CN106337908B - Torque transmission device and power tool with the torque transmission device - Google Patents
Torque transmission device and power tool with the torque transmission device Download PDFInfo
- Publication number
- CN106337908B CN106337908B CN201510406636.0A CN201510406636A CN106337908B CN 106337908 B CN106337908 B CN 106337908B CN 201510406636 A CN201510406636 A CN 201510406636A CN 106337908 B CN106337908 B CN 106337908B
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- ring
- central axis
- locking
- gear
- ring gear
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 38
- 230000000149 penetrating effect Effects 0.000 claims description 2
- 230000006835 compression Effects 0.000 claims 2
- 238000007906 compression Methods 0.000 claims 2
- 206010040007 Sense of oppression Diseases 0.000 abstract 3
- 238000010586 diagram Methods 0.000 description 4
- 230000004323 axial length Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000007935 neutral effect Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
Classifications
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- 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
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- 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
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- 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
- F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Abstract
The invention discloses a kind of torque transmission devices, including：Operate ring, ring gear and locking piece, operation ring can be around a center axis thereof, and ring gear can moving radially along central axis around center axis thereof, locking piece；Wherein, ring gear is formed with：Internal tooth and external tooth, internal tooth are set to the inner circumferential of ring gear, and external tooth is set to the periphery of ring gear；Locking piece is formed with the lock tooth and closing piece being oppositely arranged on radially of the central axis；Operation ring is formed with：Oppression department and release portion, oppression department, which can oppress locking piece, makes lock tooth coordinate with external tooth, and the closing piece that release portion can accommodate locking piece makes lock tooth disengage the cooperation with external tooth；Central axis radially, locking piece is set between operation ring and ring gear, and in the side of ring gear, the closing piece of locking piece is located at the side for operating ring for the lock tooth position of locking piece；In the circumferential direction of central axis, the circumferential position different in operation ring is arranged in oppression department and release portion.The torque transmission device of the present invention can realize high low speed switching.
Description
Technical Field
The invention relates to the field of power tools, in particular to a torque transmission device in a power tool.
Background
In prior art power tools, a torque transmission device, such as a gear box, is typically provided between the prime mover and the output system to reduce the rotational speed. In order to realize a gearbox with different transmission ratios, the prior art usually realizes locking and unlocking of the circumferential position of the inner gear ring by movement of the inner gear ring in the axial direction. Meanwhile, in order to prevent the planetary gear system from being locked to damage components during the switching of high and low speeds, a neutral gear is usually required to be arranged between the high and low speed gears. However, the axial displacement of the inner gear ring will be undoubtedly increased, which will result in an increase in the axial length of the gear box, and thus an increase in the size of the power tool, which is not beneficial to the user.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention aims to provide a torque transmission device capable of realizing high-speed and low-speed switching.
In order to achieve the above object, the present invention adopts the following technical solutions:
a torque transmitting device comprising:
the operating ring can rotate around a central axis;
the gear ring can rotate around the central axis;
a locking member movable in a radial direction of the central axis;
wherein,
the ring gear is formed with:
inner teeth provided on an inner periphery of the ring gear;
outer teeth provided on the outer periphery of the ring gear;
the locking piece is provided with a locking tooth and a locking block which are oppositely arranged in the radial direction of the central axis;
the operation ring is formed with:
a pressing part which can press the locking piece to enable the locking teeth to be matched with the external teeth;
a release portion capable of receiving the lock piece of the locking member to disengage the lock teeth from the external teeth;
in the radial direction of the central axis, the locking piece is arranged between the operating ring and the gear ring, the locking tooth of the locking piece is positioned on one side of the gear ring, and the locking block of the locking piece is positioned on one side of the operating ring;
the pressing portion and the releasing portion are provided at different circumferential positions of the operation ring in a circumferential direction of the central axis.
