JPS61135872A - Traveling device of crawler-type car - Google Patents

Abstract

PURPOSE:To prevent damage and liquid leakage due to obstructions by setting a parking brake, an outer piping and a distributor of a hydraulic motor from the center of the width of the center of a crawler shoe up to its inner end so as to form a piping for connecting them together in a casing. CONSTITUTION:A gear reduction system 31 is mounted on the outer side of a casing 3, and its output end is connected to the outer end art of a revolving wheel 21 through a bolt 32. A hydraulic driving system composed of a hydraulic motor 12, the reduction system 31 and the revolving wheel 21 is located within the width of a crawler shoe 33, a bracket 34 is provided, and the shoe 33 travels through a shaft 35. A timing plate 17 formed with a distribution valve of the hydraulic motor 12 is combined with the flange part 16 of a controlling block 10. Also, a parking brake 44 is housed in the flange part 16 and is detachably attached thereto by a bolt 45 to be located within the width of the crawler shoe 33, and consequently length of piping is saved.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a traveling device for a crawler-type vehicle such as a power shovel.

(Prior art) As a conventional crawler vehicle running device, the
-125442 publication and JP-A-49-108470
There is something described in the No.

(Problems to be Solved by the Invention) In these devices, the hydraulic motor is placed on one side of the sprocket, the reducer is placed on the other side of the sprocket, and the hydraulic motor and the reducer are connected by a relatively long connecting shaft. It was connected by. Since the connecting shaft is thus relatively long, the entire device becomes long in the width direction of the crawler shoe. For this reason, for example, in the system disclosed in Japanese Utility Model Application Publication No. 49-125442, the hydraulic motor protrudes outward from the width of the crawler shoe, making it easy for obstacles such as rocks to collide with the hydraulic motor. . Also, JP-A-49-1084
70. In the device described in the publication, a radial piston type hydraulic motor with a short axial length is used as the hydraulic motor, and the entire device is placed within the width of the crawler shoe. The diameter of the motor becomes larger, which not only increases the overall size of the traveling frame to which the hydraulic motor is attached, but also prevents interference between the crawler shoe link attached to the inner surface of the crawler shoe and the traveling frame. In order to improve earth removal performance, it is necessary to increase the gap between the link of the crawler vehicle and the running frame, that is, the distance from the center of the sprocket to the running frame. As a result, the distance from the center of the sprocket to the end face of the hydraulic motor becomes large, and when the sprocket is engaged at the center of the crawler shoe width or when the sprocket is engaged with a crawler shoe with a narrow crawler shoe width, the hydraulic There is a problem in that the external piping to the motor and the rotary valve part of the hydraulic motor protrude outside the width of the crawler shoe, and these parts collide with obstacles and are damaged, causing liquid leakage.

SUMMARY OF THE INVENTION An object of the present invention is to provide a traveling device for a crawler-type vehicle in which the width of the crawler shoe is made as narrow as possible and accessory parts such as a hydraulic drive mechanism and external piping are arranged within the width of the crawler shoe.

(Means for Solving the Problems) A traveling device for a crawler type vehicle according to the present invention has a lug-shaped portion in which a through hole penetrating from the outside to the inside is formed and has an arcuate outer end in the crawler traveling direction. and a reinforcing rib part integrally attached to the outer edge of the lug part so as to extend inward from the outer edge, a running frame located within the width of the crawler shoe, and an axial piston inserted into the casing. A hydraulic drive mechanism that has a rotary wheel driven by a hydraulic motor via a type hydraulic motor and a speed reduction mechanism, and is attached to the traveling frame by inserting the casing into a through hole so that it is located within the width of the crawler shoe. and a parking brake housed in the casing, a connecting part connected to the lug-shaped part, an inner casing part extending inward from the connecting part, and an inner casing part extending outward from the connecting part. The rotary ring has a sprocket tooth portion having teeth formed on its outer periphery, and an outer cylindrical portion extending outward from the sprocket tooth portion. The rotating ring is rotatably supported by the outer casing via two bearings spaced apart by a predetermined distance so that the sprocket teeth of the rotating ring are located approximately at the center of the crawler shoe width, and the outer cylinder of the rotating ring is A part is connected to the output end of the reduction mechanism, and a pair of external pipes through which working fluid of the hydraulic motor flows in and out is connected to the lug from the side opposite to the outer end of the lug-shaped part in the crawler running direction, across the through-hole. The reinforcing ribs run parallel to the inside of the reinforcing ribs along the inner side of the crawler shoe to protect the external piping and the inner casing, and the parking brake and external piping run from the center of the width of the crawler shoe to the inner edge of the crawler shoe. The distribution valve of the hydraulic motor is located, and the speed reduction mechanism is located from the center of the width of the crawler shoe to the outer end thereof.

