One-machine double-well mutual balancing mechanical-hydraulic combined type energy-saving oil pumping machine

Abstract

The invention relates to a one-machine double-well mutual balancing mechanical-hydraulic combined type energy-saving pumping unit which comprises a mechanical-hydraulic power system, a closed pipe heat dissipation system, a double-cylinder phase self-adjusting system, an execution system and a control system. A gear motor is adopted to drive a plurality of rows of chains to drive a piston of a double-rod power cylinder to reciprocate, mechanical energy is converted into hydraulic energy, and pressure oil is output to drive two oil well hydraulic cylinders and drive a sucker rod to reciprocate. Rod cavities of the two hydraulic cylinders are communicated, when one hydraulic cylinder is located at an upper dead center, the other hydraulic cylinder is located at a lower dead center, the gravity mutual balance relation of sucker rods of the two wells is formed, pressure oil only needs to overcome the friction of sucker rod columns of the two wells and the gravity of the oil columns, and the needed power is remarkably reduced. When phase deviation of the hydraulic cylinders is caused by leakage of pressure oil and the like, the positions of piston rods of the two hydraulic cylinders are adjusted through the double-cylinder phase self-adjusting system, the double-cylinder phase self-adjusting system works discontinuously, and the double-cylinder phase self-adjusting system operates with low power only when needed, so that the energy consumption is extremely low. The pumping unit has the advantages of being simple in structure, reliable in operation, high in efficiency, remarkable in energy conservation and the like.

Description

Technical Field

[0001] The invention belongs to the technical field of oil and natural gas extraction, and in particular relates to a mutually balanced machine-liquid composite energy-saving oil pumping unit with two wells. Background Art

[0002] Existing pumping units in oil fields are primarily beam pumping units. Due to their mechanical structure, even after leveling or counterweight optimization, the drive motor still experiences significant power fluctuations during operation, resulting in high overall energy consumption and limited energy savings. In recent years, hydraulically driven pumping units have gradually emerged. While they offer certain advantages in control accuracy and energy recovery, their application in oil fields is limited by the complex structure of the hydraulic system, high manufacturing costs, and a high failure rate.

[0003] Existing hydraulic pumping units typically use a hydraulic pump in conjunction with a reversing valve or proportional valve to control a hydraulic cylinder, driving the reciprocating motion of the pump's piston rod. These units require complex hydraulic valve systems, and frequent reversals in the hydraulic system can easily cause the oil to heat up, reducing the overall system efficiency. Complex hydraulic systems are also difficult to maintain and expensive to use. Some hydraulic pumping unit research proposes using accumulators to recover the gravitational potential energy generated by the pump's piston rod during its downward movement, releasing it during its upward movement. However, both the storage and release of pressure energy results in energy loss, making stable and efficient operation difficult due to the complex downhole operating conditions. These factors severely restrict the application and widespread adoption of hydraulic pumping units.

[0004] Existing pumping units generally operate in a single-well, stand-alone mode. This mode prevents the energy of adjacent wells from being effectively utilized in a complementary manner. The present invention proposes a novel, mutually balanced, hydraulic-hydraulic, energy-saving pumping unit with two adjacent wells. Because the well depths and pump hook depths of the two adjacent wells are similar, and the deadweight of the sucker rods is similar, liquid pressure transmission can be used to balance the deadweight of the two rods. When the sucker rod of one well moves upward, the other moves downward, maintaining a constant upward and downward rotation, thus achieving self-balancing gravity. After a period of operation, oil leakage can cause the piston rod of one cylinder to reach top dead center while the piston rod of the other cylinder has not reached bottom dead center, disrupting the mutually balanced phase relationship. To address this issue, the present invention incorporates a dual-cylinder phase self-adjustment system. Upon detecting a phase deviation, the system activates and actively corrects the position of the piston rods of the two cylinders, ensuring that the two cylinders always operate in a consistent, up-and-down phase sequence. This dual-cylinder phase self-adjustment system is idle most of the time, and the energy required for this process is extremely low. The one-machine, two-well, mutually balanced, hydraulic composite energy-saving pumping unit of the present invention significantly improves energy-saving effects, avoids the balancing work of conventional pumping units, circumvents the main problems of hydraulic pumping units, and has good application prospects. Summary of the Invention

