sleeve which appropriately surrounds the shaft.
  • this support element With sufficient axial length of this support element it is also very readily possible to place the magnetic field sensors corresponding to the two axially spaced-apart sections of the shaft, both at a certain axial distance from one another on the support element in order to thus ensure simply and efficiently a possibility for integration of the sensors.
  • the shaft in the region of one of the sections, is configured at one or more locations distributed around the circumference of the shaft such that A mechanical loading of the shaft causes a stress gradient.
  • the Joule effect in this case results in a variation of the magnetic field accompanying the position of this location. If one or more locations distributed over the circumference are provided in the region of one of the sections which cause such a variation in the magnetic field, this then results in the possibility of measuring the rotational speed without the magnetic fields needing to be provided specially for a rotational speed measurement, since a characteristic variation of the magnetic field caused by the location with the stress gradient is detected once or several times per revolution depending on the number of locations. A rotational speed signal can be derived very simply from this.
  • the locations are configured as stress-relief or runoff holes for a lubricant from a region between two seating elements of the shaft.
  • stress-relief holes can be provided, for example, in the region between two shaft seals or in the region between a piston ring and a shaft sealing ring, i.e. in a sealing region adjacent to the working chamber in order to remove lubricant accordingly at lower pressure, for example, through a central hole running inside the shaft.
  • stress-relief holes cause a stress gradient so that without additional expenditure on production technology and with the particular side effect of having already integrated one or more stress relief holes, a rotational speed measurement can be achieved simply and efficiently by means of the inhomogeneous magnetic field over the circumference which rotates with the shaft in the respective section.
  • the configuration of the hydrodynamic component according to the invention can be a converter or a hydrodynamic coupling.
  • the component can also be a hydrodynamic retarder.
  • This retarder can be constructed correspondingly simply since in contrast to structures in the prior art, the stator can be configured to be integrated directly in the housing since the torque can be detected in the region of the shaft and no rotational movement of the stator around its axis is required for this.
  • a sensor system can be integrated with minimal expenditure and minimal installation space into the corresponding retarder which can be implemented very simply, efficiently and in a space-saving manner, it allows both the torque and the rotational speed to be measured and therefore everything for controlling the retarder or for controlling a braking system comprising the retarder as one of the possibilities for braking.
  • the sensors constructed according to the principle of magnetostriction can be used under numerous conditions since the magnetic field sensors are correspondingly simple and can be configured to be very resistant to temperature, environmental influences and the like. For example, they can be used in the region of the lubricating oil or working medium and can in particular be operated securely and reliably at correspondingly high ambient temperatures.
  • FIG. 1 shows a schematic diagram of a hydrodynamic retarder
  • FIG. 2 shows a structure for measuring the torque and/or the rotational speed on the shaft of the retarder according to FIG. 1 ;
  • FIG. 3 shows a first possible embodiment for the arrangement of the magnetic field sensors
  • FIG. 4 shows a second possible embodiment for the arrangement of the magnetic field sensors
  • FIG. 5 shows a third possible embodiment for the arrangement of the magnetic field sensors
  • FIG. 6 shows a fourth possible embodiment for the arrangement of the magnetic field sensors
  • FIG. 7 shows a diagram of the shear stress profile in the shaft according to FIG. 6 .
  • a very simply constructed hydrodynamic component 1 in the form of a retarder 1 can be identified in a schematic diagram.
  • the hydrodynamic retarder 1 consists of a primary wheel 2 which is configured to be rotationally movable and which is disposed in a rotationally fixed manner on a shaft 3 .
  • the primary wheel of the hydrodynamic retarder 1 is also designated as rotor.
  • the rotor 2 now has at its outer end a bladed region which together with a corresponding bladed region in a secondary wheel 4 forms a toroidal working chamber designated by 5 .
  • the secondary wheel 4 is typically fixed and in the very simple exemplary embodiment shown here is designed to be integrated in a housing 6 .
  • the secondary wheel 4 is also designated as stator 4 .
  • the working chamber 5 of the retarder 1 is filled with a working medium, for example, the cooling water of a cooling circuit in the case of a water retarder or an oil as working medium whenever wear-free braking is to be achieved with the retarder 1 .
  • a working medium for example, the cooling water of a cooling circuit in the case of a water retarder or an oil as working medium whenever wear-free braking is to be achieved with the retarder 1 .
