KR100855458B1 - Steering drive axle for heavy equipment - Google Patents

Abstract

The present invention provides a casing on which a drive shaft rotated by engine power of heavy equipment is supported, a ring gear coupled to an end thereof, a housing fixedly coupled to a ring gear, and carrier spindles rotatably supported and coupled to an interior of the housing; And a carrier hub wheel on which wheels are fixedly coupled to carrier spindles while wrapping an end of the housing, a sun gear coupled to a drive shaft, a planet gear meshed with the sun gear and a ring gear, and an outer circumference of the carrier spins. In the planetary power transmission drive axle for heavy equipment, comprising a plurality of brake discs coupled, a plurality of friction plates inherent between the brake discs, and brake pistons that closely contact the plurality of brake discs and the friction plates to generate a braking force. ; A brake drum fitted to a drive shaft located inside the casing, a plurality of auxiliary brake disks coupled to an outer circumference of the brake drum, a plurality of auxiliary friction plates embedded between the auxiliary brake disks, and an auxiliary brake piston are included. It provides a planetary power transmission drive axle for heavy equipment, characterized in that configured.

Brake, heavy equipment, axle, multi-plate

Description

Planetary power transmission drive axle for heavy equipment {STEERING DRIVE AXLE FOR HEAVY EQUIPMENT}

1 is a cross-sectional view showing a conventional planetary power transmission drive axle for heavy equipment.

2 is a cross-sectional view showing a planetary power transmission drive axle for heavy equipment according to an embodiment of the present invention.

Figures 3a and 3b is a perspective view showing the main part of the planetary power transmission drive axle for heavy equipment according to FIG.

Figure 4 is a cross-sectional view showing a planetary power transmission drive axle for heavy equipment according to another embodiment of the present invention.

5 is a perspective view showing the main part of the planetary power transmission drive axle for heavy equipment according to FIG.

6 is a cross-sectional view showing a planetary power transmission drive axle for heavy equipment according to another embodiment of the present invention.

7 is a perspective view showing the main part of the planetary power transmission drive axle for heavy equipment according to FIG.

<Explanation of symbols for main parts of the drawings>

100: Planetary power transmission drive axle for heavy equipment

110: drive shaft 110a: spline

111: sun gear 120: casing

121: auxiliary friction plate 121a: spline

122: hollow part 123: mounting groove

123a: spline 124: stop plate

125: stop ring 126: brake pressure oil port

130: ring gear 131: coupling bolt

140: housing 140a: spline

141: friction plate 141a: spline

142: bearing 143: packing

144: brake pressure oil port 145: assembly groove

150: carrier spindle 150a: spline

151: planetary gear 152: brake disc

152a: spline 153: connecting boss

153a: connecting groove 154: snap ring

155: coupling hole 156: spline shaft

156a: external thread 157: shaft pin groove

157a: locking pin hole 158: euro

159: shaft pin 159a: locking pin hole

159b: spring pin 160: carrier hub wheel

161: insertion protrusion 162: coupling hole

163: fixing bolt 164: coupling boss

164a: spline ball 165: lock nut

170: brake piston 180: brake drum

180a, 180b, 181a: Spline 181: Auxiliary Brake Disc

190: auxiliary brake piston

The present invention relates to a planetary power transmission drive axle for heavy equipment, and more particularly, braking of heavy equipment that was in operation by simultaneously braking carrier spindles integrally coupled with a carrier hub wheel on which wheels are mounted and a drive shaft for transmitting power to the carrier spindles. It relates to a planetary power transmission drive axle for heavy equipment that is configured to be more stable and accurate.

