JPH0781510B2 - Free section shield machine - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a free-section shield machine capable of continuously excavating a tunnel having a desired cross-sectional shape, not limited to a circular shape.

[Conventional technology]

Conventionally, various types of shield machines as described above have been proposed and implemented. Generally, a cutter placed on the front surface of the shield machine body is rotated around the central axis of the shield machine to excavate the front surface in the propulsion direction of the shield machine, and the shield machine is propelled by the excavated amount to make the segment ring. It is used by digging by adding.

Further, Japanese Patent Laid-Open No. 59-102090 discloses an enlarged shield construction method for forming an expanded diameter portion such as a retreat portion or a station portion in a part of a tunnel excavated by the shield machine.

[Problems to be Solved by the Invention]

Since the conventional shield construction method and shield machine excavate by rotating the front cutter, the excavation cross-sectional shape is limited to a circular shape, and it is difficult to excavate a tunnel having another irregular cross-sectional shape. On the other hand, most of the actual cross-sectional shapes such as sewage, power lines, subway tunnels, etc., other than the circular shape, have been conventionally used for excavation of large circular cross-sections including such irregular cross-sectional shapes. Must be performed, and an extra excavation work and a work for processing the excavation shear are required. Such extra work has a greater effect on the tunnel construction cost as the cross section of the subway tunnel has a larger diameter, which is also a constraint when applying the shield construction method.

In order to solve this problem, the invention disclosed in the above publication is constructed by excavating a tunnel with a normal diameter once to assemble a segment ring, then removing the segment ring of the target portion and performing special excavation work in the radial direction. The diameter portion and the like are partially formed, and the cross section having a desired shape other than the circular shape is not continuously excavated.

In view of such circumstances, an object of the present invention is to provide a shield machine capable of continuously excavating a tunnel having a desired sectional shape, not limited to a circular shape.

[Means for Solving the Problems]

The present invention provides a shield machine main body, a rotary body rotatably supported by the shield machine main body around an axis extending in the propulsion direction, and having a center cutter on the front surface, and a rotary body drive means for driving the rotary body, A plurality of rotating members rotatably supported by the rotating body at positions deviated from the rotating shaft, rotating member driving means for driving the rotating members, and a rotating center shaft of the rotating members. A planetary cutter rotatably supported at a position away from the planetary cutter driving means, a planetary cutter driving means, a drive transmission mechanism for transmitting the driving force of the planetary cutter driving means to the rotation shaft of each planetary cutter, and each planetary cutter desired. A drive control system for controlling the drive of the rotating member so as to revolve while drawing a locus according to the excavation shape.

[Action]

According to the above configuration, the rotating body and the center cutter are rotationally driven by the rotating body driving means, so that the central portion of the face, which is the excavation front surface, is excavated. Further, during rotation of the center cutter and the rotating body, the planetary cutter rotatably supported by the rotating body revolves while drawing a unique trajectory under the control of the drive control system, and is driven by the planetary cutter driving means. By the rotation of the driving force transmitted through the transmission mechanism, the outer peripheral portion of the face is excavated, and the excavation having a desired sectional shape is performed as a whole.

〔Example〕

 Embodiments of the present invention will be described below with reference to the drawings.

1st Example (FIGS. 1-7) The shield machine shown here is equipped with the skin plate (shield machine main body) 1 of a square tube shape, and this skin plate 1
A cutting wheel (rotating body) 2 is built in at the tip of the.

This cutting wheel 2 includes a front plate 3 and a rear plate 10.
And is configured to be rotatable about the central axis (axis extending in the propulsion direction) G of the skin plate 1. A plurality of slits 3a are radially formed on the front plate 3, and a center bit 4 is formed at the center of the front plate 3.
Is provided, and a large number of cutter bits 5 are arranged on the peripheral portion of the slit 3a, and a center cutter 6 is constituted by both bits 4 and 5. Further, planetary cutters 7 having cutter bits 7a and 7b are arranged at a plurality of positions in front of the peripheral edge of the cutting wheel 2.

As shown in FIG. 2, the outer peripheral surface of the rear portion of the cutting wheel 2 is joined to the inner ring of the slewing bearing 9 fixed to the bracket 8a on the skin plate 1 side, and the rear surface plate 10 of the cutting wheel 2 is rearward. A ring 11 extending to the is fixed. On the other hand, a hollow fixing ring 15 is installed in the central portion of the skin plate 1, and the ring 11 is rotatably fitted to the outside of the fixing ring 15 with a seal 16 interposed therebetween.

