WO2014095157A1 - Dispositif de commutation pour engrenage planétaire - Google Patents

Dispositif de commutation pour engrenage planétaire Download PDF

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Publication number
WO2014095157A1
WO2014095157A1 PCT/EP2013/073467 EP2013073467W WO2014095157A1 WO 2014095157 A1 WO2014095157 A1 WO 2014095157A1 EP 2013073467 W EP2013073467 W EP 2013073467W WO 2014095157 A1 WO2014095157 A1 WO 2014095157A1
Authority
WO
WIPO (PCT)
Prior art keywords
switching
sliding sleeve
coupling element
switching device
planetary gear
Prior art date
Application number
PCT/EP2013/073467
Other languages
German (de)
English (en)
Inventor
Ewald Schmitz
Frank Richter
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2014095157A1 publication Critical patent/WO2014095157A1/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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • 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
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D2011/002—Clutches in which the members have interengaging parts using an external and axially slidable sleeve for coupling the teeth of both coupling components together
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • F16H2063/305—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force using electromagnetic solenoids
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • F16H2063/3056—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force using cam or crank gearing
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3093—Final output elements, i.e. the final elements to establish gear ratio, e.g. dog clutches or other means establishing coupling to shaft
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed

Definitions

  • the present invention relates to a switching device for a planetary gear according to the closer defined in the preamble of claim 1. Art.
  • Such switching devices for planetary gear find, for example.
  • the drive motors are DC / AC main spindle motors.
  • the gearboxes increase the power range of the main spindle motors in order to increase the flexibility of the machine tools when machining different materials or cutting forces due to high torques or speeds.
  • two gear ratios are formed in which on the one hand the drive shaft which is connected to the sun gear, with a ring gear and on the other hand, the ring gear can be coupled to the housing.
  • the planet carrier serves as an output and is connected to the output shaft.
  • From DE 199 17 673 A1 discloses a switching device for a two-stage planetary gear is known, the drive shaft is connected to a sun gear and the output shaft to a planet carrier.
  • a ring gear of the planetary gear is positively coupled via a sliding sleeve with a transmission housing or with the sun gear.
  • the sliding sleeve is displaceable coaxially to the drive shaft by means of an electric actuator in the various switching positions.
  • the actuator is an electromagnet whose armature is drivingly connected to the sliding sleeve.
  • a switching device for a planetary gear which is a sliding sleeve, which is displaceable by the actuation of an actuating means in the axial direction of the planetary gear from a neutral position to a switching position, at least one coupling element for non-rotatable coupling of two components of the planetary gear in the axial direction of the planetary gear from an idle position into an engaged position is displaceable, and at least one switching spring, which couples the sliding sleeve and the at least one coupling element such that upon displacement of the sliding sleeve from the neutral position to the switching position, the coupling element in the direction of the component to be coupled therewith is spring loaded, has. Furthermore, the switching device has a locking unit which holds the coupling element in the locked state in the idle position, so that the spring energy can be stored stored in the shift position shifted sliding sleeve and at a certain time by the unlocking of the locking unit.
  • the switching device accordingly has a sliding sleeve, at least one coupling element and at least one switching spring.
  • the sliding sleeve is displaced by the actuation of the actuating means in the axial direction of the planetary gear from the neutral position to the switching position.
  • the sliding sleeve can be designed to be displaceable in a single, or even in at least two switching positions. If the sliding sleeve has a plurality of switching positions, these can be configured with respect to their neutral position in opposite directions of displacement of the sliding sleeve. Alternatively or additionally, however, at least two switching positions can also be arranged one after the other in a direction of displacement. In the neutral position, no torque is transmitted from the drive shaft to the output shaft.
  • the at least one coupling element for rotationally fixed coupling of two components of the planetary gear in the axial direction of the planetary gear from an idle position into an engaged position is displaced.
  • the coupling element is rotatably coupled to one of the components of the planetary gear and designed to be displaceable in the axial direction of the planetary gear.
  • the coupling element has a coupling toothing, which engages positively in the engaged position with the second component to be coupled thereto.
  • the at least one switching spring couples the sliding sleeve and the at least one coupling element with each other such that upon displacement of the sliding sleeve from the neutral position to the switching position, the coupling element in the direction of it coupling member is spring loaded.
  • the switching device has a locking unit.
  • the locking unit holds the coupling element in the locked state in the idle position, so that the spring energy can be stored stored in the shift position shifted sliding sleeve and at a certain time by the unlocking of the locking unit.
  • the locking unit has at least one locking element, in particular a switching pin and / or a preferably pivotably designed hoeing element.
  • the switching pin can be decoupled by means of the chopping member of axial forces, which are applied by the switching spring.
  • the chopping element is designed to be pivotable about a pivot point for this purpose and / or pressed into the locking position by means of a spring element.
  • the locking unit has an engagement region which is formed on the coupling element and with which the locking element corresponds.
