JPH02311693A - Free sectional surface type shield machine - Google Patents

Abstract

PURPOSE:To excavate a tunnel having a desired sectional shape by turning a rotary body having a center cutter and revolving a planetary cutter supported onto the rotary body through a turning member, regulating the locus along a guide member. CONSTITUTION:When a motor 35 in a skin plate 1 is driven, a cutting wheel driving gear 12 revolves, and a cutting wheel 2 having a center cutter 6 revolves. Then, a control lever 29 fixed onto a torsion bar 23 revolves along the locus corresponding to the inner peripheral shape of a rail 34, in the state where a roller is pressed onto a guide rail 34 by a compression member. Further, a planetary cutter 7 supported by a lever 24 connected with the lever 29 revolves around a center axis G. Further, when a motor 45 is driven, a turning moment is transmitted to a planetary cutter driving pinion 18a through a gear 13, and then transmitted to a planetary turning shaft, and a cutter 7 is turning-driven.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a free-section shield machine that can continuously excavate tunnels of any desired cross-sectional shape, not just circular ones.

[Conventional technology]

Conventionally, various types of shield machines as described above have been proposed and put into practice. In general, a cutter placed on the front of the shield machine body is rotated around the central axis of the shield machine to excavate the front face in the propulsion direction of the shield machine, and the shield machine is propelled by the excavated amount to perform the excavation. Digging is done by adding rings.

Further, Japanese Patent Application Laid-Open No. 59-102090 discloses an enlarged shield construction method for forming enlarged diameter sections such as retreat sections and station sections in a section of a tunnel excavated by the above-mentioned shield machine.

[Problem to be solved by the invention]

Conventional shield construction methods and shield machines excavate tunnels by rotating the front cutter, so the cross-sectional shape of the excavation is limited to a circle, and it is difficult to excavate tunnels with other irregular cross-sectional shapes. On the other hand, most of the cross-sectional shapes actually required for sewers, power lines, subway tunnels, etc. are other than circular, so conventionally, excavations with large circular cross-sections that include such irregular cross-sectional shapes have been carried out. Therefore, extra excavation work and disposal of the excavation waste are required. Such extra work has a greater impact on tunnel construction costs as the diameter of the cross section becomes larger, such as in subway tunnels, and is a constraint when applying the shield construction method.

To solve this problem, the application shown in the above-mentioned publication is to first excavate the tunnel to a normal diameter and assemble the segment rings, then remove the segment rings in the target area and perform special excavation work in the radial direction to expand the tunnel. The method is to partially form a diameter portion, etc., and is not to continuously excavate a cross section of a desired shape other than a circle.

SUMMARY OF THE INVENTION In view of the above circumstances, an object of the present invention is to provide a shield machine that can continuously excavate a tunnel having a desired cross-sectional shape, not just a circular one.

[Means to solve the problem]

The present invention includes a shielding machine main body, a rotating body rotatably supported by the shielding machine main body so as to be rotatable about an axis extending in the propulsion direction thereof, and having a center cutter on the front surface, and a rotating body driving means for driving the rotating body. a plurality of rotating members rotatably supported by the rotating body at positions offset from the rotational axis; and a planetary cutter rotatably supported by the rotating member at positions offset from the rotational center axis. , a guide member having a guide shape corresponding to a desired excavation shape, a regulating means for regulating the orbit of the planetary cutter by pressing a rotating end of the rotating member against the guide member, and a planetary cutter driving means. , and a drive transmission mechanism that transmits the driving force of the planetary cutter drive means to the rotating shaft of each planetary cutter.

[For production]

According to the above configuration, the central portion of the face, which is the front surface of excavation, is excavated by rotationally driving the rotary body and the center cutter by the rotary body driving means. Further, while the center cutter and the rotating body are rotating, a planetary cutter rotatably supported by the rotating body revolves while drawing a unique locus corresponding to the guide shape of the guide member, and is driven by the planetary cutter driving means. By rotating on its own axis with the driving force transmitted through the transmission groove, the outer peripheral portion of the face is excavated by the planetary cutter, and the entire excavation is performed in a desired cross-sectional shape.

