Hydraulic system for iron roughneck

Abstract

The invention relates to a hydraulic system for an iron roughneck. The hydraulic system comprises a hydraulic pump station, an electromagnetic directional valve group, a pilot pressure-reducing overflow valve and two upper shackle oil cylinders which are arranged in parallel, an oil supply port and an oil return port of the hydraulic pump station are communicated with corresponding oil ports of the electromagnetic directional valve set in a one-to-one correspondence mode, the electromagnetic directional valve set comprises a first working unit, the first working unit is provided with a first working oil port and a second working oil port, the first working oil port is communicated with rodless cavities of the two upper shackle oil cylinders, and the second working oil port is communicated with rodless cavities of the two lower shackle oil cylinders. Rod cavities of the two upper shackle oil cylinders are communicated with a port B of the pilot pressure reducing overflow valve, a port T of the pilot pressure reducing overflow valve is communicated with an oil tank of the hydraulic pump station, and a port A of the pilot pressure reducing overflow valve is communicated with the second working oil port. According to the iron roughneck hydraulic system, after the screwing pressure reaches the set pressure, low-pressure overflow is carried out through the pilot pressure reduction overflow valve, and therefore it can be guaranteed that a screw thread is screwed, and the screw thread can be prevented from being damaged.

Description

Technical Field

[0001] The present invention relates to the technical field of iron roughnecks, and in particular to an iron roughneck hydraulic system. Background Art

[0002] During the drilling operation, the drill pipe needs to be frequently threaded on and off. The threading and unthreading of the drill pipe directly affects the construction effect of the drilling platform. At present, the auxiliary threading and unthreading equipment used in China is mainly hydraulic power tongs or iron roughnecks. The hydraulic power tongs need to replace the corresponding jaw plates for different clamping pipe diameters, and the replacement process is cumbersome. Iron roughnecks are suitable for connecting and unloading drill pipes and drill collars during drilling. The clamping range is 89-150mm, and there is no need to replace the jaw plates.

[0003] Chinese patent document CN116220581 A discloses an iron driller, which includes a clamping and unbuckling device, a screwing device, a horizontal drive and a lifting drive. The clamping and unbuckling device includes a lower clamp and an upper clamp, and the upper clamp includes two upper clamping arms, an upper clamping drive cylinder and an upper unbuckling drive. The upper clamping drive cylinder is connected to the driving ends of the two upper clamping arms, and is used to drive the driving ends of the two upper clamping arms to open or contract to drive the clamping ends of the two upper clamping arms to contract or open. The upper unbuckling drive is correspondingly connected to the two upper clamping arms, and is used to drive the two upper clamping arms to rotate synchronously relative to the lower clamp to buckle or unbuck. The defects and shortcomings of the iron driller are as follows: (1) when making up, after the make-up pressure of the make-up and break-out driver reaches the set value, it cannot be relieved, but the set pressure is maintained to continue making up, which will cause damage to the drill pipe thread; (2) when the drill pipe is screwed, the lower clamp and the screwing device are clamped, and the upper clamp needs to be opened, that is, the upper clamping drive cylinder contracts to drive the clamping ends of the two upper clamping arms to open. In this process, since the opening angle of the two upper clamping arms is too large, the opening / closing time of the upper clamp when making up or breaking up is relatively long, and the efficiency is low. Summary of the invention

[0004] 1. Technical issues to be resolved

[0005] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides an iron roughneck hydraulic system, which solves the technical problem that after the make-up pressure of the existing iron roughneck reaches the set value, the pressure cannot be relieved and the high-pressure make-up will continue, resulting in damage to the drill pipe thread.

[0006] (II) Technical solution

[0007] In order to achieve the above object, the main technical solutions adopted by the present invention include:

[0008] The embodiment of the present invention provides an iron roughneck hydraulic system, comprising a hydraulic pump station, an electromagnetic reversing valve group, a pilot pressure reducing relief valve and an actuator, wherein the actuator comprises two make-up and break-out cylinders arranged in parallel;

[0009] The oil supply port and the oil return port of the hydraulic pump station are connected to the corresponding oil ports of the electromagnetic reversing valve group in a one-to-one correspondence. The electromagnetic reversing valve group includes a first working joint, and the first working joint has a first working oil port and a second working oil port. The first working oil port is connected to the rodless chambers of the two make-up and make-up cylinders, and the rod chambers of the two make-up and make-up cylinders are connected to the B port of the pilot pressure reducing relief valve, and the T port of the pilot pressure reducing relief valve is connected to the oil tank of the hydraulic pump station, and the A port of the pilot pressure reducing relief valve is connected to the second working oil port.

[0010] Optionally, the pilot pressure reducing relief valve comprises a first one-way valve, a pressure reducing relief valve, a pilot relief valve and a two-position two-way electromagnetic reversing valve;

[0011] A first check valve and a pressure reducing relief valve are arranged in parallel between port A and port B. The first check valve is unidirectionally conducted from port B to port A. The oil inlet and oil outlet of the pressure reducing relief valve are connected with port A and port B one by one. The control oil port of the pressure reducing relief valve is connected with the oil inlet of the pilot relief valve and the two-position two-way solenoid reversing valve 1 respectively. The oil drain port of the pressure reducing relief valve, the oil outlet of the pilot relief valve and the oil outlet of the two-position two-way solenoid reversing valve 1 are all connected with port T.

