CN216666112U - Slow-speed propelling hydraulic system for shield tunneling machine and shield tunneling machine - Google Patents
Slow-speed propelling hydraulic system for shield tunneling machine and shield tunneling machine Download PDFInfo
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- CN216666112U CN216666112U CN202122324720.1U CN202122324720U CN216666112U CN 216666112 U CN216666112 U CN 216666112U CN 202122324720 U CN202122324720 U CN 202122324720U CN 216666112 U CN216666112 U CN 216666112U
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Abstract
The invention provides a slow-speed propelling hydraulic system for a shield machine and the shield machine, wherein a variable pump system, a filter, a speed regulating valve and a reversing valve I are sequentially connected, the reversing valve I is connected with an oil cylinder, a rodless cavity of the oil cylinder leads out a path of oil return oil path I to be connected with an oil path, a cartridge valve II is connected to the oil return oil path I, the reversing valve II is connected with a valve front oil path and a control oil path of the cartridge valve II, and the cartridge valve II is controlled to be opened and closed; the reversing valve I controls the oil inlet and outlet directions of a rodless cavity and a rod cavity of the oil cylinder; the reversing valve I is connected with an oil tank; the slow-speed propulsion pump is connected with the variable pump system in parallel, a flow control valve, a cartridge valve I and an overflow valve I are connected between oil outlets of the slow-speed propulsion pump and the variable pump system, and the overflow valve I controls the cartridge valve I to be opened and closed. The shield tunneling machine has the advantages that the service power of the shield tunneling machine is effectively reduced, unnecessary loss of the shield tunneling machine is reduced, the service life of the system is prolonged, meanwhile, the cutter head body is effectively protected due to the existence of a new system, the operation difficulty of a shield driver is reduced, and the tunneling efficiency is improved.
Description
Technical Field
The invention belongs to the technical field of shield tunneling machines, and particularly relates to a slow-speed propelling hydraulic system and a shield tunneling machine.
Background
The shield machine propulsion hydraulic system plays an extremely important role in the shield machine tunneling process, the continuity, the stability and the like of the system have extremely important influences on the tunneling speed and the tunneling efficiency of the shield machine, and the system is a key point for accurately propelling the shield machine according to a set line. The shield machine propulsion system has the characteristics of high power, variable load, small installation space and the like. When the shield machine is used for tunneling, the geological condition is often complex, the shield body of the shield machine is subjected to different resistance of strata, the tunneling direction of the shield machine is easy to deviate, and meanwhile, when curve propulsion is carried out, the shield body of the shield machine needs to be adjusted in forward tilting, backward tilting, left-right swinging or compound directions, the shield machine can not advance according to an appointed line, at the moment, a propelling hydraulic cylinder needs to be accurately controlled to correct the deviation, and in the tunneling process of the shield machine, the propelling hydraulic system has the following two functions: 1) in the propelling mode, the advancing power of the shield machine and the torsional moment for adjusting the posture of the shield machine are provided, and the deviation amount of the tunnel axis and the design axis is an important standard for measuring the shield construction quality in the shield construction, so that the propelling hydraulic system adopts zone control to reasonably adjust the propelling pressure of each zone of the propelling hydraulic system to obtain the required torsional moment so as to finish the adjustment of the posture of the shield machine; 2) under the assembly mode, after the shield machine finishes one section of tunneling, the assembly of the segments is realized to form a ring, at the moment, the propulsion oil cylinder can keep the positioning of the segments, the segments are prevented from dropping, and meanwhile, the water and soil pressure of a propulsion surface is overcome, and the shield machine is prevented from retreating.
In the existing soft soil cutterhead EPB shield machine, a propulsion hydraulic system consists of a hydraulic pump station, a speed and pressure regulating mechanism, a reversing control valve group and propulsion oil cylinders, wherein 32 oil cylinders are uniformly distributed on the inner circular wall of the middle body of the shield machine in 16 groups and are divided into an upper area, a lower area, a left area and a right area capable of regulating hydraulic pressure, propulsion force and propulsion speed are provided for the forward movement of the shield machine, and the turning direction regulating and deviation rectifying functions of the shield machine are realized by regulating the pressure difference of the four areas. The hydraulic pump station of the propulsion system consists of a constant-pressure variable pump, the power of the constant-pressure variable pump is 75KW, and the constant-pressure variable pump provides constant power for the forward movement of the shield tunneling machine. The pressure of the constant pressure pump can be adjusted through an electro-hydraulic proportional overflow valve on the oil pump, and when the flow rate is changed within the range of 0-qmax, the oil supply pressure of the adjusted pump is kept constant. Constant pressure variable displacement pumps are commonly used as a constant pressure oil source for valve controlled systems to avoid flooding losses. The high pressure oil output by the constant pressure variable pump is respectively delivered to A, B, C, D four groups of propulsion direction control valve groups which are connected in parallel, and the propulsion oil cylinder is controlled after the flow and pressure of the valve groups are adjusted and reversed, so that the propulsion speed, the thrust and the direction of the propulsion oil cylinder are controlled to a certain extent.
