Automatic infinitely variable mechanical transmission

FIELD: machine engineering, namely powered tools such as drills, screw drivers and rotary cutting tools.

SUBSTANCE: multi-speed transmission unit for rotary powdered tool includes several transmission gears. At least two transmission gears have movable reduction member that provides operation of transmission gears in active and in passive modes. Movable reduction members are joined with mechanism for switching reduction members in order to provide at least three reduction degrees or gear ratio values.

EFFECT: powdered tool with relatively large range of reducing revolution number.

91 cl, 38 dwg

 

Priority and reference to related applications

This application has a priority based on provisional application for U.S. patent No. 60/263379, filed January 23, 2001. Some other features of the present invention described and claimed in simultaneously considering the applications of the same applicant in U.S. patent No. 09/964078, entitled "Node coupling the first stage First Stage Clutch), the application of the same applicant in U.S. patent No. 09/965108 entitled "360-degree ring node clutch" (360 Degree Clutch Collar); and the application of the same applicant in U.S. patent No. 09/963905, entitled "Housing with advanced functional molded element Housing with Functional Overmold).

Background of the invention

The technical field to which the invention relates.

The present invention relates generally to mechanized tools such as rotary drills, power screwdrivers, and a rotating cutting tools. More specifically, the present invention relates to multi-speed transmission for rotating mechanized tools.

More recently, manufacturers of mechanized tools began to introduce mechanized rotating tools with electric motors with speed control in an attempt to provide users of such tools to obtain an effective means of frequency control in the stop of the output shaft of the tool, to give them the opportunity to perform various operations without having to resort to additional, specialized tools. Many of the available tools include three-stage two-speed transmission, which provides a greater degree of control the rotational speeds of these instruments.

Typically, the known transmission devices do not have enough configuration that could provide a wide range of frequencies of rotation of the output shaft and torque, which could allow the tool to perform various operations, such as drilling holes using a circular saw large diameter screws for panels of dry plaster or screws with a square cylinder of large diameter, and to perform high-speed drilling. Single-speed or two-speed transmission, which was commonly used in these tools typically do not have sufficient ability to lower speed to allow the use of these transmissions in different modes, because the configuration of these tools to perform high-torque operations leads to a deterioration of their high-speed characteristics. In addition, rechargeable batteries, which were used in many of the first wireless rotating the Xia mechanized tools, were not well adapted for operations with low speed and high torque due to high energy consumption and the rate at which spent energy mechanized tool during such operations. As a result, consumers often forced to purchase two different rotating machinery tool, i.e. a tool for "standard" applications, such as drilling and fastening screws, and the tool high power, low speed, high torque output to perform more complicated operations.

With the advent of modern high capacity battery and high voltage is made possible according to the energy needs of the mechanized tool that is used to perform operations with low speed and high torque. However, in the art there remains a need for transmission for machine tool having a relatively large range of possibilities of lowering speed.

The invention

In one preferred form the present invention provides an actuator for mechanized tools. The actuator includes a housing, a transmission and a gear shift. Transmission has first, second and third ultrasonic is s step-down gears, two of the nodes in lower gears configured to operate in active mode to perform the operation of reducing speed and increasing torque and passive mode. The derailleur has a switching part which is connected to the housing for movement between first, second and third positions and a drive part which is connected to the transmission. A drive part configured to move two of the nodes in lower gears between active and passive modes in response to movement switching portion between the first, second and third positions.

In another preferred form the present invention provides a transmission node for transmitting torque to the output shaft of mechanized tools. The transmission node includes a housing, a first gear part and the second transmission part. The housing includes a wall forming a channel for the transmission. The transmission part has a first input element, the first output element and the first reduction element. The first input element configured to receive the first intermediate output torque and the first output element configured to issue the second intermediate output torque. The first step-down element of the work of the t in the first state, when the first gear portion increases the first intermediate output torque at the first preset value. The first reduction element also operates in the second state when the first transmission part increases the first intermediate output torque to the second preset value. The second transmission portion includes a second input element, the second output element and the second reduction element. The second input element configured to receive the second intermediate output torque and the second output element configured to issue an output torque to the output shaft. The second reduction element operates in the first state, when the second transmission part increases the second intermediate output torque to the third preset value. The second reduction element also operates in the second state, when the second transmission part increases the second intermediate output torque to the fourth preset value.

In another preferred form the present invention provides a machine tool having a motor and transmission. The motor has an output shaft and an output torque. The transmission node has a housing having a wall forming a channel for transmiss and, and the transmission has first, second and third nodes of the planetary transmission. The first node of the planetary gear has a first ring gear, the first sun wheel and the first node of the planetary gears. The first node of the planetary gears has a first planetary carrier and the set of first planetary gears. The first planetary carrier rotatably connected with the first sun wheel. The first planetary carrier has a lot of pins for holding rotatably many of the first planetary gear wheels. The first sun wheel configured to receive the input torque. The first planetary carrier includes a second sun wheel and configured to transmit the first intermediate output torque to the second node of the planetary gear. Many of the first planetary gear wheels are in mesh with the second sun wheel and the first annular gear wheel. The first ring gear may be installed in the axial direction in the first position, in which the first ring gear is fixed relative to the body.

The second node of the planetary transmission includes the second ring gear and the second node of the planetary gears. The second node of the planetary gears is the second square is netarea drove and many of the second planetary gear wheels. The second planetary carrier has an output sun wheel and plenty of pins for holding rotatably the second set of planetary gears. The second sun wheel is engaged with a lot of second planetary gears, and transmits them to the first intermediate output torque. The output sun wheel configured to issue the second intermediate output torque. Many of the second planetary gears also engages with the second ring gear. The second ring gear may be installed in the axial direction in the first position, in which the second ring gear is fixed relative to the housing to prevent relative rotation between them. The second annular gear wheel can also be set in the axial direction into a second position in which the second ring gear can rotate in the channel for transmission.

The third node planetary gear set includes a third ring gear and the third node of the planetary gears. The third node of the planetary gears is third planetary carrier and a lot of third planetary gears. The third planetary carrier is the output element and the many pins that with the possibility of rotating the Oia hold a lot of third planetary gears. Many third planetary gears is engaged with the third ring gear and the output sun wheel and configured to receive the second intermediate output torque. An output element configured to issue an output torque. The third ring gear may be installed in the axial direction in the first position, in which the third ring gear is fixed relative to the housing to prevent relative rotation between them. The third ring gear can also be set in the axial direction into a second position in which the third ring gear can rotate within the channel for transmission.

Brief description of drawings

Additional advantages and features of the present invention will be understood when reading the following description and the appended claims, in which links are given on the accompanying drawings on which:

figure 1 depicts a side view of the machine tool according to the present invention;

figure 2 is a view in isometric with the spatially separated parts of the mechanized part of the tool of figure 1;

figure 3 is a view in isometric of the hull machine tool of figure 1, showing the back side of the node face the howling of the cover;

4 is a front view of the node of the end cap;

5 is a sectional view along the line 5-5 in figure 4;

6 is a rear view of part of the machine tool of figure 1 with the remote host end caps;

Fig.7 is a side view of part of the machine tool of figure 1 with the remote host end caps;

Fig is a view similar to that shown in figure 4, but illustrating the housing of the end cap to perform additional operations of molding;

Fig.9 is a view similar to that shown in figure 5, but illustrating the housing of the end cap to perform additional operations of molding;

figure 10 is a view similar to that shown in figure 4, but illustrating an alternative design is additionally molded element;

11 is a view in partial cross-section of part of a mechanized tool that utilizes the node of the end cap with optional molded element with the structure shown in figure 10;

Fig - view in isometric with the spatially separated parts parts mechanized tools, shown in figure 1, illustrating the transmission node in more detail;

Fig - view in isometric with the spatially separated parts parts mechanized tools, shown in figure 1, illustrating the unit step-down gears, a sleeve gears, part of the housing and a portion of the coupling mechanism is placed in more detail;

figa is a sectional view made along the longitudinal axis of the second ring gear;

fig.13b is a sectional view made along the longitudinal axis of the third ring gear;

Fig - side view of the sleeve of the transmission;

Fig rear view of the sleeve of the transmission;

Fig is a sectional view on the line 16-16 on Fig;

Fig is a sectional view along the line 17-17 on Fig;

Fig - view from the spatially separated parts of the unit step-down gears;

Fig is a sectional view along the longitudinal axis of the machine tool of figure 1 illustrating a portion of the block lower gears more detail;

Fig is a front view of part of the first reduction carrier;

Fig is a sectional view along the longitudinal axis of the machine tool shown in figure 1, illustrating a portion of the block lower gears more detail;

Fig rear view of part of the third reduction carrier;

Fig is a sectional view along the longitudinal axis of the machine tool of figure 1 illustrating the transmission node set for the first gear ratio;

Fig is a sectional view similar to that shown in Fig, but illustrating the transmission node set for the second gear ratio;

Fig is a sectional view similar to that shown in Fig, but illustrating the Tr is nsmission node, mounted in position to the third gear ratio;

Fig is a top view of part of the machine tool of figure 1 illustrating the derailleur in more detail;

figa - side view of the rotary Cam switch;

fig.27b is a top view of the rotary Cam switch;

figs is a sectional view made along the Central axis of the derailleur;

Fig - rear view node of the output spindle;

Fig - view in isometric with the spatially separated parts of the mechanism of coupling;

figa - view in isometric part of the clutch mechanism, illustrating another configuration of the coupling element;

fig.29b - view in isometric with the spatially separated parts, illustrating the multi-element structure of the first ring gear and the coupling element;

Fig - schematic illustration of the adjustment patterns in the "expanded" state;

Fig is a schematic illustration similar to that shown in Fig, but showing an alternative construction adjusting profile; and

Fig is a schematic illustration similar to that shown in Fig, but pokazivaushee part of another alternative construction of the regulating profile.

Detailed description the preferred option of carrying out the invention

The overall performance of the Sabbath.

Figures 1 and 2 mechanized tool, having a structure according to the present invention, indicated generally by the reference number 10. As will be clear to experts in the art, the preferred embodiment of the present invention can be any device with an electric wire or wireless (battery powered) device such as a portable mechanized screwdriver or drill. In the specific embodiment of the invention of the mechanized tool 10 is a cordless drill, having a housing 12, motor node 14, a multi-speed transmission node 16, the clutch mechanism 18, the node 20 of the output shaft, jaw Chuck 22, the actuator unit 24 and a battery pack 26 power. Specialists in the art will understand that several components of the machine tool 10, such as jaw Chuck 22, the trigger 24 and a battery pack 26 power, are in fact well-known components and do not require description in significant detail in this application. For a more complete understanding of the known components mechanized tools 10, you can refer to a variety of publications. One example of such publications is U.S. patent No. 5897454 the same applicant, issued on 27 April which I 1999, description of which is included here as reference material, as if it were set forth fully herein.