Further, the torque transmission device further includes:
a guide for limiting a circumferential position of the locking member;
the guide member includes:
a guide groove penetrating the guide member in a radial direction of the central axis;
the locking member is at least partially inserted into the guide groove.
Further, the guide groove includes: the distance between the two guide inclined planes is gradually reduced from outside to inside along the radial direction of the central axis; the locking piece includes: and the limiting inclined planes can be respectively arranged in parallel with the two guide inclined planes.
Further, the pressing part comprises a circular arc-shaped pressing wall surface; the relief portion includes a relief groove recessed radially outward of the pressing wall surface substantially along the central axis.
Furthermore, the number of the locking pieces is even, and the even locking pieces are symmetrically arranged relative to the central axis; the number of the releasing portions is the same as the number of the locking pieces.
Further, the pressing portion and the releasing portion are provided at an interval in a circumferential direction of the central axis.
Further, the torque transmission device further includes:
a drive member including a first wheel portion and a second wheel portion;
a planet wheel, which can be matched with the second wheel part;
the wheel carrier is provided with a mounting shaft which can rotatably mount the planet wheel;
the planet wheel and the first wheel part are both provided with transmission teeth which can be matched with the internal teeth of the gear ring.
Further, the air conditioner is provided with a fan,
when the operating ring rotates to a position where the lock teeth are disengaged from the external teeth, the gear ring moves to a first position where the gear ring is engaged with both the planet gear and the first gear portion in a direction parallel to the central axis;
when the operating ring is rotated to a position in which the locking teeth engage with the external teeth, the ring gear is moved in a direction parallel to the central axis to a second position in which it engages only with the planet wheels.
Further, the torque transmission device further includes:
the connecting piece can drive the gear ring to move along the direction parallel to the central axis when the operating ring rotates;
the ring gear includes:
a gear tooth portion forming an inner tooth and an outer tooth;
the wheel groove part is formed on the outer edge of the gear ring and is matched with the connecting piece;
the outer teeth and the wheel grooves are arranged at different axial positions of the ring gear.
The invention also provides a power tool comprising the torque transmission device.
The invention has the advantages that: the torque transmission device realizes high-low speed switching by locking the circumferential position of the gear ring, and the gear ring can be directly switched between high-low speed gears without setting a neutral gear, thereby reducing the axial size of the torque transmission device.
Drawings
FIG. 1 is a schematic structural view of a power tool in accordance with a preferred embodiment of the present invention;
FIG. 2 is a schematic view of a partial structure of the interior of the power tool of FIG. 1;
FIG. 3 is a schematic cross-sectional view of the structure of FIG. 2 taken along line A-A, with the locking element locking the circumferential position of the toothed ring;
FIG. 4 is a cross-sectional view of the arrangement of FIG. 2 taken along line A-A, with the locking element disengaged from the toothed ring;
FIG. 5 is a view showing a positional relationship between the guide member and the locking member;
FIG. 6 is a diagram showing the positional relationship between the ring gear, the driving member, the planetary gears, the wheel carrier and the connecting member, wherein the ring gear is simultaneously engaged with the first wheel portion of the driving member and the planetary gears;
FIG. 7 is a cross-sectional view of the structure of FIG. 6 taken along line B-B;
FIG. 8 is a diagram showing the positional relationship among the ring gear, the driving member, the planetary gears, the wheel carrier, and the connecting member, in which the ring gear is engaged with only the planetary gears;
FIG. 9 is a cross-sectional view of the structure of FIG. 8 taken along line C-C;
FIG. 10 is a structural relationship diagram of a portion of the torque transmitting device with the shaft lock assembly and the torque adjustment assembly;
fig. 11 is a diagram showing the positional relationship among the next-stage planetary gear, the next-stage ring gear, the next-stage operating ring, and the next-stage locking member;
fig. 12 is a schematic structural view of the shaft lock bracket of fig. 10.
Detailed Description
The invention is described in detail below with reference to the figures and the embodiments.
The invention provides a torque transmission device and a power tool with the same.
