Self-adjusting toothed planetary variator

FIELD: mechanical engineering, automobile construction, in particular, rotational speed changing technique.

SUBSTANCE: variator has speed regulating mechanism made in the form of toothed differential mechanism, drive for speed regulation mechanism, planetary working frame 4 and planetary balancing frame 5, frame guide 11 and frame rotation casing 12. Frames 4, 5 are meshed with central toothed gear 3 and are placed, in conjunction with said gear, within frame guide 11. Two planetary working toothed gears 6, 10 are fixed within frame 4. Planetary working toothed gear 6 is fixed through cardan drive 8 and shaft 9 to variator housing 7 to rotate relative to frame 4. Planetary toothed gear 10 is connected through second cardan drive 8, intermediate toothed gears 21, 22 and toothed gear 23 to variator driven shaft 24 to run around first planetary working toothed gear 6. On increase of rotational speed or adjustment, frames 4, 5 are offset by centrifugal force relative to rotational center of drive shaft 1. On offsetting of frames, radii of rotation of planetary working gears 6, 10 relative to rotational center of drive shaft 1 are increased and transmission ratio is changed.

EFFECT: increased efficiency and provision for transmission of great powers by toothed transmission.

12 dwg

 

The invention relates to mechanical engineering, the automotive industry, namely, devices for changing the speed, in particular for a continuously variable planetary gear variable speed, and can be used in arrangements where you want to change the speed of the driven shaft within the specified range.

Of analogues of the prior art friction speed changers, made by coaxially to the scheme and containing a drive shaft with two installed sliding in the axial direction of the conical wheels in contact with two conical satellites that are in contact with each other and having a convex outer ground contact, respectively, with a concave working surface of the two outer wheels, sliding in the axial direction and connected with the mechanism of speed regulation, and a casing in which are mounted driving and driven shafts.

The drawback of such a variable is that in such variators axis satellites rotate around the axis of the variator that increasing the transmitted power density by increasing the number of revolutions of the drive shaft leads to the emergence of large centrifugal forces adversely affecting the operation of the variator.

Of analogues of the prior art closest to the invention, the set of essential characteristics - the prototype of the m can be adopted friction variable speed", comprising a housing, a driven shaft, driving shaft, two bevel gears, one of which has a drive shaft, at least one spring in contact with the conical satellites, and at least one Central gear wheel, while the CVT is equipped with element mounted on the control shaft for axial movement relative to its mechanism of speed regulation, made in the form of the differential gear mechanism, two toothed wheels which have the same number of teeth, one of which is rigidly connected with the Central toothed wheel variator, and provided with a drive mechanism speed control (See description of the invention No. 494549, additional to the author's testimony on the application 09.09.70 (21) 1473321/25-28 from 09.09.1970, (51) M CL. F16h 15/50 Published 05.12.75. Bulletin No. 45. Date published descriptions 20.02.76 (72). The author of the invention Psilonerou. (71) Applicant").

In the invention, taken as a prototype, addressed above in the similar disadvantages.

To increase the transmitted power density of the proposed variator provided with a bushing installed on the drive shaft for axial movement relative to it, on the sleeve freely mounted conical wheels, one of which is provided with a stop screw surface variable step, entries batch is provide with thorn, mounted on the sleeve, the axis of the satellites are connected to the housing of the CVT, and one of the Central wheels with a concave working surface rigidly mounted on the output shaft, the other connected with him through the mechanism of speed regulation.

In addition, the mechanism of speed regulation is made in the form of the differential gear mechanism, two Central wheel with the same number of teeth are connected respectively with the Central wheel variator, one rigidly connected with the wheel mounted on the drive shaft, the other by means of screw connections and timing satellites mounted on a common axis in a freely rotating drive rod interacts with the other two Central wheels of the differential mechanism, having the same number of teeth, one of which is rigidly mounted in the housing of the variator and the other kinematically connected to the drive mechanism speed control.

This design by increasing the number of revolutions of the drive shaft allows you to increase the transmitted power density of the variable.

The disadvantage of the invention, taken as a prototype, compared to the claimed invention is a lower efficiency compared to the claimed design "Variator self-regulating planetary gear" and it is not possible to keep eruditione attitude in self-regulation mode gear ratio from "0" to "50" and return ratio to "0" at the termination of the rotation of the drive shaft.

