CN201288568Y - Shield cutter head hydraulic system employing motor series and parallel hybrid driving - Google Patents

Abstract

The utility model discloses a shield cutterhead hydraulic system driven by motors connected in series and in parallel. Including motor, two-way variable pump, two-position three-way reversing valve, two-position two-way reversing valve, variable motor, relief valve, one-way valve and charge pump. The connection between the hydraulic motors driving the shield cutter head in this system can realize the mutual switching between parallel connection and series connection, so that the cutter head can better adapt to the needs of different geological conditions and excavation conditions. Since the flow flowing into each hydraulic motor in series mode is the output flow of the pump, the speed regulation range of the cutter head speed has been greatly improved. The shield cutterhead driving hydraulic system in the utility model adopts the hydraulic motor series-parallel hybrid drive mode, which broadens the speed regulation range of the cutterhead, can effectively reduce the displacement of the hydraulic pump in the power oil source, and because the closed The oil source of the system is small in size and compact in structure, which can reduce the system cost.

Description

A Shield Cutter Hydraulic System Driven by Motors in Series and Parallel

technical field

The utility model relates to a fluid pressure actuator, in particular to a shield cutterhead hydraulic system driven by motors connected in series and in parallel.

Background technique

Shield boring machine is a large-scale tunneling equipment specially used for underground tunnel excavation engineering construction. Compared with traditional construction methods, the shield method has many advantages such as safe and fast construction, high engineering quality, less ground disturbance, and low labor intensity. Due to the use of advanced excavation face stabilization technology, shield excavation has shown unique advantages especially in the construction of tunnel projects with complex and changeable geological conditions and harsh construction environments. With the development of science and technology and social progress, shield tunneling will gradually replace traditional methods.

The cutter head drive system is an important part of the shield tunneling machine, which drives the cutter head to rotate and cut the soil in front of the shield. The cutterhead drive system is a typical high-power, multi-actuator system. Due to the complex and changeable geological conditions during the excavation process, the cutter head drive system must meet the needs of excavation in various strata from soft soil to hard rock, and the speed varies widely. The driving speed of the traditional multi-motor parallel system is largely limited by the displacement of the hydraulic pump, and the range of speed regulation is very limited. Therefore, in order to enhance the ground adaptability of the roadheader, the design flow rate of the hydraulic source of the cutter head drive system often has to leave a large margin, and the efficiency of the large-displacement hydraulic pump system will be significantly reduced under low-speed conditions, resulting in Big waste.

Contents of the invention

In order to meet the adaptability requirements of the shield cutter head drive to complex formations, the purpose of the utility model is to provide a shield cutter head hydraulic system which adopts motor series-parallel hybrid drive. The cutter head drive hydraulic motor adopts the hybrid connection of series and parallel connection, the motors are connected in parallel under low speed conditions, and the motors are connected in series under high speed conditions, so that the cutter head drive system can realize different geological conditions by using a small displacement hydraulic pump for oil supply. The system can realize stepless speed regulation in a wide range by cooperating with the variable control mechanism of the motor and pump.

The technical solution adopted by the utility model to solve technical problems is:

The motor is rigidly connected to the two-way variable pump through a coupling; one end of the two-way variable pump is connected to the oil inlets of the first, second, third, fourth, fifth and sixth two-position two-way reversing valves respectively , the oil port at the other end of the two-way variable pump is respectively connected with the first oil port of the first, second, third, fourth and fifth two-position three-way reversing valve; the first, second, third, and fourth The oil outlets of the fifth and sixth two-position two-way reversing valves are respectively connected with one end oil ports of the respective first, second, third, fourth, fifth and sixth hydraulic motors; The oil ports at the other ends of the second, third, fourth and fifth hydraulic motors are respectively connected to the second oil ports of the respective first, second, third, fourth and fifth two-position three-way reversing valves, and the sixth The other port of the hydraulic motor is connected to the other port of the two-way variable pump; the third port of the first, second, third, fourth and fifth two-position three-way reversing valves is connected to the respective second, The oil ports at one end of the third, fourth, fifth and sixth hydraulic motors are connected; the oil inlet ports at both ends of the shuttle valve are respectively connected with the oil ports at both ends of the variable pump, and the oil outlet port of the shuttle valve is connected with the pressure sensor; the charge pump The shaft of the charging pump is connected to the motor; the oil suction port of the charge pump is connected to the fuel tank, and the oil outlet of the charge pump is connected to the oil inlet of the relief valve and the oil inlet of the first and second charge check valves; the oil outlet of the relief valve is connected to the The oil tank is connected; the oil outlets of the first and second oil supply check valves are respectively connected with the oil ports at both ends of the two-way variable variable pump; the oil inlet of the safety valve is connected with the oil outlets of the first and second pressure limiting check valves, and The oil outlet of the valve is connected to the oil inlet of the relief valve; the oil inlets of the first and second pressure limiting one-way valves are respectively connected to the oil ports at both ends of the two-way variable variable pump;

