Hydraulic energy storage auxiliary braking system of petroleum drilling machine

Abstract

The utility model discloses a hydraulic energy storage auxiliary braking system of a petroleum drilling machine, which comprises a winch drum, a hydraulic disc brake, a transmission device, a gear rack mechanism, a combined oil cylinder, a first two-position three-way electromagnetic valve, a second two-position three-way electromagnetic valve, a third two-position three-way electromagnetic valve, a hydraulic energy accumulator, an overflow valve and an oil tank, the combined oil cylinder is provided with a first oil cavity, a second oil cavity and a third oil cavity, seven different force gears are formed by the first oil cavity, the second oil cavity and the third oil cavity through different combination modes of high-pressure oil and low-pressure oil, and the requirement for weight change of a drill column during drilling operation is met. Most gravitational potential energy released by lowering the drill stem is converted into hydraulic energy which can be reused, and the purposes of controlling the drilling speed and avoiding energy waste are achieved. Different force gears are selected according to the change of the weight of the drill string to lower the drill string, so that the gravitational potential energy of the drill string is fully recovered, and the lowering speed of the drill string is well controlled.

Description

Technical Field

[0001] The utility model relates to the field of oil drilling equipment, and particularly relates to a hydraulic energy storage auxiliary brake system for an oil drilling rig. Background Art

[0002] Tripping out and tripping in are two common operations during oil drilling. When the drill bit is worn and needs to be replaced with a new one, the drill string of several kilometers needs to be lifted out of the well completely, which is called tripping out operation; after replacing the drill bit, the drill string is then lowered into the well, which is called tripping in operation. During the tripping in operation, the drill string releases the gravitational potential energy it stores, and this energy is quite large. For a heavy-duty drilling rig with a drill string weight exceeding 200 tons, the instantaneous power released during tripping in can reach 4000 kilowatts. In order to control the tripping in speed, oil drilling rigs generally use an auxiliary brake for continuous braking to absorb most of the gravitational potential energy released by the drill string, and finally use the main brake to complete the parking brake. The existing auxiliary brakes for oil drilling rigs mainly include water brakes, electromagnetic eddy current brakes, and Eaton brakes. In order to control the tripping in speed, these three types of auxiliary brakes convert most of the gravitational potential energy released by the drill string into heat energy and consume it, which not only causes waste of energy, but also requires an additional cooling system for heat dissipation. Summary of the Utility Model

[0003] In order to solve the above technical problems, the utility model provides a hydraulic energy storage auxiliary brake system for an oil drilling rig.

[0004] The technical solution adopted by the present utility model to solve the above technical problems is: a hydraulic energy storage auxiliary brake system for an oil drilling rig, including a winch drum, a hydraulic disc brake, a transmission device, a gear rack mechanism, and a combined oil cylinder. The transmission device includes a first gear, a second gear, a third gear, a fourth gear, a first shaft, a second shaft, and a third shaft. The first gear is fixedly installed on the first shaft, the second gear and the third gear are fixedly installed on the second shaft, the fourth gear is fixedly installed on the third shaft. The first gear meshes with the second gear, and the number of teeth of the first gear is less than that of the second gear. The third gear meshes with the fourth gear, and the number of teeth of the third gear is less than that of the fourth gear. One end of the shaft of the winch drum is connected to the first shaft through a first clutch, and the other end of the shaft of the winch drum is connected to the output shaft of a speed reducer through a second clutch. The input shaft of the speed reducer is connected to the shaft of a motor through a first coupling. A fifth gear is fixedly installed on the input shaft of the speed reducer, and a sixth gear is fixedly installed on the output shaft of the speed reducer. The fifth gear meshes with the sixth gear. The gear rack mechanism includes a seventh gear and a rack that mesh with each other. The shaft of the seventh gear is connected to the third shaft through a second coupling. The combined oil cylinder is composed of a plunger oil cylinder and a piston oil cylinder combined. The fixed plunger cylinder body and the plunger movably connected thereto form the plunger oil cylinder. The plunger, the piston rod, and the piston form the piston oil cylinder. The plunger also serves as the cylinder barrel of the piston oil cylinder. The plunger is movably connected to the piston installed therein. One end of the piston rod is fixedly installed at the end of the plunger cylinder body, and the other end is fixedly connected to the piston. The plunger is fixedly connected to the rack. The combined oil cylinder has three oil cavities, namely a first oil cavity, a second oil cavity, and a third oil cavity. The first oil cavity is connected to the A1 port of a first two-position three-way solenoid valve. The second oil cavity is connected to the A2 port of a second two-position three-way solenoid valve through the hollow oil passage of the piston rod and the piston. The third oil cavity is connected to the A3 port of a third two-position three-way solenoid valve through the hollow oil passage of the piston rod. The P1 port of the first two-position three-way solenoid valve, the P2 port of the second two-position three-way solenoid valve, the P3 port of the third two-position three-way solenoid valve, and the oil inlet of the overflow valve are all connected to the oil outlet of the hydraulic accumulator. The T1 port of the first two-position three-way solenoid valve, the T2 port of the second two-position three-way solenoid valve, the T3 port of the third two-position three-way solenoid valve, and the oil return port of the overflow valve are all connected to the oil tank. One end of a wire rope is wound around the winch drum, and the other end is fixed to the frame after passing around the crown block and the traveling block. The lower end of the traveling block is connected to the drill string.