The technical result is increased efficiency and the ability to transfer large capacity gear. Gear ratio is changed from "0" to the required level, as well as the opportunity to hold the gear ratio in the mode of self-regulation ratio from "0" to "50" and return ratio to "0" at the termination of the rotation of the drive shaft.

The technical result is achieved by the fact that, compared with the invention adopted for the prototype, known friction variable speed includes a housing, a driven shaft, driving shaft, two bevel gears, one of which has a drive shaft, at least one spring in contact with the conical satellites, and at least one Central gear wheel, while the CVT is equipped with element mounted on the control shaft for axial movement relative to its mechanism of speed regulation, made in the form of the differential gear mechanism, two toothed wheels which have the same number teeth, one of which is rigidly connected with the Central toothed wheel variator, and provided with a drive mechanism speed control, in the invention, the variator self-regulating planetary gear is equipped with a planetary framework, including the working and balancing framework, upravlaushiy framework and the case of rotation of the framework, moreover, the working and balancing framework are in engagement with the said Central toothed wheel and with him are located inside the guide frame mounted in the housing part, with the above-mentioned mechanism of speed regulation is made in the form of the differential gear mechanism containing the two above-mentioned bevel gears, one of which is installed on the control shaft, and the second is mounted on the body frame and in contact with the said satellites, and the second bevel gear is made interoperable through the mentioned satellites with the first bevel gear wheel when the angular displacement of the body part relative to the drive shaft, the variator is fitted with two planetary work gears mounted on bearings in the above-mentioned planetary working frame, and one planetary work gear through the drive gear and the axle attached to the chassis of the variator and executed with a possibility of rotation relative to that of the planetary working framework, while remaining not having an angular offset relative to the axis, and the second planetary gear through the second PTO transmission combined with planetary intermediate gear interacts with the intermediate gear to ECOM, having with him the same number of teeth mounted on an axis fixed in the body of the variator, and through interacting with the gear connected with the driven shaft of the variator, and the second planetary working gear designed to obregonia, by rotation around the first mentioned planetary working gears, no angular displacement about an axis, on which is fixed, while the above-mentioned drive mechanism speed control contains the mentioned Central gear wheel and the said element mounted on the control shaft for axial movement relative to it, is made in the form of a gear rack of the follower interacting with the mentioned satellites and it also contains pushers mounted on the housing pushers located between the housing pushers and the body of the variator and through the hole in the body of the variator interacting with said rack gear pusher, which are made with the possibility of axial movement with him on the drive shaft and on the housing pushers secured mentioned spring located between the housing pushers and the body of the variator, which is arranged to hold the gear ratio in the mode of self-regulation ratio is t "0" to "50" and return ratio to "0" at the termination of the rotation of the driving shaft, these planetary working and balancing frame provided with stoppers located on both sides on the ends of the frame, is arranged to limit the stroke of the part, when you return them to the "0" gear ratio, and mentioned planetary working gears, and the planetary working, balancing, frame, body rotation part and a toothed rack pusher, made with the possibility of rotation relative to the drive shaft and adjustment of gear ratio.

"Variator self-regulating planetary gear" is illustrated by drawings which depict:

Figure 1 - the progressive self-regulating planetary gear, a side view in section.

Figure 2 - variable self-regulating planetary gear (section a-a in figure 1).

Figure 3 - part of a cardan transmission.

4 is a cross-section y-Y figure 3.

5 is a drive mechanism speed adjustment (section B-B in figure 1).

6 - adjustment mechanism speed, made in the form of differential adjustment mechanism (section B-b In figure 1).

Fig.7 - working frame, front view.

Fig - working frame, top view.

Fig.9 - balancing frame, front view.

Figure 10 - the balancing frame, top view.

11 is a diagram explaining the operation of the planetary working gears in the planetary body of the working frame, when zero is eruditionem.

Fig diagram explaining the operation of the planetary working gears in the housing of the working frame and swing frame, the motion of the planetary framework.

The essence of the invention.

