Inertial hydromechanical transmission

 

(57) Abstract:

The invention relates to a hydromechanical transmission. Inertial hydro-mechanical transmission includes a housing, input and output shafts, the pulse mechanism of the planetary type comprising a sun gear, a crown gear and drove with unbalanced loads, adjustable volume hydraulic transmission including a pump and hydraulic motor, and a check valve. Crown gear connected with the shaft of the pump. Led is connected with the input shaft. A sun gear connected with the output shaft and the shaft of the motor. A check valve is installed between the suction and pressure lines variable volume hydraulic transmission and connected the entrance to the suction pipe. This embodiment of the hydraulic transmission improves the efficiency. 3 Il.

The invention relates to hydromechanical transmissions and can be used in machines that need stepless change gear ratio of the transmission from up to 1.

Known inertial hydromechanical transmission, comprising a housing, input and output shafts, the pulse mechanism of the planetary type comprising a sun gear directly connected with the input shaft drove defined on the housing, and check valves (SU 1028924 A (Lipetsk Polytechnic Institute), 15.07.1983, F 16 H 47/04, 5 sheets), adopted for the prototype.

For reasons that impede the achievement of specified following technical result when using the known inertial hydromechanical transmission, adopted for the prototype, is that in the known transmission on the output shaft is transmitted to only the positive momentum of the inertial moment of the impulse mechanism, and a negative pulse is used to disperse drove pulse mechanism and associated rotating parts of a drive motor that is causing the increase of the weight of the cargo units and dimensions of the impulse mechanism in comparison with the proposed inertial transmission, transmitting to the output shaft both momentum moment of inertia. In addition, transformation of time in the known inertial hydromechanical transmission occurs with rupture of the power flow, which leads to a high level of dynamic load links in the known transmission, unlike the proposed inertial hydromechanical transmission, in which the transformation point without disrupting the power flow and there is no rerun of gaps in the pulse meatout in reducing the mass of the cargo and the dimensions of the impulse mechanism (this also reduces the load on the supports unbalanced parts of the impulse mechanism), while maintaining the average value of the inertia torque on the output shaft and the same frequency of rotation of the input shaft of the transmission. Also reduced the overall level dynamic load inertia hydromechanical transmission as a result of structural changes in the business cycle transmission and bridge the gap of power flow at transformation time.

The technical result is expressed in reduction of the overall dimensions of the impulse mechanism, reducing the dynamic loads on the supports satellites pulse mechanism and links inertial transfer and bridging the gap of power flow at transformation time.

This technical result in the implementation of the invention is achieved in that in the known inertial hydromechanical transmission, comprising a housing, input and output shafts, the pulse mechanism of the planetary type comprising a sun gear directly connected with the input shaft and drove satellites with unbalanced loads, adjustable volume hydraulic transmission, a pump and a hydraulic motor which is fixed on the housing, and check valves, impulse mechanism of the planetary type has a crown gear, which is associated shaft us yuusei and pressure pipelines variable volume hydraulic transmission and connected the entrance to the suction pipe.

The transformation of time in the proposed inertial hydromechanical transmission as follows. The positive impulse of the moment, i.e. coincident with the direction of rotation of the engine, perceived the sun gear and is transmitted to the output shaft mechanically. The impulses of the moment, perceived Sunny and crown gear, are in antiphase. Therefore, instead of the negative pulse appearing on the sun gear, used positive perceived a crown gear and transmitted to the output shaft by volume hydraulic transmission.

In Fig. 1 shows a kinematic diagram of the transmission of Fig. 2 and 3 are diagrams of the movement of the unbalanced link.

Inertial hydro-mechanical transmission includes a housing 1, input 2 and output shafts, the pulse mechanism 4 of the planetary type, carrier 5 which is connected directly with the input shaft 2, the sun gear 6 connected with the output shaft 3, the crown gear 7, is also associated with the output shaft 3, but by means of an adjustable volume hydraulic transmission 8, the pump 9 and the hydraulic motor 10 which is fixed on the housing 1, and their shafts are connected by gears with a crown gear 7 and you is that a check valve 11, connected the entrance to the suction pipe. Satellites 12 pulse mechanism 4 is equipped with unbalanced loads 13.

The transmit operation is carried out as follows. During the rotation of the input shaft 2, unbalanced satellites 12 obkatyvalisj on the sun gear 6 as it rotates slower than the input shaft 2, or stationary. The rotation of the satellites 12 relative to the carrier 5 is characterized by somewhat uneven. At the position of the load 13 in the right half-plane with respect to the line OO1(Fig. 2), the satellite 12 slows down its rotation relative to the carrier 5 as a result of inertial forces PCBthat affects the shoulder hiand creates a moment Mand= PCBhidirected oppositely to the rotation of the satellite 12.