FIG. 1 is a schematic structural view of a power tool according to a preferred embodiment of the present invention; fig. 2 is a schematic view showing a partial structure of the interior of the power tool of fig. 1. Referring to fig. 1 and 2 together, the power tool 100 includes: prime mover 10, torque transmission device 20, and output member 30, wherein torque transmission device 20 is configured to transmit power output by prime mover 10 to output member 30.
FIG. 3 is a schematic cross-sectional view of the structure of FIG. 2 taken along line A-A, showing the locking element locking the circumferential position of the toothed ring; fig. 4 is a cross-sectional view of the arrangement of fig. 2 taken along line a-a, with the locking element out of engagement with the toothed ring. Referring to fig. 1-4 together, the torque transmitting device 20 of the present invention includes: an operating ring 11, a toothed ring 12 and a locking element 13.
The operating ring 11 is rotatable about a central axis, and preferably the operating ring 11 is substantially annular in configuration with the central axis passing through the center of the annular configuration. The ring gear 12 is also rotatable about the central axis of the operating ring 11, and preferably, the ring gear 12 is also substantially annular in configuration, with the center of the ring gear 12 being on the central axis of the operating ring 11, i.e., the ring gear 12 and the operating ring 11 are rotatable coaxially. The locking member 13 is movable in the radial direction of the central axis. To describe the technical solution of the present invention, the following definitions are particularly made, where a direction in which the central axis is located is an axial direction, a circumferential direction around the central axis is a circumferential direction, and a direction perpendicular to the central axis and intersecting the central axis is a radial direction.
The ring gear 12 is formed with internal teeth 121 and external teeth 122, the internal teeth 121 being provided on the inner periphery of the ring gear 12, and the external teeth 122 being provided on the outer periphery of the ring gear 12. The locking member 13 is formed with a locking tooth 131 and a locking piece 132, and the locking tooth 131 and the locking piece 132 are arranged opposite to each other in the central axial direction. The operation ring 11 is formed with a pressing portion 111 and a releasing portion 112. As shown in fig. 3, the pressing portion 111 can press the locking member 13 so that the locking teeth 131 of the locking member 13 engage with the external teeth 122, thereby locking the circumferential position of the ring gear 12. As shown in fig. 4, the release portion 112 can receive the lock piece 132 of the locking member 13 so that the lock teeth 131 can be disengaged from the outer teeth 122. So that the locking member 13 can be moved in the radial direction by the pressing portion 111 and the releasing portion 112 of the operation ring 11.
In the radial direction of the central axis, the locking member 13 is disposed between the operating ring 11 and the ring gear 12, the locking teeth 131 of the locking member 13 are located on the side of the ring gear 12, and the locking pieces 132 of the locking member 13 are located on the side of the operating ring 11. That is, in the radial direction of the central axis, the locking teeth 131 are closer to the ring gear 12 than the locking pieces 132, and the locking pieces 132 are closer to the operating ring 11 than the locking teeth 131.
The pressing portion 111 and the releasing portion 112 are provided at different circumferential positions of the operation ring 11 in the circumferential direction of the central axis. Thus, when the operation ring 11 is rotated about the center axis, the pressing portion 111 and the releasing portion 112 can be sequentially brought into contact with the locking member 13.
