RU2082052C1 - Hydraulically-locked differential bevel gear - Google Patents

Abstract

FIELD: mechanical engineering. SUBSTANCE: locking mechanism of bevel gear is made in form of toothed insert with hole. Generating surface of hole performs function of cylinder of direct-acting hydraulic pump at hydraulic resistance. Toothed insert is mounted between two bevel gears; at different angular velocities of above-mentioned gears, inset is reciprocating on axle of satellites and works as hydraulic pump. Satellite axle performs function of at least one piston expulsor. EFFECT: enhanced reliability. 5 cl, 9 dwg

Description

 The present invention relates to the field of gears for communicating rotational motion, in particular to differentials with hydraulic resistance for vehicles.

 Blocking the differentials used in the power train of vehicles increases their cross-country ability. The differential lock with hydraulic resistance has the most preferred characteristic, since its blocking coefficient depends on the difference in the angular velocities of the output shafts.

 A known differential with hydraulic resistance [1] in which a blocking plunger pump is connected between the output shaft and the housing. The housing has radial holes in the form of a cylinder block in which the plungers are located. A cam sprocket is mounted on the splines of the output shaft. The plungers are pressed against the cams by springs. In the plunger, a valve device with a calibrated hole is installed, designed to release a compressible fluid. The cylinder block has inlets with valves through which fluid from the differential housing enters the cylinder chambers. A special device provides a constant flow of fluid into the differential housing. With direct movement and the absence of running one of the gears, the plunger pump does not work. When the wheels rotate at different angular speeds, the cams run on the plungers, which, making a reciprocating motion, push the fluid through the calibrated holes. Increased fluid pressure leads to an increase in the rotation resistance of the running gear. The magnitude of this resistance depends on the size of the calibrated hole and the magnitude relative to the angular velocity of the gear.

 The main disadvantage of the differential with hydraulic resistance is the complicated differential design: and plunger pump cylinders: made in the differential housing: it is difficult to restore when worn.

 Closest to the claimed technical solution is a locked bevel differential [2] comprising a housing: in which bevel gears are placed: interacting with each other through two satellites: mounted on one axis: located perpendicular to the geometric axis of the bevel gears. On bevel gears there is a blocking mechanism made in the form of friction clutches: each of which is made in the form of a package of friction washers: located between the surfaces of bevel gears and the housing. On the surface of the rear of the bevel gears and on the side surface of the housing cup, respectively, slots and grooves are made, into which friction washers are inserted. When the traction forces on the input shafts change, the package of friction washers of the locking mechanism is compressed under the action of axial forces arising in the engagement of the teeth of the bevel gears and satellites. In this case, the friction force between the bevel gears and the housing increases and the differential is locked. The differential blocking coefficient is small due to insufficient axial forces. The design of the differential is complex, since additional execution of the splines and grooves on the bevel gears and the housing, respectively, is necessary.

 The purpose of the invention is the creation of a simple and reliable locking device that is inserted into the case of a conical two-satellite differential without changing its design. This is achieved by the fact that in the hydraulic differential lock, according to the invention, the locking device is made in the form of a gear insert located on the axis of the satellites between two opposing gears. The insert, in addition to the reciprocating rotation, has the ability to make rectilinear reciprocating movements on the axis of the satellites, since its height in the plane of the axis of the satellites is less than the distance between the opposing satellites by an amount that ensures the divergence of the top of the teeth on one side, when fully engaged with the gear teeth on the other hand, during rectilinear movement on the axis of satellites.

 To interact with the teeth of the gears of the insert from two opposite sides, at least one end or at least one side of the two ends has at least one tooth. The teeth and their arrangement are designed to ensure that the tops of the teeth of the insert diverge from the tops of the teeth of the opposing gear on one side when the insert is linearly moved in the plane of the axis of the satellites and fully engaged with the teeth of the second gear on the other side. The axial hole of the insert is made as a cylinder of a direct-acting piston hydraulic pump, divided into two working chambers by a throttle ring. The working chambers communicate with the liquid medium through a check valve. The axis of the satellites is made as stationary displacing pistons.

 When a car is skidding with one wheel in the differential, the gears move together. From the interaction with the gear teeth, the insert performs reciprocating movements, displacing the fluid from one working chamber to another through a calibrated orifice of the throttle. The conversion of mechanical energy to flow energy occurs. The rate of fluid flow through the calibrated hole limits the speed of running gear.

 The edges of the teeth do not experience load at the moment of transition from meshing with one gear to meshing with another, since the teeth are loaded only when the insert is moved in a straight line with the teeth fully engaged.

The essence of the present invention is illustrated by a detailed description of the hydraulic locking device for a specific embodiment and the drawings:
FIG. 1 shows a general view of the differential with an insert in the context of the plane of the axis of the gears perpendicular to the plane of the axis of the satellites;
FIG. 2 is a general view with hydraulic locking in the context of the plane of the axis of the satellites with a schematic representation of gearing;
FIG. 3 general view of the hydraulic lock in the context of the axis of the satellites;
FIG. 4 gear insert with teeth on both sides at one end (side view in section AA);
FIG. 5 is the same as in FIG. 4 (top view);
FIG. 6 9 is a schematic illustration of an insert at various positions relative to bevel gears with a diagram above (front view).