The housing 12 includes the node 30 of the end cap and the node 32 of the housing arm, which includes a pair of mating halves of the housing 34 of the handle. Node 32 of the housing of the handle includes an engaged part 36 and part 38 for placement drive or Cabinet part. The actuator unit 24 and a battery pack 26 power mechanically connected with the capture part 36 and electrically connected to the node 14 of the electric motor. Body part 38 includes a recess 40 to accommodate the motor and the notch 42 to accommodate the transmission. The node 14 of the electric motor is located in the recess 40 to accommodate the motor and includes a rotary output shaft 44, which is held in the recess 42 to accommodate the transmission. Leading gear 46 of the electric motor, having a set of teeth 48, is connected with the output shaft 44 for joint rotation with it. The trigger 24 and a battery pack 26 power interact to selectively supply electric power to the node 14 of the motor in a known manner to control the speed and direction, which rotates the output shaft 44.

The transmission node 16 is located in the recess 42 to accommodate the transmission and includes a mechanism 60 switch near the power. Leading gear motor 46 connects the transmission node 16 with the output shaft 44, transmitting the transmission node 16 a relatively high speed and low torque. The transmission node 16 includes many step-down elements which selectively engages the mechanism 60 gear to get the gear ratios. Each of the gear ratios converts speed and torque supplied drive force given way, allowing you to change the speed and torque output transmission unit 16 as needed from the relatively low output speed and high output torque to a relatively high output speed and low output torque. Output force transmission is transmitted to the output node 20 of the spindle, which is connected to jaw Chuck 22 for joint rotation and transfer torque insertable cutting tool (not shown). The clutch mechanism 18 is connected to the transmission node 16 and is designed to limit the torque associated with a driving force elected to the specified torque limit.

Additionally molded functional elements

Figure 2-9 shows the node 30 of the end cap, on the emitting body 100 of the end cap and additionally molded element 102. In the shown example, the housing 100 of the end cap is made by injection molding of a plastic material such as ABS. The housing 100 of the end cap forms a recess 104 of the end cap, which has a size adapted to receive part of the node 14 of the electric motor, which steps back from node 32 of the housing arm. On the front surface 114 of the housing 100 of the end cap formed many first and second radial notches 108 and 110 for ledges and hard surface 128, and around the perimeter of the housing 100 end caps made many tides 116 for screws. Each of the first and second radial notches 108 and 110 for the protrusions has a size adapted for receiving one of the first radial protrusions 120 and second radial protrusions 122, respectively, which are formed on the back surface 124 of the halves 34 of the housing arm. First and second radial openings 108 and 110 for protrusions interact with the first and second radial protrusions 122 to properly align the housing 100 of the end cap relative to the node 32 of the housing of the handle, and to prevent relative rotation between them. Arcuate portion 128 of the front surface 114 of the housing 100 of the end cap angled to mate with resistant surface 132 on the rear surface 124 of the halves 34 of the handle. Tides 116 for screws allow the still to attach the case 100 of the end cap to the housing 136 of the motor by means of a set screw 138. The geometry of the casing 136 of the motor is such that it is tightly attached to the inside halves of the housing 34 of the handle. As such, the attachment of the housing 100 of the end cap to the housing 136 of the motor provides a rigid holding the housing 100 of the end cap relative to the back surface 124 of the node 32 of the housing of the handle and closing the rear of the recesses 139 in the node 32 of the housing of the handle.

In the side surfaces of the body 100 of the end cap formed many lateral slots 140 to ensure the passage of air flow through the node 32 of the housing arm and cooling node 14 of the electric motor are well known manner. In the rear surface of the housing 100 of the end cap formed many rear of the slots 144, each of the rear slots 144 includes a deep portion 146, which partially takes place in the direction of the outer surface 148 of the housing 100 of the end cap, and through the part 150, which passes completely through the housing 100 of the end cap. A pair of retaining lobes 152 formed so that they pass from the inner surface 154 of the housing 100 of the end cap inside, in the recess 104 of the end cap. In the inner surface 154 of the housing 100 of the end cap shaped channel 156, crossing each of the rear slots 144 and holding the petals 152.

Of elastic material, such as thermoplastics the second elastomer (for example, HYTREL®manufactured by E.I. du Pont de Nemours and Company), formed additionally molded element 102, which simultaneously form and connect with the body 100 of the end cap during the operation of molding. In the specific example additionally molded element 102 includes multiple buffer elements 170, a pair of insulators 172 and the connecting member 174. Each of the buffer elements 170 passes from a point approximately coincident with the inner surface 154 of the housing 100 of the end cap, to the point, receding back from the outer surface 148 of the housing 100 end cover approximately a distance of from about 0.5 mm to about 1.5 mm and preferably about 0.75 mm This design allows the buffer elements 170 to provide a degree of shock absorption, which reduces the chance of damage to the body 100 of the end cap in case of falling of the tool 10. In addition, sometimes the operator is required to exert a relatively large force to the tool 10, for example when using circular saws for drilling holes of large diameter. In such situations, the operator tends to press on the back side of the tool 10 for application of force along the line of the axis of the Chuck 22. In such situations, the buffer elements 170 form for the operator relatively soft and comfortable surface, to the which provides slip resistance, and also reduces vibration transmitted to the operator.

Around holding petals 152 are formed insulators 172 located on the inner surface 154 of the housing 100 of the end cap. In the above example, each of the insulators 172 includes an annular element 180 that extends forward from the inner surface 154 of the housing 100 of the end cap. This design allows you to enter insulators 172 of the housing 100 of the end cap in contact with the outer perimeter 14a and the rear surface 14b of the casing 14C motor for fixed retention of the motor 14d inside the casing 136 of the motor. This prevents the moving components of the node 14 of the motor along the longitudinal axis of the tool 10, and also contributes to the damping of the vibrations generated during the operation of the node 14 of the electric motor. The connecting member 174 still connected with each of the buffer elements 170 and insulators 172. The connecting member 174 forms a channel through which the elastic material is held in the course of forming the buffer elements 170 and insulators 172, thus, making them difficult to extract from the case 100 of the end cap.

The person skilled in the art it will be clear that this aspect of the present invention can be incorporated into various other points of the node 32 of the handle to create a seal between two or more components, damping shaking the Nations or positioning of one component relative to another. One such example is shown in figure 10 and 11, where the isolators 172 modified so that they pass through the perimeter portion of the recess 104 of the cover and are in sealing contact with the rear surface 14b of the motor 14d. Insulators 172 seal off the border between the body 100 of the end cap and the node 14 of the electric motor, whereas the buffer elements 170 clog the rear of the slot 144 in the housing 100 of the end cap. The space 188, limited insulators 172, fill grease grease or other lubricant that lubricates the bearing 190 of the rotor of the electric motor.

The transmission node

On Fig shows the transmission node 16, which is a three-stage, three-speed transmission, comprising a sleeve 200 transmission unit 202 of step-down gears and mechanism 60 of the gearshift. As additionally shown in Fig-17, sleeve 200 powertrain includes wall 210, which limits the channel for the transmission or cavity 212 in which is located a block 202 lower gears. The sleeve 200 of the transmission includes a housing 214 and the base 216. The housing 214 of the sleeve 200 transmission has a fairly uniform diameter, which is smaller than the diameter of the base 216. The inner diameter of the base 216 is adapted to receive a cylindrical front portion 220 of the housing 136 of the motor.

On the basis of 216 to form the ANO many speakers pads 226. The exposed pad 226 restrict the set of first grooves 228 in the outer surface 230 of the base 216 and the multiple second grooves 232 in the inner surface 234 of the base 216. The first grooves 228 are configured so that they took the centering ribs 238 formed on the inner surfaces 242 halves 34 of the handle to align the cartridge 200 of the transmission relative to the halves 34 of the handle and prevent relative rotation between the sleeve 200 of the transmission and the housing 12. Preferably, the first groove 228 and the centering ribs 238 configured so that the sleeve 200 of the transmission can be installed in half 34 of the handle with only one orientation (i.e., the configuration of the first grooves 228 and centering ribs 238 prevents rotation of the sleeve 200 transmission 180° required provisions concerning halves 34 arm). The second groove 232 will be described in more detail below.

The housing 214 of the sleeve 200 powertrain includes a cylindrical portion 246 of the housing and part 248 to place the pin. In the specific embodiment of the invention, the cylindrical portion 246 of the housing includes guide 250 copier switch, multiple grooves 252 for lubrication and the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel, respectively. Guide 250 copier switch is the switch has an essentially rectangular cross-section and extends outward from the upper part of the outer surface 258 hull 246. Groove 252 for lubrication formed concentrically around the first half of the perimeter of the hull 246. Groove 252 for lubrication have a depth, comprising from about 0.01 inch to about 0,030 inch for holding lubricant, such as grease lubricant on the upper half of the perimeter of the hull 246. Work guide 250 copier switch and grooves 252 for lubrication will be described in more detail below.

The protruding flange 264 divides the inner space of the case portion 246 of the first and second parts 260 and 262, respectively. The first set of teeth 254 for engagement with the annular gear wheel formed on the inner surface 266 hull 246 and extends backward from the speaker flange 264 towards the base 216. The second set of teeth 256 for engagement with the annular gear wheel formed on the inner surface of the hull 246, but extends forward from the speaker flange 264. Teeth 268 of the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel are evenly distributed on the inner surface 266 hull 246. The configuration of each prong 268 in the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel such that each tooth moves away from the speaker flange 264 has a pair of parallel pin is ctyh surfaces 270 and ends the terminal part 272. Terminal part 272 of each prong 268 rounded and narrowed to facilitate entry into engagement with a part of the block 202 step-down gear, which will be described in detail below.

Part 248 to place a rod element extending downward from the hull 246 for a substantial part of the length of the hull 246. In part 248 to place a core element formed hole 274 to drive, passing back through the base 216 of the sleeve 200 of the transmission. In the specific embodiment of the invention the hole 274 of the actuator has a ledge separating the first portion 276 of the first diameter in the rear part of the liner 200 of the transmission and the second part 278 smaller second diameter at the front of the liner 200 transmission. In the shown example, the first part of the 276 hole 274 of the actuator passes through the wall of the first portion 260 of the housing and forms a groove 280 in the inner surface 234 of the base 216. Part 248 to place the truss element will be described in more detail below.

In the sleeve 200 of the transmission formed by the first pair of grooves 284 to the bracket, and a second pair of grooves 286 for staples along the sides of the liner 200 of the transmission so that they are parallel to the longitudinal axis of the sleeve 200 of the transmission. The first pair of grooves 284 for staples are formed so that they pass through the sides of the building the red part 246 to the rear of the speaker flange 264 and extend back towards the base 216. The depth of the first pair of grooves 284 for staples is that they do not pass through the portion 210 of the wall forming the base 216. The second pair of grooves 286 bracket is also formed so that they pass through the sides of the hull 246, continuing forward from the speaker flange 264, and pass through the front surface 288 of the liner 200 of the transmission.

