[0001]DEVICE FOR ADJUSTING THE STROKE VOLUME OF HYDRAULIC PISTON MACHINES
[0002]
[0003]

[0004] The invention concerns a device for adjusting the swept volume of hydraulic
piston machines of the type defined In the preamble of claim 1.
[0006]

[0006] Hydraulic piston machines are utilized, for example, in hydrostatic mechanical
power split transmissions for the hydraulic power branch to continuously vary the transmission ratio. Hydraulic piston machines need for this purpose adjusting devices, by means of which the swept volume of the piston machines is adjusted.

[0007] DE 42 06 023 A1 discloses a continuously variable hydrostatic mechanical
power split transmission comprising hydraulic piston machines and adjusting devices, by means of which the piston machines can be continuously adjusted. The adjusting device comprises control elements, by means of which the piston machines can be controlled. In order to protect the system from overload, the adjusting device is provided with a pressure relief valve, by means of which the maximum pressure can be limited. When the pressure relief valve is activated, the energy Is converted Into heat, which must be released by means of a radiator.
[0008]

[0009] The object of the Invention is to create a device for adjusting the swept
volume of hydraulic piston machines, which is of simple design and protects the
system from overheating.

[0010] The object is attained with a generic adjusting device, which also has the
characteristics of the main claim.

[0011] The adjusting device comprises a first and a second piston machine
configured in transverse axis design. Piston machines of transverse axis design are
characterized by their very good overall efficiencies. Both piston machines are
positioned adjacent to each other and comprise a common component, a so-called joke, by means of which the swept volume of both piston machines can be jointly adjusted. The piston machines comprise working lines, via which the two piston machines are mutually connected. The piston machines form in this way a so-called closed circuit. The common component for adjusting the swept volume of hydraulic piston machines is arranged in such a manner that the first hydraulic piston machine is adjusted to a small or zero swept volume in the first position of the common component and the second hydraulic piston machine Is adjusted to a large or maximum swept volume. The first hydraulic piston machine functions as a pump, for example, and conveys the pressurizing medium toward the second piston machine, which functions as a motor In this operating state. In another operating state, the second piston machine functions as a pump and the first piston machine functions as a motor. If the common component is adjusted from its first position In direction toward the second position, the swept volume of the firflt piston machine, for example the pump, is increased and the swept volume of the second piston machine, for example the motor, is decreased at the same time. When the common component Is operated In Its second position, the first piston machine is at its maximum swept volume and conveys thus a maximum volume flow when it is operated as a pump, while the second piston machine is at its minimum swept volume and generates thus a very high output speed when it is operated as a motor. The common component can be adjusted, for example by means of a hydraulic cylinder, from a first position in direction toward the second position or from a second position In direction toward a first position, in this way, a driver of a vehicle can fonvard the driver's request to the devices for adjusting the common component by means of a manual input device, for example, by means of an accelerator pedal, which manually or electrically controls a valve, whereby the common component is adjusted In dependence upon the driver's request and consequently in dependence of the actuation of the manual input. If the driver requests a higher output speed in the second piston machine then the common component is adjusted In direction toward the second position. If the driver requests a k)wer output speed, then the common component is adjusted in direction toward the first position. If there in an increase in driving resistance, it is possible that this may cause a permissible
pressure in the working lines between the first and second piston machines to be exceeded.

[0012] According to the invention, the common component is adjusted in direction
toward the first position when a predefined pressure level is exceeded, whereby the first piston machine, for example the pump, is adjusted in direction toward a smaller swept volume, and the second piston machine, for example the motor, is adjusted in direction toward a larger swept volume, whereby the pressure in the working lines drops. This predefined pressure level Is below a maximum permissible pressure level at which pressure relief valves open, whereby overheating of the system is prevented, since the energy is not converted into heat via the pressure relief valves.

[0013] Another embodiment of the invention provides the option of superimposing
the current pressure level in the working lines on another Input by means of another manual input, whereby the common component is adjusted in direction toward the first position already at a low pressure level. In this way, it is possible to continuously variably influence the maximum permissible pressure. If a simply operating hydraulic cylinder is utilized, which is adjusted by means of a spring in its starting position and Is connected to the common component in its first position In this starting position, this makes possible to move the common component from the first position In direction toward the second position by pressurizing this hydraulic cylinder with the pressure of a pressurizing medium source. If the hydraulic cylinder Is connected to a pressurizing medium reservoir, the common component moves back in direction toward the first position. The manual input device can consist of another valve, which connects the pressurizing medium cylinder to the pressurizing medium source or to the pressurizing medium reservoir in dependence upon the driver's request, and thus determines the position of the common component, whereby the output speed of the piston machine Is established. A valve Is arranged between this additional valve and the hydraulic cylinder, which connects the pressurizing medium coming from the additional valve with the hydraulic cylinder in its basic position and blocks the pressurizing medium coming from the additional valve and connects the hydraulic cylinder to the pressurizing medium reservoir. The additional position Is activated when a pressure level that is above a predefined pressure level is detected in the working lines.

