WO2015135453A1 - 双离合结构减速器 - Google Patents

双离合结构减速器 Download PDF

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Publication number
WO2015135453A1
WO2015135453A1 PCT/CN2015/073875 CN2015073875W WO2015135453A1 WO 2015135453 A1 WO2015135453 A1 WO 2015135453A1 CN 2015073875 W CN2015073875 W CN 2015073875W WO 2015135453 A1 WO2015135453 A1 WO 2015135453A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
clutch device
output shaft
driven
drive
Prior art date
Application number
PCT/CN2015/073875
Other languages
English (en)
French (fr)
Inventor
张天才
安红磊
雷艳清
Original Assignee
天佑电器（苏州）有限公司
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 天佑电器（苏州）有限公司 filed Critical 天佑电器（苏州）有限公司
Priority to US15/125,281 priority Critical patent/US10006495B2/en
Priority to EP15761293.8A priority patent/EP3127417B1/en
Publication of WO2015135453A1 publication Critical patent/WO2015135453A1/zh

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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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
    • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
    • 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
    • A01D69/08—Clutches
    • 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
    • F16D11/14—Clutches in which the members have interengaging parts with clutching members movable only axially
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D2101/00—Lawn-mowers
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/126—Actuation by rocker lever; Rocker levers therefor
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/11—Application
    • F16D2500/1102—Lawnmower

Definitions

  • the invention relates to a transmission which adopts a self-propelled machine and adopts a double clutch structure to realize smooth transmission of the transmission, reduce the impact force of the transmission transmission component, and reduce the vibration of the whole machine during the clutch clutching process.
  • the transmission is mainly used for a self-propelled machine, such as a propeller mower, which is a friction ring or a friction plate drive.
  • a self-propelled machine such as a propeller mower
  • U.S. Patent No. US2003006074 discloses a transmission including a drive member on which the drive member is mounted.
  • the friction ring is driven, and further comprises a follower, and the driven friction ring is arranged on the follower.
  • the power of the driving member comes from the pulley connected to the transmission belt.
  • the driven friction ring moves axially to the position combined with the driving friction ring, and the driving friction ring transmits the power to the driven friction ring, and the driven friction ring drives the output shaft. Rotate.
  • the transmission mode is simple in structure and low in cost, but it lacks reliability, and the drive mechanism and the driven mechanism are prone to relative sliding, which cannot guarantee the transmission ratio.
  • the self-propelled machine encounters a large resistance, the two are prone to relative sliding, and the friction generates a large amount of thermal energy, resulting in a decrease in the strength and durability of the part, and even deformation of the part, and if the gear transmission is directly used as the clutch, when the clutch is engaged When the high-speed rotating drive unit is combined, the clutch gear is easy to wear due to the impact. This phenomenon is called “toothing”. The more the gear clutching “toothing” phenomenon, the more serious the wear, resulting in poor transmission or failure.
  • the patent publication No. US201214550 discloses a transmission having a speed reduction mechanism including a worm gear 6 in which a worm 5 and a worm 5 are fitted (see Patent FIG. 1), and a drive tooth on the worm wheel It is rotatably mounted on the output shaft 2 and has a friction clutch mechanism 7 including a tapered friction ring 7A fixedly coupled to the output shaft 2 and a tapered friction ring 7B rotating synchronously with the worm wheel, and a gear clutch Mechanism 8, wherein the gear clutch mechanism 8 can be toggled from the disengaged position to the engaged position by the clutch paddles in the axial direction.
  • a gear-type structure for accommodating a U-shaped pin is disposed in the gear clutch mechanism 8, and a U-shaped pin insertion hole is disposed on the output shaft 2, and the U-shaped pin transmits power to the output shaft 2 when the gear mechanism 8 and the worm wheel 6 are engaged.
  • the elastic piece 10 is disposed on the output shaft, the elastic piece moves axially with the gear mechanism 8, the end of the elastic piece interferes with the middle of the worm wheel, and the axial outward movement of the worm wheel 6 causes the tapered friction rings 7A and 7B to be combined (refer to FIG. 4 and Figure 5) At this point the output shaft 2 is driven by the friction ring to achieve pre-drive.
  • the gear 8 continues to move into the cavity of the gear mechanism 8 at a position where the worm gear 6 is engaged. At this time, a reliable gear transmission is realized between the worm 5 and the output shaft 2.
  • the solution not only ensures the transmission ratio of the transmission, but also reduces the impact force generated when the transmission is clutched.
  • the disadvantage of this technical solution is that the friction clutch mechanism 7 needs the axial movement of the elastic piece 10 to realize the combination and separation, the structure is complicated, and the friction clutch mechanism 7 is disposed outside the worm wheel. When the friction clutch mechanism 7 is combined and separated, the worm wheel also needs the axial direction. mobile.
  • the present invention aims to provide a new speed reduction mechanism which can reduce the impact generated when the clutch is engaged, and can ensure the transmission ratio, in particular, can simplify the structure of the transmission.
  • the present invention provides a dual clutch structure reducer comprising:
  • a housing for accommodating all components, the interior of the housing is provided with a speed reduction mechanism, and the speed reduction mechanism includes a driving device and a slave device coupled with the driving device;
  • the driven device is mounted on the output shaft for free rotation about the output shaft;
  • the first clutch device is synchronously rotatably mounted on the output shaft and movable along the output shaft at the combined position and the separated position;
  • the first clutch device is driven by the driven device when the position is engaged, while the first clutch device drives the output shaft;
  • a second clutch device is rotatably mounted on the output shaft and movable along the output shaft at the combined position and the separated position;
  • the second clutch device engages with the driven device when the position is engaged, and drives the output shaft;
  • a clutch control device that simultaneously operates the first and second clutch devices to move along the output shaft at the combined position and the separated position
  • the first clutch device is always coupled earlier than the second clutch device, transmitted to the second clutch device through the output shaft to initiate the rotational speed, and is always separated later than the second clutch device;
  • the first clutch device is axially disposed between the driven device and the second clutch device;
  • the first clutch device and the second clutch device are coaxially and synchronously rotatably coupled;
  • the clutch control device moves the first clutch device from the disengaged position in the axial direction of the second clutch device to the coupling position when the second clutch device is moved from the disengaged position to the engaged position.