(Example) An embodiment of the present invention will be described below with reference to the drawings.

In Fig. 1.2, reference numeral 1 denotes a running frame of a crawler-type vehicle, and this running frame l has a lug-like part in which a through hole 2 is formed from the outside to the inside, and has an arc-shaped outer end in the crawler running direction. 1a and a reinforcing rib portion 1 integrally attached to the outer edge of the lug portion 1a so as to extend inward from this outer edge.
b, and this traveling frame 1 is located within the width of the crawler sieve, which will be described later. 3 is a casing, and this casing 3 includes an insertion portion 4a having the same diameter as the through hole 2, and an insertion portion 4a.
The connecting portion 4 includes a flange portion 4b located further outward and continuous therewith and having a larger diameter than the insertion portion 4a. Then, the insertion portion 4a of the casing 3 is inserted into the through hole 2 from the outer end opening of the through hole 2 until the inner end surface of the flange portion 4b comes into contact with the outer surface of the traveling frame 1. The flange portion 4b is detachably attached to the traveling frame 1 by a plurality of bolts 5 screwed into the flange portion 4b from the inside to the outside so as to connect both the flange portions 4b. In addition, the casing 3 is connected to the flange portion 4 of the connecting portion 4.
It has an outer casing part 6 extending outward from b and having a smaller diameter than both the insertion part 4a and the flange part 4b.

The outer casing part 6 includes a first diameter part 6a that is continuous with the outer end surface 4C of the flange part 4b, a second diameter part 6b that is located outward from the first diameter part 6a and has a smaller diameter than the first diameter part 6a, and a second diameter part 6b that is located outward from the first diameter part 6a and has a smaller diameter than the first diameter part 6a. 1 diameter portion 6a
and a step 6C that connects the second diameter portion 6b. The aforementioned connecting portion 4 and outer casing portion 6 constitute a fixed holding member 7 as a whole. Further, the casing 3 has an inner casing part 8 extending inward from the connecting part 4, and this inner casing part 8 is detachably attached to the inner end surface of the fixed holding member 7 via bolts 9. The control block 10 is located inward from the traveling frame 1. A cylindrical hydraulic motor chamber 11 is formed inside the fixed holding member 7 and extends outward from the inner end surface. The bottom surface 11a of this hydraulic motor chamber 11 is a flange portion 4.
It is located outward from the outer end surface 4C of b. Reference numeral 12 denotes a swash plate type hydraulic motor with a cartridge structure, which is inserted from the inner end opening of the hydraulic motor chamber 11 and housed in the fixed holding member 7;
This hydraulic motor 12 is fixed by having its outer end abut against the bottom surface tla of the hydraulic motor chamber 11, and by inserting a pin 13 at the outer end into a hole 14 in the bottom surface 11a of the hydraulic motor chamber 11. It is positioned on the holding member 7. Therefore, when removing this hydraulic motor 12, it must be done from the inside. The hydraulic motor 12 has a rotating shaft 15,
The outer end of the rotating shaft 15 passes through the fixed holding member 7 and projects outward from the fixed holding member 7. The control block 1
0 has a flange portion 16 on the side close to the fixed holding member 7, and this flange portion 16 is detachably attached to the inner end surface of the fixed holding member 7 by the bolts 9. 17
is a timing plate on which a distribution valve for the hydraulic motor 12 is formed, and since this timing plate 17 is connected to the flange portion 16 via a pin 18, the bolt 9
This allows positioning of the seven rungs 16 and the timing plate 17 of the hydraulic motor 12, and thereby allows relative positioning of the swash plate 19 of the hydraulic motor 12 and the timing plate 17. A bearing 20 is provided adjacent to the timing plate 17 inside the flange portion 16, and the internal portion of the rotating shaft 15 protruding from the fixed holding member 7 via the bearing 20 is rotatably supported by the flange portion 16. It's been like that. 21 is a rotating ring, and this rotating shaft 21 has a sprocket tooth part n located in the center and having teeth formed on the outer periphery, an inner cylindrical part part extending inward from the sprocket tooth part n, It has an outer cylindrical portion U extending outward from the sprocket tooth portion n and having an outer diameter approximately equal to the outer diameter of the inner cylindrical portion mill. The tooth width center plane M of this sprocket tooth portion n is the rotation axis 15.
A hollow hole with a smaller diameter than the flange portion 4b and a larger diameter than the outer casing portion 6 is formed inside the zero-rotation ring 21 located inward from the outer end of the crawler shoe and located at the center of the width of the crawler shoe. The outer casing part 6 is loosely fitted into the hollow hole,
At this time, the inner end of the inner cylindrical die is located at a small distance from the outer end surface 4C of the flange portion 4b. Rotating wheel 2
The hollow hole r of 1 includes a first inner diameter part 27a located at the inner end and facing the first diameter part 6a of the outer casing part 6, and a first inner diameter part 27a located outward from the first inner diameter part 27a. A second inner diameter part 27b having a slightly smaller diameter and facing the first diameter part 6a of the outer casing part 6, and both first and second inner diameter parts 27a and 27b located outward from the second inner diameter part 27b. A third inner diameter part 27c having a larger diameter and facing the second diameter part 6b of the outer casing part 6, a first step 27d that connects the first inner diameter part 27a and the second inner diameter part 27b, and a second inner diameter part 27b and third
It has a second step 27e that is continuous with the inner diameter portion 27c,
This second step 27e is located substantially on the same plane as the step 6C. The outer end surface 4c of the flange portion 4b and the first diameter portion 6a of the outer casing portion 6 are placed in an annular chamber formed by the first inner diameter portion 27a of the hollow hole and the first step 27d of the hollow hole H. A sealing member housing is housed therein, and this sealing member seals the gap between the casing 3 and the rotating wheel 21. Two bearings 4, 291 are installed at a predetermined distance apart in the axial direction between the outer periphery of the second diameter part 6b of the outer casing part 6 and the inner periphery of the third inner diameter part 27c of the hollow hole n. 4. The rotating shaft 21 is connected to the outer casing part 6 via 29'.
is rotatably supported. The bearings 4 and 4' have an outer diameter equal to the inner diameter of the outer cylindrical portion U of the rotating shaft 21.

