The method is automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement and device for its implementation

 

The invention relates to methods and devices for continuous change in the torque on the output shaft depending on the resistance movement, primarily to the automotive industry. The device is a continuous change in the torque on the output shaft depending on the resistance movement contains infinitely variable mechanical planetary gear with sequentially coupled hydrodynamic transmission in the form of a fluid coupling, torque Converter or complex hydrodynamic transmission, planetary gearing consisting of two planetary gear sets: planetary number of the pump wheel, the planetary series of turbine wheels. All nodes are devices placed in the crankcase seals and bearings. When changing a continuous torque on the pump wheel hydraulic transmission additionally create two directions of torque transfer, which bisect: the first torque transfer from the pump wheel of the hydrodynamic transmission to the planetary series pump wheel unit and the second torque from the turbine wheel to planetary number of the turbine wheel of the device. With epitsiklov pump and turbine planetary alignments devices moments are combined and transmitted on the I of any desired band, automatic change of torque on the output shaft depending on the resistance movement. 2 N. and 7 C.p. f-crystals, 1 Il.

The invention relates to the field of engineering, primarily to the automotive industry.

Known methods of automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, which uses hydrodynamic transmission: fluid coupling, torque converters and complex hydrodynamic transmission (see the Tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 222).

However, these methods have significant drawbacks: change of torque transfer from the master to the slave shaft is in a small range, which does not ensure the transfer of torque in the desired range.

There are also known methods of automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, which in addition to the hydrodynamic transmission uses: multi-stage mechanical planetary gear set, which are installed in series with hydrogen the Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 144-165). In this way the torque and the rotation speed of the crankshaft of the engine through the intermediate elements is transmitted to the pump wheel of the hydrodynamic transmission through the transmission fluid is transmitted to the turbine wheel and the output shaft of the hydrodynamic transmission and then to the input shaft multistage mechanical planetary gear, which is a combination of multiple planetary gear sets with different ratios, connected in series, which, depending on the desired gear ratio are connected in series, thereby enables obtaining the desired range of variation of torque of the output shaft multistage mechanical planetary gear having three degrees of freedom (planetary gear American tank M 26).

The disadvantage of this method is: the change of torque transfer in planetary transmission is manual, which does not ensure the transfer of torque in the correct range automatically and continuously worsen the performance of the transmission and complicates the design makes it difficult to switch gears in the box because of the partial shutdown of the engine by reducing izmeneniya torque and speed of rotation of the output shaft depending on the resistance movement, to the desired range, improve transmission characteristics and simplify the design through the application of the proposed method for automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement.

The problem is solved in that the proposed technical solution at the pump wheel hydraulic transmission create additional two directions of torque transfer, which bisect, with the first torque transfer from the pump wheel of the hydrodynamic transmission through intermediate elements on planetary line of the pump wheel device, the second torque transfer from the pump wheel of the hydrodynamic transmission through the hydraulic transmission fluid on the turbine wheel to the turbine wheel via a shaft of the turbine wheel on the planetary series turbine wheel device, with epitsiklov pump and turbine planetary alignments devices moments are combined and transmitted on a common output shaft of the device, when passing through the first and second torque through the common axis of the planetary satellites series pump and turbine wheel torques partially disposed on a common modular drove planetaryscale hydrodynamic transmission can be fluid coupling, torque converters or complex hydrodynamic transmission.

In the drawing given a diagram of a device implementing the method of continuous variation of the torque and speed of rotation of the output shaft depending on the resistance movement.

In the drawing:

1 - engine,

2 - intermediate element,

3 - shaft of the turbine wheel of the hydrodynamic transmission,

4 - the turbine wheel of the hydrodynamic transmission,

5 - pump wheel of the hydrodynamic transmission,

6 - intermediate element,

7 - input hollow shaft planetary series pump wheel,

8 - input shaft of the planetary series of turbine wheels,

9 - solar planetary gear range of the pump wheel,

10 - input planetary satellites number of the pump wheel,

11 - total precast drove planetary alignments pump and turbine wheels,

12 satellites planetary series turbine wheel,

13 - General axis satellites planetary alignments pump and turbine wheels,

14 - solar planetary gear range of the turbine wheel,

15 - output planetary satellites number of the pump wheel,

16 - epicycle gear of the planetary series of turbine wheels,

17 - epicycle gear PLA is mi and bearings.