However, in the design mode, when a fixed pile is arranged in front or the fixed pile is spread over rocks, the tunneling speed and the tunneling posture of the shield tunneling machine are not easy to control, because a power unit arranged in a propulsion system of the shield tunneling machine is a variable pump, the forward thrust of a cutter head of the shield tunneling machine mainly depends on the variable pump in the process of cutting the fixed pile or the rocks during the construction of the shield tunneling machine, the pile grinding speed of the forward propulsion of the cutter head is unstable due to the unstable output flow of the variable pump, and if the pile grinding speed of the shield tunneling machine is too high, the cutter head of the shield tunneling machine is damaged, the service life of the cutter head is shortened, and the operation difficulty of a shield driver is greatly increased. For the above reasons, there is a need for a slow-propelling hydraulic system with a pile grinding function, which can solve the above problems, so as to achieve a controllable tunneling speed of a shield tunneling machine during pile grinding, and also protect a cutter head body from abrasion or wear loss at a controllable level.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the slow propelling hydraulic system for the shield machine and the shield machine can effectively reduce damage to a cutter head caused by the fact that the propelling speed of the shield machine is too high.
The invention is realized by the following steps: a slow-speed propelling hydraulic system for a shield machine comprises a variable pump system, a filter, a speed regulating valve, a reversing valve I, an oil cylinder, a slow-speed propelling pump, a flow control valve, a one-way valve I, a cartridge valve II, an overflow valve I and a reversing valve II;
the variable pump system, the filter, the speed regulating valve and the reversing valve I are sequentially connected, the reversing valve I is connected with the oil cylinder, a rodless cavity of the oil cylinder leads out a path of oil return oil way I to be connected with an oil way, the cartridge valve II is connected to the oil return oil way I, the reversing valve II is connected with a valve front oil way and a control oil way of the cartridge valve II and controls the cartridge valve II to open and close;
the reversing valve I controls the oil inlet and outlet directions of a rodless cavity and a rod cavity of the oil cylinder; the reversing valve I is connected with an oil tank;
the low-speed propulsion pump is connected with the variable pump system in parallel, a flow control valve, a cartridge valve I and an overflow valve I are connected between oil outlets of the low-speed propulsion pump and the variable pump system, and the overflow valve I controls the cartridge valve I to open and close.
Furthermore, the variable pump system comprises a variable pump, a swash plate oil cylinder, a reversing valve III and an overflow valve II; the swash plate oil cylinder is connected with the variable pump and controls the swash plate inclination of the variable pump, the reversing valve III is connected with the swash plate oil cylinder and controls the oil inlet and outlet directions of a rod cavity and a rodless cavity of the swash plate oil cylinder, and the overflow valve II is connected with the reversing valve III.
And the one-way valve I is connected to an oil way between the reversing valve I and the rodless cavity of the oil cylinder.
And the oil cylinder further comprises an unloading valve and an overflow valve III, wherein the unloading valve and the overflow valve III are connected in parallel on an oil path between the rodless cavity of the oil cylinder and the oil tank.
Further, the device also comprises a one-way valve II, and the one-way valve II is connected to an oil way between the slow propulsion pump and the filter.
Further, the device also comprises an overflow valve IV, a reversing valve IV and a cartridge valve III; the cartridge valve III is connected in parallel to oil paths of the filter and the speed regulating valve, an oil return path II is led out from a valve rear oil path of the speed regulating valve and connected with an oil tank, the overflow valve IV is connected in the oil return path II, and the reversing valve IV is connected with a valve front oil path of the filter, the oil return path II and a control oil path of the cartridge valve III.
The invention also provides a shield tunneling machine which comprises a hydraulic control system, wherein the hydraulic control system is the slow propelling hydraulic system.
The invention has the following beneficial effects: the damage of a cutter head caused by the over-high propelling speed of the shield machine can be effectively reduced, meanwhile, a control system for normal driving can be distinguished from a control system required by pile grinding, the original working mode can be suspended when the shield machine grinds the pile, and a slow propelling module is used instead; therefore, the using power of the shield machine can be effectively reduced, unnecessary loss of the shield machine is reduced, the service life of the system is prolonged, the cutter head body is effectively protected due to the existence of a new system, the operation difficulty of a shield driver is reduced, and the tunneling efficiency is improved.