Variable self-regulating planetary gear includes a drive shaft 1 (Fig 1, 2, 5, 6) and mounted on a drive shaft 1 (Fig 1, 2, 5, 6) bevel gear 2 (1, 6) of the differential mechanism is rigidly secured on the Central toothed wheel 3 (Fig 1, 2, 11, 12). Variable self-regulating planetary gear contains a working frame 4 (1, 2, 7, 8, 11, 12) and balancing the frame 5 (Fig 1, 2, 9, 10, 12). The variator is fitted with two planetary work gears mounted on bearings in the planetary working frame 4 (1, 2, 7, 8, 11, 12). Planetary working gear wheel 6 (Fig 1, 2, 11, 12) is made rotatable relative to the working framework 4 (1, 2, 7, 8, 11, 12) and no angular displacement relative to the body of the variator 7 (1, 2). Planetary working gear wheel 6 (Fig 1, 2, 11, 12) through the drive transmission 8 (Fig.1-3) and the axis 9 (Fig 1) is fixed to the housing of the variator 7 (figs 1, 2) and is executed with a possibility of rotation relative to the planetary working framework 4 (1, 2, 7, 8, 11, 12), while this does not have an angular offset relative to the axis 9 (Fig 1). The second planetary gear 10 (Fig 1, 11, 12) is arranged to obregonia by rotation, around the first mentioned planetary work toothed wheel 6 (Fig 1, 2, 11, 12), no angular displacement about the axis 9 (Fig 1), on which are fixed through the drive transmission 8. Variable self-regulating planetary gear is equipped with a planetary framework, including working frame 4 (1, 2, 7, 8, 11, 12), balancing 5 (1, 2, 9, 10, 12), the guide frame 11 (Fig 1, 2) and the case of the rotation frame 12 (Fig 1, 2). Working frame 4 (1, 2, 7, 8, 11, 12) and balancing frame 5 (Fig 1, 2, 9, 10, 12) are in engagement with the Central gear wheel 3 (Fig 1, 2, 11, 12) together with located inside of the guide frame 11 (Fig 1, 2)mounted in the housing of the rotation frame 12 (Fig 1, 2). The mechanism of regulation of the speed variator is made in the form of the differential gear mechanism, which includes the two above-mentioned bevel gear. One bevel gear 2 (1, 6) are mounted on the drive shaft 1 (figure 1, 6), and the second bevel gear wheel 13 (Fig 1, 2) is rigidly fixed to the body of rotation of the frame 12 (Fig 1, 2) and comes into contact with satellites 14 (1, 2, 6). The second bevel gear wheel 13 (Fig 1, 2) made interoperable through the mentioned satellites 14 (1, 2, 6) with the first bevel gear wheel 2 (1, 6) during the rotation of the housing part 12 (Fig 1, 2). The drive mechanism speed control contains the mentioned C is Tralee gear wheel 3 (Fig 1, 2, 11, 12) and the element mounted on the control shaft 1 (Fig 1, 2, 5, 6) with the possibility of axial movement relative to it, is made in the form of a gear rack pusher 15 (1, 5, 6)having thrust bearings 16 (Fig 1, 5)communicating with satellites 14 (1, 2, 6), and also contains the pushers 17 (Fig 1, 5)mounted on the housing pushers 18 (1) and located between the housing pushers 18 (figure 1) and the body of the variator 7 (1, 2), which through the hole in the body of the variator 7 (1, 2) interact with a rack and pinion gear pusher 15 (1, 5, 6). The pushers 17 (Fig 1, 5) is made with the possibility of axial movement with toothed rack pusher 15 (1, 5, 6) relative to the drive shaft 1 (Fig 1, 2, 5, 6). In the case of pushers 18 (figure 1) is fixed to the spring 19 (Fig 1)located between the housing pushers 18 (figure 1) and the body of the variator 7 (1, 2). Spring 19 (Fig 1) serve to hold the gear ratio in the mode of self-regulation ratio from "0" to "50" and return ratio to "0" at the termination of rotation of the drive shaft 1 (Fig 1, 2, 5, 6). Variable self-regulating planetary gear also contains restrictors return frames to "0" of the transmission 20 (figure 1), located on both sides on the ends of the working frame 4 (1, 2, 7, 8, 11, 12) and balancing of the frame 5 (Fig 1, 2, 9, 10, 12), made with limited opportunity which I stroke this framework, upon their return to "0" gear ratio. The second planetary gear 10 (Fig 1, 2, 11, 12) of the variator through the second PTO transmission 8 (1-4), United with her intermediate planetary gear 21 (Fig 1) communicates with the intermediate gear wheel 22 (1), having with him the same number of teeth mounted on the axis 9 (Fig 1), fixed in the housing of the variator 7 (Fig.1-3), and then through interacting with the toothed wheel 23 (Fig 1) is connected with the driven shaft 24 (1) of the variator. Variable self-regulating planetary gear contains a splined connection 25 (Fig 1, 5). Gear rack and pinion pusher 15 is supplied with fixing straps 26 (1, 2, 6). Planetary work toothed wheel 6 (Fig 1, 2, 11, 12) and 10 (1, 11, 12), and the planetary working frame 4 (1, 2, 7, 8, 11, 12) and balancing frame 5 (Fig 1, 2, 9, 10, 12), the case of rotation of the frame 12 (Fig 1, 2) and a gear rack pusher 15 (1, 5, 6), made with the possibility of rotation relative to the drive shaft 1 (Fig 1, 2, 5, 6) and adjustment of gear ratio.

