Hydraulic system based on CFA operating condition, operating method therefor, and rotary drilling rig

Abstract

Disclosed are a hydraulic system based on a CFA operating condition, a control method therefor, and a rotary drilling rig. The hydraulic system comprises an auger stem winch motor (112), a first pilot-operated proportional valve (123), a first flow path (141), a second flow path (142), a rotary head winch motor (113), a second pilot-operated proportional valve (124), a third flow path (143), a fourth flow path (144), and a fifth flow path (145); the first flow path and the second flow path are both connected between the auger stem winch motor and the first pilot-operated proportional valve, the third flow path and the fourth flow path are both connected between the rotary head winch motor and the second pilot-operated proportional valve, the fifth flow path is connected between the first flow path and the third flow path, and an on / off valve (128) is provided on the fifth flow path, wherein the on / off valve is configured for controlling communication or isolation between the first flow path and the third flow path, such that when the on / off valve is energized, the first flow path and the third flow path are in communication, and an auger stem and a rotary head have the same lifting speed. The hydraulic system based on a CFA operating condition solves the problem in the prior art of unsynchronized auger stem and rotary head lifting speeds, has a simple structure, and reduces operational challenges.

Description

Hydraulic systems and their operation methods based on CFA conditions and rotary drilling rigs Technical Field

[0001] This invention relates to the field of foundation construction equipment technology, and in particular to a hydraulic system based on CFA working conditions, its operation method, and a rotary drilling rig. Background Technology

[0002] In existing rotary drilling rigs, when performing CFA (long spiral bored pile) construction, the drill rod and power head need to move synchronously. Therefore, displacement and speed sensors are typically installed to detect the displacement and speed of the main winch and power head. Simultaneously, a high-flow-rate electro-hydraulic proportional valve is used, and the synchronization of the drill rod and power head is controlled by a program. The input current controls the pump's discharge rate by controlling the high-flow-rate electro-hydraulic proportional valve, adjusting the flow rate in real time to match the speed and position of the drill rod and power head. However, due to differences in actuators and loads, a speed difference occurs when the drill rod and power head rise, making speed synchronization impossible during ascent. Furthermore, in existing technology, when the power head rises, the drill rod winch motor is in a floating state. The power head drives the drill rod upward, forcing the drill rod winch motor to rotate along with the rising drill rod, generating significant heat and affecting its lifespan. Technical issues

[0003] Due to the different actuators and loads, a speed difference occurs when the drill pipe and the power head rise, making it impossible to achieve speed synchronization during the ascent. Furthermore, the drill pipe winch motor is forced to rotate along with the rise of the drill pipe, generating a large amount of heat and affecting the lifespan of the drill pipe winch motor. Technical solutions

[0004] In view of this, the present invention provides a hydraulic system based on CFA working conditions, which can solve the problem of asynchronous rising speed of drill pipe and power head in the prior art. It has a simple structure and reduces the difficulty of operation.

[0005] A hydraulic system based on CFA (Continuous Actuation and Optimization) operating conditions includes a drill pipe winch motor, a first hydraulic proportional valve, a first oil circuit, a second oil circuit, a power head winch motor, a second hydraulic proportional valve, a third oil circuit, a fourth oil circuit, and a fifth oil circuit. The first and second oil circuits are connected between the drill pipe winch motor and the first hydraulic proportional valve. When oil enters the first oil circuit, the drill pipe winch motor controls the drill pipe to rise. The third and fourth oil circuits are connected between the power head winch motor and the second hydraulic proportional valve. When oil enters the third oil circuit, the power head winch motor controls the power head to rise. The fifth oil circuit is connected between the first and third oil circuits. A switching valve is provided on the fifth oil circuit. The switching valve is used to control the connection or disconnection between the first and third oil circuits. When the switching valve is open, the first and third oil circuits are connected, so that the drill pipe and the power head have the same rising speed. When the switching valve is closed, the first and third oil circuits are disconnected.

[0006] In an embodiment of the present invention, the hydraulic system further includes a pilot pump, a first solenoid directional valve, and a second solenoid directional valve. The first inlet of the first solenoid directional valve is connected to the outlet of the pilot pump, the first inlet of the second solenoid directional valve is connected to the outlet of the pilot pump, the outlet of the first solenoid directional valve is connected to the first hydraulic control port of the first hydraulic proportional valve, and the outlet of the second solenoid directional valve is connected to the second hydraulic control port of the second hydraulic proportional valve. When the first solenoid directional valve and the second solenoid directional valve are simultaneously energized, the pilot oil of the pilot pump can simultaneously control the first hydraulic proportional valve and the second hydraulic proportional valve to switch directions, so that oil enters the first oil circuit and the third oil circuit, thereby synchronously starting the drill pipe winch motor and the power head winch motor.