Drawings
FIG. 1 is a schematic diagram of a preferred embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that the terms "upper", "lower", "inner", "outer", "front", "rear", "both ends", "one end", "the other end", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "disposed," "connected," and the like are to be construed broadly, such as "connected," which may be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
As shown in fig. 1, the embodiment provides a slow-speed propulsion hydraulic system for a shield machine, which includes a variable pump system, a check valve I17, a check valve II23, a filter 9, a speed control valve 10, a reversing valve I12, a cylinder I15, a cylinder II16, a slow-speed propulsion pump 1, a flow control valve 8, a check valve I17, a cartridge valve I3, a cartridge valve II11, an overflow valve I2, an overflow valve II6, a reversing valve II18, an unloading valve 14, an overflow valve III13, an overflow valve IV19, a reversing valve III7, a reversing valve IV20, and a cartridge valve III 21.
The variable pump system, the filter 9, the speed regulating valve 10 and the reversing valve I12 are sequentially connected, the reversing valve I12 is respectively connected with the oil cylinder I15 and the oil cylinder II16, a route of oil return oil way I is led out from a rodless cavity of the oil cylinder I15 and a rodless cavity of the oil cylinder II16 and is connected with an oil way, the cartridge valve II11 is connected to the oil return oil way I, the reversing valve II18 is connected with a valve front oil way and a control oil way of the cartridge valve II11, and the cartridge valve II11 is controlled to be opened and closed. The reversing valve I12 controls the oil inlet and outlet directions of the rodless cavity and the rod cavity of the oil cylinder I15 and the oil cylinder II 16; the reversing valve I12 is connected with the oil tank. The unloading valve 14 and the overflow valve III13 are connected in parallel on an oil path between the rodless cavities of the oil cylinder I15 and the oil cylinder II16 and an oil tank.
The slow-speed propulsion pump 1 is connected with the variable pump system in parallel, a flow control valve 8, a cartridge valve I3 and an overflow valve I2 are connected between oil outlets of the slow-speed propulsion pump 1 and the variable pump system, and the overflow valve I2 controls the opening and closing of the cartridge valve I3. The check valve I17 is connected to the oil path between the change valve I12 and the rodless chambers of the cylinder I15 and the cylinder II 16.
The variable pump system comprises a variable pump 4, a swash plate cylinder 5, a reversing valve III7 and an overflow valve II 6. The swash plate oil cylinder 5 is connected with the variable pump 4 and controls the inclination of a swash plate of the variable pump 4, and the reversing valve III7 is a servo reversing valve and is connected with the swash plate oil cylinder 5 and controls the oil inlet and outlet directions of a rod cavity and a rodless cavity of the swash plate oil cylinder 5, so that the extension and retraction of the swash plate oil cylinder 5 are realized. Spill valve II6 is connected to diverter valve III 7. The check valve II23 is connected to the oil path between the slow propulsion pump 1 and the filter 9.
The cartridge valve III21 is connected in parallel on the oil paths of the filter 9 and the speed regulating valve 10, an oil return path II is led out from the oil path behind the speed regulating valve 10 to be connected with the oil tank, the overflow valve IV19 is connected in the oil return path II, and the reversing valve IV20 is connected with the oil path before the filter 9, the oil return path II and the control oil path of the cartridge valve III 21.
The slow-speed propulsion pump 1 is a fixed displacement pump, the overflow valve II6 and the overflow valve IV19 are proportional overflow valves, the flow control valve 8 is a proportional flow control valve, the reversing valve I12 is a three-position four-way reversing valve, and the reversing valve II18, the reversing valve III7 and the reversing valve IV20 are two-position three-way reversing valves.
The diameter of a rodless cavity of the oil cylinder I15 and the oil cylinder II16 is 220mm, the diameter of a rod cavity is 180mm, the stroke of the oil cylinder is 2200mm, and the shield tunneling machine is required to advance at a speed of about 5-10mm under the condition of pile grinding, so that the advancing speed of the shield tunneling machine is set to be 5-10mm during pile grinding.
The respective components determine the specific selection based on the following flow calculation process:
area of rodless cavity:
wherein A1 is the area of the rodless cavity in m2(ii) a D is the rodless cavity diameter in mm.
Area of the rod cavity:
wherein A2 is the area of the rodless cavity in m2(ii) a D is the diameter of the rodless cavity and the unit is mm; d is the diameter of the lumen with the shaft in mm.
