Classifications

• • G—PHYSICS
  • G01—MEASURING; TESTING
  • G01P—MEASURING LINEAR OR ANGULAR SPEED, ACCELERATION, DECELERATION, OR SHOCK; INDICATING PRESENCE, ABSENCE, OR DIRECTION, OF MOVEMENT
  • G01P3/00—Measuring linear or angular speed; Measuring differences of linear or angular speeds
  • G01P3/42—Devices characterised by the use of electric or magnetic means
  • G01P3/56—Devices characterised by the use of electric or magnetic means for comparing two speeds
  • G01P3/60—Devices characterised by the use of electric or magnetic means for comparing two speeds by measuring or comparing frequency of generated currents or voltages
• • 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
  • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
  • F16H59/36—Inputs being a function of speed
  • F16H59/38—Inputs being a function of speed of gearing elements
• • G—PHYSICS
  • G01—MEASURING; TESTING
  • G01P—MEASURING LINEAR OR ANGULAR SPEED, ACCELERATION, DECELERATION, OR SHOCK; INDICATING PRESENCE, ABSENCE, OR DIRECTION, OF MOVEMENT
  • G01P3/00—Measuring linear or angular speed; Measuring differences of linear or angular speeds
  • G01P3/42—Devices characterised by the use of electric or magnetic means
  • G01P3/44—Devices characterised by the use of electric or magnetic means for measuring angular speed
  • G01P3/48—Devices characterised by the use of electric or magnetic means for measuring angular speed by measuring frequency of generated current or voltage

Definitions

• the present invention relates to a method for determining the rotational speed of the main shaft of a transmission, wherein the main shaft is connected via a switchable Pianetengetriebe with an output shaft, wherein the main shaft rotatably connected to the sun gear and the output shaft rotatably connected to the planet carrier. Furthermore, the present invention relates to a transmission with a Drehiereabgriffs founded.
• DE 198 14 758 A1 generally describes a device for detecting the rotational speed of a shaft.
• the known device has a non-rotatably connected to the signal generator, which is designed in the manner of a gear, wherein the teeth of the gear each have a steep and a flat tooth flank.
• an analogue Hall effect sensor is provided, which picks up the rotational speed in the radial direction on the circumference of the toothed wheel, ie on the teeth. Thanks to the different flank pitches of the two tooth flanks, it is possible to determine the speed and direction of rotation with only one sensor and at a constant refresh rate, even if the shaft rotates at a very low speed.
• the known device includes for this purpose a Getriebeweile to which a tachometer gear is rotatably mounted, wherein the tachometer gear turn a fixed speed sensor is assigned, which picks up the speed in the radial direction on the circumference of the tachometer gear, so on the teeth.
• a Getriebeweile to which a tachometer gear is rotatably mounted, wherein the tachometer gear turn a fixed speed sensor is assigned, which picks up the speed in the radial direction on the circumference of the tachometer gear, so on the teeth.
• This means that the teeth of the tachometer gear generate when driving past the speed sensor electrical impulses, which are fed to a corresponding evaluation unit.
• the present invention is therefore based on the object to provide a method for determining the rotational speed of a main shaft of a transmission, which allows a simple and reliable determination of the rotational speed while overcoming the above-mentioned disadvantages. Moreover, the invention relates to a transmission with a Drehzahiabgriffs worn.
• the inventive method is a method for determining the speed of Hauptwelie a transmission in which the main shaft is connected via a switchable planetary gear with an output shaft, the Hauptwelie rotatably connected to the sun gear and the output shaft rotatably connected to the Pianetenradong.
• the speed of the ring gear of the planetary gear is tapped in a process step.
• the rotational speed of the output shaft or of the planet carrier is tapped off. The latter is to be preferred in view of the greater radial extent of Pianetenrad umans, since then only a sensor of shorter overall length would be required.
• the rotational speed of the main shaft is calculated from the rotational speed of the Höhlrades and the rotational speed of the output shaft or the Planetenradyess. This can be done for example on the basis of the known translation of the Pianetengetriebes.