  • the working chamber 5 is sealed with respect to the surroundings by means of sealing elements 7 indicated schematically here, the shaft 3 is suitably mounted by means of indicated bearings 8 , for example, roller bearings.
  • the retarder 1 can, for example, be disposed in a commercial vehicle, a rail vehicle or the like.
  • the rotor 2 moves the working medium located in the working chamber 5 with its bladed region and thereby attempts to transmit a corresponding torque to the stator 4 . Since the stator 4 for its part is configured to be non-rotationally movable, a corresponding torque is formed.
  • the accumulated work is converted into heat in the working medium. If the working medium is the cooling medium in the cooling circuit of a vehicle fitted with a retarder 1 , the heat is removed directly via the cooling medium, if an oil is used as working medium for the retarder 1 , this is cooled by means of a heat exchanger from a cooling medium in a circuit of the vehicle.
  • Such a retarder 1 frequently forms a part of a braking system and is combined with further brakes.
  • brakes can, for example, be an engine brake, a friction brake, and possibly a generator for recuperative braking.
  • the torque for the exemplary embodiment shown here in the region of the retarder 1 , should be measured accordingly.
  • the retarder 1 indicated schematically in FIG. 1 should have a device for detecting the transmitted torque which is shown schematically in the diagram in FIG. 1 .
  • This device substantially consists of two sections 9 , 10 of the shaft 3 , which have been provided with a permanent magnetic field.
  • the two sections 9 , 10 can be made of a ferromagnetic material.
  • the sections 9 , 10 can be provided with a permanent magnetic field which remains permanently in the region of the shaft 3 or in the region of the sections 9 , 10 and thus only needs to be generated once before mounting the shaft 3 in the retarder 1 .
  • the magnetic field located in the two sections 9 , 10 is in this case configured in a rotationally fixed manner to the respective section 9 , 10 of the shaft 3 .
  • Magnetic field sensors 11 , 12 are disposed as secondary sensors in a non-manner around the sections 9 , 10 of the shaft 3 . These are implemented in the form of coils which surround the shaft 3 . They are connected via corresponding line elements 13 to evaluation electronics 14 , which for example can be disposed outside the housing 6 of the retarder 1 .
  • the magnetic field located in the region of the sections 9 , 10 can be detected by means of the magnetic field sensors 11 , 12 . if an angular deviation occurs between the two sections 9 , 10 , the magnetic fields imprinted in a rotationally fixed manner with the shaft in the sections 9 , 10 are twisted at an angle to one another. This angle of twist can be detected by the magnetic field sensors 11 , 12 and the torque can be determined with the geometric properties and the material property of the structure.
  • the device for detecting the torque uses the principle of magnetostriction or the Joule effect.
  • the magnetic field sensors 11 , 12 in the form of coils surround the shaft 3 in a non-contact manner so that as a result, additional friction expenditure or the like is formed. In addition, they are comparatively small and very robust so that they can also be inserted in lubricating oil at high temperatures and in the working medium of the retarder 1 . Since the shaft itself or the magnetized sections 9 , 10 of the shaft 3 serve as primary sensor, the structure is extraordinarily compact since only the magnetic field sensors 11 , 12 require an additional installation space. In order to now be able to arrange these in a comparatively space-saving manner in the retarder 1 , it can in particular be provided to dispose these in the region of the sealing elements 7 or integrate them in said elements.
  • FIG. 3 shows a corresponding section with the shaft 3 and the housing 6 of the retarder 1 .
  • Two shaft sealing rings 15 are disposed around the shaft 3 but merely shown above the shaft 3 , which sealing rings seal with respect to one another the region of the surroundings located to the left of the section shown with the working chamber 5 located to the right of the section shown.
  • the shaft sealing rings 15 are designed in a manner known per se.
  • they have the two magnetic field sensors 11 , 12 in the form of coils. A very compact structure is obtained by integrating the magnetic field sensors 11 , 12 into the shaft sealing rings 15 .
  • shaft sealing rings 15 are present in any case, these must only be minimally adapted in their design and thus can easily be retrofitted in existing constructions since the overall structure can be formed from shaft sealing ring 15 and integrated magnetic field sensors 11 , 12 such that this corresponds to a conventional shaft sealing ring 15 in external dimensions. Since the primary sensor in the region of the shaft 3 is merely imprinted by magnetizing, in practice no additional expenditure is incurred with regard to the installation space.
  • FIG. 4 A similar diagram can be seen in FIG. 4 .
  • the two magnetic field sensors 11 , 12 are integrated between two shaft sealing rings 15 in the space located between the shaft sealing rings 15 .
  • the space provided in any case in conventional designs can in particular be used for integration of the magnetic field sensors 11 , 12 since comparatively controlled and uniform conditions prevail here and since moderate pressures and comparatively little abrasion from the region of the working chamber 5 are present here.
