SU1191656A1 - Gearbox - Google Patents

Abstract

1. A TRANSMISSION BOX, comprising a housing, drive and driven shafts with pairs of permanently engaged gears mounted on them, forming gears for forward running, located on shafts in order of increasing gear ratio, gearshift mechanism, including a governing body, wheels mounted on one of the shafts with overrunning clutches with internal and external clips and jamming bodies, characterized in that, in order to increase box reliability when shifting gears without breaking the flow and power, the gearshift mechanism is designed as a cantilever slider in the control unit, which interacts with one side with the jamming bodies and passes the overrunning clutches between the internal and external clips. 2. Gearbox under item 1, characterized in that, in order to improve the smoothness of gear shifts, overrunning clutches are made friction, and their wedged bodies - in the form of wedge pads. 3. The gearbox under item 1, characterized in that it is. Packed in a transmission wheel mounted on a different shaft with a lower gear ratio with an additional overrunning clutch. 4. The gearbox under item 1, characterized in that the overrunning clutches are made ratchet, their wedged bodies - in the form of dogs. 5. The gearbox according to claim 1, characterized in that it is provided with cooperative plugs interacting with the slider, having slots for the slider and placed between the inner and outer collars. -6. The gearbox according to claim 1, characterized in that one of the extreme pairs of gear wheels is made single-handed, and the other wheels are double-cored and sequentially meshed with each other, the wheels mounted on the other shaft also have overrunning clutches that interact with an additional slide. 7. Gearbox on PP. 1 and 6, characterized in that it is equipped with a reverse gear, formed by a pair of gear wheels mounted on shafts and permanently connected by a chain, one of the wheels, mouth (L on the shaft with the slider, has a clutch integrated in it. 8 The gear box according to claim 7, characterized in that it is provided with a brake mounted on the driven shaft and interacting with the slide, and the overrunning clutches and slide slide are also mounted on the driven shaft. 9. The transmission gear box according to claims 1 and 7, characterized by the fact that it is equipped with a second and driven shaft with wheels, constantly hooking 10. The gearbox according to claim 1, characterized in that the control is made in the form of a carriage rigidly attached to the slider and kinematically connected to the gear shift lever. 11. A gearbox under item 1, characterized in that the control is made in the form of a hollow shaft, concentrically mounted on the driven shaft and connected to the slider by means of a cylindrical thread made on the inner surface of the polo go shaft and the outer surface crawl

Description

on, and with the driven shaft - by means of a spring.

12. The gearbox of claim 1, wherein the control is a screw-nut gear mounted on the driven shaft, the stop is screwed on the screw, and the nut is spring-loaded to the stop and communicates with the slider or is rigidly fastened to it.

13. The gearbox according to claim 1. characterized in that it is provided with a rod fastened to the slider coaxially, at the point of attachment of which a trapezoid notch is made, the distance between the lateral sides of which along the bottom is equal to or less than doubled quantities.

14. Gearbox under item 1, characterized in that at the free end of the slider ramepheny rolling body.

15. The gearbox under item 1, characterized in that at the free end of the slider a spring is fixed, which interacts with the wedging bodies.

16. The gearbox of claim 2, characterized in that it is provided with inserts that are interleaved between the inner and outer casings.

17. The gearbox according to claim 4, characterized in that at the free end of the slider the plate is hinged at one end with the possibility of moving its second end in the radial direction of the shaft and interacting with the wedging bodies.

18. The gearbox according to claim 7, characterized in that the reverse gear is located between the housing and the forward gear, which has a greater gear ratio, the overrunning clutch integrated in the wheel, in a slider at a distance from the free end equal to The extreme overrunning clutches of the forward gears are made with a wedge-shaped groove interacting with the integrated clutch.

19. The gearbox of claim 7, wherein the reverse gear is located between the housing and the forward gear having a higher gear ratio, the clutch integrated into the wheel is normally open, in a slider at a distance from the free end equal to the distance between the extreme and overrunning clutches of the forward gears, a projection is made that interacts with the integrated clutch.

20. The gearbox according to claim 7, characterized in that the reverse gear is located between the housing and the forward gear having a lower gear ratio, the clutch integrated in the wheel is normally open, and the slide interacts with the free end of the wheel.

21. A gearbox according to claim 6, characterized in that the main overrunning clutches are installed in the wheels of the upshifts.

22. A gearbox according to claim 7, characterized in that the second reverse gear wheel is rotatably mounted on the drive shaft and secured to the adjacent forward gear wheel.

23. A gearbox according to claim 9, characterized in that identical sets of wheels are arranged on the driven shafts.

24. The gearbox of claim 23, wherein the reverse gear and one of the forward gears have the same gear ratios.

25. The gearbox of claim 12, wherein slots are made on the driven shaft, and a nut is mounted on them.

26. The gearbox of claim 12, characterized in that it is provided with a gear shift lever kinematically connected with the nut.

27. A gearbox according to claim 12, characterized in that it is provided with a gear lever that interacts with the end surface of the nut and has a locking latch.

28. The gearbox of claim 27, wherein the slider is mounted on the drive shaft and is kinematically connected with the gear lever.

29. The gearbox under item 12, characterized in that it is provided with a second stop mounted on the screw.

30. A gearbox according to claim 13, characterized in that the sides of the trapezoid groove have an equal length.

31. The gearbox according to claim 17, wherein the spring is fixed at one end on the slider and the other on the plate.

32. The gearbox according to claim 16, characterized in that conical projections are made on the outer surfaces of the wedge blocks, cylindrical projections on the outer surfaces of the liners, and circular wedge-shaped depressions in the outer surfaces of the outer cages, which includes cylindrical and conical protrusions.

33. The gearbox according to claim 16, characterized in that the liners are spring-loaded to the outer shells by springs.

34. The gearbox according to claim 16, characterized in that a protective layer of antifriction material with a thickness of 0.6-1.7 microns is applied on the inner surfaces of the outer collars and the outer surfaces of the wedge pads connected to them, and the inserts are made of the same material.

35. The gearbox according to claim 31, wherein the spring is located in a recess formed on the surface of the slide facing the shaft.

36. The gearbox according to claim 33, characterized in that recesses are provided on the wedge pads, which include springs.

The invention relates to mechanical engineering and can be used in gear shifting devices in machine tools and vehicles.

The aim of the invention is to increase box reliability when shifting gears without breaking the power flow by simplifying the box design and increasing smoothness of shifting.

FIG. 1 shows a gearbox, longitudinal section; in fig. 2 shows section A-A in FIG. one; in fig. 3 is a section BB in FIG. one; in fig. 4 - drive shaft, the cross section of the separator; in fig. 5-8 are embodiments of wedge blocks and liners; in fig. 9-11 - examples of installation of bearings on the free end of the slide; in fig. 12 - gearbox, second variant of the constructive scheme, longitudinal section; in fig. 13 is a section of an LF in FIG. 12 (reverse gear); in fig. 14 shows section 3-3 in FIG. 12; in fig. 15-24 show control of overrunning clutches in the gearbox of the second variant of the structural scheme (Fig. 12); in fig. 25 shows a gearbox, the third variant of the structural scheme, a longitudinal section; in fig. 26 is a sectional view OH in FIG. 25; in fig. 27 is a section section II in FIG. 25; in fig. 28 is a P-P section in FIG. 25; in fig. 29-35 - control of overrunning clutches B using the gearbox of the third variant of the structural scheme (Fig. 25); in fig. 36 - gearbox, fourth variant of the constructive scheme, longitudinal section; in fig. 37 is a section FF in FIG. 36; in fig. 38 is a section X-X in FIG. 36; in fig. 39 is a section of the C-C in FIG. 36; in fig. 40 - gearbox, fifth variant of the constructive scheme, longitudinal section; in fig. 41 is a cross-section of HH and Sh-Sh in FIG. 4.0; in fig. 42 is a sectional view of the UE and Yu-Yu in FIG. 40; in fig. 43 - gearbox the sixth variant of the constructive scheme 1, a longitudinal section.