[0005] The technical solution adopted by the present invention is a one-machine, two-well, mutually balanced, machine-hydraulic, composite energy-saving pumping unit, comprising a machine-hydraulic power system, a closed-tube heat dissipation system, a dual-cylinder phase self-adjustment system, an execution system, and a control system. The machine-hydraulic power system is connected to the execution system via main oil circuit A, main oil circuit B, and main oil circuit C to form a mutually balanced hydraulic main circuit. The closed-tube heat dissipation system is integrated into sections of the main oil circuits A, B, and C. The dual-cylinder phase self-adjustment system is connected in parallel to the mutually balanced hydraulic main circuit via phase oil circuit A and phase oil circuit B. The control system is electrically connected to each of the above-mentioned systems respectively. The hydraulic power system includes a motor, a sprocket, a multi-row chain, a tensioning device, a tensioning wheel, a displacement sensor A and a double-rod power cylinder, an electric stop valve A, an electric stop valve B, and an electric stop valve C. The motor output shaft is fixedly connected to the sprocket, and the sprocket is engaged with the multi-row chain for transmission. The multi-row chain passes around the tensioning wheel and is maintained in a tensioned state by the tensioning device. The two ends of the multi-row chain are respectively hinged to the ends of the piston rods on both sides of the double-rod power cylinder. The displacement sensor A is installed on the double-rod power cylinder; The execution system includes a left hydraulic cylinder, a right hydraulic cylinder, a displacement sensor B installed on the left hydraulic cylinder, and a displacement sensor C installed on the right hydraulic cylinder. The left hydraulic cylinder and the right hydraulic cylinder are respectively connected to the pumping rods of two oil wells; The left oil outlet of the double-rod power cylinder is connected to the rodless chamber of the left hydraulic cylinder through the main oil circuit A, and the right oil outlet of the double-rod power cylinder is connected to the rodless chamber of the right hydraulic cylinder through the main oil circuit C. The main oil circuit B directly connects the rod chambers of the left hydraulic cylinder and the right hydraulic cylinder.

[0006] According to the above scheme, the one-machine, two-well, mutually balanced machine-liquid composite energy-saving pumping unit is characterized in that the closed pipe heat dissipation system includes a closed oil pipe with heat dissipation fins and a temperature control device, and the closed oil pipe is connected to part of the pipe sections in the main oil circuit A, the main oil circuit B and the main oil circuit C.

[0007] According to the above scheme, the one-machine, two-well, mutually balanced machine-liquid composite energy-saving pumping unit is characterized in that the dual-cylinder phase self-adjustment system includes an oil tank, an oil filter, a hydraulic pump, a relief valve, an electromagnetic reversing valve, a hydraulic lock, an electric control valve A, and an electric control valve B. The oil inlet of the hydraulic pump is connected to the oil tank through an oil filter, and the oil outlet end of the hydraulic pump is divided into two paths, one path is connected to the oil inlet of the relief valve, and the other path is connected to the P port of the electromagnetic reversing valve. The return oil ports of the relief valve and the electromagnetic reversing valve are both connected to the oil tank, and the A port and B port of the electromagnetic reversing valve are respectively connected to the control port of the hydraulic lock, and the first working port of the hydraulic lock extends out of the phase oil circuit A, and the second working port extends out of the phase oil circuit B.

[0008] According to the above scheme, the one-machine, two-well, mutually balanced machine-liquid composite energy-saving pumping unit is characterized in that the phase oil circuit A is divided into two branches after being output from the first working port of the hydraulic lock, one branch is connected to the rodless chamber of the left liquid cylinder after passing through the electric control valve A, and the other branch is connected to the rod chamber of the right liquid cylinder. The phase oil circuit B is also divided into two branches after being output from the other working port of the hydraulic lock, one branch is connected to the rodless chamber of the right liquid cylinder after passing through the electric control valve B, and the other branch is connected to the rod chamber of the left liquid cylinder.