[0012] Optionally, the iron roughneck hydraulic system further comprises a first bidirectional hydraulic lock and a second bidirectional hydraulic lock, and the actuator further comprises an upper clamping cylinder and a lower clamping cylinder;

[0013] The electromagnetic reversing valve group also includes a second working joint, which has a third working oil port and a fourth working oil port. The third working oil port is respectively connected to the rod chambers of the upper clamping cylinder and the lower clamping cylinder, and the fourth working oil port is respectively connected to the rodless chambers of the upper clamping cylinder and the lower clamping cylinder, and a first two-way hydraulic lock is arranged between the upper clamping cylinder and the second working joint to control the upper clamping cylinder to remain stationary under load, and a second two-way hydraulic lock is arranged between the lower clamping cylinder and the second working joint to control the lower clamping cylinder to remain stationary under load.

[0014] Optionally, the iron roughneck hydraulic system further comprises an oil storage cylinder, a one-way throttle valve, a first hydraulically controlled one-way valve, a second one-way valve and a third one-way valve;

[0015] The electromagnetic reversing valve group also includes a third working joint, the third working joint has a fifth working oil port, the fifth working oil port is connected to the rod chamber of the upper clamping oil cylinder, the rod chamber of the oil storage cylinder is connected to the rodless chamber of the upper clamping oil cylinder, the rodless chamber of the oil storage cylinder is connected to the first port of the one-way throttle valve, the second port of the one-way throttle valve is divided into two branches, one of which is connected to the first port of the first hydraulically controlled one-way valve, the second port of the first hydraulically controlled one-way valve is connected to the oil tank, and the other branch is connected to the fourth working oil port;

[0016] The control port of the first hydraulically controlled one-way valve is connected to the fifth working oil port, the second one-way valve is arranged between the fifth working oil port and the rod chamber of the upper clamping cylinder and is unidirectional from the fifth working oil port to the rod chamber of the upper clamping cylinder, and the third one-way valve is arranged between the fourth working oil port and the second port of the one-way throttle valve and is unidirectional from the fourth working oil port to the second port of the one-way throttle valve.

[0017] Optionally, the iron roughneck hydraulic system further comprises an electric proportional multi-way valve arranged in parallel with the electromagnetic reversing valve group, and the actuator further comprises two parallel spin-lock clamping cylinders and four parallel spin-lock motors;

[0018] The electromagnetic reversing valve group includes a fourth working joint, the fourth working joint has a sixth working oil port and a seventh working oil port, the sixth working oil port is respectively connected to the rodless chambers of the two rotary clamping cylinders, and the seventh working oil port is respectively connected to the rod chambers of the two rotary clamping cylinders;

[0019] The oil supply port and oil return port of the hydraulic pump station are connected to the corresponding oil ports of the electric proportional multi-way valve in a one-to-one correspondence. The electric proportional multi-way valve has a fifth working joint, and the fifth working joint is respectively connected to each rotary motor, so that the hydraulic oil output by the hydraulic pump station enters each rotary motor after being regulated by the fifth working joint to control the rotation speed of each rotary motor.

[0020] Optionally, the fifth working joint has an eighth working oil port and a ninth working oil port, a secondary flow diversion and collection valve is arranged between the eighth working oil port and the first ports of the four rotary motors, and the second ports of the four rotary motors are connected to the ninth working oil port.

[0021] Optionally, the actuator further comprises a lifting cylinder;

[0022] The electric proportional multi-way valve has a sixth working connection, the sixth working connection has a tenth working oil port and an eleventh working oil port, the tenth working oil port is connected to the rodless chamber of the lifting cylinder, and the eleventh working oil port is connected to the rod chamber of the lifting cylinder.

[0023] Optionally, the actuator further comprises two telescopic cylinders connected in parallel;

[0024] The electric proportional multi-way valve has a seventh working joint, which has a twelfth working oil port and a thirteenth working oil port. The twelfth working oil port is respectively connected to the rod chambers of the two telescopic cylinders, and the thirteenth working oil port is respectively connected to the rodless chambers of the two telescopic cylinders.

[0025] Optionally, the hydraulic pump station further comprises a constant pressure variable pump, the constant pressure variable pump is provided with a motor, the oil outlet of the oil tank is connected with the oil inlet of the constant pressure variable pump, the oil outlet of the constant pressure variable pump is connected with a main oil supply pipeline, the main oil supply pipeline is divided into two branches, one branch is connected with the oil inlet of the electromagnetic reversing valve group, and the other branch is connected with the oil inlet of the electric proportional multi-way valve;

[0026] The oil return port of the oil tank is connected to a main oil return pipeline, which is divided into two paths, one of which is connected to the oil outlet of the electromagnetic reversing valve group, and the other is connected to the oil outlet of the electric proportional multi-way valve.

[0027] Optionally, a pilot control on-off valve is further provided on the main oil supply pipeline, and the pilot control on-off valve includes a hydraulically controlled on-off valve and a two-position two-way electromagnetic reversing valve 2;

[0028] The oil inlet of the hydraulically controlled on-off valve is connected to the oil outlet of the constant pressure variable pump, the oil outlet of the hydraulically controlled on-off valve is connected to the main oil supply pipeline, the pilot control oil port of the hydraulically controlled on-off valve is connected to the oil inlet of the second two-position two-way solenoid reversing valve, and the oil outlet of the second two-position two-way solenoid reversing valve is connected to the main oil return pipeline.