As shown in Fig, 13, 18 and 23, block 202 lower gears includes a first step-down node 302 gears, the second step-down node 304 gears and the third step-down node 306 gears. First, second and third reduction nodes 302, 304 and 306 gears operate in an active mode and passive mode. When operating in the active mode step-down node gears performs the operation of reducing speed and increasing torque, while with decreasing node gears in passive mode step-down node gears gives the output speed and torque, which is approximately equal to the rotational speed and torque, rotational motion, the reported downward node gears. In the specific embodiment of the invention each of the first, second and third lower nodes 302, 304 and 306 gears is a planetary gear. However, the special is there in the art will understand, instead of one or more lower nodes gears forming unit 202 lower gears, can be applied to various other types of lower nodes gears known in this field.

As shown, the first step-down node 302 gears includes a first reduction element or ring gear 310, the first set 312 of the planetary gears and the first downward drove 314. The first ring gear 310 is an annular structure having a set of teeth 310a formed at the level of its internal diameter. On the outer perimeter of the front surface 318 of the first ring gear 310 formed surface 316 of the clutch, which will be described in more detail below. The first ring gear 310 is located inside the hollow part of the recess 212 formed in the base 216; the front surface 318 of the first ring gear 310 is in contact with the ledge 320 formed in the sleeve 200 of the transmission, thereby limiting the ability of the first ring gear 310 to move forward in a hollow recess 212.

The first downward drove 314 formed in the configuration of the flat cylinder having many pins 322, retreating from its back surface 324. Almost at the outer perimeter of the first reduction carrier 314 to form the ANO many teeth 314a with depression 314b, formed between each two adjacent teeth 314a. By staggering the teeth 314a one of the depressions (i.e. depression 314b') more than other depressions 314b by eliminating teeth 314a on the outer perimeter of the first reduction carrier 314. In the specific embodiment of the invention the teeth 314a of the first reduction carrier 314 configured so that they were not in direct engagement with the teeth 310a of the first ring gear 310.

On Fig and 20 depicts the profile of the teeth 314a. As shown, each prong ends 314a with radius 326 on the front surface 328 of the first reduction carrier 314, but dropped sharply on the back surface 324 of the first reduction carrier 314. Radius 330 is also formed in the hollows 314b between teeth 314a.

Returning to Fig, 13, 15, 18 and 23, we note that behind the first down-node 302 gears is the first thrust washer 332 having a first annular portion 334, the second annular portion 336 and a lot of restraint petals 338. Holding the petals 338 engages with the second groove 232 in the base 216 of the sleeve 200 of the transmission and, as such, prevents relative rotation between the first thrust washer 332 and sleeve 200 transmission. The inner diameter of the base 216 is adapted for the mA casing 136 of the motor and, the front surface 340 of the housing 136 of the motor prevents axial movement of the first thrust washer 332. The first annular portion 334 is in contact with the rear surface 342 of the first ring gear 310, forming surface wear and tool control values on which the first ring gear 310 is capable of moving in the axial direction. The second annular portion 336 is located at a distance axially from the first annular portion 334, extending forward from the first annular portion 334 for the formation of surface wear to the first set 312 of the planetary gears, which also forms a means of controlling the magnitude to which they can move in the axial direction.

The first set 312 of the planetary gears includes many planetary gears 344, each of which has an essentially cylindrical configuration and has a lot of teeth a formed on its outer perimeter, and a hole 346 for pin formed in its center. Each planetary gear 344 rotatably retained on a respective one of the pins 322 and the first Panigale driver 314 and is located so that its teeth a are in direct engagement with the teeth 310a of the first ring gear 310. On the front and back surfaces is t 350 and 352 of each of the planetary gears 344 formed protruding surface 348, which prevents the friction of the teeth a on the first downward drove 314 and the first thrust washer 332 and the formation of dust or sawdust, which could impair the characteristics of the transmission node 16 and reduce its service life. Because the teeth 46a pinion 46 of the motor shaft 44 also engages with the teeth a planetary gears 344, leading gear 46 serves as a sun wheel for the first down-node 302 gears.

The second step-down node 304 gears located inside the hollow part of the recess 212 formed in the first Cabinet part 260, and includes a second sun wheel 358, the second reduction element or ring gear 360 and the second node of the planetary gears 362 and the second downward drove 364. The second sun wheel 358 is fixed for rotation with the first step-down planet carrier 314. The second sun wheel 358 includes many teeth a, which extend forward from the front surface 328 of the first reduction carrier 314.

The second ring gear 360 is an annular structure having a set of teeth 360 formed on its inner diameter. Teeth 360 can be strongly oblique rear surface 366 of the second ring gear 360, but dropped vertically on the front surface 368. More preferably, the was b formed large radius 369 curves on the back surface 366 and the sides of each prong 360 however, a greater radius 369 rounding is preferable to a strong slant, because a large radius 369 rounded teeth 360 provides better engagement between the second ring gear 360 and the first step-down planet carrier 314.

On the outer periphery of the second ring gear 360 formed many teeth 370 for engagement with the sleeve; the teeth 370 for engagement with the sleeve and pass forward to the front surface 368 of the second ring gear 360 and the pointed end part 372, which is rounded and tapering forward and inward. On the outer perimeter of the second ring gear 360 is also formed annular groove 374 for staples. In the example shown, the groove 374 for staples is a groove of rectangular cross section having a pair of side walls 376. Groove 374 for the bracket will be described in more detail below.

The second downward drove 364 formed in the configuration of the flat cylinder having many pins 378, which extend from the back surface 380. The second node of the planetary gears 362 includes many planetary gears 382. Each planetary gear 382 has an essentially cylindrical configuration with many teeth a formed on its outer perimeter, and with a hole 384 for pin formed in its price is re. Each planetary wheel 382 is rotatably retained on a respective one of the pins 378, and the second downward drove 364 are set so that the teeth a planetary gears 382 engages with the teeth 360 of the second ring gear 360. Teeth a second sun gear 358 also engages with the teeth a planetary gears 382.

Third step-down node 306 gears located inside the hollow part of the recess 212 formed within the second Cabinet part 262, and includes a third sun wheel 398, the third step-down element or ring gear 400 and the third set of planetary gears 402 and the third down led 404. The third sun wheel 398 is attached to the second downward cage 364 to rotate together with it. The third sun wheel 398 includes many teeth a extending forward from the front surface 406 of the second reduction carrier 364.

The third ring gear 400 is an annular structure having a set of teeth 400A formed on its inner diameter. Teeth 400A can be strongly oblique to the front surface 412 of the third ring gear 400, but dropped vertically on the back surface 414. It is more preferable to form a large radius 407 bend on the front surface 412 of the sides of each of the teeth 400A, to apply a large radius 407 bend and not strong bevel, because a large radius 407 bending the prong 400A provides better engagement between the third ring gear 400 and the third step-down planet carrier 404. On the outer perimeter of the third ring gear 400 formed many teeth 418 for engagement with the sleeve; teeth 418 for engagement with the sleeve and pass back toward the back surface 414 of the third ring gear 400 and the terminal end part 420, which is rounded and tapers in the direction of the back and inside. On the outer perimeter of the third ring gear 400 is formed annular groove 422 for staples. In the example shown, the groove 422 for staples is a groove of rectangular cross section having a pair of side walls 424. Groove 422 for the bracket will be described in more detail below.

Third down led 404 is formed in the configuration of the flat cylinder having many pins 428, retreating from its rear surface 430. Almost the entire outer perimeter of the third reduction carrier 404 formed many teeth a, and between each two adjacent teeth a formed trench 404b. Through existing between the teeth a space one of the depressions 404b (i.e. trench 404b') more than other depressions 404b by eliminating zu the CA a on the outer perimeter of the third reduction carrier 404. In the specific embodiment of the invention the teeth a of the third reduction carrier 404 is configured in such a way that they are not in direct engagement with the teeth a second planetary gears 382.

On Fig and 22 shown in more detail the profile of the tooth a. As shown, the rear surface 430 of the third reduction carrier 404 beveled, and on each side of the teeth a and troughs 404b formed rounding 434 large radius. Each prong a dropped vertically on the front surface 436 of the third reduction carrier 404.

Returning to Fig, 13, 15, 18 and 23, we note that the third set 402 planetary gears includes many planetary gears 438. Each planetary gear 438 has an essentially cylindrical configuration with many teeth a formed on its outer perimeter, and a hole 440 to pin formed in its center. Each planetary gear 438 rotatably mounted on a respective one of the pins 428, and the third down led 404 is set so that the teeth a planetary gears 438 directly engages with the teeth 400 of the third ring gear 400. On each of the front and rear surfaces of the planetary gears 438 formed protruding h is the terrain 442, which prevents the friction of the teeth a on third down led 404 and the formation of dust or sawdust, which could impair the characteristics of the transmission node 12 and reduce its service life. Around the third sun gear 398 is a second thrust washer 450, and teeth a third sun gear 398 engages with the teeth a planetary gears 438. A second thrust washer 450 includes many holding petals 452, which are configured so that they come into engagement with the corresponding grooves 454 for the petals (Fig)formed in the inner surface 266 of Cabinet portion 246 of the sleeve 200 of the transmission. Holding the petals 452 and grooves 454 for petals cooperating to prevent relative rotation between the second thrust washer sleeve 450 and 200 transmission.

The node 20 of the output shaft includes gear means 458 to connect the spindle 460 with the third step-down planet carrier 404 for joint rotation so as to transfer drive torque from block 202 lower gears push the cartridge 22. Such transmission facilities 458 is well known and can easily be adapted to the unit step-down gears corresponding to the present invention. Accordingly, there is no need to include sublattice the service description gear means 458.

As shown in Fig, 13A, 13b, 16, 17, 18, and 23 to 28, the mechanism 60 of the gear shift can be moved between the first position 500, the second position 502 and the third position 504 and includes a switching portion 510, receiving the force for switching speed and drive part 512 for manipulating unit 202 lower gears in accordance with the switching speed. Driving portion 512 in the working position connected with block 202 step-down gears and moves the second and third reduction nodes 304 and 306 gears between active and passive modes in the movement of the switching part 510 between the first, second and third positions 500, 502 and 504. In the specific embodiment of the invention, the driving portion 512 includes a rotating switching copier 520, many wire clips 522 and the spring element 523. Each of the wire clip 522 formed from a wire of circular cross section which is bent in the form of a semicircle 524 with a pair of pads 526, retreating away from the semicircle 524 and located approximately in the median plane of the semicircle 524. The semicircle 524 has a size, which is designed to fit in the groove 374 and 422 for brackets in the second and third ring gears 360 and 400, respectively. The semicircle 524 is not acting radially outward from the corresponding one to licevyh gears (360, 400) and not tamamlama side walls (376, 424) of the grooves (374, 422). In the example, the side walls (376, 424) of the grooves (374, 422) for brackets spaced from each other at a distance of approximately 0.05 inches, and the diameter of the wire from which the formed wire clips 522 is approximately 0.04 in.