  • the first clutch device has a clutch drive that cooperates therewith, the clutch drive member being mated coaxially and synchronously with the output device.
  • the first clutch device is disposed in a cavity corresponding to its outer shape in the interior of the second clutch device, and the clutch drive device is disposed in a cavity of the interior of the driven device and its shape.
  • the clutch drive and the first clutch are driven using a friction structure.
  • the output shaft and the active friction member are driven by pins and pin holes provided on the output shaft.
  • the clutch drive device is disposed in a cavity that conforms to its outer shape inside the driven device.
  • the cavity of the driven device has an elastic member built in, so that the clutch drive device can elastically slide along the output shaft in the cavity.
  • the cavity of the driven device is provided with at least one slotted structure that is slidable by the clutch drive.
  • the second clutch device is provided with an elastic positioning member, and when the second clutch device is in the combined position, the positioning member is mated with the positioning groove disposed on the output shaft.
  • the elastic positioning member is U-shaped and is inserted into a mounting hole provided outside the second clutch device.
  • the clutch control device includes a fork portion built in the housing and an operation panel extending outside the housing, the operation panel having an elastic returning member, and the operation of the clutching is performed outside the housing through the operation panel.
  • the present invention does not need to separately provide a control device for the first and second clutch structures, and the present invention uses a clutch control device to operate the second clutch device while using the second clutch device to push the first clutch device to be combined.
  • the clutch structure is simpler.
  • the first clutch device is mounted in the cavity of the second clutch device, and the clutch drive device is mounted in the cavity of the driven device such that the volume occupied by the clutch device is reduced.
  • the first clutch device is combined with the second clutch device, and the first clutch device gives the second clutch device initial starting speed through the output shaft, so that the second clutch device that is combined later reduces the phenomenon of "toothing".
  • the second clutch device and the driven device are driven in a stable meshing manner, thereby ensuring the gear ratio.
  • the first clutch is disposed between the second clutch and the driven device, and the combination of the first clutch relies on the pushing of the second clutch, and the driven device does not need to move in the axial direction, which increases the operational stability of the speed reducing device.
  • the speed reducer of the present invention has a small volume, a simpler structure, stable operation, and can ensure a transmission ratio.
  • 1 is a schematic exploded view of the embodiment of the dual clutch structure reducer of the embodiment.
  • Figure 2 is a schematic cross-sectional view of the double clutch structure reducer
  • FIG 3 is an exploded perspective view of the first clutch device and the second clutch device.
  • FIG. 4 is a schematic view showing the first clutch device and the second clutch device in a separated state.
  • Fig. 5 is a schematic view showing a state in which the first clutch device is coupled.
  • Figure 6 is a schematic view showing the state of bonding of the second clutch device.
  • the transmission 1 is capable of operating between a source power input shaft 11 and a power take-off shaft 12, which is typically used in self-propelled equipment.
  • a source power input shaft 11 For example, in a self-propelled mower, power is transmitted to a pulley 2 mounted on an input shaft through a transmission belt (not shown), and the power is outputted by the power take-off shaft 12 through a transmission shift.
  • the travel wheel of the self-propelled device is driven by the power take-off shaft 12.
  • the rotational speed of the output shaft 12 is smaller than the rotational speed of the input shaft, and the torque is greater than the input shaft 11.
  • the transmission has a housing 10 which is connected by a joint surface by two half-shells, the housing is usually made of an alloy material; the transmission 1 further has a speed reduction mechanism 13; the first clutch device 14 and the second clutch device 15 The clutch control device 16.
  • the speed reduction mechanism further includes a driving device and a driven device, the driving device is a worm 18, the driven device is a worm wheel 19, the worm is disposed at a lower end of the input shaft 11, the worm wheel 19 has a driving tooth 191 on an end surface thereof, and the turbine 19 is mounted on the output shaft It is free to rotate around the output shaft 12.
  • the clutch control device 16 can be combined or disengaged with the second clutch device when the second clutch device is operated to move in the combined position and the disengaged position in the axial direction.
  • the first clutch device 14 is a friction member having a tapered structure
  • the first clutch device has a convex convex surface 141
  • the same clutch driving device 21 is also a friction member having a tapered structure
  • the clutch driving device has a concave cone. Face 211.
  • the clutch drive device 21 rotates synchronously with the worm wheel. Both the first clutch device 14 and the clutch drive device 21 are mounted on the output shaft 12 and can be moved closer to or away from each other under the control of the clutch control device 16.
  • the convex tapered surface 141 of the tapered front end portion of the first clutch device 14 enters the concave tapered surface 211 of the clutch driving device 21 (refer to FIG. 3).
  • the first clutch device 14 and the clutch drive device 21 are in mutually separated positions.
  • the second clutch device 15 has a hollow clutch chamber 151, the inner surface of which is provided with a plurality of groove-shaped structures 152 in the axial direction, and the first clutch device 14 is provided with an axial direction corresponding to the groove-shaped structure 152.
  • the extended bumps 212 are mounted in the second clutch device 15 and the bumps 212 are mated in the channel structure 152.
  • the end face of the second clutch device 15 is provided with a driven tooth 154 which meshes with the drive tooth 191 on the worm wheel 19 when it is in its engaged position.
  • the worm wheel 19 drives the second clutch device to rotate, and the second clutch device is driven to rotate from the first clutch device 14 by the slot structure 152 described above, and the first clutch device 14 further drives the output shaft 12 to rotate.
  • the first clutch device 14 drives the output shaft 12 through a pin 121 disposed on the output shaft.
  • the main body portion of the pin is inserted into the pin hole 122 disposed on the output shaft, and the pin hole extends in the output shaft in the radial direction.
  • Two mutually parallel pins 121 are provided.
