HYDRAULIC BRAKING AND/OR LOCKING DEVICE AND INTER ALIA USE OF SAME AS DIFFERENTIAL BRAKE AND/OR LOCK

Abstract: A hydraulic braking device comprises a pair of meshing gears (1, 4) which rotate in bores (3) in a pump body (6). The driven gear (1) is axially slidable, like a piston, in its cylindrical bore (3). The oil inlet and the oil outlet are connected via channels (13, 14) to a respective end of the bore (3). By this construction a hydraulic braking device with a braking delay is created. This attribute makes the device i.a. particularly suited for use in vehicles as an automatic differential brake.

Description: HYDRAULIC BRAKING AND/OR LOCKING DEVICE AND INTER ALIA USE OF SAME AS DIFFERENTIAL BRAKE AND/OR LOCK The present invention relates to a hydraulic braking and/or locking device and is based on the well-known gear pump bra¬ ke principle. An example of a hydraulic or fluid brake em¬ ployed in connection with rotating shafts, is disclosed in US Patent No 1,692,801. In general a hydraulic pump uses a pair of meshing gears. A pump body cases the gears and includes channels for the inlet and outlet of oil. As the gears rotate, the spaces between the gear teeth are filled with oil from the oil in- let. Then, as the teeth mesh, the oil is squeezed out through the oil outlet. By connecting the oil outlet to the oil inlet, a closed cir¬ cuit oil system is achieved, which on being throttled, illu¬ strates the said known hydraulic brake principle. According to the present invention, this principle is furt¬ her developed and the scope of utilization of the device is considerably extended. Some of the expressions used in the following description, need an explanation, and will be defined here: Internal oil leakage ("bypass") - the trottled oil circula¬ tion, if any, between the oil inlet and oil outlet, and the oil leakage between the gears and their cylin¬ drical bores. The leakage is minimised by closing the throttled connection and shaping the gears with a tight fit. Piston gear - a gear which also can slide axially in its bo ¬ re and sealingly function like a piston in a cylinder. Piston (gear) movement - the axially sliding motion of the piston gear. The device according to the invention is characterized in that the drive gear in the gear pump is arranged so as to be both rotable and axially slideable in its bore, like a pis¬ ton in a cylinder. Moreover, connecting channels are pro¬ vided from the oil outlet to one end of the cylinder and from the oil inlet to the other end of the cylinder. When the gears begin to rotate, oil will be displaced from one side of the piston gear to the other side and the piston gear will be accordingly axially pushed by the oil pressure without the device causing any notable resistance. To support the piston movement, the teeth of the gear may be screw-shaped. Then, as the piston gear comes into rotating contact with the cylinder end, does the braking effect occur. The brak¬ ing effect is a function of the internal oil leakage ("by- pass") and the friction between the piston gear and the cy¬ linder end. Said friction may be adjusted in the desired direction by the appropriate choice of materials and the co- nical-ness of the contact surfaces. In this way a hydraulic braking device with braking delay is created. By forming the contact surfaces with co-operating teeth or barbs, the piston gear rotation may be blocked and further rotation of the gears is hindered. In this way a hydraulic locking device is created. Below, the previously mentioned, and further features of the invention and examples of employment will be explained more in detail with reference to the accompanying diagrammatic drawing, wherin: Fig. 1 shows a section of the device with the slideable pis- ton gear in its mid-position. Fig. 2 shows a section of the device where the contact sur¬ faces are formed with co-operating teeth. Fig. 3 shows a section of the device where the slideable piston gear is held in its initial position due to its own weight. Fig. 4 shows a section of the device where the contact sur¬ faces are formed with hypoid-shaped teeth. Fig. 5 and 6 shows the device placed with clearance between the side gears in a differential with the pump drive gear coupled to one of the planetary gears. In fig. 1-6 the pump driven gear 1 (piston gear) is axially moveable. The piston gear is supplied with end discs 2 wich seal against the wall 3 of the cylinder. The drive gear 4 is coupled to an axle shaft 5 which extends out of the pump body 6. The two gears 1 and 4 are meshed with another and the pump body cavity is filled with oil and sealed off from its surroundings. A channel 13 leads from the pump oil in¬ let to one end of the cylinder and another channel 14 leads from the pump oil outlet to the other end of the cylinder. When the gears rotate,oil is sucked from one end of the cy¬ linder and forced into the other end of the cylinder. If the direction of rotasion of the gears is reversed, the oil is pumped in the opposite direction. In fig. 1 the piston gear 1 can move freely, in fig. 2, 4 and 6 it is held in its initial position by springs 7 and in fig. 3 it is held in its initial position by its own