 Hydraulic locking is an integral part of the bevel differential (Fig. 1, 2), in the housing 1 of which there are two satellites 2 and two opposing gears 3. The hydraulic locking device located between the opposing gears 3, consists (Fig. 3) of gear insert 4, set on a prefabricated axis, consisting of a two-stage rod 5 and a nozzle 6, which are both piston-displacers and the axis of the satellites 2. The axial hole of the insert 4 is made (Fig. 4, 5) as a cylinder of a direct-acting hydraulic pump CA 7, divided by the throttle ring 8 into two working chambers 9, communicating through the channel 10 with the oil medium of the gearbox by means of a check valve 11. In the throttle ring 8 there is a calibrated hole 12, which can be an annular gap between the rod 5 and ring 8. From one end on the opposite sides of the insert 4 there are teeth 13. With an even number of teeth of the satellite 2, the teeth 13 of the insert 4 are located on opposite sides with an offset equal to half the pitch of the teeth of the gear 3. The width of the insert 4 (Fig. 3) from the cavity 14 of the teeth 13 on the one hand to the peaks 13 on the other hand is equal to the distance between the tops of the teeth of the opposing gears 3, and the side faces 15 of the teeth 13 of the insert 4 are made with the possibility of lateral mixing of the insert 4 at an angle that allows the insert 4 to move rectilinearly in the plane the axis of the satellites to the divergence of the tops of the teeth 13 of the insert 4 with the tops of the teeth of the gear 3 on one side when fully engaged with the teeth of the gear 3 on the other side. With the locking device, where the teeth 13 of the insert 4 are on both sides, the insert 4 can be collapsible at both ends for ease of assembly.

 The hydraulic locking device allows you to install it in existing conical two-satellite differentials without changing their design.

The conical differential with hydraulic lock works as follows
With the rectilinear movement of the car, insert 4 remains stationary relative to the body and rotates with it. When the vehicle is skidding with one wheel (the right wheel is skidding in Fig. 6–9), when the gears 3 move in the differential, insert 4 can be in any position. For example (Fig. 6), the insert 4 is engaged with one of the gears 3 after a rectilinear movement on the axis towards the circular motion of the teeth of this gear 3 until the tooth peaks diverge from the opposite side. From the buoyant axial forces in the gear engagement, the insert 4 rotates on the axis and engages with the opposing gear 3, which rotates relative to the first and opposite side (Fig. 7). Insert 4, as a movable cylinder of a direct-acting pump 7, during rectilinear movement on a fixed axis, in which the thickening of the two-stage rod 5 and the cup 6 are piston-displacers, squeezes the oil from one chamber 9 to another (Fig. 8). The working chambers 9 are always filled with oil, since the leak through the capillary slots between the cylinder 7 and the pistons 5, 6 is compensated by a non-return valve 11, which draws oil through the channel 10 during rarefaction in the chambers 9. The axial forces arising from the interaction of the tooth lateral faces cannot the insert 4 is meshing, since the teeth 13 of the opposite side of the insert 4 are located on the tops of the teeth of the opposing gear 3. To exit the meshing, the insert 4 must be linearly moved axially to such a distance that against the teeth 13 tavki 4 mezhzubovye depressions stood gear 3. After this discrepancy vertices Box 4, again turning on the axis, is engaged with the opposite gear 3 (Fig. 9).

 So, when running one of the gears 3, with the reciprocating movement of the insert 4, when oil is displaced from one working chamber 9 to another through the calibrated hole 12 of the throttle 8, mechanical energy is converted into flow energy. The speed of oil flow through the calibrated hole 12 limits the speed of the rectilinear movement of the insert 4, thereby limiting the speed of the running gear 3. When turning the car or rolling an obstacle around the wheel, the speed of running gear 3 is small and the oil manages to push out of the chamber into the chamber through the calibrated hole 12. The lock does not effects on the handling of the car, but prevents slipping with one wheel.

Claims (5)

 1. A conical differential with hydraulic locking, comprising a housing, two bevel gears, two satellites and a blocking mechanism, introduced into interaction with bevel gears, characterized in that the blocking mechanism is made in the form of a gear insert with a hole, the surface of which acts as a direct-acting hydraulic cylinder a pump with hydraulic resistance installed with the possibility at different angular speeds of the bevel gears of the reciprocating movement on satellite, fulfilling the function of at least one propellant piston.  2. The differential according to claim 1, characterized in that the axis of the satellites consists of a two-stage rod and a glass.  3. The differential according to claim 1, characterized in that the piston pump cylinder is divided into two working chambers in communication with the liquid medium through at least one non-return valve.  4. The differential according to claim 1, characterized in that the gear insert has at least one tooth from two opposite sides, at least one end or at least one side from two ends, while the relative position of the teeth on the opposite the sides of the insert depends on the parity of the teeth of the satellites.  5. The differential according to claim 1, characterized in that the teeth of the gear insert and its height in the plane of the axis of the satellites are made taking into account the discrepancy of the tops of the teeth of the insert with the tops of the teeth of the opposing gear on one side when the insert is linearly moved along the axis in full engagement with the teeth second gears on the other hand.

Images