Continuously-variable transmission

FIELD: mechanical engineering and machine-tool building.

SUBSTANCE: invention can be used in vehicles and machine tools, different machines and mechanisms. Proposed continuously-variable transmission contains drive and output shafts and case accommodating drive and drive and driven constant-mesh gears, differential with coaxial gears mechanically engaging through planet pinions and provided with coaxial axle-shafts, and gear ratio changer including axial-plunger pump with inclined plate with rotary working member, pressure line and suction line connected with reservoir filled with working liquid. Adjustable bypass restrictor is installed in pressure line of pump. Output of restrictor is connected with said reservoir by drain line. Rotary working member of pump is made in form of block of working cylinders accommodating plungers, each being mechanically coupled with inclined plate. Differential is arranged inside working cylinder block of axial-plunger pump with coaxial arrangement of drive and driven gears and said block, and it has at least one pair of planet pinions installed for rotation in cylinder block of axial-plunger pump. Constant-mesh drive gear is connected with drive shaft, and constant-mesh driven gear is connected with drive gear of differential. Invention is aimed at enlarging functional capabilities of transmission owing to provision of limitation of speed of rotation and braking of output shaft, interruption of torque on shaft and control of delivery of pump included into gear ratio changer of transmission and increase of service life and provision of uniform rotation of output shaft and increase of efficiency of transmission.

EFFECT: enlarged operating capabilities, increased efficiency of transmission.

22 cl, 4 dwg

 

The invention relates to machine building and machine-tool construction, and more particularly to a continuously variable gear boxes, and can be used in vehicles and machines, as well as in various machines and mechanisms.

Known continuously variable transmission, containing mounted in the housing coaxially leading and output shafts, connecting their mechanism of regulation of frequency of rotation and torque on the output shaft, a reversing mechanism, a clutch and control system (see ed. St. USSR №1369928, CL 60 To 17/04).

A disadvantage of the known transmission is the complexity of the design, manufacture and management, as well as low life and reliability due to the increased mechanical wear of the parts of the mechanism of frictional engagement. In addition, in the aforementioned gearbox there is no possibility of automatic control of the speed of rotation of the output shaft depending on the magnitude of torque on it that reduces the functionality of the gearbox. However, the efficiency of the specified transmission is reduced due to the cost of power for maintaining the pressure in the cylinder.

The closest technical solution, selected as a prototype, is a continuously variable transmission, containing lead and an output shaft and a housing, which contains ve is painful and driven gears are constant mesh, the differential with coaxial gears, kinematically linked to each other through satellites, and provided with aligned axes, mechanism for switching the direction of rotation of the output shaft and the mechanism of regulation of gear ratio transmission, comprising a pump with a rotating tool, a pressure line and a suction line connected to a tank filled with working fluid, and installed in the inlet line of the pump is adjustable bypass throttle, the output of which is connected to a drain line with the mentioned capacity, while rotating the body of the pump is kinematically associated with the differential and ring gear constant mesh kinematically connected with the output shaft (see patent RU No. 2188351, CL F 16 H 47/04, priority from, 25.09.2000, publ. 27.08.2002,).

Known transmission contains two differential mechanism, two gear pumps and a large number of gears, which leads to the design complexity, the greater the intensity and large size specified transmission. Another disadvantage of the known transmission is the absence of a mechanism for restricting the rotation speed and the Parking brake output shaft, mechanism interrupts the torque on the specified shaft and mechanism for regulating the volumetric feed gear pumps, which limits the t functionality gearbox. However, for gear pumps are characterized by a large pressure pulsations in their output, which can cause surges transmitted to the gears and shafts of the whole gearbox, which reduces the resources of the latter and causes uneven rotation of the output shaft. In addition, for gear pumps typical large reverse leakage on the gear teeth, resulting in slippage (scrolling) of the output shaft and the loss of efficiency of the transmission. The big difference of the diameters of the pairs of gears 2 and 3, 17 and 18 causes more load on the teeth of these gears, which reduces their resource.

Technical problem whose solution is the invention is the simplification of the structure and reducing the metal gearbox, providing the possibility of limiting the rotation speed and the Parking brake output shaft, interruption of torque on the output shaft and regulating the volumetric flow of the pump, which is included in the regulatory mechanism gear ratio transmission, as well as reducing pressure pulsations and reverse leakage at the output of the specified pump and reduction of the difference of the diameters of the gears of the transmission.

The technical result obtained in the practical use of the present invention is to simplify the manufacture and repair and weight loss, the envelope is in and the cost of transmission by simplifying the design and reducing the metal, the increased functionality of the transmission by providing the possibility of restricting the rotation speed and the Parking brake output shaft, interruption of torque at last and regulation of the volumetric flow of the pump, which is included in the regulatory mechanism gear ratio transmission, as well as increased resource transmission and providing uniform rotation of its output shaft by reducing the pressure pulsation at the output of the specified pump, increase the efficiency of transmission by reducing the reverse leakage at the outlet of the pump and increase the service life of gears in the gearbox by reducing the load on their teeth by reducing the difference of the diameters of these gears.

To solve the technical problem in the proposed continuously variable transmission containing lead and an output shaft and a casing, which houses the leading and driven gear constant-mesh gears, differential with coaxial gears, kinematically linked to each other through satellites and provided with aligned axes, and mechanism for regulating gear ratio transmission, comprising a pump with a rotating tool, a pressure line and a suction line connected to a tank filled with working fluid, and installed in the inlet line of the pump is reguliruemyi bypass the throttle, the output of which is connected to a drain line with the mentioned capacity, while rotating the body of the pump is kinematically associated with the differential and ring gear constant mesh kinematically connected with the output shaft, unlike the prototype, the pump mechanism of regulation of the gear ratio of the gearbox is made of axial-piston with an inclined washer, valve and rotating the working body, made in the form of block working cylinders placed in them by the plungers, each of which is kinematically connected with the inclined washer, differential placed inside a block of working cylinders in an axial piston pump with axial location of its leading and driven gears and said block, and has at least one pair of satellites, mounted for rotation in the block working cylinders in an axial piston pump, the leading constant mesh gear connected with the drive shaft and driven gear constant mesh connected with a pinion differential. The axial piston pump can be equipped with a rotating disc resting on the inclined washer and the valve specified pump can be made a face and set with constant mesh gears, while the plungers axial piston pump fixed the but connected with the said rotating disc. The leading constant mesh gear fixed on the drive shaft, driven gear constant-mesh gears mounted on shafts pinion differential, and in the inlet or discharge line is retaining the throttle.

The bypass orifice may be in the form of a slide valve with a circular groove is placed in the sleeve, in which the input and output side Windows and gable window, and supplied with control line, indicating the end window of the sleeve valve with the inlet line axial piston pump, with the sleeve installed compression spring which presses the valve toward the open end of the sleeve with the message input and output Windows of the past through the annular groove of the valve when the pressure in the control line.

The transmission may be provided with a mechanism for switching the direction of rotation of the output shaft and the mechanism for restricting the rotation speed and the Parking brake output shaft, while included in the transmission mechanisms provided with a control valve.

The end of the drive shaft, which is the case fitted with a support fixed to the mechanical valve axial piston pump, and a mechanism for switching the direction of rotation of the output shaft includes a control cylinder mounted on the outer torontotoronto mechanical valve coaxial with the drive shaft and is provided inside the piston with an axial hole for passage of the drive shaft, the piston cavity, located between the piston and end valve axial piston pump, and the control line that tells the piston cavity through the control valve to the drain line or the inlet line axial piston pump, a friction disk splined on its axial hole, mounted coaxially on the drive shaft for axial movement and interaction with the piston of the control cylinder and being in engagement with each other driving and driven gears, the first of which is installed on the control shaft between the pinion constant-mesh gears and a friction disc with the opportunity to interact with the latest and the free turning relative to the drive shaft, and the second fixed block working cylinders in an axial piston pump, with the friction disc provided with a spring, clamped it to the piston of the control cylinder, leading to the mentioned gear mechanism from the side of the friction disk internal axial groove flange, which has a spring friction disc, resting with one hand in the collar of the mentioned grooves, and the end face of the friction disk, the area of the drive shaft located in the area of the axial movement of the friction disk made with protruding splines with what zmoznostjo their coupling with the slots of the friction disk when the last interaction with the pinion mechanisms, and spring friction disc made with the possibility of releasing the latter from the end of the pinion mentioned mechanism when connecting the piston cavity of the steering hydraulic cylinder with a drain line and with the possibility of coupling end face of the friction disk with the end of the pinion mentioned mechanism when connecting the piston cavity of the steering cylinder with the intake line of an axial piston pump. When this support is included in the housing end of the drive shaft can be placed inside the control cylinder of the mechanism for switching the direction of rotation of the output shaft between the piston cavity of the specified cylinder and end valve axial piston pump.

