FI87008C - Slow-acting hydraulic radial piston center motor / pump - Google Patents

Description

87008

LOW SPEED HYDRAULIC RADIUS CENTRAL MOTOR / PUMP

The invention relates to a low-speed hydraulic radial piston-centrifugal motor / pump comprising a housing, a crankshaft, a collector ring mounted thereon, a plurality of substantially radially arranged hydraulic cylinders articulated at one end to the collector ring and the other end to the housing. The engine has oil dispensers for driving the hydraulic cylinder and rotating the crankshaft relative to the housing, and the pump 10 for supplying supply oil to the cylinders and removing high pressure oil from the cylinders, respectively. Here, the hydraulic motor can also be a so-called a pole motor in which the shaft remains stationary and the housing rotates around it. Low-speed hydraulic motors are required on various machines to rotate the rollers and 15 other machine members with high force. Such a hydraulic motor for landfill mills has long been sought, but no such motor has been available. Thus, they have used high-speed hydraulic motors and a reduction gear, as well as chain transmission in the transmission to the rollers.

20

Especially in star engines used as aircraft engines, the end of the piston rod of one cylinder is formed as a collector ring into which the other piston rods are articulated. Similarly, a hydraulic reciprocating hydraulic motor of the type mentioned in the introduction is disclosed in Swedish Patent Publication 129350. However, such a solution is quite difficult to use in very slow-rotating hydraulic motors with very high torque. For example, in the case of the above-mentioned dump roller, the torque requirement of the hub motor is about 100,000 Nm. In this case, the torque required to lock the collector ring is also tens of thousands of newton meters. The high load on the hydraulic cylinder used to lock the collector ring causes a difficult construction problem.

The object of the present invention is to provide a low-speed hydraulic motor in which the above-mentioned problems have been solved and a high-torque hydraulic motor can be obtained by a simple construction. The invention can also be applied as a pump. The characteristic features of the invention are set out in the appended claims. The most surprising feature of the invention is that locking of the collector ring can be dispensed with if the hydraulic cylinders are set to operate on the traction side. When there is usually also an overpressure on the return side of the hydraulic circuit, the piston rods can even be replaced by a flexible rope, the material of which can be metal, carbon or other reinforcing fiber.

As such, the engine can be made to operate with only three hydraulic cylinders, but it is advantageous to use considerably more cylinders, since then the angular difference between the equilibrium position of the collector ring and the cylinder division varies as little as possible during the cycle. In addition, this variation can be reduced by controlling the return line pressure, i.e. the supply pressure. Other preferred embodiments and advantages of the invention will become apparent from the following embodiment.

The invention will now be described with reference to the accompanying figures, which show a low-speed hydraulic motor and a pump according to the invention.

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Figure 1 shows the hydraulic motor split.

Figure 2 shows a cross-section of point II-II in Figure 1.

Figure 3 shows the feed plate of the hydraulic motor.

Figure 4 shows the distributor plate of the hydraulic motor.

25 Figure 5 shows a schematic diagram of the pump

The hydraulic motor according to Figures 1-4 is a so-called a hub motor, wherein the crankshaft 2 is attached to the machine frame and the housing 1 rotates a roller or other piece. The housing is supported on a rotating crankshaft by means of bearings 15 and 14, the latter of which provide a favorable support force to the end 7 of the crankshaft.

A collector ring 3 is rotatably attached to the crankshaft 2 by means of bearings 8, to which the ends of the piston rods 10 of the hydraulic cylinders 4 are in turn fixed by means of joints 9. The piston rod end end of each cylindrical part 11 comprises a forged end piece 30, which also includes shaft pins for fastening the cylindrical part by means of bearings 13 to the housing 1.

3 87008

The hydraulic oil supply and return lines 18 are passed through an eccentric plate 20 belonging to the crankshaft to the supply plate 5. Between the plate 20 and the supply plate 5 there is further an intermediate housing 16 connected to the supply plate 5 so that the supply plate can slide in the axial direction 5. From the supply plate, the hydraulic oil is distributed to the distribution plate, which distributes the hydraulic oil to the cylinders 4 via the hose 29 and likewise collects the oil therefrom further through the distribution plate back to the supply plate and the return line. The operation of the dividing plate and the feed plate will be described in more detail below. Figure 1 is a schematic illustration of a hydraulic cylinder 10 marked 19, whose first end is bound epäkeskolevyyn 20 and the other end of the intermediate housing 16. The hydraulic cylinder 19 is double acting and its thrust and-LEN vetopuo terminals are connected to the inlet and outlet side of the lines. If desired to change the direction of rotation of the engine, the inlet and the return side 15 of the pressure levels in the oil change and at the same time the hydraulic cylinder 19 into a second end position, wherein the intermediate housing 16 and with it the feed plate 5 turns a selected angle around the crankshaft. The feed plate 5 is turned in the same direction as the distribution plate 6 lags behind the cylinder division of the housing. In connection with the reversal 20, the equilibrium position of the collector ring 3 is moved to the opposite side, which is taken into account by turning the feed plate. Typically, the angular difference in the equilibrium position with respect to the cylinder division is about + 10 °, i.e. the offset of the feed plate from side to side is a total of 20 *. The angular difference in the equilibrium position of the distributor plate 6 is not constant, but varies in the hydraulic motor according to this example between 10® and 12 °. Since the angular difference also depends on the operating pressure, more precise compensation can be achieved by adding springs on both sides of the piston to the hydraulic cylinder, by means of which the compensation takes place as a function of pressure.