• the rotational speed of the main shaft is thus not tapped directly on the main shaft, but rather indirectly from known sizes of the planetary gear and the rotational speeds of hollow gears. wheel and output shaft or Planetenradfräger calculated.
• This has the advantage that no Wheelzahisensor with long Bauforrn or even an additional tachometer gear must be provided at the main draw in order to tap the speed directly.
• an increase in the weight, the length and the volume of the transmission is prevented.
• a safe Drehzahi thanks is guaranteed, even if a floating main shaft is used with great axial play.
• the erfindu ⁇ gsgemiße method allows speed detection of the main shaft of the transmission, regardless of the switching state of the Pianetengetriebes.
• the method furthermore the method steps tapping the direction of rotation of the ring gear, tapping the direction of rotation of the output shaft or Planetenradfrägers and determining the direction of rotation of the main shaft based on the direction of rotation of the ring gear and the Direction of rotation of the output shaft or Pianetenradlys performed.
• the rotational speed of the main shaft is determined by the relationship
• n denotes H auptwe! Ie the speed of the main shaft
• i 0 is the Standgetriebeübersefzung of the planetary gear
• the determined directions of rotation are included in the calculation insofar as they lead to different signs in the rotational speeds.
• the planetary gear can be switched to a neutral Schaitschreib in which both the planet and the hollow wheel is solved.
• the planet carrier and the Abfriebsweiie and the ring gear are consequently, not stalled
• the speed of the main drag is determined according to the above relationship.
• the planetary gear can be switched, for example, in a low switching state in which the Hohirad is braked.
• the ratio of the planetary gear is based on the relationship
• the transmission according to the invention has a main shaft, which is connected via a switchable Pianetengetriebe with a driven shaft.
• the planetary gear can be switched to a neutral, low or high switching state.
• the main shaft is rotationally fixed to the sun gear of the planetary gear and the output shaft is rotatably connected to the planetary gear of the planetary gear.
• the transmission may be, for example, a range handrail.
• the transmission further comprises a Drehiereabgriffs founded for determining the rotational speed of the main shaft.
• the Drehiereabgriffs has a first speed sensor for tapping the speed of the Hohirades on the ring gear and a second speed sensor for tapping the speed of the output shaft or the Pianetenradträ- gers on the output shaft or the planet carrier.
• the speed sensor can be, for example, an induction sensor, a Hall effect sensor or the like, which interacts with a corresponding signal or rotational speed transmitter on the corresponding gear unit.
• the speed tapping unit has direction furthermore a calculation unit, by means of which the speed of the Hauptwelie from the speed of the ring gear and the speed of the output shaft or the Pianetenradyess is calculated.
• the first and second speed sensor are aligned in an advantageous embodiment of the transmission according to the invention such that the speed of the ring gear and the speed of the output or Pianetenradismes can be tapped in the radial direction on the circumference.
• speed sensors of particularly small design can be used in this constellation.
• no elongated brackets for the speed sensors are required.
• a signal generator preferably an outer toothing, is provided on the ring gear and on the output shaft or the planet carrier, at which the corresponding rotational speed can be tapped.
• the hollow-wheel-side signal transmitter is formed integrally with the ring gear and the other signal generator integral with the output shaft or the Plantenradfräger
• the signal generator can be stamped, for example, in the corresponding planetary gear part.
• the first and the second speed sensor are arranged in a further preferred embodiment of the transmission according to the invention to a common sensor module
• both speed sensors can be mounted simultaneously by attaching the sensor module within the transmission.
• the calculation unit calculates the rotational speed of the main shaft on the basis of the relationship
• the calculation unit thus calculates the rotational speed of the main shaft independently of the switching state of the planetary gear.
• the calculation unit determines the ratio of the planetary gear on the basis of the relationship
• ZHohirad here denotes the number of teeth on the ring gear and Zso ⁇ ne ⁇ rad the number of teeth on the sun gear.