The end of the axis driven gear of the differential is made with a groove, the ends of the axes of the leading and the trailing differential gears and the ends of the output shaft is installed in the fixed to the body support, and a mechanism for restricting the rotation speed and the Parking brake output shaft accommodated in the housing, kinematically connects the axle driven gear differential with an output shaft, providing their aligned position, and includes a gear pump with leading and driven gears, the first of which is fixed on the output shaft between its bearings in the casing, a suction line connected to the tank for alsenoy working fluid, and with the inlet line, with two taps, one of which soobschaetsa through the bypass valve with the internal cavity of the housing, communicating with the drain line, and the second overlaps the controlling valve or connects the past with the drain line, and a clutch installed between the axial-piston and gear pumps coaxially with the axis driven gear of the differential and output shaft and provided with axial bore, one end of which has a worm movable connection with the end of the axis driven gear of the differential, and the second spline is movably accommodated in the housing by the end of the output shaft, with the second outlet of the intake line gear pump installed retaining the throttle referred bypass valve is installed parallel to the axis of the output shaft and provided with an axial shaft, a spring mounted on the specified axial rod, and accommodated in the housing between the clutch and gear pump managing lever, which has one end pivotally connected to the housing, the middle portion interacts with said clutch and is made with an opening for free passage through it of the driving shaft and the other end is made with a hole, in which freely enters the end of the axial rod by-pass valve spring by-pass valve is settled between the gate of the latest and managing lever, axis driven gear of the differential gear set thrust washer with an emphasis in the flange groove of the specified axis, the clutch is made with the outer groove side of the thrust disc and provided with a spring installed on the specified coupling with stop one end of the thrust disk and the second in the shoulder grooves mentioned clutch.

The control valve mechanisms gearbox made four position and is connected to the inlet line axial piston pump, a pressure line gear pumps, drain line, the control line of the control cylinder mechanism for switching the direction of rotation of the output shaft and the control line bypass throttle while in neutral transmission position precluding rotation of the output shaft, a control valve occupies the position in which it communicates with the drain line inlet line axial piston pump, a pressure line gear pumps, control line bypass throttle and the control line mentioned cylinder, transmission position corresponding to the working rotation of the output shaft, managing the valve occupies the position in which he informs the control line bypass throttle with positive line axial piston pump and pumping if the s gear pump and the control line mentioned cylinder - with the drain line, the transmission position corresponding to the reverse rotation of the output shaft, a control valve occupies the position in which he informs the control line mentioned cylinder with the intake line of an axial piston pump, and the inlet line of gear pump and the control line bypass throttle - with the drain line, and the transmission position corresponding to the Parking brake output shaft, a control valve occupies the position in which it closes the inlet line of gear pump and communicates with the drain line inlet line axial piston pump, the control line bypass throttle and the control line mentioned cylinder.

Adjustable bypass throttle control mechanism gear ratio gearbox equipped with additional control line communicating with the inlet line axial piston pump, and the specified regulatory mechanism gear ratio is provided with a device for switching from automatic control to manual, made in the form of a two-position valve, through which the inlet line of gear pump and control line bypass throttle is connected to four-way Manager g is korespodentite mechanisms of transmission, and manual regulation mentioned gear ratio made in the form of the three-position valve, which is connected to the drain line through which the control line bypass inductor connected to the mentioned on-off valve, in the mode of automatic control of gear ratio on-off valve occupies the position in which it overlaps the additional control line bypass throttle and reports through the four-way valve and the inlet line of gear pump with the drain line and the control line bypass throttle with positive line axial piston pump, and manual control of gear ratio on-off valve occupies the position in which it closes the inlet line gear pump and control line bypass throttle and reports through the four-way valve additional control line bypass throttle with positive line axial piston pump, and a three-position valve has a neutral position in which it overlaps the additional control line bypass throttle position increase in gearing ratio is s, in which an additional control line bypass throttle communicates with the inlet line axial piston pump through a two-position and four-way valves, and the position of the reduction gear ratio, in which an additional control line bypass throttle is communicated with the drain line.

Adjustable bypass throttle can be provided with a device for regulating the speed of its spool, made in the form of adjustment of the throttle installed in the control line bypass throttle. When the valve is in the bypass throttle may be provided with a mechanical or hydraulic, or pneumatic, or electric, or electronic control. However, the spool may be provided with a drive with software control.

Transmission can be equipped with a mechanism for interrupting the torque on the output shaft, made in the form of a two-position spring loaded valve connected to the drain line, the control line bypass throttle and the control line of the control cylinder mechanism for switching the direction of rotation of the output shaft, while in the off position the above-mentioned mechanism interrupts the torque specified valve occupies a position which, in which he covers all of the connected line, and switched on the above-mentioned mechanism interrupts the torque specified valve occupies the position in which it connects with the drain line control line bypass throttle and the control line of the cylinder.

Estate washer axial piston pump can be equipped with a mechanism for regulating the angle of its inclination, and the differential may be made conical or planetary. At the outlet of the drain line can be installed in the heat exchanger, and as the vessel with the working fluid can serve as an internal cavity of the body.

The invention is illustrated by drawings, which depict:

- figure 1 is a continuously variable transmission, a longitudinal section;

- figure 2 - section a-a in figure 1;

- figure 3 - cross-section B-B in figure 1;

- figure 4 - hydraulic system of the transmission.

Continuously variable transmission contains a leading 1 (figure 1) and output 2 shafts and a housing 3 in which is placed the leading 4 and led 5 gear constant mesh, 6 differential with coaxial leads 7 and led 8 gears, kinematically linked to each other through satellites 9 and 10, and is provided coaxially with the axes 11 and 12, and the mechanism of regulation of the gear ratio of the gearbox, including the axial piston pump 13 with magnet the setup portion of line 14 (figure 2) and the suction line 15, connected to the tank 16 filled with the working fluid, and installed in the inlet line 14 adjustable bypass throttle 17, the output of which is connected to a drain line 18 with a capacity of 16. The axial piston pump 13 includes an inclined washer 19, the rotating disk 20, supported through the bearing 21 on the inclined washer 19, the rotating body in the form of block 22 of the working cylinder 23 placed in them by the plungers 24, each of which is hinged to the rotating disk 20, and mounted from the side gears 4 and 5 end of the valve 25 with sickle input box 26 (figure 2 and 3)that communicates with the suction line 15, and sickle output window 27 that communicates with the inlet line 14. There are also other versions of the axial piston pump 13, for example, with a rotating inclined plate 19, with a sloped location of the work cylinder 23, with other types of valve and others (see, for example, the book: Basta T.M. Engineering hydraulics. The Handbook. M., engineering, 1971, p.166-204).

When this differential 6 is placed inside the block 22 in an axial piston pump 13 coaxially with the location of its leading 7 and led 8 gears and block 22, the leading gear 4 constant-mesh fixed on the control shaft 1, driven gear 5 constant-mesh gears mounted on the shafts 11 leading above the Terni 7 differential 6, which has at least one pair of satellites 9 and 10, mounted on a common axis 28, each end of which is fixed to the block 22 in an axial piston pump. Through satellites 9 and 10 and the axis 28 of the block 22 in an axial piston pump 13 is kinematically connected with the differential gear 6, the driven gear 8 is kinematically connected with the output shaft 2.