  • the engagement region is preferably formed as a shoulder and / or as a circumferential annular groove.
  • a trained as an annular groove engagement region also has the advantage that the Coupling element in each of the two axial directions can be locked.
  • the coupling element may be rotatable, so that the locking element can move in the annular groove in the circumferential direction of the planetary gear.
  • the switching device has at least one locking element, in particular a switching pin and / or a preferably pivotally formed hoe element, which is coupled to the sliding sleeve so that it is able to maintain this in the activated state in the switching position.
  • the switching device can be made particularly inexpensive if it has at least one return spring which is coupled to the sliding sleeve and / or the coupling element such that it can be tensioned when moving the sliding sleeve from the neutral position to the switching position and the sliding sleeve from the switching position in the Neutral position and / or the coupling element from the engaged position into the idle position, in particular when deactivating the locking means, can push back.
  • at least one return spring which is coupled to the sliding sleeve and / or the coupling element such that it can be tensioned when moving the sliding sleeve from the neutral position to the switching position and the sliding sleeve from the switching position in the Neutral position and / or the coupling element from the engaged position into the idle position, in particular when deactivating the locking means, can push back.
  • the planetary gear can be made very compact, when the switching device comprises a first coupling element, in particular for non-rotatable coupling of a ring gear with a stationary housing of the planetary gear, and a second coupling element, in particular for rotationally fixed coupling of a sun gear with a planet carrier of the planetary gear.
  • the rotatable masses of the planetary gear can be minimized, in particular by the coupling of the sun gear with the planet carrier of the planetary gear.
  • the design effort of the planetary gear can be reduced if each of the switching spring of one of the two coupling elements is designed as a return spring of the other coupling element.
  • the rotatable masses of the planetary gear can be reduced if the first coupling element has a radially inner first and a radially outer second part, which are rotatable to each other.
  • at least one of these two parts, in particular the radially outer second part can be decoupled from the rotation of the rotatably coupled component of the planetary gear.
  • the switching device can be made particularly compact, when the first and second coupling element form a jointly displaceable in the axial direction of the planetary gear unit and / or at the same time are rotatably mounted to each other.
  • the manufacturing cost of the switching device can be reduced if the switching position of the sliding sleeve for the first and the switching position of the sliding sleeve for the second coupling element is identical. Thus, only one locking element and a return spring is needed for both coupling elements.
  • the adjusting means in particular a switching pin, corresponds with a switching groove.
  • the shift groove is on the outer circumference of a shaft, in particular the drive shaft or the rotatably coupled to the drive shaft coupled sliding sleeve arranged. Further, the shift groove has a curve extending substantially in the circumferential direction of the shaft and provided with a slope, in particular helical.
  • the rotational energy of the drive shaft can be used for switching, which can be switched with significantly higher switching power.
  • the additional components such as solenoids or electric motors, omitted for the circuit.
  • the adjusting means can be made smaller, since they have to apply the necessary force to be inserted into the switching groove, but not the actual displacement force to initiate the switching movement. This is generated by the rotating gear shaft and helically converted into an axial displacement of the sliding sleeve. Depending on the axial course of the at least one shift groove, the approach of the sliding sleeve to the coupling element can take place at a defined approach speed. Furthermore, the switching spring can be operated with a relatively high thrust. It is also advantageous if a first and a second shift groove is provided, which have an opposite course in the axial direction.
  • the adjusting means after reaching the desired position of the shaft, in particular the sliding sleeve, not specifically led out of the shift groove, but can be automatically moved back by the leakage of the groove in the starting position.
  • the adjusting means is a switching pin, which is electromagnetically actuated.
  • the adjusting means can thereby form a very space-saving, while at the same time a simple and precise control is enabled.
  • the design effort can be reduced if the actuating means is formed stationary, in particular connected to the housing.
  • the adjusting means is slidably disposed with the sliding sleeve in the axial direction of the planetary gear. In this case, the adjusting means would engage in a formed on the drive shaft shift groove.
  • the movable masses of the switching device can be reduced if the sliding sleeve has a, in particular radially inner, first and one, in particular radially outer, second part, which are designed to be rotatable relative to one another.
  • the sliding sleeve is rotatably and axially displaceably arranged on the drive shaft.
  • the sliding sleeve but also be axially displaceable and rotatably coupled to the drive shaft.
  • the switching device on a coupled with the sliding sleeve first and second stop member, which are each assigned to one of the two switching springs. Furthermore, these are so decoupled from each other that when moving the sliding sleeve from the neutral position in one of the two switching positions only one of the two switching springs is tensioned and the other dwells in its normal position. Thus, not even the spring force of the lingering in the basic position switching spring must be overcome.
  • the sliding sleeve is arranged on the drive shaft or on a countershaft parallel to this.
  • the countershaft is coupled to the drive shaft via a spur gear and a controllable clutch.