[0009] According to the above scheme, the one-machine, two-well, mutually balanced machine-liquid composite energy-saving oil pumping unit is characterized in that the electric stop valve A is arranged in series in the main oil circuit A, and is located between the left oil outlet of the double-rod power cylinder and the rodless cavity of the left liquid cylinder; the electric stop valve B is arranged in series in the main oil circuit B, and is located between the rod cavity of the left liquid cylinder and the rod cavity of the right liquid cylinder; the electric stop valve C is arranged in series in the main oil circuit C, and is located between the right oil outlet of the double-rod power cylinder and the rodless cavity of the right liquid cylinder.

[0010] According to the above scheme, the one-machine, two-well, mutually balanced machine-liquid composite energy-saving oil pumping unit is characterized in that the control system includes a programmable controller, the signal input end of the programmable controller is respectively connected to the signal output end of the displacement sensor A, the displacement sensor B and the displacement sensor C, and the control output end of the programmable controller is connected to the drive circuit of the motor, the temperature control device in the closed tube heat dissipation system, the electromagnetic reversing valve, the electric stop valve A, the electric stop valve B, the electric stop valve C, the electric control valve A and the electric control valve B.

[0011] Compared with the prior art, the present invention has the following beneficial effects: 1. A motor drives multiple chains that drive a dual-rod power cylinder, converting mechanical energy into hydraulic pressure. This pressure is then transmitted to the left and right hydraulic cylinders via the main oil circuit, completing the mechanical-hydraulic energy conversion. Compared to traditional hydraulic pumping units that rely on a hydraulic pump for driving power, this new system no longer relies on a hydraulic pump to drive the cylinders. Instead, it achieves power exchange through pressurized oil transfer between the two cylinders. This results in a simple structure and high reliability, significantly reducing leakage, volume loss, heat generation, and wear in the hydraulic system, thereby improving operational efficiency and reducing maintenance costs.

[0012] 2. The use of closed oil pipelines effectively prevents external oil contamination from affecting system stability. During each hydraulic cycle, the pressurized oil is forced to cool through closed oil pipes with cooling fins and fans, which helps achieve continuous and efficient heat exchange and cooling, ensuring the long-term stable operation of the pumping unit.

[0013] 3. The dual-bar phase self-adjustment system is activated only when there is a phase deviation in the hydraulic cylinders. That is, when the piston rod of one hydraulic cylinder is at the top dead center, the piston rod of the other hydraulic cylinder is not at the bottom dead center. At this time, the positions of the piston rods of the two hydraulic cylinders are adjusted so that the piston rods of the two hydraulic cylinders are respectively at the top dead center and the bottom dead center. The system operates at a lower power and has extremely low energy consumption.

[0014] 4. The rod chambers of the left and right hydraulic cylinders are connected by a main oil circuit. During the pumping process, the piston rod of one hydraulic cylinder descends to discharge oil, while the piston rod of the other hydraulic cylinder ascends to absorb oil, forming a gravity-balanced relationship between the sucker rods of the two wells, effectively reducing drive energy consumption and improving overall system efficiency. It is suitable for dual-well collaborative operation scenarios with similar downhole load conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a working principle diagram of the present invention.

[0016] Figure 2 It is a schematic diagram of the overall layout of the present invention.