Therefore, when the operation ring 11 is rotated about the central axis to the position shown in fig. 3, the pressing portion 111 of the operation ring 11 is in contact with the lock piece 132 of the lock member 13, and the pressing portion 111 presses the lock member 13 so that the lock teeth 131 of the lock member 13 engage with the external teeth 122 of the ring gear 12, and at this time, the ring gear 12 is locked with respect to the circumferential position of the lock member 13. When the operating ring 11 is rotated about the central axis to the position shown in fig. 4, the releasing portion 112 of the operating ring 11 contacts the locking piece 132 of the locking member 13, and the releasing portion 112 allows the locking teeth 131 of the locking member 13 to disengage from the external teeth 122 of the ring gear 12, so that the ring gear 12 can be rotated about the central axis relative to the locking member 13. In this way, the locking and releasing of the ring gear 12 can be achieved by the rotation of the operating ring 11, so that different rotation states can be provided for the transmission members inside the ring gear 12 which engage with the internal teeth 121 thereof, thereby achieving the switching of the torque transmission device 20 at high and low speeds. Therefore, the locking piece 13 which can lock or unlock the gear ring 12 is arranged at the same axial position of the gear ring 12, so that the problem that the axial length of the torque transmission device 20 is increased and the axial size of the power tool 100 is increased due to the fact that a neutral gear is arranged to prevent blocking in the prior art is solved.
To achieve this, the torque transmission device 20 further comprises a guide 14, the guide 14 being adapted to limit the circumferential position of the locking element 13. Fig. 5 is a view showing a positional relationship between the guide member and the locking member. Referring to fig. 3 to 5, the guide member 14 includes a guide groove 141, the guide groove 141 penetrates the guide member 14 in a radial direction of the central axis direction, and the locking member 13 is at least partially inserted into the guide groove 141 in a direction parallel to the central axis direction. Further, the guide groove 141 includes two opposite guide inclined surfaces 141a, a distance between the two guide inclined surfaces 141a gradually decreases from outside to inside along a radial direction of the central axis, the corresponding locking member 13 also includes two opposite limiting inclined surfaces 133, and the two limiting inclined surfaces 133 are respectively disposed in parallel with the corresponding guide inclined surfaces 141 a. In this way, the circumferential position of the locking member 13 can be locked with respect to the guide member 14, so that the locking member 13 can lock the circumferential position of the ring gear 12.
In order that the locking teeth 131 of the locking member 13 engage with the external teeth 122 of the ring gear 12 when the pressing portion 111 is in contact with the locking pieces 132 of the locking member 13, and the locking teeth 131 of the locking member 13 disengage from the external teeth 122 of the ring gear 12 when the releasing portion 112 is in contact with the locking pieces 132 of the locking member 13, the pressing portion 111 further includes a pressing wall surface 111a, and the releasing portion 112 further includes a releasing groove. Specifically, the pressing wall surface 111a of the pressing portion 111 is an arc centered on the central axis, and the relief groove is recessed outward from the pressing wall surface 111a substantially in the radial direction of the central axis, and more preferably, the relief groove includes a relief wall surface 112a, and the relief wall surface 112a is also an arc centered on the central axis. That is, the release wall surface 112a of the release groove is located at a distance from the central axis greater than the pressing wall surface 111a of the pressing portion 111, so that, when the operation ring 11 is rotated, the locking member 13 can be moved in the radial direction of the central axis to a position where it is engaged with or disengaged from the external teeth 122 of the ring gear 12 because different portions of the operation ring 11 are in contact with the locking pieces 132.
Preferably, the number of the locking pieces 13 is even, the even number of the locking pieces 13 are symmetrically arranged with respect to the central axis, the number of the releasing portions 112 is the same as the number of the locking pieces 13, and the pressing portions 111 and the releasing portions 112 are arranged at intervals in the circumferential direction of the central axis. Thus, when the operation ring 11 is rotated, the pressing portion 111 and the releasing portion 112 can be sequentially brought into contact with the locking pieces 13, and the plurality of locking pieces 13 can be simultaneously brought into contact with the pressing portion 111 or the releasing portion 112, thereby improving the effectiveness and stability with which the ring gear 12 is locked.