[0029] (III) Beneficial effects

[0030] The beneficial effects of the present invention are as follows: the iron roughneck hydraulic system of the present invention comprises a hydraulic pump station, an electromagnetic reversing valve group, a pilot pressure reducing relief valve and an actuator, the actuator comprises two make-up and make-up breakout oil cylinders arranged in parallel; the oil supply port and the oil return port of the hydraulic pump station are connected with the corresponding oil ports of the electromagnetic reversing valve group in a one-to-one correspondence, the electromagnetic reversing valve group comprises a first working joint, the first working joint has a first working oil port and a second working oil port, the first working oil port is connected with the rodless chambers of the two make-up and make-up breakout oil cylinders, and the two make-up and make-up breakout oil cylinders are connected with each other. The rod chamber of the cylinder is connected to the B port of the pilot pressure reducing relief valve, the T port of the pilot pressure reducing relief valve is connected to the oil tank of the hydraulic pump station, and the A port of the pilot pressure reducing relief valve is connected to the second working oil port. Compared with the prior art, the iron roughneck hydraulic system of the present invention ensures that the make-up and break-out cylinder is made-up according to the preset value through the pilot pressure reducing relief valve, and automatically unloads at low pressure when the make-up pressure exceeds the preset value, thereby ensuring that the drill rod thread is tightened and the drill rod thread is prevented from being damaged when the make-up and break-out cylinder is retracted to make-up. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 It is a structural schematic diagram of Embodiment 1 of the iron roughneck hydraulic system of the present invention;

[0032] Figure 2 for Figure 1 An enlarged schematic diagram of the iron roughneck hydraulic system at the electromagnetic reversing valve group;

[0033] Figure 3 It is a structural schematic diagram of Example 2 of the iron roughneck hydraulic system of the present invention.

[0034] [Description of Reference Numerals]

[0035] 1: Oil tank; 2: Motor; 3: Constant pressure variable pump; 4: Pilot control on-off valve; 5: Hydraulic control on-off valve; 6: Two-position two-way solenoid reversing valve 2; 7: Electric proportional multi-way valve; 8: Solenoid reversing valve group; 9: Lifting cylinder; 10: Telescopic cylinder; 11: Spindle motor; 12: Spindle clamping cylinder; 13: Upper clamping cylinder; 14: Lower clamping cylinder; 15: Upper unclamping cylinder; 16: Oil storage cylinder; 17: Pilot pressure relief valve; 18: First check valve; 19: Pressure relief valve Flow valve; 20: pilot relief valve; 21: two-position two-way solenoid reversing valve one; 23: first two-way hydraulic lock; 24: second two-way hydraulic lock; 25: one-way throttle valve; 26: first hydraulically controlled one-way valve; 27: second one-way valve; 28: third one-way valve; 29: first stroke switch; 30: second stroke switch; 31: first position proximity switch; 32: third stroke switch; 33: secondary diversion and collection valve; 34: second position proximity switch; 35: fourth stroke switch. DETAILED DESCRIPTION

[0036] In order to better explain the present invention and facilitate understanding, the present invention is described in detail below through specific implementation modes in conjunction with the accompanying drawings.

[0037] Embodiment 1:

[0038] Reference Figure 1 and Figure 2 The present embodiment provides an iron roughneck hydraulic system, comprising a hydraulic pump station, an actuator, an electromagnetic reversing valve group 8, and an electric proportional multi-way valve 7 arranged in parallel with the electromagnetic reversing valve group 8. The actuator comprises a lifting cylinder 9, a telescopic cylinder 10, a spinner motor 11, a spinner clamping cylinder 12, an upper clamping cylinder 13, a lower clamping cylinder 14, and an upper breakout cylinder 15.

[0039] The oil supply port and the oil return port of the hydraulic pump station are connected to the corresponding oil ports of the electromagnetic reversing valve group 8 in a one-to-one correspondence. The electromagnetic reversing valve group 8 includes a plurality of working links, each of which is connected to the upper clamping cylinder 13, the lower clamping cylinder 14, the upper unbuckling cylinder 15 and the screw clamping cylinder 12 in a one-to-one correspondence to control each cylinder to make an extension or retraction action. It should be noted that the upper clamping cylinder 13 is a driving cylinder of the upper clamp, which is used to drive the two upper clamping arms of the upper clamp to contract or open. The upper unbuckling cylinder 15 is a rotating driving member of the upper clamp, which is used to drive the two upper clamping arms of the upper clamp to rotate synchronously relative to the lower clamp to buckle or unbuck. The lower clamping cylinder 14 is a driving cylinder of the lower clamp, which is used to drive the two lower clamping arms of the lower clamp to contract or open. The screw clamping cylinder 12 is an opening and closing driving member of the screw device, which is used to drive the two screw arms of the screw device to clamp or release the upper drill rod.