[0007] In an embodiment of the present invention, the hydraulic system further includes a control valve, wherein the second port of the control valve is connected to the outlet of the pilot pump, the first port of the control valve is connected to the first inlet of the first solenoid directional valve, and the first port of the control valve is connected to the first inlet of the second solenoid directional valve. When the control valve is open, the pilot oil of the pilot pump flows through the control valve to the first solenoid directional valve and the second solenoid directional valve respectively.

[0008] In embodiments of the present invention, the control valve is an electro-proportional pressure reducing valve or a proportional relief valve.

[0009] In an embodiment of the present invention, when the control valve, the first solenoid directional valve, the second solenoid directional valve and the switching valve are all closed, the drill pipe winch motor and the power head winch motor operate independently.

[0010] In an embodiment of the present invention, the hydraulic system further includes a controller and an operating handle. The operating handle is electrically connected to the controller, and the controller is electrically connected to the control valve. When the operating handle is operated, the controller sends a signal to the control valve, enabling the control valve to simultaneously control the first hydraulic proportional valve and the second hydraulic proportional valve.

[0011] In an embodiment of the present invention, the hydraulic system further includes a controller and an operation panel. The operation panel is electrically connected to the controller, and the controller is electrically connected to the control valve. The operation panel is provided with a one-button start / stop button and a speed adjustment button. The one-button start / stop button causes the controller to send a signal to the control valve, enabling the control valve to simultaneously control the first hydraulic proportional valve and the second hydraulic proportional valve. The speed adjustment button controls the output pressure of the control valve to control the opening degree of the first hydraulic proportional valve and the second hydraulic proportional valve, thereby controlling the rising speed of the drill rod and the power head.

[0012] In an embodiment of the present invention, the hydraulic system further includes a third electromagnetic directional valve connected to the pilot pump. The third electromagnetic directional valve is connected to the second hydraulic control port of the first hydraulic proportional valve via a third pipeline, and the third electromagnetic directional valve is connected to the second oil inlet of the first electromagnetic directional valve via a fourth pipeline. When the first electromagnetic directional valve, the second electromagnetic directional valve, and the control valve are all de-energized, and the third electromagnetic directional valve is in the neutral position, the first pipeline is connected to the fourth pipeline, the first oil circuit and the second oil circuit are both connected to the first oil tank, and the third pipeline and the fourth pipeline are both connected to the second oil tank. The drill pipe winch motor is in a depressurized state and remains stationary.

[0013] In an embodiment of the present invention, the hydraulic system further includes a first oil pump connected to the first hydraulic proportional valve. When the drill pipe hoisting motor operates independently, and the third electromagnetic directional valve is controlled to be in the left position, the pilot oil of the pilot pump flows sequentially through the fourth pipeline and the first pipeline before entering the first hydraulic proportional valve, causing the first hydraulic proportional valve to be in the right position. At this time, the first oil pump is connected to the first oil circuit, and the hydraulic oil of the first oil pump enters the first oil circuit through the first hydraulic proportional valve. The drill pipe hoisting motor rotates to raise the drill pipe, and then the oil returns from the second oil circuit to the first oil tank.

[0014] In an embodiment of the present invention, when the third electromagnetic reversing valve is controlled to be in the right position, the pilot oil of the pilot pump enters the first hydraulic proportional valve, causing the first hydraulic proportional valve to be in the left position. The first oil pump is connected to the second oil circuit, and the hydraulic oil of the first oil pump enters the second oil circuit through the first hydraulic proportional valve. The drill rod winch motor rotates to lower the drill rod.

[0015] In an embodiment of the present invention, the hydraulic system further includes a fourth solenoid directional valve connected to the pilot pump. The fourth solenoid directional valve is connected to the second hydraulic control port of the second hydraulic proportional valve via a fifth pipeline, and to the second oil inlet of the second solenoid directional valve via a sixth pipeline. When the first solenoid directional valve, the second solenoid directional valve, and the control valve are all de-energized, and the fourth solenoid directional valve is in the neutral position, the second pipeline is connected to the sixth pipeline, the third oil circuit and the fourth oil circuit are both connected to the fourth oil tank, the fifth pipeline and the sixth pipeline are both connected to the third oil tank, and the power head winch motor is in a depressurized state and remains stationary.