[0005] Preferably, the number of teeth of the seventh gear is equal to the number of teeth of the first gear.

[0006] Compared with the prior art, the beneficial effects of the utility model are as follows:

[0007] (1) Most of the gravitational potential energy released when the drill string is lowered is converted into hydraulic energy that can be reused, which not only controls the lowering speed of the drill string, but also avoids waste of energy, and at the same time, there is no need to add an additional cooling system for heat dissipation.

[0008] (2) In order to meet the requirements of the change in the weight of the drill string during the drill string lowering operation, seven different force gears are used to lower the drill string. As the weight of the lowered drill string increases, higher and higher force gears are selected to lower the drill string. On the one hand, it can recover the gravitational potential energy of the drill string more fully, and on the other hand, it can better control the lowering speed of the drill string. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 is a schematic structural diagram of the utility model;

[0010] Figure 2 is a schematic diagram of the movement directions of each component during the drill string hoisting operation of the utility model.

[0011] Figure 3 is a schematic diagram of the movement directions of each component during the drill string lowering operation of the utility model.

[0012] In the figure: 1, drawworks drum; 2, hydraulic disc brake; 3, transmission device; 31, first gear; 32, second gear; 33, third gear; 34, fourth gear; 35, first shaft; 36, second shaft; 37, third shaft; 4, motor; 5, wire rope; 6, reducer; 61, fifth gear; 62, sixth gear; 7, plunger cylinder block; 8, plunger; 9, piston rod; 10, piston; 11, seventh gear; 12, rack; 13, hydraulic accumulator; 14, overflow valve; 15, crown block; 16, traveling block; 17, oil tank; 18, drill string; 19, first two-way three-way solenoid valve; 20, second two-way three-way solenoid valve; 21, third two-way three-way solenoid valve; 22, first coupling; 23, second coupling; 24, first clutch; 25, second clutch. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0013] The preferred embodiments of the utility model will be described in detail below with reference to the accompanying drawings.

