CN117967625A - Positive flow hydraulic system of rotary drilling rig and rotary drilling rig - Google Patents
Positive flow hydraulic system of rotary drilling rig and rotary drilling rig Download PDFInfo
- Publication number
- CN117967625A CN117967625A CN202410315928.2A CN202410315928A CN117967625A CN 117967625 A CN117967625 A CN 117967625A CN 202410315928 A CN202410315928 A CN 202410315928A CN 117967625 A CN117967625 A CN 117967625A
- Authority
- CN
- China
- Prior art keywords
- control valve
- oil
- power head
- flow
- pilot
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000005553 drilling Methods 0.000 title claims abstract description 37
- 239000003921 oil Substances 0.000 claims abstract description 289
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 23
- 230000007423 decrease Effects 0.000 claims abstract description 4
- 238000006073 displacement reaction Methods 0.000 claims 3
- 238000004804 winding Methods 0.000 description 10
- 230000009471 action Effects 0.000 description 7
- 150000001875 compounds Chemical class 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The positive flow hydraulic system of the rotary drilling rig comprises a main winch control valve and a power head control valve, wherein an oil inlet of the main winch control valve is connected to a hydraulic pump, an oil outlet of the main winch control valve is connected to a main winch motor, one oil inlet of the power head control valve is connected to the hydraulic pump through a power head oil path, and an oil outlet of the power head control valve is connected to the power head motor; the power head oil circuit is provided with a flow control valve, and the flow control valve is used for controlling the flow of hydraulic oil flowing into the power head control valve so that the flow of the hydraulic oil flowing through the main winch control valve is increased along with the decrease of the flow of the hydraulic oil flowing through the flow control valve. The invention also relates to a rotary drilling rig.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to a positive flow hydraulic system of a rotary drilling rig and the rotary drilling rig.
Background
The rotary drilling rig is a main device for pile foundation engineering construction. The rotary drilling rig mainly comprises a power head, a drill rod, a drilling tool, a winch, a hydraulic system, a travelling mechanism, an electrical system, an operating room and the like. The power head of the rotary drilling rig is used for driving the drill rod to rotate and move up and down, and the main winch is used for driving the winding drum to wind the rope to finish traction work. The power head and the main winch are mostly powered by a hydraulic system and execute hydraulic operation, and the hydraulic system is mainly used for realizing the compound action of the main winch and the power head.
From the hydraulic control variable mode of the pump, the hydraulic system can be divided into a positive flow system and a negative flow system. The positive flow system is characterized in that the main pump is in direct proportion to the pressure output by the pilot operation handle, so that the real-time control of the variable pump is realized; the negative flow system means that the output oil of the hydraulic pump passes through the control component of the handle, one part goes to the oil cylinder and the motor, and the other part passes through the middle oil return tank of the valve. Positive flow systems have the advantages of short variable response time, small flow fluctuations, small energy loss, etc., but the system stability is worse than negative flow systems.
When the main winch and the power head of the rotary drilling rig perform compound action, the main winch is always in a higher load state, so that the hydraulic system needs to provide more hydraulic oil for the main winch to match the hydraulic oil quantity required by the main winch. Fig. 1 is a schematic diagram of a conventional positive flow hydraulic system of a rotary drilling rig, as shown in fig. 1, where the positive flow hydraulic system of the rotary drilling rig includes a main winch control valve 1 and a power head control valve 2, the main winch control valve 1 is used for controlling the motion of a main winch motor, and the power head control valve 2 is used for controlling the motion of a power head motor. The throttle valve 3 is arranged on an oil path at one end of an oil inlet of the power head control valve 2, and the throttle valve 3 is provided with an orifice with a fixed diameter and can allow hydraulic oil to pass quantitatively. When the power head and the main winch perform compound action, the throttle valve 3 arranged in front of the power head control valve 2 can prevent part of hydraulic oil from flowing to the power head oil way with relatively low load under a specific stroke, so that more hydraulic oil flows to the main winch oil way, flow matching is realized only under specific flow, when the flow changes, the flow matching is unbalanced, the situations of power head motor rotation failure, main winch motor overspeed or power head motor overspeed, main winch lifting weakness and the like occur, and the flow matching of compound action cannot be realized in the whole course as required. Meanwhile, when the power head singly acts, the throttle valve 3 can cause liquid resistance on the power head oil path, so that energy is greatly wasted.