[0016] In an embodiment of the present invention, the hydraulic system further includes a second oil pump connected to the second hydraulic proportional valve. When the power head winch motor operates independently, the fourth electromagnetic directional valve is controlled to be in the left position, and the pilot oil of the pilot pump flows to the second hydraulic proportional valve, causing the second hydraulic proportional valve to be in the left position. At this time, the second oil pump is connected to the third oil circuit, and the oil of the second oil pump enters from the third oil circuit. The power head winch motor rotates to drive the power head to rise.

[0017] In an embodiment of the present invention, when the third electromagnetic reversing valve is controlled to be in the right position, the pilot oil of the pilot pump enters the first hydraulic proportional valve, causing the first hydraulic proportional valve to be in the left position. The first oil pump is connected to the second oil circuit, and the hydraulic oil of the first oil pump enters the second oil circuit through the first hydraulic proportional valve. The drill rod winch motor rotates to lower the drill rod.

[0018] This application relates to a control method for a hydraulic system based on the aforementioned CFA operating condition. The control method includes: under the CFA operating condition, controlling the opening of the switching valve on the fifth oil circuit to connect the first oil circuit and the third oil circuit, making the pressure of the first oil circuit and the pressure of the third oil circuit the same; controlling the first solenoid directional valve and the second solenoid directional valve to be energized, so that the control valve is connected to the first hydraulic proportional valve and the second hydraulic proportional valve; operating the one-button start / pull button on the operating handle or the operating panel, the controller sends a signal to the control valve, and the pilot oil through the control valve can simultaneously control the opening of the first hydraulic proportional valve and the second hydraulic proportional valve.

[0019] This application relates to a rotary drilling rig, including the aforementioned hydraulic system based on CFA conditions. Beneficial effects

[0020] The hydraulic system of this invention uses a switching valve to make the pressure of the first and third oil circuits the same, so that the speed at which the drill rod rises is the same as the speed at which the power head rises. This avoids the phenomenon in the prior art where, when the power head rises and the drill rod winch motor is in a floating state, the drill rod winch motor is forced to rotate to follow the rise of the drill rod, generating a large amount of heat. This extends the life of the drill rod winch motor. The hydraulic system has a simple and reliable structure, avoids the need for additional feedback control, and reduces the difficulty of operation. Attached Figure Description

[0021] Figure 1 is a control principle diagram of the hydraulic system of the present invention when both the switching valve and the control valve are energized under CFA conditions.

[0022] Figure 2 is a control principle diagram of the hydraulic system of the present invention in which the drill pipe winch motor and the power head winch motor are in a floating state.

[0023] Figure 3 is a control principle diagram of the hydraulic system of the present invention when the drill pipe winch motor and the power head winch motor work independently.

[0024] Figure 4 is a schematic diagram of the control panel of the present invention. Embodiments of the present invention

[0025] The following specific embodiments illustrate the implementation of this application. Those skilled in the art can easily understand other advantages and effects of this application from the content disclosed in this specification.

[0026] In the following description, reference is made to the accompanying drawings, which illustrate several embodiments of the present application. It should be understood that other embodiments may also be used, and changes in mechanical composition, structure, electrical and operational aspects may be made without departing from the spirit and scope of the present application. The following detailed description should not be considered limiting, and the terminology used herein is for describing particular embodiments only and is not intended to limit the present application.

[0027] Although the terms first, second, etc., are used in some instances to describe various elements herein, these elements should not be limited by these terms. These terms are only used to distinguish one element from another.

[0028] Furthermore, as used herein, the singular forms “a,” “an,” and “the” are intended to include the plural forms as well, unless the context indicates otherwise. It should be further understood that the terms “comprising,” “including,” indicate the presence of a feature, step, operation, element, component, item, kind, and / or group, but do not exclude the presence, occurrence, or addition of one or more other features, steps, operations, elements, components, items, kinds, and / or groups. The terms “or” and “and / or” as used herein are interpreted as inclusive, or mean any one or any combination thereof. Thus, “A, B, or C” or “A, B, and / or C” means “any one of: A; B; C; A and B; A and C; B and C; A, B, and C.” Exceptions to this definition arise only when combinations of elements, functions, steps, or operations are inherently mutually exclusive in some way.