• a first Dreh ⁇ chtungssensor for tapping the direction of rotation of the Hohirades and a second rotation direction sensor for tapping the direction of rotation of the output shaft or the Planetenradffys is further provided, the direction of rotation of the main shaft based on the direction of rotation of the ring gear and the direction of rotation of the output or of the planet carrier can be determined by the calculation unit. Further, the calculation unit based on the two directions of rotation determine the absolute speed and / or direction of rotation of the main shaft.
• the first rotational speed sensor and the first rotational direction sensor are formed by a first combination sensor for detecting the rotational speed and the rotational direction, while the second rotational speed sensor and the second rotational direction sensor is formed by a second combination sensor for sensing the rotational speed and the rotational direction
• Fig. 2 is an enlarged view of the planetary gear
• FIG. 3 is a flow chart for illustrating the method according to the invention on which the transmission of FIGS. 1 and 2 is based.
• Fig. 1 shows a schematic representation of an embodiment of the transmission 1 according to the invention, which is operated by the method according to the invention.
• the transmission 1 which can be used for example in a motor vehicle, is an equiaxed transmission with a drive shaft 2, a main shaft 3 and a Abf ⁇ ebswe ⁇ le 4, which are arranged one behind the other lying on an axis 5.
• There are also two countershafts 6, 7 are provided, which extend along two axes 8, 9, which are arranged parallel to the axis 5.
• the main shaft 3 is floating between the two countershafts 6, 7 and stored with a large Axialspiei between the drive shaft 2 and the output shaft 4.
• the transmission 1 further comprises a transmission housing 10 through which the main shaft 3 opposite ends of the drive and output shafts 2, 4 extend outwardly.
• Vorgeiegewellen 6 3 7 each have a drive gear 1 1, 12 is fixed, which is in engagement with a driven gear 13 of the drive shaft 2, so that the countershafts 6, 7 can be driven by the drive shaft 2.
• 6 or 7 further fixed gears 14 and 15 are provided on the countershaft bores, which are with idler gears 16 on the Hauptwelie third are engaged.
• the Fesftechnik scholar 14, 15 with the corresponding idler gear 16 each of the wheelset a gear of the transmission 1 from.
• a coupling of the main shaft 3 with one of the idler gears 16 furthermore at least one switchable coupling device is provided on the main shaft 3, au! whose presentation has been omitted for reasons of clarity.
• the main shaft 3 is connected to the output shaft 4 via a switchable planetary gear 17, which is shown enlarged in Fig. 2.
• the planetary gear 17 has a sun gear 18 which is rotatably connected to the main shaft 3.
• the sun gear 18 meshes with planetary gears 19, only one of which is shown and which are rotatably arranged on a planetary gear wheel 20.
• the planet carrier 20 is in turn rotatably connected to the output shaft 4.
• the planetary gears 19 are in turn with the (internal teeth 21 of a ring gear 22 of the planetary gear 17 in engagement.
• the transmission 1 also has a speed tapping device for determining the rotational speed of the main shaft 3.
• the Drehzahiabgriffs has a fixed sensor module 23, which is arranged on the Gef rubbing housing 10.
• a first rotational speed sensor 24 for tapping the rotational speed of the ring gear 22 and a first Drehurgissen- sensor 25 for tapping the direction of rotation of the ring gear 22 is arranged, which are combined in a first combination sensor.
• a second speed sensor 26 is provided for picking up the rotational speed of the planetary gear carrier 20, which corresponds to the rotational speed of the output shaft 4, and a second rotational direction sensor 27 for detecting the direction of rotation of the Planetenradträ- gers 20, which are combined in a second Kombinafionssensor.
• the first rotational ZDrehrichfungssensor 24, 25 engages the rotational speed or direction of rotation of the ring gear 22 in the radial direction at the periphery of the hollow Rades 22 off.
• a signal generator in the form of a circumferential external toothing 28 is provided on the circumference of the hollow wheel 22, which is formed integrally with the ring gear 22.
