A fully circumferentially adjustable distributed TBM rear support device

Abstract

The present invention relates to a support device for a TBM, and in particular to a fully circumferentially adjustable distributed TBM rear support device. The present invention comprises a fixed frame and a plurality of support mechanisms; a first transmission mechanism is provided on the fixed frame; the support mechanism comprises a support block, a first hydraulic cylinder, a hydraulic motor, a hydraulic cylinder base, a hydraulic circuit and a second transmission mechanism, and the hydraulic cylinder base is slidably mounted on the fixed frame; the hydraulic motor, the first hydraulic cylinder and the hydraulic cylinder base are connected; the support block is hinged with the piston rod of the first hydraulic cylinder; the hydraulic motor is connected to the second transmission mechanism; the second transmission mechanism cooperates with the first transmission mechanism; the hydraulic circuit controls the forward and reverse rotation of the hydraulic motor and drives the telescopic movement of the first hydraulic cylinder. The device of the present invention drives the radial and circumferential movement of the support block by the hydraulic motor and the hydraulic cylinder, thereby realizing adaptive adjustment of the circumferential and radial positions of the support block, and ensuring the accuracy and stability of the position and posture of the TBM main beam.

Description

Technical Field

[0001] The invention relates to a TBM support device, in particular to a fully circumferentially adjustable distributed TBM rear support device. Background Art

[0002] The rear support device is a key component of the TBM travel system. It is mainly responsible for ensuring the stability of the position and posture of the TBM main beam after the TBM completes the construction of an excavation section, and providing equipment conditions for the retraction of the thrust hydraulic cylinder and the forward movement of the support shoe device. When the rear support device contacts the inner wall of the surrounding rock to stabilize the main beam, the TBM support shoe separates from the rock wall and moves forward during the retraction of the thrust hydraulic cylinder. When the thrust hydraulic cylinder completes the retraction, the TBM support shoe re-extends and tightens to the inner wall of the tunnel. After the support step is completed, the rear support device retracts to complete the work task of an excavation section. During its working process, it must sequentially withstand the external loads brought by the working modes and their switching, such as rear support contact, support shoe release, thrust cylinder retraction, and support shoe tightening.

[0003] The traditional TBM rear support device uses two support legs to complete the longitudinal support of the TBM main beam. The two support legs can only achieve single-direction support and cannot achieve full circumferential support for the TBM main beam. During the TBM excavation process, due to complex external loads, the position of the main beam is prone to deviation, which seriously affects the construction accuracy and restricts the excavation efficiency. Summary of the invention

[0004] Based on the above problems, the purpose of the present invention is to provide a fully circumferentially adjustable distributed TBM rear support device to solve the technical problem that the existing TBM rear support device cannot achieve full circumferential support for the TBM main beam.

[0005] In order to achieve the above-mentioned purpose, the technical solution adopted by the present invention is: a fully circumferentially adjustable distributed TBM rear support device, including a fixed frame and a plurality of support mechanisms arranged on the fixed frame; a first transmission mechanism is provided on the fixed frame; the support mechanism includes a support block, a first hydraulic cylinder, a hydraulic motor, a hydraulic cylinder base, a hydraulic circuit and a second transmission mechanism, and the hydraulic cylinder base is slidably installed on the fixed frame; the hydraulic motor, the first hydraulic cylinder and the hydraulic cylinder base are connected; the support block is hinged to the piston rod of the first hydraulic cylinder; the hydraulic motor is connected to the second transmission mechanism; the second transmission mechanism cooperates with the first transmission mechanism; the hydraulic circuit controls the forward and reverse rotation of the hydraulic motor and drives the telescopic movement of the first hydraulic cylinder.

[0006] Furthermore, the hydraulic circuit includes a circumferential adjustment hydraulic circuit connected to the hydraulic motor and a radial adjustment hydraulic circuit connected to the first hydraulic cylinder.

[0007] Further preferably, the circumferential adjustment hydraulic circuit comprises a differential pressure reducing valve, a three-position four-way proportional reversing valve, a first hydraulically controlled non-return valve, and a second hydraulically controlled non-return valve connected in sequence; the oil source is connected to the A port of the differential pressure reducing valve; the B port of the differential pressure reducing valve is connected to the P port of the three-position four-way proportional reversing valve; the C port of the differential pressure reducing valve is connected to the C port of the shuttle valve;

[0008] The A port of the three-position four-way proportional directional valve is respectively connected to the A port of the shuttle valve, the A port of the first hydraulically controlled one-way valve, and the C port of the second hydraulically controlled one-way valve;

[0009] The B port of the three-position four-way proportional directional valve is respectively connected to the B port of the shuttle valve, the A port of the second hydraulically controlled one-way valve, and the C port of the first hydraulically controlled one-way valve;

[0010] The B port of the first hydraulically controlled one-way valve is connected to the A port of the quantitative hydraulic motor; the B port of the second hydraulically controlled one-way valve is connected to the B port of the quantitative hydraulic motor;

[0011] The T port of the three-position four-way proportional directional valve is connected to the oil tank;

[0012] When the three-position four-way proportional reversing valve is in the left position, its B port is connected to the P port, and the A port is connected to the T port; when it is in the middle position, its A port, B port and T port are connected, and the P port is disconnected; when it is in the right position, its B port is connected to the T port, and the A port is connected to the P port;

[0013] When the pressure at port C of the hydraulically controlled one-way valve is higher than the valve opening pressure, ports A and B are in a two-way conducting state; when the pressure at port C is lower than the valve opening pressure, it is in a one-way conducting state from port A to port B (port A to port B is conducting).

[0014] Furthermore, the shuttle valve is a high-pressure priority shuttle valve.

[0015] Furthermore, the hydraulic motor is provided with a brake device, which is connected to the second hydraulic cylinder; the A port of the second hydraulic cylinder is connected to the B port of the two-position three-way electromagnetic reversing valve; the A port of the two-position three-way electromagnetic reversing valve is connected to the oil source, and the C port is connected to the oil tank;

[0016] When the two-position three-way electromagnetic reversing valve is in the left position, its A port and B port are in the conducting state, and the C port is in the disconnected state; when it is in the right position, its B port and C port are in the conducting state, and its A port is in the disconnected state.

[0017] Further, the radial adjustment hydraulic circuit includes a three-position four-way solenoid reversing valve, a third hydraulically controlled one-way valve and a fourth hydraulically controlled one-way valve; the A port of the three-position four-way solenoid reversing valve is respectively connected to the A port of the third hydraulically controlled one-way valve and the C port of the fourth hydraulically controlled one-way valve; the B port of the three-position four-way solenoid reversing valve is respectively connected to the A port of the fourth hydraulically controlled one-way valve and the C port of the third hydraulically controlled one-way valve; the B port of the third hydraulically controlled one-way valve is connected to the A port of the first pressure sensor and the B ports of several first hydraulic cylinders; the B port of the fourth hydraulically controlled one-way valve is connected to the A port of the second pressure sensor and the A ports of several first hydraulic cylinders; the T port of the three-position four-way solenoid reversing valve is connected to the oil tank;

[0018] When the three-position four-way solenoid reversing valve is in the left position, its B port is connected to the P port, and the A port is connected to the T port; when it is in the middle position, its A port, B port, and T port are connected, and the P port is disconnected; when it is in the right position, its B port is connected to the T port, and the A port is connected to the P port;

[0019] When the pressure at port C of the hydraulically controlled one-way valve is higher than the valve opening pressure, ports A and B are in a two-way conducting state; when the pressure at port C is lower than the valve opening pressure, it is in a one-way conducting state from port A to port B (port A to port B are conducting).