The bearing 4.4 degrees is axially centrally facing and L"
The inner end 29. of the bearing 29', which is located on the outer side of the bearings 4 and 4', is disposed such that the tooth width center plane M of the sprocket tooth portion n is located therebetween. The hydraulic motor chamber 11 is arranged such that the bottom surface 11a of the hydraulic motor chamber 11 is located outward from 'a. Further, the inner surface N of the sprocket tooth portion 22 is located within the axial width of the bearing 4 located inwardly of the bearings 4 and 29'. 30 is a cylindrical collar which is interposed between the bearings 29 and 4° and has an inner end abutting the bearing 4 and an outer end abutting the bearing 4';
This collar 30 restricts the bearings 29, 4'' from moving in the axial direction. 31 is a gear reduction mechanism provided on the outer side of the casing 3, and the input end of this gear reduction mechanism 310 is connected to the rotating shaft 15. The output end of the gear reduction mechanism 31 is connected to the outer end of the rotary shaft 21 via a bolt 32, and decelerates the rotation of the rotary shaft 15 of the hydraulic motor 12 while simultaneously applying output torque. The hydraulic motor 12, the speed reduction mechanism 31, and the rotating wheel 21 described above constitute a hydraulic drive mechanism in the present invention, and this hydraulic drive mechanism is a crawler shoe. 33 is a crawler shoe, and a bracket 34 is provided at the inner center of the crawler shoe blade, and a shaft 35 is fixedly attached to this bracket 34. The teeth of the sprocket tooth portion 22 of the rotary wheel 21 are engaged with the rotary wheel 21, and when the rotary wheel 21 rotates, the crawler shoe blades run via the bracket 34 and the shaft 35.The above-mentioned fixed holding member 7
, hydraulic motor 12, rotating shaft 21, and gear reduction mechanism 31
As a whole, constitutes a drive assembly which is provided on the outer side of the traveling frame 1 and drives the crawler shoe 33 to travel. In Fig. 4.6, inside the flange portion 16, there are passages for the pressurized fluid to flow in and out of the parking brake, which will be described later, between the radial passages communicating with the passage group, and between the passages and the radial passages. a shuttle valve 39 interposed between;
is provided, and this shuttle valve region is configured to restrict fluid in one direction by a spring 40. Section 2.4.5.
In FIG. 6, a hydraulic motor 1 is installed inside the flange portion 16.
A pair of inflow and outflow passages 41 and 41' are formed through which a fluid for driving and rotating the inflow and outflow passages 41 and 41' are formed.
One end of the 41° angle opens to the outer circumferential surface of the flange portion 16 near the outer radial end of the radiation passage 38, and the other end communicates with holes 17a and 17'a formed in the timing plate 17.

