Automotive drive

FIELD: transport.

SUBSTANCE: invention relates to transmission of vehicle with independent mechanical drive and hydraulic drive. Vehicle drive comprises engine (1), mechanical main transmission line (2) and hydraulic extra line (3). Transmission extra hydraulic line (3) is provided with hydraulic circuit (11) with controlled hydrostatic pump (7) and hydromotors (9, 10) in wheels not driven by transmission main mechanical line. Pump (7) is arranged at engine (1) extra power takeoff shaft (8) and engaged therewith by uncoupling linkage (17).

EFFECT: higher efficiency of transmission.

10 cl, 3 dwg

 

The present invention relates to a drive unit for a vehicle according to the restrictive part of paragraph 1 of the claims.

In the publication DE4110161A1 industry described drive unit of the vehicle engine, automatic main line transmission and additional hydraulic line of transmission. The engine is represented as an internal combustion engine, through which the main mechanical transmission drives the rear wheels of the car. Hydraulic additional transmission line includes controlled hydrostatic volumetric pump and a hydraulic motor, which are connected by a hydraulic circuit. The pump through the transmission is continuously connected with extra weaning engine power. The pump is designed as adjustable Neklinovskiy pump. In comparison with the described object of the present invention is to offer efficient and convenient driving device for vehicles.

According to the invention the task is solved by a drive unit, having the characteristics described in paragraph 1 of the formula of the claims.

According to the invention between an adjustable hydrostatic pump and extra weaning power driven clutch. The pump is connected via the clutch with optional PTO with the ability when�of reason in motion, so it is possible to transmit power by an additional hydraulic line of transmission to the hydraulic motors associated with the wheels of the car, not driven mechanical main transmission line. The connection between the pump and extra power with the possibility of propulsion can be divided by the clutch so that the pump is not connected all the time with extra power with the possibility of propulsion. The pump you can connect and disconnect using the clutch and run only in case of need.

If the additional transmission line is disconnected, the clutch is also opened, and the pump is not driven, which saves power and provides a high efficiency drive unit.

In appropriate improved embodiment of the transmission device, the clutch is designed as a claw clutch.

The Cam clutch creates a kinematic relationship between the additional power of the engine and the pump by a geometric circuit, so that the clutch does not occur additional power loss. Cam clutch, in particular, inexpensive to manufacture, and with the technical use of durable and wears poorly.

In appropriate improved version of the implementation of the drive device� grip is made as a clutch with synchronization.

Clutch with synchronization creates a kinematic relationship between the additional power of the engine and the pump by a geometric circuit, so that the clutch does not occur additional power loss. Synchronization facilitates the connection of the clutch when connecting additional hydraulic line of transmission and increases the driving comfort of the vehicle.

Depending on the speed range of the engine and the speed range of the pump between the additional power of the engine and the pump can be positioned transmission. Coupling the clutch with synchronization it is recommended to place on the transmission, the transmission includes an intermediate wheel, which via a coupling clutch with synchronization possible to result in a working connection with the shaft.

In appropriate improved embodiment of the transmission device, the pump is designed as an axial piston pump.

Axial piston machines are available at any power level, and power loss them small, so that additional hydraulic line of transmission is highly efficient.

In appropriate improved embodiment of the transmission device in the hydraulic circuit has a flushing pump.

Flushing the pump can be actuated, in particular, fur�technical way the engine, however, you can also use a flushing pump with electric. The flushing pump delivers the hydraulic circuit, the working fluid from the reservoir, and the hydraulic circuit occurs, the hydraulic volume flow, in particular, through an adjustable hydrostatic pump. Mentioned hydraulic volumetric flow allows you to lead an adjustable hydrostatic pump in rotation by a broken clutch. Flushing the pump can be in particular designed as a vane pump with constant power pumping.

In appropriate improved embodiment of the transmission device between the additional power of the engine and the pump is a torsion damper (torsional vibration damper). Torsional damper dampens the rotational fluctuation of the engine, via the auxiliary power transmitted to the pump, and thus improves the service life and operational durability for more power.

When implementing the method of operation described above, a drive unit of the vehicle circuit for coupling between the additional power of the engine and the pump with clutch open the input element creates a hydraulic volumetric flow. Supply element located�Agueda in the hydraulic circuit and delivers the specified hydraulic volume flow in the hydraulic circuit, what is the volumetric flow through the pump. With clutch open, the pump is not associated with additional PTO back in motion, so that the volumetric flow causes the pump in rotation in such a way that the difference of rotation speed (differential speed) of the clutch is reduced.