weight. The magnitude of the braking delay is dependent on the lenght of the piston stroke. If, for example, a journal is to be put into rotation with a long light running period, the piston stroke is made long. If the braking effect is to come into play immediately, a short piston stroke is set. Utilisation of springs 7 holding the piston gears in its initial position, makes it possibe to have a gentle transi¬ tion from the light running state to the braking state. When a journal is to be put into rotation, the piston gear is in its initial position, i.e. at the beginning of the light run¬ ning phase. During the piston axial movement, the spring is gradually put under tension and the braking effect increases accordingly. By forming the contact surfaces of the piston end and pump body with co-operating teeth 8, 9, the rotation of the pis¬ ton gear will be blocked when it makes contact with the pump body. In fig. 2 the teeth 8 and 9 are undercut-shaped, in fig. 4 hypoid-shaped and in fig. 6 spiral-shaped. One actual use of the device is in connection with car seat- belts. The embodiment of the device shown in fig. 2 is par¬ ticularly suited to this purpose. The body 6 is designed as a seat-belt drum, the piston stroke is reduced to a minimum, and the piston end and the body are supplied with self-lock- ing meshing teeth. In this way the device block rapidly when the seat-belt is jerked. The oil "bypass" is adapted so that the seat-belt is rewound at a desired speed. Another actual use of the device is in those connections where it is desired that ropes, chains, belts etc. is to be paid out at a controlled speed, e.g. in rescue services in connection with fire-ropes and chains, rescue baskets, life¬ boats etc. In this case the design shown in fig. 1 is well suited. The body 6 is preferably designed as a drum or pul¬ ley, the piston stroke and spring tension, if any, are adap- ted so that the desired acceleration is achieved and the oil "bypass" is adjusted so that the desired spe * ed is obtained. The design shown in fig. 1 is also well suited in connection with the opening and closing of heavy gates. The device is coupled to the gate revolving hinge pin, and the braking de- lay is adjusted so that the braking effect comes into play when the gate approaches its open position. When the gate is being closed the braking effect will then come into play when the gate approaches the closed position. The design shown in fig. 3 is useable as a speed regulator for a rotating member. One area of use where all the functions of the device can be utilised, is particularly in connection with the differenti¬ al of a vehicle, i.e. as a differential brake or combined differential brake and lock. The general objection to and disadvantage of using an auto¬ matic differential brake based on the gear pump brake prin¬ ciple, e.g. as disclosed in US Patent No 4,272,993, is that this type of brake offer braking effect all the time, for ex¬ ample during driving in turns where the braking effect is un- desireable. Thus, undue wear and tear and overheating and steering trouble occur. By using a device based on the pre- sent invention however, the said disadvantages are prevented since, because of its constructional design (the moving pis¬ ton) the device has a braking delay, i.e. a delay which means that the braking effect does not come into play , unless one wheel has less traction than the other. In fig. 5 and 6 is shown how the device can be placed. The body 6 of the device is fitted with play in the space between the differential side gears 10 and 11, and the planetary gears 12. Positioned in this space (like hand in glove) the device will remain fairly firm. The pump axle shaft 5 exten- ding out on both sides of the pump body is supported in the differential case (not shown in the drawing). The planetary gears are mounted on the axle shaft 5, one of the planetary gears fixed and the other one moving freely. EXAMPLE A As a differential brake an embodiment of the the device as shown in fig. 1 is suitable. The device is equipped with springs which are preferably pre-tensioned and preferably po¬ sitioned with particular play in relation to the piston gear. The throttled connection between the pump inlet and outlet is dispensed with so that the inlet and outlet are only connec¬ ted to their respective sides of the piston gear 1. The dif¬ ferential brake functions in the following manner: Normal state: During normal straight-road driving, the ring gear with the differential case (not shown in the drawing) will rotate, but the planetary gears 12 will remain rotation-less about their own axis, i.e. the pump gears will also remain at rest. Delay phase: In a turn the outermost wheel will rotate faster than the in- nermost and the planetary gears 12 rotate slowly. The pump gears 1 and 4 is driven by one of the planetary gears, but by this normal slow rotation the piston gear 1 moves freely and t e device does not offer braking resistance. Transitional phase: However, if one of the wheels loses traction, i.e. begins to slip, the planetary gears 12 will rotate faster. Now the piston gear is pushed by the oil pressure more and more over to the one side