In the first embodiment, the gearbox contains a housing 1 (Fig. 1-4), in which the driver 2 and the driven 3 shafts are parallel mounted on bearings, on which the cylindrical gears 4-5 are fixed; 6-7; 8-9 and 10-11; located on shafts in short order. The drive wheel 4 lower gear rigidly mounted on the shaft 2 and is in constant engagement with the driven wheel 5, equipped with a roller overrunning clutch 12, the inner race of which is rigidly mounted on the shaft 3. The driven wheels 7 and 9 are rigidly mounted on the shaft 3, and the driven wheel 11, integrally formed with the shaft 3, is in constant engagement with the driving wheels 6, 8 and 10 fixed on the shaft 2, which are equipped with controllable overrunning clutches containing between the inner race

with eccentric working surfaces made integral with shaft 2, and outer collars with cylindrical working surfaces made integral with wheels 6, 8 and 10, wedged bodies made in the form of wedge blocks 13-15 separated from eccentric working surfaces internal clips rollers. In this case, the fixed overrunning clutches form several uniformly circumferentially longitudinal rows of wedge blocks 13-15, which interact with the corresponding number of sliders 16, which are fixed with the possibility of movement along the shaft 2 between the inner and outer collars and

 conjugated by one side surfaces with longitudinal guiding protrusions 17 of shaft 2. The sliders 16 are fastened together with the carriage 18, which is movably mounted on shaft 2 and kinematically

0 connected to the gearshift lever 19, the longitudinal guides 17 of the shaft 2 and the sliders 16 associated with them being located in the recesses located on the inner surface of the carriage 18, with the housing of the carriage 18 entering into

5 transverse grooves made on the second side surfaces of the sliders. The second ends of the sliders 16 are made wedge-shaped, with flat inclined surfaces 20, serving for sequentially discharging controlled overrunning clutches, starting with the overrunning clutch acting on the top gear consisting of wheels 10-11, and the second side surfaces of the sliders 16 are designed to hold them in the off state. Moving the sliders 16 in the direction of engagement of the overrunning clutches

 A spring 21 fastened to the gear lever 19, made in the form of a pedal. For ease of operation, the slides 16 are held in the working positions by a lock (not

0 is shown) interacting with the gear shift lever 19. The controlled overrunning clutches alternate with separators 22 mounted on the shaft 2, forming, together with the shaft 2, guide holes 23 for the sliders 16 and restricting the movement of the wedge blocks 13-15 in the axial direction of the shaft 2.

The inclusion of all gears is provided by the spring 21, which moves the sliders 16 to the extreme left position.

0 d

In the second exemplary embodiment (not

shown) the gearshift pedal can be fixed on an elastic support, coupled with an engine shaft speed regulator, spring-loaded to it, in this case 5 with a lever for feeding fuel to an internal combustion engine.

In the third exemplary embodiment, (Fig. 5), the sliders 24, fixed with the possibility of movement along the shaft 25 between the inner and outer collars of the controlled overrunning clutches and interacting with the longitudinal rows of the wedge shoes 26, are separated from each outer cage made as one piece with a toothed wheel 27, liners 28, which are coupled with the front and rear parts of circumferential wedge shoes 26 and have stops 29 on the surfaces facing the shaft 25 for rollers 30 located between the wedge shoes 26 and eccentric Ricke surfaces of the inner ring, made in one piece with the shaft 25. In the front and rear parts of the wedge blocks 26, there are recesses oriented parallel to the axis of the shaft 25, in which the ends of the liner 28 and the leaf springs 31 are located, pressing the liners 28 to the working surface of the outer ring. and resting on the surface of the recesses. In addition, a protective layer 32 is applied to the inner surface of the outer ring, made as a unit with the gear wheel 27, and the outer surfaces of the wedge shoes 26, which have the effect of selective transfer under friction, for example a copper layer with a thickness of 0,6- 1.7 microns, and liners 28 are made of reducing the protective layer of the material. In the fourth example, the execution Dfig. 6), the sliders 33, fixedly movable along the shaft 34 between the inner and outer collars of the controlled overrunning clutches and interacting with the longitudinal rows of the wedge pads 35, are separated from each outer cage, made in one piece with the gear wheel 36, inserts 37, which are integral with the rear portions of circumferential wedge shoes 35 and mated with the front portions of the latter, while on the inner surface of the outer race, which is integral with the gear wheel 36, and the outer surfaces of the wedge pads 35 and liners 37 mated to it, a protective layer 38 is applied, which has the effect of selective transfer during friction, and in order to prevent the protective layer 38 from grinding off, the edges of the wedge pads 35 and liners 37, coupled to the outer surface of the outer ring, are rounded . In the fifth exemplary embodiment (Figs. 7 and 8), the slides 39 secured with the ability to move along the shaft 40 between the inner and outer collars of the controlled overrunning clutches and interacting with the longitudinal rows of pads 41 are separated from each outer cage made as one integral with gear wheel 42, inserts 43, which are made in one piece with the front parts of the wedge 41 located around the circumference and are matched with the rear parts of the latter, while on the inner surface of the outer cage, made as one piece with a gear wheel 42, there are annular wedge-shaped depressions with conical working surfaces, which include protrusions 44 and 45 corresponding thereto, made respectively on the outer surfaces of the wedge shoes 41 and inserts 43 .. In the sixth embodiment (not shown), the sliders are separated liners, which, together with lamellar springs, pressing them against the inner surface of the outer sleeve, are placed in the recesses located on the front and rear parts of circumferential wedges olodok, wherein the inner surface of the outer cage there are formed alternating conical and cylindrical surfaces of the annular wedge-shaped hollows, in which enter protrusions formed on outer surfaces of the wedge shoe and with cylindrical surfaces of the wedge-shaped annular depressions interact protrusions inserts. In the seventh embodiment, (Figs. 9 and 10), each slider 46 fixedly movable along shaft 47, with longitudinal guides 48, and cooperating with a longitudinal row of wedge blocks 49, has a cutout at its second end, in which Angular contact bearings 51 and 52 are mounted on the axle axis 50, the bearing 51 interacting with the longitudinal guide 48 of the shaft 47, and the bearing 52 with inclined concave surfaces of the longitudinal row of wedge blocks 49. In the eighth embodiment (see fig. 11), each the slider 53, which is fixedly movable along the shaft 54, with the longitudinal guide protrusions 55, and interacting with the longitudinal section of a number of wedge blocks 56, has a cutout at the second end in which bearings 58-60 are mounted on the common axis 57, In this case, the extreme bearings 58 and 60 cooperate with the longitudinal guide 55 of the shaft 54, and the middle bearing 59, whose width is equal to the total width of the outer bearings 58 and 60, interacts with the longitudinal row of the wedge blocks 56. In the second embodiment of the design scheme (FIG. 12-14) the gearbox contains a housing 61, in which the bearing 62 and the driven 63 shafts are installed in parallel on the bearings. On the shafts, gears 64-65 permanently engaged and forming the forward gear are reinforced; 66-67; 68-69; 70-71, located on shafts in increasing order. In addition, on shafts 62 and 63, with the edge, next to the top gears 70 and 71 of the forward gear, sprockets 72 and 73 are fixed, permanently connected by a chain 74 and forming a reverse gear. The driven wheels 65, 67, 69 and 71 and the knowledge of the asterisk 73 are rigidly fixed on the shaft 63, and the driving wheels 64, 66, 68 and 70 and the leading sprocket 72 are equipped with controllable ratchet overrunning clutches containing between the inner clips made as one piece with shaft 62, and outer rings, having the form of ratchet wheels, made in one piece with driving wheels 64, 66, 68 and 70 and leading sprocket 72, pawls 75-79, placed in round holes of inner sleeves and spring-loaded in the radial direction to the ratchet wheels. In this case, the ratchet couplings alternate with separators mounted on the shaft 62 and form a series of dogs 75-79 along the shaft 62 that interact with the slide 80, the casing of which is placed in the longitudinal guide groove 81 of the shaft 62 and fixed in the holes of the dogs 75-79 radially, the inner surfaces of the separators and serves to remove the paws 75-79 from contact with the ratchet wheels. At one end of the slider 80 on its outer surface there is a radially directed protrusion 82 placed in an annular recess made on the inner surface of the carriage 83, moving along the shaft 62 by a control element, for example a gear lever (not shown). The second end of the slider 80 is made in one piece with the rod 84, the body of which, placed in the longitudinal guide groove 81 of the shaft 62 and oriented parallel to the axis of the shaft 62, serves to remove the paws 75-77 from contact with the ratchet wheels, while between the slide 80 and a shaft 84 forms a non-equal trapezoidal recess 85 facing shaft 62, which ensures that when one gear is shifted forward, the one gear is continuously engaged, the slider 80 forming a long side surface.86 of the trapezoidal notch.85, and the rod 84 is short Its side surface is 87. In addition to. The inner surface of the slider 80 near its end, kinematically connected through the carriage 83 with the gear lever, has a wedge-shaped notch 88 that enables the wheels 72 and 73 to form the reverse gear, after the gear lever is turned off, all the forward gears.