With the pump wheel of the hydrodynamic transmission 5 through the fluid transmission torque transmitted to the turbine wheel of the hydrodynamic transmission 4 on the shaft of the turbine wheel of the hydrodynamic transmission 3, with the pump 5 and the turbine wheel of the hydrodynamic transmission 4 rotating and revolving transfer the torque to be transmitted in two directions:

1. The first torque transmitted from the pump wheel of the hydrodynamic transmission 5 via the intermediate elements 6 on the input hollow shaft planetary series pump wheel 7, which is connected with a sun gear of the planetary number of the pump wheel 4, the sun gear of the planetary series pump wheel 9 on the input planetary satellites number of the pump wheel 15, with the input of the planetary satellites number of the pump wheel 15 on a common axis satellites planetary alignments of the pump and the turbine wheel 13, with the common axes of the planets series pump and turbine wheels 13 torque is transmitted to the output planetary satellites number of the pump wheel 15, with the output of the planets series pump wheel 15 on the epicycle gear of the planetary series pump wheel 17, with peredavaemaya precast drove planetary alignments of the pump and the turbine wheel 11.

2. The second torque transmitted from the turbine wheel of the hydrodynamic transmission 4 through the shaft of the turbine wheel of the hydrodynamic transmission 3 to the input shaft of the planetary series turbine wheel 8, which is connected with a sun gear of the planetary series of the turbine wheel 14, the sun gear of the planetary series turbine wheel 14 on the planets of some of the turbine wheel 12 with satellites planetary series turbine wheel 12 on a common axis satellites planetary alignments of the pump and the turbine wheel 13, with which the torque is transmitted on the epicycle gear of the planetary series of the turbine wheel 16, when this part of the transmitted torque with the common axes of the planets series pump and turbine wheel 13 is transmitted to the total precast drove planetary alignments of the pump and the turbine wheel 11. With epicycle gear of the planetary series pump 17 and the turbine wheel 16 of the first and second torques are combined and transmitted on a common output shaft of the device 18.

Part of the first and second torque transmitted to the General precast drove planetary alignments pump and turbine wheels 11, through the common axis of the planetary satellites series pump and turanyi series pump and turbine wheels 13, balancing itself through energy fluid hydraulic transmission, this is a change of torque or mobility total precast drove planetary alignments pump and turbine wheels 11, depending on the moment of resistance on the common output shaft of the device 18 on the one hand and the transmitted torque of the engine 1 on the other, so as to provide a change gear ratio of the device.

This required a continuous range of variation of the torque and speed of rotation of the output shaft depending on the resistance to movement is provided by a given gear ratio of the planetary series pump wheel provided immobility total precast drove planetary series pump and turbine wheels.

Automatic change continuously variable range of torque and speed of rotation of the common output shaft of the device 18, depending on the resistance to movement is provided by balancing the torque applied to the pump wheel of the hydrodynamic transmission 5 from the engine 1 on the one hand and torque resistance applied to the turbine wheel of the hydrodynamic transmission 4 with storeitem interaction through energy fluid hydraulic transmission, expressed in the change of mobility of the common carrier of the planetary series pump and turbine wheels.

To ensure the efficiency of the proposed method for automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement necessary proportionality input torque from the engine 1 to the pump wheel of the hydrodynamic transmission 5 and the side of the torque resistance applied to the turbine wheel of the hydrodynamic transmission 4 from the common output shaft of the device 18, this proportionality is ensured by a given gear ratio of the planetary series of turbine wheels.

The known device for the automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, which uses hydrodynamic transmission: fluid coupling, torque converters and integrated hydraulic transmission (see the Tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 227, 234, 237).

the future on the driven shaft occurs in a small range, that does not ensure the transfer of torque in the desired range.