A cutting wheel driving gear 12 is fixed to the rear end portion of the ring 11, and a wide planetary cutter driving gear 13 is rotatably supported by a bearing 14 on the outer peripheral surface of the ring 11. Behind the ring 11, a motor 8 with a speed reducer (rotating body driving means) 35 is fixed to a bracket 8c provided on the skin plate 1, and the pinion 18b provided on the drive shaft of the motor 35 with a speed reducer is used as described above. It is meshed with the cutting wheel drive gear 12. In addition to the motor with reduction gear 35, a motor with reduction gear 45, which is displaced from the motor 35, is fixed to the bracket 8c via a mounting seat 45a, and is provided on the drive shaft of the motor with reduction gear 45. The pinion 18d is meshed with the latter half of the planetary cutter driving gear 13.

In addition, 16a in FIG. 2 is a seal, which prevents the earth and sand in the chamber 2a from flowing backward. The inner circumference of a part of the skin plate 1 corresponding to the seat on which the seal 16a is provided is formed in a circular shape.

Next, the structure of the rotating member that supports the planetary cutter 7 and the drive transmission mechanism C for driving the planetary cutter 7 will be described with reference to FIG.

The rear plate 10 of the cutting wheel 2 includes the rear plate 10
The torsion bar 23 is attached so as to penetrate through the front and rear direction, and the lever is attached to the front and rear of the torsion bar 23.
The 24 and the control lever 29 are integrally fixed, and by these, a rotating member that is rotatable around the torsion bar 23 is configured.

Specifically, the housing is installed in the through hole provided on the rear plate 10.
Bearings in which the housing 25a is fitted and in which the housing 25a is fitted
The torsion bar 23 is rotatably supported by 26a. The torsion bar 23 is formed in a substantially cylindrical shape, and the drive shaft 19 extending in the above direction is rotatably housed inside the torsion bar 23. The rear end of the drive shaft 19 projects to the outside of the torsion bar 23, and the planetary cutter driving pinion 18a is coupled to the projecting portion by a spline 20a, and the planetary cutter driving pinion 18a is the planetary cutter driving gear. It is meshed with the first half of 13.

The lever 24 is configured to be disassembled into a lever body 24a and a lever lid 24b, and the drive shaft 1 is attached to the lever lid 24b.
A shaft-shaped protruding portion 24c is formed in a portion located on the axis center line of 9. On the other hand, a housing 25b containing a bearing 26b is fixed to the rear surface of the front plate 3, and the bearing 26b is
The shaft-shaped protrusion 24c is rotatably supported by.

In the lever 24, the rear end of the planetary cutter rotating shaft 22, the intermediate shaft 19b, and the front end of the drive shaft 19 are rotatably supported in this order from the top of FIG. Gears on each axis
21a, 21b, 21c are fixed, and gear 21a and gear 21b are meshed with each other, and gear 21b and gear 21c are meshed with each other, and the planetary cutter 7 is coupled to the front end portion of the planetary cutter rotating shaft 22 via a spline 20b. There is. In addition, the notch 2b (FIG. 1) is formed in the cutting wheel 2 according to the rotation trajectory of the planetary cutter 7.
Are formed, which prevents interference between the two.

In this structure, the planetary cutter driving pinion 18a
When the drive shaft 19 and the drive shaft 19 rotate, the rotation of the drive shaft 19 causes the gear trains 21a to 21a to rotate.
It is transmitted to the planetary cutter rotating shaft 22 via 1c, and the planetary cutter 7 rotates.

The control lever 29 is connected to the rear end of the torsion bar 23 via a spline 20c. On the other hand, the fourth
As shown in the figure, a plurality of brackets 8e are arranged on the outer circumference of the ring 11, and an expansion / contraction member (rotating member driving means) 33 is attached to each bracket 8e so as to be swingable about a pin 27b. The control lever 29 is rotatably connected to the movable end of the elastic member 33 via a pin 27c. Therefore, with the expansion and contraction of the expansion and contraction member 33, the rotation member including the control lever 29 and the like is integrally rotated.

Further, a drive control system as shown in FIG. 5 is provided inside the shield machine.

In the figure, the cutting wheel rotation position detector 90
Is for determining the reference rotational position of the cutting wheel 2 at an appropriate position (for example, the position shown in FIG. 1) and detecting the rotational displacement amount (for example, angle) of the cutting wheel 2 with respect to this reference rotational position.