[0029] As shown in Figures 1 to 4, the hydraulic system based on the CFA (Continuous Availability and Performance) operating condition can simultaneously adapt to both CFA and conventional operating conditions. The hydraulic system includes a drill pipe winch motor 112, a first hydraulic proportional valve 123, a first oil circuit 141, a second oil circuit 142, a power head winch motor 113, a second hydraulic proportional valve 124, a third oil circuit 143, a fourth oil circuit 144, and a fifth oil circuit 145. The first and second oil circuits 141 and 142 are connected between the drill pipe winch motor 112 and the first hydraulic proportional valve 123. When oil enters the first oil circuit 141, the drill pipe winch motor 112 controls the drill pipe to rise; when oil enters the second oil circuit 142, the drill pipe winch motor 112 controls the drill pipe to descend. The third and fourth oil circuits 143 and 144 are connected between the power head winch motor 113 and the second hydraulic proportional valve 124. When oil enters the third oil circuit 143… The power head winch motor 113 controls the rise of the power head. When oil enters the fourth oil passage 144, the power head winch motor 113 controls the descent of the power head. Under CFA conditions, due to the differences in actuators and loads, there will be a speed difference between the rise of the drill pipe and the rise of the power head. Therefore, the fifth oil passage 145 is connected between the first oil passage 141 and the third oil passage 143. The fifth oil passage 145 is equipped with a switch valve 128, which is used to control the connection or disconnection between the first oil passage 141 and the third oil passage 143. When the switch valve 128 is open, the first oil passage 141 and the third oil passage 143 are connected. According to Pascal's principle, the pressure in the first oil passage 141 is the same as the pressure in the third oil passage 143, so that the drill pipe and the power head have the same rising speed. When the switch valve 128 is closed, the first oil passage 141 and the third oil passage 143 are disconnected. In this embodiment, the switching valve 128 is preferably a solenoid valve. Alternatively, the switching valve 128 can also be a two-position four-way valve or a hydraulic control valve, etc., which has the same function as the switching valve 128, and is used to control the connection or disconnection between the first oil circuit 141 and the third oil circuit 143.

[0030] As shown in Figure 1, the hydraulic system includes a pilot pump 111, a first solenoid directional valve 121, a second solenoid directional valve 122, and a control valve 127. The second port 2 of the control valve 127 is connected to the outlet of the pilot pump 111, and the first port 1 of the control valve 127 is connected to the first inlet of the first solenoid directional valve 121 and the first inlet of the second solenoid directional valve 122. The first solenoid directional valve 121 is connected to the first hydraulic control port of the first hydraulic proportional valve 123 through a first pipeline 131. The first hydraulic proportional valve 123 is used to control the forward and reverse rotation of the drill pipe winch motor 112. The second solenoid directional valve 122 is connected to the second hydraulic control port of the second hydraulic proportional valve 124 through a second pipeline 132. The proportional control valve 124 is used to control the forward and reverse rotation of the power head winch motor 113. When the first solenoid directional valve 121 and the second solenoid directional valve 122 are energized simultaneously, the first pipeline 131 and the second pipeline 132 are both connected to the control valve 127. The pilot oil through the control valve 127 can simultaneously control the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124 to switch, so that oil enters the first oil circuit 141 and the third oil circuit 143, so as to realize the synchronous opening of the drill rod winch motor 112 and the power head winch motor 113. The drill rod winch motor 112 can control the rise and fall of the drill rod, and the power head winch motor 113 can control the rise and fall of the power head. Therefore, the synchronous rise of the drill rod and the power head can be realized through the control valve 127.

[0031] Preferably, the control valve 127 is an electro-proportional pressure reducing valve or a proportional relief valve. When the control valve 127 is an electro-proportional pressure reducing valve, it also includes a third port 3. Pilot oil from the pilot pump 111 enters the control valve 127 at a constant pressure through the second port 2. The control valve 127 reduces the pressure of the pilot oil and outputs it through the first port 1 to the first solenoid directional valve 121 and the second solenoid directional valve 122. The hydraulic system also includes a fifth oil tank 155, which is connected to the third port 3. When the control valve 127 is closed, the first port 1 and the third port 3 are connected, and the pressure of the control valve 127 is 0. When the control valve 127 is a proportional relief valve, its function is the same as that of the electro-proportional pressure reducing valve. The output pressure of the proportional relief valve is set. When the pressure of the pilot oil is greater than the set output pressure, part of the pilot oil flows through the third port 3 to the fifth oil tank 155, and the first port 1 outputs oil at the set output pressure.

[0032] Preferably, the hydraulic system further includes a controller and an operating handle. The operating handle is electrically connected to the controller, and the controller is electrically connected to the control valve 127. When the operating handle is operated to raise the drill pipe, the controller sends a signal to the control valve 127, enabling the control valve 127 to simultaneously control the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124.