  • the torque of the drive shaft by means of the spur gear and / or the controllable clutch can be transmitted to the countershaft, whereby a targeted displacement of the sliding sleeve on the countershaft in the switching position or by correspondingly opposite rotation can be made in the neutral position.
  • a driven-side circuit of the switching device can also take place a driven-side circuit of the switching device.
  • a planetary gear in particular a two-stage planetary gear for a machine tool is proposed, which has a central sun gear, a ring gear, which surrounds the sun gear, radially disposed therebetween planetary gears, which are rotatably supported in a planet carrier, and a switching device.
  • the drive shaft of the planetary gear is coupled to the sun gear and the output shaft of the planetary gear to the planet carrier.
  • the Switching device is formed according to the preceding description, wherein said features may be present individually or in any combination.
  • FIGS. 1 a - 1 e show the individual switching steps of the switching device shown schematically here
  • FIG. 2 shows a first embodiment of a planetary gear with a switching device in cross section, in which a sliding sleeve from the neutral position is displaceable in a first switching position and in a second switch position formed opposite thereto,
  • FIG. 3 shows a second embodiment of a planetary gear with a switching device in cross section, in which the sliding sleeve is displaceable from the neutral position into a switching position associated with both coupling elements
  • FIG. 4 shows a third embodiment of a planetary gear with switching device in cross section, in which an adjusting means is designed to be displaceable with a sliding sleeve as a unit in the axial direction,
  • Figure 5 shows a fourth embodiment of a planetary gear with countershaft
  • the switching device 1 comprises a first component 2 and a second component 3, which can be coupled to one another in a rotationally fixed manner by means of a coupling element 4.
  • the first component 2 is designed as a drive shaft 5 and the second component 3 as an output shaft 6.
  • the output shaft 6 is fixed on the drive shaft 5 in the axial direction and rotatable on this stored.
  • the drive shaft 5 has an outer toothing 7, in which the coupling element 4 engages.
  • the coupling element 4 is thus rotatably coupled to the output shaft 6 and relative to this in the axial direction from an idle position shown in Figure 1 a in an engagement position shown in Figure 1 d shown.
  • the coupling element 4 engages with a toothing 8, which is formed on the front side, in a toothing 9 of the output shaft 6 which is likewise arranged on the front side such that the coupling element 4 rotatably couples the drive shaft 5 to the output shaft 6.
  • the switching device further comprises a sliding sleeve 10.
  • This is rotatably coupled to the drive shaft 5, in particular by means of the external toothing 7 and slidably in the axial direction.
  • the axial displacement of the sliding sleeve 10 is effected from a neutral position shown in Figure 1 a in a switching position shown in Figure 1 c.
  • the sliding sleeve 10 only a single switching position. But it is also conceivable that a plurality of switch positions are formed. These may in turn be formed in a direction of displacement of the sliding sleeve 10 and / or in mutually opposite displacement directions.
  • the displacement of the sliding sleeve 10 is effected by means of an actuating means 1 1, which is able to engage in accordance with Figure 1 a in a Au on the outer circumference 12 of the sliding sleeve 10 formed shift groove 13.
  • the shift groove 13 has a substantially in the circumferential direction of the sliding sleeve 10 extending and provided with a slope curve. In the present case, the shift groove 13 is formed substantially helical.
  • the switching device 1 comprises a switching spring 14 and a return spring 15.
  • the switching spring 14 couples the sliding sleeve 10 with the coupling element 4.
  • the return spring 15 couples the axially movable sliding sleeve 10 with a fixed in the axial direction of the switching device 1 base 1 6.
  • the switching device 1 furthermore has a locking unit 17, which comprises a locking element 18 and an engagement region 19 on the coupling element 4.
  • the adjusting means 1 1, the locking member 18 and the locking member 20 are presently designed as electrically controllable switching pins, which in particular are electromagnetically actuated.
  • the adjusting means can thereby be implemented to save space in the region of the sliding sleeve 10, while at the same time a simple and precise control is possible.
  • the switching pins can alternatively but also be pneumatically or hydraulically actuated.
  • the coupling element 4 is initially in the neutral position, so that there is no rotationally fixed coupling between the first component 2 or the drive shaft 5 and the second component 3 or the output shaft 6 is present. Furthermore, the sliding sleeve 10 is in its neutral position. The switching spring 14 and the return spring 15 are substantially unloaded. In the basic position of the switching device 1 shown in FIG. 1a, only the locking element 18 is activated by all the switching pins. As a result, this engages positively in the engagement region 19 of the coupling element 4, so that it is held firmly in the neutral position. Thus, it can be avoided that the coupling element 4 inadvertently approaches the output shaft 6.
  • the engagement portion 19 is formed as an annular groove, so that the coupling element 4 is able to rotate in spite of locking together with the drive shaft 5.
