Hydromechanical transmission

 

(57) Abstract:

Usage: in engineering, actuators, machines and mechanisms. The inventive hydromechanical transmission contains mounted in the housing axial hydraulic motor with a sloped drive and planetary gear. The latter is in the form of satellites on the axes of the carrier and gears. The swash plate of the hydraulic motor is made with a bevel gear crown. Each of the gears is made conical and with two toothed crowns of the outer larger diameter and an inner smaller diameter. Large diameter rims bevel gears are distinct. Separating the cones crowns at least one bevel gear are not the same. The external crown of each bevel gear is in mesh with the bevel teeth of the swash plate of an axial motor. The inner crown of each bevel gear is engaged with the satellites. 1 Il.

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.

Known hydromechanical transmission, comprising niskama is p placed in their housings, and the clutch is mounted on protruding from the housing walls, so the weight and dimensions of such a hydromechanical transmission is greatest. By increasing the depth of the reduction of mass and volume as the gearbox and the transmission increases.

Also known hydromechanical transmission, the combination of an axial piston hydraulic motor with a sloped drive and one - or two-stage planetary gearbox integrated in the General case. This set differs from other known primarily for compactness, however, the dimensions of the mechanical parts significantly exceed the dimensions of the motor in all three dimensions. In addition, the depth of reduction used gear carried gear ratio, is not always sufficient: single-stage gear unit reduction ratio is equal to a single-digit number and a two-stage gearbox although a two-digit number, but from the first ten two-digit numbers.

Increasing the depth of the reduction in the known solutions due to the increase in the number of steps or when saving the number of stages with increasing size of the gears, i.e., increasing size and weight.

The technical result of the invention is to increase panicacci transfer, containing axial hydraulic motor with a sloped drive and planetary gear, which includes drove with satellites on its axes and gears, the swash plate of the hydraulic motor is made with a conical gear ring and two coaxially mounted between themselves and the planet carrier of the gear wheels are made conical and with two crowns: external larger and smaller internal diameters (or one wheel is made with a single crown, but extra long teeth, so it also formed two crowns with different diameters). This toothed crown of the swash plate is engaged at diametrically opposite zones with external gear wheels, and satellites to the driver is also in diametrically opposite zones engages with the inner rims. Since the circumferential speed of the outer rims of the same, and the diameters are different, the angular velocity dvuhventsovye wheels differ, moreover, the direction of rotation opposite, as the direction of the peripheral speed of the inner crowns. Therefore, the circumferential speed of the satellite relative to the geometric axis of the carrier equal to the difference of peripheral speed of the inner crowns. These speeds are not the same even when equal to the internal diameter of the crowns.

P and, its final drive ratio which is expressed by a three-digit number. Here we mean that the diameters of the wheels of the proposed solution and known solutions are the same. If the depth of the reduction of the proposed solution to fulfill the same as in the known solutions, the size of the wheels, and consequently, the dimensions and weight transfer are reduced. Since the proposed solution is applied bevel gearing, the dimension in the direction of the axes of the conical wheels decreases. This envelope is reduced when reducing the diameter of the ring gear on the inclined disk, and it simultaneously increases the depth reduction. The proposed solution is applied to only one carrier and no couplings connecting the links of the transmission.

The drawing shows a hydromechanical transmission section.

Hydromechanical transmission includes accommodated in a common housing 1 axial hydraulic motor and planetary gear. In the hydraulic motor includes a cylinder block 2, a piston 3 in contact with the rods 4 of the swash plate 5, the geometrical axis of which is inclined to the axis of the cylinder 2 at an angle .

In the planetary transmission includes a bevel gear 6, is performed on an inclined disk 5, the two gears 7 and 8, coaxially mounted with the bottom axis 11). Gears 7 and 8 are tapered with two crowns: the outer larger diameter and an inner smaller diameter. Separating the cones crowns at least one bevel gear is not the same as, for example, greater 12 and lower 13 rims wheels 7, or as the rims 14 and 15 of the wheel 8, forming practically one crown with extra long teeth, and dividing it into two crown 14 and 15 is to analyze the kinematics of the mechanism.