The expansion / contraction member expansion / contraction amount detector 94 sets the reference length of the expansion / contraction member 33 to an appropriate value and detects the actual expansion / contraction amount of the expansion / contraction member 33 with respect to this length, and is configured by a potentiometer or the like. As the reference length, for example, the length of the elastic member 33 when the control lever 29 is at the position shown in FIG. 1 may be set.

The arithmetic unit 91 has a built-in program for calculating the expansion / contraction amount of the expansion / contraction member 33 necessary for the rotational displacement amount of the cutting wheel 2 for the purpose of obtaining a predetermined excavation cross section. The expansion / contraction amount of the expansion / contraction member 33 required for the rotational displacement amount of the cutting wheel 2 input from the cutting wheel rotation position detector 90 is instantly calculated. The details of the calculation will be described later.

The comparator 92 includes an arithmetic unit 91 and an expansion / contraction member expansion / contraction detector 94.
The displacement amounts respectively input from are compared with each other, an expansion or contraction command is given to the expansion / contraction member controller 93 so that they are equal, and a stop command is given when the difference between the two is eliminated.

The elastic member controller 93 controls the actual amount of expansion and contraction of the elastic member 33. For example, when a hydraulic cylinder is used for the expansion / contraction member 33, the expansion / contraction member controller 93 corresponds to a servo valve for controlling the oil supplied to the expansion cylinder and a set of control devices for this servo valve.

In FIG. 2, 66 is a screw conveyor that carries the excavated soil in the chamber 2a backward, 37 is an erector that lays a segment 36 on the inner wall of the tunnel excavated by a shield machine, and 38 is a reaction force from the segment 36. A shield jack for propelling the shield machine, and 39 are tail seals for preventing the inflow of earth and sand or water from the outer peripheral portion of the segment 36 into the shield machine.

Next, the operation of this shield machine will be described.

By driving the motor 35 with a reducer in the skin plate 1, the cutting wheel drive gear 12 meshed with the pinion 18b fixed to the drive shaft thereof rotates,
The ring 11 and the cutting wheel 2 also rotate integrally with this. With the rotation of the cutting wheel 2, the planetary cutter 7 and its entire drive device revolve around the central axis G as a unit.

Further, by driving the motor 45 with a reduction gear in parallel with this, the rotational force thereof is transmitted to the planetary cutter driving pinion 18a via the planetary cutter driving gear 13 and further the mechanism described in FIG. 3 above. Is transmitted to each planetary cutter rotation shaft 22 by means of the above, each planetary cutter 7 is rotationally driven at a rotational speed independent of the rotation of the cutting wheel 2.

On the other hand, in the drive control system, first, the arithmetic unit 91 calculates the expansion / contraction amount of the expansion / contraction member 33 required to obtain the desired cross-sectional shape with respect to the rotational position of the cutting wheel 2, and this expansion / contraction amount and the actual expansion / contraction amount. From the comparison with, the expansion / contraction drive of the expansion / contraction member 33, that is, the rotation drive of the rotating member including the control lever 29 and the like is controlled.

The details of the control will be described. For example, when the planetary cutter 7 is located at a position corresponding to the corner of the skin plate 1, by extending the elastic member 33, the distance from the central axis G to the planetary cutter 7 ( Ie revolution radius)
To extend the excavation area by the planetary cutter 7 to the corner portion. On the contrary, when the planetary cutter 7 is located at the position corresponding to the midpoint of each side of the rectangular skin plate 1, the elastic member 33 is contracted to move the planetary cutter 7 from the central axis G.
Reduce the distance to. By such control, the planetary cutter 7 revolves around a trajectory corresponding to a desired excavation shape (here, a substantially square shape).

At this time, the mounting angle α ₁ of the control lever 29 with respect to the drive shaft 19
(Fig. 4) and the mounting angle α ₂ of the lever 24 with respect to the drive shaft 19
If (1) and (2) are set to be the same, the locus drawn by the planetary cutter 7 is completely similar to the locus drawn by the tip (movable end) of the elastic member 33.

Therefore, while rotating the cutting wheel 2 and the planetary cutter 7 by the motors 35 and 45 with the speed reducer,
By propelling the entire shield machine with the operating force of the shield machine jack 38, the center circular portion 4 and the cutter bit 5 rotating at the center excavate the central circular portion, and revolve around the periphery while drawing a unique trajectory, and The outer peripheral portion can be excavated by the cutter bits 7a and 7b of the planetary cutter 7 that rotates, and a tunnel having a desired sectional shape as a whole can be excavated.