Also known device for automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, which in addition to the hydrodynamic transmission uses: multi-stage mechanical planetary gear (see the Tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 144-165).

The prototype was taken the device for automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, which represents a multi-stage mechanical planetary gear tank M26, which are connected through intermediate elements with hydrodynamic transmission (see the Tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal Malinovsky R. J., 164, 240 C.). (Under the intermediate elements in the proposed description is assumed: input gears, reverse gear, intermediate lemanska planetary transmission with three degrees of freedom has three forward gears and one reverse gear. It consists of two planetary gear sets, two frictions and two brakes.

All nodes are placed in the crankcase, run in oil and are connected with a three-stage torque Converter “Lysholm-Smith”, in the following sequence: pump wheel of the torque Converter is connected with the engine through intermediate elements, the turbine wheel of the torque Converter is connected with the input shaft drove a multistage mechanical planetary gear transmission.

The disadvantage of this device lies in the fact that the torque transfer in a multi-stage mechanical planetary gear speed changes, which does not ensure the transfer of torque in the correct range automatically and continuously worsen the performance of the transmission and complicates the design makes it difficult to switch gears in the box because of the partial shutdown of the engine at lower rpm.

The present invention is a device that will provide the desired continuously variable automatic range change the torque and speed of rotation of the output shaft depending on the resistance movement, improve the performance of transmission and simplify the design, the speed of rotation of the output shaft depending on the resistance movement.

The task is solved in that the device for automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement is a continuous mechanical planetary gear with sequentially coupled hydrodynamic transmission.

The device comprises an intermediate elements, hydrodynamic transmission, when the pump wheel and the shaft of the turbine wheel of the hydrodynamic transmission connected two planetary series, and planetary line of the pump wheel device is connected with the pump wheel of the hydrodynamic transmission via an intermediate element, and planetary line of the turbine wheel device is connected to the shaft of the turbine wheel of the hydrodynamic transmission through a splined connection, both planetary series hosted on the same axis and have a common modular carrier common axis satellites, a common output shaft fixedly mounted thereon two epicycle gear, which is connected to the transmission.

Planetary line of the pump wheel has input and output satellites located outside the General precast drove, which are fixedly mounted on a common axis satellites, and the satellites of planetary series of the century

Total precast drove collapsible and is located inside the planetary series of turbine wheels except epicycle gear of the planetary series turbine wheel, which is located outside the General precast drove.

The input shaft of the planetary series pump wheel is hollow, which is located inside the input shaft of the planetary series of turbine wheels.

All nodes are devices placed in the crankcase seals and bearings run in oil.

Install multiple series-connected planetary alignments pump and turbine wheels with a wider range of transmitted torque when changing the overall characteristics of the device.

To receive direct transmission and the engine start to tug in a hydrodynamic transmission used to lock the turbine and the pump wheel of the hydrodynamic transmission.

To obtain reverse and neutral using more planetary gear with two degrees of freedom, which can be installed in front of the hydrodynamic transmission, and after the common output shaft of the device.

As a hydrodynamic transmission can be fluid couplings, hydrotest which contains: planetary gear, consisting of two planetary gear sets:

1. The planetary series pump wheel: input hollow shaft planetary series pump wheel 7, the sun gear of the planetary series pump wheel 9, the input 10 and output planetary satellites number of the pump wheel 15, the common axes of the planets series pump and the turbine wheel 13, General precast drove planetary alignments pump and turbine wheels 11, epicycle gear of the planetary series pump wheel 17.

2. The planetary series of turbine wheel: input shaft of the planetary series turbine wheel 8, the sun gear of the planetary series turbine wheel 14 total teams axes of the planets series pump and turbine wheels 13, General precast drove planetary alignments pump and turbine wheels 11, epicycle gear of the planetary series of the turbine wheel 16.