The holes 17a, 171a communicate with piston chambers 43, 43' formed in the cylinder block 42 of the hydraulic motor 12 which rotates together with the rotating shaft 15. A parking brake is housed in the flange portion 16 on the side remote from the hydraulic motor 11, and is removably attached by bolts 6 so as to be positioned within the crawler shoe width. The parking brake 44 has a substantially cylindrical cylinder member 46, and a passageway is provided between the outer circumference of the outer end of the cylinder member 46 and the inner circumference of the flange portion 16, which communicates with a passageway 47 connected to the shuttle valve 39. is formed. This passage 48 is
A passage 4 formed between the flange portion 16 and the rotating shaft 15
9 and the flange portion 16 and the outer peripheral wall of the bearing 20 are connected in series to the drain chamber 51 of the hydraulic motor chamber 11, and the drain generated in the parking brake 44 is drained into the drain chamber. It is designed to lead to 51. Further, the drain chamber 51 also collects drain leaked internally from the hydraulic motor 12. This drain chamber 51 communicates with a drain passage 52 formed in the flange part 16 as shown in FIG. It communicates with the attached discharge pipe 5, and discharges the drain accumulated in the drain chamber 51 to the outside. The cylinder member 46 has, on its inner periphery, a large diameter part 46a located on the inside, a small diameter part 46b located on the outside, and a stepped part 46c that connects the large diameter part 46a and the small diameter part 46b. , has. Audience is large diameter section 4
This is a closing member that is fixedly attached to the inner end of the cylinder member 46 with a bolt 57 so as to close the inner end opening of the cylinder member 6a.
6 forms a parking brake chamber. This brake chamber holder is located inward from the hydraulic motor chamber 11.

Reference numeral 59 denotes a moving member, and this moving member 59 has a first diameter portion 5 on its outer periphery that is located on the inner end side and has the same diameter as the large diameter portion 46a.
9a, a second diameter part 59b located on the outer end side and having the same diameter as the small diameter part 46b, and a stepped part 59c that connects the first diameter part 59a and the second diameter part 59b. This moving member 59 has its first diameter portion 59a as the large diameter portion a,
The second diameter portion 59b is slidably housed in the parking brake chamber 58 so as to engage with the small diameter portion 46b, so that the parking brake chamber is moved between the inner spring chamber and the outer spring chamber. It is partitioned into a brake element chamber 61.