Thus in the propulsion mode:
when the propelling speed is 5mm/min, the required flow q is1。
q1＝nv1A1＝32×5×0.038＝6.08L；
In the formula, q1The flow rate provided for the slow propulsion pump 1 is L/min; n is the number of working oil cylinders in the propulsion mode.
v1The unit is mm/min for the propulsion speed; a. the1Is the area of the rodless cavity in m2。
When the propelling speed is 10mm/min, the required flow q is2。
q2＝nv2A1＝32×10×0.038＝12.16L；
In the formula, q2The flow rate provided for the slow propelling pump is L/min; and n is the number of the working oil cylinders in the propulsion mode.
v2The unit is mm/min for the propulsion speed; a. the1Is the area of the rodless cavity in m2。
According to calculation, under the tunneling mode, when the propelling speed is 5mm/min, the system needs to provide 6.08L of flow, and when the propelling speed is 10mm/min, the system needs to provide 12.16L of flow. Meanwhile, the pressure of the system can reach 350Bar in the tunneling mode, so that the power N required by the system is as follows:
wherein N is the power required by the slow-speed propulsion system and the unit is KW; p is the working pressure in the propulsion mode, and the unit is Bar; q is the system flow in the propulsion mode and is expressed in L/min.
Through calculation, when the tunneling speed of the shield tunneling machine is 5-10mm/min, the rated power required by the system is 8.6928KW, and the maximum power is 1.2 times of the rated power of the shield tunneling machine, so that the maximum power is 10.43136 KW. According to the situation, the system of the invention needs to select an 11KW motor as a high-efficiency asynchronous motor, so that the operation reliability and safety of the slow-speed propulsion pump 1 are ensured.
Referring to the sample data of the bostwill, a mainstream hydraulic product supplier at present, the slow-speed propulsion pump 1 adopts a gear pump with internal engagement and constant displacement as a power unit, the model of the pump is PGH3-2X/011RE07VU2, and the slow-speed propulsion pump is mainly characterized by constant displacement, low working noise and low flow pulsation, has high efficiency even at low rotating speed and low-viscosity oil due to the sealing clearance compensation of the pump, is suitable for wide viscosity and rotating speed range, can bear 350Bar working pressure and output 15L/min flow.
Meanwhile, the pipeline is required to be provided with a flow control valve 8, the sample data of the bosch Lee is also referred, a proportional flow control valve of 2FRE10-4X16LBK4M is selected, the proportional flow control valve has a two-way function, corresponding flow with large degree compensation on pressure and temperature can be output according to the value of the provided electric signal, the flow can be adjusted through a potentiometer, and the maximum passing flow of the system can be set to 16L/min to meet the design requirement. When the device is in operation, the maximum flow rate is set to 16L/min.
The invention also provides a shield tunneling machine which comprises the slow propelling hydraulic system.
The working principle and the process are as follows:
under a normal tunneling mode of the shield tunneling machine, the reversing valve II18 is electrified, and the cartridge valve II11 is in a conducting state. At the moment, under the action of the variable pump 4, hydraulic oil sequentially passes through the filter 9 and the speed regulating valve 10 and then reaches the reversing valve I12, when the left side of the reversing valve I12 is electrified and is in a left position, the hydraulic oil respectively enters rod cavities of the oil cylinder I15 and the oil cylinder II16, and piston rods of the oil cylinder I15 and the oil cylinder II16 are driven to contract. The hydraulic oil in the rodless cavities of the oil cylinder I15 and the oil cylinder II16 returns to the oil tank through the cartridge valve II 11. When the reversing valve II18 is de-energized, the cartridge valve II11 is in a closed state, and the right side of the reversing valve I12 is energized and is in a right position, hydraulic oil respectively enters the rodless cavities of the oil cylinder I15 and the oil cylinder II16 to drive the piston rods of the two to extend out. The hydraulic oil in the rodless cavities of the oil cylinder I15 and the oil cylinder II16 returns to the oil tank through the reversing valve I12.
Under the splicing mode of the shield tunneling machine, the reversing valve IV20 is electrified, the cartridge valve III21 is in a conducting state, the reversing valve II18 is electrified, and the cartridge valve II11 is in a conducting state. At this time, under the action of the variable displacement pump 4, hydraulic oil sequentially passes through the cartridge valve III21 to reach the directional control valve I12, and when the left side of the directional control valve I12 is electrified and is in the left position, the hydraulic oil respectively enters the rod cavities of the oil cylinder I15 and the oil cylinder II16 to drive the piston rods of the two to contract. The hydraulic oil in the rodless cavities of the oil cylinder I15 and the oil cylinder II16 returns to the oil tank through the cartridge valve II 11. When the reversing valve II18 is de-energized, the cartridge valve II11 is in a closed state, and the right side of the reversing valve I12 is energized and is in a right position, hydraulic oil respectively enters the rodless cavities of the oil cylinder I15 and the oil cylinder II16 to drive the piston rods of the two to extend out. The hydraulic oil in the rodless cavities of the oil cylinder I15 and the oil cylinder II16 returns to the oil tank through the reversing valve I12.