The tabs 526 of the wire clips 522 extend outward from the hollow recess 212 in the corresponding slots (284, 286) bracket, formed in the sleeve 200 of the transmission. The tabs 526 have sufficient length to pass outward from the outer surface 258 of the housing 214 of the sleeve 200 of the transmission, but not so much that they acted radially outward from a portion of the first grooves 284 to the bracket at the base 216 of the sleeve 200 of the transmission. Configuring the wire clips 522, thus, facilitates the Assembly unit 16 step-down gears, allowing you to install wire clips 522 on the second and third ring gears 360 and 400, then these nodes are inserted into the hollow recess 212 along the longitudinal axis of the sleeve 200 of the transmission.

On Fig and 27A-27C shows the rotating Cam 520 switch, containing the arched frame 530 switch, key switch 532 and many spacers 534. In case switch 530 is formed a pair of first curved grooves a and 540b, a pair of second curved grooves a and 544b, cut 546 for spring and napravlyayuschiysya 548. Case 530 switch has a size adapted to cover the outer diameter of Cabinet portion 246 of the sleeve 200 of the transmission with a sliding fit. The guide notch 548 has an essentially rectangular shape and has a size adapted to enter into contact with the front and rear surfaces of the guide 250 copier switch. The width of the guide notch 548 substantially greater than the width of the guide 250 copier switch and has a size that allows you to rotate the rotating Cam 520 switch core 200 transmission between the first rotational position, the second rotational position and the third rotational position. Guide 250 copier switch interacts with the guide notch 548 to limit the range in which the rotating Cam 520 switch can be rotated on the sleeve 200 of the transmission, with the first lateral side of the guide 250 copier switch comes in contact with the first side of the guide notch 548, when the rotating Cam 520 is in the first rotational position and a second lateral side of the guide 250 copier switch comes in contact with the second side of the guide notch 548, when the rotating Cam 520 switch is in the third rotational position.

Each of the first curved tongue is a and 540b has dimensions, adapted to receive one of the tabs 526 of the wire clips 522 that is engaged with the second ring gear 360. In the specific embodiment of the invention, the first curved groove a includes the first segment 550, the second segment 552 and the intermediate segment 554. The first segment 550 is located at the first predetermined distance from the plane 558 reference, which is perpendicular to the longitudinal axis of the rotating Cam 520 switch, and the second segment 552 is located at the second distance from the plane 558 reference. The intermediate segment 554 connects the first and second segments 550 and 552 each other. The configuration of the first curved groove 540b is identical to the configuration of the first curved groove a, except that it is rotated relative to the rotating Cam 520 switch so that each of the first, second and intermediate segments 550, 552 and 554 of the first curved groove 540b is oriented with a 180° relative to the first, second and intermediate segments 550, 552 and 554 of the first curved groove a.

Each of the second curved grooves a and 544b has dimensions adapted for receiving one of the tabs 526 of the corresponding one of the wire clips 522. In the specific embodiment of the invention the second curved groove a includes the first segment 560, the second segment 562, the third segment 564 and a pair of intermediate segments 566 and 568. The first and third segments 560 and 564 are located on the third specified distance from the reference plane, and the second segment 562 is located at a fourth distance from the plane 558 reference. The intermediate segment a connects the first and second segments 560 and 562 each other, and the intermediate segment 568 connects the second and third segments 562 and 564 with each other. The configuration of the second curved groove 544b is identical to the configuration of the second curved groove a, except that it is rotated relative to the rotating Cam 520 switch so that each of the first, second, third and intermediate segments 560, 562, 564 and 566 and 568 of the second curved groove 544b rotated 180° relative to the first, second, third and intermediate segments 560, 562, 564 and 566 and 568 of the second curved groove a.

When the tabs 526 of the wire clips 522 engages with the first curvilinear grooves a and 540b and second curved slots a and 544b, the rotating Cam 520 switch can be rotated on the sleeve 200 transmission between the first, second and third positions 500, 502 and 504 for selective introduction into engagement and separation of the second and third ring gears 360 and 400 and the first and third lower led 314 and 404, respectively. the ri the rotation of the rotating Cam 520 switch the first curved grooves a and 540b and second curved slots a and 544b hold the wire tabs 526 of the corresponding wire clips 522 and moves the wire legs 526 along the longitudinal axis of the sleeve 200 transmission in the respective first and second grooves 284 and 286 for the brackets. Accordingly, the rotating Cam 520 switch operates to convert the rotational motion into axial linear motion, which causes the axial displacement of the wire legs 522 specified way. In the groove 252 for lubrication formed in hull 246 of sleeve 200 of the transmission, put a lubricant (not shown)used to lubricate the boundaries between the sleeve 200 of the transmission and the rotating Cam 520 switch.

Installation of the rotating Cam 520 switch is in the first rotational position 500 leads to the location of the tabs 526 of the wire clips 522 that is engaged with the second ring gear 360 in the first segment 550 of the first curved grooves a and 540b and the location of the tabs 526 of the wire clips 522 that is engaged with the third ring gear 400 in the first segment 560 of the second curved grooves a and 544b. Accordingly, installation of the rotating Cam 520 switch is in the first rotational position causes the occurrence of engagement of the second and third ring gears 360 and 400 with the second and third sets 362 and 402 of the planetary gears respectively. Simultaneously with entering into the engagement of the second and third ring is updateh wheels 360 and 400 with the second and third sets 362 and 402 of the planetary gears, teeth 370 and 418 for engagement with the sleeve of the second and third ring gears 360 and 400, respectively, are in engagement with the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel, respectively, to prevent relative rotation between the second and third ring gears 360 and 400 and sleeve 200 of the transmission to obtain, therefore, the provisions of 570 unit 16 step-down gear with the first overall decline or ratio shown in Fig. Specialists in the art will understand that the target portion 272 of teeth 268 of the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel and the target part 372 and 420 teeth 370 and 418 for engagement with the sleeve, respectively, rounded and narrowed to improve their ability to engage in the event of axial movement along the longitudinal axis of the block 16 step-down gears.

Installation of the rotating Cam 520 switch is in the second rotational position 502 leads to the location of the tabs 526 of the wire clips 522 that is engaged with the second ring gear 360 in the first segment 550 of the first curved grooves a and 540b, and the location of the tabs 526 of the wire clips 522 that is engaged with the third ring gear 400, the WTO is the first segment 562 of the second curved grooves a and 544b. Accordingly, installation of the rotating Cam 520 switch is in the second rotational position causes the occurrence engages the second ring gear 360 to the second set 362 planetary gears and to join in the engagement of the third ring gear 400 with the third set 402 of the planetary gears and the third step-down planet carrier 404. Installation of the rotating Cam 520 switch is in the second rotational position 502 also leads to the occurrence in the engagement of the teeth 370 for engagement with the sleeve and second ring gear 360 to the first set of teeth 254 for engagement with the annular gear wheel, while the teeth 418 for engagement with the sleeve and the third ring gear 400 is not included in engagement with the second set of teeth 256 for engagement with the annular gear wheel. Essentially, the relative rotation between the second ring gear 360 and the sleeve 200 of the transmission is prevented while relative rotation between the third ring gear 400 and sleeve 200 transmission Pets to obtain position 572 block 16 step-down gear with the second overall decline or ratio shown in Fig.

Installation of the rotating Cam 520 switch in the third rotational position 504 leads to loc is the position of the tabs 526 of the wire clips 522, which engages with the second ring gear 360, in the second segment 552 of the first curved grooves a and 540b, and the location of the tabs 526 of the wire clips 522 that is engaged with the third ring gear 400 in the third segment 564 second curved grooves a and 544b. Accordingly, installation of the rotating Cam 520 switch in the third rotational position causes the occurrence engages the second ring gear 360 to the second set 362 planetary gears and with the first step-down planet carrier 314, while the third ring gear 400 is engaged only with the third set 402 of the planetary gears. Installation of the rotating Cam 520 switch in the third rotational position 504 also causes disengagement of the teeth 370 for engagement with the sleeve and second ring gear 360 to the first set of teeth 254 for engagement with the annular gear wheel and enter the engagement of the teeth 418 for engagement with the sleeve and the third ring gear 400 with the second set of teeth 256 for engagement with the annular gear wheel to allow relative rotation between the second ring gear 360 and the sleeve 200 of the transmission and prevent mutual rotation between the third ring gear 400 the sleeve 200 of the transmission to obtain a position 574 of block 16 step-down gear gear with the third overall decline or gear ratio.

In the example shown in Fig, 27b and 28, from a flat rectangular plate of spring steel formed spring element 523, including flattened Z-shaped portion 580 and a convex portion 584. Flattened Z-shaped part 580 is configured so that it circled the two straps 586, which are cut 546 for the spring, thus to hold the convex part 584 in a predetermined position, and to transmit the spring force between the rotating Cam 520 switch and spring element 523. As shown in Fig, the convex portion 584 of the spring element 523 has a size adapted to enter the notches 590 formed in the housing 592 node 20 of the output shaft. Between the notches 590 is formed protruding pad 594 removed circumferentially from the rotating Cam 520 switch. When the node 20 of the output shaft is located on the lower block 16 gears, and mechanism 60 gear set to one of the rotational positions, i.e. the first, second or third position 500, 502 or 504, a convex portion 584 of the spring element 523 is included in a corresponding one of the cut-590. The force generated by the spring element 523, when the convex portion 584 is moved down in the direction of the rotating Cam 520 switch in response to the occurrence of the contact convex portion 584 and super serving is 594, prevents unintentional rotation mechanism 60 of the gearshift. In addition, the location of the convex part 584 in the neck 590 provides for a user perceivable indication of positioning of the rotating Cam 520 switch.

In a specific embodiment of the invention shown in Fig and 27C, the switching portion 510 includes arcuate strip 600, having formed therein the protruding hollow button switch 602 rectangular cross-section. Arcuate strip 600 is formed of a plastic material and configured so that it covered the outer diameter of the rotating Cam 520 switch. The open end of the button switch 602 is configured so that it took the key switch 532, thus providing a connection to each other switching part 510 and the rotating Cam 520 switch without mounting means. The rotating Cam 520 switch formed many spacers 534, which are protruding parts, concentric relative to the housing 530 switch and retreating from it radially outward. Spacers support 534 arcuate strip 600, preventing entry into the arcuate contact strip with wire legs 526 in the first curvilinear grooves a and 540b. Spacers 534 t is the train used to selectively strengthen areas of the rotating Cam 520 switch such as areas adjacent to the first curved grooves a and 540b.

Specialists in the art will understand that the rotating Cam 520 switch (that is, the first curved grooves a and 540b and second curved slots a and 544b) may be configured or otherwise for securing the entry engages the second ring gear 360 with the second planetary gears 362 and the first step-down planet carrier 314 when entering engages the third ring gear 400 with the third planetary gears 402 and the third step-down planet carrier 404 to obtain the position of the block 16 step-down gear with the fourth overall decline or gear ratio.

Specialists in the art will understand that instead of shown here mechanism 60 of the switch can be applied to mechanisms other switch configurations. These mechanisms of the switches may include actuators driven rotational or sliding movement, and may include traction, Cams or other devices known in the art, to ensure the sliding of the second and third ring gears relative to the sleeve 200 of the transmission. Specialists in the art will also understand that when the second and third ring subca the s wheels 360 and 400 can be independently moved between active and passive modes (i.e., the location of one of the second and third ring gears 360 and 400 does not dictate the location of the other of the second and third ring gears 360 and 400), the mechanism 60 of the switch can also be configured to install the second and third ring gears 360 and 400 independently from each other.

