CN118998136A - High-freedom-degree six-group tightening hydraulic system applied to vertical shaft heading machine - Google Patents
High-freedom-degree six-group tightening hydraulic system applied to vertical shaft heading machine Download PDFInfo
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- CN118998136A CN118998136A CN202411455123.4A CN202411455123A CN118998136A CN 118998136 A CN118998136 A CN 118998136A CN 202411455123 A CN202411455123 A CN 202411455123A CN 118998136 A CN118998136 A CN 118998136A
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- 239000003921 oil Substances 0.000 claims description 345
- 230000001502 supplementing effect Effects 0.000 claims description 34
- 238000011084 recovery Methods 0.000 claims description 7
- 239000010720 hydraulic oil Substances 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000010276 construction Methods 0.000 abstract description 6
- 238000004064 recycling Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000005641 tunneling Effects 0.000 description 2
- 238000009412 basement excavation Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
- E21D1/00—Sinking shafts
- E21D1/03—Sinking shafts mechanically, e.g. by loading shovels or loading buckets, scraping devices, conveying screws
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Life Sciences & Earth Sciences (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Geology (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
一种应用于竖井掘进机的高自由度六组撑紧液压系统属于隧道掘进机技术领域。本发明包括主液压泵、快速补油泵和动作阀组，主液压泵和快速补油泵的进油口均与油箱连接，主液压泵的出油口与动作阀组的第一进油口通过管路连接，快速补油泵的出油口与动作阀组的第二进油口通过管路连接，动作阀组的动作回油油口与油箱连接，还包括撑紧油缸控制阀组和六组撑紧油缸组，撑紧油缸控制阀组设置油缸伸出高压油口、油缸回收高压油口、撑靴调向高压油口和控制回油油口。本发明能够在平面的六个方向进行撑紧并具备更高的控制灵活度，按照施工需求自由选择撑紧油缸进行动作，为撑紧作业提供更多的选择。
A high-freedom six-group tightening hydraulic system applied to a shaft boring machine belongs to the technical field of tunnel boring machines. The present invention includes a main hydraulic pump, a quick oil replenishment pump and an action valve group. The oil inlets of the main hydraulic pump and the quick oil replenishment pump are both connected to the oil tank, the oil outlet of the main hydraulic pump is connected to the first oil inlet of the action valve group through a pipeline, the oil outlet of the quick oil replenishment pump is connected to the second oil inlet of the action valve group through a pipeline, the action oil return port of the action valve group is connected to the oil tank, and also includes a tightening cylinder control valve group and six groups of tightening cylinder groups. The tightening cylinder control valve group is provided with a high-pressure oil port for extending the cylinder, a high-pressure oil port for recovering the cylinder, a high-pressure oil port for adjusting the tightening shoe to the high-pressure oil port and a control oil return port. The present invention can tighten in six directions on the plane and has a higher control flexibility. The tightening cylinder can be freely selected to act according to construction requirements, providing more options for tightening operations.
Description
Technical Field
The invention belongs to the technical field of tunnel boring machines, and particularly relates to a high-freedom six-group tightening hydraulic system applied to a vertical shaft boring machine.
Background
The vertical shaft heading machine is tunneling equipment specially developed for vertical shaft construction, and provides new tunneling equipment and a construction mode for the construction of projects such as mine excavation, hydraulic engineering, new energy sources and the like due to the characteristics of safety, high efficiency, low cost, easy maintenance, convenient transition and the like.
The existing tightening system of the vertical shaft heading machine only needs to carry out tightening operation in the horizontal direction or the symmetrical direction and simple single-axis direction-adjusting action, and cannot meet the requirements of complicated direction-adjusting of vertical shaft equipment and strict alignment according to the guiding central axis.
Disclosure of Invention
Aiming at the problems, the invention overcomes the defects of the prior art and provides a six-group high-freedom-degree tightening hydraulic system applied to a vertical shaft heading machine; the invention can carry out tightening in six directions of a plane, has higher control flexibility, freely selects the tightening cylinder to act according to construction requirements, and provides more choices for tightening operation.