  • a sliding slot 144 is provided in the first clutch device 14 for receiving the pin. When the first clutch device 14 moves in the axial direction, the pin can slide in the sliding slot 144, and the pin 121 is opposite to the first clutch device.
  • the axial sliding of 14 has a guiding effect.
  • An annular groove 155 is provided on the second clutch device adjacent the driven tooth 154, the annular groove being operable by the clutch control device 16 to move the clutch in the disengaged position and the engaged position.
  • a U-shaped elastic member 22 mounting portion is provided, the mounting portion has four protrusions, and the through hole 157 is formed in the protrusion, and the leg portion 221 of the U-shaped elastic member 22 is provided. Inserted into the hole, a wedge-shaped barb 158 is also disposed near the top. When the bottom portion 222 of the U-shaped spring member passes over the barb, the barb keeps its position stable and does not retract.
  • the mounting portion is not limited to the above structure, and a groove structure or the like known to those skilled in the art may be employed.
  • An annular groove 123 for receiving the leg portion 221 of the U-shaped elastic member 22 is also provided on the output shaft.
  • the retarder is also provided with a clutch control device 16 that operates the first clutch device 14 and the second clutch device 15 to move from the disengaged position to the engaged position.
  • the clutch control device 16 includes a fork portion 161 built in the casing and an operation plate 17 provided outside the casing, and the fork portion 161 is mounted in a direction substantially perpendicular to the extending direction of the output shaft.
  • the fork portion 161 is rotatable about its axis at an angle, and the second clutch device 15 follows the fork portion 16 to move along the output shaft when the fork portion rotates.
  • the fork portion has upper and lower branches forming a substantially semi-circular opening between the upper branch and the lower branch, and a vertically downward lower hook portion 164 on the upper branch and a vertical portion on the lower branch Upward hook portion 165.
  • the upper hook portion 164 and the lower hook portion 165 are inserted into the annular groove 155 of the second clutch device, and when the fork portion 161 is rotated, the second clutch device 15 can be moved to move along with the first clutch device 14 following the second The clutch device 15 moves.
  • the housing 10 is provided with a mounting hole of the fork portion 161.
  • the fork portion has an upwardly extending rod 166.
  • the extension rod is mounted on the housing by a bearing, and an upper portion of the extension rod extends outside the housing.
  • An operation panel 17 is provided, which is coupled to an extension rod 166 located outside the housing.
  • the operation panel 17 is further provided with a return spring 171 for assisting the return of the second clutch device 15 to the disengaged position.
  • the clutch movement can be operated outside the housing by the operation panel 17 to be in a combined or disengaged state, and the leg portion 221 of the U-shaped elastic member 22 is caught in the annular groove 123 on the output shaft when the clutch is in the engaged state.
  • the second clutch device 15 is prevented from retracting along the axis.
  • a worm gear 19 is disposed on the output shaft 12 opposite to the second clutch device 15, and the outer circumference of the worm wheel has a worm gear 192 for receiving power from the worm, and the worm 18 and the worm gear are driven to reduce the speed.
  • the output speed of the worm wheel 19 is lower than that of the worm, and the output torque is greater than that of the worm.
  • the worm wheel 19 is provided with driving teeth 191 on the end surface of the second clutch device, and the second clutch device is engaged with the driving teeth 191.
  • the worm wheel 19 has a worm gear cavity 193 (refer to FIG.
  • the metal insert 4 is integrally provided with an outer ring wall 41 and an inner ring wall 42.
  • the outer surface of the outer ring wall is provided with a rib 43 adapted to the groove 196 in the cavity, and the rib extends in the axial direction, and is assembled. Upon completion, the ribs are mated within the recess 196.
  • the inner surface of the outer ring wall 41 is provided with a similar groove extending in a direction parallel to the output shaft.
  • the inner ring wall 42 has a smooth surface, and the inner ring wall has a through hole 44 penetrating through the metal insert through which the metal insert is sleeved on the output shaft.
  • the worm wheel 19 is formed by an injection molding process, and the metal insert 4 is embedded in the worm wheel cavity 193 in the middle of the worm wheel, whereby the metal insert 4 pieces can rotate synchronously with the worm wheel 19 when the worm drive worm wheel rotates.
  • a coil spring 46 is mounted in the metal insert 4 as an elastic member for sliding the clutch driving device 21, the diameter of which is slightly larger than the diameter of the inner ring wall 42, and the coil spring 46 is sleeved outside the inner ring wall 42.
  • the clutch driving device 21 is sleeved in the metal insert, the length of the clutch driving device 21 is slightly smaller than the length of the metal insert 4, and the outer surface has a strip-shaped slider, and the slider is matched with the groove provided on the inner surface of the outer ring wall 41.
  • the clutch drive 21 is driven to rotate with the metal insert 4.
  • One end of the coil spring 46 abuts against the bottom of the metal insert 4, and the other end abuts against the baffle 48 extending radially inward of the clutch drive (refer to FIG. 5), thereby moving the first clutch device 14 toward the clutch drive 21, the clutch drive 21 is slidable within the metal insert 4, and as the first clutch device 14 moves further, the pressure and friction experienced by the tapered surface 141 are further increased. Therefore, the clutch drive device 21 can transmit its rotation through the tapered friction surface to the first clutch device and drive the power output shaft 12 to rotate together.
  • the turbine 19 described above is powered by a worm 18 disposed in the housing, and the drive worm 181 at the bottom of the worm meshes with the worm gear 192 on the worm gear.
  • the housing 10 has a hole through which a worm passes to pass the worm, and the worm is mounted on the hole through a bearing.
  • a pulley 2 is mounted at the end of the outer worm, and power from an internal combustion engine or motor or other power unit is delivered to the worm 18 through the belt.
  • the transmission is in an initial state
  • the second clutch device 15 is disposed coaxially with the first friction member
  • the axial length of the first clutch device 14 is greater than the second clutch device
  • the end of the first clutch device 14 extends out of the second clutch.
  • the end face of the device 15 is inserted into the hole of the output shaft, and both ends thereof enter the sliding groove 144 of the first clutch device 14.