All nodes are devices placed in the crankcase seals and bearings run in oil and are connected in the following sequence: engine 1 through the intermediate element 2 is connected with the pump wheel of the hydrodynamic transmission 5, which in turn, through the intermediate element 6 is connected with input hollow shaft planetary series pump conomically transmission 4 through the shaft of the turbine wheel of the hydrodynamic transmission 3 and a splined connection is connected with the input shaft of the planetary series turbine wheel 8, the first part of which is inside the hollow input shaft of the planetary series pump wheel 7, the second part of the input shaft of the planetary series turbine wheel 8, which is connected with a sun gear of the planetary series of the turbine wheel 14, which passes through a total precast drove planetary alignments of the pump and the turbine wheel 11 and its end through a bearing mounted inside a common output shaft of the device 18 and the sun gear of the planetary series of the turbine wheel 14 is located inside the collapsible carrier of the planetary series pump and the turbine wheel 11, a sun gear of the planetary series pump 9 and the turbine wheel 14 connected with the satellites 10, 12 these series (and to planetary number of the pump wheel to the input planetary satellites number of the pump wheel 10), satellites 10, 12 are located on a common axis satellites planetary alignments of the pump and the turbine wheel 13, which for both series overall, but the input 10 and output planetary satellites number of the pump wheel 15 mounted on a common axis satellites planetary alignments pump and turbine wheels 13 and still are outside the General precast drove planetary alignments of the pump and the turbine wheel 11, and the satellites of precast drove planetary alignments pump and turbine wheels 11, the common axis of the planetary series pump and turbine wheels 13 pass through total precast drove planetary alignments pump and turbine wheels 11 and installed it freely on bearings), satellites, planetary alignments pump 15 and the turbine wheel 12, and to planetary number of the pump wheel of the output planetary satellites number of the pump wheel 15 through a splined connection connected with epicycle gear pump 17 and 16 respectively of the turbine wheel of the planetary series pump and turbine wheels that are on the common output shaft of the device 18 and rigidly fixed on it, a common output shaft of the device 18 is connected to the transmission.

All the components are placed in a housing unit with seals and bearings 19 and work in oil output and input shafts are on the bearings and through them connected: input hollow shaft planetary series pump wheel 7 and the common output shaft of the device 18 with the case of devices with seals and bearings 19 and the input shaft of the planetary series turbine wheel 8 with input hollow shaft planetary series pump wheel 7, which is located inside it.

The proposed device can be used in slave and complex hydrodynamic transmission, and to obtain direct or high gear and start the engine of the tow in a hydrodynamic transmission can be applied to lock the turbine and the pump wheel of the hydrodynamic transmission, to obtain reverse and neutral can be applied advanced planetary gearbox with two degrees of freedom.

In the initial position: the engine 1 through the intermediate element 2 is connected with the pump wheel of the hydrodynamic transmission 5, which in turn, through the intermediate element 6 is connected to the input hollow shaft planetary series pump wheel 7, which through the bearings installed on the axis of the input shaft of the planetary series turbine wheel 8 and is connected with a sun gear of the planetary series pump wheel 9, the sun gear of the planetary series pump wheel 9 is engaged with the input planetary satellites number of the pump wheel 10, the turbine wheel of the hydrodynamic transmission 4 through the shaft of the turbine wheel of the hydrodynamic transmission 3 and a splined connection is connected with the input shaft of the planetary series turbine wheel 8 and is connected with a sun gear of the planetary series of the turbine wheel 14, where the first part of the input shaft of the turbine wheel 8 is vet the input shaft of the turbine wheel 8 through General precast drove planetary alignments of the pump and the turbine wheel 11 and its end through a bearing mounted inside a common output shaft of the device, the sun gear of the planetary series of the turbine wheel 14 is located inside the General precast drove planetary alignments of the pump and the turbine wheel 11 and is engaged with the planetary satellites range of the turbine wheel 12, which are on a common axis satellites planetary alignments of the pump wheel 13, the planetary satellites range of the turbine wheel 12 located inside the collapsible carrier of the planetary series pump and turbine wheels 11 and engages with epicycle gear of the planetary series of the turbine wheel 16, the input planetary satellites number of the pump wheel 10, through the common axis of the planetary satellites series pump and turbine wheels 13 are connected with the output planetary satellites number of the pump wheel 15, the input 10 and output planetary satellites series pump and turbine wheels 15 are outside the General precast drove planetary alignments of the pump and the turbine wheel 11, the common axis of the planetary satellites series pump and turbine wheels 13 pass through total precast drove first and second planetary gear sets of the pump and the turbine wheel 11, the output planetary satellites number of the pump wheel 15 engages with epicycle gear planechase on a common output shaft of the device 18 and rigidly fixed on it, the common output shaft of the device 18 is connected on one side through the bearing to the input shaft of the planetary series turbine wheel 8, and on the other side is connected to the transmission. All the components are placed in a housing unit with seals and bearings 19 and work in oil output and input shafts are on bearings.