The earth and sand excavated in this way has slits 3a formed in the front plate 3 and notches 2b in the cutting wheel 2.
It is taken into the chamber 2a through the above, is sequentially carried out rearward by the screw conveyor 66, and is finally carried out to the ground by the belt conveyor 40 and the like shown by the one-dot chain line in FIG.

At this time, the excavated earth and sand are filled in the chamber 2a,
If the amount of earth and sand pulled out by the screw conveyor 66 is adjusted so that the pressure in 2a is kept within a certain range, the earth and sand in the chamber 2a and in front of the chamber 2a will have its tip intake port due to the pressure difference caused by the operation of the screw conveyor 66. It will flow smoothly.

According to such a shield machine, the center cutter 6 fixed to the cutting wheel 2 and the planetary cutter 7 supported around the center cutter 6 can continuously and easily excavate a tunnel having a desired cross-sectional shape. .

Moreover, in this shield machine, the motor 35 with a speed reducer drives the cutting wheel 2 and the motor 45 with a speed reducer different from this drives each planetary cutter 7 to rotate, so that the cutting wheel 2 rotates. The number and the rotational speed of the planetary cutter 7 can be set independently. Therefore, regardless of the rotation speed of the cutting wheel 2, the rotation speed of the planetary cutter 7 can be set to a desired value according to the soil quality and the like. Further, as shown in FIG. 7, a double-structured gear consisting of a front gear 13a and a rear gear 13b is used as the planetary cutter driving gear 13, and a planetary cutter driving pinion 18a is meshed with the front gear 13a, Pinion 18d on rear gear 13b
If the gears are meshed with each other, the drive reduction ratio of the planetary cutter 7 can be appropriately set by changing the gear ratio of the two gears 13a and 13b.

Further, in this shield machine, since the planetary cutter 7 can be driven in either forward or reverse directions, there is no need to be caught in the rotational direction of the planetary cutter 7 when designing the drive transmission mechanism C, the lever 24, etc. Work becomes easy. Furthermore, by changing the rotation direction of the planetary cutter 7, it is possible to remove stones caught between the outer peripheral portion of the planetary cutter 7 and the skin plate 1 and to correct rolling during excavation. Becomes

Further, as shown in this embodiment, a hollow fixing ring 15 is provided in the central portion of the shield machine main body, and this fixing ring
By providing the elastic member 33 and the like on the outer peripheral portion of the screw 15, the screw conveyor 66 is utilized by utilizing the internal space of the fixing ring 15.
Can be set at a suitable inclination angle.

Further, in this shield machine, since the planetary cutter 7 draws a desired revolution locus by controlling the rotational drive of the rotary member by the drive control system, the arithmetic unit 91
By simply converting the program installed in
Various excavation cross-sectional shapes can be easily obtained.

Further, by performing so-called overcut using such a function, a further excellent effect can be obtained. This overcut will be described with reference to FIG.

In the figure, regions J, K, L, and M indicated by hatching outside the outer periphery 1a of the skin plate 1 are overcut zones. In normal excavation, a program installed in the arithmetic unit 91 is controlled so that the planetary cutter 7 moves along the outer peripheral shape of the skin plate 1. Here, in order to realize the above-mentioned movement in the arithmetic unit 91. Other programs,
Outer peripheral shape obtained by adding the area J to the outer peripheral shape of the skin plate 1.
Program for moving the planetary cutter 7 along 96a, and moving the planetary cutter 7 along the outer peripheral shape 96b including the region K, the outer peripheral shape 96c including the region L, and the outer peripheral shape 96d including the region M, respectively. Try to incorporate the program. At the same time, a selection circuit for arbitrarily selecting the above-mentioned five types of programs is added to the arithmetic unit 91 so that one of the five types of excavation cross sections can be arbitrarily selected as required. With such a configuration, the effect of overcut as described below can be obtained.

For example, if a normal excavation cross section program is selected and excavation is in progress, if this program is switched to an excavation cross section program that matches the outer peripheral shape 96a, the earth and sand of the part protruding upward from the upper side of the skin plate 1 is also excavated. (Overcut). When excavation proceeds in this state, a cross-sectional space corresponding to the region J above the skin plate 1 is formed,
Friction resistance between the skin plate 1 and the earth and sand at this portion is reduced. On the other hand, since the lower part of the skin plate 1 is still in contact with the earth and sand, the difference between the frictional resistance of the upper part of the skin plate 1 and the frictional resistance of the lower part of the skin plate 1 gradually increases. As a result, the shield machine tries to escape to the upper side where the frictional resistance is small, and the propulsion direction of the shield machine gradually rises.