[0020] Furthermore, the first hydraulic cylinder is connected to a displacement sensor for measuring the displacement of the piston rod of the first hydraulic cylinder.

[0021] Furthermore, a proportional throttle valve is connected between the B port of the fourth hydraulically controlled one-way valve and the A port of the first hydraulic cylinder.

[0022] Furthermore, a proportional pressure reducing valve and a throttle valve are connected in sequence between the oil source and the P port of the three-position four-way electromagnetic reversing valve.

[0023] Furthermore, the fixed frame is provided with a central hole for connecting the main beam of the shield machine; the fixed frame is provided with a circumferential slide rail, the hydraulic cylinder base is connected to the slide rail, and the hydraulic cylinder base moves circumferentially along the fixed frame under the action of the hydraulic motor.

[0024] The fully circumferentially adjustable distributed TBM rear support device of the present invention adopts a cooperative driving mode of a hydraulic motor and a hydraulic cylinder. The hydraulic motor drives the pinion to realize circumferential adjustment of the support block, and the hydraulic cylinder drives the support block to move radially and realizes adaptive adjustment of the supporting force, thereby realizing full circumferential support for the TBM main beam and ensuring the accuracy and stability of the position and posture of the TBM main beam under external disturbances. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the embodiments of the present invention, the accompanying drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings in the following description are only some embodiments of the present invention. For ordinary technicians in this field, other accompanying drawings can be obtained based on these accompanying drawings without paying any creative work.

[0026] Figure 1 It is a structural schematic diagram of a distributed TBM rear support device that is adjustable in all directions according to an embodiment of the present invention;

[0027] Figure 2 This is a front view (working state) of the fully circumferentially adjustable distributed TBM rear support device according to an embodiment of the present invention;

[0028] Figure 3 This is a front view (initial state) of the fully circumferentially adjustable distributed TBM rear support device according to an embodiment of the present invention;

[0029] Figure 4 It is a schematic diagram of the hydraulic circuit connection principle of the all-circumferentially adjustable distributed TBM rear support device according to an embodiment of the present invention;

[0030] Numbers in the figure:

[0031] 1-The first elastic member acts to reset the single-piston rod hydraulic cylinder;

[0032] 2- The second elastic member acts to reset the single piston rod hydraulic cylinder;

[0033] 3- The third elastic member acts to reset the single piston rod hydraulic cylinder;

[0034] 4-The fourth elastic member acts to reset the single piston rod hydraulic cylinder;

[0035] 5-The fifth elastic member acts to reset the single piston rod hydraulic cylinder;

[0036] 6-The sixth elastic member acts to reset the single-piston rod hydraulic cylinder;

[0037] 7-first quantitative motor; 8-second quantitative motor; 9-third quantitative motor;

[0038] 10- fourth fixed-measuring motor; 11- fifth fixed-measuring motor; 12- sixth fixed-measuring motor;

[0039] No. 13-1 hydraulically controlled non-return valve; No. 14-2 hydraulically controlled non-return valve; No. 15-3 hydraulically controlled non-return valve;

[0040] No. 16-4 hydraulically controlled non-return valve; No. 17-5 hydraulically controlled non-return valve; No. 18-6 hydraulically controlled non-return valve;

[0041] No. 19-7 hydraulically controlled non-return valve; No. 20-8 hydraulically controlled non-return valve; No. 21-9 hydraulically controlled non-return valve;

[0042] No. 22-10 hydraulically controlled non-return valve; No. 23-11 hydraulically controlled non-return valve; No. 24-12 hydraulically controlled non-return valve;

[0043] 25-first throttle valve; 26-second throttle valve; 27-third throttle valve;

[0044] 28- fourth throttle valve; 29- fifth throttle valve; 30- sixth throttle valve;

[0045] 31-first shuttle valve; 32-second shuttle valve; 33-third shuttle valve;

[0046] 34-the fourth shuttle valve; 35-the fifth shuttle valve; 36-the sixth shuttle valve;

[0047] 37-first three-position four-way proportional reversing valve; 38-second three-position four-way proportional reversing valve;

[0048] 39-3rd and 3rd position four-way proportional reversing valve; 40-4th and 3rd position four-way proportional reversing valve;

[0049] 41-fifth three-position four-way proportional reversing valve; 42-sixth three-position four-way proportional reversing valve;

[0050] 43-first two-position three-way electromagnetic reversing valve; 44-second two-position three-way electromagnetic reversing valve;

[0051] 45-the third two-position three-way solenoid reversing valve; 46-the fourth two-position three-way solenoid reversing valve;

[0052] 47-fifth two-position three-way solenoid reversing valve; 48-sixth two-position three-way solenoid reversing valve;

[0053] 49-first differential pressure reducing valve; 50-second differential pressure reducing valve; 51-third differential pressure reducing valve;

[0054] 52-fourth differential pressure reducing valve; 53-fifth differential pressure reducing valve; 54-sixth differential pressure reducing valve;

[0055] 55-a first pressure sensor; 56-a second pressure sensor;

[0056] No. 57-13 hydraulically controlled non-return valve; No. 58-14 hydraulically controlled non-return valve;

[0057] 59-first proportional throttle valve; 60-second proportional throttle valve; 61-third proportional throttle valve;

[0058] 62- fourth proportional throttle valve; 63- fifth proportional throttle valve; 64- sixth proportional throttle valve;

[0059] 65-first displacement sensor; 66-second displacement sensor; 67-third displacement sensor;

[0060] 68-fourth displacement sensor; 69-fifth displacement sensor; 70-sixth displacement sensor;

[0061] 71-a first double-acting single-rod hydraulic cylinder; 72-a second double-acting single-rod hydraulic cylinder;

[0062] 73-third double-acting single-rod hydraulic cylinder; 74-fourth double-acting single-rod hydraulic cylinder;

[0063] 75-fifth double-acting single-rod hydraulic cylinder; 76-sixth double-acting single-rod hydraulic cylinder;

[0064] 77-the seventh throttle valve; 78-proportional pressure reducing valve; 79-three-position four-way solenoid reversing valve;

[0065] 80- oil source; 81- oil tank; 82- support block; 83- hydraulic cylinder base; 84- pinion;

[0066] 85-fixed frame; 86-large gear;

[0067] For ease of description and labeling, Figure 4 The markings of the various ports are in the form of a number plus a port mark, such as port A of the first three-position four-way proportional reversing valve 37, which is marked as 37A in the figure, and the other ports are marked as 37B, 37P and 37T respectively. DETAILED DESCRIPTION

[0068] In order to facilitate the understanding of the present invention, the present invention is described in more detail below in conjunction with the accompanying drawings and specific embodiments. Preferred embodiments of the present invention are provided in the accompanying drawings. However, the present invention can be implemented in many different forms and is not limited to the embodiments described in this specification. On the contrary, the purpose of providing these embodiments is to make the understanding of the disclosure of the present invention more thorough and comprehensive.