  • the magnetic field sensors can thus operate over a long period of time under very constant conditions so that the reliability of the structure can be increased. This also applies to the structure shown in FIG. 3 .
  • the diagram in FIG. 5 shows an alternative embodiment.
  • the shaft 3 is here designed as a hollow shaft which has a through hole or blind hole 16 . Since the magnetization of the sections 9 , 10 acts not only towards the outside but also into the interior of the hollow shaft, it is possible to arrange the magnetic field sensors 11 , 12 not only around the shaft 3 but also in the interior of the shaft 3 . These are connected in a positionally fixed manner to a non-rotating part, for example, the housing 6 via a corresponding support 17 . They can then measure similarly to the exemplary embodiments described above. As a result of their integration in the shaft, they are securely and reliably protected from events arising from the outer region of the shaft.
  • the line elements 13 can be simply guided towards the outside via the support 17 .
  • FIG. 6 shows a further embodiment of the structure shown similarly to that in FIGS. 3 and 4 .
  • Only a shaft sealing ring 15 is shown in this structure.
  • This is connected via a support element 18 to a piston ring 19 and supports this.
  • the support element 18 can surround the shaft 3 as an annular sheet metal element
  • the piston ring 19 cooperates with a corresponding groove 20 in the shaft 3 and seals the working chamber 5 with respect to the first sealing region 1 located between the sealing ring 19 and the shaft sealing ring 15 .
  • typically pressures of the order of magnitude of, for example, 10 bar can be present.
  • Typically a pressure of the order of magnitude of 1.5 to 2.5 bar can be established in the first sealing region 21 between the piston ring 19 and the shaft sealing ring 15 .
  • the support element 18 is also known and usual in conventional structures. It has a comparatively small axial length. In the exemplary embodiment shown in FIG. 6 this axial length of the support element 18 was correspondingly enlarged in order to thus enlarge the first sealing region 21 and provide space for the magnetic field sensors 11 , 12 which are connected to the support element 18 . A structural integration of the magnetic field sensors 11 , 12 can thus be achieved in which merely a minimal adaptation of the structure is required. In order to be able to achieve a good sealing of the retarder 1 with respect to the surroundings, in addition a further shaft sealing ring 15 can optionally be present in order to thus form a second sealing chamber on the side of the shaft sealing ring 15 shown here facing away from the first Sealing chamber 21 .
  • first sealing chamber 21 is connected via a stress-relief hole 22 to a hole 16 in the region of the shaft 13 designed as a hollow shaft. Oil can flow out from the second sealing chamber via this stress-relief hole 22 and thus decisively improve the sealing of the retarder 1 .
  • the magnetic field can be configured so that this has magnetically differently acting subregions around the circumference of the shaft 3 so that a corresponding region can be detected by means of the magnetic field sensors 11 , 12 and can be assigned to a revolution of the shaft.
  • such an inhomogeneity of the magnetic field around the circumference of the shaft 3 is also obtained when a corresponding location is disposed in the region of the shaft 3 which ensures a stress gradient in the stress produced in the stress produced under the mechanical loading of the shaft.
  • a location can, for example, be a groove, step or the like running in the axial direction.
  • the stress-relief hole 22 or a plurality of stress-relief holes 22 disposed over the circumference of the shaft 3 can be used accordingly.
  • the diagram in FIG. 7 shows the shear stress in the region of the shaft 3 over the axial extension thereof.
  • the dashed line shows the shear stress in the regions in which no stress-relief hole 22 is provided.
  • the continuous line shows the shear stress in the region in which the stress-relief hole 22 is disposed.
  • This strongly deviating shear stress ensures a variation in the magnetic field of the associated section according to the joule effect, in this case the associated second section 10 , so that a corresponding variation of the magnetic field occurs in this section at the locations of the circumference on which the stress-relief hole 22 is disposed. If then, for example a stress-relief hole 22 is disposed around the circumference, the corresponding perturbation in the shear stress and therefore in the magnetic field will always be detected when this location is at a certain position.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Braking Arrangements (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)
  • Dynamo-Electric Clutches, Dynamo-Electric Brakes (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US13/983,284 2011-02-02 2012-01-25 Hydrodynamic component Abandoned US20140050565A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011010153.5 2011-02-02
DE102011010153A DE102011010153B4 (de) 2011-02-02 2011-02-02 Hydrodynamische Komponente
PCT/EP2012/000324 WO2012104032A2 (fr) 2011-02-02 2012-01-25 Composant hydrostatique