In this way, the shield machine tries to change its direction to the overcut direction. Therefore, by appropriately selecting the excavation cross-section program that matches the outer peripheral shapes 96a to 96d in FIG. It can be easily changed to a steep curve. Further, if a program capable of overcutting each of the four corners is incorporated, the posture recovery control for the rolling can be easily performed.

Second Embodiment (FIGS. 8 to 12) Here, the planetary cutter 7 in the first embodiment is arranged behind the cutting wheel 2.

Specifically, the cutting wheel 2 is divided into a spoke-shaped front plate 3 and a rear plate 10, and a reinforcing outer ring 3c is provided on the front plate 3 side and a box-shaped cross-section ring 10a is provided on the rear plate 10 side. It is provided, and both rings 3c and 10a are torque arms.
Connected by 3b. Further, the housing 25b in the first embodiment is extended forward, and the protrusion amount of the portion of the lever lid 24b that supports the planetary cutter rotating shaft 22 is reduced.

According to such a structure, first, the center bit 4 and the cutter bit 5 provided on the front plate 3 excavate the earth and sand, and then the planetary cutter 7 excavates the peripheral portion thereof. The area to be excavated is the hatched area in FIG.

On the other hand, according to the shield machine of the first embodiment, the planetary cutter 7 is arranged in front of the face plate 3, and the planetary cutter 7 excavates the earth and sand, and the remaining part is the center bit of the front plate 3. 4 and cutter bit 5 excavate,
The excavation area by the planetary cutter 7 is the hatched area in FIG.

Therefore, according to the structure of the second embodiment, the excavation area by the planetary cutter 7 is greatly reduced as compared with the structure of the first embodiment, and the following effects can be obtained.

(1) Generally, the radius of gyration of the tip of the cutter bit 7b in the planetary cutter 7, that is, the outer radius D _{1 of the} planetary cutter 7
Is set to be smaller than the cutter diameter D ₂ of the cutting wheel 2. Therefore, when the load on the planetary cutter 7 is large as in the first embodiment (the ratio of the work of both cutters is about 1: 1 in FIG. 12), the cutter bit 7a of the planetary cutter 7,
7b is worn before the center cutter 6. On the other hand, if the planetary cutter 7 is arranged rearward as in this embodiment, the excavation area is reduced and the load on the planetary cutter 7 is reduced because the earth and sand are loosened by the excavation by the cutter of the cutting wheel 2. The wear of both cutters is averaged to extend the life of the entire shield machine.

(2) Compared to driving the cutting wheel 2, driving the planetary cutter 7 requires a complicated mechanism.
By reducing the load of the above, it is possible to further simplify the drive mechanism, reduce the cost, and reduce the size of the shield machine. In particular, by making the lever 24 in the chamber 2a thin, the fluidity of the earth and sand in the chamber 2a is enhanced, and the earth and sand excavated by the planetary cutter 7 is easily taken into the chamber 2a.

(3) The planetary cutter 7 is located on the front side of the cutting wheel 2 when viewed from the inside of the skin plate 1. Therefore, when the cutter bits 7a, 7b of the planetary cutter 7 are broken during excavation, the planetary cutter 7 can be broken. When an abnormality occurs in the, it can be easily repaired.

Third Embodiment (FIG. 13) In the shield machine as described above, in order to stabilize the cutting face and smoothly allow the sediment in the chamber 2a to flow into the sediment intake of the screw conveyor 66, the face of the shield is cut from inside the shield machine. A method of injecting muddy water into the chamber 2a is often used. In this case, a means for preventing the high concentration muddy water from accumulating in the lower part of the chamber 2a is required. Therefore, in this embodiment, the stirring blade is rotated in the chamber 2a by utilizing the driving force of the motor with a reducer.

Specifically, in FIG. 13, a cylindrical housing 62 is supported by the rear plate 10 of the cutting wheel 2 and the box-shaped cross-section ring 10a, and a pair of front and rear bearings 63 are provided in the housing 62. Bearing 63 by stirring shaft
61 is rotatably supported.

The stirring shaft 61 has a stirring blade 64 extending radially at the front end, that is, the end facing the inside of the chamber 2a, and has a stirring drive pinion 61a at the rear end, and the stirring drive pinion 61a.
Are meshed with the planetary cutter driving gear 13.