[0069] The structure of the distributed TBM rear support device provided in this embodiment is as follows: Figure 1 , Figure 2 and Figure 3 As shown, it mainly includes a fixed frame 85 and six supporting mechanisms arranged on the fixed frame, namely the first supporting mechanism, the second supporting mechanism, the third supporting mechanism, the fourth supporting mechanism, the fifth supporting mechanism and the sixth supporting mechanism. The fixed frame 85 is circular, and a circumferential slide rail is arranged on its outer edge. A large gear 86 is arranged along the circumference of the fixed frame 85. A central square hole is arranged in the middle of the fixed frame 85, and the hole is installed on the main beam of the shield machine through shape matching.

[0070] The first supporting mechanism includes a supporting block 82, a first double-acting single-rod hydraulic cylinder 71, a hydraulic cylinder base 83, a first quantitative motor 7 and a pinion 84. The first quantitative motor 7 and the first double-acting single-rod hydraulic cylinder 71 are connected to a hydraulic cylinder base 83 by bolts, or are welded or clamped, the pinion 84 is connected to the output shaft of the first quantitative motor 7 by a key, the supporting block 82 is connected to the piston rod of the first double-acting single-rod hydraulic cylinder 71 by a hinge, the hydraulic cylinder base 83 is installed inside the slide rail of the fixed frame 85, and the large gear 86 and the small gear 84 are meshed with each other.

[0071] The second supporting mechanism includes a supporting block 82, a second double-acting single-rod hydraulic cylinder 72, a hydraulic cylinder base 83, a second quantitative motor 8 and a pinion 84. The second quantitative motor 8 and the second double-acting single-rod hydraulic cylinder 72 are connected to a hydraulic cylinder base 83 by bolts, the pinion 84 is connected to the output shaft of the second quantitative motor 8 by a key, the supporting block 82 is connected to the piston rod of the second double-acting single-rod hydraulic cylinder 72 by a hinge, the hydraulic cylinder base 83 is installed inside the slide rail of the fixed frame 85, and the large gear 86 and the small gear 84 are meshed with each other.

[0072] The third supporting mechanism includes a supporting block 82, a third double-acting single-rod hydraulic cylinder 73, a hydraulic cylinder base 83, a third quantitative motor 9 and a pinion 84. The third quantitative motor 9 and the third double-acting single-rod hydraulic cylinder 73 are connected to a hydraulic cylinder base 83 by bolts, the pinion 84 is connected to the output shaft of the third quantitative motor 9 by a key, the supporting block 82 is connected to the piston rod of the third double-acting single-rod hydraulic cylinder 73 by a hinge, the hydraulic cylinder base 83 is installed inside the slide rail of the fixed frame 85, and the large gear 86 and the small gear 84 are meshed with each other.

[0073] The fourth supporting mechanism includes a supporting block 82, a fourth double-acting single-rod hydraulic cylinder 74, a hydraulic cylinder base 83, a fourth quantitative motor 10 and a pinion 84. The fourth quantitative motor 10 and the fourth double-acting single-rod hydraulic cylinder 74 are connected to the hydraulic cylinder base 83 by bolts, the pinion 84 is connected to the output shaft of the fourth quantitative motor 10 by a key, the supporting block 82 is connected to the piston rod of the fourth double-acting single-rod hydraulic cylinder 74 by a hinge, the hydraulic cylinder base 83 is installed inside the slide rail of the fixed frame 85, and the large gear 86 and the small gear 84 are meshed with each other.

[0074] The fifth supporting mechanism includes a supporting block 82, a fifth double-acting single-rod hydraulic cylinder 75, a hydraulic cylinder base 83, a fifth quantitative motor 11 and a pinion 84. The fifth quantitative motor 11 and the fifth double-acting single-rod hydraulic cylinder 75 are connected to the hydraulic cylinder base 83 by bolts, the pinion 84 is connected to the output shaft of the fifth quantitative motor 11 by a key, the supporting block 82 is connected to the piston rod of the fifth double-acting single-rod hydraulic cylinder 75 by a hinge, the hydraulic cylinder base 83 is installed inside the slide rail of the fixed frame 85, and the large gear 86 and the small gear 84 are meshed with each other.

[0075] The sixth supporting mechanism includes a supporting block 82, a sixth double-acting single-rod hydraulic cylinder 76, a hydraulic cylinder base 83, a sixth quantitative motor 12 and a pinion 84. The sixth quantitative motor 12 and the sixth double-acting single-rod hydraulic cylinder 76 are connected to the hydraulic cylinder base 83 by bolts, the pinion 84 is connected to the output shaft of the sixth quantitative motor 12 by a key, the supporting block 82 is connected to the piston rod of the sixth double-acting single-rod hydraulic cylinder 76 by a hinge, the hydraulic cylinder base 83 is installed inside the slide rail of the fixed frame 85, and the large gear 86 and the small gear 84 are meshed with each other.

[0076] Each support mechanism also includes a circumferential adjustment hydraulic circuit connected to the quantitative motor, and a radial adjustment hydraulic circuit connected to the double-acting single-rod hydraulic cylinder. The circumferential position and radial displacement of the support block 82 are controlled by the two hydraulic circuits respectively.

[0077] In the first supporting mechanism, the first circumferential regulating hydraulic circuit connected to the first quantitative motor 7 includes the first differential pressure reducing valve 49, the first three-position four-way proportional reversing valve 37, the first hydraulic control check valve 13, and the second hydraulic control check valve 14, which are connected in sequence. The oil source 80 is connected to the 49A port of the first differential pressure reducing valve 49; the 49B port of the first differential pressure reducing valve 49 is connected to the 37P port of the first three-position four-way proportional reversing valve 37; and the 49C port of the first differential pressure reducing valve 49 is connected to the 31C port of the first shuttle valve 31.

[0078] The port 37A of the first three-position four-way proportional reversing valve 37 is respectively connected to the port 31A of the first shuttle valve 31, the port 13A of the first hydraulically-controlled check valve 13, and the port 14C of the second hydraulically-controlled check valve 14. The port 37B of the first three-position four-way proportional reversing valve 37 is respectively connected to the port 31B of the first shuttle valve 31, the port 14A of the second hydraulically-controlled check valve 14, and the port 13C of the first hydraulically-controlled check valve 13.

[0079] The port 13B of the No. 1 hydraulically controlled one-way valve 13 is connected to the port 7A of the first quantitative motor 7 ; the port 14B of the No. 2 hydraulically controlled one-way valve 14 is connected to the port 7B of the first quantitative motor 7 .

[0080] The port 37T of the first three-position four-way proportional reversing valve 37 is connected to the oil tank 81 .