In order to achieve the above purpose, the present invention adopts the following technical scheme.
The invention provides a six-group tightening hydraulic system with high degree of freedom applied to a shaft heading machine, which comprises a main hydraulic pump, a quick oil supplementing pump and an action valve group, wherein oil inlets of the main hydraulic pump and the quick oil supplementing pump are connected with an oil tank, an oil outlet of the main hydraulic pump is connected with a first oil inlet of the action valve group through a pipeline, an oil outlet of the quick oil supplementing pump is connected with a second oil inlet of the action valve group through a pipeline, an action oil return oil port of the action valve group is connected with the oil tank, the six-group tightening hydraulic system also comprises a tightening oil cylinder control valve group and six-group tightening oil cylinder groups, the tightening oil cylinder control valve group is provided with an oil cylinder extending high-pressure oil port, an oil cylinder recovering high-pressure oil port, a tightening shoe direction-adjusting high-pressure oil port and a control oil return oil port, the oil cylinder extending high-pressure oil port is connected with the first oil outlet of the action valve group through a pipeline, the hydraulic jack is characterized in that the oil cylinder recovery high-pressure oil port is connected with a second oil outlet of the action valve bank through a pipeline, the hydraulic jack is connected with a third oil outlet of the action valve bank through a pipeline, a rodless cavity high-pressure oil way is arranged in the tightening oil cylinder control valve bank at the position, extending out of the high-pressure oil port, of the oil cylinder, a rod cavity high-pressure oil way is arranged at the position, where the oil cylinder recovery high-pressure oil port is arranged, of the oil cylinder, the rodless cavity high-pressure oil way is connected with rodless cavities of all tightening oil cylinder sets through the rodless cavity oil port through pipelines with tightening selection electromagnetic valves, the rod cavity high-pressure oil way is connected with rod cavities of all tightening oil cylinder sets through the pipelines with pressure relief electromagnetic valves through the rod cavity oil port, and pressure maintaining oil ways with grouping electromagnetic valves, pressure maintaining oil ways and pressure maintaining electromagnetic valves, simultaneously with each the hydro-cylinder that has the pole chamber to the solenoid valve that adjusts, simultaneously with each the oil return oil circuit that the pressure release solenoid valve is connected, and prop in the tight hydro-cylinder control valves prop boots and adjust to high pressure oil mouth department and be provided with and adjust to high pressure oil circuit, adjust to high pressure oil circuit with the hydro-cylinder is adjusted to the oil circuit and is passed through the pipe connection, the pressurize oil circuit end is connected with the one end of control overflow valve and control check valve respectively, the control overflow valve with the other end of control check valve simultaneously with the oil return oil circuit is connected, the oil return oil circuit end with control oil return hydraulic fluid port is connected, control oil return hydraulic fluid port again with the oil tank is connected.
Further, rod cavity pressure sensors are respectively arranged on oil paths connected with the rod cavities, and rodless cavity pressure sensors are respectively arranged on oil paths connected with the rodless cavities.
Further, the tightening selection electromagnetic valve, the grouping electromagnetic valve and the direction-adjusting electromagnetic valve are all electromagnetic ball valves.
Further, the tightening selection solenoid valve, the grouping solenoid valve and the direction-adjusting solenoid valve are replaced with servo valves.
Further, the pressure relief electromagnetic valve is an electromagnetic reversing valve.
Further, the control relief valve is replaced with a proportional relief valve.
Further, a throttle valve is arranged on a pipeline between the direction-adjusting high-pressure oil way and the oil cylinder direction-adjusting oil way.
Further, the direction-adjusting high-pressure oil circuit is connected with a pressure measuring joint.