According to this structure, the stirring blade 64 rotates while the stirring shaft 61 revolves in addition to the cutting wheel 2 and the planetary cutter 7 by the operation of the speed reducer motor 35. This prevents high-concentration muddy water from accumulating in the lower part of the chamber 2a, and also prevents solidification of the earth and sand in the chamber 2a. Moreover, there is no need to provide a new drive source,
The above effect can be obtained with a low cost and a simple structure. Further, it is easy to arrange a plurality of stirring devices at important points on the circumference.

Further, as shown in FIG. 14, if the front end portion of the stirring shaft 61 is supported by the bearing 65 provided on the cutting wheel 2 side, the stirring shaft 61 is supported at both ends with the stirring blade 64 interposed therebetween. Therefore, the stirring shaft is less likely to bend and the structure is advantageous in terms of strength.

The shape, size, number, etc. of the stirring blades may be appropriately set depending on the soil quality. For example, the same effect can be obtained by increasing the number of blades with round bars. Further, the position of the stirring blade may be freely arranged as long as it does not interfere with other members.

Fourth Embodiment (FIG. 15) Here, a bulging portion 2d that bulges inward is provided at a predetermined position on the peripheral portion of the cutting wheel 2, and a small disk-shaped rotating body (rotating member) is provided in the bulging portion 2d. ) 70 is rotatably mounted via a bearing 71, and the planetary cutter rotating shaft 22 is rotatably mounted at the eccentric position. The drive structure of the planetary cutter 7 and the orbital trajectory restricting structure are the same as those in the above-described embodiment.

Even in such a structure, the planetary cutter 7 revolves along a trajectory corresponding to a desired excavation shape by appropriately rotating the small rotating body 70 while the cutting wheel 2 is rotating.

However, if the turning member is formed into a lever shape as shown in each of the above-described embodiments, the planetary cutter rotating shaft 22 can be extended to the outside of the peripheral edge of the cutting wheel 2, so that the diameter of the planetary cutter 7 can be increased. There is an advantage that the chamber 2a, which is an internal space, can be made large while being made small.

Fifth Embodiment (FIGS. 16 to 18) In this embodiment, a single housing 54 is integrally connected to the cutting wheel 2 via a connecting member 53, and a lever 24, which is a rotating member, is attached to the housing 54. Is rotatably attached, and the rotation driving mechanism of the cutting wheel 2 and the planetary cutter 7 and the rotation driving mechanism of the lever 24 are
It is characterized in that the lever 24 and the housing 54 are all housed.

Specifically, the housing 54 is rotatably supported by a bracket 8a on the skin plate 1 side via a bearing 9, and a cutting wheel driving gear 12 is fixed to a rear end portion of the housing 54. 12 is,
It meshes with a pinion 18b provided on the drive shaft of the motor 35 with a reducer.

Further, a motor 45 with a speed reducer is fixed to the center of the rear end of the housing 54, and a shaft 50a extending in the front-rear direction coupled to the output shaft of the motor 45 with a speed reducer is rotatably supported in the housing 54. . The planetary cutter driving gear 13 is fixed to the front end of the shaft 50a.

On the other hand, a motor 55 with a speed reducer for rotationally driving each lever 24 is fixed to the rear end of the housing 54, and a shaft 50b coupled to the output shaft of the motor 55 with a speed reducer is attached to the housing 54.
It is rotatably supported in the shaft 50b and the shaft 50b
It is connected to a torsion bar 23, which is a rotating shaft of a lever 24, via a gear train composed of 2b and 52c. The motor 55 with a speed reducer is drive-controlled by a drive control system so that the planetary cutter 7 revolves around a trajectory corresponding to a desired shape, like the elastic member 33 of the above-described embodiment. Specifically, in the drive control system shown in FIG.
Is replaced by a motor controller and the expansion / contraction amount detector 94
Is used instead of the motor rotation speed detector.

On the other hand, a gear train composed of gears 21a to 21c similar to that shown in FIG. 3 is housed in the lever 24, and the drive shaft 19 is connected to the gear 21a and fixed to the drive shaft 19. The planetary cutter driving pinion 18a is meshed with the planetary cutter driving gear 13. The drive shaft 19 is aligned with the torsion bar 23.

In this structure, by operating the motor 35 with a reducer, its driving force is transmitted to the housing 54 via the pinion 18b and the cutting wheel driving gear 12,
The cutting wheel 2 is rotationally driven integrally with the housing 54. Also, by the operation of the motor 45 with a reducer,
The driving force is transmitted to the planetary cutter 7 via the shaft 50a, the planetary cutter driving gear 13, the planetary cutter driving pinion 18a, and the drive transmission mechanism in the lever 24, whereby the planetary cutter 7 is rotated at a desired rotation speed. Driven.