[0081] In the second supporting mechanism, the second circumferential regulating hydraulic circuit connected to the second quantitative motor 8 includes the second differential pressure reducing valve 50, the second three-position four-way proportional reversing valve 38, the third hydraulic control check valve 15, and the fourth hydraulic control check valve 16 connected in sequence. The oil source 80 is connected to the 50A port of the second differential pressure reducing valve 50; the 50B port of the second differential pressure reducing valve 50 is connected to the 38P port of the second three-position four-way proportional reversing valve 38; the 50C port of the second differential pressure reducing valve 50 is connected to the 32C port of the second shuttle valve 32.

[0082] The port 38A of the second three-position four-way proportional reversing valve 38 is respectively connected to the port 32A of the second shuttle valve 32, the port 15A of the No. 3 hydraulically controlled check valve 15, and the port 16C of the No. 4 hydraulically controlled check valve 16. The port 38B of the second three-position four-way proportional reversing valve 38 is respectively connected to the port 32B of the second shuttle valve 32, the port 16A of the No. 4 hydraulically controlled check valve 16, and the port 15C of the No. 3 hydraulically controlled check valve 15.

[0083] The port 15B of the No. 3 hydraulically controlled one-way valve 15 is connected to the port 8A of the second quantitative motor 8 ; the port 16B of the No. 4 hydraulically controlled one-way valve 16 is connected to the port 8B of the second quantitative motor 8 .

[0084] The port 38T of the second three-position four-way proportional reversing valve 38 is connected to the oil tank 81 .

[0085] In the third supporting mechanism, the third circumferential regulating hydraulic circuit connected to the third quantitative motor 9 includes the third differential pressure reducing valve 51, the third three-position four-way proportional reversing valve 39, the No. 5 hydraulic control check valve 17, and the No. 6 hydraulic control check valve 18 connected in sequence. The oil source 80 is connected to the 51A port of the third differential pressure reducing valve 51; the 51B port of the third differential pressure reducing valve 51 is connected to the 39P port of the third three-position four-way proportional reversing valve 39; the 51C port of the third differential pressure reducing valve 51 is connected to the 33C port of the third shuttle valve 33.

[0086] The 39A port of the third three-position four-way proportional reversing valve 39 is respectively connected to the 33A port of the third shuttle valve 33, the 17A port of the No. 5 hydraulically controlled check valve 17, and the 18C port of the No. 6 hydraulically controlled check valve 18. The 39B port of the third three-position four-way proportional reversing valve 39 is respectively connected to the 33B port of the third shuttle valve 33, the 18A port of the No. 6 hydraulically controlled check valve 18, and the 17C port of the No. 5 hydraulically controlled check valve 17.

[0087] The port 17B of the No. 5 hydraulically controlled one-way valve 17 is connected to the port 9A of the third quantitative motor 9 ; the port 18B of the No. 6 hydraulically controlled one-way valve 18 is connected to the port 9B of the third quantitative motor 9 .

[0088] The port 39T of the third three-position four-way proportional reversing valve 39 is connected to the oil tank 81 .

[0089] In the fourth supporting mechanism, the fourth circumferential regulating hydraulic circuit connected to the fourth fixed-displacement motor 10 includes the fourth differential pressure reducing valve 52, the fourth three-position four-way proportional reversing valve 40, the No. 7 hydraulically controlled check valve 19, and the No. 8 hydraulically controlled check valve 20, which are connected in sequence. The oil source 80 is connected to the 52A port of the fourth differential pressure reducing valve 52; the 52B port of the fourth differential pressure reducing valve 52 is connected to the 40P port of the fourth three-position four-way proportional reversing valve 40; and the 52C port of the fourth differential pressure reducing valve 52 is connected to the 34C port of the fourth shuttle valve 34.

[0090] The 40A port of the fourth three-position four-way proportional reversing valve 40 is respectively connected to the 34A port of the fourth shuttle valve 34, the 19A port of the No. 7 hydraulically controlled check valve 19, and the 20C port of the No. 8 hydraulically controlled check valve 20. The 40B port of the fourth three-position four-way proportional reversing valve 40 is respectively connected to the 34B port of the fourth shuttle valve 34, the 20A port of the No. 8 hydraulically controlled check valve 20, and the 19C port of the No. 7 hydraulically controlled check valve 19.

[0091] The port 19B of the No. 7 hydraulically controlled one-way valve 19 is connected to the port 10A of the fourth fixed-displacement motor 10 ; the port 20B of the No. 8 hydraulically controlled one-way valve 20 is connected to the port 10B of the fourth fixed-displacement motor 10 .

[0092] The 40T port of the fourth three-position four-way proportional reversing valve 40 is connected to the oil tank 81 .

[0093] In the fifth supporting mechanism, the fifth circumferential regulating hydraulic circuit connected to the fifth fixed-displacement motor 11 includes the fifth differential pressure reducing valve 53, the fifth three-position four-way proportional reversing valve 41, the No. 9 hydraulic control check valve 21, and the No. 10 hydraulic control check valve 22, which are connected in sequence. The oil source 80 is connected to the 53A port of the fifth differential pressure reducing valve 53; the 53B port of the fifth differential pressure reducing valve 53 is connected to the 41P port of the fifth three-position four-way proportional reversing valve 41; and the 53C port of the fifth differential pressure reducing valve 53 is connected to the 35C port of the fifth shuttle valve 35.

[0094] The 41A port of the fifth three-position four-way proportional reversing valve 41 is respectively connected to the 35A port of the fifth shuttle valve 35, the 21A port of the No. 9 hydraulically-controlled check valve 21, and the 22C port of the No. 10 hydraulically-controlled check valve 22. The 41B port of the fifth three-position four-way proportional reversing valve 41 is respectively connected to the 35B port of the fifth shuttle valve 35, the 22A port of the No. 10 hydraulically-controlled check valve 22, and the 21C port of the No. 9 hydraulically-controlled check valve 21.

[0095] The port 21B of the No. 9 hydraulically controlled one-way valve 21 is connected to the port 11A of the fifth fixed-displacement motor 11 ; the port 22B of the No. 10 hydraulically controlled one-way valve 22 is connected to the port 11B of the fifth fixed-displacement motor 11 .

[0096] The port 41T of the fifth three-position four-way proportional reversing valve 41 is connected to the oil tank 81 .

[0097] In the sixth supporting mechanism, the sixth circumferential regulating hydraulic circuit connected to the sixth fixed-displacement motor 12 includes the sixth differential pressure reducing valve 54, the sixth three-position four-way proportional reversing valve 42, the No. 11 hydraulically controlled check valve 23, and the No. 12 hydraulically controlled check valve 24, which are connected in sequence. The oil source 80 is connected to the 54A port of the sixth differential pressure reducing valve 54; the 54B port of the sixth differential pressure reducing valve 54 is connected to the 42P port of the sixth three-position four-way proportional reversing valve 42; and the 54C port of the sixth differential pressure reducing valve 54 is connected to the 36C port of the sixth shuttle valve 36.