In the third embodiment of the design, the scheme (Fig. 25-28), the gearbox includes a housing 89, in which a leading 90 and a driven 91 shaft are installed in parallel on the bearings. The cylindrical gears 92-93 are mounted on the shafts; 94-95; 96-97, forming transmissions arranged on shafts in increasing order. The low gear drive wheel 92 is integrally formed with the shaft 90 and is in constant engagement with the driven wheel 93 provided with an overrunning roller clutch 98, the inner race of which is rigidly fixed on the shaft 91. The drive wheels 94 and 96 rigidly fixed on the shaft 90, are permanently engaged with the driven wheels 95 and 97 mounted on the shaft 91, which are provided with controllable ratchet overrun clutches containing between the inner racers, made in one piece with the shaft 91, and the outer racers, having the appearance of ratchet wheels, integrally formed with driven wheels 95 and 97, pawls 99 and 100 mounted rotatably on axles fixed on inner yokes parallel to the axis of shaft 91, while the ratchet couplings alternate with separators 101 mounted on shaft 91 and form located along shaft 91 a series of dogs 99 and JOO, with the shafts of which interacts placed in the longitudinal guide groove 102 of the shaft 91 slider 103 through a plate 104 pivotally connected at one end with the end of the slider 103 and spring loaded in the direction of turning off the ratchet clutches in the recess 105. made on the surface of the slider 103 facing the shaft 91, a leaf spring 106 capable of holding the pawls 99 and 100 in the state deduced from contact with the ratchet wheels and deforming when the dogs 99 and 100 are engaged with the ratchet wheels sufficient full engagement gear formed by gears 94-95; 96-97. The load on the driven shaft 91 is transmitted through a spring 107, fixed at one end to the shaft 91, and the other to the hollow shaft 108, concentrically mounted on the driven shaft 91 and connected to the slider 103 by means of a cylindrical threaded connection with a multiple-stop thread with a large pitch made on the inner surface of the hollow shaft 108 and the outer surface of the body of the slide 103. The slide is held in operating positions by means of a ball retainer 109 installed in the spring of the body of the driven shaft 91 and spring odeystvuyuschego with holes 110 on the inner surface of the slider body 103, the latch 109 is valid only in the direction of turning off overrunning, preventing shutdown incomplete transmission.

In the example of the third variant (not shown), the weight and configuration of dogs introduced into contact with the ratchet

the wheels are centrifugal, and the plates pivotally connected at one end to the end of the slider and interacting with the shanks of the dogs are selected so that the centrifugal force acting on the plate is able to keep the dogs in the state brought out of contact with the ratchet wheels.

In the fourth embodiment of the design scheme (Fig. 36-39), the gearbox includes a housing 111, in which the master is mounted in parallel on the tongs

112 and driven 113 shafts, cylindrical gears 114-115 are mounted on shafts; 116-117; 118-1 19 forming transmissions arranged on shafts in increasing order. The lower gear drive 114 is integrally formed with the shaft 112 and is in constant engagement with the driven wheel 115 equipped with an uncontrollable free-wheel roller clutch 120, the inner race of which is rigidly fixed to the shaft 113. Driving wheels 116 and 118 rigidly fixed to the shaft 112, are in permanent engagement with the driven wheels 117 and 119 fixed on the shaft 113, which are equipped with controllable roller overrunning clutches containing between the inner cages with eccentric working surfaces with shaft 113, and outer collars with cylindrical working surfaces, made in one piece with gear wheels 117 and 119, placed in the slots of the powered forks 121, 122 rollers, while the powered forks 121, 122 alternate with 113 separators 123 mounted on the shaft and interact with several synchronously movable sliders 124 with wedge-shaped ends, fixed with the possibility along the shaft

113 between the inner and outer yokes and the mating one side surfaces with the longitudinal guiding protrusions of the shaft 113. In addition, the drive plugs 121 and 122 are spring-loaded in the direction of the seizure of the rollers by springs (not shown) placed in the recesses located on the side surfaces x separators 123. The load on the driven shaft 113 is transmitted through a coaxially arranged mechanism of the viit-nut type, the nut 125 of which is movable in the axial direction, which is fixed on the longitudinal guide protrusions of the shaft 113 moving and being pressed by the conical spring 126 to the end of the screw 127, is rigidly fastened to the sliders 124 by means of transverse grooves 128 formed on the outer surfaces of the sliders 124, into which the nut body 125 enters, while the sliders 124 are held in the working positions with a ball lock 129 installed in the housing of the nut 125 and interacting with the holes 130 on the driven shaft 113. Between the side

The surfaces of the screw grooves 131 nuts 125 and the screw protrusions 132 of the screw 127 in a closed contour around the screw protrusions 132 contain balls 133, the movement of which along the screw grooves 131 of the nuts 125 is limited to reflectors 134 fixed on the screw 127.

In one embodiment of the fourth embodiment (not shown), the gear pedal acting on the outer end surface of the nut may be provided, the pedal being brought out of contact with the end surface of the nut by a spring and provided with a locking latch allowing the pedal to be fixed in the position corresponding to the required transmission, and the locking latch acts only in the direction of engagement of the overrunning clutches.

In another embodiment, a fourth embodiment (not shown) may be

Q is provided with a gear lever kinematically associated with a nut.

In the fifth embodiment of the structural scheme (FIGS. 40-42), the gearbox includes a housing 135, in which a leading 136 and a driven 137 shaft are installed in parallel on the tongs, and the gears 138-139 are fixed on the shafts; 140-141; 142-143, sequentially engaging with each other and forming gears arranged on shafts in increasing order. The lower gear drive wheel 138 is made single-handed and equipped with an uncontrollable roller free-wheel clutch 144, the inner race of which is rigidly fixed on the shaft 136. Driving wheels 140 and 142 are made with two cords and equipped with controlled free-wheel clutches containing between the internal collars with eccentric working surfaces made as one piece with the shaft 136, and the outer collars with cylindrical work surfaces made

0 as one piece with wheels 140 and 142, wedge blocks 145 and 146, the longitudinal rows of which, evenly spaced around the circumference, interact with the corresponding number of sliders 147 fixed with the possibility of movement along the shaft 136 between the inner and outer yoke and mating side surfaces with longitudinal guides 148 of the shaft 136. The controlled overrunning clutches alternate with separators 149 mounted on the shaft 136,

 forming, together with the shaft 136, the guide holes for the sliders 147 and limiting the movement of the wedge blocks 145 and 146 in the axial direction of the shaft 136. The sliders 147 with just the ends

5 are fastened to a carriage 150 movably mounted on the shaft 136 and kinematically connected with a gear lever (not shown), and the second ends of the sliders 147 are tapered with concave

inclined surfaces that serve to sequentially turn off the controlled overrunning clutches, starting with the overrunning clutch acting on the top gear, and the second side surfaces of the sliders 147 are designed to keep them off. The follower wheel 143 of the lower gear is made single-pointed and equipped with an uncontrollable roller free-wheel clutch 151, the inner ring of which is rigidly fixed on the shaft 137. The home wheels 141 and 139 are double-sided and equipped with controlled free-wheel clutches containing between the internal holders with eccentric working surfaces. as one piece with the shaft 137, and outside windows with cylindrical working surfaces, made as one piece with the wheels 141 and 139, wedge pads 152 and 153, whose longitudinal rows are equal Externally circumferentially, they interact with the corresponding number of sliders 154, which are mounted with the possibility of movement along the shaft 137 between the inner and outer sleeves of the sleeves and mated by one side surfaces with the longitudinal guide lugs 155 of the shaft 137. The controlled overrunning clutches alternate with those mounted on the shaft 137 with separators 156, forming, together with valve 137, guide holes for sliders 154 and restricting the movement of the wedge blocks 152 and 153 in the axial direction of the shaft 137. The sliders 154 alone they are fastened to the carriage 157, movably mounted on the shaft 137 and kinematically connected with the gear lever (not shown), and the second ends of the sliders 154 are wedge-shaped with concave inclined surfaces that serve to successively turn off the controlled overrunning clutches, starting with the overrunning clutch acting on top gear. The second side surfaces of the sliders 154 are designed to keep them off.