The operation of the device is as follows.

In the initial moment when the moment on the common output shaft of the device 18 is equal to some value, and the total turnover of the output shaft of the device 18 and the engine 1 is equal to zero, the pump 5 and the turbine wheel of the hydrodynamic transmission 4 fixed device does not work. The engine 1 starts to operate at the minimum speed, while the turbine wheel of the hydrodynamic transmission 4 is stationary and the pump wheel of the hydrodynamic transmission 5 rotates, the liquid under the action of centrifugal forces, jumping up from the blades of the pump wheel of the hydrodynamic transmission 5 acts on the turbine wheel of the hydrodynamic transmission 4, creating the turbine wheel of the hydrodynamic transmission 4 initial moment directed in the same direction as the torque on the pump wheel of the hydrodynamic transmission 5, which pitals the standard transmission 5, the input shafts of the planetary series pump 7 and the turbine wheel 8 starts to rotate at different angular velocities and different torques, the torque passing through the gear ratio of the planetary series pump and turbine wheels vary in size, but as the moment on a common output shaft of the device 18 is greater than the sum of the torques transmitted by the planetary alignments, the common output shaft of the device 18 is stationary, respectively, with a minimum speed of the engine 1, epicycle gear of the planetary series pump 17 and the turbine wheel 16 is also fixed. Therefore, when starting from rest at the initial moment of time on a common output shaft of the device 18 is greater than the sum of the torques transmitted by the planetary alignments of the planets series pump 15 and the turbine wheel 12 obkatyvalisj fixed on the epicycle gears of the planetary series pump 17 and the turbine wheel 16, make a total precast drove planetary alignments of the pump and turbine wheel 11 to rotate in the direction opposite to the rotation of the pump wheel of the hydrodynamic transmission 5, and the torque from the pump wheel of the hydrodynamic transmission 5 through the common axis of the planetary satellites the number of todaythat the moment created by the turbine wheel of the hydrodynamic transmission 4, as a result of their addition through the planetary series turbine wheel, the turbine wheel of the hydrodynamic transmission 4 effect negative moment, which causes the rotating turbine wheel of the hydrodynamic transmission 4 in the opposite direction of rotation of the pump wheel of the hydrodynamic transmission 5, thereby increasing the drag torque of the turbine wheel of the hydrodynamic transmission 4 to the pump wheel of the hydrodynamic transmission 5, the output shaft of the device 18 is fixed, and the turbine wheel of the hydrodynamic transmission 4 is rotated in the opposite direction from the pump wheel of the hydrodynamic transmission 5, creating it moment with the opposite sign relative to the input on the pump wheel of the hydrodynamic transmission 5, and the torque from the crankshaft of the engine is converted to heat fluid in the hydraulic transmission.