Variable self-regulating planetary gear operates as follows.

Torque transmitted to the driving shaft 1 through the transfer of the Central gear 3 and gear bevel wheels 2 of the differential mechanism transmits torque through the differential of the economic mechanism on the body of the rotation frame 12 and to the frame work 4 and balancing 5. In the initial position or ratio of "0" planetary working gears 6 and 10 rotate relative to the center of the driving shaft 1 and the center gear is aligned with the center of the driving shaft 1. For increased speed, or when adjusting frame 4, 5 due to the centrifugal forces are shifted relative to the center of the driving shaft 1, thus there is angular movement of the housing part 12 relative the drive shaft 1. When the offset part of the increase in the radii of rotation of the planetary wheels 6, 10 relative to the center of rotation of the driving shaft 1 and changing the gear ratio. Planetary working gear wheel 6 cardan transmission 8 by the shaft 9 is fixed to the housing of the variator 7 and has no angular displacement about the axis 9. Planetary working gear wheel 10 spatial obbegat (revolves) around the planetary working gears 6. While the resulting torque through the second PTO transmission 8, the intermediate planetary gear 21 fixed bearings 16 in the case of the rotation frame 12, an intermediate gear wheel 22, with intermediate planetary gear 21 the same number of teeth, mounted on the axle 9, fixed in the housing of the variator 7, and through a gear wheel 23 will be transmitted to the driven shaft 24 of the variator. The angular displacement of the body of rotation Rameau is 12 relative to the drive shaft 1, i.e. ratio is governed by the differential mechanism by means of a toothed rack of the pusher 15, pushers 17, the spring 19. For longitudinal movement along the drive shaft 1 gear rack of the plunger 15, the slots 25 together with the plungers 17, corps pushers 18 through satellites 14 is the angular displacement of the housing of the rotation frame 12 relative the drive shaft 1. The spring 19 serves to hold the gear ratio at a certain speed mode samoregulivni and return ratio to "0" at the termination of rotation of the driving shaft 1. When forced adjustment of gear ratio of the spring 19 is not necessary. Strap retainer 26 serve for fixing the gear rack and pinion adjustment mechanism and satellites 14. Planetary working gears 6, 10, and referred to the working frame 4, the balancing frame 5, the housing of the rotation frame 12 and the toothed rack of the plunger 15, is executed with a possibility of rotation relative to the drive shaft 1 and the adjustment of gear ratio.