Further, the first oil inlet is connected with the inlet of the oil supplementing switching valve and the inlet of the first safety overflow valve through pipelines respectively, the outlet of the oil supplementing switching valve is connected with the inlet of the first one-way valve and the inlet of the second one-way valve through pipelines respectively, the second oil inlet is connected with the inlet of the second safety overflow valve and the inlet of the third one-way valve through pipelines respectively, the outlet of the first safety overflow valve is connected with the inlet of the second hydraulic lock through pipelines simultaneously, the outlet of the first one-way valve is connected with the inlet of the third oil outlet and the outlet of the extending action valve through pipelines respectively, the outlet of the second one-way valve is connected with the inlet of the oil supplementing action valve through pipelines simultaneously, the other inlet of the extending action valve and the outlet of the oil supplementing action valve are connected with the inlet of the first hydraulic lock through pipelines simultaneously, one outlet of the oil supplementing action valve is connected with the inlet of the second hydraulic lock through pipelines simultaneously, and the outlet of the second lock is connected with the other inlet of the second hydraulic lock through pipelines simultaneously.
Furthermore, the oil supplementing switching valve, the extending action valve and the oil supplementing action valve are all electromagnetic directional valves.
The beneficial effects of the invention are as follows:
According to the invention, the tightening oil cylinder can be freely selected to act according to construction requirements, and meanwhile, the free selection oil cylinder and a pressure maintaining oil way capable of being independently tightened are provided, after tightening, the tightening pressure can be independently regulated and is independent from a system, so that other tightening oil cylinders can be freely operated, and tightening is performed by other tightening pressures; meanwhile, by means of the system, a group of cylinders can be selected to be adjusted in direction by high-pressure tightening, other cylinders are tightened by low pressure after the cylinders are connected into a pressure maintaining oil way to maintain pressure, influence on a single group of tightening cylinders which are already adjusted in the tightening process of the other cylinders is reduced, higher control flexibility is achieved, and more choices can be provided for tightening operation.
Drawings
In order to make the technical problems, technical schemes and beneficial effects solved by the invention more clear, the invention is further described in detail below with reference to the accompanying drawings and the detailed description. It should be understood that the detailed description is presented by way of example only and is not intended to limit the invention.
Fig. 1 is a schematic view of the overall structure of the present invention.
Fig. 2 is a schematic structural diagram of a first set of tightening cylinder sets and their corresponding control valve sets according to the present invention.
Fig. 3 is a schematic diagram of the structure of the valve block of the present invention.
The marks in the figure: the hydraulic oil pump is characterized by comprising a first oil tank 1, a main hydraulic pump 2, a quick oil supplementing pump 3, an action valve group 4, a first oil inlet 5, a second oil inlet 6, an action oil return port 7, a supporting oil cylinder control valve group 8, a supporting oil cylinder group 9, an oil cylinder extension high-pressure oil port 10, an oil cylinder recovery high-pressure oil port 11, a supporting shoe high-pressure oil port 12, a control oil return port 13, a first oil outlet 14, a second oil outlet 15, a third oil outlet 16, a no-rod cavity high-pressure oil path 17, a rod cavity high-pressure oil path 18, a supporting selection electromagnetic valve 19, a no-rod cavity oil port 20, a no-rod cavity 21, a pressure relief electromagnetic valve 22, a rod cavity oil port 23, a rod cavity 24, a grouping electromagnetic valve 25, a pressure maintaining oil path 26, a direction adjusting electromagnetic valve 27, an oil cylinder direction adjusting oil path 28, an oil return oil path 29, a direction adjusting high-pressure oil path 30, a control check valve 31, a control check valve 32, a rod cavity pressure sensor 33, a no-rod cavity pressure sensor 35, a no-rod cavity throttle valve 35, a 36, a relief valve 36, a first relief valve 37, a relief valve 40, a second relief valve 45, a second relief valve 46, a relief valve 45, a second relief valve 44, a relief valve 45, a third relief valve and a relief valve 44.
Detailed Description
Referring to fig. 1-3, the embodiment provides a six-group high-freedom tightening hydraulic system applied to a shaft heading machine, which comprises a main hydraulic pump 2, a quick oil supplementing pump 3 and an action valve group 4.