Further, the engine 1 starts to increase the speed, increasing the speed of the pump wheel of the hydrodynamic transmission 5, and accordingly the torque at the pump wheel of the hydrodynamic transmission 5 or falling resistance on the common output shaft is ECE hydrodynamic transmission 5 in the direction of growth of positive over negative, which leads first to the negative braking rotation of the turbine wheel of the hydrodynamic transmission 4 until it stops and then change the direction of rotation of the turbine wheel of the hydrodynamic transmission 4 in the positive direction, in the direction of rotation of the pump wheel of the hydrodynamic transmission 5 to a speed approximately equal to the speed of rotation of the pump wheel, in which the need for transformation in addition to its own characteristics of the engine missing. The increase in the ratio of positive over negative torque on the turbine wheel of the hydrodynamic transmission 4 in the direction of positive growth ratio will lead to an increase of the torque on the axles total precast drove planetary alignments of the pump and the turbine wheel 11, which would entail first slow its rotation down to a complete stop and, as a consequence, the increase of gear ratio of the planetary series pump wheel and generally increase torque up to the maximum specified value and the falling speed of the output shaft to the minimum specified, at maximum torque, with the full stop was taken. In the subsequent growth of the ratio of positive over negative IOM is to change the direction of rotation total precast drove planetary alignments of the pump and turbine wheel 11 in the positive direction, in the direction of rotation of the pump wheel of the hydrodynamic transmission 5 to a speed approximately equal to the speed of rotation of the pump wheel of the hydrodynamic transmission 5, and as a consequence the reduction gear ratio and the magnitude of the variation of torque of the planetary series pump wheel to zero when increasing the rotation speed of the output shaft of the device to the maximum specified value.

When this planetary line of the pump wheel device passing through it changes the torque on the output shaft of the device, provides the required continuous range of variation of the torque and speed of rotation of the output shaft depending on the resistance to movement due to the set gear ratio with the relative immobility of the General drove the first and second planetary series pump and turbine wheels and a planetary series turbine wheel device provides relative immobility drove first and second planetary series pump and turbine wheels, provides automatic adjustment of the torque and speed of rotation of the output shaft depending on the resistance to movement due to the set gear ratio of the planetary series of turbine number of the CSOs planetary series pump and turbine wheels and the direction of rotation of the input shaft of the turbine wheel, provided the specified direction of rotation of the input shaft of the turbine wheel, the trim points from the crankshaft of the engine, on the one hand, expressed at the moment of impact was taken from the reaction resistance of the planetary rotation number of the pump wheel and the moment of resistance movement, on the other hand, expressed at the moment of impact was taken on the planetary series turbine wheel device, provides the pump and the turbine wheel via a hydraulic transmission fluid by rotation in different directions.

When implementing the proposed method of continuous variation of the torque and speed of rotation of the output shaft depending on the resistance movement and device for its implementation it is possible to provide any desired range of automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, to improve the characteristics of the transmission and to simplify its design through the installation of continuous mechanical planetary gear.

Sources of information

1. The tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal of the Soviet Union Menoi Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 144-165 - prototype method.

3. The tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 227, 234, 237.

4. The tanks. Basic theory and design. M: Publication of the Military order of Lenin red banner Academy of armored forces in the name of Marshal Malinovsky R. J., 1968, S. 144-165 - the prototype device.

Claims

1. The method is automatic and continuous change in the torque and speed of rotation of the output shaft depending on the resistance movement, in which the torque transfer from the engine crankshaft through intermediate elements on the hydrodynamic transmission, characterized in that the pump wheel hydraulic transmission create additional two directions of torque transfer, which bisect, with the first torque transfer from the pump wheel of the hydrodynamic transmission through intermediate elements on planetary line of the pump wheel device, the second torque transfer from the pump wheel of the hydrodynamic transmission through the hydraulic transmission fluid on the turbine wheel, with turbinehi turbine planetary alignments devices moments are combined and transmitted on a common output shaft of the device, when passing through the first and second torque through the common axis of the planetary satellites series pump and turbine wheel torques partially disposed on a common modular drove planetary alignments device and interact with each other, changing the mobility of the carrier and the direction of its rotation.

2. The device under item 1, comprising the intermediate elements, the hydrodynamic transmission, wherein the pump wheel and the shaft of the turbine wheel of the hydrodynamic transmission connected two planetary series, and planetary line of the pump wheel device is connected with the pump wheel of the hydrodynamic transmission via an intermediate element, and planetary line of the turbine wheel device is connected to the shaft of the turbine wheel of the hydrodynamic transmission through a splined connection, both planetary series hosted on the same axis and have a common modular carrier common axis satellites, a common output shaft fixedly mounted thereon two epicycle gear, which is connected to the transmission.