[0014] It is thus possible to control the common component via the additional valve
in the sense of a rotational speed control and to limit the pressure level via the valve, which is positioned between the hydraulic cylinder and the additional valve, by adjusting the common component in direction toward the first position.
[0015]

[0016] Additional features are disclosed in more detail below with reference to the
figures. In the drawings:

[0017] Fig. 1 shows a hydraulics diagram of the adjusting device; and

[0018] Fig. 2 shows a kinematic diagram of a hydrostatic mechanical power split
transmission.
[0019]
[0020] Fig. 1;

[0021] The adjusting device comprises a first piston machine 1 in transverse axis
design, which functions, for example, as a pump, in an operating condition, and a second piston machine 2 in transverse axis design, which functions, for example, as a motor, in an operating condition. The first piston machine 1 and the second piston machine 2 are connected to each other via working lines 3. The swept volume of the first piston machine 1 and the second piston machine 2 is adjusted via a common component 4. A spring-loaded hydraulic cylinder 5 is connected to the common component 4. When the hydraulic cylinder 5 Is in a non-pressurized state, the first piston machine Is adjusted to zero swept volume, which means that the first piston machine 1 does not convey any pressurizing medium when it is driven. The second piston machine 2 Is adjusted to maximum swept volume when the hydraulic cylinder 5 Is in its non-pressurized state. A pressurizing medium source 6 moves the pressurizing medium from a pressurizing medium reservoir 7 Into the line 8, If the common component 4 must be adjusted from its first position in direction toward the second position while the hydraulic cylinder 6 is in its non-pressurized state, then the valve 9 of the manual input device 10 is rerouted in such a manner that pressurizing medium flows from the line 8 into the tine 11. If the valve 12 is in its basic position, the pressurizing medium then reaches the hydraulic cylinder 5 from the line 11 via the line 13 and adjusts the common component 4 in direction toward the second position, whereby the swept volume of the first piston machine 1 is increased, the swept volume of the second piston machine 1 is reduced, and pressurizing medium is conveyed via the working lines 3 from the first piston machine 1 to the second piston machine 2. The valve 12 Is held in its basic position via the spring 14, wherein the higher pressure in the working lines 3 reaches the circular ring area 17 via the shuttle valve 15 via the tine 16. The circular ring area 17 is designed In such a way with the spring 14, that the valve 12 is rerouted to Its second position below the opening level of the pressure limiting valves 18, whereby the pressurizing medium of line 11 is prevented from further reaching the hydraulic cylinder 5 and connecting the hydraulic cylinder 5 to the pressurizing medium reservoir 7, whereby the common component 4 Is displaced in direction toward the first position, whereby the pressure in the working lines 3 is again reduced. The pressure limiting valves 18 remain closed, whereby the drive is protected from overheating, in that the valve 12 is rerouted below the pressure level of the pressure limiting valves 18. Once the pressure in the working lines 3 has again dropped, the valve 12 is again reversed to its original position, and the pressurizing medium of line 11 can again reach the hydraulic cylinder 5. The valve 12 is provided with a circular area 19, which is connected to the line 20. When the valve 21 is activated, pressurizing medium from, the line 8 reaches the circular area 19 via the line 20 via the valve 21 of the additional manual input device 22. This pressure, which acts on the circular area 19, generates a force that acts on the spring 14 of the valve 12, which is added to the force resulting from the pressure of line 16, which acts on the circular ring area 17, The pressure of the line 8 can be superimposed In this way on the pressure of line 16, whereby the switchover point of the valve 12 can be continuously variably adjusted and thus in dependence upon the additional device for manual input 22. The preferred surface ratio between the circular area 19 and the circular ring area 17 is 3:100, whereby a force can be applied on the valve 12 at a maximum control pressure of, for example, 16 bar, which will correspond to a pressure of 533 bar acting on the circular ring area 17. The continuously variable limiting of the high pressure can thus create a continuously variable traction adjustment if the adjusting device is utilized in a mobile vehicle. The manual input device 10 can thus create a continuously variable speed adjustment, A continuously variable power adjustment can be realized by combining the continuously variable speed adjustment with the continuously variable traction adjustment. If the adjusting device is utilized in a transmission, the pressurizing medium source 6 supplies the operating devices 23 . and the clutches 24 in addition to the adjusting devices.

