TW200533852A - Multispeed power tool transmission - Google Patents

Abstract

A portable power tool with a housing, a motor having a motor output member, a driven member and a transmission. The transmission, which is located in the housing, is configured to receive a rotary input from the motor output member and to produce a rotary output that is transmitted to the output spindle. The transmission has a plurality of planetary transmission stages, each of which including a ring gear, a planet carrier and a plurality of planet gears that are supported by the planet carrier for meshing engagement with the ring gear. The transmission further includes at least one member that may be configured in a first condition, which renders at least one of the planetary transmission stages operable in an active mode, and a second condition, which renders at least one of the planetary transmission stages operable in an inactive mode. The transmission is operable in at least three overall speed reduction ratios.

Description

200533852 IX. Description of the invention: [Technical field to which the invention belongs] Movement =! Included is about power tools, such as portable drills, power screwdrivers, and portable cutting tools. More specifically, the present invention relates to a transmission device for a rotary power tool for performing multiple speed transmissions. nm [Prior technology] Modern power tool manufacturing chapter p d > 蒹 has introduced a rotary power tool with a 彳 variable speed motor in an attempt to make such a tool 疋 turn. The user has sufficient control over this type of tool in order to perform various Do all kinds of work without using special tools. Many m-class, two-speed transmissions available in the market make it possible to have greater control over the speed of the sanitary equipment. Typically, these known transmissions lack a variable speed transmission that can produce a wide range of output speeds and torques to perform a variety of tasks, such as installing drywall screws with large diameter round drills or Large diameter square head wood screws and high-speed drilling operations. The single- or two-speed transmissions commonly used in such tools do not have sufficient deceleration capacity to promote their widespread use, because these tools are built for high torque operation purposes and tend to weaken their high speeds. Performance. In addition, the rechargeable batteries used in many early wireless rotary power tools were not perfectly suitable for use at low speeds and high torques due to the amount of energy consumed by the power tools and the rate of energy consumption in such work. Therefore, consumers often have to buy two different rotary power tools 99815.doc 200533852 to use: one is a medium-sized tool for "standard" applications such as countersinking and fastening, and one is for more laborious operations Heavy-duty tool with a low speed and high torque output. Because of the advent of modern high-energy, high-voltage batteries, it is now possible to meet the energy requirements of power tools used in low-speed, high-torque operation. However, in this technique, there is still a need for a transmission of a power tool 'having a wide range in terms of its deceleration capability. [Summary of the Invention]

In one form, the present invention provides a portable power tool, which includes: a peripheral device, a motor having a motor output member, a driven member, and a transmission device. The transmission device arranged in the casing is constructed to receive-rotate input from the output member of the motor, and then generate-rotate the output to the output spindle. The transmission device has a plurality of planetary transmission stages, and each transmission stage includes a ring gear, a planetary carrier and a plurality of planetary gears, the latter being supported by the planetary carrier to engage with the ring gear. The transmission device further includes at least-components, which can be built into the first condition, so that at least the planetary transmission stage is operated in the effective mode; and can be built into the second condition, so that at least the planetary transmission stage is in — Run in inactive mode. The drive can be operated with at least three total reduction ratios. Additional benefits and features of the present invention will become apparent from the description of the accompanying drawings and the scope of the appended patents. [Embodiment] Overview Regarding Figures 1 and 2 of the drawings, the tools built according to the teachings of the present invention 99815.doc 200533852 tools are generally indicated by reference numerals. As one skilled in the art can recognize, a preferred embodiment of the present invention may be a wired or wireless (battery operated) component, such as a portable screwdriver or drill (for example, a drill , Impact rock drill). In the illustrated specific embodiment, the power tool 10 may be a wireless drill with a housing 12, a motor assembly 14, a multi-speed transmission assembly 16, a clutch mechanism 18, and an output spindle. Assembly 20 --- ^ disc 22, a trigger assembly 24 and a battery pack 26. Those skilled in the art will understand that there are several components of the power tool 10. Such as the chuck 22, the trigger assembly 24 and the battery pack 26 are all of a common nature, and no major and detailed explanation is necessary in this application. For a more detailed understanding of the power tool 10, refer to various publications. An example of such a publication is U.S. Patent No. 5,897,454 (issued on April 27, 1999), which is generally assigned, the contents of which are hereby incorporated by reference as if fully set forth herein. The housing 12 includes an end cap assembly 30 and a handle shell assembly 32, the latter having a pair of paired handle shells 34. The handle shell assembly 32 includes a handle portion 36 and a drive series or body portion 38. The trigger assembly 24 and the battery pack 26 are mechanically combined with the handle portion 36, and are electrically combined with the motor assembly 14. The body portion 38 includes a motor cavity 40 and a transmission cavity 42. The motor 14 can be received in the motor cavity 40 and includes a rotary output shaft 44 projecting into the transmission cavity 42. A motor pinion 46 having a plurality of gear teeth 48 can be connected to the output shaft 44 for rotation. The trigger assembly 24 cooperates with the battery pack 26 to selectively provide power to the motor assembly 4 in a manner generally known in the art to control the speed and direction of the output shaft 44 rotation. 99815.doc 200533852 The transmission assembly 16 can be installed in the transmission space 60. The motor pinion 46 integrates the transmission into a 16: 'speed-selection mechanism. The output 16 is coupled to the output shaft 44 and transmits a relatively high-speed, low-torque drive output A ^ y ^ to the transmission assembly 16. The transmission assembly 16 includes a plurality of reduction elements, which are selectively engaged by a speed selection mechanism 60 to provide a plurality of speed ratios. Each 1U ratio can multiply the speed and torque of the drive input in a predetermined manner to allow the output speed and torque of the drive assembly 16 to be relatively low speed, high torque, and