  • the actuating means 1 1 is activated according to Figure 1 b, so that it engages positively in the shift groove 13. Due to the rotation of the drive shaft 5 and the present helical design of the shift groove 13, the shift sleeve 10 is displaced in the axial direction from the neutral position shown in Figure 1 b in the switching position shown in Figure 1 c. As a result, this advantageously the energy of the drive motor, not shown here, is used to carry out the switching operation. Thus, can be switched with significantly higher switching forces, so that additional components such as solenoids or electric motors can be saved for the circuit. When sliding the sliding sleeve 10, as shown in Figure 1 c, both the switching spring 14 and the return spring 15 stretched.
  • this time can be controlled by means of a corresponding design of the switching groove 13 by the switching groove 13 in an alternative embodiment not shown here along its course continuously reduces its depth to zero, so that the actuating means 1 1 in the illustrated in Figure 1 c Switching position of the sliding sleeve 10 is pushed back to the height of the outer periphery 12 of the sliding sleeve 10.
  • the return spring 15 and the switching spring 14 is tensioned so that they spring beaufeaufeauf sound the sliding sleeve 10 in the direction of its neutral position.
  • the locking element 20 engages in an engagement region 21 of the sliding sleeve 10 immediately after the sliding sleeve 10 has reached the switching position according to FIG. 1 c, so that the sliding sleeve 10 in FIG the switching position is locked.
  • the engagement portion 21 of the sliding sleeve 10 is presently designed as an annular groove. Since both the coupling element 4 are held by means of the locking element 18 in the idle position and the sliding sleeve 10 by means of the locking member 20 in the switching position, the spring energy, in particular the switching spring 14, are stored in the system.
  • the locking element 18 is deactivated according to Figure 1 d, wherein the locking member 18 retracts from the engagement portion 19 of the coupling element 4.
  • the spring-loaded coupling element 4 which is spring-loaded by means of the switching spring 14 in the direction of the second component 3 to be coupled thereto, is thus pressed against the second component 3 or the output shaft 6, so that the two toothings 8, 9 of the coupling element 4 and the output shaft 6 engage in one another.
  • the switching spring 14 is still stretched in this position so that the coupling element 4 can not move the drive side.
  • an unintentional decoupling of the coupling element 4 can be avoided.
  • an additional switching pin not shown here, could also be present, which engages in the engagement region 19, so that the coupling element 4 is held in the engaged position.
  • the locking element 20 is deactivated according to FIG. Since the return spring 15 is supported on the base 1 6 and the sliding sleeve 10 is spring-loaded in the direction of its neutral position, the sliding sleeve 10 is pushed back by the return spring 15 at unlocked locking element 20 back to its neutral position. Since the sliding sleeve 10, in particular by means of the switching spring 14, is coupled to the coupling element 4, the coupling element 4 is pushed back into the neutral position during displacement of the sliding sleeve 10 in the neutral position. As a result, the rotationally fixed coupling between the first component 2 and the drive shaft 5 and the second component 3 and the output shaft 6 is repealed. Once the coupling element 4 is again in its idle position, this is again locked according to Figure 1 a by means of the locking element 18.
  • Such a trained switching device 1 is particularly well suited for transmissions in which the output shaft 6 is actively braked by means of a brake device, not shown here, in particular a brake disc.
  • a brake device not shown here, in particular a brake disc.
  • the switching energy used by the drive shaft 5 can be stored by means of the shift spring 14 and at a given time, especially when the brake device is released, are released.
  • a clean engagement of the teeth 8 of the coupling element 4 in the toothing 9 of the output shaft 6 can be ensured without an expensive and complex synchronization.
  • FIGS 2 - 6 show different embodiments of the switching device 1 for a planetary gear 22.
  • the planetary gear 22 is in two stages designed and provided in particular for use in machine tools.
  • the different embodiments of the planetary gear 22 have a central sun gear 23 which is rotatably coupled to the drive shaft 5.
  • the planetary gear 22 comprises a rotatably mounted ring gear 24 which surrounds the sun gear 23.
  • planetary gears 25 are arranged, which are each held by a planetary pin 26 rotatably in a planet carrier 27.
  • the planet carrier 27 is also rotatably mounted, in particular on the sun gear 23, and form the output shaft 6.
  • the planetary gear 22 shown in Figure 2 comprises a first coupling element 28 and a second coupling element 29.
  • the first and the second coupling element 28, 29 together form a displaceable in the axial direction of the planetary gear 22 unit 32, wherein they are rotatable to each other by means of a bearing 30 to each other are.
  • the first coupling element 28 is rotatably coupled to the ring gear 24 and slidable to this in the axial direction.
  • the second coupling element 29 is rotatably coupled to the sun gear 23 and slidable to this in the axial direction.
  • the ring gear 24 In a first switching position, the ring gear 24 is rotatably coupled by means of the first coupling element 28 with a stationary housing 31.
  • the first coupling element 28 or the unit 32 which comprises the first coupling element 28, the second coupling element 29 and the bearing 30, the drive side, i. in the direction of the drive shaft 5, moved.