Further, the driving force is transmitted to the torsion bar 23 via the shaft 50b and the gears 52a to 52c by the operation of the speed reducer motor 55, whereby the lever 24 rotates around the torsion bar 23. The drive of this motor 55 with a reducer is
Since the planetary cutter 7 is controlled by the drive control system as described above, the planetary cutter 7 revolves around a trajectory corresponding to a desired excavation shape.

According to such a structure, since all rotary drive mechanisms are configured as a single unit, the assembly of the above mechanism,
It becomes easy to disassemble, and after the unit has reached the end of its life, the entire unit can be replaced, and the replacement work time can be greatly shortened. Further, since the intake port 66a of the screw conveyor 66 can be arranged in the lower part of the chamber 2a, it becomes easier to take in the earth and sand accumulated in the lower part of the chamber 2a.

Incidentally, as shown in FIG. 17, when the intake port 66a of the screw conveyor 66 is arranged in the lower center of the chamber 2a, the sediment collected in the corner G of the chamber 2a is less likely to flow toward the intake port 66a, If measures are not taken such as injecting a mud material to improve the flow of sediment, it becomes easy for sediment to collect in the corner G, but as shown in FIG. 18, a plurality of screw conveyors 66 may be installed side by side in the left-right direction. Therefore, it is possible to easily take in the soil in the corner G.

The present invention is not limited to the embodiments described above, and the following aspects can be taken as examples.

(1) The drive transmission mechanism according to the present invention is not limited to that shown in each of the above-described embodiments, and as shown in FIG. 19 instead of providing the axial projection 24c shown in FIGS. 3 and 10, for example. The end of the drive shaft 19 may be projected from the lever lid 24b, and the protruding end may be supported by the bearing 26b. Further, instead of the gear trains 21a to 21c, a sprocket 30a as shown in FIG. 20 is fixed to the shafts 22 and 19, and the two are connected by a chain 31, the same effect as above can be obtained. You can

(2) The excavation shape determined by the control of the drive control system is
The shape is not limited to the rectangular shape as in the above embodiment, and may be appropriately set according to a desired excavation shape such as a circle, an egg shape, and a horseshoe shape.

FIG. 21 is a small circle which is an excavated sectional shape obtained by rotating the outer periphery 1a of the skin plate 1 and the cutting wheel 2.
100 (dashed-dotted line), a great circle 101 which is an excavated cross-sectional shape obtained when the cutting wheel 2 is rotated with the center of the planetary cutter being farthest from the center of the small circle 100.
Although it is shown by (dashed-dotted line), this device can freely set the revolution trajectory of the planetary cutter within the range surrounded by the small circle 100 and the large circle 101. In any case, exchanging the excavation cross-section program of the arithmetic unit 91 and using a skin plate having a cross-sectional shape corresponding to the above-mentioned shape enables good excavation. For example, FIG. 1 shows the outer circumference 1a of each tubular skin plate 1. As is clear from this drawing, the outer circumference shape of the skin plate 1 is within the above range.

Similarly, FIGS. 22 and 23 show an example in which the horseshoe-shaped and oval-shaped outer peripheral shapes are accommodated within the above range. In these cases as well, a skin plate having the above-mentioned horseshoe-shaped or oval outer peripheral shape may be used, and a program for matching the revolution trajectory of the planetary cutter with these shapes may be incorporated in the arithmetic unit.

That is, according to this shield machine, various excavation cross-sections can be easily performed by a single shield machine simply by changing the program of the arithmetic unit and changing the shape of the skin plate to the shape corresponding to the program of the arithmetic unit. Can be obtained.

(3) In each of the above embodiments, the expansion / contraction member 33 and the motor 55 with a speed reducer are used as the means for driving the rotating member, but any known drive means may be used.

(4) In each of the above embodiments, the cutting wheel 2 is supported by the inner surface of the skin plate 1. However, for example, a bearing is fixed to the outer periphery of the fixing ring 15 shown in FIG. 2 may be supported.

(5) In the present invention, regardless of the number of planetary cutters and the arrangement position, the planetary cutters may be arranged at appropriate places depending on the soil quality.