The bypass throttle 17 may be performed, for example, in the form of a slide valve 29 (figure 4) with an annular groove 30, is placed in the sleeve 31, in which the inlet 32 and outlet 33 of the side Windows and gable window 34, and can be supplied with control line 35, indicating the end of the window 34 of the sleeve 31 with the inlet line 14 axial piston pump 13 or with the drain line 18. Annular groove 30 of the valve 29 is made with the possibility of periodic messages inlet 32 and outlet 33 of the Windows of the sleeve 31, the sleeve 31 is installed compression spring 36 which presses the spool 29 in the side of the open end 34 of the sleeve 31 with the message input 32 and an output 33 of the Windows last in the absence of pressure in the control line 35. In the inlet 14 or the drain line 18 has a retaining orifice 37, providing a specified minimum pressure in the inlet line 14, necessary for the operation of the hydraulic system of the transmission.

In addition to the regulatory mechanism gear ratio gearbox equipped with t is the train of the mechanism of switching the direction of rotation of the output shaft 2 and the mechanism for restricting the rotation speed and the Parking brake of the specified shaft. These mechanisms can be fitted with a control valve 38 (figure 4). While the end of the drive shaft 1, which is case 3, provided with a support 39 mounted on the end of the valve 25 in an axial piston pump 13, and a mechanism for switching the direction of rotation of the output shaft 2 includes a control cylinder 40 mounted on the outer side face of the valve 25 coaxial with the drive shaft 1 and is provided inside the piston 41 with an axial hole for passage of the drive shaft, the piston cavity 42 located between the piston 41 and end valve 25, and the control line 43, tells the piston cavity 42 via the control valve 38 to the drain line 18 or forcing line 14 axial piston pump 13, a friction disk 44 with slots on its axial hole, mounted coaxially on the drive shaft 1 with the possibility of axial movement and interaction with the piston 41 of the steering hydraulic cylinder 40, and are in engagement with each other lead 45 and the driven gear 46, the first of which has a drive shaft 1 between the pinion 4 constant-mesh gears and a friction disc 44 with the opportunity to interact with the latest and the free turning relative to the drive shaft 1, and the other fixed to the block 22 axially of porshneva the pump 13. When this friction disk 44 is supplied by spring 47, clamped it to the piston 41 of the steering hydraulic cylinder 40, in top gear 45 from the side of the friction disk 44 internal axial groove flange, in which the spring 47 of the friction disk 44, rests on the one hand in the collar of the mentioned grooves, and the end face of the friction disk 44, the section of the drive shaft 1 located in the area of the axial movement of the friction disk 44, made with protruding slots 48 within the locking slots of the friction disk 44, and the spring 47 of the friction disk 44 is configured to squeezing the last from the end of the pinion 45 when connecting the piston cavity 42 of the steering hydraulic cylinder 40 with the drain line 18 and with the possibility of coupling end face of the friction disk 44 with the end of the pinion 45 when connecting the piston cavity 42 of the steering hydraulic cylinder 40 with the inlet line 14 axial piston pump 13. Bearing 39 end of the drive shaft 1 can be placed inside of the steering hydraulic cylinder 40 between the piston cavity 42 last and end valve 25 in an axial piston pump 13.

The end of the half shaft 12 driven gear 8 of the differential is made with a groove, the ends of the axes 11 and 12 of the differential 6 and the ends of the output shaft 2 mounted in fixed to the body 3 supports, and m is the mechanism limiting the rotation speed and the Parking brake output shaft 2 are accommodated in the housing 3, kinematically connects the shaft 12 driven gear 8 of the differential gear 6 to the output shaft 2 with the inclusion of their coaxial position and includes a gear pump 49 with the leading 50 (2) 51 and driven gears, the first of which is fixed to the output shaft 2 between the supports in the housing 3, the suction line 52 connected to the tank 16 and the intake line 53 having two taps 54 and 55, the first of which soobschaetsa through the bypass valve 56 with an internal cavity 57 case 3, communicating with a drain line 18 and the second overlaps the controlling valve 38 or connected the last with the drain line 18, and the clutch 58 is installed between axial piston 13 and the gear 49 pumps coaxially with the axis 12 of the driven gear 8 of the differential and output shaft 2 and provided with axial bore, one end of which has a worm movable connection 59 with the end of the axis 12 of the differential 6 and the second slotted flexible connection 60 are accommodated in the housing 3 by the end of the output shaft 2, while the outlet 55 of the intake line 53 of gear pump 49 has a retaining orifice 61 (figure 4), blocking rotation of the output shaft 2 in the neutral position of the gearbox.

The bypass valve 56 is installed parallel to the axis of the output shaft 2 and provided with an axial rod 62, a spring 63 mounted on the axial shaft 62, and smeshannym in the housing 3 between the clutch 58 and gear pump 49 managing lever 64, which has one end pivotally connected to the housing 3, the middle part interacts with the sleeve 58 and is made with an opening for free passage through it of the drive shaft 2 and the other end is made with a hole, in which freely enters the end of the axial rod 62, a spring 63 is installed between the gate by-pass valve 56 and managing lever 64 on the axle 12 of the differential gear 6 has a thrust washer 65, with an emphasis in the flange groove of the specified axis, the clutch 58 is made with an external groove from the side of the hard disk 65, based on the control lever 64 through the bearing 66 and is supplied by spring 67 installed on the specified coupling with an emphasis one end in the thrust washer 65, and a second in the flange groove clutch 58.

The control valve 38 is made of the four-connected to the inlet line 14 axial piston pump 13, the outlet 55 of the intake line 53 of gear pump 49, the drain line 18, the control line 43 of the steering hydraulic cylinder 40 of the mechanism for switching the direction of rotation of the output shaft 2 and the control lines 35 bypass throttle 17 and may be in the neutral position "N"to prevent rotation of the output shaft 2, in the position of working rotation "PB" of the output shaft 2, in the position of the reverse rotation "S" in position Parking brake "ST" specified shaft. When COI is whether the proposed gearboxes in vehicles and machinery drives position "RV" valve 38 corresponds to direct the course of, and the position of the "OB" - back course. In this, the control valve 38 is arranged to message delivery line 14 axial piston pump 13, the inlet line 53 of gear pump 49, the control line 35 bypass throttle 17 and the control line 43 of the steering hydraulic cylinder 40 with the drain line 18 in the neutral position "N" of the valve 38, with the possibility of message control line 35 bypass throttle 17 with the inlet line 14 axial piston pump 13, and the inlet line 53 of gear pump 49 and the control line 43 of the steering hydraulic cylinder 40 with the drain line 18 in position "PB" of the valve 38, corresponding to the working rotation the output shaft 2, via the control line 43 of the steering hydraulic cylinder 40 with the inlet line 14 axial piston pump 13, and the inlet line 53 of gear pump 49 and the control line 35 bypass throttle 17 - with the drain line 18 in position "S" valve 38 corresponding to the reverse rotation of the output shaft 2, and with the possibility of overlap of the drain 55 of the intake line 53 of gear pump 49 and messages with the drain line 18 of the intake line 14 axial piston pump 13, the control line 35 bypass throttle 17 and the control line 43 of the steering hydraulic cylinder 40 in position "ARTICLE" guide is raspredeliteli 38, appropriate Parking braking of the output shaft 2.