  • a first toothing 33 arranged on the front side on the first coupling element 28 interlocks positively with a housing toothing 34.
  • the ring gear 24 is then rotatably coupled by means of the first coupling element 28 with the housing 31.
  • the switching process essentially takes place in accordance with the switching process of the schematically illustrated switching device 1, which is visualized in FIGS. 1 a to 1 e.
  • the adjusting means 1 which is also stationary in particular connected to the housing, not shown here, introduced into a shift groove 13 of the sliding sleeve 10.
  • the sliding sleeve 10 is, in particular via the second coupling element 29, rotatably coupled to the sun gear 23 and with the drive shaft 5. Due to the helical Formation of the shift groove 13, this is moved during rotation of the sliding sleeve 10 from the neutral position shown here on the drive side in a first switching position.
  • the unit 32 remains stationary during this process, as it is held in the neutral position by means of the locking element 18, which engages in an engagement region 19 of the unit 32.
  • a first switching spring 35 and a first return spring 36 is tensioned.
  • the sliding sleeve 10 is fixed in the first switching position by means of a locking element 20.
  • the locking element 20 engages in a first recess 37 of a carrier 38.
  • the carrier 38 is rotatably coupled to the sliding sleeve 10 and formed axially displaceable with this as a unit.
  • the locking element 18 is released, as a result of which the tensioned first switching spring 35 moves the unit 32 or the first coupling element 28 on the drive side, so that the first coupling element 28 engages with the housing 31.
  • the ring gear 24 is now rotatably coupled to the housing 31.
  • the locking element 20 For decoupling the locking element 20 is released, whereby the first return spring 36 moves the carrier 38 together with the sliding sleeve 10 on the output side in the central neutral position. Since the unit 32 is coupled to the sliding sleeve 10 via the first switching spring 35, and the first coupling element 28 is moved from the engaged position back to the idle position.
  • the output side planet carrier 27 by means of the second coupling element 29 rotatably coupled to the sun gear 23 and the drive shaft 5 rotationally fixed.
  • the second coupling element 29 and the unit 32 is displaced on the output side until a second toothing 39 arranged on the unit 32, namely the second coupling element 29, engages with a planet carrier toothing 40 arranged on the front side.
  • the second switching operation is analogous to the first switching operation, wherein as a difference to the first switching operation opposite output-side displacement of the sliding sleeve 10, the carrier 38 and, at a later time, the second coupling element 29.
  • the switching device 1, a second switching spring 41 and a second return spring 42.
  • the second return spring 42 is oriented opposite to the first return spring 36 in the axial direction of the planetary gear 22 opposite. The same applies to the second switching spring 41 and the first switching spring 35.
  • the sliding sleeve 10 has only a single shift groove 13.
  • the sliding sleeve but also have a plurality of switching grooves corresponding respectively with at least one adjusting means such that the sliding sleeve with a corresponding design of the shift groove from the neutral position in the first and second switching position and moved back to the neutral position becomes.
  • at least one of the two return springs 36, 42 could be saved.
  • FIG. 3 shows an alternative embodiment of the planetary gear 22 is shown, in which the switching device 1 is formed such that the rotatable masses are reduced.
  • the circuit of the two stages in a common direction in particular by an output side displacement of the sliding sleeve 10 and the first and second coupling element 28, 29th
  • the first coupling element 28 is decoupled from the rotation of the sliding sleeve 10 by means of a bearing 30 by being rotatably coupled in the region of its radially outer toothing with a housing, not shown here, and to this axially displaceable. Further, the first coupling element 28 is coupled to the carrier 38 of the sliding sleeve 10, which in turn is rotatably mounted on the sliding sleeve 10. For non-rotatable coupling of the ring gear 24 with the housing, not shown here is the first coupling element 28 shifted on the output side, so that the coupling teeth of the first coupling element 28 with the ring gear 24 come into engagement. The first coupling element 28 thus has no rotatable masses.
  • the rotatable masses of the second coupling element 29 were reduced.
  • the second coupling element 29 is formed in two parts.
  • a radially inner first part 43 is rotatably coupled to the sun gear 23 and to the drive shaft 5 and coupled to this axially displaceable.
  • the radially outer second part 44 is decoupled from this rotation by means of the bearing 30.
  • the second part 44 is coupled to the likewise decoupled from the rotation support 38 of the sliding sleeve 10.
  • Each of the two coupling elements 28, 29 is associated with its own locking unit 17a, 17b, so that they can be unlocked independently of each other to carry out the switching operation.
  • the two locking units 17a, 17b and the jointly formed for both switching stages locking unit of the locking member 20 herein comprise each a switching pin 45, a pivotally formed hook member 46 and designed as a paragraph 47 engaging portion 19.
  • a switching pin 45 a switching pin 45
  • a pivotally formed hook member 46 designed as a paragraph 47 engaging portion 19.