In general, the configuration of the conventional planetary power transmission drive axle for heavy equipment is, as shown in Figure 1, the drive shaft 10 is rotated by the engine power of the heavy equipment, and the drive shaft 10 horizontally rotatable therein A casing 20 arranged and supported, a ring gear 30 that is integrally fixedly coupled to the casing 20 end, a housing 40 that is fixedly integrally connected to the ring gear 30, and Carrier spins 50 rotatably supported and coupled to the ring gear 30 and the housing 40, and partially fixed to the carrier spins 50 while partially enclosing the ends of the housing 40. A carrier hub wheel 60 on which wheels are mounted, a sun gear 11 fixedly coupled to an end of the drive shaft 10, and a sun gear 11 and a ring gear 30 to be engaged with each other to rotate and revolve; Rotatably supported on spindle 50 Of the housing 40 to be embedded between the planetary gear 51 and the plurality of brake disks 52 which are supported and coupled with a predetermined distance on the outer circumference of the carrier spindle 50, and the brake disk 52. A plurality of friction plates 41 supported and coupled to an inner circumferential surface, and brake pistons 70 and the like installed on the housing 40 to generate a braking force by bringing the plurality of brake disks 52 and the friction plate 41 into close contact with each other. It is comprised.

In the conventional heavy-duty planetary power transmission drive axle 1, when the drive shaft 10 rotates, the sun gear 11 coupled to the end of the drive shaft 10 is rotated, and at the same time meshed with the sun gear 11. As the planetary gear 51 rotates and rotates along the ring gear 30, the carrier spindle 50 and the carrier hub wheel to which the planetary gear 51 is coupled are supported and the carrier hub wheel rotates. The wheel mounted on the wheel rotates to allow heavy equipment to travel.

In addition, when the brake piston 70 is operated in a state in which the carrier hub wheel 60 is rotating to bring the brake disc 52 and the friction plate 41 into close contact, the brake disc 52 that is rotated is supported. As the rotational force of the carrier spindles 50 is decelerated and stopped, at the same time, the wheels mounted on the carrier hub wheels 60 stop as the carrier hub wheels 60 integrally coupled with the carrier spindles 50 stop. Thus, the driving of heavy equipment can be decelerated and stopped.

The conventional planetary power transmission drive axle for heavy machinery such as the braking of the wheel to be rotated, that is, the carrier hub wheel 60 and the carrier spindle 50 is mounted on the wheel, the braking of heavy equipment was running quickly and accurately, Since backlash does not occur due to accurate braking, it is possible to stably carry out operations such as digging trenches or laying sewer pipes using heavy equipment without shaking.

However, the conventional heavy-duty planetary power transmission drive axle for braking the carrier spindle 50 directly increases the gear ratio of the sun gear 11 and the planetary gear 51 and the ring gear 30 to the drive shaft 10. Since the brake disk 52 and the friction plate 41, in which direct braking is performed, have a relatively large size due to braking, the volume of the entire steering drive axle becomes unnecessarily large.

In addition, due to the high frictional heat of the brake disk 52 and the friction plate 41 which are mutually rubbed, the temperature inside the housing 40 is rapidly increased, which affects not only the braking device but also the peripheral device, which impairs durability and braking performance. There was a problem causing.

In particular, since the oil present between the brake disc 52 and the friction plate 41 is deteriorated and extinguished as its temperature increases rapidly during braking operation, the brake disc 52 and the friction plate 41 are rapidly cooled by oil. As a result, there was a problem of lowering the braking performance and of decreasing the life of the brake disc 52 and the friction plate 41.

SUMMARY OF THE INVENTION The present invention has been proposed in view of the above-mentioned problems, and an object thereof is to provide a carrier hub wheel on which wheels are mounted, and a carrier spindle integrally coupled with a wheel and a driving shaft transmitting power to the carrier spindles simultaneously. The aim is to provide a planetary power transmission drive axle for heavy machinery that can be braked more stably and quickly and accurately.

According to a feature of the present invention for achieving the above object, the drive shaft is rotated by the engine power of the heavy equipment, the casing is horizontally rotatably disposed to support the drive shaft therein, and the casing end integrally and integrally A ring gear that is fixedly coupled, a housing that is fixedly coupled to the ring gear in series, a carrier spin that is rotatably supported and coupled to the ring gear and the inside of the housing, and partially covers an end of the housing, Carrier hub wheel that is fixedly coupled in succession, the wheel is mounted, the sun gear fixedly coupled to the end of the drive shaft, and the rotatable support to the carrier spindle by the shaft pin to engage and rotate with the sun gear and the ring gear The planetary gear is to be spaced apart from the outer periphery of the carrier spin A plurality of brake discs coupled to each other, a plurality of friction plates supported on an inner circumferential surface of the housing so as to be inherent between the brake discs, and brake pistons installed in the housing to generate a braking force by bringing the plurality of brake discs into contact with the friction plates. In the conventional heavy-duty planetary power transmission drive axle comprising: a brake drum that is supported and coupled to the drive shaft located inside the casing, and a plurality of auxiliary brake disks that are supported and bonded at regular intervals on the outer circumference of the brake drum; And a plurality of auxiliary friction plates supported and coupled to the inner surface of the casing so as to be embedded between the auxiliary brake discs, and auxiliary brake pistons installed on the casing to generate a braking force by bringing the plurality of auxiliary brake disks and the auxiliary friction plates into close contact with each other. Became There is provided a planetary power transmission drive axle for heavy equipment, characterized in that configured.