62 is a spring stored in the spring chamber ω,
The inner end of this spring 62 is held in a spring hole 63 formed in the closing member, and the outer end thereof is held in a spring hole 64 formed in the moving member 59.
Press 9 so that it always moves outward. A through hole is formed in the center of the moving member 59 to communicate the spring chamber ω and the brake element chamber 61, and the brake element chamber 61 communicates with the passage mallet. Therefore, the brake element chamber 6 is connected to the passage 4B in the spring chamber (A).
1. Fluid can flow in through the through hole, and drain can flow out from between the spring chambers into the passage 4B through the brake element chamber 61 and the through hole. The aforementioned passage 48.
49 and the through hole 65 as a whole constitute a passageway that guides the drain generated between the spring chambers and the brake element chamber 61 to the drain chamber 5I of the hydraulic motor chamber 11. U
is a hydraulic chamber, and this hydraulic type port is located between the large diameter portion 46a and the stepped portion 46G of the cylinder member 46, and the second portion of the moving member 59.
It is formed by a diameter portion 59b and a stepped portion 59c. Reference numeral 68 denotes a passage formed in the cylinder member 46, one end of which communicates with the passageway, and the other end communicates with the hydraulic pressure chamber 67. When high-pressure fluid flows into the hydraulic chamber φ through the passage 68, the moving member 59 is moved inward against the spring 62. 69 is a brake element housed in the brake element chamber 61, and this brake element 69 has a fixed brake plate 7 whose radial inner end is spline-coupled to the inner end of the rotating shaft 15.
0 and its radial outer end is the small diameter portion 46 b of the cylinder member 6
a movable brake plate 71 spline-coupled to the fixed brake plate 70 and facing the fixed brake plate 70; when the movable member 59 moves outward by the action of a spring 62, the fixed brake plate 70 and the movable brake plate 71 When engaged, the rotary shaft 15 of the hydraulic motor 12 is braked. The aforementioned cylinder member 46,
The closing member 56, the moving member 59, the spring 62, the hydraulic chamber 67 and the brake element 69 collectively constitute the parking brake 44.
When no fluid is flowing into the hydraulic pressure chamber 67, the spring 62 presses the moving member 59 outward to brake the rotating shaft 15 of the hydraulic motor 12, and the hydraulic pressure chamber 67 is When high-pressure fluid flows in, the moving member 59 is pushed inward against the spring 62 to release the rotating shaft 15 of the hydraulic motor 12 from braking. A control valve 72 is attached to the outer circumferential surface of the flange portion 16 near the parking brake 44 with bolts 73 so that it can be deposited thereon. The aforementioned flange portion 16 and control valve 72 collectively constitute the control block 10, and the control block 10 and the parking brake a are provided on the inner side of the traveling frame 1 as a whole to control the operation of the drive assembly. control assembly 7 for controlling
4. As shown in FIG. 3.4.5.6, the control valve 72 has an inflow and outflow passage 75 that communicates with the inflow and outflow passages 41 and 411, respectively, and allows fluid to flow in and out of the inflow and outflow passages 4 and 411, respectively. 75', a first switching valve 76 as a counterbalance valve, and a second switching valve 78 as a relief valve connected to the first switching valve 76 via a pair of passages 77 and 77'. , has. The first switching valve 76 is integrally attached to the inner casing part 8 so as to be located inside the reinforcing rib part 1b in the width direction of the crawler shoe. The inflow/outflow passage 75.75'' includes passages 79.79'', 80, 80'' that directly communicate with the first switching valve 76, and a first
The first switching valve 76 is composed of a passage 81.81' connecting the switching valve 76 and the inflow/outflow passage 41.41'.
．． As shown in detail in FIG. 5, the spool 82 has a spool wing which is movably held and which opens and closes the inflow and outflow passages 75, 75' by its movement, and the axis of this spool 82 is perpendicular to the crawler running surface. The first switching valve 76 also includes check valves 84 and 84' provided inside the spool blade and pressed in one direction by a spring shell 83', and a check valve 84 and 84',
841 and passage 79.791 and check valve 84
．． A hole δ formed in the spool area so as to communicate between 841 and the passage 81. And, this Kyuben version, 87g and passage boy,
(Main) A hole formed in the spool 82 to communicate between 88' and a hole formed in the spool area to communicate between 871 and the outside of both ends of the spool 82. 89', and springs 9 provided at both ends of the spool 82 so that the spool blades always return to the neutral position.
0', a damper valve 91.911 provided opposite to both end surfaces of the spool blade and configured to regulate the sliding distance and speed of the spool 82, and this damper valve 91.9.
1' and a chamber enclosure 921 surrounded by the spool 82. Reference numeral 93 denotes a selection path that communicates with the first switching valve 76 at one end and the radiation passage blade at the other end, and this selection path 93 selectively communicates with the inflow and outflow passage 75.75° on the high pressure side by movement of the spool blade. to guide high pressure fluid to the radiation passage vanes. As shown in detail in FIG. 3, the second switching valve 78 is a passage with a freely slidable shuttle valve body having a hollow legend between '77' and a flange at the middle part of the outer periphery. , has a stopper field 97' that restricts the sliding movement of the shuttle valve by abutting it against a flange on the outer periphery, and an inner periphery that allows the above-mentioned shuttle valve and the relief valve described below to slide. A guide shell, 98', having a surface is provided.

A relief valve 101.1 having a small hole 100.100' at its tip is adapted to return the shuttle valve 96 to the neutral position by a spring 991 in the guide shell 98'.
01' is slidably provided. This relief valve 1
At the rear of 01.101', a guide frame 981 is screwed and fixed, and a small hole 103.
Viloft relief valve 104.1 crimped to 103f
04', an adjustment screw 106.106f that makes it possible to adjust the body 105.105' and a screw 102.102', and a nut 107 that fixes and holds this adjustment screw 106.106'. .1
071.10B, 10B' and pilot relief valve 104.1041 bypass fluid passage 77.771
A passageway 109,109' for discharging the water is received. Further, in front of the guides 98, 98', a passage 7 is provided.
A passageway 110.110' is provided in communication with 7.771 for applying fluid pressure to the shuttle valve %. 1st
．． 4.5.6, the end of the control valve 72 on the side remote from the parking brake 44 has an inflow and outflow passage 75.7.
Outflow and inflow pipes 11 as external pipes each communicating with 5"
1.112 is attached via a joint 113 with a bolt 114 so that it can be attached freely. This inflow and outflow pipe 111.1
At 12, pressurized fluid is inflowed or flowed, and the fluid is caused to flow in and out of the passages 79.79° and 80.80° of the control valve 72. The inflow/outflow pipes 111 and 112 are run vertically in parallel inside the reinforcing rib portion 1b along the inner side surface of the lug portion 1a from the side opposite to the outer end of the lug portion 1a in the crawler running direction across the through hole 2. The reinforcing ribs 1b protect the inflow and outflow pipes 111, 112 and the inner casing part 8. The above-mentioned parking brake, external piping 111, 112, and distribution valve of the hydraulic motor are located from the center of the width of the crawler running surface to its inner end, and the reduction mechanism 31 is located from the center of the width of the crawler shoe to its outer end. It is located.