〔Example〕

Embodiments of the present invention will be described below based on the drawings.

First practical example (Figs. 1 to 5) The shield machine shown here includes a rectangular tube-shaped skin plate (shield machine main body) 1, and this skin plate 1
A cutting wheel (rotating body) 2 is built into the tip.

This cudding wheel 2 includes a front plate 3 and a rear plate 1.
0, and is configured to be rotatable around the center G of the skin plate 1 (an axis extending in the propulsion direction). A plurality of slits 3a are formed radially in the front plate 3, a center pit 4 is provided in the center of the front plate 3, and a large number of cutter rods 5 are provided in the peripheral portion of the slit 3a. are arranged, and both bits 4.5 constitute a center cutter 6. Furthermore, a planetary cutter 7 having cutter pits 7a and 7b is disposed at a plurality of locations in front of the peripheral edge of the cutting wheel 2.

As shown in FIG. 2, the rear outer circumferential surface of the cutting wheel 2 is joined to the inner ring of a swing bearing 9 fixed to a bracket 8a on the side of the skin plate 1. ring 1 extending to
1 is fixed.

On the other hand, a hollow fixing ring 15 is installed in the center of the skin plate 1.
The ring 11 is rotatably fitted on the outside of the ring 11 with a seal 16 in between.

A cutting wheel driving gear 12 is fixed to the rear end of the ring 11, and a wide planetary cutter driving gear 13 is rotatably supported on the outer peripheral surface of the ring 11 via a bearing 14.

Behind the ring 11, a motor with a reduction gear (rotating body driving means) 3 is attached to a bracket 8G provided on the skin plate 1.
5 is fixed, and a pinion 18b provided on the drive shaft of this motor 35 with a reduction gear is meshed with the cutting wheel drive gear 12. In addition to this motor 35 with a reduction gear, a motor 45 with a reduction gear is fixed to the bracket 8C via a mounting seat 45a at a position shifted from the motor 35, and is provided on the drive shaft of the motor 45 with a reduction gear. A pinion 18d is meshed with the rear half of the F planetary cutter driving gear 13.

In addition, 16a in FIG. 2 is a seal, which prevents earth and sand from flowing into the rear. The inner periphery of a portion of the skin plate 1, which is a seat on which the seal 16a is provided, is formed into 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 explained based on FIG.

A torsion bar 23 is attached to the rear plate 10 of the cudding wheel 2 so as to pass through the rear plate 10 in the front-rear direction, and a lever 24 and two control levers are integrally fixed to the front and rear parts of the torsion bar 23. These constitute a rotating member that can rotate around the torsion bar 23.

Specifically, a housing 25a is fitted into a through hole provided in the rear plate 10, and the torsion bar 23 is rotatably supported by a bearing 26a provided within the housing 25a. The torsion bar 23 is formed into a substantially cylindrical shape, and a drive shaft 19 extending in the rearward direction is rotatably housed inside the torsion bar 23 . The rear end of this drive shaft 19 protrudes outside the torsion bar 23, and a pinion 18a for driving a planetary cutter is coupled to this protruding portion by a spline 20a.
8a is meshed with the front half of the planetary cutter driving gear 13.

The lever 24 includes a lever main body 24a and a lever lid 24b.
A ring-shaped protrusion 24c is formed in a portion of the lever cover 24b located on the axis of the drive shaft 19.

On the other hand, a housing 25b containing a bearing 26b is fixed to the rear surface of the front plate 3, and the shaft-like protrusion 24c is rotatably supported by the bearing 26b.

Inside this lever 24, from the top of FIG.
The front end of 9 is rotatably supported. Each shaft has gears 21a and 21b, respectively.