[0014] See Figure 1, a hydraulic energy storage auxiliary braking system for an oil drilling rig, comprising a winch drum 1, a hydraulic disc brake 2, a transmission device 3, a rack and pinion mechanism and a combined oil cylinder. The transmission device 3 includes a first gear 31, a second gear 32, a third gear 33, a fourth gear 34, a first shaft 35, a second shaft 36 and a third shaft 37. The first gear 31 is fixedly installed on the first shaft 35, the second gear 32 and the third gear 33 are fixedly installed on the second shaft 36, the fourth gear 34 is fixedly installed on the third shaft 37. The first gear 31 meshes with the second gear 32, and the number of teeth of the first gear 31 is less than that of the second gear 32. The third gear 33 meshes with the fourth gear 34, and the number of teeth of the third gear 33 is less than that of the fourth gear 34. One end of the shaft of the winch drum 1 is connected to the first shaft 35 through a first clutch 24, and the other end of the shaft of the winch drum 1 is connected to the output shaft of a speed reducer 6 through a second clutch 25. The input shaft of the speed reducer 6 is connected to the shaft of a motor 4 through a first coupling 22. A fifth gear 61 is fixedly installed on the input shaft of the speed reducer 6, and a sixth gear 62 is fixedly installed on the output shaft of the speed reducer 6. The fifth gear 61 meshes with the sixth gear 62. The rack and pinion mechanism includes a seventh gear 11 and a rack 12 that mesh with each other. The shaft of the seventh gear 11 is connected to the third shaft 37 through a second coupling 23. The combined oil cylinder is composed of a plunger oil cylinder and a piston oil cylinder. A fixed plunger cylinder block 7 and a plunger 8 movably connected thereto form the plunger oil cylinder. The plunger 8, a piston rod 9 and a piston 10 form the piston oil cylinder. The plunger 8 also serves as the cylinder barrel of the piston oil cylinder. The plunger 8 is movably connected to the piston 10 installed therein. One end of the piston rod 9 is fixedly installed at the end of the plunger cylinder block 7, and the other end is fixedly connected to the piston 10. The plunger 8 is fixedly connected to the rack 12. The combined oil cylinder has three oil cavities, namely a first oil cavity Q1, a second oil cavity Q2 and a third oil cavity Q3. The first oil cavity Q1 is communicated with the A1 port of a first two-way three-way solenoid valve 19. The second oil cavity Q2 is communicated with the A2 port of a second two-way three-way solenoid valve 20 through the hollow oil passage of the piston rod 9 and the piston 10. The third oil cavity Q3 is communicated with the A3 port of a third two-way three-way solenoid valve 21 through the hollow oil passage of the piston rod 9. The P1 port of the first two-way three-way solenoid valve 19, the P2 port of the second two-way three-way solenoid valve 20, the P3 port of the third two-way three-way solenoid valve 21 and the oil inlet of an overflow valve 14 are all communicated with the oil outlet of a hydraulic accumulator 13. The T1 port of the first two-way three-way solenoid valve 19, the T2 port of the second two-way three-way solenoid valve 20, the T3 port of the third two-way three-way solenoid valve 21 and the oil return port of the overflow valve 14 are all communicated with a fuel tank 17. One end of a steel wire rope 5 is wound around the winch drum 1, and the other end is fixed to the frame after passing around a crown block 15 and a traveling block 16. A drill string 18 is connected to the lower end of the traveling block 16.

[0015] In this embodiment, the number of teeth of the seventh gear 11 is equal to the number of teeth of the first gear 31.

[0016] During the drill pipe pulling operation, the first clutch 24 is disengaged and the second clutch 25 is engaged. The motor 4 drives the drawworks drum 1 to rotate counterclockwise (viewed from the side opposite to the motor output shaft end) through the first coupling 22, the meshing fifth gear 61 and sixth gear 62, and the engaged second clutch 25, thereby winding the wire rope 5, and then hoisting the drill string 18 through the crown block 15 and traveling block 16. The movement directions of each component during the drill pipe pulling operation are as Figure 2 shown.

[0017] During the drill pipe running operation, the first clutch 24 is engaged, the second clutch 25 is disengaged, and the motor 4 is shut down. The hydraulic disc brake 2 is released, and the drill string 18 is lowered into the well under its own gravity. The gravity of the drill string 18 drives the drawworks drum 1 to rotate clockwise (viewed from the side opposite to the motor output shaft end) through the crown block 15, traveling block 16 and wire rope 5, and drives the seventh gear 11 to rotate clockwise after passing through the transmission device 3. The seventh gear 11 drives the rack 12 to drive the plunger 8 to move leftward, and the hydraulic oil in the combined oil cylinder is pressed into the hydraulic accumulator 13, that is, most of the gravitational potential energy released by the drill string 18 is converted into hydraulic energy in the hydraulic accumulator 13 and stored, realizing the energy recovery of the gravitational potential energy of the drill string 18. The movement directions of each component during the drill pipe running operation are as Figure 3 shown. Here, most of the gravitational potential energy released by the lowering of the drill string 18 is converted into hydraulic energy in the hydraulic accumulator 13, and the remaining part is converted into the kinetic energy of the lowering of the drill string 18, thus controlling the lowering speed of the drill string 18. Since no heat is generated during the conversion into hydraulic energy, there is no need to add an additional cooling system for heat dissipation. The recovered energy can be reused, such as for providing the energy to operate the hydraulic disc brake 2, driving the hydraulic tong to make up the connection, etc.