  • the hook portion 165 and the lower hook portion 164 of the fork portion 161 of the clutch control device 16 are caught in the annular groove 155 of the first clutch device 14, and the control plate 17 is stopped at the initial position by the return spring 171, and the fork portion 161
  • the second clutch device 14 is held in the separated position, and the first clutch device 14 is also in the separated state.
  • the convex cone surface 141 and the concave cone surface 211 of the clutch driving device 21 are in a separated state. The distance is small, so the fork portion 161 can be slightly rotated.
  • the first clutch device 14 and the clutch drive device 21 are combined.
  • the clutch driving device 21 is disposed coaxially with the worm wheel 19, and the clutch driving device 21 is sleeved in the metal insert 4.
  • the coil spring 46 is located between the metal insert and the clutch driving device 21, and the spring is in an initial state without deformation.
  • the length of the clutch driving device 21 is smaller than the length of the metal insert 4, and the concave tapered surface 211 is located in the worm wheel cavity 193, and the bottom of the clutch driving device 21 has a slidable space to the bottom of the metal insert 4, when the first 1.
  • the clutch drive device 21 slides left and right along the spacing space.
  • the transmission When the transmission is in the initial state, the external power is transmitted to the worm 18 through the pulley 2, the worm drives the worm wheel to rotate, the clutch drive device 21 also rotates synchronously, the clutch drive device 21 and the first clutch device are in a separated state, and the output shaft 12 is also in Static state.
  • the clutch control unit 16 is rotated from the outside by the operation panel 17, and the fork portion 161 is moved to move the second clutch device 15, and the second clutch device is axially moved toward the worm wheel 19, and the first clutch device 14 is
  • the two clutch device pushes 15 are also axially moved toward the clutch drive 21, and both ends of the pin 121 slide along the chute 144.
  • the leg portion 221 of the U-shaped elastic member is radially expanded perpendicularly to the output shaft 12, and the leg portion 221 of the U-shaped elastic member has a clamping force to the output shaft 12.
  • the front portion of the first clutch device 14 enters the worm gear cavity 193 of the worm gear, and the outer convex cone surface 141 of the first clutch device 14 interferes with the concave tapered surface 211 of the clutch drive device 21.
  • the axial movement of the first clutch device 14 pushes the clutch drive device 21 to slide within the metal insert 4, and the clutch drive device 21 slides a distance greater than or equal to the sliding distance of the second clutch device 15 from the disengaged position to the meshing position with the worm wheel 19. the distance.
  • the coil spring 46 is gradually compressed, and its elastic force acts on the second clutch device 15, and pressure is formed on the tapered contact faces of the first clutch device 14 and the clutch drive device 21.
  • the first clutch device 14 causes the output shaft 12 to start rotating by the pin 121, and the second clutch device 15 rotates at the same angular velocity.
  • the rotational speeds of the first clutch device 14 and the output shaft 12 are lower than the rotational speed of the clutch drive device 21, and as the first clutch device 14 moves further, the tapered contact
  • the frictional force of the surface increases as the elastic force increases, and the corresponding first clutch device 14 also gradually increases in rotational speed.
  • the first clutch device 14 is continuously moved from the state of FIG. 4, and the clutch driving device 21 continues to move to the bottom of the metal insert.
  • the first clutch device 14 and the clutch drive device 21 are rotated at the same speed, and the same clutch drive device 21 is used. It is close to the rotational speed of the worm wheel 19.
  • the first clutch device 14 and the clutch drive device 21 are further moved, and the rotational speed of the second clutch device 15 can be in the same state as or close to the rotational speed of the worm wheel 19, at which time the first clutch device 14 and the worm wheel 19 mesh.
  • the life of the gear can be prolonged.
  • the transmission has a sealed housing 10 that is filled with a lubricant that smoothes the clutch operation.
  • the present invention does not need to provide a control device for the first and second clutch structures, and the present invention uses a clutch control device to operate the second clutch device while using the second clutch device to push the first clutch device to be combined. Therefore, the clutch structure is simpler.
  • the first clutch device is mounted in the cavity of the second clutch device, and the clutch drive device is mounted in the cavity of the driven device such that the volume occupied by the clutch device is reduced.
  • the first clutch device is combined with the second clutch device, and the first clutch device gives the second clutch device initial starting speed through the output shaft, so that the second clutch device that is combined later reduces the phenomenon of "toothing".
  • the second clutch device and the driven device are driven in a stable meshing manner, thereby ensuring the gear ratio.
  • the first clutch is disposed between the second clutch and the driven device, and the combination of the first clutch relies on the pushing of the second clutch, and the driven device does not need to move in the axial direction, which increases the operational stability of the speed reducing device.
  • the turbine of the present invention is made of a plastic material for the purpose of manufacturing cost and structural strength, and a metal insert is provided in the worm wheel cavity 193, and the clutch drive device 21 is used.
  • the clutch driving device 21 of the present invention can elastically expand and contract in the worm wheel 19, and the first clutch device 14 and the two clutch device 15 are fixedly disposed, and the first clutch device 14 slides to the inside of the worm wheel when the clutch is combined.
  • the first clutch device 14 can be elastically slid in the first clutch device, and the clutch drive device 21 is fixedly disposed with the worm wheel 19, and the clutch drive device 21 enters the cavity when the clutch is engaged.