[0040] The oil supply port and the oil return port of the hydraulic pump station are connected to the corresponding oil ports of the electric proportional multi-way valve 7 one by one. The electric proportional multi-way valve 7 includes a plurality of working links, each of which is connected to the lifting cylinder 9, the telescopic cylinder 10, and the screw-on motor 11 one by one, so that the hydraulic oil output by the hydraulic pump station enters the lifting cylinder 9, the telescopic cylinder 10, and the screw-on motor 11 after being regulated by the corresponding working links of the electric proportional multi-way valve 7, so as to control the action speed of the lifting cylinder 9 and the telescopic cylinder 10 and the speed of the motor. It should be noted that the screw-on motor 11 is a rotary drive member of the screw-on device, which is used to drive the upper drill rod to rotate relative to the lower drill rod to screw in or out the drill rod connection thread. The lifting cylinder 9 is a driving cylinder of the lifting drive, which is used to drive the clamp head device to move up and down. The telescopic cylinder 10 is a driving cylinder of the horizontal drive, which is used to drive the clamp head device to move horizontally. The clamp head device includes a clamping and unbuckling device and a screw-on device.

[0041] The iron roughneck hydraulic system of this embodiment includes a pilot pressure relief valve 17. The electromagnetic reversing valve group 8 includes a first working joint, the first working joint has a first working oil port and a second working oil port, the number of the make-up and break-out oil cylinders 15 is two, the first working oil port is communicated with the rodless chambers of the two make-up and break-out oil cylinders 15, the rod chambers of the two make-up and break-out oil cylinders 15 are communicated with the B port of the pilot pressure relief valve 17, the T port of the pilot pressure relief valve 17 is communicated with the oil tank 1 of the hydraulic pump station, and the A port of the pilot pressure relief valve 17 is communicated with the second working oil port.

[0042] In the iron roughneck hydraulic system of the present embodiment, a pilot pressure reducing relief valve 17 is provided between the electromagnetic reversing valve group 8 and the rod chambers of the two make-up and break-out cylinders 15. The pilot pressure reducing relief valve 17 is a hydraulic valve with dual functions of pressure reducing and overflowing. It can automatically overflow after the make-up pressure reaches a preset value to release the excess pressure. As a result, when the make-up and break-out cylinders 15 are retracted for make-up, the drill rod thread can be tightened and the drill rod thread can be prevented from being damaged.

[0043] Specifically, the pilot pressure reducing relief valve 17 includes a first check valve 18 , a pressure reducing relief valve 19 , a pilot relief valve 20 and a two-position two-way electromagnetic reversing valve 21 .

[0044] A first one-way valve 18 and a pressure reducing relief valve 19 are arranged in parallel between port A and port B. The first one-way valve 18 is unidirectionally conducted from port B to port A. The oil inlet and oil outlet of the pressure reducing relief valve 19 are connected with port A and port B in a one-to-one correspondence. The control oil port of the pressure reducing relief valve 19 is connected with the oil inlet of the pilot relief valve 20 and the two-position two-way solenoid reversing valve 21 respectively. The oil drain port of the pressure reducing relief valve 19, the oil outlet of the pilot relief valve 20 and the oil outlet of the two-position two-way solenoid reversing valve 21 are all connected with port T.

[0045] The working principle of the pilot pressure reducing relief valve 17 of the present embodiment is as follows: before the drill pipe make-up pressure does not reach the set value, the valve group is used as a high-pressure pressure reducing valve, that is, the two-position two-way electromagnetic reversing valve 21 is powered off and closed, and the pilot relief valve 20 adjusts the pressure of the pressure reducing relief valve 19, which is the make-up pressure set value, wherein the hand wheel of the pilot relief valve 20 is arranged on the operating table panel, and the make-up pressure can be automatically adjusted online in real time; when the make-up pressure reaches the set value, the pressure sensor of the make-up oil circuit sends a signal to control the two-position two-way electromagnetic reversing valve 21 to be powered on and open, and the control oil port of the pressure reducing relief valve 19 is directly connected to the oil tank 1, which makes the pressure at the control oil port of the pressure reducing relief valve 19 almost zero, at this time, the valve group is used as a low-pressure relief valve, and the oil drain port of the pressure reducing relief valve 19 allows the high-pressure oil of the make-up circuit to be unloaded back to the oil tank 1 at low pressure, thereby protecting the drill pipe thread from damage. It should be noted that the pressure sensor of the make-up oil circuit can be set at port B to control the power loss or power supply of the two-position two-way solenoid reversing valve 21.

[0046] In this embodiment, the iron roughneck hydraulic system further includes a first two-way hydraulic lock 23 and a second two-way hydraulic lock 24. The electromagnetic reversing valve group 8 includes a second working joint, the second working joint has a third working oil port and a fourth working oil port, the third working oil port is connected to the rod chambers of the upper clamping oil cylinder 13 and the lower clamping oil cylinder 14 respectively, the fourth working oil port is connected to the rodless chambers of the upper clamping oil cylinder 13 and the lower clamping oil cylinder 14 respectively, and the first two-way hydraulic lock 23 is arranged between the upper clamping oil cylinder 13 and the second working joint to control the upper clamping oil cylinder 13 to remain in a stationary state under load, and the second two-way hydraulic lock 24 is arranged between the lower clamping oil cylinder 14 and the second working joint to control the lower clamping oil cylinder 14 to remain in a stationary state under load.

