JPS6130932B2 - - Google Patents

Description

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

(Prior Art) Conventional crawler-type vehicle traveling devices include those described in Japanese Utility Model Application Publication No. 125442/1982 and Japanese Patent Application Publication No. 108470/1983.

(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 to 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-49-108470
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. diameter 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 links attached to the inner surface of the crawler shoe and the traveling frame, and improves earth removal performance. In order to improve this, it is necessary to increase the gap between the crawler shoe link 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 distance to the hydraulic motor becomes large. There was a problem in that the external piping and the rotary valve part of the hydraulic motor protruded outside the width of the crawler shoe, and these parts collided with obstacles and were damaged, causing liquid leakage.

SUMMARY OF THE INVENTION An object of the present invention is to provide a traveling device for a crawler 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 in 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 traveling frame having a reinforcing rib part integrally attached to the outer edge of the lug part so as to extend inward from the outer edge, and an axial piston-type hydraulic motor and speed reduction mechanism inserted into the casing. a hydraulic drive mechanism having a rotating wheel driven by a hydraulic motor through the crawler shoe, the casing being inserted into a through hole so as to be positioned within the width of the crawler shoe, and attached to the traveling frame; The casing has a connecting portion connected to the lug-shaped portion, an inner casing portion extending inwardly from the connecting portion, and an outer casing portion extending outward from the connecting portion. The rotating 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, and the sprocket tooth portion of the rotating wheel has a crawler shoe width. A rotating ring is rotatably supported by the outer casing via two bearings spaced apart by a predetermined distance so as to be located approximately at the center of the rotating ring, and an outer cylindrical portion of the rotating ring is connected to the output end of the speed reduction mechanism, A pair of external piping, through which the working fluid of the hydraulic motor flows in and out, is connected to the reinforcing rib portion from the side opposite to the outer end of the lug portion in the crawler running direction, across the through hole, along the inner side surface of the lug portion. The outer piping and the inner casing are protected by reinforcing ribs that run vertically in parallel inside the casing.