Next, the operation of one embodiment of the present invention will be explained.

First, a case in which pressurized fluid flows in through the inflow/outflow pipe 111 and fluid flows out through the outflow/inflow pipe 112 will be described. In this case, the fluid that has flowed into the passage 79 out of the fluid that has flowed into the inflow and outflow passage 75 from the inflow and outflow pipe 111 enters the hole 85 in the spool 82 of the first switching valve 76 and moves the check valve 84 against the spring 83. It flows into the push-open passage 81 . The fluid that has flowed into this passage 81 flows into the piston chamber of the hydraulic motor 12 through the inflow and outflow passage 41 within the flange portion 16.
It acts to push the swash plate 19 and rotate the rotating shaft 15 of the hydraulic motor 12.

On the other hand, among the fluid that has flowed into the inflow and outflow passages 75,
The fluid that has flowed into the spool 82 enters the hole 88 in the spool 82 through the gap in the spring 90 that returns the spool 82 of the first switching valve 76.
The ball valve 87 in the spool 82 is pushed open against the spring 86 and flows into the chamber 92 through the hole 89. As the fluid flowing into the chamber increases, it acts to push the end face of the spool 82, causing the spool blade to slide against the spring 90'. This continues until the tip of this sliding spool 82 hits the damper valve 91', and this spool 82
Each passage is switched by the movement of . By this switching operation of the spool 82, the passage 79 and the selection passage 93 are communicated with each other through the hole in the spool 82, and the spool 82 is connected between the inflow/outflow passage 41' and the passage 79'.
2 through the hole δ, and the flow of fluid from the passage 80 into the interior of the chamber is stopped.

As a result of this selective passageway being selectively communicated with passageway 79 through which high pressure fluid flows, the high pressure fluid within passageway 79 is diverted to the selection passageway. The fluid that has flowed into the selection passageway is guided by the radial passage wings of the flange portion 16 and flows into the shuttle valve 39, which is pushed open against the spring 40 to communicate the radial passage wings with each passage. On the other hand, communication between the passage wing and the passage 47 is cut off to stop discharging fluid from the parking brake U. The fluid that has flowed into the radiation passage 38 flows into the hydraulic pressure chamber a of the parking brake 44 via the passage shaft and the lug. The fluid flowing into the hydraulic chamber 67 acts to move the moving member 59 inward against the spring 62. This movement of the movable member 59 separates the movable brake plate 71 from the fixed brake plate 70, and the rotary shaft 15 becomes rotatable. At this time, for the first time, hydraulic motor 1
2 is rotated, and the fluid that flows out after driving and rotating the hydraulic motor 12 flows into the piston chamber 43' of the hydraulic motor 12.
The high-pressure pressurized fluid flowing into the outflow and inflow pipe 111 automatically operates the first switching valve 76, and then flows out from the inflow and outflow pipe 112 through the inflow and outflow passages 41'' and 75'. The brake 44 releases the braking of the rotating shaft 15 of the hydraulic motor 12, and at the same time acts to drive and rotate the rotating shaft 15 of the hydraulic motor 12.