  • the adjusting means 1 1 is introduced into the shift groove 13. Due to the rotatable coupling of the sliding sleeve 10 with the drive shaft 5 and the corresponding helical configuration of the shift groove 13, the sliding sleeve 10 is displaced on the output side.
  • the return spring 1 5 is present both the first coupling element 28 and the second coupling element ment 29 assigned.
  • the actuating means 11 is led out of the shift groove 13 by active actuation or else by corresponding reduction in the depth of the shift groove 13.
  • the spring energy of the first and second switching spring 35, 41 is thus stored by the locking of the sliding sleeve 10 in the switching position and by the locking of the first and second coupling elements 28, 29 in the idle position in the system.
  • the stored spring energy can be released by releasing one of the two locking units 17a, 17b.
  • only one of the locking units 17a, 17b is always released at any time, but both at the same time.
  • the second coupling element 29 shifts from its idle position into the engaged position.
  • the teeth arranged on the face side of the rotatably coupled to the sun gear 23 first part 43 of the second coupling element 29 come into meshing engagement with the planet carrier 27, so that the sun gear 23 is rotatably coupled to the planet carrier 27.
  • the locking element 20 is deactivated at a given time, so that the sliding sleeve 10 is pushed with its carrier 38 from the switching position back to the neutral position.
  • This is done in particular by means of the return spring 15, the spring-loaded the sliding sleeve 10 in the direction of its neutral position.
  • the switching spring 35, 41 of the non-switched coupling element act in the present example, the first coupling element 29, as a return spring. Since the first switching spring 35 has thus not been released in the present exemplary switching operation, it acts on the carrier 38 and thus also on the sliding sleeve 10 with a spring force which is oriented on the drive side.
  • the return spring 15 could also be saved as a pushing back of the sliding sleeve 10 in the neutral position and the second coupling element 29 in the neutral position could be done with the first switching spring 35. As soon as the second coupling element 29 is again in the neutral position, it is automatically locked by means of the locking unit 17b.
  • Figure 4 shows a third embodiment of a planetary gear 22, the drive side is formed substantially in accordance with the second embodiment shown in Figure 3.
  • this third embodiment has no separate return spring 15 (see Figure 3). Instead acts here, as already stated above, the switching spring 35, 41 of the respective unlocked coupling element 28, 29 as return spring 15 for the sliding sleeve 10 and for each shifted in the engaged position coupling element 28, 29. Further, the sliding sleeve 10 with its carrier 38 formed in one piece.
  • the sliding sleeve 10 is completely decoupled in the embodiment shown in Figure 4 of the rotation of the drive shaft 5.
  • the shift groove 13 is not formed on the sliding sleeve 10, but on the outer circumference 12 of the drive shaft 5.
  • the adjusting means 1 1 is fixedly connected to the sliding sleeve 10, so that it is designed to be displaceable relative to the drive shaft 5 in the axial direction of the planetary gear 22.
  • Figure 5 shows a fourth embodiment of the planetary gear 22, wherein the output-side region is formed substantially identical to the second and third embodiments.
  • the main difference is that the drive energy of the drive shaft 5 can be transmitted to a countershaft 50 by means of a spur gear 48 and a controllable clutch 49.
  • an output-side circuit of the planetary gear 22 is made possible.
  • the sliding sleeve 10 does not rotate continuously, but is selectively moved by means of the clutch 49 between the neutral position and the switching position. Accordingly, the clutch closes to initiate the shift Operation, whereby the drive power of the drive shaft 5 is transmitted to the countershaft 50.
  • the rotationally fixed and axially displaceable coupled to the countershaft 50 sliding sleeve 10 is moved by the engaging adjusting means 1 1 from the neutral position to the switching position on the output side.
  • the first and second switching spring 35, 41 and the return spring 15 are tensioned.
  • the clutch 49 disengages, so that no more drive energy is transmitted from the drive shaft 5 to the countershaft 50.
  • the actuating means 1 1 thus acts as a locking element. After coupling one of the two coupling elements 28, 29 this and the sliding sleeve 10 can be brought by the release of the actuating means 1 1 and the locking member 20 back to the neutral position or the neutral position.
  • the force required for this purpose is applied by the return spring 15 as in the previous embodiments.
  • FIGS. 6a-6d A fifth exemplary embodiment of the planetary gear 22 storable for switching energy is shown in FIGS. 6a-6d.
  • the planetary gear 22 comprises a first coupling element 28 and a second coupling element 29.
  • the two Koppeleiemente 28, 29 together form a displaceable in the axial direction of the planetary gear 22 unit 32 from. They are further formed rotatable by means of the bearing 30 to each other.
  • the first coupling element 28 is rotatably coupled in a first coupling region 51 with the housing of the planetary gear 22, not shown here and slidably coupled thereto in the axial direction.
  • the second coupling element 29 is in contrast to the sun gear 23 rotatably coupled and slidable in the axial direction.
  • the first coupling element 28 is formed stationary, whereas the second coupling element 29 is able to rotate with the sun gear due to the rotationally fixed coupling in the second coupling region 52.