In the generous design version (Fig. 43), the gearbox contains a housing 158, in which the leading 159 and the driven 160 shafts are installed in parallel on the spade plates, the gears 161-165 are fixed on the shafts, which interlock with each other and form transmissions. on the shafts in order of increasing. In addition, sprockets 166 and 167 are mounted on the shafts 159 and 160, which are permanently connected by a chain 168 and form a reverse gear, the leading sprocket 166 being freely mounted on the shaft 159 and made integral with the single-high Feed wheel 165 high gear . The drive wheel 161 of the lower gear is single-pointed and equipped with an uncontrollable roller free-wheel clutch 169, the inner race of which is rigidly fixed on the shaft 159. The two-wedding drive wheel 163 and the single-needle drive wheel 165, made as one piece with the asterisk 166, are equipped with controlled free-wheel clutches containing between the inner collars with eccentric work surfaces, made as one piece with the shaft 159, and the outer collars with cylindrical work surfaces, as one piece with the gear teeth and wheels 163 and 165, wedge blocks 170 and 171, whose longitudinal rows, evenly spaced around the circumference, interact with the corresponding number of sliders 172, fixed with the possibility of movement along the shaft 159 between the inner and outer collars and adjacent one side surfaces with longitudinal guiding protrusions 173 of shaft 159. Controlled overrunning clutches alternate with separators mounted on Ba, iy 159, which together with shaft 159 form guide holes for creeps 172 and limit movement of wedges x pads 170 and 171 in the axial direction of the shaft 159, with the wedge pads 170 and 171 springing in the wedging direction with springs located in recesses located on the side surfaces of the spring separators (not shown). The slides 172 are fastened together with the carriage 174, movably mounted on the shaft 159 and kinematically connected with the gear lever (not shown), and the second ends of the sliders 172 are wedge-shaped with concave inclined surfaces that serve to successively shut off controlled overrunning clutches, starting from the overrunning clutch acting on the highest front, che. The second side surfaces of the sliders 172 are designed to keep them off. The driven wheels 164 and 162 are double-crown and are equipped with controllable overrunning clutches containing mechanical gears with eccentric working surfaces made integral with the shaft 160, and external collars with cylindrical working surfaces made as one piece with the wheels 164 and 162, the wedge pads 175 and 176, the longitudinal rows of which, evenly spaced around the circumference, interact with the corresponding number of sliders 177 fixed to move along the shaft 160 between the inner and outer sleeves and mating with one side surfaces with longitudinal guide protrusions 178 of shaft 160. Controlled overrunning clutches alternate with separators mounted on shaft 160, forming, together with shaft 160, guide holes for sliders 177 and limiting the movement of wedge blocks 175 and 176 in the axial direction of the shaft 160, the wedge blocks 175 and 176 are spring-loaded in the wedging direction with springs (not shown) placed in the recesses located on the side surfaces of the separators 177 sliders alone ends are fastened to the sleeve 179, which has an annular protrusion 180 on the external surface, and move in the direction of engagement of the overrunning clutches under the action of a conical spring

181 mounted on the shaft 160 between the hub 179 and the ball bearing; and the second ends of the sliders 177 are wedge-shaped, with concave inclined surfaces serving to successively deactivate the controlled overrunning clutches, starting with the overrunning clutch acting on the high gear. The second side surfaces of the sliders 177 are designed to keep them off. Driving sprocket 167 reverse gear is freely mounted on the outer cylindrical surface of the separator 182, rigidly fixed on the shaft 160, and equipped with a multi-plate friction clutch that interacts with the end surfaces 183 of the wedge-shaped ends of the sliders 177, and one group of disks 184 of the friction clutch is connected by means of slits with an asterisk 167, and the second disk group 185 - with a separator

182. The load on the driven shaft 160 is transmitted through a screw-nut type mechanism coaxially disposed thereto, the axially movable nut 186 of which is fixed on the longitudinal guide lugs 178 of the shaft 160 with the possibility of axial movement and pressed by the conical spring 181 through the sleeve 179 to the screw end 187, is rigidly bolted with a washer 188, the movement of which in the direction of deactivation of the overrunning clutches is limited by the protrusion 189 of the screw 187. Between the side surfaces of the screw grooves 190 are nuts 186 and the screw projections 191 of the screw 187 along This contour around the screw protrusions 191 contains balls 192, the movement of which along the helical grooves 190 of the nut 186 is limited to reflectors 193, mounted on the screw 187. The end face of the nut 186 acts on the outer end surface of the sleeve 179 and provides automatic gear shifting of the forward stroke. In addition, a gear shift pedal (not shown) acting on the outer end surface of the annular protrusion 180 of the sleeve 179 is provided, by which the forward gear is switched and switched off and the reverse gear is engaged, the pedal is brought out of contact with the end surface of the annular the protrusion 180 of the sleeve 179 spring and provided with a locking

a latch that allows the pedal to be fixed in a position corresponding to the inclusion of the required gear, with the lock latch acting only in the direction of gear shifting.

In the seventh embodiment of the structural scheme, the gearbox contains the device shown in FIG. 43, whose driven shaft transmits power to one of the tracks of a crawler vehicle, such as a bulldozer, and to another caterpillar passes power flow from a second driven shaft, on which the same set of gear wheels and the same sprocket are mounted , with the axis of the driven shaft

5 lie in a plane parallel to the axis of the drive shaft, and both sprockets mounted on the driven va, lahs are equipped with the same multi-disk friction clutches and are connected by a single chain with an asterisk,

Q mounted on the drive shaft, and sets of gear wheels mounted on the driven shafts are equally hooked with the set of gear wheels mounted on the drive shaft and are equipped with the same overrunning clutches that interact with

5 identical groups of sliders, rigidly fastened with the same bushings, movably mounted on the driven shafts, and moved in the direction of the overrunning clutch engagement by the same conical springs. The outer end surfaces of the annular protrusions made on the outer surfaces of the bushings are affected by the same gear levers, and the outer end surface of the bush mounted on the first driven shaft is affected by the end face of the nut of the first screw-nut mechanism, and the nut is kinematically connected a pusher acting on the outer face of the sleeve mounted on the second driven shaft, and providing for automatic gear shifting to synchronize the movement of the crawl new on both driven shafts. In addition, the load on the second driven shaft is transmitted through a second screw-nut type mechanism, the axially movable nut of which is pressed by a spring against the stop located on the screw, controls a slide that interacts with the overrunning clutches of the driving gears, and gears with a nut of the first screw-nut type mechanism at high load moments than a nut of the second screw-nut type mechanism; the nut of the first screw-nut type mechanism is pressed by stronger springs to the screw end face than nut preload

5 of the second mechanism type screw-nut to the end of the screw.

Transmission in the first embodiment works as follows.

Due to the fact that the gear consisting of the wheels 10-11 provides the driven shaft 3 with the highest rotational speed, the wedge pads 15, which are pressed by centrifugal forces against the working surface of the outer race, are integrally formed with the gear wheel 10, are wedged by the drive shaft 2, and the driven shaft shaft 3 rotates at a speed determined by the gear ratio of the gears 10-11. At the same time, the roller overrunning clutch 12, receiving a greater number of revolutions than the gear wheel 5, overtakes the latter and releases it, and the wedge pads 13 and 14, at which the revolutions are higher than the shaft 2, overtake it and release the gears 6 and 8 from the shaft 2.

Pressing the gear pedal 19, kinematically connected with the carriage 18, movably mounted on the shaft 2 and fastened to the sliders 16, moves the latter along the shaft 2 and inserts the wedge-shaped ends of the sliders 16 into the gaps between. do the longitudinal guides 17 of the shaft 2 and the wedge blocks 15. Considering that the movement of the wedge blocks 15 along the shaft 2 is limited to separators 22, as the wedge-shaped ends of the sliders 16 are inserted into the gaps between the longitudinal guides 17 of the shaft 2 and the wedge blocks 15 the surfaces of the 20 wedge-shaped ends of the sliders 16 slide along the surfaces of the wedge blocks 15 and move the latter in a tangential direction against the eccentricity, making them forced wedging.