Next, a case will be described in which the inflow of pressurized fluid from the inflow/outflow pipe 111 is stopped and the operation of the hydraulic motor 12 is stopped. When the fluid that has been flowing into the passage 79, 80 of the control valve 72 from the inflow/outflow pipe 111 stops flowing, the spool 82 of the first switching valve 76 is returned to the neutral position by the spring 90'. At this time, the fluid in the chamber 92 passes through the fitting gap between the spool 82 and the damper valve 91, passes through the passage 80, and is discharged from the inflow/outflow pipe 111. Further, when the spool 82 is returned, the passage 79 and the selection passage 93 are disconnected. Therefore, the shuttle valve 39 is returned by the spring 40, the radial passage wing and the passage 37 are disconnected, and the passage 47 is brought into communication with the entire passage. At this time, the moving member 59 is pressed by the spring 62 and moves outward, and the fluid in the hydraulic chamber 67 is discharged into the passage 48 through the passage 47. The fluid discharged into this passage 48 is transferred to the passage 49, (
The water flows into the drain chamber 51 of the hydraulic motor chamber 11 through the drain passageway 52 and the discharge pipe 55, where it collects together with the internal drain of the hydraulic motor 12 itself, and is then discharged to the outside through the drain passage 52 and the discharge pipe 55. . As the movable member 59 moves, the movable brake plate 71 engages with the fixed brake plate 70 and applies a brake to the rotating shaft 15 of the hydraulic motor 12. In this case, the kinetic energy of the driven vehicle causes the hydraulic motor 12 to continue to rotate in the direction in which it rotates when pressurized fluid is flowing in from the inflow/outflow pipe 111. 41 and acts as a pump to discharge the fluid to the inflow/outflow passage 41''. In this way, when the hydraulic motor 12 acts as a pump, the passage 81 in the control valve 72
This high pressure fluid enters the passage 77° and moves the shirttle valve part in the direction of the guide wall against the spring spring, and the flange 95 on the outer periphery of the shirttle valve 96 moves forward of the guide 98. It acts to move the shuttle valve portion until it hits the stopper portion 97. When the outer periphery of the shuttle valve S hits the stopper portion 97, the passage 110'' and the hollow hole 94 communicate with each other, and the fluid flows through the shuttlecock. into the hollow hole 94 of the valve 96 and into the relief valve 101.101.
The pilot relief valve 104.1041 is pushed open against the spring 102.102' by passing through the small hole 100.100° at the tip of the relief valve 101.101'. At this time, high-pressure fluid acts as a back pressure on one viroft relief valve 1041 side, and the fluid in the inflow and outflow passage 41 is sucked into the other pilot relief valve 104 side by the action of the pump of the hydraulic motor 12. Since the low-pressure fluid acts as a back pressure through the passage n, the pilot relief valve 104 opens and the high-pressure fluid flows into the passageway.

At this time, due to the throttling action of the small hole 100 of the relief valve 101, out of the force of the spring 99 and the force of back pressure that press the relief valve 101 toward the shuttle valve 96 side, the force due to the back pressure is The high pressure fluid in the hollow hole 94 decreases rapidly at the same time as the spring 9 opens.
9 to push open the relief valve 101. The relief valve 101 opens and the hollow hole 94 and passage 110
When the two are in communication, the mounting body flows into the passage 77 and the passage 65, passes through the inflow and outflow passage 41 in the flange portion 46, and is connected to the hydraulic motor 1.
2 is inhaled. That is, when the inflow of pressurized fluid from the inflow/outflow pipe 111 is stopped, the parking brake 44 acts to apply braking to the rotating shaft 15 of the hydraulic motor 12 by the functions of the first switching valve 76 and the shuttle valve 39.
Further, the first switching valve 76 and the second switching valve 78 function to circulate the fluid so that the fluid in the hydraulic motor 12 does not become insufficient. In addition, in the above-mentioned action,
If the fluid sucked into the hydraulic motor 12 from the inflow/outflow passage 41 becomes insufficient due to delay in operation or compression of the fluid, the check valve 84 is opened due to this negative pressure since the inflow/outflow passage 41 becomes negative pressure. The fluid is sucked in from the inflow/outflow pipe 111 by the amount of insufficient capacity.

The pressurized fluid flows in from the inflow and outflow pipe 111.
Although the case where the fluid flows out from the inflow/outflow pipe 112 has been described, the same operation as described above is performed when the pressurized fluid flows in from the inflow/outflow pipe 112 and the fluid flows out from the outflow/inflow pipe 111. Note that, in this case, the hydraulic motor 12 will be rotated in the opposite direction.

(Effects of the Invention) In the present invention, the axial piston type hydraulic motor is inserted into the casing that rotatably supports the rotary ring, so the hydraulic motor is placed adjacent to the reduction mechanism to transfer the power between them. The connecting shaft for transmission can be removed. Therefore, the distance from the end face of the hydraulic motor to the end face of the reduction mechanism can be shortened, and even if the crawler shoe width is made as narrow as possible, accessories such as the hydraulic drive mechanism and external piping can be arranged within the crawler shoe width. I can do it. Further, in the present invention, since the hydraulic motor is of an axial piston type, its diameter can be made smaller than that of a conventional radial piston type hydraulic motor. therefore,
By reducing the overall size of the running frame to which the hydraulic motor is attached, it is possible to avoid interference between the links of the crawler shoes and the running frame, and the running frame can be brought close to the center of the sprocket teeth. The crawler shoe width can also be made as narrow as possible by placing the running frame close to the center of the sprocket teeth in this manner. In addition, by placing the traveling frame close to the center of the sprocket teeth, a space is secured between the inner surface of the traveling frame and the inner end of the crawler shoe, and the reinforcing rib portion is extended from the lug portion inward in the width direction of the crawler shoe. A pair of external piping is made to run parallel to the inside of the reinforcing rib part along the inner surface of the lug-shaped part, and the external piping and the inner casing part are wrapped around the reinforcing rib part by the rotation of the crawler shoe. It can be protected from rocks etc.