The oil inlets of the main hydraulic pump 2 and the quick oil supplementing pump 3 are connected with the oil tank 1, the oil outlet of the main hydraulic pump 2 is connected with the first oil inlet 5 of the action valve group 4 through a pipeline, the oil outlet of the quick oil supplementing pump 3 is connected with the second oil inlet 6 of the action valve group 4 through a pipeline, and the action oil return port 7 of the action valve group 4 is connected with the oil tank 1.
As shown in fig. 3, the first oil inlet 5 in the actuation valve group 4 is connected to the inlets of the oil-compensating switch valve 37 and the first relief valve 38 through pipelines, the outlet of the oil-compensating switch valve 37 is connected to the inlets of the first check valve 39 and the second check valve 40 through pipelines, the second oil inlet 6 is connected to the inlets of the second relief valve 41 and the third check valve 42 through pipelines, the outlets of the first relief valve 38 and the second relief valve 41 are simultaneously connected to the actuation oil return port 7 through pipelines, the outlet of the first check valve 39 is connected to the inlets of the third oil outlet 16 and the extension actuation valve 43 through pipelines, the outlets of the second check valve 40 and the third check valve 42 are simultaneously connected to the inlet of the oil-compensating actuation valve 44 through pipelines, the other inlet of the extension actuation valve 43 and the oil-compensating actuation valve 44 is simultaneously connected to the actuation oil return port 7 through pipelines, the outlet of the extension actuation valve 43 is connected to the inlet of the first hydraulic lock 45, the one outlet of the oil-compensating actuation valve 44 is connected to the inlet of the second hydraulic lock 46, the first lock 45 is simultaneously connected to the other inlet of the second hydraulic lock 46 through pipelines, and the other outlet of the second lock 46 is simultaneously connected to the other inlet of the second hydraulic lock 14 through the second hydraulic lock 46.
Wherein the oil supplementing switching valve 37, the extending action valve 43 and the oil supplementing action valve 44 are all electromagnetic directional valves.
The hydraulic control system further comprises a tightening oil cylinder control valve group 8 and six tightening oil cylinder groups 9 (a first group to a sixth group are sequentially arranged from left to right as shown in fig. 1, the positions of the tightening oil cylinder groups 9 in each group are conventional in the art), and the tightening oil cylinder control valve group 8 is provided with an oil cylinder extending high-pressure oil port 10, an oil cylinder recycling high-pressure oil port 11, a tightening shoe direction-adjusting high-pressure oil port 12 and a control oil return oil port 13.
As shown in fig. 1 and 2, the oil cylinder extends out of the high-pressure oil port 10 and is connected with the first oil outlet 14 of the action valve group 4 through a pipeline, the oil cylinder recycling high-pressure oil port 11 is connected with the second oil outlet 15 of the action valve group 4 through a pipeline, and the supporting shoe is used for adjusting the direction of the high-pressure oil port 12 and is connected with the third oil outlet 16 of the action valve group 4 through a pipeline.
The hydraulic cylinder control valve group 8 is internally provided with a rodless cavity high-pressure oil way 17 at the position where the oil cylinder extends out of the high-pressure oil port 10, the oil cylinder recycling high-pressure oil port 11 is provided with a rod cavity high-pressure oil way 18, the rodless cavity high-pressure oil way 17 is respectively connected with rodless cavities 21 of the supporting oil cylinder groups 9 through a rodless cavity oil port 20 through pipelines with supporting selection electromagnetic valves 19, and the rod cavity high-pressure oil way 18 is respectively connected with rod cavities 24 of the supporting oil cylinder groups 9 through rod cavity oil ports 23 through pipelines with pressure relief electromagnetic valves 22.
The tightening cylinder control valve group 8 is also internally provided with a pressure maintaining oil path 26 with a grouping electromagnetic valve 25 connected with each rodless cavity 21, a cylinder direction adjusting oil path 28 with a direction adjusting electromagnetic valve 27 connected with each rod cavity 24, and an oil return oil path 29 connected with each pressure relief electromagnetic valve 22.