21G is fixed, gear 21a and gear 21b1 and gear 21b and gear 21c are meshed with each other, and the planetary cutter 7 is connected to the front end of the planetary cutter rotating shaft 22 via a spline 20b. In addition, a notch 2 is formed in the cutting wheel 2 according to the rotation locus of the planetary cutter 7.
b (Fig. 1) is formed, thereby preventing interference between the two.

In this structure, the planetary cutter drive binion 18
When a and the drive shaft 19 rotate, the rotation causes the gear train 2 to rotate.
It is transmitted to the planetary cutter rotating shaft 22 via 1a to 21c, and the planetary cutter 7 rotates on its own axis.

The control lever 29 is connected to the rear end of the torsion bar 23 via a spline 20c, and a roller 28 is attached to the rotating end of the control lever 29 so as to be rotatable about a pin 27a. .

On the other hand, as shown in FIG. 4, a plurality of brackets 8e are arranged on the outer periphery of the ring 11, and each bracket 8e
A telescopic member (regulating means) 33 is attached to e so as to be swingable about a pin 27b, and the control lever 29 is rotatably connected to the movable end of the telescopic member 33 via a pin 27C. . This telescopic member 33 is attached in a contracted state and always applies a force in the direction of extension to the control lever 29.

On the other hand, a guide rail (guide member) 3 is provided on the inner surface of the skin plate 1 at a position where it contacts the roller 28.
4 is fixed. This guide rail 34 has an inner circumferential surface (guiding surface) corresponding to a desired excavation shape (here, a square shape).
The roller 28 is pressed against this inner circumferential surface by the urging force of the elastic member 33.

In addition, in FIG. 2, 66 is a screw conveyor that carries out the excavated earth and sand in the chamber 2a rearward, 37 is an erector that lays the segment 36 on the inner wall of the tunnel excavated by the shield machine, and 38 is a screw conveyor that takes the reaction force from the segment 36. A shield jack 39 that propels the shield machine is a tail seal that prevents earth, sand, water, etc. from flowing into the shield machine from the outer periphery of the segment 36.

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

By driving the deceleration motor 35 in the skin plate 1, the cutting wheel drive gear 12 meshed with the binion 18b fixed to the drive shaft rotates, and the ring 11 and the cutting wheel 2 are integrally driven. It also rotates.

As the cutting wheel 2 rotates, the planetary cutter 7 and its entire drive unit also revolve around the center @G. Since it is pressed against the inner peripheral surface of the guide rail 34, it revolves along a trajectory corresponding to the inner peripheral shape of the guide rail 34. Since the torsion bar 23 and the lever 24 are integrally connected to these two control levers, the planetary cutter 7 supported at the tip of the lever 24 also follows the trajectory according to the inner peripheral shape of the guide rail 34.
That is, it revolves around the center axis 0 while drawing a trajectory corresponding to the desired excavation shape.

At this point, the mounting angle α1 (Fig. 4) of the control lever 29 with respect to one drive shaft and the drive 'I'! If the mounting angle α2 (Fig. 1) of the lever 24 with respect to It 19 is set to be the same, the locus drawn by the star cutter 7 will be the same as that of the guide rail 34.
It is completely similar to the inner circumferential shape of .

On the other hand, when the motor 45 with a reduction gear is driven in parallel, its rotational force is transmitted to the planetary cutter driving pinion 18a via the planetary cutter driving gear 13, and further, by the mechanism explained in FIG. Since the rotational speed is transmitted to each planetary cutter rotating shaft 22, each planetary cutter 7 is rotationally driven at a rotational speed independent of the rotation of the cutting wheel 2.

Therefore, while the cutting wheel 2 and the planetary cutter 7 are separately rotationally driven by the motors 35 and 45 with reduction gears, the entire shielding machine is propelled by the operating force of the shielding machine jack 38, thereby rotating the rotor bit in the center. The cutter bit 7 of the planetary cutter 7 excavates the central circular part with the cutter bit 4 and the cutter bit 5, and revolves around it while drawing a unique trajectory and rotates on its own axis.
a and 7b, the outer peripheral portion can be excavated, and a tunnel having a desired cross-sectional shape as a whole can be excavated.