Disclosure of Invention
The invention aims to provide a positive flow hydraulic system of a rotary drilling rig and the rotary drilling rig, which can be used for solving the technical problems.
The invention provides a positive flow hydraulic system of a rotary drilling rig, which comprises a main winch control valve and a power head control valve, wherein an oil inlet of the main winch control valve is connected to a hydraulic pump, an oil outlet of the main winch control valve is connected to a main winch motor, one oil inlet of the power head control valve is connected to the hydraulic pump through a power head oil path, and an oil outlet of the power head control valve is connected to the power head motor; the power head oil circuit is provided with a flow control valve, and the flow control valve is used for controlling the flow of hydraulic oil flowing into the power head control valve so that the flow of the hydraulic oil flowing through the main winch control valve is increased along with the decrease of the flow of the hydraulic oil flowing through the flow control valve.
Further, the flow control valve controls the change of the throttle aperture according to the control signal.
Further, the main winch control valve is provided with a first oil inlet A, an oil return opening T, a first working oil port A1 and a second working oil port A2; the first oil inlet A of the main winch control valve is connected to the hydraulic pump through a first main winch oil way; an oil return port T of the main winch control valve is connected with an oil return tank; the first working oil port A1 of the main winch control valve is connected to one oil inlet of the main winch motor through a first main winch working oil path, and the second working oil port A2 of the main winch control valve is connected to the other oil inlet of the main winch motor through a second main winch working oil path. The power head control valve is provided with a first oil inlet A, an oil return port T, a first working oil port A1 and a second working oil port A2; the first oil inlet A of the power head control valve is connected to the hydraulic pump through a power head oil circuit; an oil return port T of the power head control valve is connected with an oil return tank; the first working oil port A1 of the power head control valve is connected to one oil inlet of the power head motor through a first power head working oil path, and the second working oil port A2 of the power head control valve is connected to the other oil inlet of the power head motor through a second power head working oil path.
Further, the second oil inlet B and the third working oil inlet A3 of the main winch control valve and the power head control valve are respectively provided, the second oil inlet B of the main winch control valve is connected to the hydraulic pump through a second main winch oil path, and the third working oil inlet A3 of the main winch control valve is connected to the second oil inlet B of the power head control valve through a first connecting oil path.
Further, the main winch control valve and the power head control valve are three-position six-way valves;
When the main winch control valve is located at a normal position, a first working oil port A1 and a second working oil port A2 of the main winch control valve are communicated with an oil return port T of the main winch control valve, and a second oil inlet port B of the main winch control valve is communicated with a third working oil port A3.
When the power head control valve is in a normal state, the second oil inlet B of the power head control valve is communicated with the third working oil inlet A3.
Further, the main winch control valve, the power head control valve and the flow control valve are all hydraulic control valves, two hydraulic control ends of the main winch control valve are respectively connected to a pilot pump through a first pilot oil path and a second pilot oil path, and two hydraulic control ends of the power head control valve are respectively connected to the pilot pump through a third pilot oil path and a fourth pilot oil path; the pilot control end of the flow control valve is connected to the first pilot oil passage and the second pilot oil passage through a fifth pilot oil passage, respectively.
Further, a shuttle valve is arranged on the fifth pilot oil path, two oil inlets of the shuttle valve are respectively connected to the first pilot oil path and the second pilot oil path, and an oil outlet of the shuttle valve is connected to a hydraulic control end of the flow control valve.
Further, a first one-way valve is further arranged on the power head oil path and is connected between the flow control valve and the power head control valve; the power head oil way is further connected to the first connecting oil way through a second connecting oil way, a second one-way valve is arranged on the second connecting oil way, and a third one-way valve is arranged on the first main hoisting oil way.
Further, a first overflow oil supplementing valve is arranged on the first main winch working oil path, and a second overflow oil supplementing valve is arranged on the second main winch working oil path.