  • the clutch drive device 21 enters the cavity when the clutch is engaged.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Environmental Sciences (AREA)
  • Mechanical Operated Clutches (AREA)
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Abstract

一种双离合结构减速器，具有源动力输入轴（11），和动力输出轴（12）；第一离合装置（14）和第二离合装置（15）；第一离合装置（14）和第二离合装置（15）可轴向的在分离位置和结合位置移动；第一离合装置（14）总是早于第二离合装置（15）结合，并总是晚于第二离合装置（15）分离；所述的第一离合装置（14）轴向地设置在从动装置（19）和第二离合装置（15）之间；所述的第一离合装置（14）与第二离合装置（15）同轴、同步转动；离合控制装置（16），操作第二离合装置（15）轴向的从分离位置移动至结合位置时，第一离合装置（14）被第二离合装置（15）轴向的从分离位置推动至结合位置；该减速器具有较小的体积，结构更简单，运行稳定，并能够保证传动比。

Description

双离合结构减速器 技术领域
本发明涉及一种变速器，该变速器应用自推进机械，采用双离合结构，实现变速器的平稳传动，降低变速器传动部件的冲击力，减轻变速器离合过程中整机的震动。
背景技术
变速器主要用于自推进机械，例如推进割草机，传统变速器采用摩擦环或摩擦片传动，例如专利公开号为US2003006074的美国专利公开了一种变速器，其包括一个驱动件，驱动件上安装有驱动摩擦环，还包括一个从动件，从动件上设置有从动摩擦环。驱动件的动力来自与传动皮带连接的带轮，当离合结合时从动摩擦环沿轴向移动至与驱动摩擦环结合的位置，驱动摩擦环将动力传递至从动摩擦环，从动摩擦环带动输出轴旋转。此种传动方式结构简单成本低，但其缺乏可靠性，驱动机构和从动机构容易产生相对滑动无法保证传动比。当自推进机械遇到较大阻力时，二者容易产生相对滑动，摩擦产生大量的热能，导致零件的强度和耐性降低，甚至零件发生变形，而如果直接使用齿轮传动装置作为离合，当离合与高速转动的驱动装置结合时，离合的齿轮容易因为撞击产生磨损，此种现象称为“打齿”，齿轮离合“打齿”现象越多磨损就越严重，造成传动效果不佳或失效。
为解决上述摩擦离合和齿轮离合的上述问题，专利公开号为US201214550公开了一种变速器，其具有减速机构包括蜗杆5和蜗杆5配合的蜗轮6(参见专利附图1)，蜗轮上具有驱动齿并可自由旋转的安装在输出轴2上，其具有摩擦离合机构7，摩擦离合机构包括与输出轴2固定连接的锥形摩擦环7A和与蜗轮同步旋转的锥形摩擦环7B，和齿轮离合机构8，其中齿轮离合机构8能够被离合拨片沿轴向从分离位置拨动到结合位置。齿轮离合机构8内设置用于容纳U形销的槽型结构，输出轴2上设置U形销插孔，齿轮机构8和蜗轮6啮合时U形销将动力传递至输出轴2。在输出轴上设置弹片10，弹片随齿轮机构8轴向移动，弹片的端部与蜗轮的中间抵触，蜗轮6轴向的向外蹿动使锥形摩擦环7A和7B结合(参照图4和图5)此时在摩擦环的作用下输出轴2实现预传动。齿轮8继续移动至于蜗轮6啮合的位置弹片10进入齿轮机构8的腔体内。此时蜗杆5和输出轴2之间实现可靠的齿轮传动。相对于仅靠摩擦传动的减速机构，该方案既保证了变速器的传动比，又降低了变速器离合时产生的冲击力。该技术方案的缺点是摩擦离合机构7需要弹片10轴向的移动实现结合与分离，其结构复杂，并且摩擦离合机构7设置在蜗轮外侧，摩擦离合机构7结合和分离时，蜗轮同样需要轴向移动。
因此本法明旨在提供一种新的减速机构，其能够降低离合器离合时产生的冲击，又能够保证传动比，特别是能够简化变速器的结构。
发明内容
为解决上述问题本发明提供一种双离合结构减速器，包括：
源动力输入轴，和动力输出轴；
用于容纳所有部件的壳体，壳体的内部设置减速机构，减速机构包括驱动装置和与驱动装置配接从动装置；
所述从动装置安装在输出轴上绕输出轴自由的转动；
第一离合装置，同步转动地安装在输出轴上，并可沿输出轴在结合位置和分离位置移动；
第一离合装置在结合位置时其由从动装置驱动，同时第一离合装置驱动输出轴；
第二离合装置，同步转动地安装在输出轴上，并可沿输出轴在结合位置和分离位置移动；
第二离合装置在结合位置时与从动装置啮合，并驱动输出轴；
离合控制装置，其同时操作第一和第二离合装置沿着输出轴在结合位置和分离位置移动；
第一离合装置总是早于第二离合装置结合，通过输出轴传递给第二离合装置以启动转速，并总是晚于第二离合装置分离；
所述的第一离合装置轴向地设置在从动装置和第二离合装置之间；
所述的第一离合装置与第二离合装置同轴、同步转动地配接；
离合控制装置，操作第二离合装置轴向的从分离位置移动至结合位置时，第一离合装置被第二离合装置轴向的从分离位置推动至结合位置。
优选地，第一离合装置具有与其配合的离合驱动装置，所述离合驱动件与从动装置同轴、同步转动地配接。
优选地，所述的第一离合装置设置在第二离合装置的内部与其外形一致腔体中，所述的离合驱动装置设置在从动装置内部与其外形一直的腔体中。
优选地，所述的离合驱动装置和第一离合装置使用摩擦结构传动。
优选地，所述的输出轴和主动摩擦件通过设置在输出轴上销和销孔传动。
优选地，所述的离合驱动装置设置在从动装置内部与其外形一致的腔体内。
优选地，从动装置的腔体内置弹性构件，使离合驱动装置可弹性的在腔体内沿输出轴滑动。