As the wedge blocks 15 move in a tangential direction against the eccentricity, i.e., as the wedge blocks 15 roll back on the eccentric working surfaces backward, the grip force between the gear wheel 10 and the wedge blocks 15 decreases and, starting from some point, turns out to be insufficient, in order to provide the driven shaft 3 with the rotational speed determined by the gear ratio of the gears 10-11, and the wedge pads 15 begin to slip relative to the gear wheel 10 at a speed increasing p can be proportional to the reduction in the adhesion force between the gear wheel 10 and the wedge pads 15, (at a constant load moment), at which the slipping speed of the wedge pads 15 relative to the gear wheel 10 will increase until the speed of rotation of the driven shaft 3 decreases to the speed determined by the gear ratio of gears 8–9, after which the wedge pads 14, pressed by centrifugal forces to the working surface of the outer cage, made in one piece with the gear wheel 8, are wedged leading into the scrap 2 and the driven shaft 3 rotate at a speed determined by the gear ratio of gears 8-9, after which the wedge-shaped ends of the sliders 16 are fully inserted into the gaps between the guide protrusions 17 of the shaft 2 and the wedge blocks 15, thereby ensuring full wedging of the wedge blocks 15 and keeping them in a wedged state by the second side surfaces of the sliders 16, while the gear wheel 10 is freed from the shaft 2 and the gear,

0 consisting of 10-11 wheels is turned off. Continuing to press the gearshift pedal 19, the wedge-shaped ends of the sliders 16 are inserted into the gaps between the longitudinal guides 17 of the shaft 2 and the wedge blocks 14, while the second side surfaces of the sliders 16 slide along the surfaces of the wedge blocks 15, continuing to hold them in the wedged condition, while the inclined surfaces of the 20 wedge-shaped ends of the sliders

Q 16 slides across the surfaces of the wedge blocks 14 and moves the latter in a tangential direction against the eccentricity, forcing them to wedge, during which the grip force between the gear wheel 8 and the wedge blocks 14 decreases and starting from some point is insufficient to provide the driven shaft 3, the rotational speed determined by the gear ratio of the gear wheels 8-9, and the wedge pads 14 begin to slip relative to the gear wheel 8 with increasing speed, The speed of rotation of the driven shaft 3 will not decrease to the speed determined by the gear ratio of gears 6-7, after which the wedge pads 13. centrifugally pressed against the working surface of the outer cage, made as one piece with the gear wheel 6, are wedged by the drive shaft 2, and the driven shaft 3 rotates at a speed determined by the transmission

a number of gears 6-7, after which the wedge-shaped ends of the sliders 1 are fully inserted into the gaps between the guiding protrusions 17 of the shaft 2 and the wedge blocks 14, thereby ensuring complete wedging of the wedge blocks 14 and holding them

5 in the propped state by the second side surfaces of the sliders 16, with this the gear wheel 8 is released from the shaft 2 and the gear 8-9 is turned off.

Subsequent pressing the pedal gearshift pedal 19 0 introduces the wedge-shaped ends of the sliders 16 into the gaps between the guide protrusions 17 of the shaft 2 and the wedge pads 13, forced the wedging of the latter, during which, starting at some point, the wedge pads 13 begin to slip relative to the gear 6 increasing speed until the speed of rotation of the driven shaft 3 decreases to

speed determined by the gear ratio of gears 4-5, after which the roller overrunning clutch 12 is wedged by the gear wheel 5, and the driven shaft 3 rotates at a speed determined by the gear ratio of gears 4-5, after which the wedge-shaped ends of the sliders 16 are fully into the gaps between the guiding protrusions 17 of the shaft 2 and the wedge pads 13, thereby ensuring complete wedging of the wedge pads 13 and keeping them in the wedging state by the second side surfaces of the sliders 16, while the gear wheel 6 is freed from Ala 2 and the gear consisting of gears 6-7 is turned off.

The gearshift pedal 19 lets the spring 21 pull the wedge-shaped ends of the sliders 16 out of the gaps between the longitudinal guides 17 of the shaft 2 and the wedge pads 13, during which the latter are pressed against the inclined surfaces of the 20 wedge-shaped ends of the sliders 16 by friction forces arising between the wedge pads 13 and the outer race, integrally formed with the gear wheel 6 (it is believed that the angle at the wedge-shaped ends of the sliders 16 is chosen such that the components of the wedge reactions the boats on the inclined surfaces of the 20 wedge-shaped ends of the sliders 16, in the direction of movement of the sliders 16, are equal to the friction forces acting on the sliders, caused by these reactions, i.e., such that the energy consumption for switching on any upward transmission is zero) on the rollers along the eccentric working surfaces in the direction of wedging, while the cohesive force between the gear wheel 6 and the wedge pads 13 increases in direct proportion to the movement of the latter in the direction of wedging and starting from some point appears sufficient to provide the driven shaft 3 with a higher rotational speed than the rotational speed determined by the gear ratio of the gears 4-5, with the result that the roller overrunning clutch 12, receiving a greater number of revolutions than the gear 5, overtakes the latter and frees it, and the driven shaft 3 continues to rotate at an ever-increasing speed, until the grip force between the gear wheel 6 and the wedge pads 13 is sufficient to provide the driven shaft 3 with a rotational speed determined by the transmission a number of gears 6-7, whereupon the wedge-shaped ends of the sliders 16 are completely withdrawn from the gaps between the longitudinal guides 17 of the shaft 2 and the wedge pads 13, thereby ensuring full engagement of the gear consisting of gears 6-7.

Continuing to release the gearshift pedal 19, allow the spring 21 to remove the wedge-shaped ends of the sliders 16 from the gaps between the longitudinal guides 17 of the shaft 2 and the wedge pads 14, during which the latter roll on the rollers along the eccentric working surfaces in the direction of wedging In this way, the adhesion force between the outer race, which is made in one piece with the gear wheel 8, and the wedge pads 14, increases in direct proportion to the movement of the wedge pads 14 in the wedging direction and ince some points will be sufficient to provide a driven shaft 3, a higher rotational speed than a rotational speed defined by the speed ratio gears 6-7, whereby the wedge block 13 to obtain a greater speed than the shaft 2, by overtaking

Q and the latter drive the gear 6 from the shaft 2, and the driven shaft 3 continues to rotate at an ever-increasing speed until the engagement force between the gear wheel 8 and the wedge pads 14 is sufficient to ensure the speed of rotation determined by the gear ratio of the gear shaft wheels 8-9, after which the wedge-shaped ends of the sliders 16 are completely withdrawn from the gaps between the longitudinal guides 17 of the shaft 2 and the wedge pads 14,

This ensures that gear is fully engaged, consisting of gear wheels 8-9.

Subsequent release of the gear pedal 19 allows the spring 21 to output the wedge-shaped ends.

5 slides 16 of the gaps between the longitudinal guiding protrusions 17 of the shaft 2 and the wedge pads 15, during which the latter are rolled on rollers along eccentric working surfaces in

The direction of seizure Q, in this case, the cohesive force between the outer race, which is made in one piece with the gear wheel 10, and the wedge pads 15 increases and, starting from a certain moment, is sufficient to ensure