• the second rotational speed ZDrehidess- sensor 28, 27 detects the rotational speed or direction of rotation of the planet carrier 20 in the radial direction on the circumference of the planet carrier 20 from.
• a signal generator in the form of a circumferential outer toothing 29 is provided on the circumference of the planet carrier 20.
• the teeth rotating past the sensors 24, 25, 26, 27 generate corresponding pulses in the sensors 24, 25, 26, 27 which indicate the rotational speed or direction of rotation of the ring gear 22 and the planetary carrier 20.
• the configuration described in DE 198 14 758 A1 can be used.
• the sensors 24, 25, 26 27 are connected via a corresponding line 30 to a calculation unit 31.
• the calculation unit 31 can calculate the rotational speed and direction of rotation of the main shaft 3 on the basis of the determined rotational speeds and directions of rotation of the ring gear 22 and planetary gear 20, as will be explained below with reference to FIG.
• the planetary gear 17 can be switched to a neutral switching state, a low switching state and a high switching state.
• neutral switching state both the planet 17 and the ring gear 22 is released, ie they are not braked.
• low switching state the ring gear is braked.
• high switching state the planetary gear 17 performs a block revolution. Block revolution is accomplished by coupling a driven planetary gear member such as ring gear 22 to a second planetary gear member. as for example the sun gear reaches 18th
• the third planetary gear part, such as the planet carrier 20, is thus forced to rotate at the same speed.
• Fig. 3 shows the sequence of the method according to the invention, which is based on the previously described transmission 1.
• a first method step S1 the rotational speeds and rotational directions of the ring gear 22 and of the planetary gear carrier 20 are tapped with the aid of the rotational speed sensors 24, 25, 26, 27 on the corresponding planetary gear set.
• the signals generated in the sensors 24, 25, 26, 27 are transmitted via the line 30 to the calculation unit 31.
• a second method step S2 the rotational speeds and directions of rotation of the ring gear 22 and the planet carrier 20 are calculated or determined on the basis of the transmitted signals.
• the calculation unit 31 calculates the speed of the main shaft 3 according to the following equation:
• nHohirad the speed of the ring gear 22
• n Abt ris b the speed of the planet carrier 20. io denotes the stationary gear ratio of the planetary gear 17 and is calculated as follows:
• Z ⁇ ohirad denotes the number of teeth of the internal teeth 21 of the ring gear 22 and Zs om enraci the number of teeth of the external teeth of the sun gear 18,
• step S3 the direction of rotation of the main shaft 3 is further determined on the basis of the directions of rotation of the ring gear 22 and of the planetary gear 3.
• tenradlys 20 determined in order to determine the absolute speed riHauptwiie and direction of rotation of the main shaft 3 with the aid of the above-mentioned equation.
• the speed and direction of rotation of the main shaft is thus always determined on the basis of the above equation, regardless of whether the planetary gear 17 is switched to a neutral, low or high switching state.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• General Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Control Of Transmission Device (AREA)
• Retarders (AREA)
• Transmission Devices (AREA)
• Structure Of Transmissions (AREA)

Applications Claiming Priority (2)

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• 2006
  • 2006-05-19 DE DE102006023552A patent/DE102006023552A1/de not_active Ceased
• 2007
  • 2007-04-25 WO PCT/EP2007/054017 patent/WO2007134933A1/de active Application Filing
  • 2007-04-25 US US12/300,868 patent/US8050832B2/en not_active Expired - Fee Related
  • 2007-04-25 BR BRPI0711917-8A patent/BRPI0711917A2/pt not_active IP Right Cessation
  • 2007-04-25 EP EP07728473A patent/EP2021810A1/de not_active Withdrawn
  • 2007-04-25 CN CN2007800182811A patent/CN101449170B/zh not_active Expired - Fee Related
  • 2007-04-25 RU RU2008150050/28A patent/RU2008150050A/ru unknown
  • 2007-04-25 JP JP2009510390A patent/JP2009537753A/ja active Pending

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