The mechanism of adhesion

On Fig, 26 and 28-30 shows the mechanism 18 of the clutch containing element 700 clutch, the drive unit 702 clutch and control mechanism 704. The coupling element 700 is shown as a circular structure, which is fixed on the outer diameter of the first ring gear 310 and which extends radially outward from him. Element 700 clutch includes an arcuate surface 316 of the clutch formed on the front surface 318 of the first ring gear 310. The magnitude of the outer diameter of element 700 clutch allows it to rotate inside the hollow part of the recess 212 formed by the base 216 of the sleeve 200 of the transmission. As shown in Fig, the surface 316 of the clutch in the example shown is formed by a set of vertices 710 and troughs 712 located relative to each other so that they form a series of inclined surfaces at an angle, constituting approximately 18°. However, specialists in the art will understand that can also be used in other configurations of the surface of clutch, such as surface 316' clutch sinusoidal (figa).

Although the first ring is update wheel 310 and the coupling element 700 is shown as a single structure (i.e. formed in one piece), specialist in the art will understand that they can have a different design. One such variant embodiment of the invention shown in fig.29b, where the first ring gear 310 is shown as including an annular ledge 1000 and many slots 1002 for the petals. The annular ledge 1000 is shown as including a multitude of inclined surfaces 1004 with gradients in two directions, but in other places flat. The first ring gear 310' in other respects identical to the first annular gear wheel 310. To the annular ledge 1000 adjacent ring buffer element 1008, including many petals 1010, which engages with the notches 1002 for petals in the first ring gear 310' to prevent rotation of the buffer element 1008 relative to the first ring gear 310'. The buffer element 1008 includes Cabinet portion 1012 configured in such a way that it matches the contour of the annular ledge 1000, and includes many parts of 1014, which are configured to mate with each of the inclined surfaces 1004. The buffer element 1008 is formed of a suitable shock absorbing material, such as acetyl. Element 700' clutch, which is annular element formed of wear-resistant material, such as tempered the tal 8620, located on top of the buffer element 1008. As the buffer element 1008, the element 700' clutch includes many petals 1020, which are locked in the notches 1002 for the petals to prevent rotation relative to the first ring gear 310', and many of the mating parts of the 1022. The mating inclined portion 1022 element 700' clutch come into contact with the mating inclined parts 1014 buffer element 1008. Although this design is more expensive in comparison with the previously described embodiment of the invention, it better stand high shock loads associated with the operation of the clutch mechanism 18.

In the specific embodiment of the invention, the node 702 clutch includes a pin element 720, spring 722 of the pusher and the pusher 724. The whip element 720 includes a cylindrical portion 730 having an outer diameter providing a sliding fit within the second portion 278 of the hole 274 of the actuator, formed in part 248 to place pin sleeve 200 transmission. The whip element 720 also includes a terminal portion 732 and the cylinder 734. Terminal portion 732 is configured to enter into contact with the regulating mechanism 704 and in the example shown is formed on the end of the hull 730 whip element 720 with a spherical radius. Head 734 is connected to the end of the Cabinet h and 730, the opposite terminal parts 732, and configured in the form of a flat cylinder or drum having a size to provide a sliding fit within the first portion 276 holes 274 to drive. Accordingly, the cylinder 734 prevents ejection pin element 720 forward from the opening 274 to drive.

Spring 722 pusher is a compression spring, outer diameter which provides a sliding fit within the first portion 276 holes 274 to drive. The front end of the spring 722 of the pusher comes into contact with the cylinder 734 pin element 720, while the opposite end of the spring 722 of the pusher comes into contact with the follower 724. Terminal part 740 of the pusher 724 has a cylindrical configuration and size to provide a sliding fit within the inner diameter of the spring 722 pusher. In this regard, the terminal part 740 of the pusher acts as a spring rod to prevent bending of the spring 722 pusher when it is compacted. The pusher 724 also includes a pushing part 744, which has a cylindrical housing portion 746, terminal part 748 and the ledge 750. Body part 746 has dimensions, providing a sliding fit within the first portion 276 holes 274 to drive. Terminal part 748 is configured for entering into contact with the surface 316 of the coupling is possible and in the example shown is formed as an end of the carcass part 746 of the pusher 724 with a spherical radius. Step 750 is formed on the boundary between the carcass part 746 and terminal part 740. The ledge 750 has a flat shape and is designed to receive bias of the efforts transmitted by the spring 722 pusher.

Also shows the adjustment mechanism 704, including the adjustment structure 760 and ring 762. The adjustment structure 760 is configured in the form essentially of a hollow cylinder having dimensions providing the fit in the case 766 node 20 of the output shaft. The adjustment structure 760 includes an annular surface 768, which formed the adjustment profile 770. The adjustment profile 770 includes a first adjusting segment 772, the last adjustment segment 774, many intermediate adjustment segments 776 and an inclined section 778 between the first and last adjustment segments 772 and 774. In the shown embodiment of the invention between the last intermediate adjustment segments 776z and the last adjustment segment 774 has a second inclined section 779. In addition, in the specific embodiment of the invention, part of the adjustment profile 770 from the first adjustment segments 772 until the last intermediate of the adjusting segment 776z formed as an inclined surface having a constant slope. Accordingly, the Cam track is the real surface 780, connected with the housing 766 node 20 of the output shaft, is displaced radially outward toward the inner diameter of the adjustment structure 760, where it interacts with many retainers 782 formed in the regulatory mechanism 704 (for example, in the installation ring 762). The pusher 724 and a lot of clamps 782 interact, providing to the user of the tool 10 feel the designation position of the adjustment profile 770, and also preventing free rotation of the adjustment structure 760 and holding the position of the adjustment profile 770 in the desired one of the adjustment segments 772, 774 and 776.

Ring 762 is connected to the outer surface of the adjustment structure 760 and includes many convex captured surfaces 790, which allow the user of the tool 10 is conveniently rotate and ring 762, and the adjustment structure 760 to set the required segment from the number of adjustment segments 772, 774 and 776 of the adjustment profile 770. For display position adjustment profile 770 relative to the housing 766 node 20 of the output shaft is the installation indicator 792. In the example installation indicator 792 includes arrow 794 located on the housing 766 node 20 of the output shaft, and on the circumference of the adjusting ring 762 applied SHK is La 796.

When the tool 10 primary drive torque is transmitted to pinion 46 of the electric motor from the node 14 of the electric motor to the first set 312 of the planetary gears, which causes rotation of the first set 312 of the planetary gears. The rotation of the first set 312 of the planetary gears of the first annular gear wheel 310 is communicated to the first intermediate torque. This point provides the resistance of the clutch torque, which is generated by the mechanism 18 of the clutch. Clutch torque prevents free rotation of the first ring gear 310, which causes the message to the first intermediate torque to the first downward cage 314 and the rest of the block 202 lower gears in such a way that it increases the first intermediate torque specified in accordance with the setting of the change-over mechanism 60. Thus, the mechanism 18 clutch shifts the first step-down node 302 gears in the active mode.

The magnitude of the clutch torque is set by the regulating mechanism 704 and, more specifically, the relative height adjustment segments 772, 774 or 776, which comes in contact with the target part 732 pin element 720. When installing the regulatory mechanism 704 at a given one of regulierungsrahmen 772, 774 or 776 whip element 720 is pushed back into the hole 274 to drive, thus compressing the spring 722 pusher and creating traction force. Adhesive force is transmitted to the ledge 750 pusher 724, causing the coupling terminal part 748 of the pusher 724 surface 316 of the clutch and the creation of the clutch torque. The location of the terminal part 748 of the pusher 724 in one of the cavities 712 on the surface 316 of the clutch prevents rotation of the first ring gear 310 relative to the sleeve 200 of the transmission when the value of the clutch torque exceeds the first intermediate torque. However, when the first intermediate torque exceeds the clutch torque, the first ring gear 310 receives the opportunity to rotate relative to the sleeve 200 of the transmission. Depending on the configuration of the surface 316 of the clutch, the rotation of the first ring gear 310 may cause the increase of the adhesion forces sufficient to resist further rotation. In such situations, the first ring gear 310 is rotated in the opposite direction, when the value of the first intermediate torque is reduced, allowing the alignment of the terminal part 748 of the pusher 724 in one of the cavities 712 in the surface 316 of the clutch. If the rotation of the first ring gear to the ECA 310 does not cause increase of the adhesion forces sufficiently to prevent rotation of the first ring gear 310, the first step-down node 302 gears will be in the position of a passive mode in which the first ring gear 310 rotates, preventing transmission of the first intermediate torque to the first downward cage 314. In such situations, the torque will not be transmitted to the parts of the transmission unit 16, which are located in front of the first set 312 of the planetary gears (for example, the first lowering planet carrier 314, the second sun wheel 358, a second set of 362 planetary gear wheels).

This configuration mechanism 18 of the clutch is very predominant in the fact that the magnitude of the clutch torque is set so that it withstood the first intermediate torque as opposed to the output torque of the tool 10, which is generated multi-stage reducing gear hub 16 and is passed through a jaw Chuck 22. Therefore, the mechanism 18 of the clutch may be of relatively small size, which thus increases its ability to be included in the design of the tool 10 or the installation of it. In addition, since the rotational speed or the gear ratio change after the first ring gear 310, the mechanism 18 of the clutch operates with a relatively large range of output torques. Compared the structure with the conventional clutch mechanisms, which operate to limit the output torque of the transmission, these devices typically operate in a relatively narrow range of torques, requiring replacement of their spring clutch, if you want a significant change in the value of the output torque. In contrast, the mechanism 18 of the clutch corresponding to the present invention can adapt to a significant change in the value of the output torque of the tool 10 by means of a simple operation transmission unit 16 with another (i.e. low or high) gear ratio.

When operating rotating machinery tools, such as tool 10, it is often necessary to change one setting clutch to another, for example, when the tool 10 is used for drilling holes and then screwing the screw into this hole. Accordingly, the adjustment mechanism 704 can be rotated with respect to the host 20 of the output shaft to install the regulatory mechanism 704 in accordance with the required adjustment segments 772, 774 and 776 to perform the first operation and then turn in the second position of the adjustment segments 772, 774 and 776 to perform the second operation. In contrast to the well-known clutch mechanisms regulating mechanism 704 corresponding to the present invention, configured so that the adjustment structure 760 and ring 762 can rotate 360°. Assuming that the adjustment structure 760 should be installed in accordance with the interim adjustment segment h, the rotation regulating mechanism 704 at an angle of 360° will cause rotation of the adjustment structure 760 with the passage of other intermediate adjustment segments 776, as well as the first and last adjustment segments 772 and 774 and an inclined section 778 so that the adjustment structure 760 can be re-installed in accordance with the adjusting segment h. This feature is especially useful if you need to change the setting of the clutch from the relatively high strength of adhesion to a relatively low friction. Inclined section 778 allows you to rotate the adjusting ring 762 (and the adjustment structure 760) from the position of maximum adhesion forces, the last adjustment segment, at minimum power clutch corresponding to the first installation, without the need to establish a mechanism of the clutch 18 in one of the intermediate units of the clutch. Accordingly, the user of the tool 10 is capable of changing the setting of the adhesion forces from the highest setting to the lowest setting (and Vice versa) by rotation of the mouth of the mounting ring 762 at a relatively small angle.