Of course, when the torque transmission device 20 performs transmission through gears, as shown in fig. 6 to 9, the torque transmission device 20 preferably further includes: a drive member 15, planet wheels 16 and a wheel carrier 17. The driving member 15 includes a first wheel portion 151 and a second wheel portion 152, the planetary wheel 16 is matched with the second wheel portion 152, the wheel carrier 17 is used for mounting the planetary wheel 16, and the planetary wheel 16 and the first wheel portion 151 are both formed with transmission teeth capable of being matched with the internal teeth 121 of the gear ring 12. Specifically, the first wheel portion 151 has a first radius, the second wheel portion 152 has a second radius, the first radius is larger than the second radius, the second wheel portion 152 is also provided with a plurality of transmission teeth, the number of planet wheels 16 is multiple, and the plurality of planet wheels 16 are all matched with the second wheel portion 152. For mounting the planet wheels 16, the carrier 17 is formed with a mounting shaft, the planet wheels 16 being rotatably mounted on the carrier 17.
In order to achieve that the ratio of the rotational speeds of the second wheel section 152 of the driver 15 and the wheel carrier 17 can be changed, so that the torque transmission device 20 has different final output rotational speeds, the toothed ring 12 is moved in a direction parallel to the centre axis to a first position in which it engages both the planet wheels 16 and the first wheel section 151 when the operating ring 11 is rotated to disengage the locking teeth 131 from the external teeth 122, and the toothed ring 12 is moved in a direction parallel to the centre axis to a second position in which it engages only the planet wheels 16 when the operating ring 11 is rotated to a position in which the locking teeth 131 engage the external teeth 122. Thus, when the ring gear 12 moves to the first position, the planet gears 16, the ring gear 12 and the driving member 15 rotate synchronously, so that the rotation speed ratio of the first wheel part 151 to the wheel carrier 17 at this time is 1; when the ring gear 12 moves to the second position, the circumferential position of the ring gear 12 is locked, the planet wheels 16 can rotate relative to the ring gear 12, and the rotation speed ratio of the first wheel part 151 to the wheel carrier 17 is greater than 1, so that speed reduction is realized.
In order to simultaneously lock or release the toothed ring 12 by the locking elements 13 when the operating ring 11 is rotated and also to move the toothed ring 12 in a direction parallel to the central axis, the torque transmission device 20 further comprises a connecting element 18, the toothed ring 12 further comprising a gear portion 123 and a wheel groove portion 124. The connecting piece 18 can drive the gear ring 12 to move along the direction parallel to the central axis when the operating ring 11 rotates, specifically, the operating ring 11 comprises a chute, a straight line of the chute is obliquely intersected with the central axis, and the connecting piece 18 at least partially extends into the chute. The gear portion 123 of the ring gear 12 has the above-described internal teeth 121 and external teeth 122 formed thereon, the race portion 124 has a race 124a formed on the outer periphery of the ring gear 12 to be engaged with the coupling 18, and the external teeth 122 and the race 124a are provided at different axial positions of the ring gear 12. Thus, when the operating ring 11 rotates, the connecting member 18 moves in a direction parallel to the central axis by the inclined grooves, and the connecting member 18 in turn drives the ring gear 12 to move in a direction parallel to the central axis due to the engagement of the connecting member 18 with the wheel groove 124 a. It will of course be appreciated that the coupling member 18 may not extend into the chute but the movement of the coupling member 18 may be driven by an intermediate member cooperating with the chute.
It is known that a multi-stage planetary gear system is usually included in the torque transmission device 20, and therefore a plurality of toothed rings 12 are also included, so that the operating ring 11 can be arranged to lock one toothed ring 12 by the locking member 13, and at the same time, to move the other toothed ring 12 in a direction parallel to the central axis to a position where it engages with a different gear, so as to achieve a more different output speed of the torque transmission device 20.
Preferably, as shown in fig. 10 to 12, the power tool 100 of the present invention further comprises a torque adjustment assembly 40 cooperating with the torque transmission device 20 and an axle lock assembly 50, wherein the torque rotation device further comprises: a next-stage planet wheel 19, a next-stage ring gear 21, a next-stage operating ring 22 and a next-stage locking piece 23. The wheel carrier includes a mounting portion 171 and an output portion 172, the mounting portion 171 is used for mounting the planetary gear 16, the output portion 172 is used for meshing with the next-stage planetary gear 19, the next-stage locking member 23 and the locking member 13 are the same in structure and used for locking or releasing the circumferential position of the next-stage gear ring 21, and the next-stage operating ring 22 can drive the next-stage locking member 23 to lock or release the next-stage gear ring 21 when rotating.