Relatively high speed and low torque. The transmission output can be transmitted to the output main shaft assembly. The 2G 'chuck 22 can be combined with the main shaft assembly for rotation, so that the torque is transmitted to a tool head (not shown). The clutch mechanism 18 can be coupled to the transmission assembly 16 and can be operated to limit the magnitude of the torque associated with the drive input to a predetermined, selectable limit. Functional Overpressure Forming With particular reference to FIGS. 2-9, the end cap assembly 30 may include one end cover shell 100 and an overpressure forming part 102. In the specific embodiment provided, the end cap shell 100 can be made of plastic material (such as ABS) by injection molding. The end cap assembly 100 defines an end cap cavity 104, which can be sized to receive a portion of the motor assembly 14 extending behind the handle housing assembly 32. A plurality of first and second radial protruding ear gap holes 108 and 110 and an abutment surface 128 are formed in the forward surface 114 of the end cover shell 100, and a plurality of screw convex surfaces n6 are formed at the end. Cover the perimeter of the shell 100. Each of the first and second radial lug apertures 108 and 110 is sized to receive the first radial lug 120 and the second radial lug formed on the rear face 124 of the handle housing 34, respectively. One of the lugs 122. The first and second radial lug holes 108 and 110 cooperate with the first and second radial lugs 99815.doc -10 · 200533852 120, 122, so that the end cap shell 100 can correctly align the handle shell The assembly is 32, and the relative rotation between the two is prohibited. A curved portion 128 of the forward facing surface 114 of the end cap shell 100 can be formed as an inclined surface so as to cooperate with the abutting surface 132 of the rearward facing surface 124 of the handle shell 34. The screw convex surface 116 allows the end cover shell 100 to be fixedly connected to the motor shield 136 by means of a plurality of screw pins 138. The geometry of the motor shroud 136 may be such that it is forcedly restrained by the handle housing 34. If so, the end cover shell 100 can be fastened to the motor shroud 136 so as to hold the end cover shell 100 against the rear face 124 of the handle shell assembly 32, and at the same time it will also be in the handle shell assembly 32. The rear handle gap hole 139 is closed. A plurality of side slit holes 140 are formed through both sides of the end cover shell 100 to allow air to flow through the handle shell assembly 32, and the motor assembly 14 is cooled in a manner well known in the art. There are a plurality of rear slot holes 14 4 ′ formed through the rear end of the end cap shell 100, each including a recessed portion 146 that only partially extends into the outer surface 148 of the end cap shell 100, and a fully extended through the end cap. The through portion 150 of the case 100. A pair of retaining lugs 152 are made and extend inwardly from the inside surface 154 of the end cap shell 100 into the end cap cavity 104. _ The channel 1 5 6 can be made in the inner surface 1 5 4 of the end shell 1 0 0 and intersects with the rear groove, the hole 144 and the retaining lug 152. The over-molded part 102 can be made of an elastic material, such as a thermoplastic plastic elastomer (such as HYTREL (R) manufactured by EI du Pont de Nemours and Company), and can be simultaneously manufactured and bonded to one over-pressure forming operation. The knowledge set is set at 100. In the specific embodiment provided, the over-molded part 102 includes a plurality of anti-collision members 170, a pair of spacers 72, and a connecting member 174. Each bumper 170 extends from a point which is approximately 99815.doc -11-200533852 to the inner surface of the end cap shell 100 to a point behind the outer surface of the end cap shell 100, which is approximately 4.8. 5 mm to 1.5 mm, and preferably a distance of 0.75 mm. Such a construction can make the anti-collision member 170 provide some shock resistance, and when the tool is accidentally dropped, the probability of the end cover shell 100 being damaged can be reduced. Also, sometimes the operator must apply a relatively strong force to the tool, such as when using a circular hole saw to drill a large diameter hole. In such a case, the operator leans down and presses against the rear portion of the tool 10 to apply a force in line with the axis of the chuck 22. Under such circumstances, the crashworthy worker 70 can provide the operator with a relatively soft and comfortable surface, which has a tendency to prevent slipping, and at the same time, can reduce the vibration transmitted to the operator. The spacer 172 is formed around each of the retaining dog ears 152 on the inside surface 154 of the end cap shell 100. In the specific embodiment provided, each of the spacers 172 includes a ring-shaped member 180 that extends forward from the inner surface 154 of the end cap shell 100, such that the end cap shell 100 and the spacer 172 Engage to the outer direct control 14a 'and let the rear surface i4b of the motor housing 14c securely hold the motor 14d inside the motor shroud 136. This prevents the components of the motor assembly 14 from moving along the longitudinal axis of the tool 10, and also reduces the vibration generated by the motor assembly 14 during operation. The linking member 174 may be fixedly coupled to each of the collision preventing members 170 and the spacer 172. The connecting member 174 can provide an elastic material through a flow path when the collision preventing member 170 and the spacer 172 are formed. The connecting member 174 also connects the bumper 170 and the spacer 172 to each other, so that it becomes more difficult to remove them from the end cover shell 100. Anyone skilled in this art will agree that this aspect of the present invention can be added to each of the other positions inside the handle assembly 3 2 to make two or more groups. 99815.doc • 12- 200533852 A blanket between pieces , Sealing, vibration reduction, or positioning of one component relative to another component. Figures 10 and 11 show such an example, in which the spacer 172 is modified to extend around the periphery of a part of the end cap cavity 104 and comes into sealing contact with the rear surface 14b of the present motor 14d. The isolator 172 seals the interface between the end cover shell 100 and the motor assembly 14, and the impact member 170 seals the rear gap hole 144 in the cover 100. The space 188 delimited by the spacer 1 72 is then filled with grease or another suitable lubricant to lubricate the motor armature bearing 190. Transmission Assembly Referring to FIG. 12, the transmission assembly 16 may be a three-stage, three-speed transmission mechanism, which includes a transmission sleeve 200, a reduction gear assembly 202, and a speed selection mechanism 60. 13-17, the transmission sleeve 200 may include a wall member 210 that defines a general transmission inner cavity or hollow cavity 212, and a reduction gear assembly 202 may be configured therein. The transmission sleeve 200 includes a body 214 and a base 216. The body 214 of the transmission sleeve 200 may be quite uniform in diameter and smaller than the base 216 in diameter. The inside diameter of the base 216 may be sized to receive the cylindrical front portion 220 of the motor shield 136. A plurality of raised table surfaces 22 6 are formed in the base 216. The mesas 226 define a plurality of first grooves 228 on the outer surface 230 of the base 216 and a plurality of second grooves 232 on the inner surface 234 of the base 216. The first groove 228 is configured to receive a collimating rib 238, which is formed on the inner surface 242 of the handle case 34 for aligning the transmission sleeve 200 with the handle case 34 and the prohibition transmission sleeve 200 and Relative rotation between the shells 12. Preferably, the 99815.doc -13 · 200533852 first groove 228 and the collimating rib image 238 are constructed so that the transmission sleeve 200 can be assembled to the handle shell 34 only in a certain orientation (also That is, the configuration of the first grooves 228 and the collimation ribs 238 can prevent the position of the transmission sleeve 2000 relative to the handle housing 34 from being turned 180 by mistake. The second slot 232 will be discussed in more detail below. The body 214 of the transmission sleeve 200 may include a cylindrical body portion 246 and a pin shell portion 248. In the particular embodiment shown, the cylindrical body portion 246 includes a selection cam guide 250, a plurality of lubricant grooves 252, and first and second sets of ring-shaped coupling teeth 254 and 256. The inspection section of the selection cam guide 250 may be substantially rectangular 'extending outward from the top surface of the outer surface 25 8 of the body portion 246. The lubricant groove 252 is formed concentrically around the periphery of the body portion 246. The lubricant groove 252 has a depth of about 0.1 (H inches to 0.030 inches) and holds a lubricant (such as grease) in the upper half of the periphery of the body portion 246. The cam guide 250 and the lubricant groove 252 are selected Its function will be discussed in detail below. A raised circular flange 264 separates the body portion 246 into first and second housing portions 260 and 262. The first set of ring-shaped engaging teeth 254 are made on the body portion 246 The inner surface 266 extends from the raised circular flange 264 toward the base 216. The second set of annular engaging teeth 256 is also made on the inner surface of the body portion 246, but extends from the raised circular flange 264 to Forward extension. All the teeth 268 in the first and second sets of annular meshing teeth 254 and 256 are evenly spaced around the inner surface 266 of the main body portion 246. The first and second sets of ring-shaped engaging teeth 254 and 256 The configuration of each tooth 268 also extends from the convex circular surface occupation edge 264, and also has two parallel engaging surfaces 270, and also terminates at a tip portion 272. The tip portion 272 of each tooth 268 may be 99815 .doc • 14 · 200533852 is round, It can also be tapered to enhance its ability to mesh with a portion of the reduction gear assembly 202, which will be explained in detail below. The pin housing portion 248 extends down from the body portion 246 over a substantial portion of the length of the body portion 246 An introduction slot 274 can be made in the pin shell portion 248 and extends back through the base 216 of the transmission sleeve 200. In the illustrated