5 to the driven shaft 3, a higher rotational speed than the rotational speed determined by the gear ratio of the gear wheels 8-9, resulting in the wedge pads 14, gaining more speed than the shaft 2, overtaking the latter and freeing the gear wheel 8 from the shaft 2 and the driven shaft 3 continues to rotate at an ever-increasing speed until the grip force between the gear wheel 10 and the wedge blocks 15 is sufficient to ensure the speed of rotation of the driven shaft 3 determined by the gear ratio of the gear wheels 10-11, after which the curvilinear ends of the sliders 16 are completely withdrawn from the gaps between the longitudinal guide protrusions 17 of the shaft 2 and the wedge pads 15, thereby ensuring full engagement of a gear consisting of gears 10-1 1. Considering that the adhesion force between the gears 6, 8 and 10 and the wedge blocks 13-15 vary in proportion to the amount of movement of the latter in the tangential direction, and the speed of movement of the wedge blocks 13-15 in the tangential direction is determined by the speed of movement of the sliders 16, then the smoothness of switching soap has to be determined by the speed of movement of the sliders 16 provided by the driver by acting on the pedal 19, the switching gear. If necessary, the driver has the opportunity to engage any downshift without using intermediate downshifts, for which, pressing the gearshift pedal 19, forcibly slips the overrunning clutch of the active gearing with the sliders 16 and every intermediate downshift is turned off by the pedal 19 before the rotation speed of the driven shaft 3 decreases to its corresponding speed, i.e., before the overrunning clutch operating on this gear is stuck, and when the rotation speed of the driven shaft 3 decreases up to the speed determined by the gear ratio of the gears of the required reduction gear, the overrunning clutch operating on this gear is wedged, and the driven shaft 3 rotates at the speed determined by the gear ratio of the gears of the desired reduction gear. Thus, in the latter case, when turning on any downshift, the driver expends energy on forcing the sliders 16 to only force the overrunning clutch of the current gear. In addition, the costs of energy for forced wedging by sliders of 16 overrunning clutches can be completely avoided due to the fact that before intersections or before turning the driver usually slows down and, in order to save fuel, reduces the revolutions of the engine shaft, while the speed of rotation of the engine shaft decreases faster than the speed of rotation of the driven shaft 3, as a result of which the overrunning clutch of the current gear is wedged, allows the driver to engage any downshift without wasting energy on forced wedging of sliders 16 overrunning clutches that simultaneously increases the lifetime of the device, ie. e. the driver has the possibility to include without any reduction gear in a forced wedging energy costs slides overrunning clutches 16, if the pre-reducing the shaft RPM of the engine. In the case of the second exemplary embodiment (the first version of the scheme), the box works as follows. By pushing the gear pedal, the wedge-shaped ends of the sliders are inserted into the gaps between the longitudinal guides of the shaft and the wedge blocks of the overrunning clutch of the current gear, while the pedal's elastic support is deformed in direct proportion to the force of the pedal and turning the associated fuel lever, reduces the amount of fuel entering the engine, which leads to a decrease in the number of revolutions of the engine shaft and, taking into account that the speed of rotation of the engine shaft decreases faster than the speed of rotation the driven shaft - to reduce the moment of load on the driven shaft, which, in turn, leads to disruption of the equilibrium of forces acting on the wedge blocks of the overrunning clutch of the current gear, resulting in wedge blocks as the moment of load on the driven shaft decreases on rolling bodies along eccentric working surfaces in the direction of wedging, while the cohesive force between the outer coupling half and the wedge shoes decreases and, starting from a certain moment, is insufficient to balance the reactions wedges on the wedge pads of the e-direction of their wedging, and elastically, the gear shift pedal under the action of the force of elastic deformation spreads and completely inserts the wedge-shaped ends of the sliders into the gaps between the longitudinal protrusions of the shaft and the wedge pads, wedging the latter and turning off the current gear at the same time, the elastic support allows the fuel supply lever, which is spring-loaded to it, to return to its original position and restore the amount of fuel supplied to the engine, The engine is restored to the number of revolutions of the engine shaft. Due to this constructive decision, the energy expended on forcibly wedging the overrunning clutch of the current gear by the sliders is significantly reduced due to a short-term and insignificant decrease in the number of revolutions of the engine shaft at the moment the overload clutch is turned off. In the third exemplary embodiment, the contact of the sliders 24 with the working surfaces of the outer clips is eliminated and the circumferential movement of the wedge-pads 26 located around the circumference is ensured when they are jammed after the next higher gear is turned off. This lamellar springs 31, on the one hand, provide a constant frictional contact of the wedge pads 26 with the working surface of the outer cage through the liners 28 associated with them,

which increases the reliability of the device, and on the other hand, wedge pads 26 in the wedged state wring out from the working surface of the outer cage, which reduces or completely stops the wear of the latter in the idle position. The presence of a protective layer 32 on the rubbing surfaces ensures a long service life of the device, since as a result of friction the atoms of the protective layer continuously migrate, the transition from one surface to another, and the base material remains intact.

In the fourth embodiment, the contact of the sliders 33 with the working surfaces of the outer clips is eliminated, and a high degree of synchronism of movement of the circumferential wedge shoes 35 is provided when they are jammed after the next overdrive is turned off, and the presence of the protective layer 38 ensures a long service life of the device.

In the fifth embodiment, the contact of the sliders 39 with the working surfaces of the outer clips is eliminated and a high degree of synchronism of movement of the circumferential wedge blocks 41 is ensured when they are wedged after the next high gear is turned off, and due to the inner surface of the outer cage and the outer surfaces of the wedge blocks 41 and 43 bladed liners, the wedge wedge 41 wedging angle 41 is increased, with the result that the load capacity of the device is particularly high. However, centrifugal forces acting on the inoperative wedge pads 41 and liners 43 cause increased friction losses.

In a brilliant example of implementation, the leaf springs are selected taking into account the increased wedge angle of the wedge shoes and serve to balance the centrifugal forces acting on the wedge shoes and transfer them to the liners, resulting in friction losses corresponding to friction losses at using wedge blocks with cylindrical work surfaces.

In the seventh embodiment, the axial loads, which occur when the overrunning clutches of active gears are turned off, and when any higher gear is engaged, the wedge block 49, acting on the sub-surface 52, pushes the slide 46 into the working position, thereby contributing to full gear shifting, and the fact that the inclined surface of the wedge block 49 is concave, the ejecting slider 46 has an approximately constant value when the overdrive is engaged.

According to the second variant of the structural scheme, the transmission operates as follows.

With the extreme right (Fig. 12) position of the slide 80, the inner surface of the latter, holding the dog 75-78 in you. carried out from the contact with the ratchet wheels, provides for the deceleration of the forward gears formed by gear wheels 64-65, 66-67; 68-69; 70-

0 71, and a wedge-shaped notch 88 formed on the inner surface of the slider 80, allowing the pawl 79 to move under the action of a spring in the radial direction. and to engage with a ratchet wheel, ensures the inclusion of a reverse gear, formed by gears 72-73.

To turn off the reverse gear move the slide 80 to the left, with the pawl 75-78, the slide on the inner horizontal surface of the slide 80, remain in the position pulled out of contact with the ratchet wheels, and the slide 79, the slip across the inclined surface of the wedge-shaped notch 88, is removed contact with the ratchet wheel, and the transfer of the rear

Turn 5 is turned off (Figs. 15 and 16).

To enable the lower gear of the forward stroke formed by the gear wheels 65 and 64, the slider 80 continues to move to the left, while the pawls 76-79, the slides along the inner surface of the slider 80, remain in the position pulled out of contact with the ratchets, and the pawl 75, the slides along the long side surface of the trapezoid groove 85, moves in the radial direction and engages with the ratchet wheel, providing low gear engagement (Figs. 17 and 18).

Slider 80 is moved to activate a forward gear drive formed by gears 66 and 67.

to the left to the gearshift step, folding from the step of engaging the overrunning clutches and the pawl to remove the pawls from contact- with the ratchet wheels. When the slider 80 is moved to the left by the engagement clutch of the overrunning clutches (Figs. 19-21), the dogs 77-79, the slides along the inner surface of the slider 80, remain in the position removed from the contact with the ratchets, and the dog 76, the slips, along the long side The trapezoid groove 85 moves radially and engages the ratchet wheel, enabling the gear consisting of wheels 66 and 67 to be engaged, while the pawl 75 slides along the horizontal surface of the trapezoid groove 85, remains spring pressed to the ratchet wheel. but, taking into account the fact that the ratchet wheel, made in one piece with the gear wheel 64, receives a greater number of revolutions than shaft 62, the dog 75 slides along

the teeth of the ratchet wheel so that it is not caught. When the slider 80 is moved to the left by the step of pulling the dogs out of contact with the ratchet wheels (Figs. 22 and 23), the paws 77-79, slides along the inner surface of the slider 80, remain in the position brought out of contact with the ratchets, and the dog 75, slips over a short the side surface of the trapezoid groove 85, is brought out of contact with the ratchet wheel, and the gears with the gear wheels 64 and 65 are turned off, and the dog 76, the slipper on the horizontal surface of the trapezoid groove, remains in engagement with the ratchet wheel, ensuring the front Chi with gears 66 and 67, while all other gears are off.

To successively activate upstream gears consisting of gear wheels 68-71, the slide 80 is moved to the left by two more gear shift steps (Fig. 24), while the dogs 77 and 78 successively engage with the ratchet wheels, providing sequential gears consisting of wheels 68-69 and 70-71, and the body of the rod 84 successively removes the sliding dog gears 76 and 77 that slide along the teeth of the last pawl 76 and 77 from contact with the ratchet wheels. 68-69.

For successive deactivation of forward gears consisting of gears 70-71; 68-69; 66-, 67; 64-65 and the reverse gear engagement consisting of the wheels 72, 73 moves the slider 80 to the extreme right position (see Figs. 12, 13, 14).

Thanks to this technical solution, in working positions of the slider, the dogs of all ratchet overrunning clutches, except for the overrunning clutch of the current gear, are removed from contact with the ratchet wheels, which reduces both friction losses and operation noise, and increases the service life of the device.

According to the third embodiment of the design scheme (in the first embodiment), the box operates as follows.