The beneficial effect that the utility model has is:

The hydraulic system adopts a closed circuit, which has a simple structure and takes up little space, which has certain practical value for shield tunneling in underground construction. The hydraulic motor driven by the cutterhead can be switched between series and parallel connections according to the geological conditions, so that the working conditions of the system can be adapted to various geological conditions, thereby reducing the overall scale of the hydraulic power oil source system and meeting the needs of shield tunneling to the greatest extent. Cutter drive performance requirements.

Due to the adoption of hydraulic motor series-parallel hybrid drive, the range of speed regulation of the cutter head is widened, which can effectively reduce the displacement of the hydraulic pump in the power oil source, and because the oil source of the closed system is small in size and compact in structure, the system can be reduced cost.

Description of drawings

Accompanying drawing is the structural schematic diagram of a specific embodiment of the utility model.

In the figure: 1. Motor, 2. Two-way variable pump, 3.1, 3.2. Pressure limiting check valve, 4.1. Safety valve, 4.2. Relief valve, 5.1, 5.2. Oil supply check valve, 6. Motor, 7. Charge pump, 8. Fuel tank, 9.1, 9.2, 9.3, 9.4, 9.5, 9.6. Two-position two-way reversing valve, 10.1, 10.2, 10.3, 10.4, 10.5. Two-position three-way reversing valve, 11.1, 11.2, 11.3 , 11.4, 11.5, 11.6. Hydraulic motor, 12. Pressure sensor, 13. Shuttle valve, 14, 15, 16.1, 16.2, 16.3, 16.4, 16.5, 16.6, 17.1, 17.2, 17.3, 17.4, 17.5, 17.6, 18.1, 18.2, 18.3, 18.4, 18.5, 18.6, 19.1, 19.2, 19.3, 19.4, 19.5, 20.1, 20.2, 20.3, 20.4, 20.5, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33 are pipelines.

Detailed ways

Below in conjunction with accompanying drawing and embodiment the utility model is further described.

As shown in the accompanying drawings, the motor 1 in the utility model is rigidly connected to the two-way variable pump 2 through a coupling; , the second, third, fourth, fifth and sixth two-position two-way reversing valves 9.1, 9.2, 9.3, 9.4, 9.5, and 9.6 are connected to the oil inlets, and the oil ports at the other end of the two-way variable pump 2 are connected through the pipe respectively. Roads 20.1, 20.2, 20.3, 20.4, 20.5 are connected to the first oil ports of the first, second, third, fourth and fifth two-position three-way reversing valves 10.1, 10.2, 10.3, 10.4, 10.5; , The oil outlets of the second, third, fourth, fifth and sixth two-position two-way reversing valves 9.1, 9.2, 9.3, 9.4, 9.5, and 9.6 respectively pass through pipelines 17.1, 17.2, 17.3, 17.4, 17.5, 17.6 is connected with one end oil port of respective first, second, third, fourth, fifth and sixth hydraulic motors 11.1, 11.2, 11.3, 11.4, 11.5, 11.6; The other end oil ports of the four and the fifth hydraulic motors 11.1, 11.2, 11.3, 11.4, 11.5 are respectively connected with the respective first, second, third, fourth and fifth two through pipelines 18.1, 18.2, 18.3, 18.4, 18.5 10.1, 10.2, 10.3, 10.4, 10.5 of the position three-way reversing valve are connected to the second oil port, and the other end oil port of the sixth hydraulic motor 11.6 is connected to the other end oil port of the bidirectional variable pump 2 through the pipeline 18.6; Two, the third, the fourth and the fifth two-position three-way reversing valve 10.1, 10.2, 10.3, 10.4, the third oil port of 10.5 is connected with the respective second, third, One end of the fourth, fifth, and sixth hydraulic motors 11.2, 11.3, 11.4, 11.5, and 11.6 are connected to one end of the oil ports; the oil inlets at both ends of the shuttle valve 13 are respectively connected to the oil ports at both ends of the variable pump 2 through pipelines 21, 22, The oil outlet of the shuttle valve 13 is connected to the pressure sensor 12; the shaft of the oil charge 7 is connected to the motor 6; the oil suction port of the oil charge pump 7 is connected to the oil tank 8 through the pipeline 32, and the oil outlet of the oil charge pump 7 is connected to the overflow valve 4.2 through the pipeline 31 The oil inlet and the oil inlets of the first and second replenishment check valves 5.1 and 5.2 connected via the pipeline 28 are connected; the oil outlet of the overflow valve 4.2 is connected with the fuel tank 8 through the pipeline 33; The oil outlets of the one-way valves 5.1 and 5.2 are connected to the oil ports at both ends of the two-way variable pump 2 through pipelines 27 and 29 respectively; The oil outlets of valves 3.1 and 3.2 are connected, and the oil outlet of safety valve 4.1 is connected with the oil inlet of overflow valve 4.2 through pipeline 30; the oil inlets of first and second pressure limiting check valves 3.1 and 3.2 are respectively connected through pipelines 23 25 is connected with the oil ports at both ends of the two-way variable displacement pump 2;