Although the adjustment profile 770 so far was described as having a constant slope, specialists in the art will understand that the invention in a broader sense can be made any other way. For example, the adjustment profile 770' may be formed so that each of the first, last and intermediate adjustment segments 772', 774' 776' will have a locking recess, as shown in Fig. In this device, the locking elements 782 in the adjustment structure 760 and Cam followers surface 780 in the case 766 node 20 of the output shaft is not needed, because the adjustment segments 772', 774' 776' will interact with the node 702 clutch, providing to the user of the tool 10 feel the designation position of the adjustment profile 770' and preventing free rotation of the adjustment structure 760.

Another example is shown in Fig, where the adjustment profile 770" in General, this adjustment profile 770, except that the inclined section 779 excluded and, therefore, the last intermediate of the adjusting segment 776z directly adjacent to the last adjustment segment 774.

Although the invention has been disclosed in the description and illustrated in the drawings with reference to a specific variant of its implementation, the special is there in the art will understand, that it can be made various changes, and its elements can be replaced by equivalents without departing from the scope of the invention defined by the claims. In addition, in a variant embodiment of the invention can be made many modifications to adapt to a particular situation or material without departing from the true scope of the invention. Thus, it is assumed that the invention is not limited to a particular variant of its implementation, shown in the drawings and disclosed in the description as the best currently considered a variant of implementation of the present invention, and will include all variants covered by the scope of the attached claims.

1. The drive for machine tool, comprising a housing, a transmission including a first node, a reduction gear, a second node, a reduction gear and a third node, a reduction gear, and at least two of the first, second and third nodes lower gears are designed to work in passive mode and active mode to perform the operation reduce speed and increase torque, and at least two of the first, second and third nodes of the step-down gear is configured to move between active the m and passive modes so that that provides selective operation of the transmission in at least three positions for different gear ratios.

2. The actuator according to claim 1, additionally containing a derailleur having a switching part and a drive part and a switching part connected to the housing for movement between a first position, second position and third position, and the guiding portion in the operating position is connected to the transmission to move at least one element of the transmission, the transmission is performed with the opportunity to work with the first speed when the switching part in the first position from the second speed when the switching part in the second position and the third rotational speed when the switching part in the third position.

3. The actuator according to claim 2, in which the derailleur is made to move two of the first, second and third nodes lower gears between active and passive modes, and the actuator further includes a node clutch that holds the other one of the first, second and third nodes lower gears in the active mode, when that does not exceed the torque supplied to the other one of the first, second and third nodes to reduce tooth is atih transmission specified torque clutch.

4. The actuator according to claim 3, in which the second and third nodes lower gears are two of these first, second and third nodes lower gears, and the second and third nodes of the step-down gear is active when the switching part in the first position, one of the second and third nodes of the step-down gear is active, and the other one of the second and third nodes of the step-down passive gears when switching portion in the second position and both the second and third nodes of the step-down passive gears when switching part in the third position.

5. The actuator according to claim 1, in which at least one of the first, second and third nodes of the step-down gear includes a ring gear wheel, is arranged to move between the first position is fixed relative to the housing, and a second position of rotation relative to the housing, and the ring gear is made with the possibility of its establishment in the first position when at least one of the first, second and third nodes lower gears in the active mode, and the ring gear is made with the possibility of its establishment in the second position when at least one of the first, second and third nodes is onizawa gears in passive mode.

6. The actuator according to claim 5, in which each of the first, second and third nodes of the step-down gear includes a ring gear.

7. The actuator of claim 1, wherein the switching part is connected to the housing for rotation between first, second and third positions around the first axis.

8. The actuator according to claim 7, in which the first axis is a longitudinal axis of the transmission.

9. Transmission node for transmitting torque to the output shaft of machine tool, comprising a housing having a wall forming a channel for transmission, the first part of the drive train having a first input element, the first output element and the first reduction element, and the first input element configured to receive the first intermediate output torque of the first output element is configured to issue the second intermediate output torque, the first reduction element works in the first position when the increase in the first part of the transmission of the first intermediate output torque to a predetermined first value, the first reduction item operates in the second position when the increase in the first part of the transmission the first intermediate output torque to a predetermined second value, and the second part of the transmission with the second input element, the second o is the initial element and the second reduction element, moreover, the second input element configured to receive the second intermediate output torque, the second output element is designed with the ability to provide output torque to the output shaft of the second reduction element works in the first position when the magnification of the second part transmission of the second intermediate output torque to a predetermined third value, the second step-down element runs in the second position when the magnification of the second part transmission of the second intermediate output torque to a predetermined fourth value and the first and second step-down items made with the possibility of the election of the establishment to obtain a transmission unit with at least three gear ratios.

10. The transmission node according to claim 9, in which at least one of the first and second parts of the transmission is a node of the planetary gear.

11. The transmission node according to claim 9, in which at least one of the first and second step-down element is a ring gear.

12. The transmission node according to claim 11, in which the ring gear is made slidable in the axial direction, which is parallel to the longitudinal axis of the channel for transmission.

13. The transmission node indicated in paragraph 12, in which the annular gear to the eco made slidable between a first position, in which the ring gear is fixed relative to the housing, and a second position in which the annular gear wheel accommodated rotatably inside the housing.

14. The transmission node according to claim 9, in which the first and second step-down elements are made with the possibility of independent movement between first and second positions.

15. The transmission node according to claim 9, in which the first intermediate output torque creates another part of the transmission node.

16. The transmission node according to 15, optionally containing a third part of the drive train having a third input element, the third output element and the third step-down element, and the third input element configured to receive the input torque, the third output element configured to output of the first intermediate output torque, the third reduction item operates in the first position when you commit a third of the reduction element relative to the housing to enable the third part of the transmission to increase the input torque of the fifth preset value.

17. The transmission node according to clause 16, in which the third step-down element configured to work in the second position, the third step-down element configured to move relative what about the casing to prevent the increase in the third part of the transmission input torque on the fifth preset value.

18. The transmission node according to 17, further containing a node clutch having an annular flange and the drive unit clutch, and an annular flange connected to one of the first, second and third lower elements and has a specified profile of the clutch, the drive unit clutch has a pusher, and the pusher abuts against the annular flange and communicates with the profile of the coupling to prevent relative rotation between the annular flange and the plunger when the application to one of the first, second and third lower elements of the torque having a magnitude which is less than the preset value of maximum torque.

19. Machine tool, comprising a housing having a wall that forms a channel for transmission, and the transmission having a first node of the planetary gear and the second node of the planetary gear, the first node planetary gear set includes a first ring gear, the first sun wheel and the first node of the planetary gears, and the first node of the planetary gears has a first planetary carrier and the set of first planetary gears, a first planetary pinion carrier has an output sun wheel and plenty of pins for holding rotatably a multitude of first planetary gears, the first Solna is Noah wheel is configured to receive the first intermediate output torque the moment the output sun wheel made with the possibility of issuing a second intermediate output torque, the set of first planetary gears posted with the possibility of entering into engagement with the first sun wheel and with the first ring gear, the first ring gear is placed to be movable in the axial direction in the first position, in which the first ring gear is fixed relative to the housing to prevent relative rotation between them, the first ring gear is also placed so that they can move in the axial direction into a second position in which the first ring gear is placed rotatably in the channel for transmission, and the second node the planetary gear set includes a second ring gear and the second node of the planetary gears, and the second node of the planetary gears has a second planetary carrier and the set of second planetary gears, a second planetary pinion carrier has an output element and a lot of pins for holding rotatably the second set of planetary gears, a lot of second planetary gears communicates with the second annular gear wheel and the output sun wheel and with the possibility of the reception of the second intermediate output torque, the output element is made with the possibility of delivery of the output torque, the second ring gear is placed to be movable in the axial direction in the first position, in which the second ring gear is fixed relative to the housing to prevent relative rotation between them, the second ring gear is placed to be movable in the axial direction into a second position in which the second ring gear accommodated rotatably inside the channel for transmission, each of the first and second ring gears are placed with selective installation in the first and second position to obtain a mechanized tool with at least three working speeds.

20. Machine tool according to claim 19, in which the first and second ring gears are made with the possibility of independent movement between first and second positions.

21. Machine tool according to claim 19, in which the transmission also includes a third node planetary gear set having a third ring gear, the third sun wheel and the third node of the planetary gears, and the third node of the planetary gears has a third planetary carrier, and many of the third planetary gear stake is, the third planetary carrier rotatably connected with the first sun wheel, the third planetary carrier has a lot of pins for holding rotatably a variety of third planetary gears, the third sun wheel is configured to receive the input torque, the third planetary carrier configured to transfer the first intermediate output torque to the first sun wheel, many of the third planetary gear wheels in contact with the third sun wheel and with the third ring gear, the third ring gear is configured to move in the axial direction in the first position, in which the third ring gear is fixed relative to the body.

22. Machine tool according to item 21, in which step-down element of the third node of the planetary gear is arranged to work in the second position, in which the third ring gear accommodated rotatably inside the housing.

23. Machine tool according to article 22, optionally containing node clutch having an annular flange and the drive unit clutch, and an annular flange connected to one of the first, second and third ring gears and has a specified profile clutch, etc is this the drive unit clutch has a pusher, the plunger abuts against the annular flange and communicates with the profile of the coupling to prevent relative rotation between the annular flange and the follower when the torque supplied to one of the first, second, and third ring gears, has a value which is less than the value specified maximum torque.

24. Machine tool according to item 23, further containing a switching node to coordinate the axial sliding movement of the first and second ring gears.