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

In FIGS. 1 and 2, reference numeral 1 denotes a running frame of a crawler-type vehicle, and this running frame 1 has a lug-shaped portion having a through hole 2 formed from the outside to the inside, and having an arcuate outer end in the crawler running direction. 1a and a reinforcing rib 1b integrally attached to the outer edge of the lug portion 1a so as to extend inward from the outer edge, and the running frame 1 is located within a crawler shoe width to be described later. Reference numeral 3 denotes a casing, and this casing 3 includes an insertion portion 4a having the same diameter as the through hole 2, and an insertion portion 4 that is located outward from and continuous with the insertion portion 4a.
It has a flange portion 4b having a larger diameter than a, and a connecting 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 has a connecting portion 4
It has an outer casing part 6 which extends outward from the flange part 4b and has 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 continuous to the outer end surface 4c of the flange part 4b, a second diameter part 6b located outward from the first diameter part 6a and having a smaller diameter than the first diameter part 6a, and a second diameter part 6b which is located outward from the first diameter part 6a and has a smaller diameter than the first diameter part 6a. It has a step 6c that connects the first diameter portion 6a and the second diameter portion 6b. The aforementioned connecting portion 4 and outer casing portion 6
constitutes the fixed holding member 7 as a whole. Also,
The casing 3 has an inner casing part 8 extending inward from the connecting part 4, and the inner casing part 8 is removably attached to the inner end surface of the fixed holding member 7 via bolts 9. It consists of a control block 10 located inside the 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 located outward from the outer end surface 4c of the flange portion 4b. Reference numeral 12 denotes a swash plate type hydraulic motor with a cartridge structure inserted from the inner end opening of the hydraulic motor chamber 11 and housed in the fixed holding member 7. The outer end of the hydraulic motor 12 is connected to the hydraulic motor chamber 11 bottom surface 11
a, and the pin 13 at the outer end thereof is inserted into the hole 14 in the bottom surface 11a of the hydraulic motor chamber 11, thereby positioning it in the fixed 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 , and 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 10 has a flange portion 16 on the side adjacent 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 in which a distribution valve for the hydraulic motor 12 is formed, and this timing plate 17 is connected to the flange portion 16 via a pin 18.
Since the timing plate 1 of the hydraulic motor 12 is connected to the flange portion 16 by the bolt 9,
positioning with hydraulic motor 1 is possible.
The swash plate 19 of No. 2 and the timing plate 17 can be positioned relative to each other. A bearing 20 is provided inside the flange portion 16 adjacent to the timing plate 17, and the inner end 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 is designed so that Reference numeral 21 denotes a rotating ring, and this rotating ring 21 includes a sprocket toothed portion 22 located at the center and having teeth formed on the outer periphery, an inner cylindrical portion 23 extending inward from the sprocket toothed portion 22, An outer cylindrical portion 24 extends outward from the sprocket tooth portion 22 and has an outer diameter approximately equal to the outer diameter of the inner cylindrical portion 23. The tooth width center plane M of the sprocket tooth portion 22 is located inward from the outer end of the rotating shaft 15, and is located at the center of the crawler shoe width. A flange portion 4 is provided inside the rotating ring 21.
A hollow hole 27 is formed with a diameter smaller than b and larger than the outer casing part 6, and the outer casing part 6 is loosely fitted into the hollow hole 27. At this time, the inner end of the inner cylindrical part 23 is fitted with a flange. It is located at a slight distance from the outer end surface 4c of the portion 4b. The hollow hole 27 of the rotating ring 21 has 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 located outward from the first inner diameter part 27a. 27
The first part of the outer casing part 6 has a diameter slightly smaller than a.
A second inner diameter portion 27b facing the diameter portion 6a, and first and second inner diameter portions 2 located outward from the second inner diameter portion 27b.
The outer casing part 6 has a larger diameter than both 7a and 27b.
a third inner diameter portion 27c facing the second diameter portion 6b;
It has a first step 27d that connects the first inner diameter section 27a and the second inner diameter section 27b, and a second step 27e that connects the second inner diameter section 27b and the third inner diameter section 27c. 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
A sealing member 28 is housed in the annular chamber formed by the first inner diameter portion 27a of the hollow hole 27 and the first step 27d of the hollow hole 27, and this sealing member 28 connects the casing 3 and the rotating ring 21. Seal the gap between. Second diameter portion 6 of outer casing portion 6
Two bearings 2 are spaced apart from each other by a predetermined distance in the axial direction between the outer circumference b and the inner circumference of the third inner diameter portion 27c of the hollow hole 27.
9 and 29' are attached, and the rotating ring 21 is rotatably supported by the outer casing part 6 via these bearings 29 and 29'. The bearings 29, 29' have an outer diameter equal to the inner diameter of the outer cylindrical portion 24 of the rotary ring 21. The bearings 29 and 29' have a tooth width center plane M of the sprocket tooth portion 22 between their axial center planes L and L'.
The bearings 29,
The inner end 2 of the bearing 29' located on the outer side of the bearing 29'
The bottom surface 11a of the hydraulic motor chamber 11 is located outward from 9'a.