The direction-adjusting high-pressure oil way 30 is arranged at the position of the direction-adjusting high-pressure oil port 12 of the supporting shoe in the supporting oil cylinder control valve group 8, the direction-adjusting high-pressure oil way 30 is connected with the oil cylinder direction-adjusting oil way 28 through a pipeline, and a throttle valve 35 is arranged on the pipeline between the direction-adjusting high-pressure oil way 30 and the oil cylinder direction-adjusting oil way 28.
The direction-adjusting high-pressure oil way 30 is also connected with a pressure measuring joint 36 for debugging and equipment fault detection, and the pressure measuring joint 36 can not be connected at ordinary times.
The tail end of the pressure maintaining oil way 26 is respectively connected with one ends of a control overflow valve 31 and a control one-way valve 32, the other ends of the control overflow valve 31 and the control one-way valve 32 are simultaneously connected with an oil return oil way 29, the tail end of the oil return oil way 29 is connected with a control oil return oil port 13, and the control oil return oil port 13 is connected with the oil tank 1.
The pressure relief solenoid valve 22 is an electromagnetic reversing valve. The tightening selection electromagnetic valve 19, the grouping electromagnetic valve 25 and the direction-regulating electromagnetic valve 27 are all electromagnetic ball valves, or the pressure relief electromagnetic valve 22 can be replaced by a servo valve better, the servo valve can accurately control the speed and the stroke of the tightening oil cylinder, and at the moment, the automatic centering operation of the whole tightening system can be realized according to the calculation result of the guiding system, so that the automatic operation of equipment is realized.
The control overflow valve 31 can be replaced by a proportional overflow valve, if the proportional overflow valve is used, the function of slowly releasing pressure can be provided for the tightening system, the impact in the pressure release process of the tightening system is reduced, and the disturbance to the rock stratum is lightened.
In addition, each oil path connected with the rod cavity 24 is respectively provided with a rod cavity pressure sensor 33 for respectively detecting the pressure of the rod cavity 24 of each group of tightening cylinders.
And each oil way connected with the rodless cavity 21 is respectively provided with a rodless cavity pressure sensor 34 for respectively detecting the pressure of the rodless cavity 21 of each group of tightening oil cylinders.
The working mode of the system is as follows:
1. Fast mode extension: the main hydraulic pump 2 and the quick oil supplementing pump 3 are used for supplying oil simultaneously, the main hydraulic pump 2 is set to be in a low-pressure mode, the left position of the oil supplementing switching valve 37 is powered on, the main hydraulic pump 2 and the quick oil supplementing pump 3 are combined, the right position of the oil supplementing action valve 44 is powered on, oil enters an oil cylinder of the tightening oil cylinder control valve group 8 through a high-pressure oil pipe and stretches out of the high-pressure oil port 10 through the oil supplementing action valve 44 and the second hydraulic lock 46 to the first oil outlet 14; the oil which extends out of the high-pressure oil port 10 through the oil cylinder enters the rodless cavity 21 of the tightening oil cylinder through each tightening selection electromagnetic valve 19 and the rodless cavity oil port 20.
The independent action of the corresponding groups of tightening cylinders can be selected through the switch of each tightening selection electromagnetic valve 19 according to the requirement; the oil with the rod cavity 24 returns to the tightening oil cylinder control valve group 8 through the oil port 23 of each rod cavity and flows to each pressure relief electromagnetic valve 22, and the switch of each pressure relief electromagnetic valve 22 can select the independent action of the corresponding tightening oil cylinder. The oil flows to the left position of the pressure relief electromagnetic valve 22 to obtain electricity, the oil returns to the oil cylinder through the pressure relief electromagnetic valve 22 to recycle the high-pressure oil port 11, returns to the second oil outlet 15 of the action valve group 4 through the high-pressure oil pipe, returns to the action oil return port 7 through the oil supplementing action valve 44, and finally returns to the oil tank 1 to complete the rapid extending action.