specific embodiment, the introduction slot 274 can be provided in a step shape. The rear portion of the transmission sleeve 200 has a first portion 276 of a first diameter, and at the front portion of the transmission sleeve 200 has a second portion 278 of a smaller second diameter. In the embodiment shown, the drive slot is A first portion 276 of 274 penetrates the first housing portion 260 to form a groove 280 on the inside surface 234 of the base 216. The pin housing portion 248 will be discussed in more detail below. A pair of first clip grooves 284 and A pair of second clamping grooves 286 are formed in the transmission sleeve 200 along two sides of the transmission sleeve 2000 and extend in a manner parallel to the longitudinal axis of the transmission sleeve 200. The first pair of clamping grooves 284 Can pass through the body part 246 in a convex circle The two rear sides of the flange 264 are made and extend backward toward the base 2 16. The depth of the first pair of clamping grooves 284 can be extended to not penetrate the portion of the wall member 210 defining the base 216. The second pair of clamping grooves 286 can also pass through The two sides of the body portion 246 are made in front of the raised circular flange 264 and extend through the front surface 288 of the transmission sleeve 200. Referring to Figs. 12, 13, 18, and 23, the total reduction gear set The component 202 may include a first reduction gear set 302, a second reduction gear set 304, and a third reduction gear set 306. The first, second, and third reduction gear sets 302, 304, and 306 can all operate in an effective mode, and in the example provided, the second and third reduction gear sets 304 , 306 can also operate in a useless mode. 99815.doc 200533852 Running in the effective mode will cause the speed reduction and torque increase of the reduction gear set; and running in the ineffective mode will cause the deceleration gear set to provide an output, which has The speed and torque are approximately equal to the speed and torque of the rotational input supplied to the reduction gear set. In the illustrated specific embodiment, the first, second, and third reduction gear sets 302, 3, and 306 are each a set of planetary gears. However, those skilled in the art will understand that various other types of reduction gear sets that are well known in the art can also be used in place of one or more reduction gear ® wheels that make up the reduction gear assembly 202. As shown in the figure, the first reduction gear set 302 may include a first reduction element or ring gear 310, a first set of planetary gears 312, and a first planetary or reduction gear holder 314. The first ring gear 31 may have a ring structure and have a plurality of gear teeth 310a formed along its inner diameter. A clutch surface 316 may be formed in the outer periphery of the front surface 318 of the first ring gear 310, which will be discussed in more detail below. The first ring gear 31 may be disposed in a hollow cavity 212 portion bounded by φ 疋 at the base 216; the front surface 318 of the first ring gear 310 contacts a step 32 formed in the transmission sleeve 200. 〇, thereby limiting the ability of the first ring gt > gear 310 to move forward into the hollow cavity 212. The first reduction bracket 314 can be made into a flat cylindrical shape, and has a plurality of pins 322 extending from the rear surface 324 thereof. A plurality of gear teeth 314a are formed on almost the entire outer periphery of the first reduction bracket 314, and valleys 314b are formed between the adjacent two gear teeth 31 乜. Due to the arrangement of the gear teeth 314a, one of the valleys (namely, valley valley) is larger than the rest of the land 314b. This is because of the first reduction bracket 314 99815.doc • 16-200533852 The reason for omitting one of the gear teeth 3 14a on the outer periphery. In the illustrated specific embodiment, the teeth 3 14a of the first reduction bracket 314 are constructed so that they cannot mesh with the teeth 310a of the first ring gear 310. The external shape of the gear teeth 3 14a will be described in detail with reference to FIGS. 19 and 20 in particular. As shown in the figure, each gear tooth 314a terminates with a progressive arc 326 on the forward surface 328 of the reduction bracket 314, but terminates abruptly at the rear surface 324 of the reduction bracket 314. A round fox 330 is also made on the valley 314b between the teeth 314a. Returning to FIGS. 12, 13, 15, 18, and 23, a first thrust washer 332 having a first annular portion 334, a second The ring-shaped portion 336 and the plurality of retaining lugs 338 may be disposed behind the first reduction gear set 302. The retaining lug 338 is engaged with the second groove 232 in the base 216 of the transfer sleeve 200, so that relative rotation between the first thrust washer 332 and the transmission sleeve 200 can be prohibited. The inner diameter of the base 216 can be set to be suitable for receiving the motor shroud 136, and the front surface 34 of the motor shroud 136 can prevent the axial movement of the first thrust washer 332. The first ring portion 334 is in contact with the rear surface 342 of the first ring gear 31o, provides a wear surface, and controls the extent to which the first ring gear 3o can move in the axial direction. The second annular portion 336 may be axially spaced apart from the first annular portion 334 and protrude in front of the first annular portion 334 to provide a wearing surface of the first set of planetary gears 312 and control the first The degree to which the planetary gears 3 12 can move in the axial direction. The first set of planetary gears 312 may include a plurality of planetary gears 344, each of which is generally cylindrical in shape, has a plurality of gear tooth centers formed on its outer periphery and a pin-pin gap hole 346 formed at its center. Each planetary gear 344 can be 99815.doc • 17-200533852 rotatably supported on an associated pin 322 of the first reduction bracket 314, and can be arranged so that its teeth 344a and the first ring gear 310 Teeth 3 14a mesh with each other. A convex portion 348 may be formed on the front and rear surfaces 350 and 352 of each planetary gear 344 to prevent the gear teeth 344a from rubbing against the first reduction bracket 314 and the first thrust washer 332, which may damage the transmission gear. It becomes 16 sex month b and detracts from the dust and broken genus of the working brother's life. Since the teeth 46a of the motor pinion 46 on the output shaft 44 are also in mesh with the teeth 344a of the planetary gear 344, the motor pinion 46 can be used as a sun gear of the first reduction gear set 302. The second reduction gear set 304 may be disposed in a portion of the hollow cavity 212 defined by the first housing portion 26o, and may include a second sun gear 358, a second reduction element or ring gear 36o, a The second set of planetary gears 3 62 and the second planetary or reduction bracket 364. The second sun gear 358 can be fixed to co-rotate with the first reduction bracket 314. The second sun gear 358 includes a plurality of gear teeth 358a extending forward from a front surface 328 of the first reduction bracket 314. The second ring gear 360 may be a ring structure containing a plurality of gear teeth 360a made along its inner diameter. The gear teeth 36〇a may be chamfered on the rear surface 366 of the second ring gear 360, but may terminate sharply on the front surface 368. The car's proper shape can make a large arc 369 on the rear surface 366 and both sides of each tooth 36〇, because the large arc 369 is used on each tooth 36〇a without a large chamfer A better meshing relationship between the second ring gear 36 and the first reduction bracket 314 can be provided. A plurality of sleeve meshing teeth 37 are formed on the outer side of the second ring gear 36〇 on the periphery of 99815.doc -18- 200533852. The sleeve grooving teeth 37 are directed forward to the front surface of the second ring gear 36. 3 68 Extend | Terminate at the tip portion 372; the tip portion can be made round or tapered forward and inward. An annular clamping groove 374 may also be formed in the outer periphery of the second ring gear 36o. In the illustrated example, the clip groove 374 may be a rectangular slot, and includes a pair of side walls 376. This clip groove 374 will be discussed in more detail later. The second reduction bracket 364 can be made in the shape of a flat cylinder, and has a plurality of pins 378 protruding from the rear surface 380 toward the surface. The second set of planetary gears 362 may include a plurality of planetary gears 382. Each planetary gear may be substantially cylindrical, having a plurality of gear teeth 3 82a formed in the outer periphery thereof and a pin slot hole 384 formed in the center thereof. Each planetary gear 382 may be rotatably supported on an associated pin 378, and the second reduction bracket 364 may be provided so that the gear teeth 382 a of the planetary gear 382 and the gear teeth 3 60 a of the second ring gear 360 interact with each other. Bite engagement. The gear teeth 358a of the second sun gear 358 and the gear teeth 3 82a of the planetary gear 3 82 also bite and spray. The third reduction gear set 306 may be disposed in a portion of the hollow cavity 212 defined by the second housing portion 262, and may include a third sun gear 398, a third reduction element or ring gear 400, a third set of planets Gear 402, and-the third planet or reduction bracket 404. The third sun gear 398 may be fixed to rotate in the same manner as the second reduction bracket 364. The third sun gear 398 includes a plurality of gear teeth 398a extending forward from the front surface 406 of the second reduction bracket 364. The third ring gear 400 may be a ring structure containing a plurality of gear teeth 400a made along its inner diameter. The gear teeth 400a can be chamfered on the front surface 412 of the third ring gear 400, but terminate sharply on the rear surface 414. The best, 99815.doc -19- 200533852 will make a large round fox 407 on the front surface 412 and both sides of the gear tooth 400a. Because the large arc 407 is used instead of a large chamfer, a third ring gear can be provided. The third deceleration brackets 404 have a better response relationship. A plurality of sleeve yoke teeth 418 are formed on the outer periphery of the third ring gear 400; the sleeve spray teeth 418 extend backward toward the rear surface 414 of the third ring gear 400 'stop at- The tip portion 42 ′ may be made round or tapered backwards and inwards. An outer periphery of the third ring gear 400 can also be made.