The earth and sand excavated in this way is taken into the chamber 2a through the slit 3a formed in the front plate 3 and the notch 2b of the cutting wheel 2, and is sequentially carried out rearward by the screw conveyor 66. The bell indicated by the dash-dot line in Figure 2!・Finally transported to and from the ground using a conveyor 40, etc.

At this time, if the excavated earth and sand fills the chamber 2a and the amount of earth and sand pulled out by the screw conveyor 66 is adjusted so as to maintain the pressure inside the chamber 2a within a certain range, the earth and sand in the chamber 2a and in front of it can be removed. The pressure difference created by the operation of the screw conveyor 66 allows for smooth flow to its tip intake.

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

Moreover, in the case of this shield machine, the orbit of the planetary cutter 7 is restricted by the guide rail 34 having a fixed shape, so even if an external force acts on the planetary cutter 7,
This has the advantage that the trajectory is less likely to be disturbed.

Furthermore, in this shield machine, the cutting wheel 2 is driven by the motor 35 with a reduction gear, and each planetary cutter 7 is rotationally driven by a separate motor 45 with a reduction gear, so that the cutting wheel 2 is rotated. The number of rotations and the rotation speed of the planetary cutter 7 can be set separately and independently.

Therefore, regardless of the rotation speed of C and the cutting wheel 2, T
The rotation speed of the i-star cutter can be set to a desired value depending on the soil quality and the like. Further, as shown in FIG. 5, a double structure gear consisting of a front gear 13a and a rear gear 13b is used as the planetary cutter driving gear 13, and the front gear 13
If the pinion 18a for driving the planetary cutter 18a is engaged with the pinion 18a and the pinion 18d is engaged with the rear gear 13b, the drive reduction ratio of the planetary cutter 7 can be appropriately set by changing the gear ratio of both gears 13a and 13b. I can do it.

In addition, in this shield machine, the planetary cutter 7 can be driven in either the forward or reverse direction, so there is no need to set the drive transmission mechanism C, lever 24, etc. in the rotational direction of the planetary cutter 7. , the work becomes easier. moreover,
By changing the rotation direction of the planetary cutter 7, it is also possible to remove stones stuck between the outer circumference of the planetary cutter 7 and the skin plate 1, or to correct rolling during excavation. .

Further, as shown in this embodiment, if a hollow fixing ring 15 is provided in the center of the shield machine body and an elastic member 33 is provided on the outer periphery of this fixing ring 15, this fixing ring 15 It becomes possible to install the screw conveyor 66 at a suitable inclination angle by utilizing the internal space of the screw conveyor 66.

Second Embodiment (FIGS. 6 to 10) 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, a reinforcing outer ring 3c is provided on the front plate 3 side, and a box-shaped cross-section ring 1 is provided on the rear plate 10 side.
0a are provided respectively, and both the hinges 3c and 10a are connected to each other by a torque arm 3b. Further, the housing 25b in the first embodiment is extended forward, and the amount of protrusion of the portion of the lever cover 24b that supports the planetary cutter rotating shaft 22 is reduced or contracted.

According to this structure, first, the center pit 4 and cutter bit 5 provided on the front plate 3 excavate the earth and sand, and then the planetary cutter 7 excavates the surrounding area. The area to be excavated is the shaded 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 first excavates the earth and sand, and the remaining part is placed in the center of the front plate 3. Since the bit 4 and cutter bit 5 excavate, the area excavated by the planetary cutter 7 is the shaded area in FIG.

Therefore, according to the structure of the second embodiment, the area to be excavated by the planetary cutter 7 is significantly reduced compared to the structure of the first embodiment, and the following effects can be obtained accordingly.