The invention also provides a rotary drilling rig, which is provided with the positive flow hydraulic system.
The positive flow hydraulic system of the rotary drilling rig provided by the invention has the following beneficial effects:
1. The compound action flow distribution of the main winch and the power head in the rotary drilling rig of the positive flow hydraulic system is realized as required.
2. The problem of when the unit head acts alone, the positive flow system priority valve is to the energy waste of branch road (unit head oil circuit) place is solved.
3. The system is simple, the maintenance is convenient, and the cost is low.
The foregoing description is only an overview of the technical solution of the present invention, and may be implemented according to the content of the specification, so that the positive flow hydraulic system of the rotary drilling machine and other objects, features and advantages of the rotary drilling machine of the present invention may be more clearly understood, and the following specific preferred embodiments are described in detail with reference to the accompanying drawings.
Drawings
Fig. 1 is a schematic diagram of a positive flow hydraulic system of a conventional rotary drilling rig.
Fig. 2 is a schematic diagram of a positive flow hydraulic system of a rotary drilling rig according to a preferred embodiment of the present invention.
Detailed Description
In order to further describe the technical means and effects adopted by the invention to achieve the preset aim, the following detailed description is given of the positive flow hydraulic system of the rotary drilling rig and the specific implementation, structure, characteristics and effects of the rotary drilling rig according to the invention by combining the accompanying drawings and the preferred embodiment:
The foregoing and other features, aspects, and advantages of the present invention will become more apparent from the following detailed description of the preferred embodiments, which proceeds with reference to the accompanying drawings. While the invention may be susceptible to further details of embodiment and specific details of construction and operation for achieving the desired purpose, there is shown in the drawings a form a further embodiment which may be used herein with the understanding that the present invention is limited to the specific embodiments and the drawings are incorporated in their entirety.
Fig. 2 is a schematic view of a positive flow hydraulic system of a rotary drilling rig according to a preferred embodiment of the present invention, referring to fig. 2, the positive flow hydraulic system of the rotary drilling rig includes a main hoist control valve 10 and a power head control valve 20, an oil inlet of the main hoist control valve 10 is connected to a hydraulic pump, an oil outlet of the main hoist control valve 10 is connected to a main hoist motor, one oil inlet of the power head control valve 20 is connected to the hydraulic pump through a power head oil path 21, and an oil outlet of the power head control valve 20 is connected to the power head motor; the power head oil passage 21 is provided with a flow control valve 31, and the flow control valve 31 is configured to control the flow rate of the hydraulic oil flowing into the power head control valve 20 so that the flow rate of the hydraulic oil flowing through the main hoisting control valve 10 increases as the flow rate of the hydraulic oil flowing through the flow control valve 31 decreases.
The positive flow hydraulic system of the rotary drilling rig controls the flow of the hydraulic oil flowing into the power head control valve 20 by arranging the flow control valve 31, when the flow of the hydraulic oil flowing through the flow control valve 31 is reduced, the flow of the hydraulic oil flowing to the main winch control valve 10 is correspondingly increased, thereby achieving the effect of improving the main winch speed, and realizing the on-demand matching of the flow during the combined action of the main winch and the power head.
The flow control valve 31 has an orifice with an adjustable aperture, and the flow control valve 31 controls the change of the orifice aperture thereof according to a control signal. The main hoisting control valve 10, the power head control valve 20 and the flow control valve 31 may be hydraulic control valves, electric control valves, pneumatic control valves, etc., and the flow control valve 31 may also be controlled by an operation handle or a controller to change the throttle aperture of a valve core in the flow control valve 31. The following description is given by way of example only, and not limitation.
Specifically, the main hoist control valve 10 has a first oil inlet port a, an oil return port T, a first work oil port A1, and a second work oil port A2; the first oil inlet A of the main hoist control valve 10 is connected to the hydraulic pump through a first main hoist oil passage 11; the oil return port T of the main winch control valve 10 is connected with an oil return tank; the first working oil port A1 of the main hoist control valve 10 is connected to one of the oil inlets of the main hoist motor through a first main hoist working oil path 12, and the second main hoist working oil port A2 of the main hoist control valve 10 is connected to the other oil inlet of the main hoist motor through a second main hoist working oil path 13.