is located so that Further, the inner surface N of the sprocket tooth portion 22 is located within the axial width of the inner bearing 29 of the bearings 29, 29'. Reference numeral 30 denotes a cylindrical collar which is interposed between the bearings 29, 29' and has an inner end abutting the bearing 29 and an outer end abutting the bearing 29', and this collar 30 prevents the bearings 29, 29' from moving in the axial direction. regulations. Reference numeral 31 denotes a gear reduction mechanism provided on the outer side of the casing 3, and an input end of this gear reduction mechanism 31 is engaged with the outer end of the rotating shaft 15. The output end of the gear reduction mechanism 31 is connected to the outer end of the rotating wheel 21 via a bolt 32, and reduces the rotation of the rotating shaft 15 of the hydraulic motor 12 while simultaneously increasing the output torque and transmitting it to the rotating wheel 21. It is done like this. The aforementioned hydraulic motor 12, deceleration mechanism 31, and rotary wheel 21 constitute a hydraulic drive mechanism in the present invention, and this hydraulic drive mechanism is located within the crawler shoe width. 33 is Crawler Shu,
A bracket 34 is provided at the center inside the crawler shoe 33, and a shaft 35 is fixedly attached to the bracket 34. The teeth of the sprocket teeth 22 of the rotary wheel 21 engage with this shaft 35, and when the rotary wheel 21 rotates, the crawler shaft 33 is connected to the shaft 35 via the bracket 34 and the shaft 35.
It is like running there. The aforementioned fixed holding member 7, hydraulic motor 12, rotary wheel 21, and gear reduction mechanism 31 collectively constitute a drive assembly 36 that is provided on the outer side of the traveling frame 1 and drives the crawler shoe 33 to travel. 4 and 6, inside the flange portion 16 there is a passage 37 through which pressurized fluid flows in and out of the parking brake, which will be described later, and a radial passage 38 communicating with the passage 37.
A shuttle valve 39 is provided between the passage 37 and the radial passage 38, and the shuttle valve 39 is adapted to regulate fluid in one direction by a spring 40. In Figures 2, 4, 5, and 6,
A pair of inflow and outflow passages 41 and 41' through which fluid for driving and rotating the hydraulic motor 12 flows in and out is formed inside the flange portion 16.
One end of 1, 41' opens on the outer peripheral surface of the flange portion 16 near the radial outer end of the radiation passage 38, and the other end opens on the hole 17 formed in the timing plate 17.
a, 17'a. These holes 17a, 17'a
communicate with piston chambers 43, 43' formed within the cylinder block 42 of the hydraulic motor 12 which rotates together with the rotary shaft 15. A parking brake 44 is housed within the flange portion 16 on the side remote from the hydraulic motor 11 and is detachably attached by bolts 45 so as to be located within the width of the crawler shoe. This parking brake 44 has a substantially cylindrical cylinder member 46 , and a passage 48 that communicates with a passage 47 connected to the shuttle valve 39 is provided between the outer periphery of the outer end of the cylinder member 46 and the inner periphery of the flange portion 16 . is formed. This passage 48 is
It is connected to the drain chamber 51 of the hydraulic motor chamber 11 through a passage 49 formed between the flange part 16 and the rotating shaft 15 and a passage 50 formed between the flange part 16 and the outer peripheral wall of the bearing 20 in series. The drain generated in the parking brake 44 is transferred to the drain chamber 5.
It is designed to lead to 1. 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. The drain chamber 51 is connected to a discharge pipe 55, and drain accumulated in the drain chamber 51 is discharged to the outside. The cylinder member 46 has, on its inner periphery, a large diameter portion 46a located on the inner side, a small diameter portion 46b located on the outer side, and a stepped portion 46c that connects the large diameter portion 46a and the small diameter portion 46b. has. Reference numeral 56 denotes a closing member fixedly attached to the inner end of the cylinder member 46 with bolts 57 so as to close the inner end opening of the large diameter portion 46a. A parking brake chamber 58 is thus formed. This brake chamber 58 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 59a located on the inner end side and having the same diameter as the large diameter portion 46a, and a first diameter portion 59a located on the outer end side and having the same diameter as the small diameter portion 46b. The second diameter portion 59b and the first diameter portion 59
A step portion 59c that connects a and the second diameter portion 59b.
and has. The movable member 59 is slidably housed in the parking brake chamber 58 such that its first diameter portion 59a engages with the large diameter portion 46a and its second diameter portion 59b engages with the small diameter portion 46b. As a result, the parking brake chamber 58 is partitioned into an inner spring chamber 60 and an outer brake element chamber 61. 62 is a spring housed in the spring chamber 60, and the inner end of this spring 62 is connected to a spring hole 63 formed in the closing member 56.
The outer end of the movable member 59 is held in a spring hole 64 formed in the movable member 59.
Always press to move outward.
A spring chamber 60 is provided in the center of the moving member 59.
A through hole 65 is formed to communicate between the brake element chamber 61 and the brake element chamber 61, and the brake element chamber 61 communicates with the passage 48. For this reason, the spring chamber 60 is connected from the passage 48 to the brake element chamber 61 and the through hole 6.
5, fluid can flow in from the spring chamber 60 to the brake element chamber 61 and the through hole 65.
Condensate can drain into the passageway 48 via. The aforementioned passages 48, 49, 50 and the through hole 65 collectively form the spring chamber 60 and the brake element chamber 6.
A passage 66 is configured to guide the drain generated in the hydraulic motor chamber 11 to the drain chamber 51 of the hydraulic motor chamber 11. Reference numeral 67 denotes a hydraulic chamber, and this hydraulic chamber 67 is formed by the large diameter portion 46a and step portion 46c of the cylinder member 46, and the second diameter portion 59b and step portion 59c of the moving member 59. Reference numeral 68 denotes a passage formed within the cylinder member 46 , one end of which communicates with the passage 37 and the other end communicates with the hydraulic chamber 67 . When high-pressure fluid flows into the hydraulic chamber 67 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 70 whose radial inner end is spline-coupled to the inner end of the rotating shaft 15, and whose radial outer end is connected to the cylinder. a movable brake plate 71 that is spline-coupled to the small diameter portion 46b of the member 46 and faces the fixed brake plate 70; when the movable member 59 moves outward by the action of the spring 62, the fixed brake plate 7