  • the ring gear 24 is rotatably coupled by means of the first coupling element 28 with the stationary housing.
  • the first coupling element 28 or the unit 32 which comprises the first coupling element 28, the second coupling element 29 and the bearing 30, on the drive side, ie in the direction of the drive shaft 5, moved.
  • the switching operation of the switching device 1 takes place according to the method visualized in FIGS. 6a-6d. Accordingly, starting from the neutral position shown in Figure 6a of the switching device 1, in which none of the two coupling elements 28, 29 is active, according to Figure 6b for rotatably coupling the ring gear 24 to the stationary housing, first the adjusting means 1 1 in a shift groove 13 of the drive shaft 5 introduced.
  • the sliding sleeve 10 is thus completely decoupled from the rotation of the drive shaft 5, since the shift groove 13 is not formed on the sliding sleeve 10, but on the outer circumference 12 of the drive shaft 5.
  • the adjusting means 1 1 is fixedly connected to the sliding sleeve 10, so that it is designed to be displaceable relative to the drive shaft 5 in the axial direction of the planetary gear 22.
  • the sliding sleeve 10 is moved with the adjusting means 1 1, the carrier 38 and a first stop element 54 as a displacement unit due to the helical shift groove 13 from the neutral position to the output-side switching position according to Figure 6b.
  • the unit 32 remains stationary during this process, as it is held in the neutral position by means of the locking element 18, which engages in an engagement region 19 of the unit 32.
  • a first switching spring 35 and a first return spring 36 of the switching device 1 is tensioned.
  • the first switching spring 35 is tensioned between the first stop element 54 and the first coupling element 28, relative to which the first stop element 54 is designed to be displaceable in the axial direction.
  • the return spring 36 is stretched between the carrier 38 and the housing-fixed base 1 6b.
  • the locking member 18 is unlocked according to Figure 6d for non-rotatable coupling of the housing, not shown here with the ring gear 24, whereby the tensioned or charged first switching spring 35, the unit 32 and the first coupling element 28 moves on the drive side, so that the first toothing 33 of first coupling element 28 with the ring gear teeth 53 comes into meshing engagement.
  • the ring gear 24 is now rotatably coupled to the housing of the planetary gear 22, not shown here, wherein the two shift springs 35, 41 are both relieved and only the first return spring 36 is under tension.
  • the locking element 20 For decoupling the locking element 20 must be released or disengaged from the recess 37, whereby the tensioned first return spring 36, the carrier 38 along with the sliding sleeve 10 on the output side in the back in Fig. 6a shown central neutral position.
  • the first coupling element 28 is displaced from the engagement position back into the idle position, since the unit 32 is coupled via the second stop element 55 and the second switching spring 41 to the carrier 38 or the sliding sleeve 10.
  • the first toothing 33 of the first coupling element 28 thus no longer engages in the ring gear teeth 53 of the ring gear 24.
  • the second switching operation for the rotationally fixed coupling of the sun gear 23 to the planet carrier 27 via the meshing of the second toothing 39 of the second coupling element 29 in the planet carrier toothing 40 of the planet carrier 27 is substantially mirrored in an analogous manner. Accordingly, the sliding sleeve 10 - when reversing the direction of rotation of the drive shaft 5 or at a second with a formed in comparison to the first shift groove 13 with an inverse pitch angle second shift groove - the drive side in the direction of the output shaft 6 moves as soon the adjusting means 1 1 engages in the switching groove 13.
  • the second switching spring 41 in particular by the displacement of the second stop element 55, and the second return spring 42 tensioned, since the unit 32 are held in its neutral position due to the locking element 18.
  • the second switching spring 41 releases its spring energy, whereby the second coupling element 29 is displaced on the output side and the second toothing 39 engages in the planetary toothing 40.
  • the sun gear 23 and the planet carrier 27 are now rotatably coupled together.
  • the locking element 20 For decoupling the locking element 20 is released, whereby the tensioned second return spring 42, the carrier 38 together with the sliding sleeve 10 on the output side boastverschiebt back to the central neutral position.
  • the second coupling element 29 is displaced from the engagement position back into the idle position, since the unit 32 is coupled via the first stop element 54 and the first shift spring 35 to the carrier 38 or the sliding sleeve 10.
  • the second toothing 39 of the second coupling element 29 thus no longer engages in the planet carrier toothing 40.