[0033] As shown in Figure 4, the hydraulic system also includes an operation panel 16, which is electrically connected to the controller. The controller is electrically connected to the control valve 127. The operation panel 16 is equipped with a one-button start / stop button 161 and a speed adjustment button 162. The one-button start / stop button 161 sends a signal from the controller to the control valve 127, enabling the control valve 127 to simultaneously control the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124. When using the one-button start / stop function, there is no need to operate the operating handle. Simply click the one-button start / stop button 161 on the operation panel 16 to output a signal to the control valve 127, thereby simultaneously controlling the rise of the drill rod and the power head, achieving intelligent operation and reducing the difficulty of operation. The speed adjustment button 162 can control the output pressure of the control valve 127 to control the opening of the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124, and thus control the rising speed of the drill rod and the power head.

[0034] Preferably, under normal operating conditions, as shown in Figure 2 or Figure 3, the control valve 127, the first solenoid directional valve 121, the second solenoid directional valve 122, and the switching valve 128 are all de-energized, and the drill pipe winch motor 112 and the power head winch motor 113 operate independently.

[0035] As shown in Figure 2, the hydraulic system also includes a third solenoid directional valve 125 connected to the pilot pump 111. The third solenoid directional valve 125 is connected to the second hydraulic port of the first hydraulic proportional valve 123 through the third pipeline 133. The third solenoid directional valve 125 is connected to the second oil port of the first solenoid directional valve 121 through the fourth pipeline 134. When neither the first solenoid directional valve 121 nor the second solenoid directional valve 122 is energized, the control valve 127 is closed, and the third solenoid directional valve 125 is in the neutral position. At this time, the first solenoid directional valve 121 is in the left position. The fourth pipeline 134 is connected to the first pipeline 131 through the first solenoid directional valve 121. The first oil circuit 141 and the second oil circuit 142 are both connected to the first oil tank 151. The third pipeline 133 and the fourth pipeline 134 are both connected to the second oil tank 152. The drill pipe winch motor 112 is in a depressurized state and remains stationary. At this time, the fourth solenoid directional valve 126 is not energized and is in the neutral position. The hydraulic system also includes a first oil pump 171, which is connected to a first hydraulic proportional valve 123. When the drill pipe hoisting motor 112 works independently, as shown in Figure 3, when the third solenoid directional valve 125 is in the left position, the pilot oil of the pilot pump 111 flows through the fourth pipeline 134 and the first pipeline 131 in sequence and then enters the first hydraulic proportional valve 123, so that the first hydraulic proportional valve 123 is in the right position. At this time, the first oil pump 171 is connected to the first oil circuit 141. The hydraulic oil of the first oil pump 171 enters the first oil circuit 141 through the first hydraulic proportional valve 123. The drill pipe hoisting motor 112 rotates to raise the drill pipe, and then returns the oil from the second oil circuit 142 to the first oil tank 151. When the third solenoid directional valve 125 is in the right position, the pilot oil of the pilot pump 111 flows through the third pipeline 133 and enters the first hydraulic proportional valve 123, causing the first hydraulic proportional valve 123 to be in the left position. At this time, the first oil pump 171 is connected to the second oil circuit 142. The hydraulic oil of the first oil pump 171 enters the second oil circuit 142 through the first hydraulic proportional valve 123. The drill pipe winch motor 112 rotates to lower the drill pipe, and then the oil returns from the first oil circuit 141 to the first oil tank 151.

[0036] As shown in Figure 2, the hydraulic system also includes a fourth solenoid directional valve 126 connected to the pilot pump 111. The fourth solenoid directional valve 126 is connected to the second hydraulic control port of the second hydraulic proportional valve 124 through the fifth pipeline 135, and the fourth solenoid directional valve 126 is connected to the second oil inlet port of the second solenoid directional valve 122 through the sixth pipeline 136. When the first solenoid directional valve 121 and the second solenoid directional valve 122 are both de-energized, the control valve 127 is closed, and the fourth solenoid directional valve 126 is in the neutral position, the second pipeline 132 is connected to the sixth pipeline 136, the third oil circuit 143 and the fourth oil circuit 144 are both connected to the fourth oil tank 154, and the fifth pipeline 135 and the sixth pipeline 136 are both connected to the third oil tank 153. The power head winch motor 113 is in a depressurized state and remains stationary. At this time, the third solenoid directional valve 125 is de-energized and is in the neutral position. The hydraulic system also includes a second oil pump 172, which is connected to a second hydraulic proportional valve 124. When the power head winch motor 113 works independently, as shown in Figure 3, the fourth solenoid directional valve 126 is controlled to be in the left position. The pilot oil from the pilot pump 111 flows through the sixth pipeline 136 and the second pipeline 132 to the second hydraulic proportional valve 124, so that the second hydraulic proportional valve 124 is in the left position. At this time, the second oil pump 172 is connected to the third oil circuit 143. The oil from the second oil pump 172 enters from the third oil circuit 143. The power head winch motor 113 rotates to drive the power head to rise, and then returns the oil from the fourth oil circuit 144 to the fourth oil tank 154. When the fourth solenoid directional valve 126 is in the right position, the pilot oil from the pilot pump 111 flows through the fifth pipeline 135 to the second hydraulic proportional valve 124, causing the second hydraulic proportional valve 124 to be in the right position. At this time, the second oil pump 172 is connected to the fourth oil circuit 144, and the oil from the second oil pump 172 enters from the fourth oil circuit 144. The power head winch motor 113 rotates to drive the power head to descend, and then the oil returns from the third oil circuit 143 to the fourth oil tank 154.