(1) Generally, cutter bit 7b in planetary cutter 7
The rotation radius of the tip of the planetary cutter 7, that is, the outer circumferential radius D1 of the planetary cutter 7 is set smaller than the cutter diameter D2 of the cutting wheel 2. Therefore, when the load on the planetary cutter 7 is large as in the first embodiment (in FIG. 10, the ratio of the workload of the double-force vines is about 1:1), the cutter bits 7a and 7b of the planetary cutter 7 are The center cutter 6 will wear out before the center cutter 6. On the other hand, if the planetary cutter 7 is placed at the rear as in this embodiment, the excavation area is reduced, and the excavation by the cutter of the cutting wheel 2 loosens the earth and sand, so the burden on the planetary cutter 7 is reduced. The degree of wear and tear on both power vines is averaged out, extending the life of the shield machine as a whole.

(2) Compared to driving the cutting wheel 2, driving the planetary cutter 7 requires a complicated mechanism;
By reducing the burden on the shield machine, the drive mechanism can be further simplified, manufacturing costs can be reduced, and the shield machine can be made smaller.

In particular, by making the lever 24 in the chamber 2a thin, the fluidity of the earth and sand in the chamber 2a is increased, and the earth and sand excavated by the planetary cutter 7 is easily taken into the chamber 2a.

(3) Since the planetary cutter 7 is located on the front side of the cutting wheel 2 when viewed from inside the skin plate 1, the cutter pits 7a and 7 of the planetary cutter 7 are
When an abnormality occurs in the planetary cutter 7, such as when the blade b breaks, it can be easily repaired.

Third Embodiment (FIG. 11) In the above shield type, the face is stabilized, and a chamber 2 is installed at the earth and sand intake port of the screw conveyor 66.
In order to smoothly flow the earth and sand in the shield machine, a method of injecting muddy water from inside the shield machine toward the face and into the chamber 2a is often used. In this case, a means is required to prevent highly concentrated muddy water from accumulating in the lower part of the chaleba 2a. Therefore, in this embodiment, the driving force of the motor with a speed reducer is used to rotate the stirring blades within the chamber 2a.

Specifically, in FIG. 11, cutting wheel 2
A cylindrical housing 62 is supported by the rear plate 10 and the box-shaped ring 10a.
A pair of front and rear bearings 63 are provided inside, and these bearings 63
The stirring @61 is rotatably supported by.

This stirring shaft 61 has a front end portion, that is, 1? It has a stirring blade 64 extending radially at the end facing into the lever 2a, and a stirring drive binion 61a at the rear end, and this stirring drive binion 61a is the front gear 1 of the planetary cutter drive gear 13.
It is meshed with 3a.

According to such a structure, by the operation of the motor 35 with a reduction gear or the motor 45 with a reduction gear, the stirring blade 64 rotates while the stirring shaft 61 revolves in addition to the cutting wheel 2 and the planetary cutter 7 . This prevents highly concentrated muddy water from accumulating in the lower part of the chamber 2a, and also prevents the earth and sand within the chamber 2a from coagulating. Moreover,
There is no need to provide a new drive source, and the above effects can be achieved at low cost and with a simple structure. Further, it is also easy to arrange a plurality of stirring devices at key points on the circumference.

Furthermore, as shown in FIG. 12, if the front end of the stirring @ 61 is supported by a bearing 65 provided on the cutting wheel 2 side, the stirring shaft 61 can be supported at both ends with the stirring blade 64 in between. As a result, the stirring shaft becomes difficult to bend, resulting in an advantageous structure in terms of strength.

Note that 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 using round rods as the blades and increasing the number of blades. Further, the position of the stirring plate may be freely placed as long as it does not interfere with other members.

Fourth Embodiment (FIG. 13) Here, a bulge 2d that bulges inward is provided at a predetermined location on the peripheral edge of the cutting wheel 2, and this bulge 2d is provided with a small disc-shaped rotating body (rotating member). ) 70 is rotatably mounted via a bearing 71, and a planetary cutter rotating shaft 2 is installed at the eccentric position.
2 is rotatably attached. Furthermore, this planetary cutter 7
The drive structure and the regulation structure of the revolution locus are the same as in the previous embodiment.