Variable self-regulating planetary gear, comprising a housing, a driven shaft, driving shaft, two bevel gears, one of which has a drive shaft, at least one spring in contact with the conical satellites, and at least one Central the e gear, when this variable is supplied element mounted on the control shaft for axial movement relative to its mechanism of speed regulation, made in the form of the differential gear mechanism, two toothed wheels which have the same number of teeth, one of which is rigidly connected with the Central toothed wheel variator, and provided with a drive mechanism speed control, wherein the variator is equipped with a planetary framework, including the working and balancing of the frame, the guide frame and the housing of the rotation part, and a working and balancing framework are in engagement with the said Central toothed wheel and with him are located inside the guide frame mounted in the case of the framework, with the above-mentioned mechanism of speed regulation, made in the form of the differential gear mechanism includes the two above-mentioned bevel gears, one of which is installed on the control shaft, and the second is mounted on the body frame and in contact with the said satellites, and the second bevel gear is made interoperable through the mentioned satellites with the first bevel gear wheel when the angular displacement of the body part relative to the drive shaft, the variator is fitted with two planetary R is working gears, mounted on bearings in the above-mentioned planetary working frame, and one planetary work gear through the drive gear and the axle attached to the chassis of the variator and executed with a possibility of rotation relative to that of the planetary working framework, while remaining not having an angular offset relative to the axis, and the second planetary gear through the second PTO transmission combined with planetary intermediate gear interacts with the intermediate gear wheel, having with him the same number of teeth mounted on an axis fixed in the body of the variator, and through interacting with the gear connected with the driven shaft of the variator, and the second planetary working gear wheel is arranged to cover by rotating around the first mentioned planetary working gears, no angular displacement about an axis, on which is fixed, while the above-mentioned drive mechanism speed control contains the mentioned Central gear wheel and the said element mounted on the control shaft for axial movement relative to it, is made in the form of a gear rack of the follower interacting with the mentioned satellites, and also contains pushers, with antiromance on the body pushers, located between the housing pushers and the body of the variator and through the hole in the body of the variator interacting with said rack gear pusher, which are made with the possibility of axial movement with him on the drive shaft and on the housing pushers secured mentioned spring located between the housing pushers and the body of the variator, which is arranged to hold the gear ratio in the mode of self-regulation ratio from "0" to "50" and return ratio to "0" at the termination of the rotation of the drive shaft, these planetary working and balancing frame provided with stoppers located on both sides on the ends of the framework made with the possibility of travel limit framework, when returning them to the "0" gear ratio, and mentioned planetary working gears, and the planetary working, balancing, frame, body rotation part and a toothed rack plunger is made with a possibility of rotation relative to the drive shaft and adjustment of gear ratio.



 

Same patents:

FIELD: mechanical engineering.

SUBSTANCE: proposed system of transmission with constantly changing gear ratio has input and output shafts, 16 and 24, respectively, transfer unit V with constantly changing gear ratio connected to input shaft 16, mixed epicyclical transfer mechanism E1 and second epicyclical transfer mechanism E2. Mechanism E1 has input sun gear S1 connected to output shaft of variable speed drive 18, carrier C1 connected to input shaft 16 and planetary gear P1 installed on carrier C1. Planetary gear P1 drives first intermediate output shaft 32 selectively connected to output shaft 24 of system through first clutch H at high speed of system. Planetary gear P1 provides also input power for second epicyclical transfer mechanism E2. Mechanism E2 has output C2 which is selectively connected to output shaft 24 of system through brake member L at low speeds of system.

EFFECT: minimization of engagement of gears, thus minimizing transmission losses, no backlash in mechanism E1, increased range of selection of sizes of gears, thus reducing speed of gears.

2 cl, 2 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in tractors, automobiles, road building machines, etc. Additional simple three-member planetary mechanism is installed in gearbox between off-axial two-shaft reduction gear and main three-member planetary mechanism. Gear rims 27, 28, 29 of tubular shaft 26 of epicyclic wheel 25 and output shaft of carrier 24 of main three-member planetary mechanism and output shaft 6 of set 1 are arranged close to each other. Shifter sleeve 35D is located on gear rim 29 of set output shaft 6. Shifter fork 36 is connected by slider 37 with gear rim 38 with internal and external gearing. Gear rim 38 connects gear rims 32, 30 of set housing and housing of epicyclic wheel 25.

EFFECT: increased range of gear ratios and number to forward speeds to sixteen and reverse speed to eight, contributes to transformation of high torques.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet friction variator comprises shaft (1), solar wheel (2), corona wheel (6), carrier (4) with satellites (3), and secondary shaft (5). Corona wheel (6) that is used as a control member is connected with variator housing (11) and primary shaft (1) through friction mechanisms. Secondary shaft (5) is made in block with carrier (4) for permitting control of velocity and direction of rotation of the corona wheel by means of friction mechanisms and control electric motor (9) connected with the corona wheel.