The working principle of the utility model is as follows:

The motor 1 is powered on, drives the two-way variable pump 2 to rotate, and adjusts the variable mechanism so that the variable pump 2 absorbs oil from the oil return pipe 14, and the pressure oil pumped out by the variable pump 2 is sent to the pipelines 16.1, 16.2, 16.3, and 16.4 through the pipeline 15 , 16.5, 16.6, 21.

When the shield machine is excavating in soft ground, the typical working condition of its cutterhead drive is low speed and high torque. At this time, the electromagnets of the two-position two-way reversing valves 9.1, 9.2, 9.3, 9.4, 9.5, and 9.6 are energized, and the electromagnets of the two-position three-way reversing valves 10.1, 10.2, 10.3, 10.4, and 10.5 are de-energized. The high-pressure oil in the pipelines 16.1, 16.2, 16.3, 16.4, 16.5, and 16.6 respectively passes through the two-position two-way reversing valves 9.1, 9.2, 9.3, 9.4, 9.5, and 9.6, and the pipelines 17.1, 17.2, 17.3, 17.4, 17.5, and 17.6 , hydraulic motors 11.1, 11.2, 11.3, 11.4, 11.5, 11.6, pipelines 20.1, 20.2, 20.3, 20.4, 20.5, 18.6 are collected into the oil return pipeline 14. Since the driving hydraulic motors are connected in parallel, when the output flow of the pump is constant, the sum of the flow entering each hydraulic motor is equal to the output flow of the pump, and the pressure difference at both ends of each hydraulic motor is the system working pressure, which is suitable for low speed and high torque working conditions.

When the shield excavates in hard formations, the typical working condition of its cutter head drive is high speed and low torque. At this time, the electromagnet of the two-position two-way reversing valve 9.1 is energized, the electromagnets of the two-position two-way reversing valve 9.2, 9.3, 9.4, 9.5, and 9.6 are de-energized, and the two-position three-way reversing valve 10.1, 10.2, The electromagnets of 10.3, 10.4, and 10.5 are energized, and the high-pressure oil in pipeline 15 passes through pipeline 16.1, two-position two-way reversing valve 9.1, pipeline 17.1, hydraulic motor 11.1, pipeline 18.1, two-position three-way reversing valve 10.1, pipeline 19.1, hydraulic motor 11.2, pipeline 18.2, two-position three-way reversing valve 10.2, pipeline 19.2, hydraulic motor 11.3, pipeline 18.3, two-position three-way reversing valve 10.3, pipeline 19.3, hydraulic motor 11.4, pipeline 18.4, two-position three-way reversing valve 10.4, pipeline 19.4, hydraulic motor 11.5, pipeline 18.5, two-position three-way reversing valve 10.5, pipeline 19.5, hydraulic motor 11.6, pipeline 18.6 flow back Line 14. Since the driving hydraulic motors are connected in series, when the output flow of the pump is constant, the flow entering each hydraulic motor is equal to the output flow of the pump, and the sum of the pressure differences at both ends of each hydraulic motor is equal to the working pressure of the system, which is suitable for high-speed and low-torque work condition.

When the oil ports at both ends of the two-way variable variable pump 2 are interchanged, the pipeline 15 becomes an oil return pipe, and the pipeline 14 becomes a high-pressure oil pipe, and the flow direction of the hydraulic oil in each oil circuit is opposite to the above situation. Or in series to achieve reverse rotation, its working principle is the same as the previous case

The one-way valves 3.1, 3.2 and the safety valve 4.1 form a pressure-limiting circuit. When the pipeline 15 is a pressure oil pipe, the hydraulic oil in the pipeline 15 flows to the safety valve 4.1 through the pipeline 23, the one-way valve 3.1, and the pipeline 26. When the system pressure exceeds the set pressure of the safety valve, the safety valve 4.1 opens, and part of the hydraulic oil in the pipeline 26 flows into the oil supply pipeline 30, and the system realizes pressure relief. When the pipeline 14 is a pressure oil pipe, the hydraulic oil in the pipeline 14 flows to the oil inlet of the safety valve 4.1 through the pipeline 25, the check valve 3.2, and the pipeline 24 to realize pressure limiting protection.