The torque adjusting assembly 40 is used for adjusting the output torque of the power tool 100, and the detailed structure of the torque adjusting assembly 40 is not described in detail. The main point of the present invention is that the torque force adjusting assembly 40 is engaged with the next-stage toothed ring 21, so that when the next-stage toothed ring 21 is released by the next-stage locking member 23, the torque force adjusting assembly 40 can adjust the fixing force of the next-stage toothed ring 21, thereby adjusting the output torque force of the power tool 100. When the circumferential position of the next-stage ring gear 21 is locked by the next-stage locking piece 23, the next-stage planetary gear 19 can rotate relative to the next-stage ring gear 21, so that the torque transmission device 20 can output a certain torque force.
The shaft lock assembly 50 is used to lock the torque force transmitted from the output member 30 to the prime mover 10 in a reverse direction, thereby preventing damage to the prime mover 10. The shaft lock assembly 50 includes a shaft lock bracket 51, a paddle 52, a shaft lock pin 53, and a ring. The next-stage planetary gear 19 is mounted on the shaft lock carrier 51, that is to say, for the next-stage planetary gear 19, the shaft lock carrier 51 corresponds to the planet carrier of the next-stage planetary gear 19. The shaft lock frame 51 comprises a central through hole 511, the central through hole 511 is connected with the output member 30 through a flat structure, a groove 512 surrounding the central through hole 511 is further formed on the surface of the shaft lock frame 51 close to the next-stage planet wheel 19, and the plectrum 52 is accommodated in the groove 512. An accommodating groove 513 is formed at an edge of the shaft locking bracket 51, and the accommodating groove 513 is used for accommodating the shaft locking pin 53. The ring member is disposed around the shaft lock bracket 51, and the shaft lock pin 53 is located between the inner wall of the ring member and the receiving groove 513. Preferably, the annular element is formed integrally with the ring gear 21 of the next stage, that is to say the ring gear 21 of the next stage comprises a ring gear portion 211 cooperating with the planet gears 19 of the next stage and an annular portion 212 forming an annular element. In this way, the pick 52 is disposed in the groove 512 of the shaft lock bracket 51, and the shaft lock pin 53 is located between the receiving groove 513 on the edge of the shaft lock bracket 51 and the ring, so that the axial length of the shaft lock assembly 50 is reduced, thereby reducing the axial dimension of the entire power tool 100.
The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It should be understood by those skilled in the art that the above embodiments do not limit the present invention in any way, and all technical solutions obtained by using equivalent alternatives or equivalent variations fall within the scope of the present invention.
Claims (10)
1. A torque transmitting device comprising:
the operating ring can rotate around a central axis;
a toothed ring rotatable about the central axis;
a locking member movable in a radial direction of the central axis;
wherein,
the ring gear is formed with:
inner teeth provided on an inner periphery of the ring gear;
outer teeth provided on an outer periphery of the ring gear;
the locking piece is provided with a locking tooth and a locking block which are oppositely arranged in the radial direction of the central axis;
the operation ring is formed with:
the pressing part can press the locking piece to enable the locking teeth to be matched with the external teeth;
a release portion capable of receiving the lock piece of the lock piece to disengage the lock teeth from the external teeth;
in the radial direction of the central axis, the locking piece is arranged between the operating ring and the gear ring, the locking tooth of the locking piece is positioned on one side of the gear ring, and the locking block of the locking piece is positioned on one side of the operating ring;
the pressing portion and the releasing portion are disposed at different circumferential positions of the operation ring in a circumferential direction of the central axis.