The power head control valve 20 is provided with a first oil inlet A, an oil return port T, a first working oil port A1 and a second working oil port A2; the first oil inlet A of the power head control valve 20 is connected to the hydraulic pump through a power head oil path 21; the oil return port T of the power head control valve 20 is connected with an oil return tank; the first working oil port A1 of the power head control valve 20 is connected to one of the oil inlets of the power head motor through a first power head working oil passage 22, and the second working oil port A2 of the power head control valve 20 is connected to the other oil inlet of the power head motor through a second power head working oil passage 23.
Further, the main hoist control valve 10 and the power head control valve 20 have a second oil inlet B and a third working oil inlet A3, the second oil inlet B of the main hoist control valve 10 is connected to the hydraulic pump through a second main hoist oil passage 14, the third working oil inlet A3 of the main hoist control valve 10 is connected to the second oil inlet B of the power head control valve 20 through a first connecting oil passage 15, and the third working oil inlet A3 of the power head control valve 20 is connected to other components in the positive flow hydraulic system through a third power head working oil passage 4 for providing hydraulic oil to the other components when the main hoist control valve 10 and the power head control valve 20 are not operated.
In this embodiment, the main winding control valve 10 is a three-position eight-way valve, two ports in the main winding control valve 10 are used for communicating with a lubrication oil path, and when the lubrication oil path is not required to pass through the main winding control valve 10, the main winding control valve 10 may also be a three-position six-way valve. The power head control valve 20 is preferably a three-position six-way valve, but not limited to this, and may be a three-position eight-way switching valve with more ports, and other ports may be used without or as other ports.
The main winding control valve 10 has a normal position in the middle and a first operating position and a second operating position at both ends, respectively. When the main winch control valve 10 is in the normal position, the first oil inlet A of the main winch control valve 10 is disconnected, the first working oil inlet A1 and the second working oil inlet A2 of the main winch control valve 10 are both communicated with the oil return opening T of the main winch control valve 10, and the second oil inlet B of the main winch control valve 10 is communicated with the third working oil inlet A3. When the main winch control valve 10 is located at the first working position (left position in the drawing), the first oil inlet a of the main winch control valve 10 is communicated with the second working oil inlet A2, the first working oil inlet A1 is communicated with the oil return port T, and the second oil inlet B is disconnected from the third working oil inlet A3. When the main winch control valve 10 is located at the second working position (right position in the drawing), the first oil inlet a of the main winch control valve 10 is communicated with the first working oil inlet A1, the second working oil inlet A2 is communicated with the oil return port T, and the second oil inlet B is disconnected with the third working oil inlet A3.
Taking main winch lifting as an example, the first pilot oil path 41 has pilot oil, along with the rising of pilot pressure, the valve core of the main winch control valve 10 gradually moves to the right to the first working position, the flow direction of high hydraulic oil of the first main winch oil path 11 is divided into two parts, one part flows to the second main winch working oil path 13 through the main winch valve core 1, the other part returns to the oil tank through the middle position of each valve core, and when the valve cores are fully opened, the oil of the oil return tank branch is cut off.
The power head control valve 20 has a normal position in the middle and a first operating position and a second operating position at both ends, respectively. When the power head control valve 20 is in the normal position, the first oil inlet port a, the oil return port T, the first working oil port A1 and the second working oil port A2 of the power head control valve 20 are disconnected. The second oil inlet B of the power head control valve 20 communicates with the third working oil port A3. When the power head control valve 20 is located at the first working position (left position in the drawing), the first oil inlet a of the power head control valve 20 is communicated with the first working oil inlet A1, the second working oil inlet A2 is communicated with the oil return port T, and the second oil inlet B is disconnected from the third working oil inlet A3. When the power head control valve 20 is located at the second working position (right position in the drawing), the first oil inlet a of the power head control valve 20 is communicated with the second working oil inlet A2, the first working oil inlet A1 is communicated with the oil return port T, and the second oil inlet B is disconnected from the third working oil inlet A3.