[0047] It should be noted that the two-way hydraulic lock is composed of two hydraulically controlled one-way valves. The two hydraulically controlled one-way valves take the pressure of the other oil circuit as the pilot oil to open in the reverse direction. When there is no pressure in one pipeline, the other hydraulic lock is closed in the reverse direction. When the second working joint of the electromagnetic reversing valve group 8 is in the middle position, the third working oil port and the fourth working oil port are both connected to the oil tank 1, and the first two-way hydraulic lock 23 and the second two-way hydraulic lock 24 are closed in the reverse direction, respectively locking the hydraulic oil in the two chambers of the upper clamping oil cylinder 13 and the lower clamping oil cylinder 14, so that the upper clamping oil cylinder 13 and the lower clamping oil cylinder 14 can remain in a static state for a long time, thereby forming a two-way hydraulic lock.

[0048] In this embodiment, the iron roughneck hydraulic system further includes an oil storage cylinder 16 , a one-way throttle valve 25 , a first hydraulically controlled one-way valve 26 , a second one-way valve 27 and a third one-way valve 28 .

[0049] The electromagnetic reversing valve group 8 includes a third working connection, the third working connection has a fifth working oil port, the fifth working oil port is connected to the rod chamber of the upper clamping cylinder 13, the rod chamber of the oil storage cylinder 16 is connected to the rodless chamber of the upper clamping cylinder 13, the rodless chamber of the oil storage cylinder 16 is connected to the first port of the one-way throttle valve 25, the second port of the one-way throttle valve 25 is divided into two branches, one of which is connected to the first port of the first hydraulically controlled one-way valve 26, the second port of the first hydraulically controlled one-way valve 26 is connected to the oil tank 1, and the other branch is connected to the fourth working oil port.

[0050] The control liquid port of the first hydraulically controlled one-way valve 26 is connected to the fifth working oil port, the second one-way valve 27 is arranged between the fifth working oil port and the rod chamber of the upper clamping cylinder 13 and is unidirectional from the fifth working oil port to the rod chamber of the upper clamping cylinder 13, and the third one-way valve 28 is arranged between the fourth working oil port and the oil inlet port of the one-way throttle valve 25 and is unidirectional from the fourth working oil port to the oil inlet port of the one-way throttle valve 25.

[0051] The function of the oil storage cylinder 16 is to reduce the opening angle of the two upper clamping arms by controlling the retraction amount of the upper clamping cylinder 13. Its working principle is as follows: when the drill pipe is screwed, the lower clamping arm and the screwing arm are clamped, and the upper clamping arm needs to be opened. At this time, the third working link is operated, and the fifth working oil port provides pressure oil. The pressure oil enters the rod chamber of the upper clamping cylinder 13 through the second one-way valve 27. Since the first two-way hydraulic lock 23 is locked, the hydraulic oil in the rodless chamber of the upper clamping cylinder 13 passes through the rod chamber of the oil storage cylinder 16. The hydraulic oil in the rodless chamber of the oil storage cylinder 16 returns to the oil tank through the one-way throttle valve 25 and the first hydraulically controlled one-way valve 26 that opens in reverse, causing the oil storage cylinder 16 to retract. During this process, the rod chamber volume of the oil storage cylinder 16 determines the retraction amount of the upper clamping cylinder 13, and further determines the opening angle of the upper clamping arm. When selecting the specifications of the oil storage cylinder 16, the rod chamber volume can be controlled within the range of the upper clamping cava to clear the drill rod. At the same time, in order to ensure that the oil storage cylinder 16 can be fully extended and reset before the upper and lower clamps are clamped, the oil storage cylinder 16 needs to select a larger cylinder diameter and a smaller rod diameter, or select a cylinder seal with small friction resistance to ensure that the oil storage cylinder 16 is extended and reset first.

[0052] When the second working link is operated to drive the upper clamping arm and the lower clamping arm to clamp, the fourth working oil port provides pressure oil, and the pressure oil enters the rodless chamber of the oil storage cylinder 16 through the third one-way valve 28 and the one-way throttle valve 25. The hydraulic oil in the rod chamber of the oil storage cylinder 16 and the hydraulic oil coming out of the fourth working oil port are connected to the rodless chamber of the upper clamping cylinder 13, so that the piston rod of the oil storage cylinder 16 is quickly extended and reset, and at the same time, the upper clamping cylinder 13 and the lower clamping cylinder 14 are also extended to clamp.

[0053] In this embodiment, the electromagnetic reversing valve group 8 includes a fourth working joint, the fourth working joint has a sixth working oil port and a seventh working oil port, the sixth working oil port is connected to the rodless chamber of the rotary lock clamping cylinder 12, and the seventh working oil port is connected to the rod chamber of the rotary lock clamping cylinder 12. The electric proportional multi-way valve 7 has a fifth working joint, and the fifth working joint is connected to the rotary lock motor 11, so that the hydraulic oil output by the hydraulic pump station enters the rotary lock motor 11 after being regulated by the fifth working joint to control the rotation speed of the rotary lock motor 11.

[0054] Further, in this embodiment, the number of the spinner clamping oil cylinders 12 is two, and the two spinner clamping oil cylinders 12 are arranged in parallel. The number of the spinner motors 11 is four, and the four spinner motors 11 are arranged in parallel. The fifth working joint has an eighth working oil port and a ninth working oil port. A secondary flow dividing and collecting valve 33 is arranged between the eighth working oil port and the first ports of the four spinner motors 11, and the second ports of the four spinner motors 11 are connected to the ninth working oil port.