[0017] In the figure: 1- hydraulic power system, 101- motor, 102- sprocket, 103- multi-row chain, 104- tensioning device, 105- tensioning pulley, 106- displacement sensor A, 107- double-rod power cylinder, 108- electric stop valve A, 109- electric stop valve B, 110- electric stop valve C, 2- closed pipe cooling system, 3- double cylinder phase self-adjusting system, 301- oil tank, 302- oil filter, 303- hydraulic Pump, 304-overflow valve, 305-electromagnetic reversing valve, 306-hydraulic lock, 307-electric control valve A, 308-electric control valve B, 4-execution system, 401-left hydraulic cylinder, 402-right hydraulic cylinder, 403-displacement sensor B, 404-displacement sensor C, 5-control system, 601-main oil circuit A, 602-main oil circuit B, 603-main oil circuit C, 604-phase oil circuit A, 605-phase oil circuit B. DETAILED DESCRIPTION

[0018] The following will clearly and completely describe the technical solution of the present invention in conjunction with the accompanying drawings. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0019] The present invention is further described below with reference to the accompanying drawings and embodiments.

[0020] Reference Figure 1 、 Figure 2As shown, the present invention includes a machine-hydraulic power system 1, a closed-tube heat dissipation system 2, a dual-cylinder phase self-adjustment system 3, an execution system 4, and a control system 5. The machine-hydraulic power system 1 is connected to the execution system 4 via the main oil circuit A601, the main oil circuit B602, and the main oil circuit C603 to form a mutually balanced hydraulic main circuit. The closed-tube heat dissipation system 2 is integrated into a portion of the pipe sections in the main oil circuits A601, B602, and C603. The dual-cylinder phase self-adjustment system 3 is connected in parallel to the mutually balanced hydraulic main circuit via the phase oil circuit A604 and the phase oil circuit B605. The control system 5 is electrically connected to each of the above systems to monitor the operating status of the entire machine and output control instructions to each system. The hydraulic power system 1 includes a motor 101, a sprocket 102, a multi-row chain 103, a tensioning device 104, a tensioning wheel 105, a displacement sensor A106 and a double-rod power cylinder 107, an electric stop valve A108, an electric stop valve B109, and an electric stop valve C110. The output shaft of the motor 101 is fixedly connected to the sprocket 102, and the sprocket 102 is engaged with the multi-row chain 103 for transmission. The multi-row chain 103 passes around the tensioning wheel 105 and is maintained in a tensioned state by the tensioning device 104. The two ends of the multi-row chain 103 are respectively hinged to the ends of the piston rods on both sides of the double-rod power cylinder 107, and the displacement sensor A106 is installed on the double-rod power cylinder 107. The displacement sensor A106 is used to collect piston stroke data of the dual-rod power cylinder 107. When the motor 101 drives the multi-row chain 103 through the sprocket 102, the multi-row chain 103 drives the piston of the dual-rod power cylinder 107 to move back and forth, thereby converting the mechanical energy output by the motor 101 into hydraulic energy. The execution system 4 includes a left hydraulic cylinder 401, a right hydraulic cylinder 402, a displacement sensor B403 installed on the left hydraulic cylinder 401, and a displacement sensor C404 installed on the right hydraulic cylinder 402. The left hydraulic cylinder 401 and the right hydraulic cylinder 402 are respectively connected to the pumping rods of the two oil wells; The left oil outlet of the double-rod power cylinder 107 is connected to the rodless chamber of the left cylinder 401 through the main oil circuit A601, and the right oil outlet of the double-rod power cylinder 107 is connected to the rodless chamber of the right cylinder 402 through the main oil circuit C603. The main oil circuit B602 directly connects the rod chambers of the left cylinder 401 and the right cylinder 402. When any cylinder is in a downstroke, the hydraulic oil discharged by it is guided to the rod chamber of the other cylinder through the main oil circuit B602, thereby prompting the piston rod of the cylinder to move upward, thereby forming a two-way transmission path of hydraulic energy between the two cylinders.

[0021] Motor 101 drives the pistons of dual-rod power cylinder 107 reciprocatingly via sprocket 102 and multiple chains 103. Dual-rod power cylinder 107 is hydraulically connected to left and right hydraulic cylinders 401 and 402 via main oil lines A601, B602, and C603, forming a hydraulic cylinder linkage mechanism that drives each other. This hydraulic connection, driven by motor 101, converts mechanical energy into hydraulic energy, and, through actuator system 4, achieves mutually balanced pumping operations between the two wells.