环 夹 槽 422。 Ring clip groove 422. In the illustrated example, the clip groove 422 may be a rectangular slot ' The $ 422 will be discussed in detail. The third reduction bracket 404 can be made into a flat cylindrical shape, and a plurality of pins 428 extend from the rear surface 430 to the rear surface 430. A plurality of gear teeth 40 is made in almost all of the outer periphery of the third reduction bracket 404, with two adjacent gear teeth each.

A valley 404b is formed between 404a. Because the gear teeth are arranged at a distance of 40 °, one of the valleys 404b (that is, valley 404b) is larger than the rest of the valley 404b. This is because the outer periphery of the third reduction bracket 404 is omitted. For the sake of gear 404a. In the particular embodiment shown, the gear teeth 404a of the third reduction bracket 404 are constructed so that they cannot interengage with the gear teeth 382a of the second planetary gear 382. In addition, please refer to Fig. 21 and Fig. 2 for a brief description of the shape of the gear tooth 4 04a. As shown in the figure, the rear surface 430 of the third reduction bracket 404 may be chamfered and a large arc 434 may be formed on each side of each of the gear teeth 404a and the valley 404b. Each of the gear teeth 404a terminates abruptly at the front surface 436 of the third reduction bracket 404. Returning to FIGS. 12, 13, 15, 18, and 23, the third set of planetary gears 402 99815.doc -20-200533852 may include a plurality of planetary gears 438. Each planetary gear 438 may be substantially cylindrical in shape, and a plurality of gear teeth 438a are made on its outer periphery, and a pin gap is made in the center. Each planetary gear 438 can be rotatably supported on the relevant pin 428, and the third reduction bracket 404 can be provided as the gear teeth 43 "of the planetary gear 438 and the gear teeth 400 of the third ring gear 400. a Inter-bite meshing. A raised portion 442 can be made on the front and rear surfaces of each planetary gear 438, which can forbid the gear teeth 43 8a from rubbing against the third reduction bracket 4 04, which will damage the performance of the transmission assembly 16 And reduce the dust and debris of the transmission assembly with a working life of 16 °. The second thrust ring can be set around the third sun gear 398, and the teeth 398a of the second sun gear 398 are all the same as those of the planetary gear 438. The gear teeth 438a mesh with each other. The second thrust washer 45 may include a plurality of retaining lugs 452 'which are configured to engage corresponding protrusions made on the inner surface 266 of the body portion of the transmission sleeve 200. Ear groove 454 (Figure 3). The retaining lug 452 and the lug groove 454 can cooperate to prohibit the relative rotation between the third thrust washer 45 and the transmission sleeve 200. • The output spindle assembly 20 can Includes a transmission member 458 for connecting a main shaft 460 to be the same as the third reduction bracket 404 In order to transmit the driving torque from the reduction gear assembly 202 to the chuck 22. This transmission member 458 is well known in the art and can be easily adjusted to fit the transmission assembly of the present invention. Therefore, The transmission member 458 is not intended to be described in detail here. Referring to FIGS. 13, 13a, 13b, 16, 17, 18, and 23-28, the speed selection mechanism 60 may be in a first position of 500, a first Move between the second position 502 and a third position 504, and include a conversion part knife 5 1 〇 ′ for receiving a speed change input and a speed reduction gear assembly assembly 99815 for operating according to the speed change input .doc -21-200533852 202 of the driving part 5 12. The driving part 5 12 can be operatively connected to the reduction gear assembly 202, and can respond to the conversion part 5 1 in the first, first, and The second position is moved between 500, 50, and 50, and the second and third reduction gear sets 304 and 306 are moved between the active and inactive modes. In the particular embodiment shown, the The driving part 5 12 includes a rotary selection cam 520 and a plurality of clamps 52 2 and a spring member 523. Each clamp 522 can be made of round steel wire; the steel wire is bent into a semi-circle 524 shape, and a pair of lugs 526 protrude outward from the semi-circle 524 and are arranged approximately on the center line of the semi-circle 524. The semicircle 524 is sized to fit into the clamping grooves 374 and 422 in the second and third ring gears 360 and 400, respectively. In this regard, the semicircle 524 does not protrude in the radial direction. Besides a related ring gear (360, 400), it is not tightly bound between the two walls (376, 424) of the clamping groove (374, 422). In the example provided, the two walls (376, 424) of the clamp groove (374, 422) are spaced about 0.05 inches apart, and the diameter of the steel wire used to make the clamp 522 can be approximately 0.04 Inches. Each lug 526 of the clamp 522 projects outward from the hollow cavity 212 and enters an associated clamp groove (284, 286) which can be made in the transmission sleeve 200. Each of the lugs 5 2 6 is sufficiently long to protrude outward from the outer surface 2 5 8 of the transmission sleeve 2 00 body 2 4, but is not far enough to project radially outward to the transmission sleeve. Outside of the first clamping groove 284 in the base 216 of the cartridge 200. The configuration of the wire clamp 522 is extremely convenient for the assembly of the transmission assembly 16. The wire clamp 522 can be installed on the second and third ring gears 360 and 400 first, and then the assemblies are driven along the transmission sleeve 200. The longitudinal axis is inserted into the hollow cavity 2-12. With particular reference to Figs. 13 and 27a to 27c, the rotary selection cam 52 may include 99815.doc -22-200533852, a curved selector body 530, a conversion lug 532, and a plurality of spacers 534. There are a pair of first cam grooves 54〇a & 54b, a pair of second cam grooves 544a and 544b, a spring slot hole 546 and a guide slot hole 548, which are made through the selector body 530. The selector body 530 is sized to feed the outer diameter of the body portion 246 of the transmission sleeve 200 in a sliding fit. The guide slot hole 548 may be substantially rectangular, and is sized to engage the front and rear surfaces of the selection cam guide 250. The guide gap hole 548 may be relatively wider than the width of the selection cam guide 250; such a size arrangement is to make the rotary selection cam 520 convenient for the first and second on the transmission sleeve 200 And the third position. The selection cam guide 250 cooperates with the guide gap hole 548 to limit the degree to which the rotary cam 520 may rotate on the transmission sleeve 200; when the rotary selection cam 520 is positioned at the first rotation position, the selection of the cam guide 250 The first side of the guide contact 548 is in contact with the first side of the guide slot 548, and when the rotary selection cam 520 is positioned in the third rotation position, the second side of the selection cam guide 250 and the guide slot 548 The second side is in contact. Each of the first cam grooves 540a and 540b may be sized so as to receive a lug 526 of the wire clip 522 which has been fused to the second ring gear 360. In the particular embodiment shown, the first cam groove 54a includes a first segment 550, a second segment 552, and an intermediate segment. The first segment 55 may be set at a first predetermined distance from a reference plane 558 (which may be perpendicular to the longitudinal axis of the rotary selection cam 520), and the second segment may be set at a distance from the reference At a second predetermined distance from the plane 558. This intermediate segment interconnects the first and second segments 550 and 552. The configuration of the first cam groove "puff 99815.doc -23- 200533852" is identical to the first cam groove 540a, except that the first and second positions on the first cam groove 540b when rotating relative to the rotary selection cam 520 And the intermediate segments 5 50, 552, and 5 54 are respectively disposed 180 ° from the first, second, and intermediate segments 550, 552, and 554 on the first cam groove 540a. Each of the second cam grooves 544a and 544b The size can be arranged to receive a lug 526 of a corresponding wire clip 522. In the illustrated specific embodiment, the second cam slot 544a includes a first segment 560, a second segment 562, a The third segment 564 and a pair of intermediate segments 566 and 568. The first and third segments 560 and 564 are set at a third predetermined distance from the reference plane 558, and the second segment 562 may be Set at a fourth predetermined distance from the reference plane 558. The middle segment 566 connects the first and second segments 560 and 562 to each other, and the middle segment 568 connects the second and third segments 562 and 566. Connected together. The configuration of the second cam groove 544b is exactly the same as that of the second cam groove 544a, only relative to the rotation When the type selection cam 520 rotates, the first, second, third, and intermediate sections 560, 562, 564, and 5 66, 5 68 on the second cam groove 544b are each connected to the second cam groove 544a. The first, second, third, and middle segments 560, 5 62, 5 64, and 566, 5 68 are disposed 180 ° apart. Each lug 526 in each wire clamp 522 engages the first cam grooves 540a and 540b. And the second cam groove 544a and 544b, the rotary selection cam 520 can be rotated between the first, second and third positions 500, 502 and 504 on the transmission sleeve 200, and the second And third ring gears 360 and 400 engage and disengage the first and third reduction brackets 314 and 404, respectively. When the rotary selection cam 520 rotates, the first cam grooves 540a and 540b and the second cam grooves 544a and 544b, The lugs 526 of the related clip 522 are restrained, so that the 998l5.doc -24- 200533852 iso-clamp lugs 526 can only run along the longitudinal direction of the transmission sleeve 200 in the first and second clamping slots 2 84 and 286. The shaft moves. Therefore, the rotary selection cam 52 can be operated to convert a rotary input into an axial output, so that the clamp 522 acts as A predetermined axial movement. A lubricant (not explicitly shown) may be applied to the lubrication groove 252 formed in the body portion 246 of the transmission sleeve 200 to lubricate between the transmission sleeve 200 and the rotary selection cam 520 Positioning the rotary selection cam 520 at the first rotation position 500, resulting in that the lug 526 of the wire clamp 522 that has been engaged to the second ring gear 360 is positioned at the first cam groove 540a, 540b. In a segment 55, the lugs 526 that have been engaged to the clamp 522 of the third ring gear 400 are positioned in the first segment 560 of the second cam grooves 544a, 544b. Therefore, the positioning of the rotary selection cam 52o in the first rotary position 500 will cause the second and third ring gears 360 and 400 to be placed in line with the second and third sets of planetary gears 2 and 402, respectively. Interlocking position. At the same time, because the second and third ring gears 36 and 400 and the second and third sets of planetary gears 362 and 40 are in an interengaging meshing relationship, the second and third ring gears 360 and 400 The sleeve meshing teeth 37 ° and 418 are respectively placed at the positions of the first and second sets of ring meshing teeth 254 and the interlocking teeth a. The second and third ring gears 360 and 400 and the transmission are prohibited. The relative rotation between the sleeves 200 provides the transmission assembly with a first-total gear reduction or speed ratio of 57G, as shown in Figure 23. Those skilled in the art will understand that the first and second groups The annular meshing teeth 254 and 2% of the tip portion 272 of each tooth 268, and the tip portions 372々 and 420 'of the sleeve spray teeth 37 and 418 are made into a circular shape and a tapered shape, respectively, so as to improve them. In response to the axial repositioning along the longitudinal axis of the transmission assembly 16: 99815.doc • 25- 200533852 Ability to engage with each other. Position the square rotary selection cam 520 at the second rotation position 5. 2. The lug 526 that causes the clamp 522 that has been engaged to the second ring gear 360 is placed in the first cam groove 54. The first segment 550_ of 0a, 540b, and the lug 526 that has been engaged to the clamp 522 of the third ring gear 400 is placed in the second segment 562 of the second cam groove 544a, 544b. Therefore, the rotation The type selection cam 52 ° in the first rotation position 502 causes the second ring gear 360 and the second group of planetary gears 362 to have a mutual relationship, and also causes the third ring gear to simultaneously with the third group of planetary gears 402 and the third reduction bracket. 404 is engaged with each other. Positioning the rotary selection cam 520 in the second rotational position 502 also swings the sleeve meshing teeth 3 70 of the second ring gear 3 60 to mesh with the first set of ring meshing teeth 254 In position, however, the sleeve meshing teeth 418 of the third ring gear 400 are not in an interengaging relationship with the ring meshing teeth 256 of the second group. Therefore, between the second ring gear 360 and the transmission sleeve 200 The relative rotation is prohibited, however, the relative rotation between the third ring gear 400 and the transmission sleeve 200 is allowed to 'provide the transmission assembly 丨 6 a second total gear reduction or speed ratio 572' As shown in Figure 24. Position the rotary selection cam 520 In the third rotation position 504, the lug 526 that caused the clip 522 of the second ring gear 360 to be placed in the second segment 552 of the first cam grooves 540a, 5 40b, and has been engaged to the third The lugs 526 of the clamp 522 of the ring gear 400 are placed in the third segment 560 of the second cam grooves 544a, 544b. Therefore, positioning the rotary selection cam 52o in the third rotation position causes the second The ring gear 36 is simultaneously engaged with the second set of planetary gears 362 and the first reduction bracket 314, but the third 99815.doc -26- 200533852 ring gear 400 is only engaged with the third planetary gear 402. The rotary selection cam 520 is positioned at the third rotation position 504, and the sleeve meshing tooth 370 on the second ring gear 360 is placed to a position that does not have a mutual affinity relationship with the first group of ring meshing teeth 254, and the first The sleeve spur teeth 4 1 8 on the three ring gears 4 00 and the group of ring sprocket teeth 2 5 6 are engaged with each other to prohibit the relative between the second ring gear 360 and the transmission sleeve 200. Rotate and allow relative rotation between the third gear 400 and the transmission sleeve 200 to provide the transmission assembly 16—the third total gear reduction or speed ratio 574. In the examples shown in Figs. 13, 27b and 28, the spring member 523 can be made of a flat rectangular spring steel sheet, and includes a flat 2-shaped portion 58 and a raised portion 584. The flat z-shaped portion 580 can be constructed to form two reinforcing bars 586 extending into the spring gap holes 546, so that the raised portion 5 can be maintained in a predetermined position, and can also be selected in a rotary manner. A spring force is transmitted between the cam 52 and the resilient member 523. In addition, referring to FIG. 28, the size of the convex portion 584 of the spring member 523 is designed to be engaged with the inner notch 59o, and the notch 590 is formed in the housing 592 of the output spindle assembly 20. A plurality of table surfaces 594 spaced circumferentially from the rotary selection cam 520 are formed between the plurality of notches 590. When the s output spindle assembly 20 is installed on the transmission assembly η and the speed selection mechanism 60 is installed on the positions of the first, second, and third rotation positions "" and 504, the spring member 523's The raised portion 584 combines one of the notches 590. The spring member 523 turns the selection cam in the downward direction in response to the contact between the raised portion 584 and the table 594: 20 The force will cause the speed selection mechanism 60 to prevent unintentional rotation. In addition, the convex portion 584 is placed in a notch 59〇99815.doc -27- 200533852. Regarding the rotary selection cam 52G The position is in the special and dependent embodiment shown in FIGS. 13 and 27c. The conversion section 51 may include a curved arc 600, with a raised, hollow rectangular selection under the upper 1 Button 602. The curved band 600 can be made of plastic dolphin repair material and can be constructed to have an outer diameter suitable for the rotary selection cam 520. The open end of the selection button 602 can be constructed to accept the conversion lug 532, so that the conversion section 51 and rotary selection