With the closure of the clutch differential rotation speed on the clutch is reduced, while in the closed clutch slippage does not stop completely, and the coupling elements (couplings) move at the same speed. Because when you open the clutch, the PTO rotates at engine speed of the engine, and the pump basically is at rest and not rotating at all, for clutch must be given to the pump and a corresponding input shaft acceleration. The acceleration pump is supported by the specified hydraulic volumetric flow of the feed element, since the volumetric flow through the pump and drives the pump in motion with an open grip. Volumetric flow accelerates the rotation of the pump so that the differential speed of the clutch is reduced.

In appropriate improved version of the method an adjustable hydrostatic pump set depending on the target value of speed of rotation of the additional selection powerful�STI. Pump power is set so that the volumetric flow rotates the pump with the speed, which reduces the differential speed of rotation between the clutch optional PTO and pump, and the differential speed of rotation depends on speed of rotation of the additional power and the speed of rotation of the pump. In particular, the setting of the pump also depends on the volumetric flow passing through the pump. To configure the pump can, in particular, by controlling or adjusting.

In appropriate improved version of the method specified hydraulic volumetric flow at least partially constructed of a wash pump. The flushing pump is connected to a hydraulic circuit so that the volumetric flow through the pump. Consequently, the flushing pump is partly takes on the role of the feeding unit in the hydraulic circuit.

In appropriate improved version of the method specified hydraulic volumetric flow at least in part generated by the hydraulic motor rotating wheel. A hydraulic motor converts hydraulic wheel volume flow into rotational movement, and rotational movement in a hydraulic volumetric flow. Thus, the rotating wheel with hydraulic motor also� is a supply element in the hydraulic circuit. The rotating wheel of a vehicle traveling may by the hydraulic motor to create hydraulic volume flow flowing through the hydraulic circuit. Volume flow flowing through the pump, at least in part generated by the hydraulic motor. Volume flow generated by the hydraulic motor, can be enhanced volumetric flux created by the flushing pump. In particular, the flushing pump generates only a portion of the volumetric flow and therefore may be small, saving weight and energy. If the volume flow from the hydraulic motors sufficient to accelerate the rotation of the pump, wash the pump should never work out the pumping power, which saves energy and increases the efficiency of the drive unit.

Other embodiments of the invention are clear from the description and drawings. Examples of execution of the invention represented in the drawings in simplified form, as explained in more detail in the following description.

A more detailed explanation of the invention is given by the following examples. While in the drawings:

Fig.1 is a schematic representation of a vehicle with an engine mechanical main line transmission and additional hydraulic line of transmission,

Fig.2 - schematic illustration of the hydrostatic pump, �smeshennogo extra power of the engine.

Figure 1 shows a schematic representation of a drive unit of the vehicle with the engine 1, the mechanical main transmission line 2 and additional hydraulic transmission line 3.

Mechanical main transmission line 2 transmits the stress part of the drive engine via a main drive shaft 5A, the gear unit 4 and the drive shaft 5b on the rear axle 6 of the vehicle. In particular, mechanical main drive line 2 transmits mainly the force of the actuator during normal driving on the road and car corresponds to known technical solutions. Hydraulic additional transmission line 3 is equipped with a hydraulic circuit 11 with an adjustable hydrostatic pump 7 and the hydraulic motors 9, 10 - one on each of the front wheels of the car, not driven mechanical main transmission line. The pump 7 is connected to an optional power outlet 8 of the engine 1. Additional PTO 8 is connected to the engine 1 with the main drive shaft 5A and rotates at a speed proportional. Between the pump 7 and the additional power take-off 8 is the clutch 17. The clutch 17 can divide the pump 7 and the additional power take-off 8.

The pump 7 shows, in particular, in the form of an axial piston machine, which through a swing angle of the pump 7 can of ass�AMB power and the direction of flow. Off additional hydraulic line drive 3 pump 7 does not transmit power to the hydraulic motors 9, 10. Through the tripping (opening) of the clutch 17, the pump 7 is separated from the additional power take-off 8, and the power loss in the pump 7 is absent, while the additional PTO 8 continues to rotate.

Figure 2 shows a schematic representation of a hydrostatic pump 7 is placed on the additional PTO 8 of the engine 1.

Between the pump 7 and the additional power take-off 8 is the transmission 14, which has a freely rotating wheel 16 for extra PTO 8 and is rigidly secured to the wheel 15 on the input shaft of the pump 13. A freely rotating wheel 16 is rigidly (non-rotatably) connected via a coupling 17 with the additional power, the clutch 17 is designed as a claw clutch with a freely rotating wheel and is rigidly secured to the wheel 19 on extra PTO 8 and the sliding sleeve 20. With the clutch closed 17 of the sliding sleeve 20 connects the freely rotating wheel 16 with fixed wheel 19 with geometric circuit.

