Abstract
The invention relates to a radial piston hydraulic motor. The radial piston hydraulic motor comprises a cam ring provided, with a wave-shaped inner surface and radial cylinders provided in the inner part inside the cam ring and pistons that move therein as well as rollers coupled to the pistons so as to follow the inner surface of the cam ring. By the effect of the working pressure of hydraulic oil conveyed to the cylinders, the rollers that are pressed against the inner surface of the cam ring provide a rotating movement of the cam ring and the inner part relative to each other. The hydraulic motor is provided with disengaging members disengaging the rollers coupled to the pistons from contact to the inner surface of the cam ring when the working pressure stops acting in the cylinders for bringing the hydraulic motor into freewheeling. The hydraulic motor is provided with a control coupling which, when the prevailing pressure of hydraulic oil in the working pressure line that leads to the cylinders drops below a specific level, automatically disengages the cylinders from the working pressure line and couples the hydraulic motor into freewheeling.
Claims
1. A radial piston hydraulic motor comprising a cam ring provided with a wave-shaped inner surface and radial cylinders disposed in the inner part inside the cam ring and pistons that move therein as well as rollers coupled to the pistons so as to follow the inner surface of the cam ring in order that, by the effect of the working pressure of hydraulic oil conveyed to the cylinders, the rollers that are pressed against the inner surface of the cam ring provide a rotating movement of the cam ring and the inner part relative to each other, and the hydraulic motor being provided with disengaging members which disengage the rollers coupled to the pistons from contact to the inner surface of the cam ring when the working pressure stops acting in the cylinders for bringing the hydraulic motor into freewheeling, wherein the hydraulic motor is provided with a control coupling which, when the prevailing pressure of hydraulic oil in a working pressure line that leads to the cylinders drops below a specific level, automatically disengages the cylinders from the working pressure line and couples the hydraulic motor into freewheeling.
2. The radial piston hydraulic motor according to claim 1, wherein the control coupling comprises a first valve which is a pressure-controlled valve that is coupled to the working pressure line leading to the cylinders of the hydraulic motor and to a return line provided from the cylinders, respectively, and which is controlled via the working pressure line so that, when the prevailing pressure of hydraulic oil in the working pressure line drops below a specific level, the first valve closes the working pressure line and the return line to the hydraulic motor.
3. The radial piston hydraulic motor according to claim 2, wherein the first valve is a component internal to the hydraulic motor.
4. The radial piston hydraulic motor according to claim 2, wherein the first valve is a component external to the hydraulic motor.
5. The radial piston hydraulic motor according to claim 2, wherein the hydraulic motor comprises a control pressure line, wherein the control coupling of the hydraulic motor comprises a separately operated second valve coupled to the control pressure line that leads to the first valve for forcing a working mode of the hydraulic motor that has been coupled or that is coupling into freewheeling irrespective of the rotating speed or working pressure.
6. The radial piston hydraulic motor according to claim 5, wherein the control pressure line comprises the part, wherein the control coupling of the hydraulic motor further comprises the separately operated third valve coupled to the part of the control pressure line of the first valve for forcing the hydraulic motor from the working mode into freewheeling irrespective of the rotating speed or working pressure.
7. The radial piston hydraulic motor according to claim 2, wherein the hydraulic motor comprises the control pressure line and the control pressure line comprises a part, wherein the control coupling of the hydraulic motor further comprises a separately operated third valve coupled to the part of the control pressure line of the first valve for forcing the hydraulic motor from the working mode into freewheeling irrespective of the rotating speed or working pressure.
8. The radial piston hydraulic motor according to claim 2, wherein the hydraulic motor comprises a case line, an inlet line and an outlet line so that, when the prevailing pressure of hydraulic oil in the working pressure line drops below a specific level, the first valve is arranged to connect, by means of hydraulic oil, the inlet line and the outlet line of the hydraulic motor to each other and to connect the inlet line and the outlet line to the case line of the hydraulic motor through the first valve.
9. The radial piston hydraulic motor according to claim 8, wherein the hydraulic motor comprises a drain line and a tank line, the case line being connected through the hydraulic motor to the drain line which is coupled to the tank line.