. 30

Figures 3 and 4 show in detail the feed and dividing plate, in which the grooves 23 of the dividing plate 5 are placed against the openings 25 of the feed plate 6. The above-mentioned supply and return lines 18 connected to the feed conduit 21 of the plate 5 from which they can enjoy the main duct 22, 35 there are distributed to respective inlet and outlet passages 23. In such a way through the upstream channel 23 to the openings 25 which are in this area and thus shift. These holes 25 leads to a channel conduit 26, which is connected to the corresponding hydroxy '87 008 leading to cylinders of a hydraulic hose 29. Similarly, the reverse side of the channel region 23 of the divider plate 6 the openings 25 feed the hydraulic cylinder return oil.

5 of the divider plate 4 is rotated against the feed plate 5 slides in a time slot inlet side gap 23 and, respectively, on the opposite side to the exit side opening 23 on the ends of the channel 23 and the opening of these channels at a time, exits the top. This allows the cylinder at a time will shift, every 10 takes almost 180 °, after which opening leaves the input side of the channel 23 of the top and the opening 25 in the middle of the groove 27 coincides Feeder-bath of the hole 28, which allows high-pressure hydraulic oil to the housing, which is vuotoöljysäiliönä. Subsequently, the corresponding aperture 25 to the exit side 23 of the box channel 15 so that the oil can flow from the cylinder space to the return line. The feed plate 5 has a base between the channels 23 which is substantially the width of the openings 25, which prevents direct leakage through the openings 25 from the inlet side to the return side.

20 With a filling pressure of 320 bar and a supply pressure of approx. 5 bar on the return line side, a torque of approx. 100,000 Nm and a maximum speed of 17 rpm are achieved with a motor with a diameter of approx. 1000 mm.

The housing 1 preferably functions as an oil tank, whereby the housing oil cools the hydraulic equipment.

The accompanying exemplary engine can, of course, be modified by selecting a different number of hydraulic cylinders or by placing two or more such sets of cylinders in parallel on the same crankshaft.

The invention can also be applied as a pump, in which case, according to Figure 5, the supply and discharge of oil from the hydraulic cylinders takes place quite simply. Each cylinder 4 is connected by its own check valves 31 and 31 'to common inlet and return lines 18 and 18 ·.

Claims (8)

A low-speed radial piston eccentric hydraulic motor / pump comprising a housing (1), a crankshaft (2) rotatably mounted thereon 5, a manifold ring (3) mounted thereon, a plurality of substantially radially arranged hydraulic cylinders (4) articulated at its first end to the manifold ring (3) at one end of the housing (1), oil distribution devices (5,6) for connecting the inlet and pile line to the hydraulic cylinders (4), characterized in that the hydraulic cylinders (4) are adapted to operate only on the traction side, the hydraulic cylinders in each case pulling the collector ring into a stable equilibrium position, which deviates by a certain angular difference from the cylinder division of the housing (1). 15 Hydraulic radial piston eccentric motor / pump according to Claim 1, characterized in that the ends of the piston rod (10) are articulated to the collector ring (3) and the piston rod-side ends of the cylinder cylinders (11) are articulated to the housing (1). . Hydraulic radial piston eccentric motor / pump according to Claim 1 or 2, characterized in that the piston rods (10) are made of a flexible material, for example a rope assembled from metal, carbon or other reinforcing fiber. Hydraulic radial piston eccentric motor according to one of Claims 1 to 3, characterized in that it is arranged in a so-called as a hub motor, i.e. the housing (1) rotates while the crankshaft (2) remains stationary and the hydraulic oil supply and return lines (18) are led to a supply plate (5) connected to the crankshaft (2) and through it to a manifold (6) rotating with the collector ring (3) for each shift cylinder 35 (4) and collects, respectively, the rest of the hydraulic oil to be removed from the cylinders in the return line. 6 87008 Hydraulic radial piston eccentric motor according to claim 4, characterized in that the hydraulic motor comprises an actuator (19) adapted to turn the feed or distributor plate (5, 6) by a selected angle of rotation from the symmetrical position 5 to account for said angular difference in oil supply and discharge. 5 87008 Patented Applications Hydraulic radial piston eccentric motor according to Claim 4 or 5, characterized in that the feed / distribution plate (5, 6) comprises hydraulic cylinders (24) formed on the side opposite to the distribution / supply plate (6,5), each piston (17) being adapted to push the opposite plates (5,6) against each other and of which the hydraulic cylinders (24) each connected to a respective inlet side or the reverse side of the channel 15 (23). 7. in any one of claims 1-6 hydraulic säteismäntäepäkeskomoottori, characterized in that the hydraulic motor is a hydraulic motor apparatus without a supply pressure to control the angle difference of 20 to adjust the pressure on the return side. Hydraulic pump according to one of Claims 1 to 3, characterized in that each hydraulic cylinder (4) is connected to a common inlet line and a common return line by means of separate non-return valves (31). 7 87008