When pilot oil (determined according to the direction of rotation of the power head) is present in third pilot oil passage 43 or fourth pilot oil passage 44, the flow direction of hydraulic oil in power head oil passage 21 is divided into two parts as the spool of power head control valve 20 gradually moves with an increase in pilot pressure, one part flows through flow control valve 31 to power head control valve 20 and then to first power head working oil passage 22 or second power head working oil passage 23, and the other part returns to the oil tank through the middle position of each spool, and when the spools are fully opened, the oil in the return oil tank branch is cut off.
In this embodiment, the main hoisting control valve 10, the power head control valve 20, and the flow control valve 31 are all hydraulic control valves, and the control signal for controlling the change in the throttle aperture of the flow control valve 31 is the pilot oil of the pilot oil passage. Specifically, the two pilot ends of the main hoisting control valve 10 are connected to the pilot pump through a first pilot oil passage 41 and a second pilot oil passage 42, respectively, and the two pilot ends of the power head control valve 20 are connected to the pilot pump through a third pilot oil passage 43 and a fourth pilot oil passage 44, respectively; the pilot ends of flow control valve 31 are connected to first pilot oil passage 41 and second pilot oil passage 42, respectively, through fifth pilot oil passage 50. Wherein, pilot valves for controlling the on-off of the pilot oil paths are arranged on the first pilot oil path 41 and the second pilot oil path 42, the main winch control valve 10 and the power head control valve 20 are connected to the pilot valves first, and then the pilot pumps are connected through the pilot valves.
Further, a shuttle valve 51 is provided on the fifth pilot oil path 50, two oil inlets of the shuttle valve 51 are connected to the first pilot oil path 41 and the second pilot oil path 42, respectively, and an oil outlet of the shuttle valve 51 is connected to a pilot end of the flow control valve 31.
Since flow control valve 31 has an orifice with an adjustable aperture, and is controlled by the pilot pressures of first pilot oil passage 41 and second pilot oil passage 42, a pressure selection is made between first pilot oil passage 41 and second pilot oil passage 42 by shuttle valve 51, and the higher pressure is taken to flow control valve 31. When the main winding requires a larger flow, the pressure of the first pilot oil path 41 is increased, and the pressure of the first pilot oil path 41 is larger than that of the second pilot oil path 42, so that the pressure is transmitted to the flow control valve 31 through the shuttle valve 51, the flow control valve 31 is pushed to gradually switch from the non-throttling position (normal position) to the throttling position, at the moment, the flow to the main winding control valve 10 is increased, the flow flowing through the flow control valve 31 is reduced, the effect of increasing the main winding speed is achieved, and the target of matching the flow according to the requirement is achieved.
When the main hoisting alone is operated, the spool of the flow control valve 31 is displaced according to the pilot pressures of the first pilot oil passage 41 and the second pilot oil passage 42, but at this time, the flow rate of the power head oil passage 21 is 0, so that the flow control valve 31 is not operated.
When the power head is operated alone, the pilot pressure of the first pilot oil passage 41 and the second pilot oil passage 42 is 0, so that the flow control valve 31 is in the non-throttling position, the flow rate of the power head oil passage 21 is not throttled, the pressure loss of the power head oil passage 21 is reduced, and the energy-saving effect is achieved.
Further, the power head oil path 21 is further provided with a first check valve (not labeled), and the first check valve is connected between the flow control valve 31 and the power head control valve 20; the power head oil path 21 is further connected to the first connecting oil path 15 through a second connecting oil path 16, a second check valve (not shown) is arranged on the second connecting oil path 16, and a third check valve (not shown) is arranged on the first main winding oil path 11.
The first main winch working oil path 12 is provided with a first overflow oil compensating valve 121, and the second main winch working oil path 13 is provided with a second overflow oil compensating valve 131.
The invention also relates to a rotary drilling rig, which is provided with the positive flow hydraulic system. Other structures of the rotary drilling machine are well known to those skilled in the art and will not be described in detail herein.
The beneficial effects of the invention are as follows:
1. The compound action flow distribution of the main winch and the power head in the rotary drilling rig of the positive flow hydraulic system is realized as required.