The motor 6 drives the charge pump 7 to absorb oil from the oil tank 8, and the pressure oil passes through the pipeline 31 to the pipeline 30 and the oil inlet of the overflow valve 4.2. When the pipeline 14 is an oil return pipeline, the pressure of the hydraulic oil in the pipeline 30 is higher than the pressure of the hydraulic oil in the pipeline 14, and the hydraulic oil in the pipeline 30 flows into the pipeline 14 through the check valve 5.2 for oil replenishment. When the pipeline 15 is an oil return pipeline, the pressure of the hydraulic oil in the pipeline 30 is higher than the pressure of the hydraulic oil in the pipeline 15, and the hydraulic oil in the pipeline 30 flows into the pipeline 15 through the check valve 5.1 for replenishment. The pressure of oil replenishment of the system is set by overflow valve 4.2, and the excess flow of oil replenishment system flows back to the oil tank through overflow valve 4.2 and pipeline 33.

The pressure sensor 12 can always detect the pressure of the high-pressure chamber in the hydraulic system under the action of the shuttle valve 13. This signal can be fed back to the control system in real time to adjust the variable mechanism of the two-way variable pump 2 and change the displacement of the pump to form a load sensitive system. , making the system more energy efficient.

Since the displacement of the pump and motor used in this system is variable, it is not only possible to switch between high and low speeds of the shield cutterhead under different working conditions by changing the connection method of the motor, but also to adjust the The displacement adjustment mechanism of variable pump and variable motor can realize stepless speed regulation under high-speed working conditions and low-speed working conditions.

The above-mentioned specific embodiments are used to explain the utility model, rather than to limit the utility model. Within the spirit of the utility model and the scope of protection of the claims, any modifications and changes made to the utility model fall into the scope of the utility model. scope of protection.

Claims (1)

1, a kind of shield-structured cutter head hydraulic system that adopts motor connection in series-parallel combination drive is characterized in that: motor (1) is rigidly connected through shaft coupling and two-way variable displacement pump (2); One end hydraulic fluid port of two-way variable displacement pump (2) links to each other with the oil-in of the 6th bi-bit bi-pass reversal valve (9.1,9.2,9.3,9.4,9.5,9.6) with the first, second, third, fourth, the 5th respectively, and the other end hydraulic fluid port of two-way variable displacement pump (2) links to each other with first hydraulic fluid port of the 5th two position three way directional control valve (10.1,10.2,10.3,10.4,10.5) with first, second, third, fourth respectively; First, second, third, fourth, the 5th with the oil-out of the 6th bi-bit bi-pass reversal valve (9.1,9.2,9.3,9.4,9.5,9.6) respectively with the first, second, third, fourth, the 5th linking to each other separately with an end hydraulic fluid port of the 6th hydraulic motor (11.1,11.2,11.3,11.4,11.5,11.6); First, second, third, fourth with the other end hydraulic fluid port of the 5th hydraulic motor (11.1,11.2,11.3,11.4,11.5) respectively with first, second, third, fourth linking to each other separately with the 5th two position three way directional control valve (10.1,10.2,10.3,10.4,10.5) second hydraulic fluid port, the other end hydraulic fluid port of the 6th hydraulic motor (11.6) is connected with the other end hydraulic fluid port of two-way variable displacement pump (2); First, second, third, fourth with the 3rd hydraulic fluid port of the 5th two position three way directional control valve (10.1,10.2,10.3,10.4,10.5) with separately second, third, the 4th, the 5th link to each other with an end hydraulic fluid port of the 6th hydraulic motor (11.2,11.3,11.4,11.5,11.6); The two ends oil-in of shuttle valve (13) is connected with variable pump (2) two ends hydraulic fluid port respectively, and the oil-out of shuttle valve (13) is connected with pressure sensor (12); The axle of slippage pump (7) is connected with motor (6); Slippage pump (7) inlet port connects fuel tank (8), and the oil-out of slippage pump (7) links to each other with the oil-in of overflow valve (4.2) oil-in and first, second repairing one way valve (5.1,5.2); Overflow valve (4.2) oil-out is connected with fuel tank (8); The oil-out of first, second repairing one way valve (5.1,5.2) links to each other with two-way variable displacement pump (2) two ends hydraulic fluid port respectively; Safety valve (4.1) oil-in links to each other with first, second pressure limiting one way valve (3.1,3.2) oil-out, and safety valve (4.1) oil-out links to each other with overflow valve (4.2) oil-in; First, second pressure limiting one way valve (3.1,3.2) oil-in links to each other with two-way variable displacement pump (2) two ends hydraulic fluid port respectively.

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