Located in engagement with the satellite 12 6 solar and crown 7 gear also change its speed: the speed of the sun gear is increased, and the crown decreases. This is due to the fact that the inertial moments of the satellites 12 are formed on the sun gear 6 and form the output torque of the pulse mechanism 4, which coincides with the direction of rotation of the sun gear 6 and the carrier 5. Volumetric who was above, the pump 9 and the hydraulic motor 10 volume hydraulic transmission are connected by gears with a crown gear 7 and the output shaft 3, respectively. Under the above described change speed links impulse mechanism 4 also change the speed of rotation of the shafts of the pump and motor speed, and hence the feed pump 9 is reduced, and the consumption of the motor 10 increases. These conditions result in the treatment volume hydraulic transmission (hydraulic motor operates as a pump and the pump as a hydraulic motor), and the transfer time can be done through a volumetric hydraulic transmission in the reverse direction from the output shaft 3 of the crown gear 7. To prevent this phenomenon, between the suction and pressure lines a check valve 11, which compensates the decrease of the feed pump, perepiska working fluid from the suction pipe pressure pump feed pump feed not shown) to the input of the motor 10.

Thus, when the position of the load 13 in the right half-plane with respect to the line OO1(Fig. 2), the output of the inertial moment of the impulse mechanism 4 is transmitted to the sun gear 6 to the output shaft 3 by mechanical and hydraulic machines 9 and 10 are not casemated in the left half-plane with respect to the line OO1(Fig. 3), the satellite 12 increases the speed of its rotation relative to the carrier 5 as a result of inertial forces PCBthat affects the shoulder hiand creates a moment Mand= PCBhiaimed in the direction of rotation of the satellite 12. Located in engagement with the satellite 12 6 solar and crown 7 gear also change its speed: the speed of the sun gear is reduced, and the crown increases. Correspondingly change the speed of rotation of both hydraulic machines, therefore, the pump flow increases, and the consumption of the motor is reduced. When the flow becomes equal to the flow rate, the valve 11 is closed and three-dimensional hydraulic transmission 8 begins to transmit the inertial moment of the impulse mechanism 4 with the crown gear 7 on the output shaft 3. The filing of the pump 9 will exceed the cost of the motor 10, this difference increases in direct proportion to the pressure in the pressure line and is a volumetric leak in the pumping nodes of the hydraulic machine.

At the intersection of the load 13 direct PO1(Fig. 2) inertial moment again begins to be transmitted to the output shaft mechanically.

To ensure the normal functioning of the volumetric midwicket from the rotation speed of the input 2 and output shaft 3 of the transmission. Configure the system must provide a positive value of the force P (Fig. 2 and 3) the impact of unbalanced satellite 12 to the sun gear 6 when the inertial moment of inertia of the transmission 8. Power P should be close to zero when sending a negative pulse time to avoid overloading the drive motor, but at the same time must be of sufficient magnitude to prevent the relaying of gaps in the pulse mechanism 4, to ensure continuity of power flow and reduce noise during operation of the transmission.

The advantage of the invention is to reduce the weight of the cargo and the dimensions of the impulse mechanism (this also reduces the load on the supports unbalanced parts of the impulse mechanism), while maintaining the average value of the inertia torque on the output shaft and the same frequency of rotation of the input shaft of the transmission. Also reduced the overall level dynamic load inertia hydromechanical transmission as a result of structural changes in the business cycle transmission and bridge the gap of power flow at transformation time.

Inertial hydromechanical transmission, comprising a housing, input and output shafts, impulsy and satellites with unbalanced loads, adjustable volumetric hydraulic transmission, a pump and a hydraulic motor which is fixed on the housing, and a check valve, wherein the switching mechanism of the planetary type has a crown gear, which is connected to the pump shaft, the sun gear and the shaft of the motor associated with the output shaft, and a check valve is installed between the suction and pressure lines variable volume hydraulic transmission and connected the entrance to the suction pipe.

 

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FIELD: mechanical engineering.

SUBSTANCE: transmission comprises housing (1), axially aligned driving (2) and driven (3) shafts, driving (4) and driven (5) central gear wheels, central conical thrust gear wheel (10), carrier (6) with radial axles provided with main satellites (7) and (8) and additional satellites (9), bearing shaft (11) with two cylindrical gear wheels (12) and (13), and intermediate shaft (16). Driving wheel (4), driven wheel (5), and two main satellites (7) and (8) are made of cylindrical gear wheels. Driving wheel (4) and driven wheel (5) are arranged on opposite sides of radial axles of carrier (6). The two wheels of main satellites (7) and (8) are rigidly interconnected through shaft (17) of main satellites to form a single unit. The unit is mounted for permitting rotation on one of the axles of carrier (6) parallel to the axis of the transmission.

EFFECT: simplified design and reduced labor consumption in manufacturing.

5 cl, 1 dwg

FIELD: mechanical engineering.

SUBSTANCE: transmission comprises housing (14), axially aligned input (1) and output (2) shafts, central conical driving (3) and driven (4) gear wheels, carrier (5) with radial axles and satellites made of wheels (6) and (7), basic, additional (8), and auxiliary (9) satellites which are in engagement with driving (3), driven (4) and additional bearing (11) and auxiliary bearing (10) central conical gear wheels, respectively. Additional (11) and auxiliary (10) bearing wheels are mounted on additional (12) and auxiliary (15) hollow intermediate shafts mounted coaxially with respect to input (1) and output (2) shafts, respectively, and connected with them through drives made of gear wheels and shafts (13) and (16).

EFFECT: enhanced efficiency.

7 cl, 1 dwg

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