To enable regulation of the gear ratio of the gearbox in manual and automatic mode, the bypass throttle 17 is provided with an additional control line 68, communicating with the inlet line 14 axial piston pump 13 through the control valve 38 and the mechanism of regulation of the gear ratio of a transmission provided with a device for switching from automatic control to manual, made in the form of a two-position valve 69 through which the inlet line 53 of gear pump and control lines 35 and 68 bypass throttle 17 is connected to the valve 38, and manual control of gear ratio made in the form of the three-position valve 70, which is connected to the drain line 18 and through which an additional control line 68 bypass throttle 17 is connected to the on-off valve 69. In the mode of automatic control of gear ratio on-off valve 69 is position "A", in which he covers the additional control line 68 bypass throttle 17 and reported through the four-way valve 38 of the intake line 53 gear us the sa with the drain line 18, and the control line 35 bypass throttle 17 with the inlet line 14 axial piston pump 13, and manual control of gear ratio on-off valve 69 occupies the position of "P", in which it closes the outlet 55 of the intake line 53 of gear pump 49 and the control line 35 bypass throttle 17 and reported through the four-way valve 38 additional control line 68 bypass throttle 17 with the inlet line 14 axial piston pump 13. The three-position valve 70 has a neutral position "N"in which he covers the additional control line 68 bypass throttle 17, the position of the zoom ratio "KJV", in which an additional control line 68 bypass throttle 17 is communicated with the inlet line 14 axial piston pump 13 through a two-position 69 and four-way valves 38, and the position of the reduction gear ratio "act", in which an additional control line 68 bypass throttle 17 is communicated with the drain line 18.

To enable the speed control response bypass throttle 17 to a pressure change in the intake line 14 axial piston pump 13 bypass throttle 17 is equipped with a device regulated the I speed it slide valve 29, made in the form of adjustment of the throttle 71 installed in the control line 35 bypass throttle 17. The spool 29 bypass throttle 17 may be provided with a mechanical or hydraulic, or pneumatic, or electric, or electronic control. However, to increase the level of automation of the operation of the proposed transmission valve 29 bypass throttle 17 may be provided with a drive with software control (not shown).

Transmission can be equipped with a mechanism for interrupting the torque on the output shaft 2 made in the form of a two-position valve spring 72 (figure 4)connected to the drain line 18, the control line 35 bypass throttle 17 and the control line 43 of the steering hydraulic cylinder 40, while in the off position the above-mentioned mechanism interrupts the torque valve 72 is closed position "C", in which he covers all of the connected line, and switched on the above-mentioned mechanism interrupts the torque control valve 72 is open position "O", in which he connects with the drain line 18 the control line 35 bypass throttle 17 and the control line 43 of the steering hydraulic cylinder 40.

To enable regulation of the flow-pressure x the characteristics of axial-piston pump 13 of his estate washer 19 may be provided with a mechanism 73 of the regulation of the angle of its inclination. Depending on the required differential 6 may be made conical, as shown in figure 1, or planetary. To ensure the possibility of maintaining a required level of temperature of the working fluid circulating in the hydraulic system of a transmission, at the outlet of the drain line 18 is a heat exchanger 74, and to exclude the possibility of clogging and jamming valves and valves hydraulic gearbox inlet suction lines 15 and 52 is a filter 75.

For ease of Assembly and disassembly of the gearbox housing 3 can be made of three detachable sections 76, 77 and 78, the first of which is placed the gears 4 and 5 of the constant-mesh gears and mechanism for switching the direction of rotation of the output shaft 2, the second axial piston pump 13 and the differential 6 and the third mechanism for restricting the rotation speed and the Parking brake output shaft 2. There is also a variant of execution of the transmission, where as the vessel 16 with the working fluid serves as the internal cavity 57 of the housing 3, the internal cavity sections 76-78 case 3 can communicate with each other. The valves 38, 69 and 70 can be placed in a common block 79 (figure 4) and can be equipped with mechanical or hydraulic, or pneumatic, or electric, or electronic control.

Box re the Ah works as follows.

In its neutral position, the valves 38 and 70 are in position "H", the valve 69 in the position a and the valve 72 in position "C", the bypass throttle 17 is fully opened and the working fluid freely passes through the annular groove 30 of the valve 29 from the window 32 in the window 33 of the sleeve 31 and then to the drain line 18 and the rotation of the driving shaft 1 is transmitted through the gears 4 and 5 and the axle 11 to the differential 6. While satellites 9 and 10 are rotated from the gear 7 and rotates together with them their axis 28 and associated with the last block 22 axial piston pump 13, and the rotation of the output shaft 2 and kinematically associated driven gear 8 of the differential gear 6 is blocked by the pump 49 through the creation in the inlet line of the last pressure retaining throttle 61. In position "H" valve 38 communicates with the drain line 18 of the intake line 14 axial piston pump 13, the inlet line 53 of gear pump 49, the control line 35 bypass throttle 17 and the control line 43 of the steering hydraulic cylinder 40. Because the working fluid from an exit of an axial piston pump 13 freely drained through the bypass throttle 17, the valve 38 and the drain line 18 in the container 16, the pressure in the inlet line 14 axial piston pump 13 is low, resulting in block 22 rotates without resisting film to prevent the effect from the inlet line 14, while the friction plate 44 is pressed by the spring 47 from the gear 45, so that the rotation of the driving shaft 1 is not transmitted to the gear 46.

For transfer gearbox with neutral mode on the mode of working of rotation of the output shaft 2 of the valve 38 is smoothly transferred to the position "RV" and maintain the same position of the other valves. In position "RV" valve 38 informs the control line 35 bypass throttle 17 with the inlet line 14 axial piston pump 13 through the control valve 69 and the inlet line 53 of gear pump 49 and the control line 43 of the steering hydraulic cylinder 40 with the drain line 18. The flow of the working fluid generated by the axial-piston pump 13 to a pressure line 14, passes only through the bypass throttle 17 and the retaining orifice 37. Due to the hydraulic resistance of the last pressure in the inlet line 14 and the associated control line 35 increases and the valve 29 under increasing pressure in the line 35 is moved, compressing the spring 36 and overlapping window 32 and 33 of the sleeve 31. This increases the pressure in the inlet line 14 and with it increases the resistance to movement of the plungers 24 and the rotation unit 22 in an axial piston pump 13, so that the rotation of the satellites 9 and 10 is transmitted to the driven pole is rny 8 differential 6 and then through the axle 12 and the clutch 58 to the output shaft 2. The higher the pressure in the inlet 14 and the control 35 lines, the greater the degree of overlap of the Windows 32 and 33 of the sleeve 31 of the spool 29 and, accordingly, the greater the resistance to rotation of the block 22 and above the speed of rotation of the output shaft 2. When the maximum pressure in the lines 14 and 35 there is a complete overlap of the Windows 32 and 33 of the sleeve 31 of the spool 29 and maximum number of revolutions of the output shaft 2.

Thus, after switching the valve 38 of the working fluid flow from the inlet line 14 to the bypass throttle 17 axial piston pump 13 and the differential 6 gearbox transformed into a hydrostatic clutch gear that transmits rotation from the drive shaft 1 to the output shaft 2. Thus the ratio of the number of revolutions of the output shaft 2 to the number of revolutions of the driving shaft 1 and the torque value and, accordingly, the power transmitted from the driving shaft 1 to the output shaft 2 is determined by the value of the hydraulic resistance of the inductor 17. Moreover, the higher the value of the hydraulic resistance of the inductor 17, the greater the value of the specified relation of speed and less than the amount transmitted through the transmission of torque and power. In turn, the value of the hydraulic resistance of the inductor 17 is determined by the value of the volume flow flowing through it W is dcosta, as well as geometric shape and area of its bore, through which the coolant is expanded working fluid. With increasing volumetric flow of liquid through the orifice 17 and the reduction of the area of its bore gidravlicheskiy resistance specified throttle is increased and, conversely, with a decrease in the volumetric flow of liquid through the orifice 17 and with the increase of the area of its bore gidravlicheskiy resistance specified throttle is reduced. Thus, due to selection of the rotation speed of the block 22 and the number, diameter and stroke of the plungers 24 of the pump 13, which determine the magnitude of the volumetric flow of liquid through the orifice 17, and also due to selection of the hydraulic characteristics of the specified throttle (the dependence of the pressure drop across the throttle on the magnitude of the volumetric flow passing through it liquid) and the selection of the diameter and number of teeth of the gears 4 and 5 it is possible to obtain the desired value of the ratio of the number of revolutions of the output shaft 2 to the number of revolutions of the driving shaft 1 and the torque and power transmitted from the driving shaft 1 to the output shaft 2.