[0022] Fig. 2:

[0023] The hydrostatic mechanical power split transmission is provided with a first
piston machine 1 and a second piston machine 2 of the kind represented in Fig. 1, whose swept volume can be adjusted via a common component 4. The output 25 can be connected to the drive 28 via a clutch for forward travel 26 or a clutch for reverse travel 27. The operating ranges may be shifted by means of a clutch 29 and a clutch 30. The summation gear unit 31 sums the mechanical and the hydraulic power branch.

Reference Numerals:
1 First piston machine
2 Second piston machine
3 Working line
4 Common component
5 Hydraulic cylinder
6 Pressurizing medium source
7 Pressurizing medium reservoir
8 Line
9 Valve
10 Manual input device
11 Line
12 Valve
13 Line
14 Spring
15 Shuttle valve
18 Line
17 Circular ring area
18 Pressure limiting valve
19 Circular area
20 Line
21 Valve
22 Additional manual input device
23 Operating device
24 Clutch
25 Output
26 Clutch for forward travel
27 Clutch for reverse travel
28 Input
29 Clutch
30 Clutch
31 Summation gear

CLAIMS

1-9. (CANCELED)

1.(NEW) A device for adjusting a swept volume of a hydraulic piston machine of a transverse axis design in which a first piston machine (1) being arranged adjacent to a second piston machine (2), both the first and the second piston machines having working lines (3) via which the first and the second piston machines being hydraulically connected to one another, and the first and the second piston machines being provided with adjustable axles which are connected, via a common component (4), such that the adjustable axles are simultaneously adjusted by movement of the common component (4);

wherein, in the first position of the common component (4), the first hydraulic piston machine (1) is adjusted to one of a small and a zero swept volume and the second hydraulic piston machine (2) is adjusted to one of a large and a maximum swept volume, and, in a second position of the common component (4), the first hydraulic piston machine (1) is adjusted to one of a large and a maximum swept volume and the second hydraulic piston machine (2) is adjusted to one of a small and a minimum swept volume with means for adjusting (5) of the common component (4);

the common component (4) is adjusted .depending on an input dependent upon a first manual Input device (10), in one of a direction toward the first position and in a direct toward the second position;

the common component (4) is adjusted, if a predefined pressure is exceed in one of the working lines (3), in the direction toward the first position independently of the manual input (10);

an additional manual input device (22) is provided; and

the common component (4) is adjusted, when the additional manual input device (22) is actuated by dependence upon a pressure in the working lines (3) and by dependence upon the actuation of the additional manual input device (22), in the direction toward the first position so that the common component (4) is adjusted in the direction toward a first position similar to that with an unactuated additional manual input device (22) when the actuation of the first manual input device (10) is unchanged and the additional manual input device (22) is actuated.

2. (NEW) The adjusting device of claim w, wherein a means for adjusting the common component (4) is configured as a hydraulic cylinder which, in a basic position, retains the common component (4) in the first position and. when pressurized, adjusts the common component (4) in the direction toward the second position.

3. (NEW) The adjusting device of claim 44-, wherein a valve (12) is arranged upstream of the hydraulic cylinder (5), the hydraulic cylinder (5) is connectable, via a basic position of the valve (12), by dependence upon the manual input device (10) one of to a pressurizing medium source (6) and a pressurizing medium reservoir (7), and, in an additional position, the valve (12) connects the hydraulic cylinder (5) to a pressurizing medium reservoir (7) whereby the common component (4) is adjusted, independently from the manual input (10), in the direction toward the first position.

4. (NEW) The adjusting device of claim 'B, wherein a pressure of one of the working lines (3) acts on the valve (12) in order to adjust the valve (12) from the basic position to the additional position.

5. (NEW) The adjusting device of claim 1, wherein an additional pressure, which can be adjusted by the additional manual input device (22), is superimposed on the pressure of the working lines (3), which acts on the valve (12) so that the valve (12) is already rerouted into the additional position when the working lines (3) have a lower pressure during the superimposition of the additional pressure.

6. (NEW) The adjusting device of claim 1 wherein the valve (12) is provided with a first pressurizable area (19) and a second pressurizable area (17) and can be adjusted against force of a spring (14), and the valve (12) Is adjusted from the basic position to the additional position, against the force of the spring (14), when pressure acts on at least one of the first and the second pressurizable areas (17,19), the first area (19) is connectable to a pressurizing medium from a pressurizing medium source (6) via the additional manual input device (22), and the second area (17) is connectable to the pressurizing medium from the working line (3), which has the higher pressure.

7. (NEW) The adjusting device of claim 6 wherein the first pressurizable area (19) is larger than the pressurizable area area (17).

8. (NEW) The adjusting device of claim i©-, wherein the first piston machine (1) and the second piston machine (2) are arranged in a hydrostatic mechanical power split transmission with a hydraulic and a mechanical branch, and the hydraulic branch is connected to the first piston machine (1) and the second piston machine (2).