[0018] The several-thousand-meter drill string 18 used in oil drilling is connected by tool joints of more than twenty meters. During the drill pipe running operation, the weight of the lowered drill string 18 changes. At the beginning, the weight of the lowered drill string 18 is small, and as the tool joints are continuously connected and lowered into the well, the weight of the drill string 18 gradually increases. In order to meet the needs of the weight change of the drill string 18 in different stages of running the drill pipe, the present utility model adopts seven different force gears to lower the drill string 18. The first two-way three-way solenoid valve 19, the second two-way three-way solenoid valve 20 and the third two-way three-way solenoid valve 21 respectively control the first oil chamber Q1, the second oil chamber Q2 and the third oil chamber Q3 of the combined oil cylinder to communicate with high-pressure oil (hydraulic accumulator 13) or low-pressure oil (oil tank 17). Different combinations of the first oil chamber Q1, the second oil chamber Q2 and the third oil chamber Q3 communicating with high and low-pressure oils form seven different force gears, as shown in Table 1.

[0019] Table 1 Force gear table

[0020] Force gear First oil chamber Q1 Second oil chamber Q2 Third oil chamber Q3 Plunger force F 0 - - - 0 1 - + + P(A2 - A3) 2 - + - PA2 3 + - + P(A1 - A3) 4 + - - PA1 5 + + + P(A1 + A2 - A3) 6 + + - P(A1 + A2)

[0021] In the table: + indicates that this chamber is connected to high-pressure oil; - indicates that this chamber is connected to low-pressure oil; P indicates the oil pressure in the hydraulic accumulator 13; A1 indicates the oil pressure acting area of the first oil chamber Q1; A2 indicates the oil pressure acting area of the second oil chamber Q2; A3 indicates the oil pressure acting area of the third oil chamber Q3; the plunger force F is the force exerted by the oil pressure in the hydraulic accumulator 13 on the plunger 8 in this force range, with the direction to the right. From force range 0 to force range 6, the plunger force F increases successively.

[0022] When the force acting on the plunger 8 to the left due to the gravity of the drill string 18, which acts through the crown block 15, traveling block 16, wire rope 5, drawworks drum 1, transmission device 3 and the rack and pinion mechanism, is greater than the plunger force F in a certain force range, the plunger 8 will move to the left and pump a corresponding portion of the hydraulic oil into the hydraulic accumulator 13 for storage. At the beginning, the weight of the drill string 18 being lowered is small, and at this time, the drill string 18 can be lowered in force range 0, that is, the gravitational potential energy of the drill string 18 is not recovered. As the stands are continuously added, the weight of the drill string 18 gradually increases, and an appropriate force range can be selected to lower the drill string 18 to recover the gravitational potential energy of the drill string 18, and thus the lowering speed of the drill string 18 is also controlled. When the drill string 18 is lowered in force range 1, a part of the hydraulic oil in the second oil chamber Q2 is pumped into the third oil chamber Q3, and the remaining part is pumped into the hydraulic accumulator 13 for storage; when the drill string 18 is lowered in force range 2, all the hydraulic oil in the second oil chamber Q2 is pumped into the hydraulic accumulator 13 for storage; when the drill string 18 is lowered in force range 3, a part of the hydraulic oil in the first oil chamber Q1 is pumped into the third oil chamber Q3, and the remaining part is pumped into the hydraulic accumulator 13 for storage; when the drill string 18 is lowered in force range 4, all the hydraulic oil in the first oil chamber Q1 is pumped into the hydraulic accumulator 13 for storage; when the drill string 18 is lowered in force range 5, the hydraulic oil in the first oil chamber Q1 and the second oil chamber Q2 converges and a part of it is pumped into the third oil chamber Q3, and the remaining part is pumped into the hydraulic accumulator 13 for storage; when the drill string 18 is lowered in force range 6, the hydraulic oil in the first oil chamber Q1 and the second oil chamber Q2 converges and all of it is pumped into the hydraulic accumulator 13 for storage. Thus, it can be seen that as the weight of the drill string 18 being lowered continuously increases, a higher and higher force range is selected to lower the drill string 18. On the one hand, the gravitational potential energy of the drill string 18 can be recovered more fully, and on the other hand, the lowering speed of the drill string 18 can be better controlled. At the end of each drilling operation, the hydraulic disc brake 2 is used as the main brake to complete the parking brake. When the pressure of the hydraulic energy recovered in the hydraulic accumulator 13 reaches the limited maximum pressure, the relief valve 14 opens for overflow.