10. The radial piston hydraulic motor according to claim 9, wherein the control coupling is provided with the choke through which the first valve is controlled via the working pressure line.
11. The radial piston hydraulic motor according to claim 8, wherein the control coupling is provided with the choke through which the first valve is controlled via the working pressure line.
12. The racial piston hydraulic motor according to claim 2, wherein the control coupling is provided with a choke through which the first valve is controlled via the working pressure line.
13. The radial piston hydraulic motor according to claim 1, wherein the control coupling comprises the first valve which is a pressure-controlled valve that is coupled to the working pressure line leading to the cylinders of the hydraulic motor and to the return line provided from the cylinders, respectively, and which is controlled via the working pressure line so that, when the prevailing pressure of hydraulic oil in the working pressure line drops below a specific level, the first valve closes the working pressure line and the return line to the hydraulic motor, in which case the hydraulic oil is conveyed from the working pressure line directly to the return line.
14. The radial piston hydraulic motor according to claim 13, wherein the hydraulic motor comprises the case line, the inlet line and the outlet line so that, when the prevailing pressure of hydraulic oil in the working pressure line drops below a specific level, the first valve is arranged to connect, by means of hydraulic oil, the inlet line and the outlet line of the hydraulic motor to each other and to connect the inlet line and the outlet line to the case line of the hydraulic motor through the first valve.
15. The radial piston hydraulic motor according to claim 14, wherein the hydraulic motor comprises the drain line and the tank line, the case line being connected through the hydraulic motor to the drain line which is coupled to the tank line.
16. The radial piston hydraulic motor according to claim 15, wherein the control coupling is provided with the choke through which the first valve is controlled via the working pressure line.
17. The radial piston hydraulic motor according to claim 14, wherein the control coupling is provided with the choke through which the first valve is controlled via the working pressure line.
18. The radial piston hydraulic motor according to claim 13, wherein the control coupling is provided with the choke through which the first valve is controlled via the working pressure line.
19. The radial piston hydraulic motor according to claim 1, wherein the disengaging members provided in the hydraulic motor are mechanical spring devices.
Description
BRIEF DESCRIPTION OF THE FIGURES
(1) FIG. 1 is a simplified hydraulic schematic of the radial piston hydraulic motor with the control coupling.
(2) FIG. 2 shows a simplified sectional view of the freewheeling motor in a working state.
(3) FIG. 3 shows the freewheeling motor corresponding to FIG. 2 in a freewheeling state.
(4) FIG. 4 shows another alternative simplified hydraulic schematic of the radial piston hydraulic motor with the control coupling.
(5) The simplified hydraulic schematic of FIG. 5 illustrating the radial piston hydraulic motor shows alternative solutions to the first valve of the simplified hydraulic schematic shown in FIG. 1.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
(6) In the accompanying figures, similar components are referred to by the same numbers.
(7) FIG. 1 shows a simplified hydraulic schematic of a hydraulic motor 4 with a control coupling. The hydraulic motor 4 is a cam ring motor as illustrated in FIGS. 2 and 3, comprising a cam ring 12, radial cylinders 15 disposed in the inner part 16 inside the cam ring and pistons 13 that move therein as well as rollers 14 coupled to the pistons so as to follow the cam ring 12. The operation of the hydraulic motor 4 is based on conveying hydraulic oil or other such hydraulic medium to the cylinders 15 under the pistons 13 for moving the pistons 13 outward in the cylinders 15 so as to force the rollers 14 against the inner surface 12a of the cam ring 12. The hydraulic motor 4 has several cylinders 15, eight in the case of FIGS. 2 and 3, so that the rollers 14 of different pistons 13 contact the cam ring 12 at different points and stages of the wave-shaped inner surface 12a thereof, forcing the cam ring 12 and the inner part 16 to rotate relative to each other. In some situations, the hydraulic motor 4 must be couplable into freewheeling so that, as illustrated in FIG. 3, the rollers 14 of the pistons 13 come off the inner surface 12a of the cam ring 12 as the pressure is withdrawn from the cylinders 15 under the pistons 13. This can be carried out e.g. by the corresponding spring devices i.e. disengaging members coupled to the pistons 13 as described in U.S. Pat. No. 7,225,720 that is herein referred to regarding implementation of the mechanical spring devices.