against a correspondingly increasing spring tension. The braking effect of the device increases corre¬ spondingly and this effect is transmitted to the wheel with traction. Braking phase: If one of the wheel is spinning freely, the rotation of the planetary gears 12 will increase further, the spring 7 ten¬ sion will be overcome, and the piston gear 1 comes into ro¬ tating contact with the cylinder end in the pump body. The braking effect is now depending on the internal oil leakage and the friction between the piston and the pump body. The device works as an differential brake. Return phase: In cases where both wheels get traction, the oil pressure de- creases gradually and the spring 7 will push the piston gear back to its initial position. Re-cycle: If the slipping or spinning wheel should get traction and the other wheel begin to slip or spin, then the rotation of the gears in the pump will be reversed and the gear pis¬ ton will be pushed by the oil pressure to the opposite side in the pump body and the cycle will be repeated. EXAMPLE B As a combined differential brake and lock an embodiment of the device as shown in fig. 4 or 6 is utilised and it func¬ tions in the following manner: Normal state: Corresponds to the normal state as described in example A. Delay phase: Corresponds to the delay phase as described in example A. Transitional phase: Corresponds to the transitional phase as described in examp¬ le A. Locking state: If free spinning occurs, however, the piston gear will be mo¬ ved into locking engagement with the co-operating teeth in the pump body and lock itself. In this way the planetary gears have their rotation hindered and the device now works as an differential lock. Return phase: Corresponds to the return phase as described in example A. Re-cycle: Corresponds to the re-cycle as described in example A. The embodiment of the device as described and shown may be modified in many ways; for example, the locking teeth may be replaced by a hub coupling. Furthermore, the piston and cy¬ linder may be designed so that the internal oil leakage may be altered in accordance with the displacement of.the piston away from the initial position, for example by giving the cy- linder a slightly conical design. Moreover, the number of gears in the pump may be increased and other forms of gear utilised. In addition the piston gear may be held in its initial position by aids of magnets.

Claims: CLAIMS : 1. A hydraulic braking and/or locking device, comprising a fluid gear pump with a closed-circuit oil system, where the pump body (6) have a pair of bores (3), each of which con- tains a gear (1 and 4), of which a first driven gear (1) is rotably meshed with a second drive gear (4) and fixed to an axle shaft (5) which extends out of the pump body (6); and where the braking effect of the device, eg transmitted to a rotating journal, is depending on the throttling of the oil circuit, c h a r a c t e r i z e d i n that the first dri¬ ven gear (1), at the same time as it is meshed with the se¬ cond drive gear (4), is arranged axially slideable, like a piston, in its bore (3), and that the oil inlet and the oil outlet are connected to a respective end of the bore (3) . 2. A device as defined in claim 1, c h a r a c t e r i z ¬ e b y means for holding the piston in its initial posit¬ ion, eg springs (7), the weight of the piston gear (fig. 3) etc. 3. A device as defined in claim 1 or 2, c h a r a c t e - r i z e d b y means which hinder further rotation of the gears, when the piston gear (4) makes contact with one of the cylinder ends, eg by forming the contact surfaces with co-operating teeth, lugs, barbs (8, 9) etc. 4. A device as defined in claim 3, c h a r a c t e r i z - e d b y means (8, 9) wich hinders further rotation of the gears, when the piston gear (1) makes contact with any one end of the cylinder. 5. Use of the device as defined in claim 1 or 2 as a drum. brake, pulley brake and the like, eg for ropes, chains, belts etc. 6.. Use of the device as defined in claim 3 as a drum lock, pulley lock and the like, eg for a self-winding car seat- belt. 7. Use of the device as defined in claim 1 and 2 as a differential brake, or as defined in claim 4 as a combined differential brake/lock for a vehicle, by coupling one of the dif.planetary gears (12) to the device; for example by fitting the device with play in the space between the dif¬ ferential side gears (10, 11) and the planetary gears (12), with the axle shaft (5) of the device extending out of the pump body at both sides and replacing the planetary gear shaft in the differential case, one of the planetary gears being fixed to and the other rotating freely on the axle shaft (5); and coordinating the internal oil leakage "by¬ pass", the piston gear (1) stroke and the spring tension, so that when the vehicle is being driven with tractive wheels, the device is inactive, when slipping occurs the device offers gradually increasing braking effect and when spinning take place the device acts as a differential bra¬ ke/lock.

Inventors: BRUUN ARNE, BRUUN, ARNE
Applicants: BRUUN ARNE, BRUUN, ARNE
Application year: 1985
Main classification: F16H1
IPC codes: F16D59, F16H48