2. Fast mode recovery: the main hydraulic pump 2 and the quick oil supplementing pump 3 are supplied with oil simultaneously, the main hydraulic pump 2 is set to be in a low-pressure mode, the left position of the oil supplementing switching valve 37 is powered on, the main hydraulic pump 2 and the quick oil supplementing pump 3 are combined, the left position of the oil supplementing action valve 44 is powered on, oil flows to the second hydraulic lock 46 and the second oil outlet 15 respectively through the oil supplementing action valve 44, the second hydraulic lock 46 is opened, oil flows to the oil cylinder recovery high-pressure oil port 11 of the tightening oil cylinder control valve group 8 from the second oil outlet 15 through a high-pressure oil pipe simultaneously, and then flows to the pressure relief electromagnetic valves 22. The switch of each pressure relief solenoid valve 22 can select the independent action of each group of tightening cylinders.
The left position of each pressure relief electromagnetic valve 22 is electrified, oil enters a rod cavity 24 of the tightening oil cylinder through each rod cavity oil port 23, oil in the rodless cavity 21 returns to each tightening selection electromagnetic valve 19 through each rodless cavity oil port 20, returns to the oil cylinder through the tightening selection electromagnetic valve 19 to extend out of the high-pressure oil port 10, returns to the first oil outlet 14 of the action valve group 4, returns to the action oil return port 7 through the second hydraulic lock 46 and the oil supplementing action valve 44, and returns to the oil tank 1.
3. High-pressure bracing mode:
The main hydraulic pump 2 is supplied with oil, and is set in a high-pressure mode, the oil supply switching valve 37 is electrified to the right, and the high-pressure oil passes through the oil supply switching valve 37 and the first one-way valve 39 to reach the extending action valve 43. The left position of the extending action valve 43 is electrified, high-pressure oil reaches the first oil outlet 14 from the extending action valve 43 through the first hydraulic lock 45, the oil cylinder entering the tightening oil cylinder control valve group 8 through the high-pressure oil pipe extends out of the high-pressure oil port 10, and the oil liquid extending out of the high-pressure oil port 10 through the oil cylinder enters the rodless cavity 21 of the tightening oil cylinder through each tightening selection electromagnetic valve 19 and the rodless cavity oil port 20, so that the high-pressure tightening action is completed. The switch of each tightening selection solenoid valve 19 can select the individual high-pressure tightening action of each set of tightening cylinders.
4. Steering mode:
the axial direction-adjusting mode is carried out on the coaxial line tightening oil cylinder which is already tightened.
Taking the first and sixth sets of tightening cylinders 9 as an example (the first and sixth sets are on the same axis, which is a conventional design). The main hydraulic pump 2 is supplied with oil, is set to be in a direction-regulating mode, the right position of the oil-supplementing switching valve 37 is electrified, high-pressure oil reaches the third oil outlet 16 through the oil-supplementing switching valve 37 and the first one-way valve 39, then enters the supporting shoe of the supporting oil cylinder control valve group 8 through the high-pressure oil pipe to regulate the direction of the high-pressure oil port 12, and reaches the direction-regulating electromagnetic valves 27 of the first group and the sixth group through the throttle valve 35. The first group of direction-adjusting electromagnetic valves 27 are powered, oil enters the rod cavities 24 of the first group of tightening oil cylinder groups 9 through the first group of direction-adjusting electromagnetic valves 27 and the rod cavity oil ports 23, the oil cylinders are recovered, the first group of grouping electromagnetic valves 25 and the sixth group of grouping electromagnetic valves 25 are powered, oil in the rodless cavities 21 of the first group of tightening oil cylinder groups 9 flows out from the rodless cavities 20 of the first group, the first group of grouping electromagnetic valves 25, the sixth group of grouping electromagnetic valves 25 and the sixth group of rodless cavities 20 into the rodless cavities 21 of the sixth group of tightening oil cylinder groups 9, the tightening oil cylinders of the sixth group extend, the oil in the rod cavities 24 returns to the tightening oil cylinder control valve group 8 through the rod cavity oil ports 23 of the sixth group, the oil flows to the pressure relief electromagnetic valves 22 of the sixth group and the right of the pressure relief electromagnetic valves 22 are powered, the oil flows out from the pressure relief electromagnetic valves 22 of the sixth group, returns to the oil tank 1 through the control oil return oil ports 13, and the coaxial oil cylinder direction-adjusting action is completed.
