The invention relates to a generic hydraulic controller having at least one input for a hydraulic fluid for controlling the speed of a hydraulic pump driven by an internal combustion engine, and the use of the controller.
Today, hydraulic systems are applied in multiple ways for providing large forces, for example for operating tools. Particularly tools in rescue and salvage technology, such as spreaders, presses or shears, also require the mobility of such hydraulic systems. As normally there is no power supply available at these various and undefined sites of operation, the mechanical drive of the pumps of the hydraulic systems also has to be performed by mobile drives, such as, for example, by internal combustion engines or battery-driven electric motors (DE-9412147-U).
However, especially in the case of mobile systems, high energy efficiency may be important because owing to circumstances the energy carriers used may be available only in a highly restricted manner at the site of operation. Further, when assembling the hydraulic systems and/or connecting the respective hydraulic tools to the hydraulic system, an assembly or connection as quick and simple as possible is often desired because every additionally required hand movement takes time and/or harbors other sources of errors. In rescue service in particular, there is often no time or capacity to provide for an especially efficient or low-emission operation of the rescue device. In addition, the hydraulic pump is controlled by the connected hydraulic tool in a sense that upon its actuation, the drive is raised from idle running to higher speeds.
In the prior art, this is caused by an electric switch provided on the tool (DE-9412147-U) that, however, has to be connected to the motor via a separate electric line which, however, is not desired.
In the prior art, a hydraulic controller having at least one input for a hydraulic fluid for controlling the speed of a hydraulic pump driven by an internal combustion engine has also been previously used in which the deflection of a piston, which is floatingly supported to some extent, effected by the flow of the hydraulic fluid is obtained by an electric proximity switch whereby an electric signal is output to the drive control. Thus, the speed of the internal combustion engine is changed by means of an electric servo motor via a carburetor provided on the former. Neither the failure-prone proximity switch nor the additional servo motor on the carburetor are particularly preferred in rescue because they make the devices unnecessarily complicated and are not always sufficiently robust for the tough use in emergencies.
Furthermore, the mobile hydraulic aggregates usually have at least two mutually independent hydraulic circuits. If all of these hydraulic circuits are also to be driven, at least two further disclosed controllers are required which is even less desirable.
Therefore, it is the object of the invention to provide an enhanced controller particularly suited for the operation of such pumps that have at least two mutually independent hydraulic circuits.
According to the invention, this object is achieved in a generic hydraulic controller having at least one input for a hydraulic fluid for controlling the speed of a hydraulic pump driven by an internal combustion engine by the fact that the controller has at least two inputs, that at least two pressure chambers each connected to one of the inputs are provided, that each of the same has a piston displaceable under pressure from a rest position (
When the pistons are in the rest position, the end of the connected rod or pull makes the internal combustion engine run idle. If due to the operation of one of the at least two or of two connected tools the pressure of the hydraulic fluid increases, the one or both pistons are moved from the rest position into the switched position. Consequently, the end of the piston or the pull is also moved and effects the increase to the maximum speed of the internal combustion engine from the idling cycle thereof and thus also for a higher power output of the hydraulic pump driven by this internal combustion engine. In a manner of speaking, the hydraulics is speeded up without the need of a separate, for example electric, line from the tool to the internal combustion engine. When the tool is no longer operated, the pressure drops and the piston is returned to its rest position while at the same time the end of the rod or pull is moved back whereby the internal combustion engine is returned to the idling cycle.
Thus, according to the teaching of the invention, it is advantageously possible in any case to control two tools simultaneously connected to correspondingly adapted pumps by a single inventive controller; it works like an OR element having a mechanical output, which element is fluidically driven at the input side.
Suitably, the hydraulic pump, the intake side and pressure side of which are connected to each other via a return or flow in the form of hydraulic conduits, can be connected to a hydraulic tool operable via a hand switch of a valve, which valve preferably has a switching position connecting the flow to the return wherein the hydraulic pump driven by the drive circulates the hydraulic fluid in the idling cycle of the drive from the intake side to the pressure side to that of the pump.
The controller is particularly easily designed if the pull of the controller is formed as a Bowden cable and if a drive control connected to the end of the rod or the pull is provided for the drive advantageously formed as a carburetor of the internal combustion engine.
Further advantageous embodiments and developments of the invention are described hereinafter.
Preferred embodiments of the invention will be explained in more detail below with reference to the drawings, wherein:
In this case, a controller 30 for measuring the pressure of the hydraulic fluid 400 is inserted in each of the at least two pressure-side terminals 12 of the pump 10. The hydraulic pump, the intake side 11 and pressure side 12 of which are connected via a return 51 or flow 52 in the form of hydraulic conduits to the hydraulic tool 12 operable via a hand switch 610 of a valve 600, is disposed between the controller 30 and the tank 40 taking up the hydraulic fluid and driven by the drive 20 designed as an internal combustion engine M.
Furthermore, the controller 30 is connected to a drive control 21 designed as a carburetor via a Bowden cable 35 whereby it is possible to control the speed of the drive 20. The drive 20 provides a mechanical drive performance to the pump 10 by means of a power transmission 22, such as, for example, a shaft. The drive control 21 adjusts the driving performance of the drive 20 in a manner controlled by the controller 30.
The valve 600 has a switching position 601 connecting the flow 52 to the return 51 in which the hydraulic pump 10 driven by the drive 20 circulates the hydraulic fluid in the idling cycle of the drive from the intake side 11 to the pressure side 12 into the housing of the pump 10. The tool 60 is provided with a doubly acting piston/cylinder arrangement 620 comprising a proper piston 624 and a piston having a piston rod 623 as well as a cutting tool 630. The pressure side 12 of the pump 10 is connected to the hydraulic tool 60 via the flow 52, and the intake side 11 of the pump is connected to the hydraulic tool via the return 51. Detachable couplings 71, 72 and 640 may be provided on the side of the hydraulic system 4 and/or on the side of the hydraulic tool 60 in order to enable a tool change.
The valve 600, which can be adjusted via a mechanical, manual or electrical actuator 610 from outside, furthermore has a first valve position 601, a second valve position 602 and a third valve position 603. In the second valve position 602, the valve 600 connects the flow 52 and thus the pressure side 12 of the pump 10 via the conduit 621 to the cylinder chamber, and connects the return 51 and thus the intake side 11 of the pump to the piston rod chamber via the conduit 622. In this condition, the pump 10 delivers hydraulic fluid 400 to the cylinder chamber whereby the piston rod 623 is extended and the tool 60 correspondingly operated.
In the third valve position 603, the valve 600 connects the flow 52 and thus the pressure side 12 of the pump 10 to the piston rod chamber via the conduit 622, and connects the return 51 and thus the intake side 11 of the pump to the cylinder chamber via the conduit 621. In this condition, the pump 10 delivers hydraulic fluid 400 to the piston rod chamber, whereby the hydraulic tool 60 is moved in a reverse direction.
Both in the second and the third valve position 602 and 603, respectively, the hydraulic fluid 400 is supplementarily delivered from the tank 40. This means that during the operation of the hydraulic tool 60 or while the hydraulic tool 60 performs work, the speed of the drive 20 is advantageously increased automatically to maximum speed via the position switch and the drive control 21 in comparison to the idle speed.
Furthermore, in the first valve position 601 the valve 600 connects the flow 52 to the return 51 and thus enables a circulation of the hydraulic fluid 400.
The proper controller 30 is illustrated in more detail in
If the pistons 313, 323 are in the rest position, the end 34 of the connected Bowden cable 35 makes the internal combustion engine M run idle. If due to the operation of one of the two connected tools 60 the pressure of the hydraulic fluid 400 increases, the one piston 313 of the two pistons 313, 323 is displaced from the rest position (
The piston rods 311, 321 of the controller 30 extend into a separate cylinder-shaped chamber 318, 328 delimited by the pressure chamber 310, 320 and accommodating the springs 312, 322 and abut the rear bottom of a cup-shaped piston 319, 329. One end of the spring 312, 322 abuts the base of the cup-shaped piston 391, 329 opposite this rear bottom.
In this case in the controller 30, the end 34 of the Bowden cable 34 extends into the movement path of each cup-shaped piston 319, 329 and is displaced by the latter when it moves in the switched position parallel thereto in the sense of an operation of the carburetor 21 as drive control of the internal combustion engine M or 20, whereby the latter is raised from idle speed to its maximum speed. Thus, the piston rod 311, 321 in the switched position indirectly engages at the end 34 of the rod or the pull 35 via the cup-shaped piston 319, 329 and operates the same and thus the carburetor as drive control 21 of the internal combustion engine.
For the purpose of adjustment, the other end of the spring 312, 322 is supported in likewise cup-shaped piston 402 which can be adjusted from outside via an adjusting screw 401. In this manner it is possible to adjust the initial tension of the spring as well as the adjustment range of the Bowden cable and thus the drive control.
Number | Date | Country | Kind |
---|---|---|---|
10 2008 013 849.5 | Mar 2008 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
---|---|---|---|---|
PCT/EP2009/000463 | 1/25/2009 | WO | 00 | 8/6/2010 |