优选地，从动装置的腔体设置可供离合驱动装置滑动的至少一个槽型结构。
优选地，第二离合装置上设置弹性定位件，第二离合装置处于结合位置时，定位件与设置在输出轴上的定位槽配接。
优选地，弹性定位件呈U型并插装在第二离合装置外侧设置的安装孔内。
优选地，离合控制装置包括内置在壳体中的拨叉部和延伸到壳体外的操作板，所述的操作板具有弹性复位件，操作离合的动作通过操作板在壳体外部实施。
本发明相对现有技术具有以下优点：
本发明相对现有的减速器，不需要为第一第二离合结构分别设置控制装置，本发明采用一个离合控制装置操作第二离合装置，同时利用第二离合装置推动第一离合装置结合，因此离合结构更为简单。
第一离合装置安装在第二离合装置的腔体内，离合驱动装置安装在从动装置的腔体内，使得离合装置的所占体积减小。
第一离合装置先于第二离合装置结合，第一离合装置通过输出轴给予第二离合装置初始启动转速，使在后结合的第二离合装置减少“打齿”的现象。
第二离合装置与从动装置采用稳定的啮合方式传动，因此能够保证传动比。
第一离合设置在第二离合和从动装置之间，第一离合的结合依靠第二离合的推动，而从动装置在轴向上无需移动，增加了减速装置的运行稳定性。
因此，本发明的减速器具有较小的体积，结构更简单，运行稳定，并能够保证传动比。
附图说明
图1是实施例双离合结构减速器零件分解示意图。
图2是双离合结构减速器整机剖面示意图
图3是第一离合装置和第二离合装置分解示意图。
图4是第一离合装置和第二离合装置都处于分离状态示意图。
图5是第一离合装置结合状态示意图。
图6是第二离合装置结合状态示意图。
具体实施方式
下面结合附图对本发明做进一步详细的说明。
参照图1和图2，变速器1能够在源动力输入轴11和动力输出轴12之间工作，其通常用于自行机械设备中。例如在自行割草机中动力通过传动带(图中未示出)传递至安装在输入轴上的带轮2上，经过变速器变速，由动力输出轴12输出动力。常规地，由动力输出轴12驱动自行机械设备的行驶轮。为了适于行走，在自行机械设备的应用中输出轴12的转速小于输入轴的转速，其扭力大于输入轴11。
变速器具有壳体10，壳体是通过两个半壳体通过结合面连接在一起，壳体通常采用合金材料制成；变速器1还具有减速机构13；第一离合装置14和第二离合装置15、离合控制装置16。减速机构进一步包括 驱动装置和从动装置，驱动装置是蜗杆18，从动装置是蜗轮19，所述的蜗杆设置在输入轴11的下端，所述蜗轮19端面上具有驱动齿191，涡轮19安装在输出轴上可自由的绕输出轴12转动。离合控制装置16，操纵第二离合装置轴向的在结合位置和分离位置移动时，蜗轮19可与第二离合装置结合或分离。所述的第一离合装置14是具有锥形结构的摩擦件，第一离合装置具有外凸锥面141，同样的离合驱动装置21也是具有锥形结构的摩擦件，离合驱动装置具有内凹锥面211。所述的离合驱动装置21与蜗轮同步旋转，第一离合装置14和离合驱动装置21都安装在输出轴12上，并且可以在离合控制装置16的操纵下相互靠近或远离。第一离合装置14和离合驱动装置21结合时，第一离合装置14的锥形前端部分的外凸锥面141进入离合驱动装置21的内凹锥面211中(参照图3)。参照图4第一离合装置14和离合驱动装置21处于相互分离的位置。
参照图3第二离合装置15具有中空的离合腔151，其内表面沿轴向设置了多个槽型结构152，第一离合装置14上设置了与该槽型结构152相适应的沿轴向延伸的凸块212，第一离合装置14安装在第二离合装置15内，凸块212配接在槽型结构152中。第二离合装置15的端面上设置从动齿154，该从动齿在其结合位置时与蜗轮19上的驱动齿191啮合。第二离合装置15啮合时蜗轮19驱动第二离合装置转动，第二离合装置通过上述的槽型结构152驱动离第一离合装置14旋转，第一离合装置14进一步的驱动输出轴12转动。第一离合装置14通过设置在输出轴上的销121驱动输出轴12，销的主体部分插在设置在输出轴上的销孔122内，销孔沿径向在输出轴内延伸，本实施例设置两个相互平行的销121。第一离合装置14内设置了用于容纳所述销的滑槽144，第一离合装置14沿轴向移动时，所述销可在该滑槽144内滑动，同时销121对第一离合装置14的轴向滑动具有导向作用。与从动齿154相邻地第二离合装置上设置有环形槽155，所述环形槽可供离合控制装置16操纵以使离合在分离位置和结合位置移动。在第二离合装置15的另一端面上设置了U形弹性件22安装部，该安装部具有4个凸起，凸起上设置通孔157，所述的U形弹性件22的腿部221插装在所述的孔内，在靠近顶部的还设置了一楔形的倒钩158。当U形弹簧件底部222越过倒钩时，该倒钩使其位置保持稳定不会回退，该安装部不限于上述结构还可以采用本领域技术人员公知的槽型结构等。在输出轴上还设置了用于接纳U形弹性件22腿部221的环形凹槽123。
减速器还设置有离合控制装置16，其操纵第一离合装置14和第二离合装置15从分离位置移动至结合位置。离合控制装置16包括内置在壳体中的拨叉部161和设置在壳体外部的操作板17组成，拨叉部161安装方向与输出轴的延伸方向大致垂直。拨叉部161可绕其轴沿一定角度转动，拨叉部转动时第二离合装置15跟随拨叉部16转移沿输出轴移动。所述拨叉部具有上、下两个分支在上分支和下分支之间形成一大致呈半圆形的开口，在上分支上具有垂直向下的下钩部164，在下分支上具有竖直向上的上钩部165。所述的上钩部164和下钩部165插入第二离合装置的环形槽155，当拨叉部161转动时其可拨动第二离合装置15随之移动，同时第一离合装置14跟随第二离合装置15移动。壳体10上设置有拨叉部161的安装孔，拨叉部具有向上的延伸杆166，延伸杆通过轴承安装在壳体上，延伸杆的上部延伸至壳体外。在壳体外部 设置有操作板17，操作板17与位于壳体外部的延伸杆166配接，操作板17上还设置复位弹簧171，复位弹簧171是用于帮助第二离合装置15恢复至分离位置。由此，可以通过操作板17在壳体外部操作离合移动使其处于结合或分离状态，当离合处于结合状态时所述U形弹性件22腿部221卡入输出轴上的环形凹槽123内，防止第二离合装置15沿轴回退。当人为地使用操作板17使离合分离，U形弹性件22腿部221从环形凹槽123内脱出，此时在复位弹簧171的作用下第二离合装置回到起始位置。