Furthermore, if necessary, it is also possible to attach a lid or the like to the reinforcing rib portion to completely seal and protect the external piping and the inner casing portion. Further, the reinforcing rib portion can also increase the bending rigidity and torsional rigidity of the lug portion. Further, as described above, since the overall size of the traveling frame can be reduced, the space between the traveling frame and the crawler shoe can be increased, and soil removal performance can be improved. Therefore, there is no need to increase the pitch circle of the sprocket teeth,
There is no loss of propulsion. Further, in the present invention, since an axial piston type hydraulic motor having high speed and low torque characteristics is used, the parking brake can be of a small capacity, and as a result, the parking brake can be disposed inside the casing. Furthermore, in the present invention, the parking brake, external piping, and distribution valve of the hydraulic motor are located from the center of the width of the crawler shoe to its inner end, and the deceleration mechanism is located from the center of the width of the crawler shoe to its outer end. Therefore, the connecting boat for the external piping can be provided close to the distribution valve of the hydraulic motor and the parking brake, and the piping connecting these can be formed inside the casing. Therefore, unlike conventional devices in which the distance from the connection port of the external piping to the distribution valve of the hydraulic motor or the parking brake is long, there is no need for long piping to connect these parts.

[Brief explanation of the drawing]

The drawings show an embodiment of a traveling device for a crawler-type vehicle according to the present invention, and FIG. 1 is a side view thereof, FIG. 2 is a sectional view taken along the line A-A in FIG. 1, and FIG. 1. FIG. 4 is a sectional view taken along C-C in FIG. 1. FIG. 5 is a sectional view taken along D-D in FIG. 4. FIG. 6 is a JfS symbol. It is a circuit diagram expressed in . 1------1 traveling frame, 1a-- lug-like part, 1b-- reinforcing rib part, 2-- casing, 3-- casing, 4-- 1 connection part, 6------ one outer casing section, 8-- inner casing section, 12--=- hydraulic motor, tS --- one rotating shaft, 21------ One rotation wheel, 22-- Sprocket teeth, 11-11 inner cylindrical section, 24-- outer cylindrical section, 29.29' - one bearing , 31.--1111 gear reduction mechanism, 33-------- crawler shoe, 44-------- parking brake, 76-------
1 Counterbalance valve, 78--Relief valve, 111.112-111.-Outflow and inflow pipe.

Claims (1)

[Claims] A through hole penetrating from the outside to the inside is formed, and the lug part has an arcuate outer end in the crawler running direction and is integrally attached to the outer edge of the lug part so as to extend inward from the outer edge. It has a running frame located within the width of the crawler shoe, and an axial piston-type hydraulic motor inserted into the casing, and a rotating wheel driven by the hydraulic motor via a speed reduction mechanism. The casing is inserted into the through hole and attached to the traveling frame so as to be positioned within the width of the crawler shoe, and the hydraulic drive mechanism is installed on the traveling frame, and the parking brake is housed in the casing. a connecting portion, an inner casing portion extending inwardly from the connecting portion, and an outer casing portion extending outwardly from the connecting portion; a rotating wheel having formed sprocket teeth and an outer cylindrical portion extending outwardly from the sprocket teeth so that the sprocket teeth of the rotating wheel are located approximately at the center of the crawler shoe width; is rotatably supported by the outer casing part via two bearings spaced apart by a predetermined distance, and the outer cylindrical part of the rotating ring is connected to the output end of the reduction mechanism, so that the working fluid of the hydraulic motor flows in and out. A pair of external piping is made to run in parallel inside the reinforcing rib part along the inner side surface of the lug part from the side opposite to the outer end of the lug part in the crawler running direction across the through hole. The parking brake, external piping and hydraulic motor distribution valve are located from the center of the width of the crawler shoe to its inner edge, and the distribution valve of the hydraulic motor is located from the center of the width of the crawler shoe to its outer edge. A traveling device for a crawler-type vehicle, characterized in that a deceleration mechanism is located at.