Hereinafter, the planetary power transmission drive axle for the heavy equipment of the present invention will be described in detail with reference to the accompanying drawings.

2 is a cross-sectional view showing a planetary power transmission drive axle for heavy equipment according to an embodiment of the present invention, Figures 3a and 3b is a perspective view showing the main part of the planetary power transmission drive axle for heavy equipment according to FIG.

Planetary power transmission drive axle 100 for the heavy machinery of the present invention as shown is a drive shaft 110 is rotated by the engine power of the heavy equipment, the drive shaft 110 is casing is horizontally rotatably disposed and supported therein. (120), the ring gear 130 which is integrally fixedly coupled to the casing 120 end, the housing 140 is fixedly and integrally coupled to the ring gear 130, and the ring gear 130 And the carrier spins 150 rotatably supported and coupled to the inside of the housing 140, and the wheels are mounted to be integrally fixed to the carrier spins 150 while partially wrapping the end of the housing 140. The carrier hub wheel 160, the sun gear 111 is fixedly coupled to the end of the drive shaft 110, the sun gear 111 and the ring gear 130 is engaged with the carrier by the shaft pin 159 to rotate and rotate Rotatable on spindle 150 The housing 140 is embedded between the planetary gear 151 coupled to the support, a plurality of brake disks 152 supported and coupled to the outer circumference of the carrier spindle 150 at a predetermined interval, and the brake disk 152. Brake piston 170 is installed in the housing 140 to generate a braking force by bringing a plurality of friction plates 141 supported and coupled to the inner circumferential surface of the) and the plurality of brake discs 152 and the friction plate 141 to each other. In the conventional planetary power transmission drive axle for heavy equipment 100,

The brake drum 180 is inserted into and supported by the drive shaft 110 positioned inside the casing 120, and the plurality of auxiliary brake discs 181 are coupled to the outer peripheral edge of the brake drum 180 at a predetermined interval. And a plurality of auxiliary friction plates 121 supported and coupled to an inner surface of the casing 120 to be inherently interposed between the auxiliary brake discs 181, and the plurality of auxiliary brake discs 181 and the auxiliary friction plates 121. It is configured to include an auxiliary brake piston 190 installed in the casing 120 to generate a braking force.

Inside the casing 120, a hollow portion 122 is rotatably supported and coupled to the drive shaft 110, and an assembly in which the carrier spindle 150 is rotatably supported is coupled to the inside of the housing 140. A recess 145 is formed, and the casing 120, the ring gear 130, and the housing 140 are integrally fixed to each other by a coupling bolt 131 so as to be separated from each other, and the housing 140 and the casing ( There is oil in the interior of 120).

The mounting recess 123 into which the brake drum 180 is inserted is formed in the casing 120 so as to communicate with the hollow portion 122, and the outer circumference of the drive shaft 110 and the inner circumferential surface of the brake drum 180. And splines that are integrally coupled to each other and engaged with each other on the inner surface of the mounting groove 123 and the outer circumference of the auxiliary friction plate 121 and the outer circumference of the brake drum 180 and the inner circumference of the auxiliary brake disk 181, respectively. 110a, 180a, 123a, 121a, 180b, and 181a are formed, and the auxiliary brake disc 181 and the auxiliary friction plate 121 are formed at the inlet of the mounting recess 123 by the auxiliary brake piston 190. Stop plate 124 is supported and is configured to be supported so as not to be pushed, the stop ring 125 is fitted to the end of the mounting groove 123 adjacent to the stop plate 124, the stop plate 124 is more stable It is configured to be fixed.