[0037] In this embodiment, the control valve 127 is preferably a solenoid valve, the first solenoid directional valve 121 and the second solenoid directional valve 122 are both two-position three-way valves, the third solenoid directional valve 125 and the fourth solenoid directional valve 126 are both three-position four-way valves, and the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124 are both three-position four-way valves.

[0038] This invention also relates to a control method for the aforementioned hydraulic system based on CFA operating conditions, the control method comprising:

[0039] Under CFA operating conditions, the switch valve 128 on the fifth oil circuit 145 is opened, connecting the first oil circuit 141 and the third oil circuit 143, so that the pressure of the first oil circuit 141 and the pressure of the third oil circuit 143 are the same.

[0040] The first solenoid directional valve 121 and the second solenoid directional valve 122 are energized, connecting the control valve 127 with the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124. Specifically, when the first solenoid directional valve 121 is energized and in the right position, the control valve 127 is connected to the first hydraulic proportional valve 123 through the first pipeline 131, and the first hydraulic proportional valve 123 is in the right position. At this time, the hydraulic oil from the first oil pump 171 enters from the first oil circuit 141, thereby controlling the drill pipe winch motor 112 to rotate and raise the drill pipe. When the second solenoid directional valve 122 is energized and in the right position, the control valve 127 is connected to the second hydraulic proportional valve 123 through the second pipeline 132, and the second hydraulic proportional valve 124 is in the left position. The hydraulic oil from the second oil pump 172 enters from the third oil circuit 143, thereby controlling the power head winch motor 113 to rotate and raise the power head.

[0041] By operating the control handle or the one-button start / stop button 161 on the control panel 16, the controller sends a signal to the control valve 127. The pilot oil through the control valve 127 can simultaneously control the opening of the first hydraulic proportional valve 123 and the second hydraulic proportional valve 124.

[0042] The present invention also relates to a rotary drilling rig, including the aforementioned hydraulic system based on CFA conditions.

[0043] The hydraulic system of the present invention uses a switching valve 128 to make the pressure of the first oil circuit 141 and the third oil circuit 143 the same, so that the speed at which the drill rod rises is the same as the speed at which the power head rises. This avoids the phenomenon in the prior art where, when the power head rises and the drill rod winch motor 112 is in a floating state, the drill rod winch motor 112 is forced to rotate to follow the rise of the drill rod, which generates a lot of heat. This can extend the life of the drill rod winch motor 112. The hydraulic system has a simple and reliable structure, avoids the need for additional feedback control, and reduces the difficulty of operation. Industrial applicability

[0044] The hydraulic system of this invention uses a switching valve to make the pressure of the first and third oil circuits the same, so that the speed at which the drill rod rises is the same as the speed at which the power head rises. This avoids the phenomenon in the prior art where, when the power head rises and the drill rod winch motor is in a floating state, the drill rod winch motor is forced to rotate to follow the rise of the drill rod, generating a large amount of heat. This extends the life of the drill rod winch motor. The hydraulic system has a simple and reliable structure, avoids the need for additional feedback control, and reduces the difficulty of operation.