(8) As illustrated in FIG. 1, the hydraulic motor comprises three valves in the hydraulic circuit of the motor, i.e. a first valve 1, a second valve 2 and a third valve 3. The first valve 1 is a directional valve with four ports and two operating positions that is coupled to a working pressure line 5 leading to the hydraulic motor 4 and to a return line 6 provided from the motor. The first valve 1 is a pressure-controlled valve which is controlled via the working pressure line 5 through a choke 9. The pressure control channel is indicated with reference number 8 in FIG. 1.
(9) The second valve 2 and the third valve 3 are directional valves with two ports and two operating positions (switched on/switch off position), coupled to a control pressure line 7. More specifically, the third valve 3 is coupled to a part 7 of the control pressure line 7. In addition, the second valve 2 is provided with check valve operation in the switched on position, so that, in the case of the second valve 2 in FIG. 1, hydraulic oil is able to flow in only one direction from the control pressure line 7 to the part 7 of the control pressure line 7. The above-mentioned check valve operation can be left out from FIG. 1 if said check valve operation is provided in connection with the second valve 2 in some other way.
(10) The operation of the control coupling according to the hydraulic schematic shown in FIG. 1 can be briefly described as follows. By means of the control coupling, the hydraulic motor 4 automatically couples into freewheeling, so that the hydraulic motor 4 can be driven freely in the freewheeling state irrespective of whether the hydraulic oil supplied to the hydraulic motor 4 be available or not. When e.g. a working machine (not illustrated) or the like which is provided with the control coupling according to the invention is started from a slow speed while the hydraulic motor 4 is driving, the second valve 2 and the third valve 3 are disposed in the position illustrated in FIG. 1, where said valves 2, 3 close the control pressure line 7 in both directions. The first valve 1, instead, is disposed in its extreme position on the right in contrast to FIG. 1, in which position the working pressure line 5 and the return line 6, respectively, are directly connected to the hydraulic motor 4 through the first valve 1, so that the hydraulic oil circulates through the hydraulic motor 4 and the hydraulic motor 4 is driving. The first valve 1 is disposed in the extreme position on the right in contrast to FIG. 1 because it is pressure-controlled via the working pressure line 5 through a pressure control line 8 and a choice 9. In the working pressure line 5, the pressure is so high as to push the first valve 1 to its right extreme position. The purpose of the choke 9 in the case of FIG. 1 is to limit the amount of hydraulic oil supplied to the control pressure of the first valve 1 and make the pushing of the first valve 1 to its right extreme position smoother. If the first valve 1 already has a built-in choke 9 or the structure of the first valve 1 is provided such that the flow to the control pressure of the first valve 1 is limited, the choke 9 is not necessary and may be left out from FIG. 1.
(11) If the hydraulic motor 4 was not provided with the control coupling illustrated in FIG. 1, as the speed would rise sufficiently high, the rollers 14 of the pistons 13 would start to come off the cam ring 12 and the hydraulic motor 4 would start to make as abnormal sound. When a motor starts to make this kind of a sound, there is obviously a risk of breakage. This is because, as the speed rises, the output supplied by the pump, i.e. the volume flow, is no longer sufficient at a certain point relative to the speed of the motor 4, in which case the pressure in the working pressure line 5 drops. It is characteristic of the hydraulic motor 4 that a certain supply pressure must be constantly available so as to keep the rollers 14 of the pistons 13 engaged to the wave-shaped inner surface 12a of the cam ring 12. However, by means of the control coupling according to FIG. 1, as the speed rises and the pressure in the working pressure line 5 drops below a specific level, the first valve 1 moves to the position illustrated in FIG. 1, i.e. to its extreme position on the left, so that the working pressure is no longer supplied to the hydraulic motor 4, but the motor 4 is instead disposed in a freewheeling state and is freewheelable. The structure of the hydraulic motor 4 must be such that, as the pressure is withdrawn from under the pistons 13, the rollers 14 of the pistons 13 automatically come off the inner surface 12a of the cam ring 12 and the motor is freewheeled. Such a freewheeling motor is described e.g. in FI patent publication 118233.
(12) In the illustration of FIG. 1, the first valve 1 is such that the hydraulic oil is directly supplied from the working pressure line 5 to the return line 6 in the freewheeling state. Alternatively, the structure of the valve 1 may be such that the working pressure line 5 and the return line 6 are connected to the plug in the freewheeling state. This alternative is described with reference to the valve 1c of FIG. 5 and described in more detail with reference to FIG. 5. Further, FIG. 1 indicates by the dash line 10 that the first valve 1 is a component internal to the motor 4. However, the valve 1 may alternatively be provided outside the motor 4. Also the choke 9 may alternatively be provided outside the motor 4.
(13) When the working mode of the hydraulic motor 4 is to be assumed from the freewheeling state illustrated in FIG. 1, the second valve 2 is moved from the position illustrated in FIG. 1 to its second position, i.e. to the extreme position on the right. In this case, the control pressure is able to act from the control pressure line 7 through said second valve 2 on the first value 1 so as to push it from the position illustrated in FIG. 1 to the right. In this position, the working pressure is able to move from the working pressure line 5 to the motor 4. By using the second valve 2, the hydraulic motor 4 can thus be forced into the working mode, i.e. to drive irrespective of the rotating speed or pressure. In other words, the hydraulic motor 4 can be started by pressing on the button of the valve 2. In the illustration of FIG. 1, the second valve 2 is controlled, by a button against a spring. Thus, when said valve 2 has been operated and the motor 4 brought into the working mode, the second valve 2 returns to the position illustrated in FIG. 1 as the button is released. Alternatively, said button may also be implemented e.g. by electromagnetic control, pneumatic control or other control that carries out the change of the operating position of said valve.
(14) The third valve 3, in turn, is used for forcing the hydraulic motor 4 into freewheeling irrespective of the rotating speed or pressure. Once the motor 4 is provided in the working mode, the first valve 1 is disposed in the extreme position on the right in contrast to FIG. 1. To bring the hydraulic motor 4 into freewheeling, the third valve 3 is operated so as to move it from the position illustrated in FIG. 1 to the right. In this case, a connection is formed between the part 7 of the control pressure line 7 and a line 11 that leads to the tank. The control pressure is thereby withdrawn from the first valve 1 and it moves back to the position illustrated in FIG. 1 where the hydraulic motor 4 is provided in the freewheeling state. In the illustration of FIG. 1, the third valve 3 is provided with electromagnetic control against a spring. The control may also be implemented by a button, pneumatic control or other such manner by which the change of the operating position is established.
(15) The above-described second valve 2 and third valve 3 can alternatively be combined into one valve so as to provide in said combined valve the same operation as described above with reference to the second valve 2 and the third valve 3, so it is not explained in any more detail in the figures.
(16) FIG. 4 shows another alternative hydraulic schematic of the hydraulic motor with the control coupling. The hydraulic motor 4 of FIG. 4 with the control coupling operates as described above with reference to FIG. 1 with the exception that, in the illustration of FIG. 4, the hydraulic motor comprises a case line 19, an inlet line 17 and an outlet line 18 of the hydraulic motor 4 so that, when the pressure of hydraulic oil drops below a specific level, the valve 1a or 1b is arranged to connect, by means of hydraulic oil, the inlet line 17 and the outlet line 18 of the hydraulic motor 4 to each other and to connect the inlet line 17 and the outlet line 18 to the case line 19 of the hydraulic motor 4 through the valve 1a or 1b. The working pressure line 5 comprises the inlet line 17 provided between the valve 1a or 1b and the hydraulic motor 4. The return line 6 comprises the outlet line 18 provided between the valve 1a or 1b and the hydraulic motor 4. In addition, the hydraulic motor also comprises a drain line 20 and a tank line 21, wherein the case line 19 is connected, through the hydraulic motor 4, to the drain line 20 which is coupled to the tank line 21. In addition, when the pressure of hydraulic oil in the working pressure line 5 drops below a specific level, the first valve 1a connects the working pressure line 5 to the return line 6 or, in the case of the valve 1b, closes the pressure line 5 to the valve 1b. In the hydraulic schematic according to FIG. 4, the discharge of hydraulic oil, which controls the pistons, from under the pistons into the tank line 21 and the coupling to the freewheeling state by the hydraulic motor 4 may be accelerated. The purpose of the choke 9 in the case of FIG. 4 is the same as described earlier with reference to FIG. 1 i.e. is to limit the amount of hydraulic oil supplied to the control pressure of the first valve 1a or 1b and make the pushing of the first valve 1a or 1b to its right extreme position smoother. If the first valve 1a or 1b already has a built-in choke 9 or the structure of the first valve 1a or 1b is provided such that the flow to the control pressure of the first valve 1a or 1b is limited, the choke 9 is not necessary and may be left out from FIG. 4.
(17) The hydraulic schematic of FIG. 5 illustrates alternative solutions to the first valve 1 illustrated in FIG. 1. The hydraulic motor of FIG. 5 operates as described above with reference to FIG. 1 with the exception that alternative valve structures 1c, 1d, 1e and 1f to the first valve 1 are illustrated. The purpose of the choke 9 in the case of FIG. 5 is the same as described earlier with reference to FIG. 1 i.e. is to limit the amount of hydraulic oil supplied to the control pressure of the first valve 1c-1f and make the pushing of the first valve 1c-1f to its right extreme position smoother. If the first valve 1c-1f already has a built-in choke 9 or the structure of the first valve 1c-1f is provided such that the flow to the control pressure of the first valve 1c-1f is limited, the choke 9 is not necessary and may be left out from FIG. 5.
(18) The control coupling of FIG. 5 comprises the first valve 1c operating as described with reference to FIG. 1 with the exception that, when the prevailing pressure of hydraulic fluid in the working pressure line drops below a specific level, the first valve 1c closes the working pressure line and the return line to the hydraulic motor and to the first valve 1c.
(19) The control coupling of FIG. 5 comprises the first valve 1d operating as described with reference to FIG. 1 with the following exception: the working pressure line 5 comprises the inlet line 17 of the hydraulic motor 4 provided between the first valve 1d and the hydraulic motor 4 and the return line 6 comprises the outlet line 18 of the hydraulic motor 4 provided between the first valve 1d and the hydraulic motor; when the prevailing pressure of hydraulic oil in the working pressure line 5 drops below a specific level, the first valve 1d closes the working pressure line 5 and the return line 6 to the first valve 1d and connects the inlet line 17 and the outlet line 18 to each other through the first valve 1d.
(20) The control coupling of FIG. 5 comprises the first valve 1e operating as described with reference to FIG. 1 with the following exception: the working pressure line 5 comprises the inlet line 17 of the hydraulic motor 4 provided between the first valve 1e and the hydraulic motor 4 and the return line 6 comprises the outlet line 18 of the hydraulic motor 4 provided between the first valve 1e and the hydraulic motor; when the prevailing pressure of hydraulic oil in the working pressure line 5 drops below a specific level, the first valve 1e closes the working pressure line 5 and the return line 6 to the hydraulic motor 4 and connects the inlet line 17 and the outlet line 18 to each other through the valve 1e, in which case the hydraulic oil is conveyed from the working pressure line 5 directly to the return line 6.
(21) The control coupling of FIG. 5 comprises the first valve 1f operating as described with reference to FIG. 1 with the following exception: the working pressure line 5 comprises the inlet line 17 of the hydraulic motor 4 provided between the first valve 1f and the hydraulic motor 4 and the return line 6 comprises the outlet line 18 of the hydraulic motor 4 provided between the first valve 1f and the hydraulic motor; when the prevailing pressure of hydraulic oil in the working pressure line 5 drops below a specific level, the first valve 1f closes the working pressure line 5 to the hydraulic motor and connects the inlet line 17 and the outlet line 18 to the return line 6 through the first valve 1f.
(22) The hydraulic motor with the control coupling has been exemplified above with reference to the accompanying figures. However, the scope of protection of the invention is not limited merely to the examples illustrated in the figures; instead, the embodiments of the invention may vary within the scope of the inventive idea defined in the accompanying claims.