The selection cams 520 can be combined with each other without a fastener. The plurality of spacers are raised portions formed on ^ on the rotary selection cam 52o, which are concentric with the selector body 5 3 0 and extend outwardly into a light private space and widely radiate. The spacer 534 raises the curved band to prevent the curved band from contacting the lug 526 in the first cam groove tear and 540b. The spacer 534 can also be used to selectively reinforce various areas of the rotary selection cam 520, for example, the areas adjacent to the first cam groove 5 and 5 4 0 b.

User-friendly instructions are available in. Those skilled in the art can understand that the rotary selection cam 52 (that is, the first cam grooves 540a and 540b and the second cam grooves 54 and 544b) can be differently constructed so as to cause the second ring gear 36 〇 At the same time, the second group of planetary gears 362 and the first reduction bracket 314 are engaged with each other, and the third ring gear 400 is simultaneously injected with the third group of planetary gears and the third reduction bracket 404. This can provide the transmission assembly i 6 —the fourth total gear ⑥ deceleration or speed ratio. Those skilled in the art will understand that ‘other configuration selection mechanisms may be used in place of the selection mechanism 60 shown herein. These selection mechanisms may include actuators that are actuated by rotation or sliding, or they may include interlocks, cams, or other devices known in the art 99815.doc -28- 200533852 to make the second and third ring gears 360 and 400 glide 200 relative to the transmission sleeve. Those skilled in the art can also understand that because the second and third ring gears 360 and 400 can independently move between the active and inactive modes (the second and third ring gears 36 and 400)- The placement position of one person does not constrain the position selection of the other), the conversion mechanism 60 can also be constructed to place the second and third ring gears 36 and 400 ′, respectively, so that there is no correlation between the two. Clutch mechanism In Figs. 23, 26, and 28-30, the clutch mechanism 18 may include a clutch member 700, a meshing assembly 702, and an adjustment mechanism 704. The clutch member 7⑼ may be a ring structure, and may be fixed to the outer diameter of the first ring gear 31o and extend radially outward from the gear 310. The clutch member 700 may include a clutch surface 316 may be formed on the front surface 318 of the first ring gear 31o. The outer diameter of the clutch member 700 is made to be rotatable in the hollow cavity 212 portion, and the latter is defined by the base 216 of the transmission sleeve 200. With particular reference to the figure, the clutch surface 316 in the legend is shown as being defined by a plurality of spires 71 and valleys 712, which are arranged relative to each other into a series of slopes from-about 18. However, those skilled in the art can understand that other clutch surface configurations can also be used, such as a sinusoidal clutch surface 316, (Figure 29a). Although the first ring gear 310 and the clutch member 700. It has been described as a one-piece (i.e., one-body) structure, which can still be constructed in other ways, and those skilled in the art will understand. Specific examples of other ways are shown in Figure 29b, where the first ring gear 310 'may include an annular collar 1000 and a plurality of ear gap holes 99815.doc -29- 200533852. The annular collar _ may include a plurality of slopes 1004' with double oblique sides, but its dagger aspect is Flat. The other aspects of the first ring gear ^ are exactly the same as the ring gear 31G.-Ring damping member_ abuts the ring collar 1000 and includes a plurality of lug members 1010, the latter and Ear gap hole 1 in the first ring gear 310, 2 slack, to prevent the damping member from rotating relative to the first% -shaped gear 31 ′. The damping member 008 includes a main body blade 1012, which can be constructed to fit the shape of the annular collar 1000. Therefore, a plurality of matching slope portions 1014 are built to be engaged with each slope 1004. The damping member 1008 can be made of a suitable impact damping material, such as acetyl. Clutch member 700, which can be a ring-shaped member made of wear-resistant material (such as hardened 8620 steel), can be arranged above the damping member ι 08. Like the damping member 1008, the clutch member 700 contains a plurality of A lug member 1020 for preventing rotation relative to the first ring gear 310, and a plurality of matching slope portions 1022. The matching slope portion 1022 of the clutch member 700, can be matched The matching ramp portion 1014 of the mode meshing damper 1008. Although such a construction is much more expensive than the foregoing specific embodiment, it has a high impact force associated with the clutch mechanism 18 operation. Greater tolerance. In the particular embodiment shown The engaging assembly 702 includes a pin member 720, a driven spring 722, and a driven member 724. The pin member 720 includes a cylindrical body portion 730 having an outer diameter and is sized to slide in Fitting in the second portion 278 of the driving slot 274, the driving slot 274 is formed in the pin housing portion 248 of the transmission sleeve 200. The pin member 720 further includes a tip portion 732 and a head portion 734. The tip portion 732 can be built to engage with the adjustment mechanism 704 '. However, in the example shown, it is formed on the end of the body portion of the pin member 72〇 99815.doc -30- 200533852 730 with a spherical circular surface as limit. The head 734 may be connected to an end portion of the body portion 730 opposite to the tip portion 732, and may be made into a flat-cylinder or H1 barrel shape. Its size is arranged to be slidably fitted in the first portion 276 of the guide slot 274. . Therefore, 'the head m prevents the pin member ㈣ from being pushed forward out of the guide slot 274. The driven spring 722 may be a compression spring, and its outer diameter may be configured to be slidably fitted into the first portion 276 of the guide slot 274. The front end of the driven spring 722 is in contact with the head 734 of the pin member 720, and the other end is in contact with the driven member 724. The trailing end portion 740 of the follower 724 may be cylindrical and sized to be slidably fitted into the inner diameter of the follower spring 722. In this regard, the trailing end portion 740 of the follower plays the role of a follower of the spring, and prevents the follower spring 722 from being bent when it is pressed. The follower 724 also includes a follower portion 744 having a cylindrical body portion 746, a tip portion 748, and a flange portion 750. The body portion 746 is sized to be slidably fitted into the first portion 276 of the guide slot 274. The tip portion 748 can be constructed to engage the clutch surface 316, and in the example shown, the tip portion 748 is formed on the end of the body portion 746 of the follower 724 and defines a spherical circular surface. The flange portion 750 may be formed at a junction of the body portion 746 and the end portion 74o. The flange portion 750 may be substantially flat and constructed to receive a biasing force that may be exerted by the driven spring 722. The adjusting mechanism 704 may further include an adjusting structure 760 and a adjusting collar 762. The adjusting structure 760 can be made into a substantially hollow cylindrical shape, and its size is configured to fit into an outer shell portion 20 of the output spindle assembly 20 as 766. The adjusting structure 760 includes an annular surface 768 on which 99815.doc • 31- 200533852 can be adjusted to a contour 7 7 0. The tuning profile 7 70 includes an initial adjustment section 772, a last adjustment section 774, a plurality of intermediate adjustment sections 776, and a slope section 778 between the first and last adjustment sections 772 and 774. In the illustrated embodiment, a second slope segment 779 exists between the last intermediate adjustment segment 776z and the last adjustment segment 774. Furthermore, in the illustrated specific embodiment, the adjustment contour 770 is formed from a portion of the initial adjustment to the portion 772 to a portion of the last adjustment portion 776z of the middle adjustment portion to form a slope having a constant slope. Therefore, a follower 780 connected to the output shaft assembly 20 housing portion 766 may be radially biased toward the inside diameter of the adjustment structure 760, where it is formed against the plurality of adjustment mechanisms 704 (i.e., In the setting collar 762) a detent 782 acts. The follower 724 cooperates with a plurality of detents 782 to provide a tool 10 user with a sensible indication of the position of the adjustment contour 770, and also prohibits free rotation of the adjustment structure 760 to maintain the position of the adjustment contour 77 It is on a desired one of the adjustment sections 772, 774, and 776. The adjustment collar 762 can be connected to the outside of the adjustment structure 760, and can include a plurality of raised gripping surfaces 79 °, allowing the user of the tool 10 to comfortably rotate the adjustment collar 762 and the adjustment structure in the same day. 760. Set the adjustment contour 770 to a desired adjustment section 772, 774, and 776. A setting indicator 792 is known to indicate the position of the adjusting contour 770 relative to the output shaft assembly 20 housing portion 766. In the example provided, the setting indication 792 includes a front 794 made in the housing portion of the output spindle assembly 20 and a scale 796 marked on the periphery of the setting collar 762. When the tool 10 is operated, an initial driving torque is transmitted by the motor pinion 46 from 998l5.doc -32- 200533852 to the first group of planetary gears 312, causing the first group of planetary gears 312 to rotate. In response to the rotation of the first set of planetary gears 312, an intermediate torque is applied to the first ring gear 3 10. Against this torque is a clutch torque known by the clutch mechanism 18. The clutch torque prohibits the free rotation of the first ring gear 3 10, causing the intermediate torque to be used on the first reduction bracket 314 and the remaining components of the reduction gear assembly 202, resulting in the first intermediate torque being based on The setting of the conversion mechanism 60 is increased in a predetermined manner. In this regard, the clutch mechanism 18 biases the first reduction gear set 302 in the effective mode. The magnitude of the clutch torque is determined by the adjustment mechanism 704, and more specifically, 疋 is controlled by the relative height of the adjustment sections 772, 774, and 776 in contact with the tip portion 732 of the pin member 720. The adjustment mechanism 704 is positioned on a predetermined adjustment section 772, 774 or 776, and the pin member 720 in the driving gap hole 274 is pushed backward, thereby compressing the driven spring 722 and generating a clutch force. This clutch force is transmitted to the flange portion 750 of the follower 724, causing the tip portion 748 of the follower 724 to engage the clutch surface 316 and generate a clutch torque. The tip portion 748 of the follower 724 is placed in a valley 712 of the clutch surface 316. When the magnitude of the clutch torque exceeds the first intermediate torque, the first ring gear 3 1 can be prohibited from opposing. The rotation of the drive sleeve 200. When the intermediate torque exceeds the clutch torque ', the first ring gear 31 may be allowed to rotate relative to the transmission sleeve 200. Depending on the configuration of the clutch surface 316, the rotation of the first ring gear 310 may cause the clutch force to increase to a degree sufficient to resist further rotation. In this case, 'when the intensity of the intermediate torque decreases, the first ring gear 3 1 0 will rotate in an opposite direction, and let the tip portion of the follower 724 be 748 99815.doc -33- 200533852 The pair is on a concave valley 712 of the clutch surface 316. If the rotation of the first ring gear 31〇 • does not cause the clutch force to increase sufficiently to fully resist the rotation of the first ring gear 31〇, the first reduction gear set 302 will rotate to limit the torque Transmission to the first reduction bracket 3 丨 4. The configuration of the clutch mechanism 18 is extremely advantageous, because the clutch torque is divided into magnitudes to resist the first intermediate torque, which is generated by the multiple reduction gear transmission assembly 16 with the tool 10 and transmitted via the chuck 22 When the output torque is opposed. Because of this, the clutch mechanism 18 can be made into a relatively small volume, thereby improving the ability to be incorporated into or incorporated into the tool 10. In addition, since the speed or gear ratio is changed after or downstream of the first ring gear 310, the clutch mechanism 18 can be operated within a range of a larger output torque. Compared with the traditional clutch mechanism that limits the output torque of the transmission mechanism by operation, these mechanisms are typically operated in a relatively narrow torque range. If the output torque needs to be changed substantially, it must be in their Change on the clutch spring. Very different, the clutch mechanism 18 of the present invention, as long as the transmission assembly 16 is simply run at a different (ie, lower or higher) gear ratio, the tool can be equivalent to 10 Large degree of output torque conversion. When operating a rotary power tool such as the tool 10, it is often necessary to change between the two clutch settings, such as when the tool 10 is used for drilling and then installing screws in the holes. Then, you can turn the adjustment mechanism Chuan 4 to make the relative output spindle assembly 20 turn to the adjustment sections 772, 774, and 7%. Stop at the desired section to perform the first task, and then, turn to Stop at the second subsection of the adjustment subsections 772, 774, and 776 to perform the second task. Different from the known clutch device, the adjustment of the present invention: 99815.doc.34-200533852 system 704 is constructed so that the adjustment structure 760 and the setting collar 762 can be rotated through a 360 ° angle. Assume that the adjustment structure 760 is fixed on an intermediate section 776x. After the adjustment mechanism 704 rotates through 360 °, the adjustment structure 760 will rotate through the other intermediate sections 776, and also through the first and last adjustment sections 772, 774, and The ramp section 778 causes the adjustment structure 760 to be set on the intermediate adjustment section 776x again. This feature is especially helpful when you have to change the clutch setting between a higher clutch setting and a lower clutch setting. At this point, the ramp section 778 allows the setting collar 762 (and the adjusting structure 760) to be turned from the highest clutch setting (corresponding to the last clutch setting) to the lowest clutch setting (corresponding to the initial clutch setting) without using The clutch mechanism 18 is first placed in a middle clutch setting. Therefore, the user of the tool 10 can change the clutch setting from the maximum setting to the minimum setting by turning the setting collar 762—a relatively small amount (and vice versa). Although the adjustment contour 770 has been described so far with a constant slope, those skilled in the art can agree that the present invention can be constructed slightly differently in terms of its broader aspects. For example, the adjustment contour 770 'can be made such that the first, last, and middle adjustment sections 722', 774 ', and 776' become jagged as shown in FIG. In this arrangement, the recesses 782 in the adjustment structure 760 and the followers 780 in the output spindle assembly 20 housing portion 766 are not necessary because the adjustment sections 722, 77V, and 776 'will In cooperation with the adjustment mechanism 702, a user of the tool 10 is provided with a sensible hint about the adjustment contour 770 ', while at the same time inhibiting the free rotation of the adjustment structure 760. Another example is shown in Fig. 32, where the adjustment contour 770 "is probably similar to 99815.doc -35- 200533852, except that the slope section 779 has been omitted, so that the last intermediate adjustment section 776z is directly adjacent This final adjustment is divided into sections 774. Although the transmission assembly 16 has been explained so far including a three-stage, three-speed transmission mechanism, a person skilled in the art will know from this content that the present invention, in its broad sense On the other hand, it can be constructed slightly differently. For example, if two reduction gear sets (such as both the second and third reduction gear sets 304 and 3 06) are operated in the ineffective mode, another (ie Fourth) or different speed ratios. Ordinary artisans in this process can also learn from this content that by combining the second ring gear 360 to the second planetary carrier 364 (instead of to the first planetary carrier 314), The second reduction gear set 300 can be placed in an ineffective mode, and / or the third ring gear 400 can be coupled to the second planetary carrier 364 (rather than the third planetary carrier 400). ) Can make the third reduction gear 306 It is in an ineffective mode. Other transmission assemblies constructed in accordance with the teachings of the present invention are shown in Figures 3 to 56. In summary, these configurations are similar to those previously stated and are shown in detail in Figure 23- The configuration of 35. Therefore, the similar or equivalent components of each alternative construction of the transmission assembly are identified by reference numerals similar to those used to describe the transmission assembly 16. In the example in Figure 33-35, the transmission The assembly 16-1 may include one or more movable elements that may be used to selectively couple the ring gears of the first and third reduction gear sets 304-1 and 306_1 to the transmission sleeve 200-1, respectively. The components can be pins 2000 and 2000, which can be inserted into the transmission sleeve 2 'and passed through the corresponding gap holes 2004 and 2_ in the transmission sleeve purchase, and can be moved to or from the Another ring gear (ie 99815.doc • 36-200533852 bad gear 360-1 or 400-1) meshes. In the example provided, the ring gear-wheels 36〇-1 and 400-1 each include a plurality Teeth 370-1 and 418-1 (similar to teeth 370 and 418 shown in FIG. 23, respectively), with a sufficient distance between the two Set so that the pins 2000 and 2000 can be received in between. The ring gears 3 60-1 and 400-1 are locked to the drive sleeve 2000-1 as shown in Figure 33 Next, the transmission assembly 16-1 operates in the same manner as stated in the previous correlation diagram. In Figure 34, it is shown that the transmission assembly 16_ 丨 is below the second overall speed or gear • reduction ratio , Wherein the first and second reduction gear sets 302-1 and 304-1 are in an effective condition and the third reduction gear set 300-1 is in an ineffective condition. The third reduction gear set 306-1 can make it idle, and by moving (such as translating) the pin 2002 to disengage it from the tooth 418-1 of the ring gear 400-1, and engage the third planetary carrier 404-1 to the first Three ring gear 400-i. The latter action can be completed by sliding the third planetary carrier 404-1 toward the third ring gear 400-1 and meshing with it. Any suitable means may be adopted to cause the third planetary carrier 404-1 and the third ring gear 400-1 to mesh with each other, including friction (i.e., frictional meshing), special parts, such as pins or teeth, the latter may be manufactured in the first One or both of the three planet carrier 4044 and the third ring gear 400-1. In the example provided, a plurality of teeth 20 10 formed on the third ring gear 400-1 mesh with the mating teeth 2012 made on the planet carrier 404-1. It is shown in FIG. 35 that the transmission assembly 1 6-1 is at the third total speed or the gear reduction ratio, in which the first and second reduction gear sets 302-1 and 306-1 are in effective condition. The second reduction gear set 304-1 is in an ineffective state. The second reduction gear set 304-1 can make it idle, and by moving (such as flat 99815.doc -37- 200533852 to move) the pin 2_ to disengage it from the ring gear 36 (M's tooth t, and The first planetary carrier 314-1 is meshed with the second ring gear. This post-action, for example, can be accomplished by sliding the first planetary carrier M! Toward the second ring gear 36 (M and yelling with it. Any Appropriate means can be used to make the second ring gear of the first planetary bracket 314 rhyme yell at each other, including friction (that is, friction resonance), special parts such as lock cylinders or teeth, the latter can be made in the first- Planetary bracket 314 ″ and the second ring gear 3㈤—