Even in such 4M ii, the small rotating body 70 rotates appropriately while the cutting wheel 2 is rotating, so that the yrt star cutter 7 revolves while drawing a trajectory according to the desired excavation shape.

However, if the rotating member is shaped like a lever as shown in each of the embodiments described above, the planetary cutter rotating shaft 22 can be extended to the outside of the cutting wheel 2, so that the diameter of the M star cutter 7 can be reduced. Along with making it smaller,
There is an advantage that a large internal space, the lever 2a, can be secured.

Note that the present invention is not limited to the embodiments described above, and may take the following embodiments as examples.

(1) The drive transmission mechanism according to the present invention is not limited to the one shown in FIGS. 3 and 8, and for example, instead of providing the annular protrusion 24c shown in FIG. Alternatively, the end of the drive shaft 19 may be made to protrude from the lever 124b, and this protruding end may be supported by the bearing 26b. Also, instead of the gear trains 218 to 21C, a sprocket 30a as shown in FIG. 15 is installed on each shaft 22.19.
The same effect as described above can also be obtained by fixing the two ends together and connecting the two ends with a chain 31.

(2) The shape of the guide member in the present invention is not limited to a rectangular shape like the guide rail 34 described above, but may be appropriately set in accordance with the desired excavation shape, such as a circle, an oval shape, or a horseshoe shape.

FIG. 16 shows the outer periphery 1a of the skin plate 1, a small circle 100 (dotted chain line) which is the excavation cross-sectional shape obtained by rotating the cutting wheel 2, and a state in which the center of the planetary cutter is farthest from the center of this small circle 100. This figure shows a large circle 101 (dotted chain line) that is the cross-sectional shape of excavation obtained by rotating the cutting wheel 2, but in this device, within the range surrounded by the small circle 100 and the large circle 101, You can freely set the orbit of the planetary cutter. In either case, good excavation can be achieved by using a skin plate having a cross-sectional shape that corresponds to each excavated cross-sectional shape. For example, the figure shows the outer periphery 1a of each cylindrical skin plate 1, and as is clear from this figure, the outer periphery shape of the skin plate 1 falls within the above-mentioned range.

Similarly, FIGS. 17 and 18 show examples in which the outer peripheral shapes of a horseshoe and an oval are kept within the above-mentioned range. In these cases as well, it is sufficient to use a skin plate having the above-mentioned horseshoe-shaped or oval-shaped outer peripheral shape, and to use a guide rail having a shape such that the orbit of the planetary cutter matches these shapes.

That is, according to this shield machine, various excavation cross sections can be easily obtained with a single shield machine by simply changing the shapes of the guide rail and skin plate as appropriate.

On the other hand, regarding the structure of the guide member, in addition to the above-mentioned rail, for example, an inner FA may be used, and instead of using the roller 28, a pinion gear A7 that meshes with the internal gear may be used.

(3) In each of the above embodiments, the roller 28 is connected to the guide rail 34.
Although the telescopic member 33 is used as a means for pressing the guide rail 5, the telescopic member 33 can be omitted if, for example, the guide rail 5 is configured to have two sets of inner and outer parts, and the roller 28 is made to pass between them.

(4) In each of the above embodiments, the cutting wheel 2 is supported on the inner surface of the skin plate 1. 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, the number and placement position of the Ti star cutters do not matter; they may be placed at appropriate locations depending on the soil quality.

〔Effect of the invention〕

As described above, the present invention rotates a rotating body having a center cutter, and also causes a planetary cutter supported by the rotating body via a rotating member to revolve along a guide member.
Since it is designed to draw a trajectory corresponding to the desired excavation shape, the central circular part of the face is excavated with the center cutter, and the outer periphery is excavated with a planetary vine that draws a unique trajectory. A tunnel having a desired overall cross-sectional shape can be freely excavated.