[0055] It should be noted that the secondary flow dividing and collecting valve 33 of the present embodiment is composed of three flow dividing and collecting valves, and has an oil inlet and four oil outlets. After the hydraulic oil from the eighth working oil port enters the secondary flow dividing and collecting valve 33, it is first evenly divided into two parts by one of the flow dividing and collecting valves, and then evenly divided into four parts by the other two flow dividing and collecting valves. The four parts of hydraulic oil enter the four rotary motors 11 one by one, thereby realizing the speed proportional control and synchronous rotation of the four rotary motors 11.

[0056] In this embodiment, the electric proportional multi-way valve 7 has a sixth working connection, the sixth working connection has a tenth working oil port and an eleventh working oil port, the tenth working oil port is connected to the rodless chamber of the lifting cylinder 9, and the eleventh working oil port is connected to the rod chamber of the lifting cylinder 9.

[0057] The lifting circuit of this embodiment adopts constant pressure variable pump 3+electric proportional multi-way valve 7+travel switch to realize closed-loop control, and the action process of lifting cylinder 9 is as follows: operate the electric proportional multi-way valve 7 upward, lift cylinder 9 extends, drives the driller's tongs to rise, touches the first travel switch 29 at the first set height, automatically controls the electric proportional multi-way valve 7 to close, and lift cylinder stops extending. Operate the electric proportional multi-way valve 7 downward, lift cylinder 9 retracts, drives the driller's tongs to descend, touches the second travel switch 30 at the second set height, automatically controls the electric proportional multi-way valve 7 to close, and lift cylinder stops retracting.

[0058] In this embodiment, there are two telescopic cylinders 10, and the electric proportional multi-way valve 7 has a seventh working connection, the seventh working connection has a twelfth working oil port and a thirteenth working oil port, the twelfth working oil port is connected to the rod chambers of the two telescopic cylinders 10, and the thirteenth working oil port is connected to the rodless chambers of the two telescopic cylinders 10.

[0059] The telescopic circuit of this embodiment adopts a constant pressure variable pump 3+electric proportional multi-way valve 7+position proximity switch and travel switch to realize closed-loop control. The action process of the telescopic cylinder 10 is as follows:

[0060] The electric proportional multi-way valve 7 is operated to open, the telescopic oil cylinder 10 is extended, the iron roughneck pliers head moves forward, and after touching the first position proximity switch 31, the opening degree of the electric proportional multi-way valve 7 is automatically controlled to decrease, and the telescopic oil cylinder 10 slows down and extends. After the drill rod is extended to the center of the main back-up tongs, it touches the third stroke switch 32, and the electric proportional multi-way valve 7 is automatically controlled to close, and the telescopic oil cylinder 10 stops extending. When the telescopic oil cylinder 10 is retracted in the reverse direction, it is also quickly retracted first, decelerated after touching the second position proximity switch 34, and stopped after touching the fourth stroke switch 35.

[0061] Embodiment 2:

[0062] See also Figure 3 This embodiment provides another iron roughneck hydraulic system. On the basis of this embodiment 1, the hydraulic pump station of this embodiment specifically includes an oil tank 1 and a constant pressure variable pump 3. The constant pressure variable pump 3 is provided with a motor 2, the oil outlet of the oil tank 1 is connected to the oil inlet of the constant pressure variable pump 3, the oil outlet of the constant pressure variable pump 3 is connected to the main oil supply pipeline, and the main oil supply pipeline is divided into two branches, one of which is connected to the oil inlet of the electromagnetic reversing valve group 8, and the other branch is connected to the oil inlet of the electric proportional multi-way valve 7.

[0063] The oil return port of the oil tank 1 is connected to a main oil return pipeline, which is divided into two branches, one of which is connected to the oil outlet of the electromagnetic reversing valve group 8, and the other branch is connected to the oil outlet of the electric proportional multi-way valve 7.

[0064] The iron roughneck hydraulic system of this embodiment is driven by a motor 2, and is composed of a motor 2, a constant pressure variable pump 3, an electric proportional multi-way valve 7 and an electromagnetic reversing valve group 8 arranged in parallel, and an actuator to form a constant pressure variable hydraulic system. The output flow of the hydraulic pump drill matches the flow required by the actuator, which can reduce system heating and achieve energy saving. In addition, the electromagnetic reversing valve group 8 is cheaper than the electric proportional multi-way valve 7. The electromagnetic reversing valve group 8 is used to control the upper clamping cylinder 13, the lower clamping cylinder 14, the upper unclamping cylinder 15 and the spinner clamping cylinder 12, which can save the overall cost of the iron roughneck hydraulic system.

[0065] In this embodiment, the iron roughneck hydraulic system further includes an electric control unit and a handle. The electric control unit is electrically connected to the electric proportional multi-way valve 7 and the electromagnetic reversing valve group 8 respectively, so as to remotely control the electric proportional multi-way valve 7 and the electromagnetic reversing valve group 8; the handle is mechanically connected to the electric proportional multi-way valve 7 and the electromagnetic reversing valve group 8 respectively, so as to manually control the electric proportional multi-way valve 7 and the electromagnetic reversing valve group 8 in an emergency.