The pressure in the inlet line 14 axial piston pump 13, which is the mode of working of rotation of the output shaft 2, is adjusted by changing the value of the initial efforts with the Atiyah spring 36 of the valve 29 by changing the thickness of the shims (not shown), mounted between the spring 36 and the valve 29 or the end face of the sleeve 31. If necessary, increase the value of the specified pressure to increase the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 36 and, if necessary, reduce the value of the specified pressure to reduce the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 36.

The reaction rate of the bypass throttle 17 to a pressure change in the intake line 14 axial piston pump 13 is controlled by adjusting the inductor 71. When it is necessary to increase said speed of response reduce the hydraulic resistance of the inductor 71, which leads to an increase in the speed of movement of the valve 29 in the sleeve 31 and, consequently, to reduce the time of overlap of the spool 29 of the Windows 32 and 33 of the sleeve 31, and Vice versa, if necessary, reduce the responsiveness bypass throttle 17 increase the hydraulic resistance of the inductor 71, which reduces the speed of movement of the valve 29 in the sleeve 31 and, consequently, to increase the time of overlap of the spool 29 of the Windows 32 and 33 of the sleeve 31.

The regulation gear ratio transmission with an operating rotation of the output shaft 2 is in automatic mode as long as the valve 69 is in position"A", in which it overlaps the additional control line 68 bypass throttle 17 and reported through the four-way valve 38 of the intake line 53 of gear pump to the drain line 18 and the control line 35 bypass throttle 17 with the inlet line 14 axial piston pump 13. If necessary, translation regulatory mechanism gear ratio transmission with automatic mode to manual valve 69 is switched to the position "R", in which it closes the outlet 55 of the intake line 53 of gear pump 49 and the control line 35 bypass throttle 17 and reported through the four-way valve 38 additional control line 68 bypass throttle 17 with the inlet line 14 axial piston pump 13. This enables the mechanism for restricting the rotation speed of the output shaft 2 with the regulation of the pressure in the inlet line 53 of gear pump 49 through the bypass valve 56.

The speed of the output shaft 2 is supported within the specified limits with a mechanism for restricting the rotation speed of the specified shaft. With increasing speed of rotation of the output shaft 2 over setpoint clutch 58 is moved by a worm 59 and spline 60 connections in the direction of the lever 64 and acting on the latter, zakryvai the bypass valve 56, what causes a rise in pressure in the inlet line 53 of gear pump 49, calling the braking-driving gear 50 gear pump 49 and reducing the speed of rotation of the output shaft 2 to the specified level, then the clutch 58 is moved in the direction of the thrust disk 65, which is accompanied by opening of the bypass valve 56 and the rotation of the output shaft 2 with a speed corresponding to the specified limits.

If necessary, increase the reduction ratio control valve 70 is smoothly moved from the neutral position "N" in position "KJV", in which an additional control line 68 bypass throttle 17 is communicated with the inlet line 14 axial piston pump 13 through a two-position 69 and four-way valves 38, which is accompanied by increase of pressure in the lines 68 and 35 and, respectively, overlap the spool 29 of the Windows 32 and 33 of the sleeve 31, which causes increased pressure in the inlet line 14, after which increases the resistance to movement of the working fluid at the outlet axial piston pump 13 and, accordingly, increases the resistance moving his plungers 24, which leads to increased hydrostatic clutch axial piston pump 13 driven by the gear 8 of the differential 6 and, consequently, to increase the speed of rotation of the output shaft 2 and the fall of rutsiro torque and power on the specified shaft. In the process of moving the valve 70 from the position "N" in position "KJV" volumetric flow rate of working fluid through the orifice 17 and, accordingly, the hydraulic resistance of the latter are growing and with them grows the speed of rotation of the output shaft 2 and decreases torque and power at last. The maximum value of the speed of rotation of the output shaft 2 and, respectively, the minimum value of torque and power on the specified shaft is achieved at the end of the movement of the valve 70 in the position of the "KJV".

If necessary, the reduction ratio control valve 70 is smoothly transferred to the position of "act", in which an additional control line 68 bypass throttle 17 is communicated with the drain line 18, which reduces the pressure in the control line 35 and the movement of the slide valve 29 under the action of the spring 36 in the direction of its original position with the opening of the Windows 32 and 33 of the sleeve 31, which is accompanied by a pressure drop in the inlet line 14 and, accordingly, by decreasing the speed of rotation of the output shaft 2 and the increase in torque and power at last.

For a translation of a transmission on the reverse rotation of the output shaft 2 of the valve 38 is switched to the position "S", while the other valves are in the position shown in figure 4. In position "S" guide is raspredelitel 38 informs the control line 43 of the hydraulic cylinder 40 with the inlet line 14 axial piston pump 13, and the inlet line 53 of gear pump 49 and the control line 35 bypass throttle 17 - with the drain line 18. The pressure in the control line 35, which is connected to a drain line 18 falls and the valve 29 by means of a spring 36 occupies a position in which the window 32 and 33 of the sleeve 31 are communicated with each other through the annular groove 30 of the valve 29, passing the working fluid from the inlet line 14 in the drain line 18. In this regard, the pressure in the inlet line 14 is low and the block 22 in an axial piston pump rotates freely without resistance from the inlet line 14, and the piston 41 under the action of pressure transmitted to the piston cavity 42 of the cylinder 40 from the control line 43, is moved together with a friction disc 44 in the side of the gear 45. In the process of moving friction disk slots is a progressive move in the slots 48 of the drive shaft 1. Specified joint movement of the piston 41 and the friction disk 44 ends with the pressing end of the latter to the end of the gear 45, after which the rotation of the shaft 1 is transmitted to the gear 45 and the pinion 46, which, along with its rotation creates additional torque on the block 22 in an axial piston pump 13. The speed of rotation of the block 22 and kinematically associated satellites 9 and 10 increases to such an extent that it changes the direction of rotation is of driven gear 8 of the differential 6 and connected with it the output shaft 2.

The pressure in the control line 43, in which there is the inclusion of the reverse rotation of the output shaft 2, is regulated by changing the amount of force the initial compression of the spring 47 by changing the thickness of the shims (not shown)mounted between the spring 47 and the friction wheel 44 or the gear 45. If necessary, increase the value of the specified pressure to increase the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 47, and, if necessary, reduce the value of the specified pressure to reduce the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 47. By selection of the diameter and number of teeth of the gears 45 and 46 is regulated by the ratio of the number of revolutions of the lead 1 and the output 2 of the shafts during the reverse rotation of the latter.

For a translation of a transmission mode of the Parking braking of the output shaft 2 of the valve 38 is switched to the position "ST", and the remaining valves are left in the position shown in figure 4. In the ARTICLE" the valve 38 closes the outlet 55 of the intake line 53 of gear pump 49 and communicates with the drain line 18 of the intake line 14 axial piston pump 13, the control line 35 bypass throttle 17 and the control line 43 of the hydraulic cylinder 40. While working zhidkosti intake line 14 is freely discharged into the tank 16 through the bypass throttle 17 and the valve 38, so that the pressure in line 14 is at a minimum, and therefore the block 22 in an axial piston pump 13 rotates freely without resistance from the inlet line 14 and without transmission of rotation from the satellites 9 and 10 on the driven gear 8 of the differential gear 6. However, the output shaft 2 is inhibited from possible turning external forces (arising, for example, at the location of the vehicle on the slope) using the master gear 50 gear pump 49, the rotation of which is blocked by closing valve 38 and the outlet 55 of the intake line 53 of the pump 49.

The rate of deceleration of the output shaft 2 is controlled by changing the amount of force the initial compression of the spring 67 by changing the thickness of the shims (not shown)mounted between the spring 67 and hard disk 65 or coupling 58. If necessary, increase the specified speed braking increase the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 67, and, if necessary, reducing specified speed braking, reduce the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 67. More stepless speed adjustment braking of the output shaft 2 is carried out by changing the amount of force the initial compression of the spring 63 propusnog the valve 56 by changing the thickness of the shims (not shown), mounted between the spring 63 and the lever 64, or gate valve 56. If you need a more smooth speed adjustment braking of the output shaft 2 to reduce the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 63 and, if necessary, more stringent regulation specified speed braking increase the thickness specified washers and, accordingly, the amount of force the initial compression of the spring 63.