With the outer rims 12 and 14 into engagement entered the crown 6, with the inner rims 13 and 15 are in engagement satellites 10. The diameters of d12and d14the outer rims 12 and 14 are not the same. The relationship of the diameters d13and d15the inner rims 13 and 15, depending on the angle of the axis of the satellite, which can be acute, obtuse, or straight, less than, greater than or equal to one. If the geometric axis of the swash plate 5, the shaft 9 and drove satellites 10 intersect at a point, angles and should not be equal. All the diameters of the crowns are given for the average length of the teeth sections.

Hydromechanical transmission works as follows.

Under the action of oil pressure supplied to the cylinder block 2, pistons 3 are formed forces, leading through the connecting rods 4 in degeneracies in opposite directions and with different angular velocities. The rims 13 and 15 with different and oppositely directed cutting speeds except when =, and the geometrical axis of the swash plate 5, the shaft 9 and drove satellites 10 intersect at one point, lead satellites 10 in complex movement around the axis 11 and around the shaft 9 led, which is driven into rotation with angular velocityin. When the circumferential speed of the satellite is equal to the difference of the peripheral speed of the rims 13 and 15, and the rotation direction of the shaft 9 led depends on the sign of the difference of the peripheral speed of these crowns.

If the swash plate 5 with a ring gear 6 of a diameter of d6rotates with angular velocity6, the circumferential speed of the middle sections of teeth crowns 6, 12, 14

V6=V12=V14= Angular velocity of gear wheels 7 and 8

7= = and

8= = Since d12d14then78Circumferential speed of the internal rims 13 and 15

V13= = and

V15= = Since d12d14even if the equality d13=d15V13V15. As the direction of rotation of the wheels 7 and 8 to the contrary, the peripheral speed of the satellite 10 Vwith(the speed the point at which the circumferential force from the satellite 10 is transmitted to the axle 11 and the distance to cotorras polprasert peripheral speed of the rims 13 and 15

Vc= (V13-V15) = The angular speed of the shaft 9 (led)

in= = - (1) Gear ratio of the planetary gear has a ratio of angular velocity of the input link (crown 6) and the output link (shaft 9)

i = From the expression (1) receive

i = (2)

Formulas (1) and (2) show that the angular speed and gear ratio i depend on the diameters of the toothed crowns and can take various values. At the same diameters of the toothed wheels of the proposed solution with the wheels of the known solutions of the angular speedinand gear ratio i can be not less than an order of magnitude, i.e., if theoretically the difference , thenin->> 0, and i is>> .

Thus, to obtain a gear ratio such large values, as proposed, in the known solutions must be increased or the size of the wheels, or increased number of steps, which is associated with an increase in the weight and size. In addition, the proposed transfer has smaller dimensions in the direction of the axis of the shaft 9 in comparison with the other two dimensions. This envelope is reduced when reducing the diameter of the crown 6 on the inclined disk, while deepening the reduction gear. In the transmission no clutch, soudanaise hydraulic motor with a sloped drive and planetary gear in the form of satellites on the axes of the carrier and gears, characterized in that the swash plate of the hydraulic motor is made with a bevel ring gear, each of the gears is made conical and with two toothed crowns of the outer larger diameter and an inner smaller diameter, large diameter rims bevel gears are distinct, separating the cones crowns at least one bevel gear does not coincide with the external crown of each bevel gear is in mesh with the bevel teeth of the swash plate of an axial motor, and an inner crown of each bevel gear is engaged with the satellites.

 

Same patents:

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

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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.

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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.

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EFFECT: expanded functional capabilities and prolonged service life.

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

18 cl, 20 dwg

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

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EFFECT: enlarged kinematic capabilities increased service life of transmission.

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