3. The device according to p. 2, characterized in that the planetary series pump wheel has input and output satellites located outside the General precast drove that still C the total precast drove, freely mounted on a common axis satellites.

4. The device according to p. 2, characterized in that the total precast drove collapsible and is located inside the planetary series of turbine wheels except epicycle gear of the planetary series turbine wheel, which is located outside the General precast drove.

5. The device according to p. 2, characterized in that the input shaft of the planetary series pump wheel is hollow, which is located inside the input shaft of the planetary series of turbine wheels.

6. The device according to p. 2, characterized in that all the components are placed in the crankcase seals and bearings and run in oil.

7. The device according to p. 2, characterized in that install multiple series-connected planetary alignments pump and turbine wheels with a wider range of transmitted torque when changing the overall characteristics of the device.

8. The device according to p. 2, characterized in that to obtain the direct transmission and the engine start to tug in a hydrodynamic transmission used to lock the turbine and the pump wheel of the hydrodynamic transmission.

9. The device according to p. 2, characterized in that for obtaining to be installed before the hydrodynamic transmission, and after the common output shaft of the device.

 

Same patents:

The invention relates to mechanical engineering, in particular for a continuously variable transmission (CVT) that provides a change speed power feed

The invention relates to mechanical engineering and can be used in cars instead of gearbox

The invention relates to mechanical engineering and can be used in drives of machines and mechanisms to ensure the compactness of the drive and the great depth reduction

FIELD: transport engineering.

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

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

1 dwg

FIELD: transport engineering.

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

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

1 dwg

FIELD: transport engineering.

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

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

1 dwg

FIELD: transport engineering.

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

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

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises hydrodynamic converter of torque (2) and planet reduction gear. Carrier (6) of the first planet row is connected with crankcase of the gear box (1) through friction brake (17). Corona pinion (7) of the first planet row is connected to 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 controlled 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 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. Corona pinion (10) of the second planet row is connected with carrier (6) of the first planet row through friction controlled 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 tansmission 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 (epicycle). Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10 (epicycle). Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13 (epicycle). Crown gear 10 of second planetary gear train is connected by friction clutch 14 with carrier 9 of second planetary gear train. Input member 3 is connected 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 crown gear 10 of second planetary gear train with case 1. Friction brake 18 connected sun gear 11 of third planetary gear train with case 1.

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

18 cl, 20 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with seven forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, three friction clutch and three friction brakes. Planetary reduction fear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and 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 intercoupled sun gear 8 and sun gear 11 and it is coupled also by friction clutch 15 with intercoupled carrier 9 and carrier 12. Carrier 9 coupled with carrier 12 is connected by friction clutch 16 with sun gear 11 coupled with sun gear 8. Sun gear is coupled with input member 3. Carrier 6 is connected with case 1 by friction brake 18 connects intercoupled carrier 9 and carrier 12 with case 1. Friction brake 19 connects intercoupled sun gear 8 and sun gear 11 with case 1.

EFFECT: enlarged kinematic capabilities, reduced consumption of fuel, increased service life of transmission, enlarged number of types of vehicles which can operate with transmission of proposed kinematic diagram.

4 cl, 6 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical transmission with six forward speeds and two reverse speeds 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 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. Carrier of second planetary gear train is connected by friction clutch 14 with input member 3. Input member 3 is connected by friction clutch 15 with sun gear 5 of first planetary gear train. Crown gear 7 of first 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 crown gear 13 of third planetary gear train and sun gear 8 of second planetary gear train with case 1. Friction brake 18 connects sun gear 11 of third planetary gear train with case 1. Friction brake 19 connects intercoupled carrier 9 of second planetary gear train and carrier 12 of third planetary gear train with case 1.

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

5 cl, 7 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.

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

Up!