[0022] Furthermore, the closed tube heat dissipation system 2 includes a closed oil pipe with heat dissipation fins and a temperature control device. The closed oil pipe is connected to partial pipe sections in the main oil circuit A601, the main oil circuit B602 and the main oil circuit C603 to achieve heat exchange and cooling of the pressurized oil during the circulation process of the main oil circuit.

[0023] The temperature control device includes a temperature sensor and a fan drive module. When the oil temperature exceeds a set threshold, the control system 5 activates the fan to force air cooling of the main oil lines A601, B602, and C603, which have integrated cooling fins. This achieves efficient heat exchange, effectively prevents oil contamination, and ensures the long-term stable operation of the pumping unit.

[0024] Furthermore, the dual-cylinder phase self-adjustment system 3 includes an oil tank 301, an oil filter 302, a hydraulic pump 303, a relief valve 304, an electromagnetic reversing valve 305, a hydraulic lock 306, an electric control valve A307, and an electric control valve B308. The oil inlet of the hydraulic pump 303 is connected to the oil tank 301 through the oil filter 302. The oil outlet end of the hydraulic pump 303 is divided into two paths, one path is connected to the oil inlet of the relief valve 304, and the other path is connected to the P port of the electromagnetic reversing valve 305. The return oil ports of the relief valve 304 and the electromagnetic reversing valve 305 are both connected to the oil tank 301. The A port and the B port of the electromagnetic reversing valve 305 are respectively connected to the control port of the hydraulic lock 306. The first working port of the hydraulic lock 306 extends out of the phase oil circuit A604, and the second working port extends out of the phase oil circuit B605.

[0025] The phase oil circuit A604 is divided into two branches after being output from the first working port of the hydraulic lock 306, one of which is connected to the rodless chamber of the left cylinder 401 after passing through the electric control valve A307, and the other is connected to the rod chamber of the right cylinder 402. The phase oil circuit B605 is also divided into two branches after being output from the other working port of the hydraulic lock 306, one of which is connected to the rodless chamber of the right cylinder 402 after passing through the electric control valve B308, and the other is connected to the rod chamber of the left cylinder 401.

[0026] Furthermore, the electric stop valve A108 is arranged in series in the main oil circuit A601, and is located between the left oil outlet of the double-rod power cylinder 107 and the rodless cavity of the left liquid cylinder 401; the electric stop valve B109 is arranged in series in the main oil circuit B602, and is located between the rod cavity of the left liquid cylinder 401 and the rod cavity of the right liquid cylinder 402; the electric stop valve C110 is arranged in series in the main oil circuit C603, and is located between the right oil outlet of the double-rod power cylinder 107 and the rodless cavity of the right liquid cylinder 402; when the displacement sensor B403 and the displacement sensor C404 detect a phase deviation, the electric stop valve A108, the electric stop valve B109, and the electric stop valve C110 are set to block the oil flow of the corresponding main oil circuit in the closed state, thereby realizing the isolation of the hydraulic main circuit in the phase adjustment mode, so that the double-cylinder phase self-adjustment system 3 can be compensated and adjusted through the phase oil circuit A604 and the phase oil circuit B605.

[0027] The displacement sensor A106 is installed on the double-rod power cylinder 107 to collect piston stroke data, the displacement sensor B403 is installed on the left hydraulic cylinder 401, and the displacement sensor C404 is installed on the right hydraulic cylinder 402, respectively used to detect the displacement data of the piston rods of the two hydraulic cylinders.

[0028] Furthermore, the control system 5 includes a programmable controller, the signal input end of the programmable controller is respectively connected to the signal output end of the displacement sensor A106, the displacement sensor B403 and the displacement sensor C404, and the control output end of the programmable controller is connected to the drive circuit of the motor 101, the temperature control device in the closed tube heat dissipation system 2, the electromagnetic reversing valve 305, the electric stop valve A108, the electric stop valve B109, the electric stop valve C110, the electric control valve A307 and the electric control valve B308.