EFFECT: simplified structure, reduced sizes, and enhanced reliability.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: continuously variable transmission comprises housing, input and output shafts, reverse mechanism and multi-disk planet variator provided with planet reduction gear, which define a variator. The solar pinion of the reduction gear is fit on the output shaft with interference and its epicycle is secured to the housing of the transmission. The variator has epicycle mounted in the housing of the transmission and made of a stack of disks and solar pinion made of a disk stack mounted on the output shaft of the variator connected with the output shaft of the reverse mechanism. The carrier of the variator is connected with the carrier of the planet reduction gear and consists of two disks interconnected by means of tension bolts. The disks of the carrier have shaped slots the number of which is equal to the number of axles mounted in the shaped slots for permitting change of position and interaction with the disks of the solar pinion and epicycle. The gear ration controller is build in the carrier of the variator. The planet reduction gear, planet multi-disk variator, and reverse mechanism are axially aligned.

EFFECT: prolonged service life and expanded functional capabilities.

18 cl, 8 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: according to invention, gear 14 is secured on primary shaft 3, and gear 13 is secured on first tubular shaft 9 freely fitted on primary shaft 3. Gear rims 21 and 22 are fitted on shafts 3 and 9. Input shaft 2 with hub of three-position shifter sleeve 23 and additional driving shaft 4 are installed coaxially to shaft 3. Two gears 17 and 18 in meshing with gears 19 and 20 of secondary shaft 5 are secured on shaft 4. Gear 19 is fitted on shaft 5. Gear 20 is secured on second tubular shaft 10 freely installed on shaft 5. Gear rims 24 and 25 are secured on shafts 5 and 10. Shaft 6 with hub of two-position shifter sleeve 26 and sun gear 27 of planetary mechanism is installed coaxially to shaft 5. Gear 27 engages through planet pinions 31 with epicyclic wheel 32. Planet pinions 31 are freely fitted on axles of carrier 33. Two gear rims 34 and 35 are arranged on periphery of housing of carrier 33. Shaft 7 of carrier 33 with two position gear rim is arranged coaxially to shaft 5 and shaft 6. Third tubular shaft 11 of housing of epicyclic wheel with gear rim 38 is freely fitted on shaft 7. Output shaft 8 with hub of three-position shifter sleeve 40 is arranged coaxially to shaft 7. Sleeve 40 is movably coupled by guide 41 with two-rim shifter sleeve 42 arranged between gear rim 37 of housing 36 of epicyclic wheel 32 and gear rim 43 of gearbox case provided with two inner gear rims and one outer gear rim.

EFFECT: perfected design owing to reduction of metal usage and complexity.

2 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: in proposed coaxial shaft-and-planetary transmission gear 10 on primary shaft 2 is secured and is in meshing with gear 7 provided with rim of increased width and freely fitted on intermediate shaft 6. Gear 11 of secondary shaft 3 has also rim of increased width near gear rim of gear 10 of primary shaft 2. shifter sleeve member 24 fitted on said gear rims is coupled with other sleeve member 25 by shifter fork 26, sleeve member 25 being installed on gear rims of gears 7 and 8 of intermediate shaft 6. Gear rim 19 of output shaft of carrier 15 is two-position one. Gear rim 20 of output shaft of set 5 is three-position one, and shifter sleeve 28 on said rim is provided with three internal gear rims. Gear rim 31 with internal and external meshing is teeth rigidly secured on slider 30 of shifter sleeve 28, external meshing teeth being coupled with three-position gear rim 23 of housing of set 1.

EFFECT: increased range of gear ratios of shaft reduction gear at reduced overall dimensions and metal usage, improved gear shift mechanism of planetary mechanism.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: mechanical amplifier comprises power differential (1), comparing differential (30), adjusting differential (2), control differential (36), and two self-braking mechanisms (3) and (4). The input of the power differential (1) is connected with the drive and input of control differential (2). Central wheels (17) and (18) of the power differential are secured to driven links (15) and (16) of the self-braking mechanisms and connected with central wheels (32) and (33) of the comparing differential so that the central wheels of the comparing differential rotate in opposite directions. Driving links (13) and (14) of the self-braking mechanisms are connected with central wheels (19) and (20) of the adjusting differential and central wheels (42) and (43) of the control differential so that the central wheels of the control differential rotate in opposite directions.

EFFECT: enhanced reliability and expanded functional capabilities.

1 dwg

Drive (versions) // 2278309

FIELD: mechanical engineering; devices for control of rotational speed of working member shaft.