0 and the movable brake plate 71 engage with each other, and the hydraulic motor 12
Braking is applied to the rotating shaft 15 of. The aforementioned cylinder member 46, closing member 56, moving member 59, spring 62, hydraulic pressure chamber 67 and brake element 69 collectively constitute the parking brake 44, and this parking brake 44 has a fluid in its hydraulic pressure chamber 67. When there is no flow, spring 6
2 presses and moves the movable member 59 outward to brake the rotating shaft 15 of the hydraulic motor 12, and when high-pressure fluid flows into the hydraulic pressure chamber 67, the movable member 59 is moved against the spring 62. The rotary shaft 15 of the hydraulic motor 12 is released from braking by being pushed inward. A control valve 72 is detachably attached to the outer peripheral surface of the flange portion 16 near the parking brake 44 with bolts 73. The aforementioned flange portion 16 and control valve 72 constitute the control block 10 as a whole, and the control block 10 and the parking brake 44 as a whole are provided on the inner side of the traveling frame 1 to operate the drive assembly 36. A control assembly 74 is configured to control the. The control valve 72
As shown in FIGS. 3, 4, 5 and 6, the inflow and outflow passages 75 and 75' communicate with the inflow and outflow passages 41 and 41', respectively, and allow fluid to flow in and out of the inflow and outflow passages 41 and 41', respectively. a first switching valve 76 as a counterbalance valve interposed in the middle of the switching valve 76, and a second switching valve 78 as a relief valve connected to the first switching valve 76 via a pair of passages 77, 77'. . 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 and outflow passages 75, 75' include passages 79, 79', 80, 80' that directly communicate with the first switching valve 76, and passages 79, 79', 80, 80' that directly communicate with the first switching valve 76.
6 and the inflow and outflow passages 41, 41'.
1,81'. As shown in FIGS. 3 and 5 in detail, the first switching valve 76 has a spool 82 that is movably held and opens and closes the inflow and outflow passages 75 and 75' by the movement of the spool 82. is perpendicular to the crawler running surface. The first switching valve 76 also includes check valves 84, 84' which are pressed in one direction by springs 83, 83' provided inside the spool 82, and passages 79, 79' between the check valves 84, 84' and passages 79, 79'. and a hole 85 formed in the spool 82 to provide communication between the check valves 84, 84' and the passages 81, 81'.
85' and springs 86, 86' provided inside both ends of the spool 82 to push the ball valve 8 in one direction.
7, 87', this ball valve 87, 87' and the passage 80,
Holes 88, 88' formed in the spool 82 to communicate between the ball valves 87, 87' and the outside of both ends of the spool 82; , 89', springs 90, 90' provided at both ends of the spool 82 so that the spool 82 always returns to the neutral position, and springs 90, 90' provided opposite to both end surfaces of the spool 82 so that the spool 82 always returns to the neutral position.
damper valves 91, 91' that regulate the sliding distance and speed of the damper valve 9;
Room 9 surrounded by 1,91' and spool 82
2,92'. Reference numeral 93 denotes a selection path which communicates with the first switching valve 76 at one end and the radiation passage 38 at the other end, and this selection path 93 is selectively connected to the inflow and outflow passages 75 and 75' on the high pressure side by movement of the spool 82. The radial passages 38 are in communication with each other to guide high-pressure fluid to the radiation passage 38. Further, as shown in detail in FIG. 3, the second switching valve 78 has a hollow hole 9 between the passages 77 and 77'.
4 and has a flange 95 formed at the middle part of the outer periphery, and has a freely slidable shuttle valve 96, and stopper parts 97, 97' that restrict the sliding movement of the shuttle valve 96 by abutting against the flange 95 on the outer periphery. Furthermore, guides 98, 98' having inner circumferential surfaces on which the aforementioned shuttle valve 96 and the later-described relief valve can slide are provided. Within these guides 98, 98', relief valves 101, 101' having small holes 100, 100' at their tips are slidably provided to return the shuttle valve 96 to the neutral position by springs 99, 99'. It is being
At the rear of the relief valves 101, 101', guides 98, 98' are screwed and fixed, and springs 102,
Bodies 105, 105' have built-in pilot relief valves 104, 104' which are pressed into small holes 103, 103' by 102';
Adjustment screws 106, 106' that are screwed into 05' to make it possible to adjust the springs 102, 102', and a nut 10 that fixes and holds the adjustment screws 106, 106'.
7, 107', 108, 108', and passages 109, 109' through which the bypass fluid of the pilot relief valves 104, 104' flows out to the passages 77, 77'.
and are provided. Furthermore, guides 98,9
8' is a passage 11 communicating with the passages 77, 77' and applying fluid pressure to the shuttle valve 96.
0,110' is provided. 1st, 4th, 5th,
In Figure 6, the parking brake 4 of the control valve 72
4, an inflow/outflow passage 75,
Outflow and inflow pipes 111 and 112 as external pipes communicating with 75' are removably attached via a joint 113 with bolts 114. Pressurized fluid flows into or out of the inflow and outflow pipes 111 and 112, and the passage 79 of the control valve 72,
79', 80, 80' allow fluid to flow in and out. The inflow and outflow pipes 111 and 112 are connected to the through hole 2
The reinforcing rib 1b causes the water to 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 lug portion 1a. The entry pipes 111, 112 and the inside of the casing portion 8 are protected. The parking brake 44, the inlet/outlet pipes 111, 112, and the hydraulic motor distribution valve described above are located from the center of the width of the crawler shoe to its inner end, and the deceleration mechanism 31
is located from the center of the crawler shoe width to its outer edge.