Claims

1. A hydraulic system based on CFA operating conditions, characterized in that, The system includes a drill pipe winch motor (112), a first hydraulic proportional valve (123), a first oil circuit (141), a second oil circuit (142), a power head winch motor (113), a second hydraulic proportional valve (124), a third oil circuit (143), a fourth oil circuit (144), and a fifth oil circuit (145). The first oil circuit (141) and the second oil circuit (142) are connected between the drill pipe winch motor (112) and the first hydraulic proportional valve (123). When oil enters the first oil circuit (141), the drill pipe winch motor (112) controls the drill pipe to rise. The third oil circuit (143) and the fourth oil circuit (144) are connected between the power head winch motor (113) and the second hydraulic proportional valve (124). When oil enters the third oil passage (143), the power head winch motor (113) controls the power head to rise. The fifth oil passage (145) is connected between the first oil passage (141) and the third oil passage (143). The fifth oil passage (145) is equipped with a switch valve (128). The switch valve (128) is used to control the connection or disconnection between the first oil passage (141) and the third oil passage (143). When the switch valve (128) is open, the first oil passage (141) and the third oil passage (143) are connected, so that the drill rod and the power head have the same rising speed. When the switch valve (128) is closed, the first oil passage (141) and the third oil passage (143) are disconnected.

2. The hydraulic system based on CFA operating conditions as described in claim 1, characterized in that, The hydraulic system further includes a pilot pump (111), a first solenoid directional valve (121), and a second solenoid directional valve (122). The first inlet of the first solenoid directional valve (121) is connected to the outlet of the pilot pump (111), and the first inlet of the second solenoid directional valve (122) is connected to the outlet of the pilot pump (111). The outlet of the first solenoid directional valve (121) is connected to the first hydraulic control port of the first hydraulic proportional valve (123). The outlet of the second solenoid directional valve (122) is connected to the first hydraulic control port of the first hydraulic proportional valve (123). The oil port is connected to the second hydraulic port of the second hydraulic proportional valve (124). When the first electromagnetic reversing valve (121) and the second electromagnetic reversing valve (122) are energized at the same time, the pilot oil of the pilot pump (111) can simultaneously control the first hydraulic proportional valve (123) and the second hydraulic proportional valve (124) to switch, so that the first oil circuit (141) and the third oil circuit (143) can be filled with oil, so as to simultaneously start the drill pipe winch motor (112) and the power head winch motor (113).

3. The hydraulic system based on CFA operating conditions as described in claim 2, characterized in that, The hydraulic system also includes a control valve (127). The second port (2) of the control valve (127) is connected to the outlet of the pilot pump (111). The first port (1) of the control valve (127) is connected to the first inlet of the first solenoid directional valve (121). The first port (1) of the control valve (127) is connected to the first inlet of the second solenoid directional valve (122). When the control valve (127) is open, the pilot oil of the pilot pump (111) flows through the control valve (127) to the first solenoid directional valve (121) and the second solenoid directional valve (122) respectively.

4. The hydraulic system based on CFA operating conditions as described in claim 3, characterized in that, The control valve (127) is an electro-proportional pressure reducing valve or a proportional relief valve.

5. The hydraulic system based on CFA operating conditions as described in claim 3, characterized in that, When the control valve (127), the first electromagnetic reversing valve (121), the second electromagnetic reversing valve (122), and the switching valve (128) are all closed, the drill pipe winch motor (112) and the power head winch motor (113) operate independently.

6. The hydraulic system based on CFA operating conditions as described in claim 3, characterized in that, The hydraulic system also includes a controller and an operating handle. The operating handle is electrically connected to the controller, and the controller is electrically connected to the control valve (127). When the operating handle is operated, the controller sends a signal to the control valve (127), enabling the control valve (127) to simultaneously control the first hydraulic proportional valve (123) and the second hydraulic proportional valve (124).

7. The hydraulic system based on CFA operating conditions as described in claim 3, characterized in that, The hydraulic system also includes a controller and an operation panel. The operation panel is electrically connected to the controller, and the controller is electrically connected to the control valve (127). The operation panel is provided with a one-button start button (161) and a speed adjustment button (162). The one-button start button (161) causes the controller to send a signal to the control valve (127), so that the control valve (127) can simultaneously control the first hydraulic proportional valve (123) and the second hydraulic proportional valve (124). The output pressure of the control valve (127) can be controlled by the speed adjustment button (162) to control the opening of the first hydraulic proportional valve (123) and the second hydraulic proportional valve (124), thereby controlling the rising speed of the drill rod and the power head.