Moreover, since the driving means for the rotary body and the driving means for the planetary cutter are provided separately, the rotational direction and rotation speed of the center cutter and the planetary cutter can be set independently, making it possible to set the rotation direction and rotation speed of the center cutter and planetary cutter independently. This has the effect of allowing the rotation speed to be freely selected.

In addition, the orbit of the planetary claw is regulated by pressing the rotation axis of the planetary cutter onto the guide surface of the guide member with a predetermined shape, so that even if an external force is applied to the single star cutter, the above trajectory will not be disturbed easily. .

[Brief explanation of the drawing]

Fig. 1 is a front view of a shielding machine according to a first embodiment of the present invention, Fig. 2 is a sectional view taken along the line I-IF in Fig. 1, and Fig. 3 is a sectional view showing the drive structure of the planetary cutter in the above shielding machine. , FIG. 4 is a sectional view taken along the line IV-IV in FIG. 2, and FIG. 5 is a sectional view equivalent to FIG. 2 showing another example of the drive structure of the i-star cutter.
Figure 6 is a front view of the shield machine in the second embodiment;
The figures are a sectional view taken along the line Vl-Vl in Fig. 6, Fig. 8 is a sectional view showing the drive structure of the planetary cutter in the shield machine, and Fig. 9 is a sectional view showing the drive structure of the planetary cutter in the shield machine.
The figure is an explanatory diagram showing the area excavated by the planetary cutter of the shield machine in the second embodiment, FIG. 10 is an explanatory diagram showing the area excavated by the planetary cutter of the shield machine in the first embodiment, and FIG. FIG. 12 is a sectional view equivalent to FIG. 7 showing a modification of the third embodiment, and FIG. 13 is a sectional view equivalent to FIG. 7 showing the main parts of the shield machine in the third embodiment. 14 and 15 are cross-sectional front views showing essential parts of the shield machine J3, and cross-sectional views showing other modifications of the drive structure of the planetary cutter. FIG. 16 is an explanatory diagram showing the orbit of the planetary cutter and the setting range of the outer peripheral shape of the skin plate, and FIGS. 17 and 18 are explanatory diagrams showing other examples of the outer peripheral shape of the skin plate. 1...Skin plate (shield machine body), 2...
Cutting wheel (rotating body), 3...Front plate, 6
...Center cutter, 7...Planetary cutter, 23...
- Torsion bar (constituting a rotating member), 24... Lever (constituting a rotating member), 29... Control lever (constituting a rotating member), 33... Telescopic member (regulating means), 34・
... Guide rail (guide member), 35 ... Reduction separate motor (rotating body drive means), 45 ... Motor with reduction gear (planetary cutter drive means), C ... Drive transmission mechanism, G.
... Central axis (axis extending in the propulsion direction). Patent applicant: Civil Engineering Research Center Foundation
Kobe Steel Corporation Representative Patent Attorney Etsushi Kotani Patent Attorney Chief 1)
Masaru Patent Attorney 9Fuji 4Fujli1
Figure 4 Figure 5 Figure 6 Figure 9 Figure 10 Figure 11 Figure 12 Figure 13 Figure 16 Figure 17

Claims (1)

[Claims] 1. A shield machine main body, a rotary body rotatably supported by the shield machine body around an axis extending in its propulsion direction and having a center cutter on the front surface, a rotary body driving means for driving this rotary body, and a rotary body driving means for driving this rotary body, a plurality of rotating members rotatably supported on the body at positions offset from the rotational axis; a planetary cutter rotatably supported at the rotating members at positions offset from the rotational center axis; a guide member having a guide shape corresponding to the excavation shape; a regulating means for regulating the orbit of the planetary cutter by pressing a rotating end of the rotating member against the guide member; a planetary cutter driving means; A free section shielding machine characterized by comprising a drive transmission mechanism that transmits the driving force of the planetary cutter drive means to the rotating shaft of each planetary cutter.