Insertion protrusions 161 are integrally formed on one side of the central portion of the carrier hub wheel 160 to be coupled to each other, and the insertion protrusions 161 of the carrier hub wheel 160 are fitted to the carrier spindles 150. The connecting boss 153 having the connecting groove 153a therein is integrally formed to protrude, and is connected to the connecting boss 153 of the carrier spindle 150 and the peripheral edge of the carrier hub wheel 160 in a line with each other. Coupling holes 155 and 162 are formed to match each other, and fixing bolts 163 are fastened to the coupling holes 155 and 162 so that the carrier hub wheel 160 and the carrier spins 150 are connected to each other. It is configured to be detachably integrally coupled.

In some cases, as shown in FIGS. 4 and 5, the coupling boss portion 164 having the spline hole 164a therein is integrally formed to protrude continuously in one side of the center of the carrier hub wheel 160. The spline shaft 156, which is inserted into and supported by the spline hole 164a of the carrier hub wheel 160, is integrally formed to protrude in succession at one end of the carrier spindle 150, and at the end of the spline shaft 156. A lock nut 165 is formed on the male screw 156a of the spline shaft 156 of the carrier spindle 150 exposed to the outside through the spline hole 164a of the carrier hub wheel 160. Is fastened, the carrier hub wheel 160 and the carrier spins 150 may be configured to be detachably coupled integrally.

The shaft pin 159 is formed so that the planetary gear 151 meshed with the sun gear 111 and the ring gear 130 is rotatably coupled to the carrier spins 150 so as to be integrally connected to the carrier spins 150. Preferably, the shaft pin 159 is fitted with a snap ring 154 to prevent separation of the assembled planetary gear 151.

In addition, the shaft pin 159 to the rotatable support coupled to the sun gear 111 and the ring gear 130 and the planetary gear 151 rotatably to the carrier spins 150, as shown in Figures 6 and 7 As described above, the carrier spins 150 are formed separately from each other, and a axial pin fitting groove 157 into which the shaft pins 159 are fitted is formed at a peripheral portion of the carrier spins 150, and the shaft pins 159 and the carrier are formed. Lock pin holes 159a and 157a are formed on the outer circumference of the spindle 150, and spring pins 159b are coupled to the lock pin holes 159a and 157a, so that the shaft pins 159 are carrier spins. It may be configured to be integrally coupled with the 150 detachably.

Bearing 142 is embedded between the inner peripheral surface of the assembling groove 145 of the housing 140 and the outer periphery of the connecting boss 153 of the carrier spindle 150 or the coupling boss 164 of the carrier hub wheel 160. In addition, a flow path 158 is formed on the carrier spins 150 to smoothly flow oil, and the carrier spins 150 and the carrier hub wheel 160 supported and coupled to the housing 140 rotate smoothly. Of course, it is configured to suppress the generation of frictional heat as much as possible to cool quickly.

Splines 150a, 152a, 140a and 141a which are meshed with each other are formed on the coupling surface of the carrier spins 150 and the brake disk 152 and the coupling surface of the housing 140 and the friction plate 141, respectively. The brake disc 152 and the friction plate 141 are configured to be stably supported and coupled to the carrier spins 150 and the housing 140, respectively.

A packing 143 may be coupled between the housing 140 and the carrier hub wheel 160 to block oil leakage and entry of foreign substances from the outside, and the brake piston may be connected to the housing 140 and the casing 120, respectively. Brake pressure oil ports 144 and 126 to which the brake oil for operating the 170 and the auxiliary brake piston 190 are injected and discharged are formed.

The action of the inventors of the planetary power transmission drive axle 100 for heavy equipment configured as described above is as follows.

When the drive shaft 110 is rotated by the driving force of the engine, the sun gear 111 coupled to the end of the drive shaft 110 is rotated, and the planetary gear 151 meshed with the sun gear 111 rotates at the same time. In addition, the carrier spindles are revolved along the ring gear 130, and at the same time, the carrier spindles 150 rotatably supported by the planetary gear 151 and the carrier hub wheel 160 coupled to the spindle rotate simultaneously. The wheels mounted at 150 are rotated to allow the heavy equipment to travel.