2. The problem of when the unit head acts alone, the positive flow system priority valve is to the energy waste of branch road (unit head oil circuit) place is solved.
3. The system is simple, the maintenance is convenient, and the cost is low.
The positive flow hydraulic system of the rotary drilling rig and the rotary drilling rig provided by the invention are described in detail, and specific examples are applied to the principle and the implementation mode of the invention, and the description of the examples is only used for helping to understand the method and the core idea of the invention; meanwhile, as those skilled in the art will have variations in the specific embodiments and application scope in accordance with the ideas of the present invention, the present description should not be construed as limiting the present invention in view of the above.
Claims (10)
1. The positive flow hydraulic system of the rotary drilling rig comprises a main winch control valve (10) and a power head control valve (20), and is characterized in that an oil inlet of the main winch control valve (10) is connected to a hydraulic pump, an oil outlet of the main winch control valve (10) is connected to a main winch motor, one oil inlet of the power head control valve (20) is connected to the hydraulic pump through a power head oil circuit (21), and an oil outlet of the power head control valve (20) is connected to the power head motor; the power head oil way (21) is provided with a flow control valve (31), and the flow control valve (31) is used for controlling the flow of hydraulic oil flowing into the power head control valve (20) so that the flow of the hydraulic oil flowing through the main winch control valve (10) increases along with the decrease of the flow of the hydraulic oil flowing through the flow control valve (31).
2. Positive-flow hydraulic system according to claim 1, characterized in that the flow control valve (31) controls its throttle aperture variation in accordance with a control signal.
3. Positive-flow hydraulic system according to claim 1 or 2, characterized in that the main hoisting control valve (10) has a first oil inlet a, an oil return T, a first working oil port A1 and a second working oil port A2; a first oil inlet A of the main winch control valve (10) is connected to the hydraulic pump through a first main winch oil circuit (11); an oil return port T of the main winch control valve (10) is connected with an oil return tank; the first working oil port A1 of the main winch control valve (10) is connected to one oil inlet of the main winch motor through a first main winch working oil path (12), and the second working oil port A2 of the main winch control valve (10) is connected to the other oil inlet of the main winch motor through a second main winch working oil path (13);
the power head control valve (20) is provided with a first oil inlet A, an oil return port T, a first working oil port A1 and a second working oil port A2; the first oil inlet A of the power head control valve (20) is connected to the hydraulic pump through a power head oil circuit (21); an oil return port T of the power head control valve (20) is connected with an oil return tank; the first working oil port A1 of the power head control valve (20) is connected to one oil inlet of the power head motor through a first power head working oil circuit (22), and the second working oil port A2 of the power head control valve (20) is connected to the other oil inlet of the power head motor through a second power head working oil circuit (23).
4. A positive-displacement hydraulic system as claimed in claim 3, characterized in that the main hoisting control valve (10) and the power head control valve (20) each have a second inlet port B and a third working port A3, the second inlet port B of the main hoisting control valve (10) being connected to the hydraulic pump by a second main hoisting oil circuit (14), the third working port A3 of the main hoisting control valve (10) being connected to the second inlet port B of the power head control valve (20) by a first connecting oil circuit (15).
5. The positive-displacement hydraulic system of claim 4, wherein the main hoist control valve (10) and the power head control valve (20) are both three-position six-way valves;
When the main winch control valve (10) is located at a normal position, a first working oil port A1 and a second working oil port A2 of the main winch control valve (10) are communicated with an oil return port T of the main winch control valve (10), and a second oil inlet port B of the main winch control valve (10) is communicated with a third working oil port A3.
When the power head control valve (20) is located at a normal position, a second oil inlet B of the power head control valve (20) is communicated with a third working oil inlet A3.
6. Positive-flow hydraulic system according to claim 4, characterized in that the main hoisting control valve (10), the power head control valve (20) and the flow control valve (31) are all pilot valves, the two pilot ends of the main hoisting control valve (10) are connected to a pilot pump by a first pilot oil circuit (41) and a second pilot oil circuit (42), respectively, and the two pilot ends of the power head control valve (20) are connected to the pilot pump by a third pilot oil circuit (43) and a fourth pilot oil circuit (44), respectively; the pilot control end of the flow control valve (31) is connected to the first pilot oil passage (41) and the second pilot oil passage (42) through a fifth pilot oil passage (50), respectively.