  • the main advantage of the fifth embodiment shown in Figures 6a-6d is that all electronic switching parts, i. the adjusting means 1 1, the locking element 18 and the locking member 20 are decoupled from the rotation. Furthermore, the locking element 18 and the locking element 20 is fixedly coupled to the housing. Furthermore, the switching device 1 has rotationally symmetrical components which are not interlaced. In addition, the switching device 1 may be formed as a preassembled module which can be mounted on a planetary gear 22. Also, the structural implementation according to the fifth embodiment allows only the switching pins of the actuators, i. of the actuating means 1 1, the locking element 18 and the locking element 20, are arranged in the oil chamber. The spring assemblies can be designed for both switching 35, 41 and / or return springs 36, 42 with different forces.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

L'invention concerne un dispositif de commutation (1) pour un engrenage planétaire (22), comportant un manchon coulissant (10) qui peut être déplacé par l'action d'un moyen de régulation (11) dans la direction axiale de l'engrenage planétaire (22) d'une position neutre dans une position de commutation, au moins un élément de couplage (4) qui peut être déplacé pour rendre solidaires en rotation deux éléments (2; 3) de l'engrenage planétaire (22) dans la direction axiale de l'engrenage planétaire (22) d'une position de point mort dans une position de prise, et au moins un ressort de commutation (14) qui couple le manchon coulissant (10) et au moins un élément de couplage (4) l'un à l'autre de telle sorte que, en cas de déplacement du manchon coulissant (10) de la position neutre dans la position de commutation, l'élément de couplage (4) est sollicité par le ressort en direction de l'élément (3) à coupler avec celui-ci. Selon l'invention, le dispositif de commutation (1) comporte un ensemble de verrouillage (17) qui maintient l'élément de couplage (4) dans l'état verrouillé dans la position de point mort de telle sorte que l'énergie du ressort peut être stockée lorsque le manchon coulissant (10) est déplacé dans la position de commutation et libérée à un moment donné par le déverrouillage de l'ensemble de verrouillage (17).
PCT/EP2013/073467 2012-12-19 2013-11-11 Dispositif de commutation pour engrenage planétaire WO2014095157A1 (fr)

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DE102012223792.5A DE102012223792A1 (de) 2012-12-19 2012-12-19 Schalteinrichtung für ein Planetengetriebe
DE102012223792.5 2012-12-19

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CN113236772A (zh) * 2021-04-30 2021-08-10 华南理工大学 一种变挡装置及其组成的助力器械
DE102021207134A1 (de) 2021-07-07 2023-01-12 Zf Friedrichshafen Ag Drehmomentübertragungsvorrichtung zur Übertragung eines Drehmoments von einer Eingangswelle auf eine koaxial zu der Eingangswelle angeordneten Ausgangswelle
DE102021210676A1 (de) 2021-09-24 2023-03-30 Zf Friedrichshafen Ag Kopplungsvorrichtung für ein Kraftfahrzeug
DE102022109199B4 (de) 2022-04-14 2024-01-25 Schaeffler Technologies AG & Co. KG Schiebevorrichtung und Vorrichtung zum Koppeln und Entkoppeln zweier Wellen sowie elektrische Achsantriebsvorrichtung für ein hybrides oder elektrisches Fahrzeug
DE102022109198B4 (de) 2022-04-14 2024-02-01 Schaeffler Technologies AG & Co. KG Schiebevorrichtung und Vorrichtung zum Koppeln und Entkoppeln zweier Wellen und elektrische Achsantriebsvorrichtung für ein hybrides oder elektrisches Fahrzeug
SE546267C2 (en) * 2022-12-21 2024-09-17 Scania Cv Ab A coupling arrangement

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DE19917673A1 (de) * 1999-04-19 2000-10-26 Zahnradfabrik Friedrichshafen Schalteinrichtung eines zweistufigen Planetengetriebes
DE102008000635A1 (de) * 2008-03-13 2009-09-17 Zf Friedrichshafen Ag Anordnung zur Betätigung zumindest einer Schalteinrichtung eines Getriebes
WO2011072945A1 (fr) * 2009-12-18 2011-06-23 Zf Friedrichshafen Ag Dispositif de commutation pour une boîte de vitesses à engrenages

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GB325263A (en) * 1928-11-15 1930-02-17 John Neville Morris Improvements in means for facilitating the changing of gears on motor vehicles
DE1128715B (de) * 1959-12-03 1962-04-26 Zahnradfabrik Friedrichshafen Durch AEnderung der Antriebsdrehrichtung schaltbares Umlaufraedergetriebe
US4449416A (en) * 1981-09-04 1984-05-22 J. I. Case Company Transmission control system
DE10241006A1 (de) * 2002-09-05 2004-03-25 Zf Friedrichshafen Ag Elektromagnetische Schalteinrichrung eines zweistufigen Planetengetriebes

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DE19917673A1 (de) * 1999-04-19 2000-10-26 Zahnradfabrik Friedrichshafen Schalteinrichtung eines zweistufigen Planetengetriebes
DE102008000635A1 (de) * 2008-03-13 2009-09-17 Zf Friedrichshafen Ag Anordnung zur Betätigung zumindest einer Schalteinrichtung eines Getriebes
WO2011072945A1 (fr) * 2009-12-18 2011-06-23 Zf Friedrichshafen Ag Dispositif de commutation pour une boîte de vitesses à engrenages

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