Either or both. In the provided fancai, a plurality of teeth 2014 formed on the second ring gear 360-1 and the mating teeth 2016 formed on the first planetary support η center 1 are sialed. Those skilled in the art will agree that although the movable element (ie, Cylinder fiber and 2002) has been illustrated to translate in a direction approximately perpendicular to the longitudinal axis of the 16 rhyme of the transmission assembly ', the present invention is in its broadest aspect In terms of construction, it can be constructed slightly differently. For example, each movable element can be translated between the first and second positions in a direction approximately parallel to the 16-i longitudinal axis of the transmission assembly; in the ㈣-position, the movable element is allowed Spraying a special part on a respective ring gear, and in the second position, the movable element can be aligned on the ring gear—annular groove or flat / month. There is no feature so that the movable element does not prohibit the rotation of the individual ring gear. The transmission assembly 16-2 of Figs. 36 to 38 is a specific example which is roughly similar to that of Figs. 33 to 35. The [reduction gear set 3 () 2々 of the _th planetary gear 344 and the third reduction gear set The third set of planetary gears of 3 () 6_2 still stays in a fixed position relative to the [and third ring gears and · "99815.doc -38-200533852, regardless of the first and third planetary supports 3 What are the positions of 14-1 and 404-1? Completely different, in the specific embodiments of FIGS. 33 to 35, the first set of planetary gears 344 and the third set of planetary gears 402, respectively, slide with the first and third planetary carriers 314-1 and 404-1. . With reference to Figures 39-41, the transmission assembly 16-3 may include one or more locking elements' optionally used to lock the second and third ring gears 360_3 and 400-3 to the first and the third, respectively. Three planetary brackets 314-3 and 4 04-3. The locking element may include, for example, first and second idler gears 2050 and 2052, for example, may have teeth 2050a and 2052a, respectively, and the latter two may be formed on the first and third planetary brackets 314-3, respectively. And the teeth 314a and 404a on 404-3 and each other bite into spit. The locking elements 2050 and 2052 can be rotatably supported on the pins 2054 and 2056, respectively, and the latter two can be mounted on another part of the power tool, such as the transmission sleeve 200-3. At the first reduction ratio shown in FIG. 39, «1st and 3rd ring gears 3 60-3 and 400-3, for example, with the help of the ring > gears 360-3 and 40 0- The teeth 370-3 and 418-3 on the outer diameter 3 mesh with the teeth 254-3 and 256-3 formed inside the transmission sleeve 200-3, respectively, and are fixed to the transmission sleeve 200-3. In Fig. 40, it is shown that the transmission assembly 6-3 is under the second total gear reduction ratio, in which the first and second reduction gear sets 302-3 and 30-4 · 3 are effectively used Under the condition, the second reduction gear set 306-3 is in an ineffective condition. By translating the third ring gear 400-3, the teeth 4 丨 8 · 3 are not meshed with the mating teeth 256-3 on the transmission sleeve 2000-θ3, but are engaged with the teeth 2052 of the second idler gear 20052 & Engagement can make the third reduction gear set 306_3 ineffective (idling). The translation of the third ring gear 400-3 'may also cause the third planetary carrier 404_3 to slide onto the second idler gear 2052 of 998l5.doc -39- 200533852, and / or cause the third group of planetary gears 402 to face each other The transmission sleeve 200-3 slides. In FIG. 41, it is shown that the transmission assembly 16_3 is below the third total gear reduction ratio, where the first and third reduction gear sets 30.2 · 3 and 30.6_3 are in the effective condition and the second The reduction gear set 304-3 is in an ineffective condition. By translating the second ring gear 360_3, the tooth 37〇_3 does not mesh with the mating tooth 254-3 on the transmission sleeve 2000_3, but is in contact with the tooth 2050 of the first idler gear 2500. ; Engagement can make the second reduction gear set 304_3 idle. The translation of the second ring gear 36〇_3 can cause the first planetary carrier 314_3 to slide onto the first idler gear 2050, and / or cause the planetary gear 344 of the first group to slide relative to the transmission sleeve 200-3. With reference to Figures 42-44, the transmission always uses “the second reduction gear set 304-4 and the third reduction gear set 306_4 can be constructed to slide into and out of the gear and engage with another component of the transmission assembly 16_4. In the provided In the example, the first and second sets of planetary gears 382-4 and 402-4 can be respectively in a first position (which is in mesh with an associated ring gear) and a second position (which is in association with a related planet The bracket meshes in a non-rotatable manner, and at the same time engages with the related ring gear in an interengaging manner. Under the first reduction ratio shown in FIG. 42, the second and third ring gears 36〇_4 and 4〇〇_4 is fixed to the drive sleeve 2000-4 in the same way as explained in relation to Figure 33. In Figure 43, the drive assembly 16_4 is under the total speed or gear reduction ratio, where the The first and second reduction gear sets 30-2_4 and 30-4_4 are in an effective condition and the third reduction gear set 306_4 is in an ineffective condition. With the help of the translation pin 脱 2002, the third ring gear is released The meshing of the teeth on 〇〇_4 99815.doc -40- 200533852 418-1 and translate the The third set of planetary gears 402-4 enters intermeshing with the third row-star bracket 404-4, so that the third set of planetary gears 402-4 can be kept in phase. • The second planetary bracket 404-4 is stationary. In a stationary state, the third reduction gear set 306-4 can be idled. The engagement of the third set of planetary gears 402-4 with the third planetary carrier 404-4 can be performed in any manner, such as frictional engagement or via combination Special parts. In the example provided, teeth 2076 are formed on the axial end face of the third set of planetary gears 402-4, and mating teeth 2078 are formed on the third planetary carrier 404-1; The mating tooth 2078 interengages with the tooth sight 2076 on the third group of planetary gears 40-2_4. The third ring gear 400_4 can be translated in parallel with the third group of planetary gears 402-4, as shown in the figure. 44 shows that the transmission assembly 丨 6-4 is at the third overall speed or gear reduction ratio, wherein the first and third reduction gear sets 3 〇2-4 and 306-4 are under effective conditions and the first The second reduction gear set 30-4-4 is in an ineffective condition. With the translation pin 2000, it is disengaged from the tooth 370-1 on the second ring gear 36〇_4. Close, and translate the second set of planetary gears 382-4 into mesh with the first planetary support 3 14-4, so that the second set of planetary gears 382-4 remains stationary relative to the first planetary support 3 14-4 Under the condition, the second reduction gear set 304-4 can be idled. The meshing of the second planetary gear 382-4 with the first planetary carrier 3 14-4 can be performed in any desired manner, such as frictional meshing or via combination In the example provided, the teeth 2072 made on the axial end face of the second set of planetary gears 382_4 are mated with the teeth 2074 made on the first planetary carrier 314_4. The second ring gear 360-4 may be translated in parallel with the second group of planetary gears 382-4 as appropriate. Figures 45 to 47 show yet another transmission structure constructed in accordance with the teachings of the present invention 99815.doc -41- 200533852 to 16-5. The transmission assembly 16-5 can include more than one movable element, such as pins 2000 and 2002, which can be used to lock the second and third ring gears 360-5 and 400-5, respectively, in a stationary position. And the locking elements, such as the first and second idler gears 2050-5 and 2052-5, can be used to lock the second and third ring gears 360-5 and 400-5 to the first and third planetary carriers respectively. 3 14-5 and 404-5. With particular reference to FIG. 45, the figure shows that the transmission assembly 16_5 is in the case of the first overall reduction or gear ratio, wherein the pins 2000 and 2002 can be placed with the second and third ring gears 36 respectively. The teeth 370-1 and 418-1 of _5 and 400_5 are held in a quiescent position, and the second and third ring gears 360-5 and 400-5 are maintained in a rest position, respectively. In this case, the first and second idler gears 205 0-5 and 205 2-5 can be separated from the teeth 370-1 and 418-1 of the second and third ring gears 360-5 and 400-5. At the same time, it also disengages from the teeth 3 14a and 404a of the first and third planetary supports 314-5 and 404-5. In FIG. 46, it is shown that the transmission assembly 16-5 is under the second total reduction or gear ratio, wherein the first and second reduction gear sets 3 02-5 and 3 04-5 are in an effective condition, The third reduction gear set 306-5 is in an ineffective condition. The third reduction gear set 306-5 can make it idle, and disengage the tooth 418-1 of the third ring gear 400-5 by the translation pin 2002, and by translation and / or rotation, for example, the idler gear 2052 -5 is moved into a position so that the teeth 2052a of the idler gear 2052-5 and the teeth 418-1 of the third ring gear 400-5 and the teeth 404a of the third planetary carrier 404-5 are simultaneously engaged with each other. In FIG. 4, it is shown that the transmission assembly 16-5 is under the third overall reduction or gear ratio, wherein the first and third reduction gear sets 3 02-5 and 3 06-5 are in an effective condition. , And the second reduction gear set 304-5 is in an ineffective condition 99815.doc -42- 200533852. The second reduction gear set 304-5 can make it idle, and by the translation pin 2000, it can be separated from the tooth 370-1 of the second ring gear 360-5, and by translation and / or rotation, for example, the idler The gear 2050-5 is moved in such a way that the teeth 2050a of the idler gear 2050-5 are simultaneously interlocked with the teeth 370-1 of the second ring gear 360-5 and the teeth 314a of the first planetary bracket 314-5. position. 48 to 50 show yet another transmission assembly 16-6 constructed in accordance with the teachings of the present invention. The transmission assembly 16-6 may include more than one movable element, such as idler gears 2050-6 and 2052-6, which can be used to lock the ring gears 36〇_6 and 400-6, respectively. A stationary drive sleeve 200_6 is stationary. Do not move, or lock the first and second ring gears 360-6 and 400-6, so as to rotate with the first and third planetary supports 314-6 and 404-6, respectively. With particular reference to FIG. 48, it is shown that the transmission assembly 16-6 is under the first overall reduction or gear ratio, wherein the idler gears 2050-6 and 2052-6 are fixed to maintain the second and third ring gears 36〇6. And 400 · 6 in a stationary position. The idler gears 2050-6 and 2052-6 can engage a special part, such as teeth 2090 and 2092, respectively, and are formed on another part of the power tool (such as the housing 12_6 or the transmission sleeve 2000_6). The latter prohibits the rotation of the former, thereby locking each ring gear in a rest position. It is shown in FIG. 49 that the transmission assembly 16_6 is under the second overall reduction or gear ratio, wherein the first and second reduction gear sets 3002_6 and 34.0_6 are in an effective condition and the third reduction gear Group 3 06_6 is in an ineffective condition. The third reduction gear set 3 06_6 can make it idle. With the help of translational idler gear 52 6, for example, it enters a position along the journal pin 2096, so that the teeth 2052 2a of the idler gear 2052-6 are not equal to one or A plurality of teeth 2092 mesh, but at the same time, they are sprayed with teeth 418-1 of the second ring gear 400-6 and teeth 404a of the third planet carrier 4 04-6. In FIG. 50, it is shown that the transmission assembly 16-6 is under the third overall reduction or gear ratio 'wherein the first and third reduction gear sets 3 02-6 and 306-6 are under effective conditions' and the first The second reduction gear set 304-6 is in a state of ineffectiveness, brother. δ Hai first reduction gear set 304-6 can make it idle, by translating the idler shaft 2050-6, for example, entering a position along the shaft pin 2096, so that the teeth 2050a of the idler gear 2050-6 are not equal to one or The plurality of teeth 2090 mesh, but simultaneously mesh with the teeth 370-1 of the second ring gear 360-6 and the teeth 3 14a of the first planetary carrier 314-6. In Figs. 51 to 53, a further transmission assembly 16-7 constructed in accordance with the teachings of the present invention is shown. The transmission assembly 16-7 may include more than one movable intermediate locking element, such as the collars 3000 and 3002, which can be used to lock the second and third ring gears 360-7 and 400-7, respectively, at a stationary position. Position, or respectively "the first and the first planetary brackets 314-7 and 404-7 together to rotate. Especially in relation to Figure 51, the figure shows that the transmission assembly 16_7 is under the first total reduction or gear ratio, The collars 3000 and 3002 are fixed in a position that can maintain the second and first ring gears 360-7 and 400_7. The collars 3000 and 3 002 can be connected with the second and first ring gears respectively. The third ring gears 36〇_7 and 4 have tooth pods and 418.1 meshed, and may have special parts (such as teeth or pins 3004 and 3006) that can be used to mesh with other parts formed in the power tool, respectively. (Such as the transmission sleeve 200-7) with a coupling member (such as a tooth or a gap hole 3008) to lock another ring gear in a rest position. The transmission assembly 16_7 is shown in FIG. 52 The second total reduction or gear ratio is below 99815.doc -44-200533852, wherein the first and second reduction gear sets 302-7 And 304-7 is in the effective condition and the third reduction gear set 3 0 6-7 is in an ineffective condition. The third reduction gear set 306-7 can make it idle, and enter by translation of the collar 3002 In one position, the pin 3006 can be released from the gap hole 3008 on the transmission sleeve 200_7, and the collar 3002 is simultaneously engaged with the teeth 418-1 of the third ring gear 400-7 and the third planetary bracket 404-7. Taken Any suitable method to cause the collar 3002 to interengage with the third planetary bracket 404-7, including friction (ie, frictional engagement), or be formed in one or both of the third planetary bracket 404-7 and the neck ring 3002 Special parts such as pins or teeth. In the example provided, the collar 3002 frictionally engages the planetary bracket 404-7. The transmission assembly 16_7 is shown in FIG. 53 Three total reductions or gear ratios' where the first and third reduction gear sets 3 02-7 and 3 06-7 are in an effective condition, and the second reduction gear set 304_7 is in an ineffective condition .To make the first reduction gear set 304-7 idling, it is to move the pin 3004 out of the transmission by translating the journal 3000. Clearance holes on the sleeve 200-73008, and the collar 3000 while the teeth of the third ring gear 36〇-7 "heart Shu and planet carrier 314-7 first engaging position. The collar 3000 and the second planetary bracket 314_7 can be engaged with each other in any suitable manner, including friction (that is, frictional meshing) 'or formed in one or both of the third planetary bracket 314_7 and the neck ring 3000. Special parts (such as pins or teeth). In the example provided, the collar 3000 is frictionally engaged with the planetary carrier 3 14_7. Figures 54 to 56 are generally the same as the specific embodiments of Figures 51 to 53, except that each of the shafts ¥ 3000-8 and 3 002-8 has teeth 3050 and 3 052, respectively, and is formed on the second and third ring gears, respectively. The teeth on 360-8 and 400-8 are 370_8 and 99815.doc • 45 · 200533852 418-8 Interlocking meshing exception. The collar 30000_8 can be translated to a position where the gear tooth 3050 is simultaneously with the tooth 3708_8 of the second ring gear 36〇-8 and the tooth 314a of the first fixed star bracket 314-8. Mesh, so that the second reduction gear set 304-8 is in an ineffective mode. Similarly, the collar 3002_8 can be translated to a position where the gear teeth 3052 simultaneously mesh with the teeth 418-8 of the third ring gear 400_8 and the teeth 404a of the second planetary carrier 404-8. Therefore, the third reduction gear set 306-8 is in an ineffective mode. Although the present invention has been explained in this specification, and illustrated in the drawings for various specific specific examples, however, those skilled in the art will understand that there are various changes that can be made and equivalents can be made. Replace its components without departing from the scope of the invention as defined in the scope of the patent application. In addition, the mixing and cooperation of special parts, components, and / or functions between various specific embodiments have been explicitly covered in this article, so ordinary artisans in this process can also know from the content of this article, a specific The special features, elements and / or functions in the embodiments may be appropriately incorporated in another specific example, unless otherwise stated previously. In addition, many modifications may be made to adapt to a particular situation or material in connection with the teachings of the present invention. Therefore, the present invention is not intended to be limited to the specific embodiments listed in the drawings and stated in the present specification as the best mode for implementing the present invention, but will include any incorporated in the scope of the foregoing specification and the appended patents. Within specific embodiments. [Brief description of the drawings] Figure 1 is a side view of a power tool constructed according to the teachings of the present invention; Figure 2 is an exploded view of a part of the power tool of Figure 1; 998l5.doc -46-200533852 Figure 3 is a power tool of Figure 1 An exploded view of a part showing the rear of the cap assembly; FIG. 4 is a front view of the end cap assembly; FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 4; FIG. 6 is a part of the power tool of FIG. Rear view after removing the end cap assembly; FIG. 7 is a side view of a part of the power tool of FIG. 1 after the end cap assembly is removed.