SUBSTANCE: proposed drive has unadjustable electric motor, adjustable electric motors, input shaft 1 and output shaft 2, gear trains, differential gear trains formed by two wave gear trains with common wave generator 3 and worm transmissions and differential gear. Worm shafts 11 and 12 are set in rotation from adjustable electric motors. External gear wheels 6 and 7 of wave gear trains are coupled with worms 11 and 12. Internal gear wheels 9 and 10 of wave gear trains are kinematically linked with differential gear wheels 19 and 20 which are connected with output shaft 21 of drive. Two wave gear trains are chain-type in construction and are related as follows: Zch1+Zch2=2Zext; Zch1+Z=Zch2-Z, where Zch1 and Zch2 is number of rollers in chains of first and second wave gear trains; Zext is number of teeth of external gear wheel of wave gear drives thrown into engagement with rollers of chains; 2Z is difference of rollers in chains.

EFFECT: possibility of changing the direction of rotation and rotational speed of shaft of working member in wide range; increased speed of response; enhanced reliability.

5 cl, 3 dwg

FIELD: agricultural engineering; offroad tractor.

SUBSTANCE: invention relates to driving axle with suspension and agricultural tractor with such axle which has central housing with build-in final drives and left-hand and right-hand axle housings suspended by means of upper and lower adjusting arms, with axle-shafts projecting from axle on which wheel-and-tire units are installed. Constant-velocity universal joint is installed between fitted-in final drives and axle-shafts. Said universal joint has pair of journal members and coupling holder radially enclosing driving and driven races of joint, thus minimizing axial length of universal joint providing arrangement of wheels on axle-shafts at width of 1524 mm.

EFFECT: possibility of using driving shaft on tractor-cultivator without changing design of load-bearing frame of standard tractor-cultivator with preservation of performance characteristics of said tractor-cultivator.

39 cl, 15 dwg

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.

1 dwg

The invention relates to machine building, machine-tool construction, the design of automatic converters torque and gear ratios

FIELD: mechanical engineering.

SUBSTANCE: continuously variable transmission comprises housing, input and output shafts, reverse mechanism and multi-disk planet variator provided with planet reduction gear, which define a variator. The solar pinion of the reduction gear is fit on the output shaft with interference and its epicycle is secured to the housing of the transmission. The variator has epicycle mounted in the housing of the transmission and made of a stack of disks and solar pinion made of a disk stack mounted on the output shaft of the variator connected with the output shaft of the reverse mechanism. The carrier of the variator is connected with the carrier of the planet reduction gear and consists of two disks interconnected by means of tension bolts. The disks of the carrier have shaped slots the number of which is equal to the number of axles mounted in the shaped slots for permitting change of position and interaction with the disks of the solar pinion and epicycle. The gear ration controller is build in the carrier of the variator. The planet reduction gear, planet multi-disk variator, and reverse mechanism are axially aligned.

EFFECT: prolonged service life and expanded functional capabilities.

18 cl, 8 dwg

FIELD: mechanical engineering, particularly continuous transmissions used as wide-range transmission mechanism.

SUBSTANCE: device for power transmission with variable velocity ratio comprises input 21 and output 27 members, leading draft member 7 and disc member 1 rotationally installed in case. Input member 21 transmits rotational moment of at least one leading draft member 7. Disc member 1 is coaxial to rotary shaft 2 brought into drive connection with at least one leading draft member 7 and is formed as driven member. Disc member 1 may be selectively moved in axial direction along rotary shaft 2 to change position of disc member 1 relative at least one leading draft member 7 to selectively change draft velocity ratio between leading draft member 7 and disc member 1. Output member 27 is displaced by rotary shaft 2 and is selectively brought into engagement with it to transmit rotational moment under determined velocity ratio relative input member 21.

EFFECT: extended velocity range.

27 cl, 4 dwg

Transformer torque // 2188973

The invention relates to the field of engineering

The invention relates to the field of engineering

The invention relates to the field of mechanical engineering

Transformer moment // 2160400
The invention relates to the field of engineering

The invention relates to mechanical engineering and can be used in particular for a continuously variable transmission of a vehicle

The invention relates to mechanical engineering and can be used particularly in motor-variators

Transformer torque // 2115848
The invention relates to mechanical engineering, in particular to the transfer mechanisms
Up!