When transmitting a torque from the drive shaft 90 to the driven shaft 91, the spring 107 twists the stronger, the greater the load torque. As a result, the thread made on the inner surface of the hollow shaft 108 rotates relative to the thread made on the outer surface of the hollow shaft 103 fixed in the longitudinal guide groove 102 of the shaft 91 and moves the slider 103 along the shaft 91 in the direction of overrunning clutches until while the plate 104 slides over the rounded surface of the shank of the doggie 100 and rotates on

the hinge, thus deforming the plate spring 106, will not press its end to the base of the longitudinal guide groove 102 of the shaft 91, and the retainer 109 will not enter the hole 110 made on the inner surface of the slide 103 (Fig. 29).

A subsequent increase in load torque is balanced by the pawl 100 and latch 109 in engagement with the ratchet wheel and a latch 109 to a certain value sufficient to turn off the ratchet clutch 96-97 by the slider 103, after which the slider 103 leaves the latch 109 and quickly moves in with the plate 104, the end of which slides along the base of the groove 102 of the shaft 91, and the outer surface tilted to the axis of the shaft 91 - along the rounded surface of the shank of the pawl 100, the output of the last engagement with the storage turning off the gear consisting of wheels 96-97, as a result of which the plate spring 106 rotates the plate 104 on the hinge and presses it against the inner surface of the separator 101, and soon the rotation shaft of the driven shaft 91 decreases to a speed determined by the gear ratio gears 94-95, after which the pawl 99, pressed by centrifugal force to the ratchet wheel, engages with the latter and the driven shaft 91 rotates at a speed determined by the gear ratio of the gears 94-95 (Fig. 30 and 31).

With a subsequent increase in load torque in the same way, the gear consisting of gear wheels 94-95 is turned off and the roller is wedged.

the overrunning clutch 98 of the transmission wheels 92-93, after which the driven shaft 91 rotates at a speed determined by the gear ratio of the gears 92-93.

As the load torque decreases, the spring 107 spins up the more, the lower the load torque. As a result, the thread made on the inner surface of the hollow shaft 108 rotates relative to the thread made on the outer surface of the slider 103 in the opposite direction and moves the slider 103 in the direction of engaging the ratchet sleeves, while the plate 104 is pressed by the plate spring 106 to the inner surface of the separator 101 and to the rounded surface of the shank of the doggie 100, slides over them,

 holding the dog 100 in a state brought out of contact with the ratchet wheel until the end of the plate 104, sliding along the rounded surface of the shank from the tank 100 from the middle to the narrowing edge, will allow the dog 100 to come into contact with the ratchet wheel ( Fig. 32 and 33), then, taking into account that the teeth of the ratchet wheel have an engagement angle with the pawl

100 is greater than the friction angle, the doggie 100 slides along the working surface of the ratchet wheel tooth and rotates on the axis, engages fully with the ratchet wheel, pivots the plate 104 and deforms the spring plate 106 (Fig. 34 and 35).

Thanks to this technical solution, an automatic gear shift is provided depending on the moment of load on the driven shaft, and also the incomplete inclusion of the overdrive is eliminated, i.e. the impact load is largely relieved by the spring transferring the load torque to the driven shaft. In addition, the placement of the leaf spring in the recess, made on the surface of the slide facing the shaft, eliminates, in the case of the breakage of the leaf spring, the danger of debris entering the mechanism.

According to the second embodiment of the third embodiment of the structural scheme, the need for a leaf spring used in the first embodiment is eliminated.

According to the fourth variant of the structural scheme (the first exemplary embodiment), the transmission operates as follows.

When transmitting a torque from the drive shaft 112 to the driven shaft 113, the screw lugs 132 of the screw 127 pass the torque 133 to the lateral surfaces of the screw grooves 131 of the nut 125 through the balls 133, while the torque of the load in the axial direction is balanced by a conical spring 126 and a lock 129 (disregarding the friction forces between the longitudinal guides of the shaft 113 and the nut 125) until the load torque increases to a certain value sufficient to turn off the overrunning clutch 124 gearing consisting of gears, after which the screw 127, turning relative to the nut 125 and compressing the conical spring 126, removes the nut 125 from the clamp 129 and quickly moves it in the direction of the overrunning clutches together with the sliders and 124, the sloping surfaces of the wedge-shaped ends of which , slide along the inclined surfaces of the drive fork K i 122, turn the latter along with the rollers placed in its nests in the direction of the rollers wedging and turn off the gear from the wheels 118-119, while the latch 129 enters the next hole 130 on the va 113 and the rotational speed of the driven shaft 113 decreases to a speed determined by the gear ratio of the gears 116-117, as a result of which the overrunning clutch operating on this gear is wedged by the gear 117

and the driven shaft 113 rotates at a speed determined by the gear ratio of the gears 116-117.

With a subsequent increase in load torque in the same way, the transmission of gear wheels 116-117 is shut off and the roller overrunning clutch 120 of the gear wheels 114-115 jams, causing the driven shaft 113 to rotate at a speed determined by the gear ratio of gears 114-115 .

The system returns to its original position by reducing the torque of the load.

In the second exemplary embodiment of the fourth embodiment of the structural scheme, the device can be controlled both automatically and by means of a gear pedal, moreover, the actuation of the locking latch, the pedal is used simultaneously as a speed limiter.

In the third exemplary embodiment, the control of the device can be carried out both automatically and by means of a gear lever, with the actual gear being determined by the position of the gear lever.

In the fifth embodiment of the design for switching on the lower gear, the sliders 147 are moved to the extreme right (Fig. 40) position, and the sliders 154 are moved to the extreme left position, while the sliders 147 successively wedge the top-V-blocks and the wedge-blocks 145 for the intermediate gear, freeing the wheels 142 and 140 from the drive shaft 136, and the sliders 154 successively wedge the wedge blocks 153 of the highest gear and the wedge blocks 152 of the intermediate gear, releasing the wheels 139 and 141 from the driven shaft 137, and the roller clutch 144 leading to timber 138 wedged lower transmission shaft 146 and a roller 151 of the overrunning clutch driven wheel 143 wedged low gear.

To switch on the higher gear, the slide blocks 154 move two steps of the gear shift to the right, and the slide blocks 147 move two steps of the gear shift to the left, while as the sliders 154 move to the right, the wedge blocks 152 of the intermediate gear and the wedge blocks 153 of the high gear sequentially wedge the wheels 141 and 139 increasing the rotational speed of the driven shaft 137, and as the sliders 147 move to the left, the intermediate-drive wedge blocks 145 and the high-gear wedge blocks 146 are successively wedged by the drive shaft 136, multiplying the speed of rotation of a set of gears 138-143 sequentially engaged with each other, and hence the speed of rotation of the driven shaft 137, taking into account that the sliders 147 and 154 have three working positions, the diameters of the wheels 138143 are chosen in such a way that the device provides nine gears with gear ratios increasing exponentially.

Thanks to this technical solution, gear ratios of gears are used in direct and reverse ratios, which is especially useful when designing devices with a large number of gears.

In the sixth variant of the structural scheme, when moving the sliders 172 to the extreme right (FIG. 43), wedge pads 171 of the highest gear and intermediate wedge pads 170 are successively wedged, releasing the wheels 165 and 163 from its shaft 159, and the roller overrunning clutch 169 lugs , its lower gear wheels 161 are wedged by the drive shaft 159, ensuring successive engagement with one another of the gear wheels 161-165 and the sprockets 166 and 167 permanently associated with them the lowest rotational speed.

When transmitting torque from the drive shaft 159 to the driven shaft 160, the screw lugs 191 of the screw 187 transfer the torque of the load to the side surfaces of the screw grooves 190 of the nut 186 through the balls 192, while the torque of the load in the axial direction is balanced by a conical spring 181 to a certain values, above which the screw 187, turning relative to the nut 186 and moving it together with the sleeve 179 and the sliders 177 rigidly fastened with it in the direction of the overrunning clutches, compresses the conical spring 1-81 the stronger Longer torque of the load, until the inclined surfaces of the wedge-shaped ends of the sliders 177 wedge t wedge blocks 176 of the highest forward gear and the wheel 162 is released from the driven shaft 160, and the washer 188 is rigidly fixed to the nut 186, resists the annular protrusion 189 of the screw 187; at the same time, the lower vane wedges 75 are wedged by the wheel 164, and the driven shaft 160 rotates at the slowest speed (with the rightmost position of the sliders 172).

To turn off all forward gears, the gearshift pedal moves the slide blocks 177 to the gearshift shaft in the same direction and wedges the forward low gear wedge pads 175, releasing the wheel 164 from the driven shaft 160.