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

First, pressurized fluid flows in from the inflow and outflow pipe 111,
The case where fluid flows out from the inflow/outflow pipe 112 will be explained. 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 43 of the hydraulic motor 12 through the inflow and outflow passage 41 in the flange portion 16, acts to push the swash plate 19, and acts on the rotation shaft of the hydraulic motor 12. It works to rotate 15. On the other hand, among the fluid that has flowed into the inflow and outflow passages 75, the passage 8
0 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, pushes the ball valve 87 in the spool 82 open against the spring 86, and opens the hole 89. Through room 9
2. The fluid that has flowed into this chamber 92 is
As it increases, it acts to push the end face of the spool 82, causing the spool 82 to slide against the spring 90'. This sliding continues until the tip of the spool 82 hits the damper valve 91', and each passage is switched by this movement of the spool 82. Due to this switching operation of the spool 82,
The passage 79 and the selection passage 93 communicate through the hole 85 in the spool 82, and the inflow/outflow passage 41' and the passage 79' communicate with each other through the hole 85 in the spool 82.
5, and the flow of fluid from the passage 80 into the chamber 92 is stopped. As a result of selective passage 93 communicating with passage 79 through which high-pressure fluid flows,
High pressure fluid in passageway 79 is diverted to selection passageway 93 . The fluid flowing into the selection passage 93 is guided to the radial passage 38 of the flange portion 16 and flows into the shuttle valve 39, and pushes the shuttle valve 39 open against the spring 40 to connect the radial passage 38 and the passage 37. On the other hand, communication between the passage 37 and the passage 47 is cut off to stop discharging fluid from the parking brake 44. The fluid flowing into the radiation passage 38 is applied to the parking brake 44 via the passages 37 and 68.
into the hydraulic pressure chamber 67. The fluid flowing into the hydraulic chamber 67 acts to move the moving member 59 inwardly 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, the hydraulic motor 12 is rotated for the first time, and the fluid that flows out after driving and rotating the hydraulic motor 12 flows out from the piston chamber 43' of the hydraulic motor 12 through the inflow and outflow passages 41' and 75'. It flows out from the inlet pipe 112. That is, the high-pressure pressurized fluid that has flowed into the inflow/outflow pipe 111 automatically operates the first switching valve 76 and then operates the rotation shaft 15 of the hydraulic motor 12 by the parking brake 44.
At the same time, the brake on hydraulic motor 1 is released.
It acts to drive and rotate the rotation shaft 15 of No. 2.