In the case of interrupting the torque on the output shaft 2 of the valve 72 is switched to the position "On", in which he connects with the drain line 18 direction line 35 bypass throttle 17 and the control line 43 of the hydraulic cylinder 40. The pressure in the control lines 35 and 43 falls, causing the spool 29 and the piston 41 with a friction disc 44 is moved, respectively, by springs 36 and 47 to its original position at which the annular groove 30 of the valve 29 informs each other of the window 32 and 33 of the sleeve 31, and the gear 45 disengages from drive shaft 1. This reduces the pressure in the inlet line 14 and the rotation speed of the block 22 in an axial piston pump 13, as a result stops the transmission of rotation from the satellites 9 and 10 on the driven gear 8 of the differential 6 and, accordingly, stops the transmission of torque from the driving shaft 1 to the output Val. If necessary, renewal of torque on the output shaft 2 of the valve 72 is switched to the original closed position "C", in which he covers all of the connected line.

If necessary, reduce to a specified temperature level of the working fluid circulating in the hydraulic transmission, along with the heat exchanger 74 are constructive measures: reduced volume flow of the operating fluid in the inlet line 14 axial piston pump 13 by reducing the stroke of the plungers 24 by reducing the angle of inclination of the inclined washer 19 through the mechanism 73, and by reducing the diameter of the cylinder 23 of the block 22 and double reduction speed of rotation of the latter relative to the speed of rotation axis 11 of the differential 6.

Perform pump control mechanism gear ratio of a transmission in the form of an axial piston pump and accommodation of differential within a block of working cylinders specified pump with axial location of the leading and driven gears of the differential and the specified block of working cylinders and attaching the satellites of the differential unit working cylinders in an axial piston pump with rotation allows to simplify the design and reduce the metal gearbox, to reduce the pulsation of the pressure and return at ECCI at the output of the specified pump and reduce the load on the teeth leading and driven gears constant mesh by reducing the difference of the diameters of these gears. In turn, simplifying the design and reducing the metal gearbox simplifies its manufacture and repair and reduces the weight, size and cost of transmission, low ripple output pressure characteristic of axial piston pumps, increases the life of the gearbox and provides uniform rotation of its output shaft, low reverse leakage characteristic of axial piston pumps, increases the efficiency of the transmission, and reducing stress on the teeth leading and driven gears constant mesh increases the service life of these gears. Included in the design of the proposed transmission axial piston pump 13 also performs the function of hydroaspartate rotation of the lead 1 and the output 2 shafts, absorbing mechanical vibrations of rotation of these shafts, which can occur when uneven loads on the latter.

However, the introduction in the design of the transmission mechanism limits rotation speed and the Parking brake output shaft, and mechanism for interrupting the torque on the latter extends the functionality of the transmission.

Unlike the currently used mechanical and hydromechanical transmissions of the proposed transmission has both advantages of both mechanical and hydromechanical transmissions, because it has high reliability and durability and high efficiency, which is typical for manual transmissions, and provides continuously variable gear ratio, which is characteristic of hydromechanical gear boxes. In this regard, the practical use of the proposed transmission can provide high technical and economic effect.

1. Continuously variable transmission containing lead and an output shaft and a casing, which houses the leading and driven gear constant-mesh gears, differential with coaxial gears, kinematically linked to each other through satellites and provided with aligned axes, and mechanism for regulating gear ratio transmission, comprising a pump with a rotating tool, a pressure line and a suction line connected to a tank filled with working fluid, and installed in the inlet line of the pump is adjustable bypass throttle, the output of which is connected to a drain line with the mentioned capacity, while rotating the body of the pump is kinematically connected with the differential, and the guest constant mesh gear kinematically connected with the output shaft, wherein the pump mechanism of regulation of the gear ratio of the gearbox is made of Axia is Hino piston with an inclined washer, the valve and rotating the working body, made in the form of block working cylinders placed in them by the plungers, each of which is kinematically connected with the inclined washer, differential placed inside a block of working cylinders in an axial piston pump with axial location of its leading and driven gears and the said block and has at least one pair of satellites, mounted for rotation in the block working cylinders in an axial piston pump, the leading constant mesh gear connected with the drive shaft and driven gear constant mesh connected with a pinion differential.

2. Transmission according to claim 1, characterized in that the axial piston pump is provided with a rotating disc resting on the inclined washer and the valve specified pump made a face and set with constant mesh gears, while the plungers axial piston pump pivotally connected with the said rotating disk.

3. Transmission according to claim 1, characterized in that the leading constant mesh gear fixed on the drive shaft and driven gear constant-mesh gears mounted on shafts pinion differential.

4. Transmission according to claim 1, characterized in that the inlet or discharge of linustatin retaining the throttle.

5. Transmission according to claim 1, wherein the adjustable bypass throttle is made in the form of a slide valve with a circular groove is placed in the sleeve, in which the input and output side Windows and gable window, and supplied with control line, indicating the end window of the sleeve valve with the inlet line axial piston pump, with the sleeve installed compression spring which presses the valve toward the open end of the sleeve with the message input and output Windows of the past through the annular groove of the valve when the pressure in the control line.

6. Transmission according to claim 1, characterized in that it is equipped with a mechanism for switching the direction of rotation of the output shaft.

7. Transmission according to claim 1, characterized in that it is provided with mechanism for restricting the rotation speed and the Parking brake output shaft.

8. Transmission on PP and 7, characterized in that the mechanisms provided with a control valve.

9. Transmission of claim 8, characterized in that the end of the drive shaft, which is the case fitted with a support fixed on the end of the valve axial piston pump, and a mechanism for switching the direction of rotation of the output shaft includes a control cylinder mounted on the outer side of the mentioned end hydrorise is adelitas coaxial with the drive shaft and is provided inside the piston with an axial hole for passage of the drive shaft, the piston cavity, located between the piston and end valve axial piston pump, and the control line that tells the piston cavity through the control valve to the drain line or the inlet line axial piston pump, a friction disk splined on its axial hole, mounted coaxially on the drive shaft for axial movement and interaction with the piston of the control cylinder, and being in engagement with each other driving and driven gears, the first of which is installed on the control shaft between the pinion constant-mesh gears and a friction disc with the opportunity to interact with the latest and the free turning relative to the drive shaft, and the second pinned on the block working cylinders in an axial piston pump, with the friction disc provided with a spring, clamped it to the piston of the control cylinder, leading to the mentioned gear mechanism from the side of the friction disk internal axial groove flange, which has a spring friction disc, resting with one hand in the collar of the mentioned grooves, and the end face of the friction disk, the area of the drive shaft located in the area of the axial movement of the friction disk made with protruding splines with what zmoznostjo their coupling with the splined friction disc when communicating with the last mentioned pinion mechanism, and spring friction disc made with the possibility of releasing the latter from the end of the pinion mentioned mechanism when connecting the piston cavity of the steering hydraulic cylinder with a drain line and with the possibility of coupling end face of the friction disk with the end of the pinion mentioned mechanism when connecting the piston cavity of the steering cylinder with the intake line of an axial piston pump.

10. Transmission according to claim 9, characterized in that the bearing incorporated in the housing end of the drive shaft located inside the control cylinder of the mechanism for switching the direction of rotation of the output shaft between the piston cavity of the specified cylinder and end valve axial piston pump.