In addition, the brake piston 170 installed in the housing 140 and the casing 120 in a state in which the carrier hub wheel 160 and the carrier spindle 150 is mounted on the wheel by the rotation of the drive shaft 110 is rotated. And the auxiliary brake piston 190 are operated at the same time to bring the brake disk 152 and the friction plate 141 and the auxiliary brake disk 181 and the auxiliary friction plate 121 in close contact with each other, the brake disk 152 is supported and coupled The rotational force of the drive shaft 110 to which the carrier spins 150 and the auxiliary brake disc 181 are supported and coupled is gradually decelerated to stop immediately, and at the same time, the carrier hub wheel 160 fixedly coupled to the carrier spindles 150. As the stop, the wheel mounted on the carrier hub wheel 160 is stopped so that the heavy equipment that is running can be decelerated and stopped immediately.

According to the present invention, the brake drum 180 is further provided with means for preventing arbitrary flow in the axial direction of the drive shaft in the state fitted to the drive shaft (110). This is provided with a key groove 112 to be spaced apart by the thickness of the brake drum 180 on the outer periphery of the drive shaft 110 and two stop keys 114 are installed in the key groove 112 of the drive shaft with the brake drum 180 interposed therebetween. To make it possible. The stop key 114 may be of the general type (O-ring) to be fitted on the shaft while being elastically opened by a predetermined forceps as shown in FIG. 3A or 7. However, the stop key 114 is not limited thereto, and various key means capable of performing a function of preventing axial flow of the brake drum may be alternatively employed.

As described above, the planetary power transmission drive axle for heavy equipment of the present invention rotates by simultaneously generating braking force at two places of the drive shaft to transfer power to the carrier spins and the carrier spindles integrally coupled to the carrier hub wheel on which the wheel is mounted. Since the wheels are decelerated and stopped, the braking of the heavy equipment while driving is effected quickly and accurately.

In addition, the inventors of the present invention, the planetary power transmission drive axle for heavy equipment, by braking the carrier spin mounted on the wheel directly to the backlash phenomenon between the conventional sun gear and planetary gear and ring gear when working such as trench digging or water and sewer pipe laying using heavy equipment Since the wheel is not fixed and the back and forth of the wheel does not occur, it is effective to safely and accurately carry out tasks such as lifting or digging of objects using heavy equipment without shaking the wheel.

In addition, the inventors of the present invention, the planetary power transmission drive axle for heavy equipment generates a braking force at both the carrier spindle and the drive shaft at the same time can reduce the braking force required in the carrier spindle portion, and consequently friction heat by the brake disc and the friction plate Can be suppressed as much as possible, thereby reducing the wear of the brake disc and the friction plate and reducing the size of the brake disc and the friction plate as a whole to ensure the diversity of the size of the planetary power transmission drive axle. .

Claims (7)