Next, a case will be described in which the flow of pressurized fluid from the inflow/outflow pipe 111 is stopped and the operation of the hydraulic motor 12 is stopped. From the inflow/outflow pipe 111 to the control valve 72
When the fluid that had been flowing into the passages 79 and 80 stops flowing, the spool 82 of the first switching valve 76 is moved by the spring 9.
0' returns it to the neutral position. At this time, the fluid in the chamber 92 flows between the spool 82 and the damper valve 9.
1, passes through the passage 80, and is discharged from the inflow/outflow pipe 111. Furthermore, when the spool 82 is returned, the passage 79 and the selection passage 93 are disconnected. For this reason, the shuttle valve 39 is
0, the radiation passage 38 and the passage 37 are disconnected, and the passage 37 and the passage 47 are communicated with each other. 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 via the passage 68, passage 37, and passage 47. The fluid discharged into this passage 48 is
It flows into the drain chamber 51 of the hydraulic motor chamber 11 through the passages 49 and 50, collects together with the internal drain of the hydraulic motor 12 itself, and then flows into the drain passage 5.
2. It is discharged to the outside through the discharge pipe 55. Due to the movement of the movable member 59, the movable brake plate 71 engages with the fixed brake plate 70, and the rotation shaft 1 of the hydraulic motor 12
5 to give a brake. In this case, the kinetic energy of the driven vehicle causes the hydraulic motor 12 to
In order to continue rotating in the direction in which pressurized fluid is flowing from the inflow/outflow pipe 111, the hydraulic motor 12 is a pump that sucks fluid from the inflow/outflow passage 41 and discharges the fluid to the inflow/outflow passage 41'. has the effect of In this way, when the hydraulic motor 12 acts as a pump, the hydraulic pressure in the passage 81' within the control valve 72 increases. This high pressure fluid enters the passage 77' and moves the shuttle valve 96 in the direction of the guide 98 against the spring 99 until the flange 95 on the outer periphery of the shuttle valve 96 hits the stopper part 97 at the front of the guide 98. It acts to move. When the flange 95 on the outer periphery of the shuttle valve 96 hits the stopper portion 97, the passage 1
10' and the hollow hole 94 communicate with each other, and the fluid flows into the hollow hole 94 of the shuttle valve 96.
The pilot relief valves 104, 104' are inserted into the relief valves 101, 101' through the small holes 100, 100' at the tips of the springs 102, 101'.
102' and tries to push it open. At this time, high pressure fluid acts as back pressure on one pilot relief valve 104' side, and the hydraulic motor 12 acts on the other pilot relief valve 104 side.
Since the fluid in the inflow/outflow passageway 41 is being sucked by the action of the pump, the low pressure fluid acts as a back pressure through the passageway 77, so the pilot relief valve 104 opens and the high pressure fluid flows into the passageway 77. 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 that presses the relief valve 101 toward the shuttle valve 96 and the force of the back pressure, the force due to the back pressure is reduced by the pilot. Since the pressure decreases rapidly when the relief valve 104 opens, the high pressure fluid in the hollow hole 94 acts against the spring 99 to push the relief valve 101 open.
The relief valve 101 opens and the hollow hole 94 and passage 11
0 communicates, fluid flows through passage 77 and passage 65.
The liquid flows into the hydraulic motor 12 through the inflow/outflow passage 41 in the flange portion 16 . That is, when the inflow of pressurized fluid from the inflow/outflow pipe 111 is stopped, the parking brake 44 is switched to the hydraulic motor 12 by the action of the first switching valve 76 and the shuttle valve 39.
acts to apply braking to the rotating shaft 15 of, and
The first switching valve 76 and the second switching valve 78 function to circulate the fluid so that the fluid within the hydraulic motor 12 does not run out. In addition, in the above-mentioned action, due to the delay in operation and compression of the fluid,
If the fluid sucked into the hydraulic motor 12 from the inflow/outflow passage 41 becomes insufficient, the check valve 84 is opened by this negative pressure to prevent the fluid from running out from the inflow/outflow pipe 111, since the inflow/outflow passage 41 becomes negative pressure. It is designed to suck in fluid according to its capacity.