FIG. 8 is a view similar to FIG. 4 except for showing the end cover shell before the overpressure forming operation; FIG. 9 is a view similar to FIG. 5 except for showing the end cover shell before the overpressure forming operation; FIG. 10 is a view similar to FIG. 4 except that it shows an alternative structure of the over-pressure forming member; FIG. 11 is a partial cross-sectional view of a part of a power tool; The compression-molded component is constructed in the style shown in FIG. 10; FIG. 12 is an exploded perspective view of a part of the power tool of FIG. 1, showing the moving assembly in more detail; FIG. 13 is a one-speed gear set assembly of the power tool of FIG. Part of the transmission sleeve; 4 is an exploded perspective view, which is more detailed and undiminished, a part of the casing and the clutch mechanism. Figure 13a is a cross-sectional view taken along the longitudinal axis of the second ring gear. Figure 13b is a third ring Sectional view of the longitudinal axis of the gear · 99815.doc -47- 200533852 Fig. 14 is a side view of a transmission sleeve; Fig. 15 is a rear view of a transmission sleeve; Sectional view; Figure 17 is a straight line in Figure 15 ... taken with a knife Fig. 18 is an exploded view of a reduction gear assembly;-Fig. 19 is a cross-sectional view taken along the longitudinal axis of a power tool, showing a part of the reduction gear assembly in more detail;

Figure 20 is a front view of a part of the-reduction bracket; Figure 21 is / σ mesh! A cross-sectional view of the longitudinal axis of the power tool, showing a part of the reduction gear assembly in more detail; FIG. 22 is a rear view of a part of the third reduction bracket; FIG. 23 is a cross-sectional view of / σ FIG. 24 shows a transmission assembly placed at the first speed ratio position; FIG. 24 is a cross-sectional view similar to FIG. 23, but shows the transmission assembly placed at the second speed ratio position; FIG. 25 is a view similar to FIG. Sectional view, only showing the transmission assembly placed at the third speed ratio position; Figure 26 is a top view of a part of the power tool of Figure 1, showing the speed selection mechanism in more detail; Figure 27a is one side of a rotary selection cam View; Figure 27b is a top view of one of the rotary selection cams; Figure 27c is a cross-sectional view taken along the main axis of the speed selection mechanism; Figure 28 is a rear view of an output spindle assembly; Figure 29 is a clutch mechanism An exploded perspective view; 99815.doc -48- 200533852 Figure 29a is a perspective view of a part of the clutch mechanism, showing another configuration of the clutch member; Figure 29b is an exploded perspective view showing the first ring gear A multi-piece structure of a wheel and a clutch member; FIG. 30 is a schematic diagram of an adjustment structure in a “flattened” state; FIG. 31 is a schematic diagram similar to FIG. 30, showing only an adjustment contour—a flexible construction; and

FIG. 32 is a schematic diagram similar to FIG. 30, except that it shows a part of another alternative construction of the adjusting roe; FIGS. 33 to 35 are cross-sectional views similar to FIGS. 23 to 25, respectively, following the first embodiment constructed according to the teachings of the present invention. Figs. 36 to 38 are cross-sectional views similar to Figs. 23 to 25, respectively, taken along the longitudinal axis of a third transmission device constructed in accordance with the teachings of the present invention; Figs. 39 to 41 are similar to 23 to 25 are cross-sectional views taken along the longitudinal axis of a fourth transmission device constructed in accordance with the teachings of the present invention; Figs. 42 to 44 are cross-sectional views similar to Figs. 23 to 25, respectively, along a fifth construction constructed in accordance with the teachings of the present invention; Figures 45 to 47 are cross-sectional views similar to Figures 23 to 25, respectively, taken along the longitudinal axis of a sixth transmission constructed in accordance with the teachings of the present invention; 48 through 50 according to the present invention are sectional views similar to Figs. 23 to 25, respectively, taken along the longitudinal axis of the invention teaching construction of the seventh transmission; Figs. 51 to 53 are respectively similar to Figs. 23 to 25 sectional views, the invention teaches Constructor Figures 54 to 56 are cross-sectional views similar to Figures 23 to 25, respectively. 99815.doc -49- 200533852 The vertical axis of the ninth transmission device constructed by the teachings of the invention; [Description of main component symbols] 10 Power tool 12, 592 Housing 14 Motor assembly 14a Outer diameter 14b, 342, 352, 366, rear surface 414, 430

14c Motor housing 14d Motor 16, 16-1, 16-2, 16-3, Transmission assembly 16-4, 16-5, 16-6, 16-7 18 20 22 24 26 30 32 34 36 38 40 Clutch mechanism Output Spindle Assembly Chuck Plate Machine Assembly Battery Pack End Cap Assembly Handle Case Assembly Handle Case Handle Part Drive Series or Body Part Motor Cavity Transmission Cavity 99815.doc -50- 42 200533852 44 Output shaft 46 Motor pinion 46a Gear 60 (speed) selection mechanism or conversion mechanism 100 End cap shell 102 Over-molded part 104 End cap cavity 108, 110 Radial ear gap 114, 328, 406, 436 Forward face 116 Screw convex face 124, 314, 324, 380, 430 rear facing surface 128 abutting surface or curved portion 132 abutting surface 136 motor cover 138 screw 139 rear handle slot hole 140 side slot hole 144 rear slot hole 146 recessed portion 148, 230, 258 outside surface 150 through parts 152, 338, 452 retaining lugs 154, 234 > 242 > 266 inside surface 156 channel 99815.doc -51- 200533852