Drive shaft 110 is rotated by the engine power of the heavy equipment, the casing 120 is horizontally rotatably disposed and supported coupled to the drive shaft 110, the casing 120 is fixed to the end of the casing 120 integrally Ring gear 130 to be connected to the housing 140 is fixedly coupled to the ring gear 130 in series, and carrier spins rotatably supported and coupled to the ring gear 130 and the housing 140. 150 and the carrier hub wheel 160 to which the wheels are mounted to be integrally fixed to the carrier spindles 150 while partially wrapping the end of the housing 140, and fixed to an end of the drive shaft 110. The planetary gear 151 is rotatably supported and coupled to the carrier spindle 150 by the shaft pin 159 to be engaged with the sun gear 111 and the sun gear 111 and the ring gear 130 to be rotated and rotated. On the outer circumference of the carrier spindle 150, A plurality of brake discs 152 supported and spaced apart from each other, a plurality of friction plates 141 supported and coupled to an inner circumferential surface of the housing 140 to be embedded between the brake discs 152, and the plurality of brake discs 152. In the conventional heavy-duty planetary power transmission drive axle (100) consisting of a brake piston (170) installed in the housing (140) to generate a braking force by bringing the friction plate (141) into close contact with each other, The brake drum 180 is inserted into and supported by the drive shaft 110 positioned inside the casing 120, and the plurality of auxiliary brake discs 181 are coupled to the outer peripheral edge of the brake drum 180 at a predetermined interval. And a plurality of auxiliary friction plates 121 supported and coupled to the inner surface of the casing 120 to be inherently interposed between the auxiliary brake discs 181, and the plurality of auxiliary brake discs 181 and the auxiliary friction plates 121. The planetary power transmission drive axle for heavy machinery, characterized in that the auxiliary brake piston 190 is installed to be installed to the casing 120 to generate a braking force. According to claim 1, wherein the mounting groove 123 for inserting the brake drum 180 is formed in the casing 120, the outer periphery of the drive shaft 110 and the inner peripheral surface of the brake drum 180 and the Splines (110a), (180a), (123a) and (121a) are integrally engaged with each other on the inner circumference of the mounting recess (123) and the outer friction plate (121), respectively, and the entrance of the mounting recess (123) is formed. The planetary power transmission drive axle for heavy equipment, characterized in that the auxiliary brake disc 181 and the stop plate 124 is supported by the auxiliary brake piston 190 so that the auxiliary friction plate 121 is not pushed. The method of claim 1, wherein the insertion protrusion 161 is integrally formed on one side of the central portion of the carrier hub wheel 160, and the insertion protrusion 161 of the carrier hub wheel 160 to the carrier spindle 150. The connecting boss 153 having a connecting groove 153a into which the fitting is inserted is formed to protrude continuously, and is connected to the connecting boss 153 of the carrier spindle 150 and the peripheral edge of the carrier hub wheel 160. Coupling holes 155 and 162 are formed to be aligned with each other in a straight line, and fixing bolts 163 are fastened to the coupling holes 155 and 162, and the carrier hub wheel 160 and the carrier are fastened. Planetary power transmission drive axle for heavy equipment, characterized in that the spindle 150 is configured to be integrally coupled. The method of claim 1, wherein the coupling boss 164 having the spline hole 164a therein is formed integrally and continuously protruding from one side of the central portion of the carrier hub wheel 160, one end of the carrier spins 150 The spline shaft 156, which is inserted into and coupled to the spline hole 164a of the carrier hub wheel 160, is integrally formed to protrude in succession, and a predetermined section male screw 156a is formed at an end of the spline shaft 156. In addition, the lock nut 165 is fastened to the male screw 156a of the spline shaft 156 of the carrier spindle 150 exposed to the outside through the spline hole 164a of the carrier hub wheel 160, and thus the carrier hub wheel ( Planetary power transmission drive axle for heavy equipment, characterized in that the 160 and the carrier spinner 150 is configured to be detachably integrally coupled. The shaft pin 159 of any one of claims 1 to 4, wherein the planetary gear 151 meshed with the sun gear 111 and the ring gear 130 is rotatably supported and coupled to the carrier spins 150. ) Is a planetary power transmission drive axle for heavy equipment, characterized in that is configured to protrude integrally with the carrier spins (150). The shaft pin 159 of any one of claims 1 to 4, wherein the planetary gear 151 meshed with the sun gear 111 and the ring gear 130 is rotatably supported and coupled to the carrier spins 150. ) Is formed separately from the carrier spins 150, the axial pin fitting groove 157 is formed in the peripheral portion of the carrier spins 150, the shaft pin 159 is fitted, the shaft pin 159 and the carrier spins ( Lock pin holes 159a and 157a which are coincident with each other are formed at the outer circumference of the 150, and spring pins 159b are coupled to the lock pin holes 159a and 157a, so that the shaft pins 159 are carrier spins 150. And a planetary power transmission drive axle for heavy equipment, characterized in that it is configured to be integrally coupled with each other. According to claim 1, wherein the brake drum 180 is fitted to the drive shaft 110; Optionally in the axial direction of the drive shaft 110 by the key groove 112 provided on the drive shaft 110 and the stop key 114 fitted into the key groove 112 with the brake drum 180 therebetween. Planetary power transmission drive axle for heavy equipment, characterized in that it does not flow.

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