[0029] The following describes a one-time use process of the present invention in conjunction with the accompanying drawings: The displacement sensor A106 is installed on the double-rod power cylinder 107 and is used to detect the piston stroke position. Its output signal can be used to set the lower limit of the stroke of the piston rod of the left hydraulic cylinder 401 and the upper limit of the stroke of the piston rod of the right hydraulic cylinder 402, as well as the upper limit of the stroke of the left hydraulic cylinder 401 and the lower limit of the stroke of the right hydraulic cylinder 402, as the basis for the control system 5 to determine the stroke of the whole machine reversal.

[0030] Furthermore, the control system 5 controls the motor 101 to switch the rotation direction and drive the piston of the double-rod power cylinder 107 to move in the opposite direction based on the stroke signal fed back by the displacement sensor A106, when it detects that the piston of the double-rod power cylinder 107 moves to the set left stroke limit or right stroke limit, thereby realizing continuous reciprocating motion.

[0031] When the equipment is in normal working condition, the electric stop valve A108, electric stop valve B109 and electric stop valve C110 remain in the open state, and the electric control valve A307 and electric control valve B308 are in the closed state to ensure that the mutually balanced hydraulic main circuit is unobstructed.

[0032] Furthermore, when the mutually balanced, mechanical-hydraulic, energy-saving pumping unit is operating, control system 5 outputs a control command, causing motor 101 to rotate counterclockwise, driving multi-row chains 103 to pull the piston of dual-rod power cylinder 107 rightward. The left piston rod retracts into the cylinder, reducing the volume of the right oil chamber and discharging pressurized oil into main oil circuit C603. After cooling through closed-tube heat dissipation system 2, this pressurized oil enters the rodless chamber of right hydraulic cylinder 402, pushing the piston rod of right hydraulic cylinder 402 downward.

[0033] The downward movement of the piston rod of right hydraulic cylinder 402 reduces the volume of its rod chamber, discharging pressurized oil into main oil circuit B602. This pressurized oil passes through closed-tube cooling system 2 and electric shutoff valve B109 before entering the rod chamber of left hydraulic cylinder 401, pushing its piston rod upward. The upward movement of the piston rod of left hydraulic cylinder 401 reduces the volume of its rodless chamber, discharging pressurized oil into main oil circuit A601 and flowing back into the left oil chamber of dual-rod power cylinder 107.

[0034] Furthermore, the control system 5 controls the motor 101 to rotate according to the set stroke requirements in accordance with the above process, so that the downward power of the piston rod of the right hydraulic cylinder 402 is converted into the upward force of the piston rod of the left hydraulic cylinder 401, so that when the piston rod of the right hydraulic cylinder 402 is at the bottom dead center, the piston rod of the left hydraulic cylinder 401 is synchronously at the top dead center, forming a mutually balanced phase relationship.

[0035] When the piston of the double-rod power cylinder 107 moves to the right stroke limit, the displacement sensor A106 senses a signal, and the control system 5 instructs the motor 101 to switch to clockwise operation. The multi-row chain 103 drives the piston to move to the left, forming a reverse movement of the above process. The pressure oil discharged from the left side of the double-rod power cylinder 107 drives the left liquid cylinder 401 downward, and the pressure oil discharged from the rod chamber of the left liquid cylinder 401 drives the right liquid cylinder 402 upward.

[0036] This process is repeated and the whole machine starts to work in a cycle.

[0037] During the circulation operation, due to factors such as oil leakage, gas mixing or unbalanced load on the two wells, the piston rods of the left cylinder 401 and the right cylinder 402 may become out of sync, destroying the original mutually balanced phase relationship, that is, it is impossible to achieve the expected state that the piston rod of one cylinder is at the bottom dead center when the piston rod of the other cylinder is at the top dead center, thereby affecting the oil production efficiency and system stability.