7. Positive-flow hydraulic system according to claim 5, characterized in that a shuttle valve (51) is provided on the fifth pilot oil passage (50), two oil inlets of the shuttle valve (51) being connected to the first pilot oil passage (41) and the second pilot oil passage (42), respectively, and an oil outlet of the shuttle valve (51) being connected to a pilot end of the flow control valve (31).
8. The positive-displacement hydraulic system according to claim 7, wherein the power head oil passage (21) is further provided with a first check valve connected between the flow control valve (31) and the power head control valve (20); the power head oil circuit (21) is further connected to the first connecting oil circuit (15) through a second connecting oil circuit (16), a second one-way valve is arranged on the second connecting oil circuit (16), and a third one-way valve is arranged on the first main winch oil circuit (11).
9. A positive flow hydraulic system according to claim 3, characterized in that the first main hoisting working oil circuit (12) is provided with a first overflow oil compensating valve (121), and the second main hoisting working oil circuit (13) is provided with a second overflow oil compensating valve (131).
10. Rotary drilling rig, characterized in that it is provided with a positive flow hydraulic system according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410315928.2A CN117967625A (en) | 2024-03-19 | 2024-03-19 | Positive flow hydraulic system of rotary drilling rig and rotary drilling rig |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410315928.2A CN117967625A (en) | 2024-03-19 | 2024-03-19 | Positive flow hydraulic system of rotary drilling rig and rotary drilling rig |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117967625A true CN117967625A (en) | 2024-05-03 |
Family
ID=90851553
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410315928.2A Pending CN117967625A (en) | 2024-03-19 | 2024-03-19 | Positive flow hydraulic system of rotary drilling rig and rotary drilling rig |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117967625A (en) |
-
2024
- 2024-03-19 CN CN202410315928.2A patent/CN117967625A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103671335B (en) | Load-sensitive electric proportional multi-loop valve | |
| CN103016438B (en) | A kind of electrohydraulic proportional control valve group | |
| CN104379945B (en) | The control system of building machinery | |
| CN101709725B (en) | Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique | |
| CN112746996B (en) | Load sensitive system and engineering hoisting machinery | |
| CN103470565A (en) | Rotary cushion valve and rotary system for crane | |
| CN201526546U (en) | Hydraulic control system of underground anti-explosion hoister adopting multi-pump combination technique | |
| CN111255007B (en) | Loader constant-variable hydraulic system based on load signal direct control | |
| WO2016092809A1 (en) | Hydraulic drive system for construction machinery | |
| CN117967625A (en) | Positive flow hydraulic system of rotary drilling rig and rotary drilling rig | |
| CN207406274U (en) | Stake machine equipment hydraulic speed-limiting system | |
| CN111980978B (en) | Torque control hydraulic system based on push-pull speed of power head | |
| CN112460086B (en) | Composite speed regulation hydraulic system and control method thereof, crane and engineering machinery | |
| EP0084835A2 (en) | Power transmission | |
| CN104373399A (en) | Hydraulic system capable of achieving multi-torque output and rotary drilling rig | |
| CN110594222B (en) | Hydraulic valve group of unmanned agricultural machinery | |
| CN107100909B (en) | A kind of intelligent control energy-saving valve | |
| CN111963505A (en) | Hydraulic system combination action control method and device and engineering machinery | |
| CN114109936B (en) | Boom hydraulic transmission system and control method thereof | |
| CN113152575B (en) | Hydraulic bridge circuit based set pilot positive flow control system | |
| CN112555205B (en) | Rotary hydraulic system and engineering machinery | |
| CN220377407U (en) | Hydraulic control unit and rotary hydraulic system | |
| CN110431317A (en) | Oil hydraulic system | |
| CN218235642U (en) | Double-speed control system of quantitative motor | |
| CN110526140B (en) | Tire crane auxiliary system and control method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination |