DE2536310A1 - HYDRAULIC TORQUE LIMITER - Google Patents

Description

PATENT LAWYERS
DR. ANDREJEWSKI

DR.-ING. HONKE Essen, d. August 13, 1975

DIPL.-ING. GESTHUYSEN

DR. MASCH
43 FOOD, TfliiÄTiiRi'LATZ 3

N.V. KEMPENSE STEENKOLENMIJNEN, gevestigd Grote Baan 27, 3530 Houthalen (Belgium)

"Hydraulic Torque Limiters"

The present invention relates to a hydraulic torque limiter, in other words a device which ensures that when a specified, maximum permissible torque is reached during the transmission process, the transmission switches off automatically and thus damage to machine parts can be avoided.

Such torque limiters can do many things

Machines and drives are used. As a special area of application However, the break protection of the coal plow chain and the coal plow drive as well as the chain and the drive can be used viewed from armored conveyor systems in pits. The torque limiters known to this day work as a whole mechanical and consist of a so-called breaking bolt safety device, i.e. that at a certain point two components of a machine with precisely calculated and designed breaking pins be assembled so that these bolts break when the maximum permissible transmission torque is reached and thus the The drive is interrupted without breaking the machine.

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However, this breaking pin protection has various disadvantages, the most important of which is the cost price Φι Breaking bolts must be counted, in the manufacture of which the precision of the dimensions and the meticulous execution a to play an important role; In addition, there is the variability of the maximum permissible transmission torque that depends on the respective degree of fatigue and / or depends on the already partial state of wear of the breaking pin; then also the loss of time in bringing in new break bolt; the risk of accidents for the worker, which the new breaking bolts must install, etc.

Accordingly, the present invention relates to a hydraulic torque limiter incorporating the aforesaid and other disadvantages of the known mechanical torque limiters excludes.

The main advantages of this hydraulic torque limiter are:

- the maximum permissible transmission torque always remains constant;

- the maximum permissible transmission torque is adjustable;

- the recoupling of the driving with the driven After the torque limiter has intervened, the machine part can be set up very quickly, easily and safely;

- the recoupling of the driving with the driven Machine part can be managed by remote control.

The hydraulic torque limiter according to the invention with the aforementioned and other advantages exists for this purpose essentially from a radial oil cylinder with piston as part of a first part of the torque limiter, for example

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the driving part of the torque limiter; added in connection with the aforementioned oil cylinder, namely behind the piston of which has a supply line or discharge line for the pressurized oil; is in the aforementioned supply line a check valve; in the aforementioned discharge there is a pressure relief valve; in connection with the second part of the torque limiter, for example with the driven one Part, a projection and between this and the free end of the aforementioned piston, an intermediate part through which the on the Forces exerted by the piston can act radially on the latter.

The proposed hydraulic torque limiter ensures the complete interruption of the coupling between a drive and the driven part, namely by the sudden escape of a liquid when reaching a specified fluid pressure.

Appropriately designed contact surfaces on the inside of the driving ring press against one or more Rolling in the driven ring, at an angle of about 45 °, so that overloading the coupling immediately and completely interrupts.

The tangential components on these rollers are made mechanical but frictionless by a rolling or hinge system caught.

The radial components on these rollers are caught by the fluid under the various pistons. These pistons are installed radially under each roller in the driven ring. The force is evenly applied to all pistons

B Π 9 R 3 7 / Π 2 6 9

distributed because the cylinders are communicating.

In the event of overload, the liquid will penetrate very quickly the pressure relief valve discharged into a liquid container. Remote control can then be used in the possibly built-in Liquid containers develop a certain pressure and thus re-establish the coupling for both directions of rotation. the The force of the transmission torque depends on the total area of the piston and the set pressure of the pressure relief valve. For better Presentation of the characteristic features of the invention is given below by way of example and not of limitation preferred embodiment of a torque limiter according to the invention with reference to the accompanying drawings:

Figure 1 shows the sectional plane of the basic drawing of a torque limiter according to the invention;

Figure 2 shows a side view with a partial sectional plane of the embodiment of a torque limiter according to the invention, in which the principle as shown in the figure is used;

Figure 3 shows a section along line III-III of Figure 2;

Figure Ί shows the in Figure 3 with F4 indicated game.

Figure 1 shows the schematic representation of a hydraulic torque limiter according to the invention, this torque limiter mainly consists of a driving part 1 and a driven part 2. the Driving part 1 consists of one in the present case

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cylindrical body in which a radial chamber 3 is provided at a certain point in which a piston H moves can. This piston H works at the free end together with a lever 5, which is inserted into elongated holes 8 and 7 via spindles 6 and 7, respectively.

9 is held.

The lever 5 is preferably cylindrical in the middle Part that, on the one hand, cooperates with the free end of the piston U and, on the other hand, with a projection

10 can work together, which is located on the inner wall of the driven Part 2 is located. The projection 10 is preferably rounded.

The aforementioned chamber 3 stands over two lines 11 or 12 in connection with an oil supply line 13, for example from an axial hole in the shaft of the driving part 1 is formed, with a so-called overpressure valve IH and a so-called overpressure valve in the lines 11 and 12, respectively 15being.

The operation of such a torque limiter is very simple and is as follows.

From the line 13, pressurized oil is passed through the check valve 15 into the space 3, with the outflow this oil is prevented by valve IH up to a certain pressure while the check valve 15 ensures that no oil can flow back through the line 12. That in the Chamber 3 guided oil causes a displacement of the piston H, which presses against the lever 5 and so this lever, if the cylinder allows this, pushes outwards. When turning the Part 1 is reached by lever 5 with its center

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central and rounded thickening in the way of the projection 10 of the driven part 2, whereby this driven part 2 is then taken along in the movement of part 1, and although it is obvious that the direction of rotation of part 1 and thus the direction of rotation of part 2 are both clockwise as well as counterclockwise.

If the driven part 2 now encounters an excessively high resistance from a certain distance, the circumferential force on this part 2 becomes greater and the force exerted on the projection 10 on the lever 5 increases accordingly. The construction of the torque limiter according to the invention ensures that this force exerts a practically radial pressure on the piston k while the lever 5 is subject to a tensile load, and it should be noted that as a result the time components of the piston on the wall of the chamber 3 are very slight - so little or no abnormal wear - while the lever 5 can be designed in a lighter design when it is subjected to a pressure load, at the same time the influence of the frictional forces of the rollers on the piston is as small as possible. At the same time, this prevents the rollers from becoming self-braking as a result of this friction.

The construction of the lever 5 is in fact designed so that the axis 6 or 7 of the unloaded arm of the lever is located in the middle of the elongated hole 8 or 9, so that this axis can move practically without friction and not on the Participates in a play of forces. The tangential forces can possibly also be absorbed by rolling against a vertical Press groove.

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The compressive force exerted on piston H causes a pressure increase at 01 in chamber 3 until the pressure relief valve Ik opens at a set pressure that corresponds to a certain encircling force on part 2. As a result, the 01 flows out through this valve 14 and the piston can move radially inwards. So the lever 5 detaches from the projection 10 and thus the parts 1 and 2 are uncoupled. This avoids breakage of machine parts and the coupling can be easily re-established by inserting 01 into chamber 3 again.

Obviously, this gives you a very simple torque limiter that you can effortlessly use once it has entered into force and can be ready for use again in the shortest possible time without costs.

Figures 2 to M- show an embodiment in which the principle shown in Figure 1 has been applied. In the present case there are four pistons 4 and one the same number of levers 5 are provided, each of which can cooperate with a projection in part 2, this projection in the present case consists of a roller 16 which is expediently attached in part 2. The levers 5 exist in the present Case of two parts 51 and 52, which are equipped in their highest part with a spindle 17, on the free a bush is rotatably applied, which can cooperate with a roller 16.

In the present case, the lines 12 also open into the line 13, which is in the drive shaft through an axial bore 19 is extended, with the

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aforementioned check valve 15 is seated. This valve consists, as known, mainly of a valve seat 20 with one Closing ball 21 cooperates, the latter being pressed against its seat by a spring 22.

The pressure relief valve 14 is of conventional design and is like the aforementioned check valve 15 only briefly described. It consists mainly of a cavity 23 in which gas, for example nitrogen, is under a pressure which corresponds to that at which the pressure relief valve opens must, in other words, the one with the maximum permissible transmission torque matches.

This space 2 3 can be filled and emptied with the aid of a check valve 24.

The sealing of the chamber 2 3 is also ensured by a sealing hood 2 5, under which a disk 2_6 is located. Under this disc 26 is a ring 27 which, with the exception of a small annular space 28 on a central Part of the body of the pressure relief valve fits, with an annular ring between this ring 27 and the central body Space 29 remains, which is connected to the aforementioned bore 19 via one or more passages 30. Finally, the aforementioned lines 11 are mounted in the central body of the pressure relief valve.

In this case too, if the part 2, for example a belt pulley, a chain wheel, becomes a chain sprocket or the like, encountered excessive resistance which can lead to the breakage of a certain machine part, the various Lever 5 by the action of the rollers 16 on the

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Bushings 18 the various pistons U towards the center of the device Press, whereby the 01 can act under high pressure on the disc 26 via passage 31 and space 32, which thereby and if the pressure becomes greater than the pressure in the chamber 23, so bent is shown as the dashed line in Figure 4. This causes the 01 to pass through space 32 under high pressure and passes under the disc 26 into the annular space 28 and then through the annular space 29 and the passage or the passages 30 flow back into the original supply line 19.

As soon as this 01 has been discharged, the pressure relief valve returns to its initial position, under the pressure of the gas in the chamber 2 3, so that when the resistance is removed from part 2 by simply supplying 01 via line 19 and the check valve 15, the various cylinders U- can again be pressed radially outward, and so that the various levers 5 are each in contact with a roller 16 again.

It is obvious that the number of cylinders U or the lever 5 and the rollers 16 the respective needs and Requirements can be customized. In addition, it goes without saying that the present invention is not limited to taking as an example Embodiment described and shown on the accompanying drawings is limited, because such a hydraulic torque limiter can be realized in many shapes and dimensions without going beyond the scope of the invention.

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Claims (11)

-ίο- 253631 EXPECTATIONS Hydraulic torque limiter, characterized in that it mainly consists of at least one radial cylinder (3) with piston (4) which is part of a first part of the torque limiter, for example the driving part of the torque limiter; in connection with the aforementioned cylinder (3), behind its piston (4), there is a feed line (12) or discharge line (11) for the pressurized oil; in the aforementioned supply line there is a check valve (15); in the aforementioned derivation there is a pressure relief valve (I ¹ +); in connection with the second part of the torque limiter, for example with the driven part, a projection (10) and between this latter and the free end of the aforementioned piston (4) an intermediate part (5) through which the acting on the piston (4) Forces can be applied axially to this. 2.- Hydraulic torque limiter according to claim 1, characterized in that each oil cylinder consists of a radial bore (3) in the driving part of the torque limiter consists, behind the piston (4), in the cylinder space (3), a line (12) opens out from a common line (13) branches off, namely between the aforementioned check valve (15) and the aforementioned pressure relief valve (14). 3.- Hydraulic torque limiter according to claim 2, characterized in that the check valve (15) directly is built into the supply line (13), the latter from an axial bore in the drive shaft of the 609837/0269 - * - 253B3 1 O Torque limiter exists. 4. Hydraulic torque limiter according to claim 2, characterized in that the pressure relief valve (14) with a suitable line or lines (30) is connected, which derive the 01s from the aforementioned Cylinder (3) make it possible as soon as a pressure is exerted on this 01 that is greater than that of the pressure relief valve (14). 5.- Hydraulic torque limiter according to one of the preceding claims, characterized in that the the aforementioned projection (10) is rounded. 6.- Hydraulic torque limiter according to one of the preceding claims, characterized in that the the aforementioned projection (10) consists of a roller (16). 7.- Hydraulic torque limiter according to one of the preceding claims, characterized in that the Intermediate part between the free end of the piston and the aforementioned projection from a role in a lever or from a Roll, the tangential components of which are caught in a groove and which is attached to the part in which the Liquid cylinder is installed. 8.- Hydraulic torque limiter according to claim 7, characterized in that the aforementioned lever in the Center on the free end of the piston (4) in question rests, while its parallel adjustable ends on the cylinder attached to the part in which this cylinder (3) is installed. 9.- Hydraulic torque limiter according to claim 609837/0269 253631Π 8, characterized in that the aforementioned lever in
the middle shows a cylindrical part (17) which,
on the one hand, with the free end of the relevant piston (4) and, on the other hand, with the relevant projection (10) cooperation. 10, - Hydraulic torque limiter according to one of the preceding claims, characterized in that the The aforementioned lever shows two arms of equal length (51-52) which form an obtuse angle in relation to one another. 11.- Hydraulic torque limiter according to one of the preceding claims, characterized in that the the aforementioned lever is equipped with a spindle (6-7) at each end, which cooperates with an elongated hole (8-9), whose longitudinal axis runs parallel to the longitudinal axis of the piston (4) which cooperates with this lever. 609837/0269 Blank page