To engage the lower reverse gear, the sliders 177 continue to be moved in the same direction by the gearshift pedal, while the end surfaces of the 183 wedge-shaped ends of the sliders 177,

Pressing the outermost disk 185, move the group of disks 185, connected by means of slots to the separator 182, along the latter and press the disks of this group to the disks 184 of the second group, connected by means of the slots with an asterisk 167, to drive the multi-plate friction clutch into action.

To successively turn on the middle and higher reverse gears, the slider 172 interferes with two steps to shift the gears to the left.

The device provides six gears

forward travel and three reverse gears,

and when shifting gears straight

the course and when shifting gears of the backward course of the power flow is not interrupted.

According to the seventh variant of constructive

The gearbox circuit works as follows

in a way.

The gears of a caterpillar vehicle are shifted both by moving the sliders that interact with the overrunning clutches of gear wheels mounted on the drive shaft, as well as synchronously moving the sliders that interact with the overrunning clutches of the gears mounted on both driven shafts and turning the tracked vehicle carried out by moving the sliders interacting with the overrunning clutches of gear wheels mounted on one of the driven shafts relative to the sliders, interactions gears with overrunning clutches mounted on a different driven shaft, taking into account that overrunning clutches with wedge pads allow smooth gear shifting, turning the tracked vehicle can be done along any radius. When a tracked vehicle encounters an obstacle, i.e., as the load torque increases, a screw-nut type mechanism mounted on the second driven shaft, as the load torque increases, sequentially turns off the overrunning clutches of gear wheels mounted on the drive shaft. the shaft, as a result of which the uncontrollable roller, the overrunning clutch of the low-end gear wheel is wedged by the drive shaft, which ensures constant engagement of the gear wheels and sprockets; eni

If the load torque continues to increase, a screw-nut type mechanism mounted on the first driven shaft turns off the forward gear on both of the driven shafts, and the tracked vehicle moves to the downstream gear. As the obstacle is overcome, the loading torque decreases, and the system, returning to the initial position, increases the speed of loading.

27

the movement of the tracked vehicle is corresponding to a decrease in the load torque.

To engage the reverse gear, simultaneously press the gearshift lever all the way down and drive it into

28

action multidisk friction clutches of the driven reversing sprockets. Thanks to this technical solution, the maneuverability and maneuverability of tracked vehicles, and, consequently, their performance, are significantly improved.

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Claims (36)

1. A GEARBOX, comprising a housing, drive and driven shafts with pairs of constantly engaged gears mounted on them, forming forward gears located on the shafts in increasing gear ratio, a gear shift mechanism including a control member, wheels mounted on one of the shafts having overrunning clutches with internal and external cages and jammed bodies, characterized in that, in order to increase the reliability of the gearbox when shifting gears without interrupting the flow of power STI, gear selection is made as a cantilever disposed in the control slider body cooperating with one side of the wedging bodies and extending between the inner and outer race overrunning clutches. 2. Gearbox according to π. 1, characterized in that, in order to increase the smoothness of gear changes, overrunning clutches are made of friction, and their jammed bodies are in the form of wedge blocks. 3. Gearbox according to π. 1, characterized in that it is provided with an additional overrunning clutch arranged in a gear wheel mounted on another shaft with a lower gear ratio. 4. Gearbox according to π. 1, characterized in that the overrunning clutch is made ratchet, their wedged bodies - in the form of dogs. 5. Transmission according to π. 1, characterized in that it is equipped with interacting with the slider leash forks having grooves for the slider and placed between the inner and outer clips. • 6. Gearbox according to π. 1, characterized in that one of the extreme pairs of gears is made single-shaft, and the other wheels are double-walled and sequentially engaged with each other, the wheels mounted on the other shaft also have overrunning clutches interacting with an additional slider. 7. Transmission according to paragraphs. 1 and 6, characterized in that it is equipped with a reverse gear formed by a pair of gears mounted on shafts and permanently connected by a chain, one of the wheels mounted on a shaft with a slider has a clutch built into it. 8. The gearbox according to claim 7, characterized in that it is equipped with a brake mounted on the driven shaft and interacting with the slider, and overrunning clutches and the slider are also mounted on the driven shaft. 9. The gearbox according to paragraphs. 1 and 7, characterized in that it is equipped with a second driven shaft with wheels constantly clinging to the wheels of the drive shaft, forming an additional forward gear. 10. Transmission according to π. 1, characterized in that the control element is made in the form of a carriage rigidly fastened with a slider and kinematically connected with a gear lever connected to the housing by a spring. 1 1. Transmission according to π. 1, characterized in that the control element is made in the form of a hollow shaft concentrically mounted on the driven shaft and connected to the slider by means of a cylindrical thread made on the inner surface of the hollow shaft and the outer surface:; the slider is sliding, and with the driven shaft by means of a spring . 12. Gearbox on π. 1, characterized in that the control element is a screw-nut transmission mounted on a driven shaft, a stop is made on the screw, and the nut is spring-loaded to the stop and interacts with the slider or is rigidly fixed to it. 13. Gearbox on π. 1. characterized in that it is equipped with a shaft fixed to the slider coaxially with it, at the attachment point of which a trapezoidal recess is made, the distance between the sides of which along the bottom is equal to the distance between adjacent overrunning clutches or less than twice its size. 14. Gearbox on π. 1, characterized in that at the free end of the slider are placed rolling bodies. 15. Transmission according to π. 1, characterized in that at the free end of the slider is fixed spring, interacting with jammed bodies. 16. The gearbox according to claim 2, characterized in that it is provided with liners placed between the inner and outer clips. 17. The gearbox according to claim 4, characterized in that on the free end of the slider is pivotally fixed at one end of the plate with the possibility of moving its second end in the radial direction of the shaft and interacting with jammed bodies. 18. The gearbox according to claim 7, characterized in that the reverse gear is located between the housing and the forward gear, having a greater gear ratio, an overrunning clutch integrated in the wheel, in a slider at a distance from the free end equal to the distance between the extreme overrunning clutches forward stroke, a wedge-shaped recess is made, interacting with the built-in coupling. 19. The gearbox according to claim 7, characterized in that the reverse gear is located between the housing and the forward gear having a higher gear ratio, the clutch integrated in the wheel is normally open, in the slider at a distance from the free end equal to the distance between the extreme and overrunning clutches of forward gears, a protrusion is made, interacting with the built-in clutch. 20. The gearbox according to claim 7, characterized in that the reverse gear is located between the housing and the forward gear having a lower gear ratio, the clutch built into the wheel is normally open, and the slider interacts with it with a free end. 21. The gearbox according to p. 6, characterized in that the main overrunning clutch is installed in the wheels of overdrive. 22. The gearbox according to claim 7, characterized in that the second reverse gear wheel is mounted rotatably on the drive shaft and fastened to an adjacent forward gear wheel. 23. Gearbox pop. 9, characterized in that the same sets of wheels are placed on the driven shafts. 24. The gearbox of claim 23, wherein the reverse gear and one of the forward gears have the same gear ratios. 25. The gearbox according to claim 12, characterized in that the slots are made on the driven shaft, and the nut is mounted on them. 26. The gearbox according to p. 12, characterized in that it is equipped with a gear lever kinematically connected with a nut. 27. The gearbox according to p. 12, characterized in that it is equipped with a gear lever interacting with the end surface of the nut and having a locking latch. 28. The gearbox according to p. 27, characterized in that the slider is mounted on the drive shaft and kinematically connected with the gear lever. 29. The gearbox according to claim 12, characterized in that it is equipped with a second stop mounted on the screw. 30. The gearbox of claim 13, wherein the sides of the trapezoidal recess are of equal length. 31. The gearbox according to claim 17, characterized in that the spring is fixed at one end to the slider and the other to the plate. 32. The gearbox according to claim 16, characterized in that the conical protrusions are made on the outer surfaces of the wedge blocks, cylindrical protrusions are made on the outer surfaces of the liners, and annular wedge-shaped in the longitudinal planes of the depression, which include cylindrical and conical, are made on the outer surfaces of the liners protrusions. 33. The gearbox according to claim 16, characterized in that the liners are spring-loaded to the outer clips. 34. The gearbox according to claim 16, characterized in that on the inner surfaces of the outer casing and the outer surfaces of the wedge blocks mating with them, a protective layer of antifriction material is applied, 0.6-1.7 μm thick, and the liners are made of the same material. 35. The gearbox according to p. 31, characterized in that the spring is placed in a recess made on the surface of the slider facing the shaft. 36. The gearbox according to p. 33, characterized in that the wedge blocks are made indentations in which the springs are placed.