It will be appreciated that the above detailed description of the invention is provided for illustration of the invention and not for limitation of the technical solutions described in the embodiments of the invention, and that the person skilled in the art should understand that the invention may be modified or substituted for the same technical effects; as long as the use requirement is met, the invention is within the protection scope of the invention.
Claims (10)
1. The utility model provides a six tight hydraulic system of support of high degree of freedom who is applied to shaft development machine, includes main hydraulic pump (2), quick oil compensating pump (3) and action valves (4), main hydraulic pump (2) with the oil inlet of quick oil compensating pump (3) all is connected with oil tank (1), the oil-out of main hydraulic pump (2) with first oil inlet (5) of action valves (4) pass through the pipeline connection, the oil-out of quick oil compensating pump (3) with second oil inlet (6) of action valves (4) pass through the pipeline connection, action oil return port (7) of action valves (4) with oil tank (1) are connected, characterized in that still includes support hydro-cylinder control valves (8) and six tight hydro-cylinder groups (9), support hydro-cylinder control valves (8) set up hydro-cylinder and stretch out high pressure oil port (10), hydro-cylinder recovery high pressure oil port (11), prop boots pressure regulating to high pressure oil port (12) and control oil return port (13), hydro-cylinder stretch out high pressure oil port (10) and action valves (4) first oil outlet (14) pass through the pipeline connection with oil-out of action valves (4) pass through oil-out of recovery valves (11), the supporting shoe direction-regulating high-pressure oil port (12) is connected with a third oil outlet (16) of the action valve bank (4) through a pipeline, a rodless cavity high-pressure oil path (17) is arranged in the supporting oil cylinder control valve bank (8) at the position where the oil cylinder extends out of the high-pressure oil port (10), a rod cavity high-pressure oil path (18) is arranged at the position where the oil cylinder recovers the high-pressure oil port (11), the rodless cavity high-pressure oil path (17) is respectively connected with rodless cavities (21) of the supporting oil cylinder banks (9) through pipelines with supporting selection electromagnetic valves (19) through rodless cavity oil ports (20), the rod cavity high-pressure oil path (18) is respectively connected with rod cavities (24) of the supporting oil cylinder banks (9) through pipelines with pressure relief electromagnetic valves (22) through rod cavity oil ports (23), a pressure maintaining oil path (26) with grouping electromagnetic valves (25) which are simultaneously connected with the rodless cavities (21) are also arranged in the supporting oil cylinder control valve bank (8), an oil return path (27) which is simultaneously connected with the supporting oil cylinder control valve bank (28) to the high-pressure oil path (30) at the positions of the supporting shoe high-pressure oil port (28), the hydraulic oil cylinder is characterized in that the direction-adjusting high-pressure oil way (30) is connected with the oil cylinder direction-adjusting oil way (28) through a pipeline, the tail end of the pressure-maintaining oil way (26) is connected with one ends of the control overflow valve (31) and the control one-way valve (32) respectively, the other ends of the control overflow valve (31) and the control one-way valve (32) are simultaneously connected with the oil return oil way (29), the tail end of the oil return oil way (29) is connected with the control oil return oil port (13), and the control oil return oil port (13) is connected with the oil tank (1) again.
2. The six-degree-of-freedom tightening hydraulic system applied to the shaft heading machine according to claim 1, wherein a rod cavity pressure sensor (33) is respectively arranged on each oil path connected with the rod cavity (24), and a rodless cavity pressure sensor (34) is respectively arranged on each oil path connected with the rodless cavity (21).
3. The six-degree-of-freedom tightening hydraulic system applied to a shaft boring machine according to claim 1, wherein the tightening selection solenoid valve (19), the grouping solenoid valve (25) and the direction-adjusting solenoid valve (27) are all solenoid valves.
4. A six-degree-of-freedom tightening hydraulic system for a shaft boring machine according to claim 1, characterized in that the tightening selection solenoid valve (19), the grouping solenoid valve (25) and the steering solenoid valve (27) are replaced with servo valves.