Publications (1)

Publication Number Publication Date
US20140050565A1 true US20140050565A1 (en) 2014-02-20

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US13/983,284 Abandoned US20140050565A1 (en) 2011-02-02 2012-01-25 Hydrodynamic component

Country Status (7)

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US (1) US20140050565A1 (fr)
EP (1) EP2671059A2 (fr)
JP (1) JP2014508923A (fr)
KR (1) KR20140052947A (fr)
CN (1) CN103534505A (fr)
DE (1) DE102011010153B4 (fr)
WO (1) WO2012104032A2 (fr)

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US11629763B2 (en) * 2020-01-21 2023-04-18 Ford Global Technologies, Llc Clutch assembly for a manual transmission of a motor vehicle

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DE102013110311A1 (de) * 2013-09-19 2015-03-19 Claas Tractor Sas Sensoranordnung zum Erfassen einer mechanischen Beanspruchung eines Bauteils eines landwirtschaftlichen Fahrzeugs
DE102013221056A1 (de) * 2013-10-17 2015-04-23 Robert Bosch Gmbh Kupplungssensorsystem
DE102013224836A1 (de) 2013-12-04 2015-06-11 Voith Patent Gmbh Hydrodynamische Maschine mit Messsystem
DE102015218856A1 (de) * 2015-09-30 2017-03-30 Siemens Aktiengesellschaft Elektrische Maschineneinheit, insbesondere für ein Elektro- oder Hybridfahrzeug
DE102016212277A1 (de) * 2016-07-06 2018-01-11 Robert Bosch Gmbh Drehmomenterfassungseinrichtung und Fahrzeug
CN109113789B (zh) * 2018-10-30 2024-02-09 山东安达尔信息科技有限公司 地压多向监测可定位钻孔应力传感器
CN115183935A (zh) * 2022-07-21 2022-10-14 中国船舶重工集团公司第七0四研究所 一种基于静态扭矩标准机的旋转扭矩校准装置

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EP2671059A2 (fr) 2013-12-11
WO2012104032A3 (fr) 2013-10-24
KR20140052947A (ko) 2014-05-07
WO2012104032A2 (fr) 2012-08-09
CN103534505A (zh) 2014-01-22
JP2014508923A (ja) 2014-04-10
DE102011010153A1 (de) 2012-08-02

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