11. Transmission of claim 8, characterized in that the end of the axis driven gear of the differential is made with a groove, the ends of the axes of the leading and the trailing differential gears and the ends of the output shaft is installed in the fixed to the body support, and a mechanism for restricting the rotation speed and the Parking brake output shaft accommodated in the housing, kinematically connects the axle driven gear differential with an output shaft, providing their aligned position, and includes a gear pump with leading and driven gears, the first of which is fixed to the output VA is in between his legs in the housing, a suction line connected to a tank filled with working fluid, and a pressure line having two taps, one of which is communicated through the bypass valve with the internal cavity of the housing, communicating with the drain line, and the second overlaps the controlling valve or connects the past with the drain line, and a clutch installed between the axial-piston and gear pumps coaxially with the axis driven gear of the differential and output shaft and provided with axial bore, one end of which has a worm movable connection with the end of the axis driven gear of the differential, and the second slotted movable connection is placed in the case by the end of the output shaft, with the second outlet of the intake line of gear pump is installed retaining the throttle referred bypass valve is installed parallel to the axis of the output shaft and provided with an axial shaft, a spring mounted on the specified axial rod, and accommodated in the housing between the clutch and gear pump managing lever, which has one end pivotally connected to the housing, the middle portion interacts with said clutch and is made with an opening for free passage through it of the output shaft and the other end is made with a hole, in which freely enter the end of the axial rod by-pass valve, spring by-pass valve is installed between the gate of the latest and managing lever on the axle driven gear of the differential gear set thrust washer with an emphasis in the flange groove of the specified axis, the clutch is made with the outer groove side of the thrust disc and provided with a spring installed on the specified coupling with stop one end of the thrust disk and the second in the shoulder grooves mentioned clutch.

12. Transmission according to claim 9, 10 or 11, characterized in that the control valve is made of the four position and is connected to the inlet line axial piston pump, a pressure line gear pumps, drain line, the control line of the control cylinder mechanism for switching the direction of rotation of the output shaft and the control line bypass throttle while in neutral transmission position precluding rotation of the output shaft, a control valve occupies the position in which it communicates with the drain line inlet line axial piston pump, a pressure line gear pumps, control line bypass throttle and the control line mentioned cylinder, in the transmission position corresponding to the working rotation of the output shaft, the control valve takes a position, in which the he informs the control line bypass throttle with positive line axial piston pump, and forcing the line of the gear pump and the control line of the above-mentioned cylinder with the drain line, a transmission position corresponding to the reverse rotation of the output shaft, a control valve occupies the position in which he informs the control line mentioned cylinder with the intake line of an axial piston pump, and the inlet line of gear pump and the control line bypass throttle - with the drain line, and the transmission position corresponding to the Parking brake output shaft, a control valve occupies the position in which it closes the inlet line of gear pump and communicates with the drain line inlet line axial piston pump, control line bypass throttle and the control line mentioned cylinder.

13. Transmission according to claim 1, characterized in that the bypass throttle is equipped with additional control line communicating with the inlet line axial piston pump, and a throttling mechanism gear ratio of a transmission provided with a device for switching from automatic control to manual, made in the form of a two-position valve, through which the inlet line of gear pump and control lines perepolkin the first inductor is connected to four-way control valve mechanisms of transmission, and manual regulation mentioned gear ratio made in the form of the three-position valve, which is connected to the drain line through which the control line bypass inductor connected to the mentioned on-off valve, in the mode of automatic control of gear ratio on-off valve occupies the position in which it overlaps the additional control line bypass throttle and reports through the four-way valve and the inlet line of gear pump with the drain line and the control line bypass throttle with positive line axial piston pump, and manual control of gear ratio on-off valve occupies the position in which it closes the inlet line gear pump and control line bypass throttle and reports through the four-way valve additional control line bypass throttle with positive line axial piston pump, and a three-position valve has a neutral position in which it overlaps the additional control line bypass throttle position increase in gearing ratio is s, in which an additional control line bypass throttle communicates with the inlet line axial piston pump through a two-position and four-way valves, and the position of the reduction gear ratio, in which an additional control line bypass throttle is communicated with the drain line.

14. Transmission according to claim 5, characterized in that the bypass orifice provided with a device for regulating the speed of its spool, made in the form of adjustment of the throttle installed in the control line bypass throttle.

15. Transmission according to claim 5, characterized in that the bypass valve reactor fitted with mechanical or hydraulic, or pneumatic, or electric, or electronic control.

16. Transmission according to claim 5, characterized in that the valve is in the bypass throttle is equipped with a drive with software control.

17. Transmission according to claim 1, characterized in that it is provided with mechanism for interrupting the torque on the output shaft, made in the form of a two-position spring loaded valve connected to the drain line, the control line bypass throttle and the control line of the control cylinder mechanism for switching the direction of rotation of the output shaft, while off in the th position of the above-mentioned mechanism interrupts the torque specified valve occupies the position, in which he covers all of the connected line, and switched on the above-mentioned mechanism interrupts the torque specified valve occupies the position in which it connects with the drain line control line bypass throttle and the control line of the cylinder.

18. Transmission according to claim 1, characterized in that the inclined washer in an axial piston pump is provided with a mechanism for the regulation of the angle of its inclination.

19. Transmission according to claim 1, characterized in that the differential is made conical.

20. Transmission according to claim 1, characterized in that the differential is made planetary.

21. Transmission according to claim 1, characterized in that the outlet drain line installed heat exchanger.

22. Transmission according to claim 1, characterized in that capacity with the working fluid is inside the body cavity.



 

Same patents:

FIELD: transport engineering.

SUBSTANCE: invention can be used as gearbox in vehicles or as actuator in tank armament stabilizers. Proposed stepless transmission contains power differential 1, comparing differential 30, regulating differential 2, two self-braking mechanisms 3, 4 operating in release mode, two regulators, and mechanism 36 for equalizing speeds of rotation of central gears of regulating differential. Input of power differential 1 is connected with drive and with input of regulating differential 2. Central gears 17, 18 of power differential are rigidly connected with driven members 15, 16 of self-braking mechanisms and are connected with central gears of comparing differential 30 to provide rotation of the latter in opposite directions. Driving members 13, 14 of self-braking mechanisms are connected with central gears of regulating differential by mechanism 36 equalizing speeds of rotation and are rigidly connected with regulators.

EFFECT: enlarged range of change of gear ratio, improved dynamic characteristics of vehicle, its reliability and multipurposeness.

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FIELD: mechanical engineering.

SUBSTANCE: positive-displacement hydraulic-mechanical transmission comprises input shaft (1), output shaft (2), two interconnected reversible controlled hydraulic motors (3) and (4), four-link differential (5), and pumping devices (12), (13), (14), and (15). Satellites (7) and (8) of differential (5) are made in pairs and engage each other. Satellite (8) is wide and interposed between the large solar gear (10) and central wheel (11) with the inner engagement. Satellite (7) is narrow and engages small solar gear (9). Two switching devices (14) and (15) connect the shaft of hydraulic motor (4) with input shaft (1) of the transmission and central wheel (11) with the inner engagement. Two switching devices (12) and (13) connect the shaft of hydraulic motor (3) with output shaft (2) of the transmission and small solar gear (9) of the differential.

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EFFECT: enhanced reliability and simplified structure.

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SUBSTANCE: invention relates to crawler tractors and it can be used in their full-flow hydrostatic transmissions. Said transmission contains dividing reduction unit 2, two parallel final hydrostatic drives with pumps 3, 4 and hydraulic motors 5, 6, track reduction units 17, 18 and two planetary mechanisms. Planetary mechanisms are installed between hydraulic motors 17, 18 and track reduction units 17, 18. Sun gears 9, 10 of planetary mechanisms are connected with each hydraulic motor by two similar gear trains 7, 9. Carriers 11, 12 of each planetary mechanism are connected with epicyclic wheels 14, 13 of other planetary mechanism and with track reduction units 17, 18. invention improves maneuverability of tractor, provides economic recuperation of brake power from trailing side to leading side at turning of tractor, reduced power load on engine at turning, reduced power losses in hydrostatic drives of transmission of tractor with possibility of use of hydrostatic drives of lower installed power.

EFFECT: improved service characteristics of tractor.

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The invention relates to a transport engineering

The invention relates to mechanical engineering and can be used in hydraulic drive control for continuously variable transmission

The invention relates to transport machinery and can be used as a continuously variable transmission of a vehicle

The invention relates to mechanical engineering and can be used to create a continuously variable transmission vehicles

FIELD: automotive industry.