参照图1至3，在输出轴12上与第二离合装置15相对的方向设置有蜗轮19，蜗轮的外周具有用于接收来自蜗杆动力的蜗齿192，蜗杆18与蜗轮传动的过程即降低转速的过程，所述蜗轮19的输出的转速低于蜗杆，其输出的扭力大于蜗杆。蜗轮19朝向第二离合装置的端面上设置驱动齿191，第二离合装置与驱动齿191啮合时，。所述蜗轮19中间具有蜗轮腔193(参照图5)，腔体内表面设置沿轴向延伸的凹槽196，在蜗轮腔193内安装有金属嵌件4。该金属嵌件4一体的设置外环壁41和内环壁42，外环壁外表面上设置与所述的腔体内的凹槽196相适应的凸条43，凸条沿轴向延伸，装配完成时，凸条配接在所述的凹槽196内。外环壁41的内表面设置类似的凹槽，其延伸方向与输出轴平行。内环壁42具有光滑的表面，内环壁内部是贯穿金属嵌件的通孔44，金属嵌件通过该通孔套设在输出轴上。在本实施例中蜗轮19采用注塑工艺制作，金属嵌件4嵌入在蜗轮中间的蜗轮腔193，由此蜗杆驱动蜗轮转动时金属嵌4件可与蜗轮19同步转动。在金属嵌件4内安装有螺旋弹簧46，作为离合驱动装置21滑动的弹性件，其直径略大于内环壁42的直径，螺旋弹簧46套设在内环壁42外。离合驱动装置21套设在金属嵌件内，离合驱动装置21的长度略小于金属嵌件4的长度，其外表面具有条状滑块，滑块与外环壁41内表面设置的凹槽配接并驱使离合驱动装置21随金属嵌件4转动，。螺旋弹簧46的一端抵住金属嵌件4的底部，另一端抵住离合驱动装置径向向内延伸的挡板48上(参照图5)，由此当第一离合装置14移向离合驱动装置21，离合驱动装置21可在金属嵌4件内滑动，并且随着第一离合装置14的进一步移动，锥面141受到的压力和摩擦力也进一步增大。因此，离合驱动装置21可将其转动通过锥形摩擦面传递至第一离合装置，并带动动力输出轴12一同转动。
上述的涡轮19动力来自设置在壳体的蜗杆18，蜗杆底部的驱动蜗齿181与蜗轮上的蜗齿192啮合。壳体10上具有蜗杆使蜗杆穿过的孔，蜗杆通过轴承安装在孔上。在壳体外蜗杆的端部安装有带轮2，来自内燃机或电机或其他动力装置的动力通过传动带输送给蜗杆18。
参照图4变速器处于初始状态，第二离合装置15与第一摩擦件同轴设置，第一离合装置14的轴向长度大于第二离合装置，第一离合装置14的端部伸出第二离合装置15的端面，销121插在输出轴的孔上，其两端进入第一离合装置14的滑槽144内。此时离合控制装置16拨叉部161上钩部165和下钩部164卡在第一离合装置14的环形槽155内，控制板17在复位弹簧171的作用下停靠在初始位置，拨叉部161使第二离合装置14保持在分离位置，同时，第一离合装置14也处于分离状态，第一离合装置14处于分离位置时其外凸的锥面141与离合驱动装置21的内凹锥面211距离微小，因此拨叉部161轻微的转动即可 使第一离合装置14和离合驱动装置21结合。离合驱动装置21与蜗轮19同轴设置离合驱动装置21套设在金属嵌件4内，上述的螺旋弹簧46位于金属嵌件和离合驱动装置21之间，弹簧处于无形变初始状态。所述的离合驱动装置21长度小于金属嵌件4的长度，其内凹锥面211处于蜗轮腔193内，离合驱动装置21的底部到金属嵌件4的底部具可滑动的间距空间，当第一、第二离合装置进行分离或结合时离合驱动装置21沿间距空间左右滑动。变速器处于初始状态时，外部动力通过带轮2传递给蜗杆18，蜗杆带动蜗轮转动，离合驱动装置21也做同步转动，离合驱动装置21和第一离合装置都处于分离状态，输出轴12也处于静上的状态。
参照图4，通过操作板17从外部转动离合控制装置16，拨叉部161拨动第二离合装置15，所述的第二离合装置轴向地向蜗轮19移动，第一离合装置14被第二离合装置推动15同样轴向地向离合驱动装置21移动，所述的销121两端沿滑槽144滑动。U型弹性件的腿部221垂直于输出轴12径向地撑开，U型弹性件的腿部221对输出轴12具有夹持力。第一离合装置14的前部进入蜗轮的蜗轮腔193，第一离合装置14外凸锥面141与离合驱动装置21的内凹锥面211抵触。所述第一离合装置14轴向的移动推动离合驱动装置21在金属嵌件4内滑动，离合驱动装置21滑动的距离大于等于第二离合装置15从分离位置到与蜗轮19啮合位置所需要滑动的距离。螺旋弹簧46逐渐压缩，其弹力作用于第二离合装置15，第一离合装置14和离合驱动装置21的锥形接触面上形成压力。在离合驱动装置21内凹锥面211的摩擦作用下，第一离合装置14通过销121使输出轴12开始转动，第二离合装置15以同样的角速度转动。通常在第一离合装置14和离合驱动装置21开始结合时，第一离合装置14和输出轴12的转速低于离合驱动装置21的转速，并且随着第一离合装置14进一步移动，锥形接触面的摩擦力随弹力的增大而增大相应的第一离合装置14转速也逐渐增大。