8. The hydraulic system based on CFA operating conditions as described in claim 3, characterized in that, The hydraulic system also includes a third solenoid directional valve (125) connected to the pilot pump (111). The third solenoid directional valve (125) is connected to the second hydraulic port of the first hydraulic proportional valve (123) via a third pipeline (133). The third solenoid directional valve (125) is connected to the second oil inlet of the first solenoid directional valve (121) via a fourth pipeline (134). When the first solenoid directional valve (121) and the second solenoid directional valve (122) are connected... When the first pipeline (131) and the control valve (127) are not energized, and the third electromagnetic reversing valve (125) is in the neutral position, the first pipeline (131) is connected to the fourth pipeline (134), the first oil circuit (141) and the second oil circuit (142) are both connected to the first oil tank (151), the third pipeline (133) and the fourth pipeline (134) are both connected to the second oil tank (152), and the drill pipe winch motor (112) is in a depressurized state and remains stationary.

9. The hydraulic system based on CFA operating conditions as described in claim 8, characterized in that, The hydraulic system also includes a first oil pump (171), which is connected to the first hydraulic proportional valve (123). When the drill rod winch motor (112) works independently, the third electromagnetic directional valve (125) is controlled to be in the left position. The pilot oil of the pilot pump (111) flows through the fourth pipeline (134) and the first pipeline (131) in sequence and then enters the first hydraulic proportional valve (123), so that the first hydraulic proportional valve (123) is in the right position. At this time, the first oil pump (171) is connected to the first oil circuit (141). The hydraulic oil of the first oil pump (171) enters the first oil circuit (141) through the first hydraulic proportional valve (123). The drill rod winch motor (112) rotates to make the drill rod rise.

10. The hydraulic system based on CFA operating conditions as described in claim 9, characterized in that, When the third electromagnetic directional valve (125) is in the right position, the pilot oil of the pilot pump (111) enters the first hydraulic proportional valve (123), causing the first hydraulic proportional valve (123) to be in the left position. The first oil pump (171) is connected to the second oil circuit (142). The hydraulic oil of the first oil pump (171) enters the second oil circuit (142) through the first hydraulic proportional valve (123). The drill rod winch motor (112) rotates to lower the drill rod.

11. The hydraulic system based on CFA operating conditions as described in claim 3, characterized in that, The hydraulic system also includes a fourth solenoid directional valve (126) connected to the pilot pump (111). The fourth solenoid directional valve (126) is connected to the second hydraulic port of the second hydraulic proportional valve (124) through a fifth pipeline (135). The fourth solenoid directional valve (126) is connected to the second oil inlet of the second solenoid directional valve (122). When the first solenoid directional valve (121), the second solenoid directional valve (122) and the control valve (127) are all de-energized, and the fourth solenoid directional valve (126) is in the neutral position, the power head winch motor (113) is in a depressurized state and remains stationary.

12. The hydraulic system based on CFA operating conditions as described in claim 11, characterized in that, The hydraulic system also includes a second oil pump (172), which is connected to the second hydraulic proportional valve (124). When the power head winch motor (113) works independently, it controls the fourth electromagnetic directional valve (126) to be in the left position. The pilot oil of the pilot pump (111) flows to the second hydraulic proportional valve (124), so that the second hydraulic proportional valve (124) is in the left position. At this time, the second oil pump (172) is connected to the third oil circuit (143). The oil of the second oil pump (172) enters from the third oil circuit (143), and the power head winch motor (113) rotates to drive the power head to rise.

13. The hydraulic system based on CFA operating conditions as described in claim 12, characterized in that, When the fourth electromagnetic reversing valve (126) is in the right position, the pilot oil of the pilot pump (111) flows to the second hydraulic proportional valve (124), so that the second hydraulic proportional valve (124) is in the right position. At this time, the second oil pump (172) is connected to the fourth oil circuit (144), and the oil of the second oil pump (172) enters from the fourth oil circuit (144). The power head winch motor (113) rotates to drive the power head to descend.

14. A control method for a hydraulic system based on CFA operating conditions as described in any one of claims 1 to 13, characterized in that, The control method includes: Under CFA operating conditions, the switch valve (128) on the fifth oil circuit (145) is opened, so that the first oil circuit (141) and the third oil circuit (143) are connected, so that the pressure of the first oil circuit (141) and the pressure of the third oil circuit (143) are the same; The first solenoid directional valve (121) and the second solenoid directional valve (122) are energized, so that the control valve (127) is connected to the first hydraulic proportional valve (123) and the second hydraulic proportional valve (124); Operate the one-button start button (161) on the operating handle or operating panel (16) to send a signal to the control valve (127), and control the opening of the first hydraulic proportional valve (123) and the second hydraulic proportional valve (124) simultaneously via the pilot oil of the control valve (127).

15. A rotary drilling rig, characterized in that, Includes the hydraulic system based on CFA conditions as described in any one of claims 1 to 14.

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