[0098] The port 42A of the sixth three-position four-way proportional reversing valve 42 is respectively connected to the port 36A of the sixth shuttle valve 36, the port 23A of the No. 11 hydraulically controlled check valve 23, and the port 24C of the No. 12 hydraulically controlled check valve 24. The port 42B of the sixth three-position four-way proportional reversing valve 42 is respectively connected to the port 36B of the sixth shuttle valve 36, the port 24A of the No. 12 hydraulically controlled check valve 24, and the port 23C of the No. 11 hydraulically controlled check valve 23.

[0099] The port 23B of the No. 11 hydraulically controlled one-way valve 23 is connected to the port 12A of the sixth fixed-displacement motor 12 ; the port 24B of the No. 12 hydraulically controlled one-way valve 24 is connected to the port 12B of the sixth fixed-displacement motor 12 .

[0100] The port 42T of the sixth three-position four-way proportional reversing valve 42 is connected to the oil tank 81 .

[0101] The status of each valve in the above six circumferential adjustment hydraulic circuits is as follows:

[0102] When the three-position four-way proportional directional valve is in the left position, its B port is connected to the P port, and the A port is connected to the T port; when it is in the middle position, its A port, B port and T port are connected, and the P port is disconnected; when it is in the right position, its B port is connected to the T port, and the A port is connected to the P port.

[0103] When the pressure at port C of the hydraulically controlled one-way valve is higher than the valve opening pressure, ports A and B are in a two-way conducting state; when the pressure at port C is lower than the valve opening pressure, it is in a one-way conducting state from port A to port B (port A to port B are conducting).

[0104] The shuttle valve is a high pressure priority shuttle valve.

[0105] The radial adjustment hydraulic circuit connected to the double-acting single-rod hydraulic cylinder includes a proportional pressure reducing valve 78, a seventh throttle valve 77, a three-position four-way solenoid reversing valve 79, a No. 13 hydraulic control check valve 57, and a No. 14 hydraulic control check valve 58, which are connected in sequence. Among them, the oil source 80 is connected to the 78A port of the proportional pressure reducing valve 78; the 78B port of the proportional pressure reducing valve 78 is connected to the 77A port of the seventh throttle valve 77; the 77B port of the seventh throttle valve 77 is connected to the 79P port of the three-position four-way solenoid reversing valve 79; the 79A port of the three-position four-way solenoid reversing valve 79 is respectively connected to the 57A port of the No. 13 hydraulic control check valve 57 and the 58C port of the No. 14 hydraulic control check valve 58; the 79B port of the three-position four-way solenoid reversing valve 79 is respectively connected to the 58A port of the No. 14 hydraulic control check valve 58 and the 57C port of the No. 13 hydraulic control check valve 57. The T port of the three-position four-way electromagnetic reversing valve 79 is connected to the oil tank 81 .

[0106] Port 57B of hydraulically controlled check valve No. 13 57 is connected to port 55A of the first pressure sensor 55, as well as port 71B of the first double-acting single-rod hydraulic cylinder 71, port 72B of the second double-acting single-rod hydraulic cylinder 72, port 73B of the third double-acting single-rod hydraulic cylinder 73, port 74B of the fourth double-acting single-rod hydraulic cylinder 74, port 75B of the fifth double-acting single-rod hydraulic cylinder 75, and port 76B of the sixth double-acting single-rod hydraulic cylinder 76.

[0107] The 58B port of the No. 14 hydraulically controlled check valve 58 is connected to the 56A port of the second pressure sensor 56, as well as the 59A port of the first proportional throttle valve 59, the 60A port of the second proportional throttle valve 60, the 61A port of the third proportional throttle valve 61, the 62A port of the fourth proportional throttle valve 62, the 63A port of the fifth proportional throttle valve 63, and the 64A port of the sixth proportional throttle valve 64.

[0108] The 59B port of the first proportional throttle valve 59 is connected to the 71A port of the first double-acting single-rod hydraulic cylinder 71; the 60B port of the second proportional throttle valve 60 is connected to the 72A port of the second double-acting single-rod hydraulic cylinder 72; the 61B port of the third proportional throttle valve 61 is connected to the 73A port of the third double-acting single-rod hydraulic cylinder 73; the 62B port of the fourth proportional throttle valve 62 is connected to the 74A port of the fourth double-acting single-rod hydraulic cylinder 74; the 63B port of the fifth proportional throttle valve 63 is connected to the 75A port of the fifth double-acting single-rod hydraulic cylinder 75; the 64B port of the sixth proportional throttle valve 64 is connected to the 76A port of the sixth double-acting single-rod hydraulic cylinder 76; the synchronous movement of the six double-acting single-rod hydraulic cylinders is achieved by adjusting the proportional throttle valves.

[0109] The first double-acting single-rod hydraulic cylinder 71 is connected to the first displacement sensor 65, the second double-acting single-rod hydraulic cylinder 72 is connected to the second displacement sensor 66, the third double-acting single-rod hydraulic cylinder 73 is connected to the third displacement sensor 67, the fourth double-acting single-rod hydraulic cylinder 74 is connected to the fourth displacement sensor 68, the fifth double-acting single-rod hydraulic cylinder 75 is connected to the fifth displacement sensor 69, and the sixth double-acting single-rod hydraulic cylinder 76 is connected to the sixth displacement sensor 70. The displacement sensors measure the displacement of the piston rods of the corresponding double-acting single-rod hydraulic cylinders.

[0110] When the three-position four-way solenoid reversing valve 79 is in the left position, its port 79B is connected to port 79P, and port 79A is connected to port 79T; when it is in the middle position, its port 79A, port 79B, and port 79T are connected, and port 79P is disconnected; when it is in the right position, its port 79B is connected to port 79T, and port 79A is connected to port 79P.

[0111] When the pressure at port C of the hydraulically controlled one-way valve is higher than the valve opening pressure, ports A and B are in a two-way conductive state; when the pressure at port C is lower than the valve opening pressure, it is in a one-way conductive state from port A to port B (port A to port B are conductive).

[0112] In order to control the quantitative motor to remain stationary at a corresponding position, each quantitative motor is also provided with a braking device, which brakes or releases the quantitative motor by contacting or disengaging with the output shaft of the quantitative motor.

[0113] The brake device of the first quantitative motor 7 is driven by the first elastic member acting to reset the single piston rod hydraulic cylinder 1. The rod chamber of the first elastic member acting to reset the single piston rod hydraulic cylinder 1 is connected to the oil tank 81; the 43A port of the first two-position three-way electromagnetic reversing valve 43 is connected to the oil source 80, the 43C port of the first two-position three-way electromagnetic reversing valve 43 is connected to the oil tank 81, and the 43B port of the first two-position three-way electromagnetic reversing valve 43 is connected to the 1A port of the first elastic member acting to reset the single piston rod hydraulic cylinder 1. A first throttle valve 25 is also connected between the 43B port of the first two-position three-way electromagnetic reversing valve 43 and the 1A port of the first elastic member acting to reset the single piston rod hydraulic cylinder 1.

[0114] The brake device of the second quantitative motor 8 is driven by the second elastic member acting to reset the single piston rod hydraulic cylinder 2. The rod chamber of the second elastic member acting to reset the single piston rod hydraulic cylinder 2 is connected to the oil tank 81; the 44A port of the second two-position three-way electromagnetic reversing valve 44 is connected to the oil source 80, the 44C port of the second two-position three-way electromagnetic reversing valve 44 is connected to the oil tank 81, and the 44B port of the second two-position three-way electromagnetic reversing valve 44 is connected to the 2A port of the second elastic member acting to reset the single piston rod hydraulic cylinder 2. A second throttle valve 26 is also connected between the 44B port of the second two-position three-way electromagnetic reversing valve 44 and the 2A port of the second elastic member acting to reset the single piston rod hydraulic cylinder 2.

[0115] The brake device of the third quantitative motor 9 is driven by the third elastic member acting to reset the single piston rod hydraulic cylinder 3. The rod chamber of the third elastic member acting to reset the single piston rod hydraulic cylinder 3 is connected to the oil tank 81; the 45A port of the third two-position three-way electromagnetic reversing valve 45 is connected to the oil source 80, the 45C port of the third two-position three-way electromagnetic reversing valve 45 is connected to the oil tank 81, and the 45B port of the third two-position three-way electromagnetic reversing valve 45 is connected to the 3A port of the third elastic member acting to reset the single piston rod hydraulic cylinder 3. A third throttle valve 27 is also connected between the 45B port of the third two-position three-way electromagnetic reversing valve 45 and the 3A port of the third elastic member acting to reset the single piston rod hydraulic cylinder 3.

[0116] The brake device of the fourth quantitative motor 10 is driven by the fourth elastic member action reset single piston rod hydraulic cylinder 4. The rod chamber of the fourth elastic member action reset single piston rod hydraulic cylinder 4 is connected to the oil tank 81; the 46A port of the fourth two-position three-way electromagnetic reversing valve 46 is connected to the oil source 80, the 46C port of the fourth two-position three-way electromagnetic reversing valve 46 is connected to the oil tank 81, and the 46B port of the fourth two-position three-way electromagnetic reversing valve 46 is connected to the 4A port of the fourth elastic member action reset single piston rod hydraulic cylinder 4. A fourth throttle valve 28 is also connected between the 46B port of the fourth two-position three-way electromagnetic reversing valve 46 and the 4A port of the fourth elastic member action reset single piston rod hydraulic cylinder 4.

[0117] The brake device of the fifth quantitative motor 11 is driven by the fifth elastic member action reset single piston rod hydraulic cylinder 5. The rod chamber of the fifth elastic member action reset single piston rod hydraulic cylinder 5 is connected to the oil tank 81; the 47A port of the fifth two-position three-way electromagnetic reversing valve 47 is connected to the oil source 80, the 47C port of the fifth two-position three-way electromagnetic reversing valve 47 is connected to the oil tank 81, and the 47B port of the fifth two-position three-way electromagnetic reversing valve 47 is connected to the 5A port of the fifth elastic member action reset single piston rod hydraulic cylinder 5. A fifth throttle valve 29 is also connected between the 47B port of the fifth two-position three-way electromagnetic reversing valve 47 and the 5A port of the fifth elastic member action reset single piston rod hydraulic cylinder 5.

[0118] The brake device of the sixth quantitative motor 12 is driven by the sixth elastic member action reset single piston rod hydraulic cylinder 6. The rod chamber of the sixth elastic member action reset single piston rod hydraulic cylinder 6 is connected to the oil tank 81; the 48A port of the sixth two-position three-way electromagnetic reversing valve 48 is connected to the oil source 80, the 48C port of the sixth two-position three-way electromagnetic reversing valve 48 is connected to the oil tank 81, and the 48B port of the sixth two-position three-way electromagnetic reversing valve 48 is connected to the 6A port of the sixth elastic member action reset single piston rod hydraulic cylinder 6. A sixth throttle valve 30 is also connected between the 48B port of the sixth two-position three-way electromagnetic reversing valve 48 and the 6A port of the sixth elastic member action reset single piston rod hydraulic cylinder 6.

[0119] The status of each valve in the drive circuit of the above six brake devices is as follows:

[0120] When the two-position three-way solenoid reversing valve is in the left position, its A port and B port are in the conducting state, and the C port is in the disconnected state; when it is in the right position, its B port and C port are in the conducting state, and its A port is in the disconnected state.

[0121] In the embodiment of the present invention, a circumferential adjustment hydraulic circuit and a radial adjustment hydraulic circuit are used to achieve full circumferential and radial position adjustment of the six support mechanisms. The specific adjustment process and principle are described in detail as follows:

[0122] Taking the first supporting structure as an example, the circumferential position adjustment process and principle of the supporting block 82 are as follows: when the first quantitative motor 7 needs to rotate forward, the first three-position four-way proportional reversing valve 37 is in the right position, and the high-pressure oil in the oil source 80 flows into the differential pressure reducing valve 49 through the 49A port of the first differential pressure reducing valve 49, and the hydraulic oil flows out from the 49B port after the pressure regulation of the first differential pressure reducing valve 49, and the hydraulic oil flowing out of the 49B port flows into the first three-position four-way proportional reversing valve 37 through the 37P port of the first three-position four-way proportional reversing valve 37, and the hydraulic oil flows out from the 37A port of the first three-position four-way proportional reversing valve 37, and the hydraulic oil flows out from the 37A port into the No. 1 hydraulically controlled one-way valve 13 through the 13A port of the No. 1 hydraulically controlled one-way valve 13, and flows into the No. 2 hydraulically controlled one-way valve 14 through the 14C port of the No. 2 hydraulically controlled one-way valve 14, and the No. 2 hydraulically controlled one-way valve 14 becomes a two-way conducting state, and flows through the 31A port of the first shuttle valve 31. The hydraulic oil flows into the first shuttle valve 31 through the port 31C after passing through the first shuttle valve 31. The hydraulic oil flowing out of the port 31C serves as a pilot oil and flows into the first differential pressure reducing valve 49 through the port 49C of the first differential pressure reducing valve 49 to adjust the outlet pressure of the first differential pressure reducing valve 49. The hydraulic oil flows out of the port 13B through the port 13B of the first hydraulically controlled one-way valve 13 and flows into the first quantitative motor 7 through the port 7A of the first quantitative motor 7. The hydraulic oil flows out of the port 7B through the port 7B of the first quantitative motor 7. The hydraulic oil flows out of the port 7B through the port 14B of the second hydraulically controlled one-way valve 14 and flows out of the port 14A of the second hydraulically controlled one-way valve 14. The hydraulic oil flows out of the port 14A through the port 37B of the first three-position four-way proportional reversing valve 37 and flows into the first three-position four-way proportional reversing valve 37. The hydraulic oil flows back to the oil tank 81 through the port 37T of the first three-position four-way proportional reversing valve 37. At this time, the first quantitative motor 7 drives the small gear 84 to rotate in the positive direction along the large gear 86, thereby driving the hydraulic cylinder base 83 to move in the positive direction of the slide rail.

[0123] When the first quantitative motor 7 needs to rotate in the opposite direction, the first three-position four-way proportional reversing valve 37 is in the left position, and the high-pressure oil in the oil source 80 flows into the differential pressure reducing valve 49 through the 49A port of the first differential pressure reducing valve 49, and the hydraulic oil flows out from the 49B port after the pressure regulation of the first differential pressure reducing valve 49, and the hydraulic oil flowing out of the 49B port flows into the first three-position four-way proportional reversing valve 37 through the 37P port of the first three-position four-way proportional reversing valve 37, and the hydraulic oil flows out from the 37B port after passing through the first three-position four-way proportional reversing valve 37, and the hydraulic oil flows out from the 37B port respectively flows into the No. 2 hydraulic control check valve 14 through the 14A port of the No. 2 hydraulic control check valve 14, and flows into the No. 1 hydraulic control check valve 13 through the 13C port of the No. 1 hydraulic control check valve 13, and the No. 1 hydraulic control check valve 13 becomes a two-way conducting state, and flows into the shuttle valve 31 through the 31B port of the first shuttle valve 31, and the hydraulic oil flows out of the 37P port of the first shuttle valve 31 after passing through the 37P port of the first shuttle valve 31. The hydraulic oil flows out from the 1C port, and the hydraulic oil flowing out from the 31C port serves as the pilot oil and flows into the differential pressure reducing valve 49 through the 49C port of the first differential pressure reducing valve 49 to adjust the outlet pressure of the first differential pressure reducing valve 49. The hydraulic oil flows out from the 14B port after passing through the No. 2 hydraulically controlled one-way valve 14. The hydraulic oil flowing out from the 14B port flows into the first quantitative motor 7 through the 7B port of the quantitative motor 7. The hydraulic oil flows out from the 7A port after passing through the first quantitative motor 7. The hydraulic oil flows out from the 7A port flows into the No. 1 hydraulically controlled one-way valve 13 through the 13B port of the No. 1 hydraulically controlled one-way valve 13. The hydraulic oil flows out from the 13A port of the No. 1 hydraulically controlled one-way valve 13. The hydraulic oil flows out from the 13A port through the 37A port of the first three-position four-way proportional reversing valve 37 and flows back to the oil tank 81 through the 37T port of the first three-position four-way proportional reversing valve 37 to realize the reverse rotation of the first quantitative motor 7. At this time, the first quantitative motor 7 drives the small gear 84 to rotate in the opposite direction along the large gear 86, thereby driving the hydraulic cylinder base 83 to move in the opposite direction along the slide rail.

[0124] The rotation of the first quantitative motor 7 drives the rotation of the small gear 84, which meshes with the large gear 86, and the large gear 86 is fixed, so the small gear 84 makes a circular motion along the circumferential direction of the large gear 86, driving the hydraulic cylinder base 83 to make a circular motion along the slide rail of the fixed frame 85, thereby realizing independent position control of the support block 82 in the circumferential direction. The forward and reverse control principles of the other five quantitative motors are the same as above.

[0125] Taking the first fixed-displacement motor 7 as an example, its braking adjustment process and principle are as follows: the first two-position three-way electromagnetic reversing valve 43 is in the right position, and under the action of the elastic element, the first elastic member resets the piston rod of the single-piston rod hydraulic cylinder 1 to drive the braking device, and the braking device contacts the output shaft of the first fixed-displacement motor 7, so that the first fixed-displacement motor 7 is in a braking state. When the braking state of the first fixed-displacement motor 7 needs to be released, the first two-position three-way electromagnetic reversing valve 43 is switched to the left position, and the high-pressure oil in the oil source 80 flows into the first two-position three-way electromagnetic reversing valve 43 through the 43A port of the first two-position three-way electromagnetic reversing valve 43, and the hydraulic oil flows out of the 43B port of the first two-position three-way electromagnetic reversing valve 43, and the hydraulic oil flowing out of the 43B port flows into the rod chamber of the first elastic member reset single-piston rod hydraulic cylinder 1 through the 1A port of the first elastic member reset single-piston rod hydraulic cylinder 1, and the piston rod of the first elastic member reset single-piston rod hydraulic cylinder 1 is retracted by force, and the piston rod of the first elastic member reset single-piston rod hydraulic cylinder 1 drives the brake device to disengage from the output shaft of the first fixed-displacement motor 7, so that the first fixed-displacement motor 7 is in a free state. The braking adjustment principle of the other five fixed-displacement motors is the same as above.

[0126] Taking the first supporting mechanism as an example, the radial position adjustment process and principle of the supporting block 82 are as follows: when the supporting block 82 moves to the specified position in the circumferential direction, the first double-acting single-rod hydraulic cylinder 71 extends, so that the supporting block 82 is in close contact with the rock wall. At this time, the three-position four-way electromagnetic reversing valve 79 is in the left position, and the high-pressure oil in the oil source 80 flows into the proportional reducing valve 78 through the 78A port of the proportional reducing valve 78, and the hydraulic oil flows out from the 78B port after passing through the proportional reducing valve 78. The hydraulic oil flowing out of the 78B port flows into the seventh throttle valve 77 through the 77A port of the seventh throttle valve 77, and the hydraulic oil flows out from the 77B port after passing through the seventh throttle valve 77. The hydraulic oil flowing out of the 77B port flows into the seventh throttle valve 77 through the 77A port of the seventh throttle valve 77. The 79P port of the electromagnetic reversing valve 79 flows into the three-position four-way electromagnetic reversing valve 79, and the hydraulic oil flows out from the 79B port after passing through the three-position four-way electromagnetic reversing valve 79. The hydraulic oil flowing out of the 79B port flows into the No. 14 hydraulic control check valve 58 through the 58A port of the No. 14 hydraulic control check valve 58, and flows into the No. 13 hydraulic control check valve 57 through the 57C port of the No. 13 hydraulic control check valve 57. The No. 13 hydraulic control check valve 57 becomes a two-way conductive state, and the hydraulic oil flows out from the 58B port after passing through the No. 14 hydraulic control check valve 58. The hydraulic oil flowing out of the 58B port flows into the second pressure sensor 56 through the 56A port of the second pressure sensor 56, and flows into the first proportional throttle valve 59 through the 59A port. The hydraulic oil flows out of the 59B port after being adjusted by the first proportional throttle valve 59. The hydraulic oil flowing out of the 59B port flows into the rodless chamber of the first double-acting single-rod hydraulic cylinder 71 through the 71A port of the first double-acting single-rod hydraulic cylinder 71. The hydraulic oil in the rod chamber of the first double-acting single-rod hydraulic cylinder 71 flows out through the 71B port. The hydraulic oil flowing out of the 71B port flows into the first pressure sensor 55 through the 55A port of the first pressure sensor 55, flows into the No. 13 hydraulic control check valve 57 through the 57B port of the No. 13 hydraulic control check valve 57, and flows out of the 57A port of the No. 13 hydraulic control check valve 57 after the hydraulic oil flows out. The hydraulic oil flowing out of the 57A port flows into the three-position four-way electromagnetic reversing valve 79. The hydraulic oil flows into the three-position four-way solenoid reversing valve 79 through the 79A port, and the hydraulic oil flows out from the 79T port of the three-position four-way solenoid reversing valve 79 and flows back to the oil tank 81. According to the displacement signal of the first displacement sensor 65, the displacement of the piston rod of the first double-acting single-rod hydraulic cylinder 71 is adjusted, and the synchronous movement of the double-acting single-rod hydraulic cylinder group is achieved by adjusting the valve port size of the corresponding proportional throttle valve. When the support blocks 82 are in close contact with the rock wall, the three-position four-way solenoid reversing valve 79 is switched to the middle position, the No. 13 hydraulic-controlled one-way valve 57 and the No. 14 hydraulic-controlled one-way valve 58 are in a one-way conduction state, and the double-acting single-rod hydraulic cylinder group is in a static self-locking state, so as to achieve the radial position adjustment of the support block 82.