参照图5从图4所在的状态继续移动第一离合装置14，离合驱动装置21继续移动到金属嵌件的底部，第一离合装置14与离合驱动装置21的转速接近，同样的离合驱动装置21与蜗轮19的转速接近。进一步移动第一离合装置14和离合驱动装置21，第二离合装置15的转速可以与蜗轮19的转速一致或接近的状态，此时第一离合装置14和蜗轮19啮合。同转速下的驱动齿191啮合时不会存在“打齿”的现象能够延长齿轮的使用寿命。第二离合装置与蜗轮啮合后其动力蜗杆19和输出轴12之间形成齿轮传动，其具有稳定高效的特点，能够保证传动比。所述的U形弹性件22的腿部221进入设置在输出轴的环形凹槽123内，将第二离合装置卡在其结合的位置上，U形弹性件22的卡位的作用能够平衡复位弹簧171对操作板17的拉力，并防止离合装置退回分离位置。当采用较大的外力操作操作板17来分离离合时，U形弹性件22又能够从环形凹槽123中顺利脱出，此时在复位弹簧的作用下第二离合装置可回复至分离位置。变速器的具有密封的壳体10，壳体内填充润滑剂，润滑剂使离合的操作顺畅。
总之，本发明相对现有的减速器，不需要为第一第二离合结构分别设置控制装置，本发明采用一个离合控制装置操作第二离合装置，同时利用第二离合装置推动第一离合装置结合，因此离合结构更为简单。 第一离合装置安装在第二离合装置的腔体内，离合驱动装置安装在从动装置的腔体内，使得离合装置的所占体积减小。第一离合装置先于第二离合装置结合，第一离合装置通过输出轴给予第二离合装置初始启动转速，使在后结合的第二离合装置减少“打齿”的现象。第二离合装置与从动装置采用稳定的啮合方式传动，因此能够保证传动比。第一离合设置在第二离合和从动装置之间，第一离合的结合依靠第二离合的推动，而从动装置在轴向上无需移动，增加了减速装置的运行稳定性。
上述的实施例是本发明一较佳的实施例，但本发明的保护范围不限于此。遵照本发明精神还可以做等效的更改或替换，例如：出于制造成本和结构强度的考虑，本发明的涡轮采用塑料材料制成，蜗轮腔193内设置金属嵌件，离合驱动装置21使用金属制成；同样的第二离合装置15使用塑料件制成，其内部的第一离合装置14使用金属件；通过本发明的启示可以知道以下改进方案，①蜗轮19采用金属件制造，蜗轮腔193直接形成可供第二离合装置15滑动的腔，从而省略金属嵌件4的减少结构复杂度；②将第二离合件和第一离合装置14采用金属件制造从而降低第二离合装置15的结构复杂度。本发明的采用离合驱动装置21可在蜗轮19内弹性的伸缩，第一离合装置14与二离合装置15固定设置，离合结合时第一离合装置14滑动至蜗轮内部。作为一种变换方案，可以设置第一离合装置14可弹性的在第一离合装置内滑动，离合驱动装置21与蜗轮19固定设置，当离合结时离合驱动装置21进入的腔内。③还可以在第一离合装置上设置内凹锥面，相对的在离合驱动装置上设置外凸锥面。因此本发明保护范围应当以说明书为准凡根据本发明权利要求的实质精神所做的更改和等效替换均在本发明的保护范围内。

Claims (11)

  1. 双离合结构减速器，包括：
    源动力输入轴，和动力输出轴；
    用于容纳所有部件的壳体，壳体的内部设置减速机构，减速机构包括驱动装置和与驱动装置配接从动装置；
    所述从动装置安装在输出轴上绕输出轴自由的转动；
    第一离合装置，同步转动地安装在输出轴上，并可沿输出轴在结合位置和分离位置移动；
    第一离合装置在结合位置时其由从动装置驱动，同时第一离合装置驱动输出轴；
    第二离合装置，同步转动地安装在输出轴上，并可沿输出轴在结合位置和分离位置移动；
    第二离合装置在结合位置时与从动装置啮合，并驱动输出轴；
    离合控制装置，其同时操作第一和第二离合装置沿着输出轴在结合位置和分离位置移动；
    第一离合装置总是早于第二离合装置结合，并总是晚于第二离合装置分离；
    其特征在于：
    所述的第一离合装置轴向地设置在从动装置和第二离合装置之间；
    所述的第一离合装置与第二离合装置同轴、同步转动；
    所述的离合控制装置，操作第二离合装置轴向的从分离位置移动至结合位置时，第一离合装置被第二离合装置轴向的从分离位置推动至结合位置。
  2. 根据权利要求1所述双离合结构减速器，其特征在于，第一离合装置具有与其配合的离合驱动装置，所述离合驱动件与从动装置同轴、同步转动地配接。
  3. 根据权利要求2所述双离合结构减速器，其特征在于，所述的第一离合装置设置在第二离合装置的内部与其外形一致腔体中，所述的离合驱动装置设置在从动装置内部与其外形一直的腔体中。
  4. 根据权利要求2所述的双离合结构减速器，其特征在于，所述的离合驱动装置和第一离合装置使用摩擦结构传动。
  5. 根据权利要求3所述的双离合结构减速器，其特征在于，所述的输出轴和主动摩擦件通过设置在输出轴上销和销孔传动。
  6. 根据权利要求5所述的双离合结构减速器，其特征在于，所述的离合驱动装置设置在从动装置内部与其外形一致的腔体内。
  7. 根据权利要求3所述的双离合结构减速器，其特征在于，所述的从动装置的腔体内置弹 性构件，使离合驱动装置可弹性的在腔体内沿输出轴滑动。
  8. 根据权利要求7所述的双离合结构减速器，其特征在于，所述从动装置的腔体设置可供离合驱动装置滑动的至少一个槽型结构。
  9. 根据权利要求1所述的双离合结构减速器，其特征在于，所述的第二离合装置上设置弹性定位件，第二离合装置处于结合位置时，定位件与设置在输出轴上的定位槽配接。
  10. 根据权利要求8所述的双离合结构减速器，其特征在于，所述的弹性定位件呈U型并插装在第二离合装置外侧设置的安装孔内。
  11. 根据权利要求1所述的双离合结构减速器，其特征在于，所述的离合控制装置包括内置在壳体中的拨叉部和延伸到壳体外的操作板，所述的操作杆具有弹性复位件，操作离合的动作通过操作板在壳体外部实施。
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