Under the slow propulsion mode of the shield tunneling machine and under the action of the slow propulsion pump 1, hydraulic oil sequentially passes through the one-way valve II23, the filter 9 and the speed regulating valve 10, then reaches the reversing valve I12, and then reaches the oil cylinder I15 and the oil cylinder II 16. In the mode, the shield machine can stably enter a pile grinding mode, the operation difficulty of a shield driver is greatly reduced, and the shield machine can stably tunnel.
Although the present invention has been described in detail with reference to examples, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (7)
1. A slow-speed propelling hydraulic system for a shield machine is characterized by comprising a variable pump system, a filter (9), a speed regulating valve (10), a reversing valve I (12), an oil cylinder, a slow-speed propelling pump (1), a flow control valve (8), a one-way valve I (17), a cartridge valve I (3), a cartridge valve II (11), an overflow valve I (2) and a reversing valve II (18);
the variable pump system, the filter (9), the speed regulating valve (10) and the reversing valve I (12) are sequentially connected, the reversing valve I (12) is connected with the oil cylinder, one oil return oil way I is led out from a rodless cavity of the oil cylinder and is connected with an oil way, the cartridge valve II (11) is connected to the oil return oil way I, the reversing valve II (18) is connected with a valve front oil way and a control oil way of the cartridge valve II (11), and the cartridge valve II (11) is controlled to be opened and closed;
the reversing valve I (12) controls the oil inlet and outlet directions of a rodless cavity and a rod cavity of the oil cylinder; the reversing valve I (12) is connected with an oil tank;
the slow-speed propulsion pump (1) is connected with the variable pump system in parallel, a flow control valve (8), a cartridge valve I (3) and an overflow valve I (2) are connected between oil outlets of the slow-speed propulsion pump and the variable pump system, and the overflow valve I (2) controls the cartridge valve I (3) to be opened and closed.
2. The slow-propelling hydraulic system for a shield tunneling machine according to claim 1, wherein the variable pump system comprises a variable pump (4), a swash plate cylinder (5), a reversing valve III (7) and an overflow valve II (6); the swash plate oil cylinder (5) is connected with the variable pump (4) and controls the inclination of a swash plate of the variable pump (4), the reversing valve III (7) is connected with the swash plate oil cylinder (5) and controls the oil inlet and outlet directions of a rod cavity and a rodless cavity of the swash plate oil cylinder (5), and the overflow valve II (6) is connected with the reversing valve III (7).
3. The slow-propelling hydraulic system for the shield tunneling machine according to claim 2, further comprising a one-way valve I (17), wherein the one-way valve I (17) is connected to an oil path between the reversing valve I (12) and the rodless cavity of the oil cylinder.
4. The slow-speed propelling hydraulic system for the shield tunneling machine according to claim 3, further comprising an unloading valve (14) and an overflow valve III (13), wherein the unloading valve (14) and the overflow valve III (13) are connected in parallel on an oil path between the rodless cavity of the oil cylinder and the oil tank.
5. A slow-propulsion hydraulic system for a shield tunneling machine according to claim 4, characterized by further comprising a check valve II (23), wherein the check valve II (23) is connected to the oil path between the slow-propulsion pump (1) and the filter (9).
6. The slow-propelling hydraulic system for the shield tunneling machine according to claim 5, further comprising an overflow valve IV (19), a reversing valve IV (20) and a cartridge valve III (21); the cartridge valve III (21) is connected in parallel to oil ways of the filter (9) and the speed regulating valve (10), an oil return oil way II is led out from an oil way behind the speed regulating valve (10) to be connected with an oil tank, the overflow valve IV (19) is connected in the oil return oil way II, and the reversing valve IV (20) is connected with a valve front oil way of the filter (9), the oil return oil way II and a control oil way of the cartridge valve III (21).
7. A shield tunneling machine comprising a hydraulic control system, wherein the hydraulic control system is the slow-propulsion hydraulic system of claim 1.
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| CN202122324720.1U CN216666112U (en) | 2021-09-26 | 2021-09-26 | Slow-speed propelling hydraulic system for shield tunneling machine and shield tunneling machine |
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