[0066] Furthermore, a pilot control on-off valve 4 is also provided on the main oil supply pipeline, and the pilot control on-off valve 4 includes a two-position two-way electromagnetic reversing valve 26 and a hydraulic control on-off valve 5, the oil inlet of the hydraulic control on-off valve 5 is connected to the oil outlet of the constant pressure variable pump 3, the oil outlet of the hydraulic control on-off valve 5 is connected to the main oil supply pipeline, the pilot control oil port of the hydraulic control on-off valve 5 is connected to the oil inlet of the two-position two-way electromagnetic reversing valve 26, and the oil outlet of the two-position two-way electromagnetic reversing valve 26 is connected to the main return oil pipeline.

[0067] The working process of the pilot control on-off valve 4 is as follows: when the two-position two-way solenoid reversing valve 2 6 loses power, the two-position two-way solenoid reversing valve 2 6 is closed, blocking the flow of hydraulic oil to the main return pipeline, and controlling the hydraulic control on-off valve 5 to close.

[0068] When the two-position two-way solenoid reversing valve 26 is energized, the two-position two-way solenoid reversing valve 26 opens, and the pilot control oil of the hydraulically controlled on-off valve 5 enters the main return pipeline through the two-position two-way solenoid reversing valve 26, thereby the valve core of the hydraulically controlled on-off valve 5 moves and switches to the open state. At this time, the hydraulic system for operating the iron roughneck will be activated, which can prevent the worker from accidentally touching the iron roughneck button and causing misoperation when the remote driller operates other drilling operations, thereby improving the safety of the equipment.

[0069] The rest of the same points as in Example 1 will not be repeated here.

[0070] In the description of the present invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0071] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0072] In the present invention, unless otherwise clearly specified and limited, when a first feature is “on” or “below” a second feature, it may be that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. Moreover, when a first feature is “above”, “above” or “above” a second feature, it may be that the first feature is directly above or obliquely above the second feature, or it may simply mean that the first feature is higher in level than the second feature. When a first feature is “below”, “below” or “below” a second feature, it may be that the first feature is directly below or obliquely below the second feature, or it may simply mean that the first feature is lower in level than the second feature.

[0073] In the description of this specification, the description of the terms "one embodiment", "some embodiments", "embodiment", "example", "specific example" or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, unless they are contradictory.

[0074] Although the embodiments of the present invention have been shown and described above, it is to be understood that the above embodiments are exemplary and are not to be construed as limitations of the present invention. A person skilled in the art may alter, modify, replace and modify the above embodiments within the scope of the present invention.

Claims

1. An iron roughneck hydraulic system, characterized in that: It comprises a hydraulic pump station, an electromagnetic reversing valve group (8), a pilot pressure reducing relief valve (17) and an actuator, wherein the actuator comprises two make-up and make-down oil cylinders (15) arranged in parallel; The oil supply port and the oil return port of the hydraulic pump station are connected to the corresponding oil ports of the electromagnetic reversing valve group (8) in a one-to-one correspondence. The electromagnetic reversing valve group (8) includes a first working joint, and the first working joint has a first working oil port and a second working oil port. The first working oil port is connected to the rodless chambers of the two make-up and make-up cylinders (15), and the rod chambers of the two make-up and make-up cylinders (15) are connected to the B port of the pilot pressure reducing relief valve (17). The T port of the pilot pressure reducing relief valve (17) is connected to the oil tank (1) of the hydraulic pump station, and the A port of the pilot pressure reducing relief valve (17) is connected to the second working oil port.

2. The iron roughneck hydraulic system of claim 1, wherein: The pilot pressure reducing relief valve (17) comprises a first check valve (18), a pressure reducing relief valve (19), a pilot relief valve (20) and a two-position two-way electromagnetic reversing valve (21); A first non-return valve (18) and a pressure reducing relief valve (19) are arranged in parallel between port A and port B. The first non-return valve (18) is unidirectionally connected in a direction from port B to port A. The oil inlet and oil outlet of the pressure reducing relief valve (19) are connected to port A and port B in a one-to-one correspondence. The control oil port of the pressure reducing relief valve (19) is connected to the oil inlet of the pilot relief valve (20) and the two-position two-way electromagnetic reversing valve (21) respectively. The oil drain port of the pressure reducing relief valve (19), the oil outlet of the pilot relief valve (20) and the oil outlet of the two-position two-way electromagnetic reversing valve (21) are all connected to port T.

3. The iron roughneck hydraulic system of claim 1, wherein: The iron roughneck hydraulic system further comprises a first bidirectional hydraulic lock (23) and a second bidirectional hydraulic lock (24), and the actuator further comprises an upper clamping cylinder (13) and a lower clamping cylinder (14); The electromagnetic reversing valve group (8) also includes a second working joint, the second working joint has a third working oil port and a fourth working oil port, the third working oil port is respectively connected to the rod chambers of the upper clamping oil cylinder (13) and the lower clamping oil cylinder (14), and the fourth working oil port is respectively connected to the rodless chambers of the upper clamping oil cylinder (13) and the lower clamping oil cylinder (14), and a first bidirectional hydraulic lock (23) is arranged between the upper clamping oil cylinder (13) and the second working joint to control the upper clamping oil cylinder (13) to remain in a stationary state under a load state, and a second bidirectional hydraulic lock (24) is arranged between the lower clamping oil cylinder (14) and the second working joint to control the lower clamping oil cylinder (14) to remain in a stationary state under a load state.