[0127] The details not described in detail in the present invention are all conventional technical means known to those skilled in the art.

[0128] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A distributed TBM rear support device that is adjustable in all directions, characterized in that: It comprises a fixed frame connected with the main beam of the shield machine and a plurality of supporting mechanisms arranged on the fixed frame; the fixed frame is provided with a first transmission mechanism; the supporting mechanism comprises a supporting block, a first hydraulic cylinder, a hydraulic motor, a hydraulic cylinder base, a hydraulic circuit and a second transmission mechanism, and the hydraulic cylinder base is slidably mounted on the fixed frame; the hydraulic motor, the first hydraulic cylinder and the hydraulic cylinder base are connected; the supporting block is hinged with the piston rod of the first hydraulic cylinder; the hydraulic motor is connected with the second transmission mechanism; the second transmission mechanism cooperates with the first transmission mechanism; the hydraulic circuit controls the forward and reverse rotation of the hydraulic motor and drives the telescopic movement of the first hydraulic cylinder; The hydraulic circuit includes a circumferential adjustment hydraulic circuit connected to the hydraulic motor and a radial adjustment hydraulic circuit connected to the first hydraulic cylinder; The circumferential adjustment hydraulic circuit comprises a differential pressure reducing valve, a three-position four-way proportional reversing valve, a first hydraulically controlled one-way valve, and a second hydraulically controlled one-way valve connected in sequence; The oil source is connected to the A port of the differential pressure reducing valve; the B port of the differential pressure reducing valve is connected to the P port of the three-position four-way proportional reversing valve; the C port of the differential pressure reducing valve is connected to the C port of the shuttle valve; The A port of the three-position four-way proportional directional valve is respectively connected to the A port of the shuttle valve, the A port of the first hydraulically controlled one-way valve, and the C port of the second hydraulically controlled one-way valve; The B port of the three-position four-way proportional directional valve is respectively connected to the B port of the shuttle valve, the A port of the second hydraulically controlled one-way valve, and the C port of the first hydraulically controlled one-way valve; The B port of the first hydraulically controlled one-way valve is connected to the A port of the quantitative hydraulic motor; the B port of the second hydraulically controlled one-way valve is connected to the B port of the quantitative hydraulic motor; The T port of the three-position four-way proportional directional valve is connected to the oil tank; When the three-position four-way proportional reversing valve is in the left position, its B port is connected to the P port, and the A port is connected to the T port; when it is in the middle position, its A port, B port and T port are connected, and the P port is disconnected; when it is in the right position, its B port is connected to the T port, and the A port is connected to the P port; When the pressure at the C port of the first hydraulically controlled one-way valve and the second hydraulically controlled one-way valve is higher than the valve opening pressure, the A port and the B port are in a two-way conducting state; when the pressure at the C port is lower than the valve opening pressure, the A port to the B port is in a one-way conducting state; The radial adjustment hydraulic circuit includes a three-position four-way electromagnetic reversing valve, a third hydraulically controlled one-way valve, and a fourth hydraulically controlled one-way valve; the A port of the three-position four-way electromagnetic reversing valve is respectively connected to the A port of the third hydraulically controlled one-way valve and the C port of the fourth hydraulically controlled one-way valve; the B port of the three-position four-way electromagnetic reversing valve is respectively connected to the A port of the fourth hydraulically controlled one-way valve and the C port of the third hydraulically controlled one-way valve; the B port of the third hydraulically controlled one-way valve is connected to the A port of the first pressure sensor and the B ports of several first hydraulic cylinders; the B port of the fourth hydraulically controlled one-way valve is connected to the A port of the second pressure sensor and the A ports of several first hydraulic cylinders; the T port of the three-position four-way electromagnetic reversing valve is connected to the oil tank; When the three-position four-way solenoid reversing valve is in the left position, its B port is connected to the P port, and the A port is connected to the T port; when it is in the middle position, its A port, B port, and T port are connected, and the P port is disconnected; when it is in the right position, its B port is connected to the T port, and the A port is connected to the P port; When the pressure at the C port of the third hydraulically controlled one-way valve and the fourth hydraulically controlled one-way valve is higher than the valve opening pressure, their A port and B port are in a two-way conductive state; when the pressure at their C port is lower than the valve opening pressure, they are in a one-way conductive state from port A to port B.

2. The fully circumferentially adjustable distributed TBM rear support device according to claim 1 is characterized in that: The shuttle valve is a high-pressure priority shuttle valve.

3. The fully circumferentially adjustable distributed TBM rear support device according to claim 1 is characterized in that: The hydraulic motor is provided with a brake device, which is connected to the second hydraulic cylinder; the A port of the second hydraulic cylinder is connected to the B port of the two-position three-way electromagnetic reversing valve; the A port of the two-position three-way electromagnetic reversing valve is connected to the oil source, and the C port is connected to the oil tank; When the two-position three-way electromagnetic reversing valve is in the left position, its A port and B port are in the conducting state, and the C port is in the disconnected state; when it is in the right position, its B port and C port are in the conducting state, and its A port is in the disconnected state.

4. The fully circumferentially adjustable distributed TBM rear support device according to claim 1 is characterized in that: The first hydraulic cylinder is connected to a displacement sensor, and the displacement sensor is used to measure the displacement of the piston rod of the first hydraulic cylinder.

5. The fully circumferentially adjustable distributed TBM rear support device according to claim 1 is characterized in that: A proportional throttle valve is connected between the B port of the fourth hydraulically controlled one-way valve and the A port of the first hydraulic cylinder.

6. The fully circumferentially adjustable distributed TBM rear support device according to claim 1 is characterized in that: A proportional pressure reducing valve and a throttle valve are connected in sequence between the oil source and the P port of the three-position four-way solenoid directional valve.

7. The fully circumferentially adjustable distributed TBM rear support device according to any one of claims 1 to 6, characterized in that: The fixed frame is provided with a central hole for connecting the main beam of the shield machine; the fixed frame is provided with a circumferential slide rail, the hydraulic cylinder base is connected to the slide rail, and the hydraulic cylinder base moves circumferentially along the fixed frame under the action of the hydraulic motor.

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