Between the additional PTO 8 and the pump 7 is a torsion damper (torsional vibration damper) 18. The torsional damper to�vibrations 18 is made as an element of the input shaft of the pump 13. The pump 7 is connected to the hydraulic circuit 11 having a circulating pump 12. The flushing pump 12 delivers the working fluid from the hydraulic reservoir through the valve 22 to the hydraulic circuit 11. The valve 22 is designed as a switching valve with a check valve, so that during operation of the purge pump 7 pump 12 is not exposed to high pressure from the hydraulic circuit 11 to the high pressure pump 7, and may still feeding the working fluid in the hydraulic circuit 11 to the low pressure side of the pump 7. The valve 22 is connected to the hydraulic circuit 11 to the low pressure side of the pump 7 and the connection with the hydraulic circuit 11 to the high pressure pump 7, and the working fluid is fed through the valve 22 only by the connection with the hydraulic circuit 11 to the low pressure side of the pump 7 and the valve 22 closes the connection to the hydraulic circuit 11 to the high pressure pump 7. The flushing pump 12 also serves for the hydraulic circuit of the pump to compensate for leakage and other losses of the working fluid. Via a controllable valve 21 is designed as a switching valve, the hydraulic circuit 11 is connected to a hydraulic tank, and depending on the position of valve 21 connection with a hydraulic reservoir open or closed. TC�pan 21 is connected to the hydraulic circuit 11 to the low pressure side of the pump 7 and the connection with the hydraulic circuit 11 to the high pressure pump 7, and depending on the position of the switching valve 21 opens only one connection and closes the other, or closes both connections. When you open the clutch 17 can on the position of the switching valve 22 and valve 21 to set the direction of the flow of the volumetric flow created by the flushing pump 12, through the pump 7. Volume flow passes from the hydraulic tank through a circulating pump 12, the valve 22, through the pump 7 and through the valve 21 again in the hydraulic tank. The switch position of the valves 22, 21 determines the direction of flow of the volumetric flow through the pump 7. The image is not represented in other standard technical elements of the hydraulic circuit, in particular safety valves (gauge pressure), valves, filters and coolers fluid, as well as their exact connection with the hydraulic circuit 11.

The control unit 25 controls the position of valves 21, 22, other unrepresented valves and hydraulic components. Control unit 25 also regulates the setting of the pump 7 and the position of the sliding clutch 20 in the clutch 17. For this purpose, the control unit 25 processes the signals of the sensors such as the speed sensor 23 for extra PTO 8, the speed sensor 24 on the input shaft of the pump 13 and the other sensors, not represented�s in the drawing. As a substitute of the signal from the speed sensor 23 for extra power 8, you can also use the signal of the rotational speed of the engine 1, since the rotation speed optional PTO 8 is proportional to the speed of rotation of the motor 1.

During normal use on roads transmits drive power of the mechanical main transmission line 2. Hydraulic additional transmission line 3 is disconnected, and the clutch 17 is open so that the pump 7 is separated from the additional power take-off 8. Additional PTO 8 (shaft) rotates continuously at a speed corresponding to such engine, and the pump 7 is basically alone. The valve 21 is opened so that the working fluid flows from the hydraulic circuit 11 in the hydraulic tank and the flushing pump 12 delivers the working fluid from the hydraulic reservoir to the hydraulic circuit 11.

If it becomes necessary to connect a mechanical main transmission line 3 additional hydraulic line drivetrain 2 or pull away only to additional hydraulic lines to transmission, the clutch 17 must be closed. As additional PTO 8 rotates at a certain speed, and the pump 7 is basically resting on the clutch 17 has a differential speed in�of Amenia. The clutch 17 is designed as a claw clutch, and the circuit is possible only at very low differential speeds of rotation on the clutch 17, so that the locking clutch 17 differential speed must be reduced so that the rotation of the pump 7 accelerate.

In order to clutch 17 to accelerate the rotational motion of the pump use the following method. If still open, the clutch 17, the valve 21 is open and the circulating pump 12 delivers the working fluid from the hydraulic reservoir to the hydraulic circuit 11. Valves 21, 22 is switched so that the volumetric flow of hydraulic fluid that is created flushing pump 12, flow through the valve 22, the pump 7 and through the valve 21 again back to the hydraulic tank. The control unit 25 controls the intensity of the pumping of the pump 7, depending on the signal of the rotational speed for extra power and the signal of the rotational speed on the input shaft of the pump 13. For clutch 17 must the rapprochement of the two speeds of rotation, so that the differential speed of rotation on the clutch 17 has gone to zero. Accordingly, the control unit 25 sets the pumping power of the pump 7 so that the pump 7 has been accelerating from the volumetric flow of the flushing pump 12 until such time as the differential rotation speed�I on the clutch 17 is sufficiently small, to enable the clutch 17 to be closed without compromising comfort or manifestations of wear. Depending on the differential speed of rotation of the clutch 17, the control unit 25 instructs the closing of the clutch 17.