〔The invention's effect〕

As described above, according to the present invention, the rotating body having the center cutter is rotated, and the planetary cutter is supported by the rotating body via the rotating member so that the planetary cutter draws a trajectory corresponding to a desired excavation shape. In order to control the rotation of the rotating member, by excavating the central circular portion of the face by the center cutter, by excavating the outer peripheral portion by a planetary cutter that draws a unique trajectory,
It is possible to freely excavate a tunnel having a desired sectional shape as a whole. Moreover, there is an effect that the excavation shape by the planetary cutter can be easily changed only by changing the drive control content of the rotating member.

Further, since the driving means for the rotating body and the driving means for the planetary cutter are separately provided, the rotation direction and the rotation speed of the center cutter and the planetary cutter can be set independently, and the rotation suitable for excavation is performed. There is an effect that the number can be freely selected.

[Brief description of drawings]

FIG. 1 is a front view of a shield machine according to a first embodiment of the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is a sectional view showing a drive structure of a planetary cutter in the shield machine. ,
FIG. 4 is a sectional view taken along line IV-IV in FIG. 2, FIG. 5 is a block diagram showing a drive control system provided in the shield machine, and FIG. 6 is a front view showing an overcut area by the shield machine. , FIG. 7 is a second view showing another example of the drive structure of the planetary cutter.
8 is a front view of the shield machine according to the second embodiment, FIG. 9 is a sectional view taken along the line IX-IX of FIG. 8, and FIG. 10 is a drive structure of the planetary cutter in the shield machine. FIG. 11 is a sectional view showing the region excavated by the planetary cutter of the shield machine in the second embodiment, and FIG. 12 is an explanatory diagram showing the region excavated by the planetary cutter of the shield machine in the first embodiment. FIG. 13 is a sectional view corresponding to FIG. 9 showing a main part of a shield machine in a third embodiment, and FIG. 14 is a sectional view corresponding to FIG. 9 showing a modification of the same embodiment, and FIG. Is a sectional front view showing an essential part of the shield machine in the fourth embodiment, FIG. 16 is a sectional view showing an essential part of the shield machine in the fifth embodiment, and FIGS. 17 and 18 are screw conveyors in the shield machine. Fig. 19 and Fig. 20 are cross-sectional front views showing examples of arrangements of planetary cutters. FIG. 21 is a cross-sectional view showing another modified example of the drive structure, FIG. 21 is an explanatory view showing the revolution locus of the planetary cutter and the setting range of the outer peripheral shape of the skin plate, and FIGS. 22 and 23 are other outer peripheral shapes of the skin plate. It is an explanatory view showing an example of. 1 ... Skin plate (shielding machine main body), 2 ... Cutting wheel (rotating body), 3 ... Front plate, 6 ... Center cutter, 7 ... Planetary cutter, 23 ... Torsion bar (constituting rotating member), 24 ... Lever ( Rotating member), 29 ... Control lever (rotating member), 33 ... Telescopic member (rotating member driving means), 35 ... Motor with reduction gear (rotating member driving means), 45 ...
Motor with speed reducer (planetary cutter driving means), 55 ... Motor with speed reducer (rotating member driving means), 90 ... Cutting wheel rotational position detector (constitutes drive control system), 91 ... Computing device (drive control system) Configuration), 92 ... Comparator (configures drive control system), 93 ... Expandable member controller (configures drive control system), 94 ...
Expansion / contraction member expansion / contraction amount detector (which constitutes a drive control system), C ... Drive transmission mechanism, G ... Central axis (axis extending in the propulsion direction).

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Toshinori Asahi 3-5-25 Himejima, Nishiyodogawa-ku, Osaka City, Osaka Prefecture Okumura Machine Manufacturing Co., Ltd. 1-711 (72) Inventor Morinori Takemura 3-1-812 Takahama-cho, Ashiya-shi, Hyogo (56) Reference JP-A-50-21542 (JP, A) JP-B-367671 (JP, B1)

Claims (1)

[Claims] 1. A shield machine main body, a rotary body rotatably supported by the shield machine main body around an axis extending in its propulsion direction, and having a center cutter on the front surface, and a rotary body drive means for driving the rotary body. , A plurality of rotating members rotatably supported by the rotating body at a position deviated from the rotation axis thereof,
Rotating member driving means for driving the rotating member, a planetary cutter rotatably supported on the rotating member at a position deviated from the central axis of rotation, planetary cutter driving means, and planetary cutter driving means. A drive transmission mechanism that transmits the driving force of the above to the rotation shaft of each planetary cutter, and a drive control system that controls the drive of the rotating member so that each planetary cutter revolves while drawing a trajectory according to the desired excavation shape. A free-section shield machine characterized by being equipped.