4. The iron roughneck hydraulic system of claim 3, wherein: The iron roughneck hydraulic system also includes an oil storage cylinder (16), a one-way throttle valve (25), a first hydraulically controlled one-way valve (26), a second one-way valve (27) and a third one-way valve (28); The electromagnetic reversing valve group (8) also includes a third working joint, the third working joint has a fifth working oil port, the fifth working oil port is connected to the rod chamber of the upper clamping oil cylinder (13), the rod chamber of the oil storage cylinder (16) is connected to the rodless chamber of the upper clamping oil cylinder (13), the rodless chamber of the oil storage cylinder (16) is connected to the first port of the one-way throttle valve (25), the second port of the one-way throttle valve (25) is divided into two branches, one of which is connected to the first port of the first hydraulically controlled one-way valve (26), the second port of the first hydraulically controlled one-way valve (26) is connected to the oil tank (1), and the other branch is connected to the fourth working oil port; The control port of the first hydraulically controlled one-way valve (26) is connected to the fifth working oil port, the second one-way valve (27) is arranged between the fifth working oil port and the rod chamber of the upper clamping cylinder (13) and is one-way from the fifth working oil port to the rod chamber of the upper clamping cylinder (13), and the third one-way valve (28) is arranged between the fourth working oil port and the second port of the one-way throttle valve (25) and is one-way from the fourth working oil port to the second port of the one-way throttle valve (25).

5. The iron roughneck hydraulic system of claim 3, wherein: The iron roughneck hydraulic system also includes an electric proportional multi-way valve (7) arranged in parallel with the electromagnetic reversing valve group (8), and the actuator also includes two parallel-connected spindle clamping cylinders (12) and four parallel-connected spindle motors (11); The electromagnetic reversing valve group (8) comprises a fourth working joint, the fourth working joint has a sixth working oil port and a seventh working oil port, the sixth working oil port is respectively connected to the rodless chambers of the two rotary clamping oil cylinders (12), and the seventh working oil port is respectively connected to the rod chambers of the two rotary clamping oil cylinders (12); The oil supply port and the oil return port of the hydraulic pump station are connected to the corresponding oil ports of the electric proportional multi-way valve (7) in a one-to-one correspondence. The electric proportional multi-way valve (7) has a fifth working joint, and the fifth working joint is respectively connected to each rotary motor (11), so that the hydraulic oil output by the hydraulic pump station enters each rotary motor (11) after being regulated by the fifth working joint, so as to control the rotation speed of each rotary motor (11).

6. The iron roughneck hydraulic system of claim 5, wherein: The fifth working joint has an eighth working oil port and a ninth working oil port, a secondary flow dividing and collecting valve (33) is arranged between the eighth working oil port and the first ports of the four rotary motors (11), and the second ports of the four rotary motors (11) are connected to the ninth working oil port.

7. The iron roughneck hydraulic system of claim 5, wherein: The actuator also includes a lifting cylinder (9); The electric proportional multi-way valve (7) has a sixth working joint, the sixth working joint has a tenth working oil port and an eleventh working oil port, the tenth working oil port is connected to the rodless chamber of the lifting cylinder (9), and the eleventh working oil port is connected to the rod chamber of the lifting cylinder (9).

8. The iron roughneck hydraulic system of claim 5, wherein: The actuator also includes two parallel telescopic cylinders (10); The electric proportional multi-way valve (7) has a seventh working joint, the seventh working joint has a twelfth working oil port and a thirteenth working oil port, the twelfth working oil port is respectively connected to the rod chambers of the two telescopic oil cylinders (10), and the thirteenth working oil port is respectively connected to the rodless chambers of the two telescopic oil cylinders (10).

9. The iron roughneck hydraulic system of claim 5, wherein: The hydraulic pump station also includes a constant pressure variable pump (3), the constant pressure variable pump (3) is provided with a motor (2), the oil outlet of the oil tank (1) is connected to the oil inlet of the constant pressure variable pump (3), the oil outlet of the constant pressure variable pump (3) is connected to a main oil supply pipeline, the main oil supply pipeline is divided into two branches, one branch is connected to the oil inlet of the electromagnetic reversing valve group (8), and the other branch is connected to the oil inlet of the electric proportional multi-way valve (7); The oil return port of the oil tank (1) is connected to a main oil return pipeline, which is divided into two branches, one of which is connected to the oil outlet of the electromagnetic reversing valve group (8), and the other is connected to the oil outlet of the electric proportional multi-way valve (7).

10. The iron roughneck hydraulic system of claim 9, wherein: A pilot control on-off valve (4) is also provided on the main oil supply pipeline, and the pilot control on-off valve (4) comprises a hydraulically controlled on-off valve (5) and a two-position two-way electromagnetic reversing valve (6); The oil inlet of the hydraulically controlled on-off valve (5) is connected to the oil outlet of the constant pressure variable pump (3), the oil outlet of the hydraulically controlled on-off valve (5) is connected to the main oil supply pipeline, the pilot control oil port of the hydraulically controlled on-off valve (5) is connected to the oil inlet of the second two-position two-way electromagnetic reversing valve (6), and the oil outlet of the second two-position two-way electromagnetic reversing valve (6) is connected to the main oil return pipeline.

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