SUBSTANCE: hydromechanical gear box comprises hydromechanical torque converter (2) and planet reduction gear. Carrier (6) of the first planet row is connecter with crankcase of gear box (1) through friction brake (17). Corona pinion (17) of the first planet row is connected with carrier (12) of the third planet row that represents output link (4) of the gear box. Output member (3) of the hydrodynamic torque converter is connected with solar pinion (5) of the first planet row through controllable clutch (15). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (18). Solar pinion (5) of the first planet row is connected with the crankcase of the gear box through friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with solar pinion (8) of the second planet row. Output members (3) of the hydrodynamic torque converter is connected with carrier (9) of the second planet row. Carrier (6) of the first planet row is connected with corona pinion (10) of the second planet row through friction controllable clutch (14).

EFFECT: expanded functional capabilities.

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FIELD: automotive industry.

SUBSTANCE: hydromechanical gear box comprises hydromechanical torque converter (2) and planet reduction gear. Carrier (6) of the first planet row is connecter with crankcase of gear box (1) through friction brake (17). Corona pinion (17) of the first planet row is connected with carrier (12) of the third planet row that represents output link (4) of the gear box. Output member (3) of the hydrodynamic torque converter is connected with solar pinion (5) of the first planet row through controllable clutch (15) and with carrier (6) of the first planet row through controllable clutch (14). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (18). Solar pinion (5) of the first planet row is connected with the crankcase of the gear box through friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with solar pinion (8) of the second planet row. Output members (3) of the hydrodynamic torque converter is connected with carrier (9) of the second planet row.

EFFECT: expanded functional capabilities.

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FIELD: automotive industry.

SUBSTANCE: hydromechanical gear box comprises hydrodynamic torque converter (2) and planet reduction gear. Carrier (6) of the first planet row is connected with the crankcase of gear box (1) through friction brake (17). Corona pinion (7) of the first planet row is connected with carrier (12) of the third planet row that is output link (4) of the gear box. Output member (3) of the hydrodynamic converter of torque is connected with solar pinion (8) of the second planet row and with solar pinion (5) of the first planet row through friction controllable clutch (15). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with carrier (9) of the second planet row. The solar pinion of the second planet row is connected with corona pinion (10) of the second planet row through the friction clutch.

EFFECT: expanded functional capabilities and prolonged service life.

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FIELD: automotive industry.

SUBSTANCE: hydromechanical gear box comprises hydromechanical torque converter (2) and planet reduction gear. Carrier (6) of the first planet row is connected with crankcase of gear box (1) through friction brake (17). Corona pinion (7) of the first planet row is connected with carrier (12) of the third planet row that represents output link (4) of the gear box. Output member (3) of the hydromechanical converter of torque is connected with solar pinion (8) of the second planet row and with solar pinion (5) of the first planet row via friction controllable clutch (15). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (18). Solar pinion (5) of the first planet row is connected with the crankcase of the gear box via the friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with carrier (9) of the second planet row. Solar pinion (8) of the second planet row is connected with corona pinion (10) of the second planet row through friction clutch (14).

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical transmission with nine forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and four friction brakes. Planetary reduction gear consists of four planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7. Second planetary gear train consist of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Fourth planetary gear train consists of sun gear 14, planet pinion carrier 15 and crown gear 16. Sun gear 5 is connected with case 1 by fricition brake 17. Friction brake 18 connects intercoupled carrier 6 and carrier 9 with case 1. Friction brake 19 connects intercoupled crown gear 10, sun gear 11 and gear 14 with case 1. Friction brake 19 connects intercoupled crown gear 10, sun gear 11 and sun gear 14 with case 1. Friction brake 20 connects intercoupled carrier 15 and crown gear 13 with case 1. Input member 3 of torque converter is coupled by friction clutch 21 with intercoupled crown gear 13 and carrier 15. Carrier 12 is coupled by friction clutch 22 with intercoupled carrier 6 and carrier 9. Sun gear 8 and crown gear 7 are coupled with input member 3.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

10 cl, 12 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission system. Proposed transmission with six forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and three friction brakes. Planetary reduction gear contains three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Input member 3 is connected with carrier 9 of second planetary gear train by friction clutch 24, and with sun gear 5 of first planetary gear train by friction clutch 15. Sun gear 8 of second planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train and crown gear 10 of second planetary gear train with case 1. Friction brake 18 connects sun gear 11 third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

16 cl, 18 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed transmission contains hydrodynamic torque converter 2 and planetary reduction gear. Carrier 6 of first planetary gear train is coupled by friction brake 17 with transmission case. Crown gear 7 of first planetary gear train is coupled with carrier 12 of third planetary gear train being output member 4 of transmission. Output member 3 of hydrodynamic torque converter is coupled with sun gear 8 second planetary gear train and by friction controlled clutch 15 with sun gear 5 of first planetary gear train. Sun gear 11 of third planetary gear is coupled by friction brake 18 with transmission case. Output member 3 of hydraulic torque converter is coupled by friction controlled clutch 14 with carrier 6 of first planetary gear train. Sun gear 5 of first planetary gear train is coupled by friction brake 16 with transmission case 1. Crown gear 10 of second planetary gear train is coupled with crown gear 13 of third planetary gear train. Carrier 6 of first planetary gear train is coupled with carrier 9 of second planetary gear train.

EFFECT: enlarged kinematic capabilities increased service life of transmission.

9 cl, 11 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed automatic hydromechancial transmission with six forward speeds and open reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, three friction clutches and two friction brakes. According to invention, planetary reduction gear of proposed transmission consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Input member 3 is connected by friction clutch 14 with carrier 9 of second planetaty gear train. Input member 3 is connected by friction clutch 15 with carrier 6 of first planetary gear train. Crown gear 10 of second planetary gear train is coupled with input member 3. Carrier 6 of first planetary gear train is connected by friction clutch 16 with carrier of second planetary gear train. Carrier 6 of first planetary gear train is connected with case 1 by friction brake 17. Friction brake 18 connects crown gear 13 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

12 cl, 14 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed transmission with six forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and three friction brakes. Planetary reduction gear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Input member 3 is connected by friction clutch 14 with carrier 6 of first planetary gear train, and by friction clutch 15, with sun gear 5 of first planetary gear train. Sun gear 8 of second planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train and sun gear 11 of third planetary gear train with case 1. Friction brake 18 connects carrier 12 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities increased service life of transmission.

24 cl, 26 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed transmission with six forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4, planetary reduction gear, two friction clutches and three friction brakes. Planetary reduction gear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, carrier 6 and crown gear 7. Second planetary gear train consists of sun gear 8, carrier 9 and crown 10. Third planetary gear train consists of sun gear 11, carrier 12 and crown gear 13. Input member 3 is connected by friction clutch 14 with carrier 6 of first planetary gear train and by friction clutch 15, with sun gear 5 of first planetary gear train. Sun gear 8 of second planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train and carrier 12 of third planetary gear train with case 1. Friction brake 18 connects sun gear 11 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increase life of transmission.

24 cl, 28 dwg

FIELD: transport engineering; self-propelled wheeled vehicles.

SUBSTANCE: proposed vehicle contains frame 1 with cab 9, front and rear steerable wheels 4, 6 and middle wheels 5, engine placed behind the cab along vehicle and covered by hood 11. hydrostatic transmission contains pumping station 21 consisting of matching reduction gear driven by engine placed behind the cab, and three pumps connected by pipelines with hydraulic motors providing separate drives of wheels. Hydraulic motors are arranged along frame 1 between sidemembers on solid brackets made in form of boxes with flanges connected with wall of side member between its webs. Invention makes it possible to create ecologically clean and reliable multipurpose all-wheel-drive vehicle of high cross-country capacity with hydrostatic transmission to drive all wheels.

EFFECT: provision of convenient mounting and servicing of transmission units.

5 cl, 7 dwg

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