5. The six-degree-of-freedom tightening hydraulic system applied to a shaft boring machine according to claim 1, wherein the pressure relief electromagnetic valve (22) is an electromagnetic directional valve.
6. A six-degree-of-freedom tightening hydraulic system for a shaft boring machine according to claim 1, characterized in that the control relief valve (31) is replaced by a proportional relief valve.
7. The six-degree-of-freedom tightening hydraulic system applied to the shaft heading machine according to claim 1, wherein a throttle valve (35) is arranged on a pipeline between the direction-adjusting high-pressure oil pipeline (30) and the oil cylinder direction-adjusting oil pipeline (28).
8. The six-degree-of-freedom tightening hydraulic system applied to the shaft heading machine according to claim 1, wherein a pressure measuring connector (36) is connected to the direction-adjusting high-pressure oil path (30).
9. The six-group high-freedom-degree tightening hydraulic system for a shaft boring machine according to claim 1, wherein the first oil inlet (5) of the action valve group (4) is connected with the inlets of the oil supplementing switching valve (37) and the first safety relief valve (38) through pipelines respectively, the outlet of the oil supplementing switching valve (37) is connected with the inlets of the first one-way valve (39) and the second one-way valve (40) through pipelines respectively, the second oil inlet (6) is connected with the inlets of the second safety relief valve (41) and the third one-way valve (42) through pipelines respectively, the outlet of the first safety relief valve (38) and the outlet of the second safety relief valve (41) are simultaneously connected with the action oil return port (7) through pipelines respectively, the outlet of the first one-way valve (39) is connected with the inlets of the third oil outlet (16) and the extension action valve (43) through pipelines respectively, the outlet of the second one-way valve (40) and the outlet of the third one-way valve (42) are simultaneously connected with the inlet of the oil supplementing valve (44) through pipelines respectively, the outlet of the second one-way valve (43) is simultaneously connected with the outlet of the hydraulic oil supplementing valve (43) through the other action valve (43) and the extension port (43), one outlet of the oil supplementing action valve (44) is connected with an inlet of a second hydraulic lock (46), the first hydraulic lock (45) and the outlet of the second hydraulic lock (46) are simultaneously connected with the first oil outlet (14) through a pipeline, and the other outlet of the oil supplementing action valve (44) and the other inlet of the second hydraulic lock (46) are simultaneously connected with the second oil outlet (15) through a pipeline.
10. The six-degree-of-freedom tightening hydraulic system applied to a shaft boring machine according to claim 9, wherein the oil compensating switching valve (37), the extending action valve (43) and the oil compensating action valve (44) are all electromagnetic directional valves.
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| JP2005195081A (en) * | 2004-01-06 | 2005-07-21 | Daikin Ind Ltd | hydraulic unit |
| CN107060797A (en) * | 2017-04-10 | 2017-08-18 | 浙江大学 | Hard rock mole horizontal attitude adjusts hydraulic system |
| CN111828406A (en) * | 2020-06-19 | 2020-10-27 | 浙江大学 | An efficient and energy-saving TBM horizontal attitude adjustment hydraulic system |
| CN116181722A (en) * | 2022-11-26 | 2023-05-30 | 江苏神盾工程机械有限公司 | TBM tunneling machine support shoe quick-acting hydraulic system and control method |
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- 2024-10-18 CN CN202411455123.4A patent/CN118998136B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005195081A (en) * | 2004-01-06 | 2005-07-21 | Daikin Ind Ltd | hydraulic unit |
| CN107060797A (en) * | 2017-04-10 | 2017-08-18 | 浙江大学 | Hard rock mole horizontal attitude adjusts hydraulic system |
| CN111828406A (en) * | 2020-06-19 | 2020-10-27 | 浙江大学 | An efficient and energy-saving TBM horizontal attitude adjustment hydraulic system |
| CN116181722A (en) * | 2022-11-26 | 2023-05-30 | 江苏神盾工程机械有限公司 | TBM tunneling machine support shoe quick-acting hydraulic system and control method |
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