25. A mechanized tool containing a motor having an output shaft, the engine creates an input torque transmission unit having a housing and a transmission, the housing has a wall forming a channel for transmission, the transmission has a first node of the planetary gear, the second node of the planetary gear and the third node of the planetary gear, and the first node of the planetary gear has a first ring gear, the first sun wheel and the first node of the planetary gears, the first node of the planetary gears has a first planetary carrier and the set of first planetary gears, a first planetary pinion carrier rotatably connected with the first sun wheel, with the first planetary carrier has set the creation of the pins for holding rotatably a multitude of first planetary gears, the first sun wheel is configured to receive the input torque, the first planetary carrier includes a second sun wheel and configured to transfer the first intermediate output torque to the second node planetary gear set, while the set of first planetary gears interacts with the second sun wheel and with the first ring gear, the first ring gear is configured to move in the axial direction in the first position, in which the first ring gear is fixed relative to the housing, the second node of the planetary gear includes a second ring gear and the second node of the planetary gears, the second node of the planetary gears is the second planetary carrier and the set of second planetary gears, a second planetary pinion carrier has an output sun wheel and plenty of pins for holding rotatably the second set of planetary gears, with the second sun wheel interacts with many of the second planetary gear wheels to transmit them to the first intermediate output torque, the output sun wheel made with the possibility of issuing a second intermediate output torque, the centre of the second planetary gears also communicates with the second annular gear wheel, the second ring gear is configured to move in the axial direction in the first position, in which the second ring gear is fixed relative to the housing to prevent relative rotation between them, the second ring gear is also made with the possibility of moving into the second position in which the second ring gear accommodated rotatably inside the channel for transmission, the third node planetary gear set includes a third ring gear and the third node of the planetary gears, the third node of the planetary gear has a third planetary carrier and a lot of third planetary gears, and the third planetary carrier has an output element and a lot of pins for holding rotatably a variety of third planetary gears, a lot of third planetary gears interacts with the third ring gear and the output sun wheel and configured to receive the second intermediate output torque, the output element is designed with the possibility of delivery of the output torque, the third ring gear is configured to move in the axial direction in the first position, in which the third ring gear is a wheel fixed relative to the housing to prevent relative rotation between them, the third ring gear is also made with the possibility of moving in the axial direction into a second position in which the third ring gear accommodated rotatably inside the channel for transmission, and each of the second and third gear wheels made with the possibility of selective setting in the first and second position to obtain a mechanized tool with at least three working speeds.

26. Machine tool A.25, in which the first ring gear is also designed to work in the second position, in which the first annular gear wheel placed with a possibility of rotation relative to the body.

27. Machine tool A.25, in which the transmission node further comprises a node clutch having an annular flange and the drive unit clutch, and an annular flange connected to one of the first, second and third ring gears and has a specified profile of the clutch, the drive unit clutch has a pusher, the pusher abuts against the annular flange and communicates with the profile of the coupling to prevent relative rotation between the annular flange and the follower when the torque supplied to one of the first, second and third ring gear stake is, has a value which is less than the value specified maximum torque.

28. Machine tool according to item 27, further containing a switching node to coordinate the axial sliding movement of the second and third ring gears.

29. Portable machine tool, comprising a housing, a motor located in the housing and including an output element of the engine, a driven element and a transmission located in the housing in the operating position is connected with the output element of the engine, the transmission has at least three separate gear ratios, the transmission includes a number of units of gear, at least two of which are designed to work in active mode, and in another mode other than the active, these two nodes gears configured to operate in active mode, when the transmission operates at least in one of three positions for different gear ratios.

30. The tool according to clause 29, additionally containing a shifter coupled to the housing and cooperating with the transmission, and the shifter is made with the possibility of changing gear ratios in accordance with the input setting.

31. The tool according to item 30, in which the first lane from the handout numbers off and the second gear ratio is switched in accordance with the installation the input to the shifter.

32. The tool according to item 30, in which the shifter is connected rotatably to the body.

33. The tool according to clause 29, in which the transmission includes at least one movable element which is selectively set to change the first gear ratio to other gear.

34. The tool p, in which the transmission contains at least one node of the planetary gear having a sun wheel, a node of the planetary gears and the ring gear, and the movable element includes at least one of the sun wheels, a node of the planetary gears and the ring gear.

35. The tool 34, in which at least one of the sun wheels, a node of the planetary gears and the ring gear is arranged to move in the axial direction for engagement with the locking structure.

36. The tool p, in which the locking structure comprises a gear element formed in the body.

37. The tool p, in which the interaction of at least one of the sun wheels, a node of the planetary gears and the ring gear with locking design prevents relative rotation between the sun wheel, planet site is different gears and the ring gear.

38. The tool 34, optionally containing a shifter having an actuator made with the possibility of application of force to the surface of at least one of the sun wheels, a node of the planetary gears and the ring gear, and this surface is oriented essentially perpendicular to the longitudinal axis of the drive element, while applying pressure to the surface moves at least one of the sun wheels, a node of the planetary gears and the ring gear for at least a partial change of the gear ratio.

39. Tool 38, in which the surface is annular wall formed around the ring gear.

40. The tool according to clause 29, additionally containing a node clutch connected to at least one of the powertrain and the driven element, and the node coupling configured to limit the output torque, which is transmitted through the driven element.

41. The tool p, in which the transmission node contains a planetary gear set having a ring gear, the knot clutch is operating in the first position, in which the interaction between the host clutch and ring gear holds the ring gear in non-rotating position, and the node coupling ispolnen with the opportunity to work in the second position, in which the ring gear is placed with the possibility of rotation.

42. The tool according to clause 29, in which at least one of the two nodes gear is in an inactive mode when the transmission operates in a different one of the three positions for different gear ratios.

43. Method of drilling holes, which receive a tool having a transmission with multiple nodes of the planetary gear, and the transmission has a movable part, which provides the transmission with at least three separate ratios, move the movable portion of the transmission from the first position to the second position and drill the hole tool, working with the rotational speed being in the range specified by the second position of the specified floating moving parts, and placing the movable part in the first position causes an increase in at least one of the multiple nodes of the planetary gear input for this node point to a predetermined first value and placement of mobile part in the second position causes an increase in at least one of the multiple nodes of the planetary gear input for this node point to a predetermined second value that is different from the first value.

44. The method according to item 43, in which the travel of moving the Asti in one of the first and second positions prevents relative rotation of the movable part relative to the rest of the at least one of the multiple nodes of the planetary gears.

45. The method according to item 44, in which the movement of the movable part to another of the first and second positions allowing rotation of the movable part relative to the rest of the at least one of the multiple nodes of the planetary transmission.

46. The method according to item 45, in which the movable part of the drive train includes a ring gear with internal teeth and external teeth.

47. The method according to item 46, in which the annular gear wheel is connected with one of the nodes of the planetary gear.

48. The method according to item 44, in which the moving operation of the movable part includes at least one input stimulus to the tool.

49. The method according to p, in which at least one input action is reported to the shifter, which in the working position is connected with a moving part.

50. The method according to 49, in which at least one input parameter is a rotational movement.

51. The method according to item 50, in which the movable part includes a timing element, which is moved to the position of engagement and withdrawal from interaction with another part of the transmission through the work of the shifter.

52. The method according to 51, in which the shifter moves the toothed element in a direction essentially parallel to the axis of at least one of the multiple nodes of the planetary transmission.

53. With the persons in paragraph 52, in which the gear element is a ring gear.

54. The method according to item 53, in which another part of the transmission is a planetary carrier.

55. Portable machine tool, comprising a housing, a motor, a driven element and a multistage transmission, at least partially located in the housing, which receives torque from the engine and transmits the output torque on the driven element, and a multi-stage transmission includes the first node gears, the second node gears and the third node gears, while the first node gears has a first planetary carrier and the set of first planetary gears supported for rotation planetary planet carrier, the second node gear includes a ring gear that is not in mesh with the planetary gears the first node gears, and a planetary carrier, the third node gear includes a ring gear and a planetary carrier, and a multi-stage transmission is performed with at least three positions for the total gear ratio, while the ring gear of one of the second timing node and a third timing node may be selectively connected by scorponok to prevent relative rotation between them, thus the annular gear wheel of the other one of the second timing node and a third timing node may be selectively connected with one of the planetary carrier.

56. The tool according to 55, in which the second ring gear is configured to move from a position in which it is connected to the housing, and an opposite position in which it engages with the planetary planet carrier of the first timing node.

57. The tool p, in which the third ring gear is configured to move from a position in which it is connected to the housing, and an opposite position in which it is able to rotate relative to the body.

58. Tool 57, in which the torque is transmitted from one of the first, second and third units of gear to another one of the first, second and third units of gear, and then to the rest of the one of the first, second and third units of gear.

59. The tool p containing switching part to change the overall gear ratio, which provides a multistage transmission.

60. The tool p, in which the switching part includes a wire clip, which is adapted to move relative to the longitudinal axis of the multistage transmission, you are yvouxeo change the overall gear ratio, when running a multi-stage transmission, the movement of the wire bail is used to connect the ring gear of the second node of the gear housing and for connecting the ring gear of the second node gears with planetary planet carrier of the first node gears.

61. The tool p, in which the wire clamp includes a housing part that goes on the outside part of the ring gear.

62. The tool p, in which a multi-stage transmission further includes a sleeve of the transmission, which is connected to the housing, and at least part of a second node of the gear is located in the sleeve and the sleeve has an inner surface with lots of teeth through which the transmitted torque, is used to connect the ring gear of the second node timing transmission case.

63. The tool according to item 62, optionally containing a wire clip, which is adapted to move relative to the longitudinal axis of the multi-stage transmission, which causes changes in the overall gear ratio, which provides a multistage transmission, thus moving the wire bail is used to connect the ring gear of the second node gears with the body and with the organisations the ring gear of the second node gears with planetary planet carrier of the first node gears.

64. The tool p, in which the sleeve of the transmission comprises a pair of grooves adapted for insertion into their respective pads formed on the wire bracket.

65. The tool p, in which the foot is configured to transmit the input force applied to the drive gear, which is located on the outer side of the sleeve multistage transmission, to a portion of a multi-stage transmission on the outer side of the sleeve multistage transmission.

66. The tool according to item 62, in which the outer surface of the sleeve of the transmission formed many teeth for torque transmission, which is used to connect the ring gear of the third node of the gear transmission case.

67. Machine tool, comprising a housing, a motor for actuating output shaft through a multi-stage transmission, which provides numerous step-down planetary gears between the motor and the output spindle, the two step-down planetary gear selectively set in a first mode in which the ring gear is rotated relative to the housing, and a second mode in which the ring gear is connected to the housing, and the transmission provides at least three working with the stand: the first one of the ring gears is in the first mode and the second one of the ring gears is in the first mode,, the first one of the ring gears is in the first mode and the second one of the ring gears is in the second mode, the first one of the ring gears is in the second mode and the second one of the ring gears is in the first mode, and the first one of the ring gears is in the second mode and the second one of the ring gears is in the second mode.

68. The tool p, where the translation of the first one of the ring gears in the first mode, one of the many planetary gear means in an inactive mode.

69. The tool p, where the translation of the second one of the ring gears in the first mode, one of the many planetary gear means in an inactive mode.

70. The tool p, optionally containing adhesion, while the profile of the clutch is formed on the annular gear wheel of the third reduction planetary gear.

71. The tool according to item 70, in which a third decreasing the planetary gear is a multi-stage transmission, which is most close to the engine.

72. The tool p, in which the shifter includes an actuator that moves the element into engagement with the mating element for translation with is the fact that one of the selectively settable lower planetary gears in the first mode, when this element or the mating element is connected with the toothed wheel of the corresponding one of the selectively settable lower planetary gears.

73. The tool according to item 72, in which the element or the mating element is connected with the annular gear wheel of the corresponding one of the selectively settable lower planetary gears.

74. The tool according to item 72, in which the engagement element and stragelove element is effected by sliding movement of the actuator.