[0038] Control system 5 collects real-time piston rod position signals from displacement sensors B403 and C404 for the left and right cylinders 401 and 402, respectively. Based on the preset symmetrical motion patterns, it determines whether there is a phase deviation. Phase deviation occurs when one cylinder is at its top dead center while the other is below its bottom dead center, disrupting the mutually balanced phase relationship. Phase deviation is determined to exist if the distance between one cylinder and its bottom dead center exceeds a set threshold. If a phase deviation is detected outside the allowable range, control system 5 automatically activates dual-cylinder phase self-adjustment system 3 to correct it. The adjustment process is as follows.

[0039] First, the control system 5 instructs the motor 101 to stop running, and at the same time closes the electric stop valve A108, the electric stop valve B109 and the electric stop valve C110 to isolate the mutually balanced hydraulic main circuits of the hydraulic power system 1 and the execution system 4.

[0040] Based on the real-time position signals fed back by displacement sensors B403 and C404, control system 5 calculates the displacement difference between the piston rods of the two cylinders and their upper and lower dead centers. If it detects that the piston rod of left cylinder 401 is lagging while the piston rod of right cylinder 402 is normal (i.e., the piston rod of right cylinder 402 has reached the top dead center while the piston rod of left cylinder 401 has not reached the bottom dead center), the system enters the single-cylinder adjustment phase. It then starts hydraulic pump 303 and switches solenoid reversing valve 305 to the left position, outputting pressurized oil to hydraulic lock 306 to unlock it. This opens electric control valve A307, while electric control valve B308 remains closed.

[0041] At this point, the pressure oil output by hydraulic pump 303 enters phase oil circuit A604 through the unlocked hydraulic lock 306, then passes through electric control valve A307 and into the rodless chamber of left cylinder 401, pushing its piston rod downward. Simultaneously, the pressure oil discharged from the rod chamber of left cylinder 401 passes through phase oil circuit B605, passes through hydraulic lock 306, and returns to oil tank 301.

[0042] If it is detected that the piston rod of the left cylinder 401 is normal and the piston rod of the right cylinder 402 is lagging, that is, the piston rod of the left cylinder 401 reaches the top dead center and the piston rod of the right cylinder 402 does not reach the bottom dead center, the hydraulic pump 303 is started and the electromagnetic reversing valve 305 is switched to the right position.

[0043] Electric control valve A307 remains closed, while electric control valve B308 opens. The pressurized oil output by hydraulic pump 303 now flows through the unlocked hydraulic lock 306 into phase oil circuit B605, then through electric control valve B308 into the rodless chamber of right cylinder 402, pushing its piston rod downward. Simultaneously, the pressurized oil discharged from the rod chamber of right cylinder 402 flows through phase oil circuit A604, passes through hydraulic lock 306, and returns to oil tank 301.

[0044] Throughout the adjustment process, displacement sensors B403 and C404 continuously monitor the positions of the two cylinder piston rods in real time. When one cylinder's piston rod is detected at its top dead center and the other at its bottom dead center, and the displacement difference between the two cylinder piston rods and the preset top and bottom dead centers is less than a preset threshold, the phase deviation adjustment is determined to be complete. Control system 5 then closes electric control valves A307 and B308, returns solenoid reversing valve 305 to its neutral position, resets hydraulic lock 306, and simultaneously shuts off hydraulic pump 303. Electric shut-off valves A108, B109, and C110 are reopened, and control system 5 instructs motor 101 to restart, restoring the system to its normal, mutually balanced operating state.