2. The torque transmitting device of claim 1, further comprising:
a guide for limiting a circumferential position of the locking member;
the guide member includes:
a guide groove penetrating the guide member in a radial direction of the central axis;
the locking member is at least partially inserted into the guide groove.
3. The torque transmitting device of claim 2, wherein the guide slot comprises: the distance between the two guide inclined planes is gradually reduced from outside to inside along the radial direction of the central axis; the locking member includes: and the limiting inclined planes can be respectively arranged in parallel with the two guide inclined planes.
4. The torque transmitting device of claim 1, wherein the compression portion includes a compression wall surface in the shape of a circular arc; the relief portion includes a relief groove recessed outward substantially in a radial direction of the central axis with respect to the pressing wall surface.
5. The torque transmission device according to claim 1, wherein the number of the locking pieces is an even number, and the even number of the locking pieces are symmetrically arranged with respect to the central axis; the number of the release portions is the same as the number of the locking pieces.
6. The torque transmission device according to claim 4, wherein the pressing portion and the releasing portion are provided at an interval in a circumferential direction of the central axis.
7. The torque transmission device according to any one of claims 1 to 6, further comprising:
a drive member including a first wheel portion and a second wheel portion;
a planet wheel, cooperable with the second wheel portion;
the wheel carrier is provided with a mounting shaft which can rotatably mount the planet wheel;
the planet wheel with first wheel portion all be formed with can with the ring gear the internal tooth complex driving tooth.
8. The torque transmission device of claim 7,
when the operating ring rotates to a position where the lock teeth are disengaged from the external teeth, the gear ring moves in a direction parallel to the central axis to a first position where the gear ring is engaged with both the planet gear and the first gear portion;
when the operating ring is rotated to a position where the locking teeth engage with the external teeth, the ring gear is moved in a direction parallel to the central axis to a second position where it engages only with the planet gears.
9. The torque transmitting device of claim 8, further comprising:
the connecting piece can drive the gear ring to move along the direction parallel to the central axis when the operating ring rotates;
the ring gear includes:
a gear tooth portion forming the inner tooth and the outer tooth;
the wheel groove part is formed on the outer edge of the gear ring and is matched with the connecting piece;
the outer teeth and the wheel grooves are provided at different axial positions of the ring gear.
10. A power tool comprising a torque transmitting device as claimed in any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510406636.0A CN106337908B (en) | 2015-07-10 | 2015-07-10 | Torque transmission device and power tool with the torque transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510406636.0A CN106337908B (en) | 2015-07-10 | 2015-07-10 | Torque transmission device and power tool with the torque transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106337908A CN106337908A (en) | 2017-01-18 |
| CN106337908B true CN106337908B (en) | 2018-08-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510406636.0A Expired - Fee Related CN106337908B (en) | 2015-07-10 | 2015-07-10 | Torque transmission device and power tool with the torque transmission device |
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| Country | Link |
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| CN (1) | CN106337908B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114483934A (en) * | 2022-01-25 | 2022-05-13 | 王国富 | Automatic speed changing method and device of multi-connected planetary gear speed changing device |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0674835B2 (en) * | 1986-03-27 | 1994-09-21 | マテックス株式会社 | Casing mounting structure for planetary gear unit |
| US6733414B2 (en) * | 2001-01-12 | 2004-05-11 | Milwaukee Electric Tool Corporation | Gear assembly for a power tool |
| US7101300B2 (en) * | 2001-01-23 | 2006-09-05 | Black & Decker Inc. | Multispeed power tool transmission |
| DE10315138A1 (en) * | 2003-04-03 | 2004-10-21 | Atlas Copco Electric Tools Gmbh | Switchable gear of a hand-held machine tool |
| DE102010041172A1 (en) * | 2010-09-22 | 2012-03-22 | Robert Bosch Gmbh | Hand-held power tool with a gearbox |
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| CN106337908A (en) | 2017-01-18 |
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