170 172 174 188 190 200, 200-1, -3, 4, -6 202 210 212 214 216 220 226 > 594 228 '232 230 238 246 > 730 ^ 1012 248 250 252 254, 254-3, 256, Anti-collision parts, spacers, connection parts, space motors, armature bearings, transmission sleeves, reduction gear sets, assembly wall parts, transmission inner cavity or hollow cavity, body front part, table surface, groove, outer surface, collimating rib body part, pin shell part, and cam guide lubrication. Agent slot spraying teeth or mating teeth 256-3, 2012 2016, 2074, 2078 housing part 260 > 262 > 766 99815.doc -52- 200533852 264 round flange 268 ^ 2010 > 2014 > tooth 2050a, 2052a, 2072, 2076, 2090, 2092

270 272 > 372 '420 ^ 732 > 274 276 278 284' 286, 374 '422 288, 318, 328, 340, 350' 368, 412 302 > 302-1 ^ 302-2-Apparent surface 748 tip Partially actuated gap hole Part I Part II Slotted front surface First reduction gear set 302-3, 302-4, 302-5, 302-6, 302-7 3 04, 304-1, 304-2, second Reduction gear set

304-3, 304-4, 304-5, 304-6, 304-7 306, 3 06_1, 306-2, third reduction gear set 306-3, 306-4, 306-5, first ring gear (Or reduction element) Group planetary gears First planet (or reduction) bracket 306-6 > 306-7 ^ 306-8 310, 3101 312 '362, 402, 402-4 314, 314-1, 314-2, 99815.doc -53- 200533852 314-3, 314-4, 314-5, 314-6, 314-7

314b, 314 *, 404b, 404b1 310a, 314a, 344a, 358a, 3360a, 82a 398a '400a, 404a' 438a, 316, 3161 320 322, 378, 428, 2000, 2002 '2054, 2056, 2096 3004, 3006 326 , 330, 369, 407, 434, 332, 450 334, 336 344, 382, 382-3, 382-4, 438 348, 584 358, 398 360 > 360-1 ^ 360-3 > 360-4, 360 -5, 360-6, 360-7 364 370, 370-1, 370-3, Valley gear tooth clutch surface step pin circular arc thrust washer ring part planetary gear (individual) convex part too% gear second Ring gear (or reduction element) The first planet (or reduction) bracket sleeve Jingran gear teeth 98815.doc -54- 200533852 370-8, 418, 418-1, 418-3, 418-8 376, 424 384, 440 400, 400-1, 400-3, 400-4, 400-5 '400-6, 400-7, 400-8 404, 404-1, 404-2, side ring pin slot holes third ring gear ( Or reduction element) third planet (or reduction) bracket

404-3, 404-4, 404-5, 404-6 '404-7, 404-8

454 458 460 500 502 504 510 512 520 522 523 524 526 530 532 532 534 Lug slot transmission member Spindle rotation position conversion part Induction part Rotary selection cam clip spring member Semicircle lug selector body conversion lug spacer 99815 .doc -55- 200533852

540a, 540b, 544a, 544b Cam grooves 548 550, 552, 554, 560, 562, 564, 566, 568 558 570, 572 '574 580 586 590 600 602 700 ^ 700? 702 704 710 712 720 722 730, 746, 746, 1012 734 740 744 750 760 Guide slot segmented reference plane Total gear reduction or speed ratio Z-shaped part Reinforcement notch Curved belt selection group Clutch member meshing assembly Adjustment mechanism Spire concave pin Pin follower body part Head and tail end driven part flange part adjustment structure 99815.doc -56- 200533852

762 768 770, 770, 770-, 772, 772f, 774, 774 'ΊΊ6, ΊΊ6}, ΊΊ6ζ 778 ^ 779 782 790 794 796 1000 1002 1004 1008 1010, 1020 1014, 1022 2004, 2006, 3008 2050, 2050-5 , 2050-6 2052, 2052-5, 2052-6 3000 ^ 3000-8 > 3002 ^ 3002-8 Adjusting the collar ring surface Adjusting the profile adjusting segment slope segment detent or recess grip surface arrow scale ring collar Lug hole ramp damper lug ramp part gap, locking element or idler gear collar 99815.doc -57-

Claims (1)

200533852 10. Scope of patent application: 1. A portable power tool including: a housing; a motor having a motor output member; a driven member; and a transmission device i which is disposed in the housing, and The structure can receive-rotate input from the motor output member, and can produce-rotate output transmitted to the output spindle; the transmission device has a plurality of planetary transmission stages, each transmission stage includes an annular ring gear, a planetary support , And a plurality of planetary gears supported by the 仃 star bracket to inter-engage with the ring gear; 忒 = the 装置 transmission device further includes at least one component, which can be built in the first condition, which makes such At least one of the planetary gear stages can be operated in an active mode; and can be built in a second state, which enables at least one of the planetary gear stages to be operated in an inactive mode; where The transmission is operable at at least three total reduction ratios. 2. The portable power tool of claim T, wherein the at least one component includes a #knife which can selectively engage a related ring gear, thereby prohibiting relative rotation between the related ring gear and the portion. . If the portable power tool of claim 2, the part includes at least one of a pin, a ball and a roller. 4. ^ The portable power tool of claim 2, wherein the at least one component further includes a plurality of teeth made on the related planetary support, and a plurality of teeth made on 99815.doc 200533852 § the related ring gear and the related plural At least one of the planetary gears, U4, and wherein the special teeth and the mating teeth are coupled with each other to facilitate the common rotation of the related% -shaped gear and the related planetary carrier. 5. The portable power tool as described in claim 4, wherein the teeth extend axially from at least one of the related ring gear and the related plurality of planetary gears, and the related planetary support and The at least one of the related ring gear and the related plurality of planetary gears can be engaged with the mating teeth when they abut each other. 6. 7. 8. 9. • The portable power tool of member 4, wherein the teeth are formed around the inner diameter of the relevant $ U wheel, and wherein the mating teeth and a plurality of 'completion' are formed in a plurality of planets related to 4 Both of the teeth on the gears will simultaneously mesh with the teeth when the planetary gear train including § 幵 gear is operated in the ineffective mode. : The portable power tool of claim 1, in which the at least one component includes an idler gear, which can selectively couple-related ring gears and-related planetary supports > 2? In order to facilitate the co-rotation of the related ring gear and the related planetary carrier when the planetary transmission stage containing the related ring gear is operated in the ineffective mode. : = The portable power tool of item 7 ', the idler gear includes a plurality of X, which are formed on the related planetary supporting teeth, regardless of whether the planetary gear stage of the ring gear is operated at the Effective use of nuclear or in this ineffective mode. ::: Item 8 of the portable power tool 'of which a plurality of teeth are located on the idler gear— # 八 — ^ ^ x Dao Tian dagger the planetary transmission of the relevant ring gear 998l5.doc 200533852 = Zhu Zai In this ineffective mode, one or a plurality of teeth formed on the δ-related ring gear will be spitted. Please ==; with 'its __ brackets plural, mouth. The mating teeth formed on the related ring-shaped ring gear, regardless of whether the planetary 偻 ·% θ use mode of the related ring gear or the inactive use mode τΤ: transmission stage is in the effective η ::: Γ Engageable power tool, in which the idler gear is moved into the position, at which position the teeth of the idler gear are operated in the ineffective mode at the planetary gear stage of the gear; :: σ hard numbers are formed Tooth on the planet carrier. 12 = Portable power tool of claim 7, wherein the idler gear is moved into a second transmission. This: Γ is the planetary transmission when the relevant ring gear is included, and the operation is in the ineffective mode. Gear and the associated planetary support. H Hai related bad request: the item is a portable power safety gear, where the at least _ component is additionally covered by two: Γ can be selectively combined to-when the planetary gear stage utility mode containing the related ring gear is- Relevant relative two V hunting prohibits a portable power tool between the relevant ring gear and the part 14 · = finding term i, wherein the at least-member additionally includes the = structure, which can be in a first position and the first Translation between two positions, two: The construction can be torsion-related ㈣ gears are prohibited on the housing when being positioned in the first position, the planetary gear stage of the related ring gear can be operated: 99815. doc 200533852. 15. If the 14th item of the request is in the second place: when the ring structure is fixed ^ ^, the ring structure connects the related ring gear to a related line f to add .. 3, branch, so that The related ring gear can be co-rotated with the related lamp holder. 16. Two requests: The portable power tool of item 14, wherein the ring structure can be translated independently of the related ring gear. A portable power tool according to item 14, wherein the annular structure includes a complex, ω 'which, when the annular structure is positioned in the second position, will be formed by a plurality of mating teeth formed on the relevant planetary support. Inter-biting 18. The portable power king gear of claim 17, wherein the mating teeth are formed on one side of the associated planetary support. 19. The portable power safety device of claim 17, wherein the mating teeth are formed on an axial end portion of the associated planetary support. 20: The portable power tool of claim 5, wherein the annular structure engages the relevant planetary support frictionally when it is positioned in the second position. 21. The portable power tool according to item 14 wherein the ring structure includes a locking member that engages the housing to prevent the ring structure from rotating relative to the housing. Α The portable power tool as described in claim 21, wherein the locking member on the annular structure includes at least one special piece selected from the group consisting of a pin and a tooth. 23. —A method for drilling a hole includes: 99815.doc 200533852 24. 25. 26. 27. 28. Provide a power tool having a multi-speed transmission device, the multi-speed transmission device comprising a plurality of epicyclic transmission stages; axially shifting at least one associated with one or more of the epicyclic transmission stages A collar for changing from a first speed ratio to a second speed production ratio; and axially shifting at least one collar for changing from the second speed ratio to the third speed ratio. The method of claim 23, wherein the collar is a ring gear which is associated with one of the epicyclic gear stages. The method of claim 23, wherein the ring gear includes a ring groove and a plurality of teeth; the ring groove is used to axially shift the ring gear, and the plurality of teeth are used relative to the power tool— The housing selectively maintains the bad gear in a non-rotating state. The method of claim 23, wherein each epicyclic transmission stage includes a ring gear, and wherein the annular gear of each epicyclic transmission stage is below at least one of the first, second, and third speed ratios relative to the The power tool housing is non-rotatable. The method of claim 26, wherein each of the epicyclic transmission stages further includes a planetary support and a plurality of planetary gears, and one of the ring-shaped money towels is connected = such as one of the planetary supports, so that the ring gear and the -The Health u-wheel can co-rotate at the _, 2 and 3 speed ratios. : The second method of finding item 27, wherein the one planet support supports a plurality of planets ^ # and the —_ wire form a mutual bite. 99815.doc 200533852 29. The method of claim 23, wherein the collar includes an annular groove and a plurality of teeth, the annular groove is used to axially shift the ring gear, and the plurality of teeth are used to The ring gear is selectively maintained in a non-rotating state relative to a housing of the power tool. 99815.doc