When closed, the clutch 17 is closed and valve 21 to the pumping power of the pump 7, which is now driven by the engine 1 is not passed from the hydraulic circuit 11 in the hydraulic tank. Elsewhere, the control unit 25 opens not represented in the drawing, the switching valves that conduct hydraulic circuit 11 via the hydraulic motors 9, 10 in wheels. Due to the closed clutch 17 and the switching valve driving force of the engine 1 is transmitted via the auxiliary power take-off 8, a pump 7, the hydraulic circuit 11 to the hydraulic motors 9, 10 in wheels. Now drive the car by at least partially using additional hydraulic line of transmission.

For disconnection of the clutch control unit 25 adjusts (changes) the pumping power of the pump 7 so that the force with additional PTO 8 are not transmitted to the pump 7, and thus the clutch 17 can be easily disconnected.

Figure 3 is a schematic view of the hydrostatic pump 7 is placed on the additional PTO 8, essentially ID�ntinue figure 2, except in the execution of the clutch 17.

All entered and describes the elements and the legend to figure 3 taken from figure 2, and a repeated explanation is not provided. The same elements also play the same role.

In the illustrated embodiment of the invention, the clutch 17 is made as a clutch 26 with synchronization. Clutch 26 connects the power take-off 8 (flush) with a freely rotating wheel 16, which is available for extra PTO 8 and is part of the transmission 14 from the additional PTO 8 to the input shaft of the pump 13. Clutch 26 is equipped with sync, which promotes the closure of the clutch 17, and the timing by means of friction loss further reduces the differential speed of rotation on the clutch 17 during the circuit. Known from figure 2, the method of closure of the clutch 17 is also used in the circuit shown in figure 3, and the timing of the clutch 26 supports the closure of the clutch 17. The control unit 25 gives the command to shift the clutch 26 to close the clutch 17 is already at somewhat higher differential speed of the clutch 17 than does the control block 25 of figure 2 in relation to the sliding sleeve 20 of a dog coupling.

1. Driving device for vehicle engine (1), mechanical main transmission line (2) and additional hydraulic line of transmission (3), and additional hydraulic line of transmission (3) has a hydraulic circuit (11) with an adjustable hydrostatic pump (7) and actuators (9, 10) associated with the wheels of the car, not driven mechanical main transmission line (2), and an adjustable hydraulic pump (7) can be set in motion by means of additional PTO (8) of the engine (1), characterized in that between the pump (7) and additional PTO (8) has a coupling (17).

2. Driving device according to claim 1, characterized in that the clutch (17) is made in the form of a dog coupling.

3. Driving device according to claim 1, characterized in that the clutch (17) is made in the form of the clutch (17) with synchronization.

4. Driving device according to one of the preceding claims, characterized in that the pump (7) is designed as an axial piston pump.

5. Driving device according to one of claims. 1-3, characterized in that the hydraulic circuit (11) is equipped with a rinse pump (12).

6. Driving device according to one of claims. 1-3, characterized in that between the additional PTO (8) of the engine (1) and the pump (7) has a torsional vibration damper (18).

7. A method of operating a drive Ustra�STV for car, with the engine (1), mechanical main transmission line (2) and additional hydraulic line of transmission (3), and additional hydraulic line of transmission (3) has a hydraulic circuit (11) with an adjustable hydrostatic pump (7) and hydraulic motor (9, 10), and an adjustable hydraulic pump (7) can be set in motion by means of additional PTO (8) of the engine (1), characterized in that for closing the controlled clutch (17) placed between the pump (7) additional PTO (8), if still open, the clutch (17) of the feed element (12) in the hydraulic circuit (11) generates a pump (7) hydraulic volume flow, which drives the pump (7) into rotation so that the differential speed of the clutch (17) is reduced.

8. A method according to claim 7, characterized in that the adjustable hydrostatic pump (7) being adjusted in accordance with the target value of the rotation speed optional PTO (8).

9. A method according to claim 7 or 8, characterized in that the hydraulic volume flow is at least partially constructed of a wash pump (12).

10. A method according to claim 7 or 8, characterized in that the hydraulic volume flow at least in part generated by the hydraulic motor (9, 10) of the rotating wheel.



 

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