[0023] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A hydraulic energy storage auxiliary brake system for oil drilling rigs, characterized in that: The invention comprises a winch drum (1), a hydraulic disc brake (2), a transmission device (3), a gear rack mechanism and a combined oil cylinder, wherein the transmission device (3) comprises a first gear (31), a second gear (32), a third gear (33), a fourth gear (34), a first shaft (35), a second shaft (36) and a third shaft (37), wherein the first gear (31) is fixedly mounted on the first shaft (35), the second gear (32) and the third gear (33) are fixedly mounted on the second shaft (36), and the fourth gear (34) is fixedly mounted on the third shaft (37). On the shaft (37), the first gear (31) and the second gear (32) are meshed, the number of teeth of the first gear (31) is less than the number of teeth of the second gear (32), the third gear (33) and the fourth gear (34) are meshed, the number of teeth of the third gear (33) is less than the number of teeth of the fourth gear (34); one end of the shaft of the winch drum (1) is connected to the first shaft (35) through a first clutch (24), and the other end of the shaft of the winch drum (1) is connected to the output shaft of the reducer (6) through a second clutch (25). The input shaft of the reducer (6) is connected to the shaft of the motor (4) through a first coupling (22); a fifth gear (61) is fixedly mounted on the input shaft of the reducer (6); a sixth gear (62) is fixedly mounted on the output shaft of the reducer (6); the fifth gear (61) and the sixth gear (62) are meshed; the rack and pinion mechanism comprises a seventh gear (11) and a rack (12) meshed with each other; the shaft of the seventh gear (11) is connected to the third shaft (37) through a second coupling (23); the combined oil cylinder is composed of a A plunger cylinder and a piston cylinder are combined, wherein a fixed plunger cylinder body (7) and a plunger (8) movably connected thereto constitute the plunger cylinder, the plunger (8), a piston rod (9) and a piston (10) constitute the piston cylinder, the plunger (8) also serves as the cylinder barrel of the piston cylinder, the plunger (8) is movably connected to the piston (10) installed therein, one end of the piston rod (9) is fixedly mounted on the end of the plunger cylinder body (7), and the other end is fixedly connected to the piston (10), and the plunger (8) is fixedly connected to the rack (12);The combined oil cylinder comprises a first oil chamber (Q1), a second oil chamber (Q2) and a third oil chamber (Q3), the first oil chamber (Q1) being connected to the A1 port of the first two-position three-way solenoid valve, the second oil chamber (Q2) being connected to the A2 port of the second two-position three-way solenoid valve through the hollow oil passage of the piston rod (9) and the piston (10), the third oil chamber (Q3) being connected to the A3 port of the third two-position three-way solenoid valve through the hollow oil passage of the piston rod (9), the P1 port of the first two-position three-way solenoid valve and the P2 port of the second two-position three-way solenoid valve being connected to the A3 port of the third two-position three-way solenoid valve. The P2 port of the third two-position three-way solenoid valve, the P3 port of the third two-position three-way solenoid valve and the oil inlet of the overflow valve (14) are all connected to the oil delivery port of the hydraulic accumulator (13), and the T1 port of the first two-position three-way solenoid valve, the T2 port of the second two-position three-way solenoid valve, the T3 port of the third two-position three-way solenoid valve and the oil return port of the overflow valve (14) are all connected to the oil tank (17); one end of the wire rope (5) is wound around the winch drum (1), and the other end is fixed to the frame after passing through the crown block (15) and the traveling block (16), and the lower end of the traveling block (16) is connected to the drill string (18). ; 2. The oil drilling rig hydraulic energy storage auxiliary brake system according to claim 1 is characterized in that: The number of teeth of the seventh gear (11) is equal to the number of teeth of the first gear (31).

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