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

(Effects of the Invention) In the present invention, an axial piston type hydraulic motor is inserted into a casing that rotatably supports a rotary ring, so the hydraulic motor is placed adjacent to a speed reduction mechanism to transfer power between them. The connecting shaft that transmits this 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, it is possible to reduce the overall size of the running frame to which the hydraulic motor is attached, to avoid interference between the crawler shoe link and the running frame, and to move the running frame closer to the center of the sprocket teeth. . By placing the running frame close to the center of the sprocket teeth in this manner, the crawler shoe width can be made as narrow as possible. In addition, by placing the running frame close to the center of the sprocket teeth, a space is secured between the inner surface of the running frame and the inner end of the crawler shoe, and the reinforcing rib portion is extended from the lug portion to the inner side in the width direction of the crawler shoe. The pair of external pipes are made to run parallel to each other inside the reinforcing rib part along the inner surface of the lug-shaped part, and the outer pipe and the inner casing part are connected by the reinforcing rib part to each other by the rotation of the crawler shoe. It can be protected from entangled 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, and the propulsion force does not decrease.

[Brief explanation of the drawing]

The drawings show an embodiment of the 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. Figure 1 is a sectional view taken along line B-B in Figure 1, Figure 4 is a sectional view taken along line CC in Figure 1, Figure 5 is a sectional view taken along line D-D in Figure 4, and Figure 6 is a JIS symbol. It is a circuit diagram expressed in . 1... Traveling frame, 1a... Lug-shaped part, 1b
... Reinforcement rib part, 2 ... Through hole, 3 ... Casing, 4 ... Connection part, 6 ... Outer casing part, 8
... Inner casing part, 12 ... Hydraulic motor, 1
5... Rotating shaft, 21... Rotating ring, 22... Sprocket teeth, 23... Inner cylindrical part, 24... Outer cylindrical part, 29, 29'... Bearing, 31... Gear reduction mechanism, 33... Crawler show, 44... Parking brake, 76... Counter balance valve, 78... Relief valve, 111, 112... Outflow/inflow pipe.

Claims (1)

[Claims] 1 A through hole penetrating from the outside to the inside is formed,
A running frame having a lug portion having an arc-shaped outer end in the crawler running direction and a reinforcing rib portion integrally attached to the outer edge of the lug portion so as to extend inward from the outer edge; It has a rotating wheel that is driven by the hydraulic motor via an inserted axial piston type hydraulic motor and a speed reduction mechanism, and the casing is inserted into the through hole so as to be positioned within the width of the crawler shoe and is attached to the traveling frame. a hydraulic drive mechanism, a connecting portion in which the casing of the hydraulic motor is connected to a lug-shaped portion, an inner casing portion extending inward from the connecting portion;
and an outer casing portion extending outward from the connecting portion, wherein the rotating ring has a sprocket tooth portion having teeth formed on its outer periphery, and an outer casing portion extending outward from the sprocket tooth portion. The rotating ring is rotatably supported by the outer casing part via two bearings spaced apart by a predetermined distance so that the sprocket teeth of the rotating ring are located approximately in the center of the width of the crawler shoe. , and the outer cylindrical part of the rotating ring is connected to the output end of the speed reduction mechanism, and a pair of external pipes through which the working fluid of the hydraulic motor flows in and out is connected to the outer cylindrical part of the lug-like part outside the crawler running direction by straddling the through hole. A crawler type characterized in that the outer piping and the inner casing part are protected by the reinforcing rib part, which runs parallel to the inside of the reinforcing rib part along the inner side surface of the lug-shaped part from the opposite side from the end. Vehicle running equipment.