75. The tool p, in which the drive also rotates when the element is engaged with the mating element.

76. The tool p, in which the actuator includes a housing, a wire in the form of a semicircle.

77. The tool p, in which the ring gear is moved when changing the mode in which they are located between the first mode and the second mode.

78. Hand power tool, containing a motor, an output spindle and a transmission connected to the motor and the output spindle, the transmission has many steps, interacting so that provided a three gear ratios, for each of which there are three stages that are set so that the output of one stage is the input for the subsequent steps, and measures at the two of the many degrees are in an active state for at least one gear ratio and at least one of the multiple stages is not in the active state for at least two of the three gear ratios.

79. The tool p, in which at least one of the steps is provided in an inactive state by fixing the ring gear of the node of the planetary gear so that it rotates together with the sun gear, which is connected with the planetary gear.

80. The tool p, in which the ring gear is arranged to move into engagement with the planetary planet carrier to bring the level in the inactive state, while the planetary carrier connected for rotation with a sun gear wheel.

81. The tool according to item 80, in which the ring gear is arranged to move into engagement with the planetary planet carrier to bring the level in the inactive state, while the planetary carrier supports multiple planetary gears which are in mesh with the sun gear and the annular gear wheel.

82. The tool p, in which the first one of the stages is inactive for one of the gear ratios and the other one of the steps is inactive for another one of the gear ratios.

83. The tool p in which each of the gear ratios is achieved by activating one step and izbiratelni the th activation or removal from the active state at least two other steps.

84. The tool p, in which at least one of the steps of selectively activated by fixing the ring gear so as to prevent relative rotation between the ring gear and the housing, in which is located the annular gear wheel.

85. The tool p, in which the annular gear wheel includes a set of external teeth, incoming engages with lots of teeth formed on the inner surface of the element, located between the housing and the ring gear, when the degree connected with the annular gear wheel is in an active state.

86. The tool p, wherein said element is a sleeve powertrain.

87. The tool p, in which the annular gear wheel or the specified element is arranged to move between the first position and the second position, thus placing the ring gear or the specified element in the first position prevents relative rotation between the ring gear element and the housing.

88. The tool p, in which the degree connected with the annular gear wheel is in an inactive state, when the ring gear or the specified element placed in the second position.

89. The tool p, more is tion containing the clutch, which contains an annular coupling element, plunger and spring, and the coupling element is connected with the annular gear wheel associated with one of the gears, and the spring pushes the plunger to the coupling element so that prevents relative rotation between the ring gear and the housing, in which is placed a ring gear.

90. The tool p, in which the annular gear wheel associated with stage, is in the active state for each of the three gear ratios.

91. The tool p, in which the transmission is connected directly to the motor and the output spindle.



 

Same patents:

FIELD: transport engineering.

SUBSTANCE: proposed wheel has rim of regular shape and center of rotation. To drive the wheel, planetary reduction gear is fitted in wheel rim whose drive gear is planet pinion installed on driving "floating shaft whose axis, taking weight of vehicle applied to wheel, executes complex movement relative to axis of wheel rotation making it possible to: 1) spread projections of axis of rotation (being simultaneously point/line of support) of wheel and point of application of vehicle weight P to wheel on horizontal surface by some distance L; 2) change position of projection of point P on vertical; plane by some height h and provide constantly acting "canting" torque PL on wheel creating effect of eccentric wheel at wheel circumference remaining unchanged and eliminating cyclic loads.

EFFECT: improved cross-country capacity of vehicle, its steerability, efficiency of wheeled propulsor, simplified design.

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Mechanized tool // 2252348

FIELD: mechanical engineering.

SUBSTANCE: mechanized tool comprises clutching unit and multi-speed planet transmission. The clutching unit comprises clutch member and pusher. The clutch member is connected with the transmission member which is mounted in the vicinity of the means for supplying input torque to the transmission and should be irrotational, allowing the transmission to increase the torque. The pusher is loaded for its engagement with the clutch member to prevent their mutual rotation. When the clutch member and transmission member are interconnected, transmission capable to increase the torque. When the value of the torque applied to the clutch member is sufficient to overcome friction between the pusher and clutch member, the clutch member and transmission member rotate thus preventing the transmission from increasing torque.

EFFECT: enhanced reliability.

25 cl, 38 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmissions controlled by electronic unit and hydraulic devices. Proposed hydromechanical transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. All planetary trains have negative inner gear ratio output link of torque converter is coupled with sun gear 8 of second planetary trains and is connected through friction clutch 17 with carrier 6 of first planetary train. Carrier 6 is coupled with sun gear 14 of fourth planetary train and, through friction brake 21, with case 1. Sun gear 5 of first planetary train is coupled with case 1 through friction brake 20. Ring gear 10 of second planetary train is connected through friction brake 19 with case 1 and through friction clutch 18, with carrier 12 of third planetary train. Carrier of 9 of second planetary train is coupled with sun gear 11 of third planetary train. Ring gear 13 of third planetary train is coupled with carrier 15 of fourth planetary train which is coupled with case through friction brake 22. Ring gear 7 of first planetary train is connected with ring gear 16 of fourth planetary train and with carrier 12 of third planetary train which is coupled link of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of nine forward speeds and one reverse speed at preservation of overall dimensions.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmission controlled by electronic unit and hydraulic devices. Proposed transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. All planetary trains have negative inner ratio. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 6 of first planetary train, and through friction clutch 17, with sun gear 5 of said train which is connected with case 1 through friction brake 19. Carrier 6 is connected with ring gear 13 of third planetary train and, through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with sun gear 11 of third planetary train. Ring gear 10 of second planetary train is coupled with sun gear 14 of fourth planetary train which is coupled through friction brake 22 with case 1. Carrier 15 of fourth planetary train is coupled, through friction brake 21, with case 1. Ring gear 16 of fourth planetary train is coupled with carrier 12 of third planetary train being output link of transmission.

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1 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmissions controlled by electronic unit and hydraulic devices. Proposed hydromechanical transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 12 of third planetary train and through friction clutch 17, with gear 11 of this train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is connected with case 1 through friction brake 19. Ring gear 10 of second planetary train is coupled with carrier 6 of first planetary train and through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with rings gears 13 and 16 of third and fourth planetary gear trains. Sun gear 14 of fourth planetary train is coupled with carrier 12 of third planetary train and, through friction brake 21, with case 1. Carrier 15 of fourth planetary gear train is output link of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of ten forward speeds and one reverse speed at preservation of overall dimensions.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmissions controlled by electronic unit and hydraulic devices. Proposed hydromechanical transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. All planetary trains have negative inner ratio. Output link of torque converter is coupled with ring gear 7 of first planetary train, with sun gear 8 of second planetary train and, through friction clutch 18, with carrier 12 of third planetary train, and through friction clutch 17, with sun gear 11 of the same train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is coupled with case 1 through friction brake 19. Carrier 6 of this train is coupled with carrier 9 of second planetary train, with ring gears 13 and 16 of third and fourth and fourth planetary trains. Ring gear 10 second planetary train is connected with case 1 through friction brake 20. Sun gear 14 of fourth planetary train is coupled with carrier 12 of third planetary train and, through friction brake 21, with case 1. Carrier 15 of fourth planetary train is output link 4 of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of ten forward speeds, one reverse speed and enlargement of range up to 6.286 at preservation of overall dimensions.

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The invention relates to mechanical engineering and can be used in industry, with the release of a high-performance machine with reciprocating movement of the working tool of continuous action

The invention relates to mechanical engineering and can be used in vehicles

The invention relates to the field of mechanical engineering

The invention relates to timing mechanisms continuously variable transmission and can be used in mechanical engineering, machine building and instrument making

FIELD: apparatuses designed for dismounting treaded joints.

SUBSTANCE: apparatus includes tool and guiding sleeve. Stem of tool has outer thread whose pitch is equal to that of unscrewed screw, bolt or nut. Sleeve has annular stop and inner thread forming together with tool stem screw pair. Sleeve through nut engages with bracket. The last sets position of tool relative to coordinate system of unscrewed screw, bolt or nut. In one end of tool stem with thread there is square for joining changeable heads for screws, bolts or nuts. In other end of tool stem there is cylindrical head with opening for placing tap wrench. It provides displacement and unscrewing of screws, bolts, nuts reliably locked by means of high effective means.

EFFECT: prevention of stripping of threaded tool.

2 cl, 2 dwg

Mechanized tool // 2252348

FIELD: mechanical engineering.

SUBSTANCE: mechanized tool comprises clutching unit and multi-speed planet transmission. The clutching unit comprises clutch member and pusher. The clutch member is connected with the transmission member which is mounted in the vicinity of the means for supplying input torque to the transmission and should be irrotational, allowing the transmission to increase the torque. The pusher is loaded for its engagement with the clutch member to prevent their mutual rotation. When the clutch member and transmission member are interconnected, transmission capable to increase the torque. When the value of the torque applied to the clutch member is sufficient to overcome friction between the pusher and clutch member, the clutch member and transmission member rotate thus preventing the transmission from increasing torque.

EFFECT: enhanced reliability.

25 cl, 38 dwg

FIELD: mechanical engineering.

SUBSTANCE: screw swinging mechanism comprises housing which receives above-piston and under-piston chambers, passages for supplying fluid into the chambers, and first nut. The mechanism is also provided with the piston with the rod and output shaft. The rod is provided with the first thread which cooperates with the first nut. The output shaft is mounted for permitting rotation and has the race provided with radial thrust bearing and second nut. The rod is also provided with the second thread, which interacts with the second nut.

EFFECT: expanded functional capabilities.

1 cl, 3 dwg

FIELD: mechanical engineering.

SUBSTANCE: nut-driver comprises actuator made of hydraulic cylinder, housing which receives the piston, and actuating mechanism made of detachable unit which comprises housing with the ratchet mechanism, ratchet wheel, and spring-loaded dog which engages the wheel. The dog is mounted in the lever groove. The housing of the unit is pivotally connected with the housing of the hydraulic cylinder. The teeth of the dog and mating hollows of the ratchet wheel are cylindrical.

EFFECT: enhanced convenience of operation and prolonged service life.

1 cl, 2 dwg

The invention relates to mechanical engineering and can be used when assembling threaded connections

The invention relates to a device for screwing or unscrewing nuts

The invention relates to mechanical devices, hydraulic Assembly and disassembly of threaded connections

Drive hand tool // 2219044
The invention relates to portable power tools

The invention relates to the field of mechanization of track facilities of railway transport and can be used when laying rail lashes or in the exercise of their discharge temperature

FIELD: mechanical engineering.

SUBSTANCE: nut-driver comprises actuator made of hydraulic cylinder, housing which receives the piston, and actuating mechanism made of detachable unit which comprises housing with the ratchet mechanism, ratchet wheel, and spring-loaded dog which engages the wheel. The dog is mounted in the lever groove. The housing of the unit is pivotally connected with the housing of the hydraulic cylinder. The teeth of the dog and mating hollows of the ratchet wheel are cylindrical.

EFFECT: enhanced convenience of operation and prolonged service life.

1 cl, 2 dwg

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