[0045] For the convenience of description, the relative position relationship of each component in the present invention is described based on the Figure 1 The layout is described in detail, such as the front, back, left, right, top, bottom, and middle positions are based on the instructions in the attached diagram. Figure 1 The layout of the drawings is determined only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the devices or components referred to must have a specific orientation, be constructed and operate in a specific orientation. Therefore, it should not be understood as limiting the present invention. In the present invention, unless otherwise expressly specified or limited, terms such as "mounted," "connected," "connect," and "fixed" should be understood broadly. For example, they may refer to fixed connection, detachable connection, or integration; they may refer to direct connection or indirect connection through an intermediate medium; they may refer to internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

Claims

1. A mutually balanced machine-liquid composite energy-saving pumping unit with two wells, characterized by: The invention comprises a machine-hydraulic power system (1), a closed-tube heat dissipation system (2), a dual-cylinder phase self-adjustment system (3), an execution system (4) and a control system (5), wherein the machine-hydraulic power system (1) is connected to the execution system (4) via a main oil circuit A (601), a main oil circuit B (602) and a main oil circuit C (603) to form a mutually balanced hydraulic main circuit, the closed-tube heat dissipation system (2) is integrated into a portion of the pipe sections in the main oil circuit A (601), the main oil circuit B (602) and the main oil circuit C (603), the dual-cylinder phase self-adjustment system (3) is connected in parallel to the mutually balanced hydraulic main circuit via a phase oil circuit A (604) and a phase oil circuit B (605), and the control system (5) is electrically connected to each of the above systems respectively; The hydraulic power system (1) comprises a motor (101), a sprocket (102), a multi-row chain (103), a tensioning device (104), a tensioning wheel (105), a displacement sensor A (106), a double-rod power cylinder (107), an electric stop valve A (108), an electric stop valve B (109), and an electric stop valve C (110). The output shaft of the motor (101) is fixedly connected to the sprocket (102). The sprocket (102) is meshed with the multi-row chain (103) for transmission. The multi-row chain (103) passes around the tensioning wheel (105) and is maintained in a tensioned state by the tensioning device (104). The two ends of the multi-row chain (103) are respectively hinged to the ends of the piston rods on both sides of the double-rod power cylinder (107). The displacement sensor A (106) is installed on the double-rod power cylinder (107). The execution system (4) includes a left hydraulic cylinder (401), a right hydraulic cylinder (402), a displacement sensor B (403) installed on the left hydraulic cylinder (401), and a displacement sensor C (404) installed on the right hydraulic cylinder (402). The left hydraulic cylinder (401) and the right hydraulic cylinder (402) are respectively connected to the pumping rods of two oil wells; The left oil outlet of the double-rod power cylinder (107) is connected to the rodless chamber of the left liquid cylinder (401) through the main oil circuit A (601), the right oil outlet of the double-rod power cylinder (107) is connected to the rodless chamber of the right liquid cylinder (402) through the main oil circuit C (603), and the main oil circuit B (602) directly connects the rod chambers of the left liquid cylinder (401) and the right liquid cylinder (402).

2. The energy-saving pumping unit with two wells and mutual balance of machine and fluid according to claim 1 is characterized in that: The closed tube heat dissipation system (2) comprises a closed oil tube with heat dissipation fins and a temperature control device, wherein the closed oil tube is connected to a portion of the pipe sections in the main oil circuit A (601), the main oil circuit B (602) and the main oil circuit C (603).

3. The energy-saving pumping unit with two wells and mutual balance of machine and fluid according to claim 1 is characterized in that: The dual-cylinder phase self-adjusting system (3) comprises an oil tank (301), an oil filter (302), a hydraulic pump (303), an overflow valve (304), an electromagnetic reversing valve (305), a hydraulic lock (306), an electric control valve A (307), and an electric control valve B (308). The oil inlet of the hydraulic pump (303) is connected to the oil tank (301) through the oil filter (302). The oil outlet of the hydraulic pump (303) is divided into two paths, one of which is connected to the oil outlet of the hydraulic pump (303). The oil inlet of the relief valve (304) is connected to the P port of the electromagnetic reversing valve (305) through another path. The oil return ports of the relief valve (304) and the electromagnetic reversing valve (305) are both connected to the oil tank (301). The A port and the B port of the electromagnetic reversing valve (305) are respectively connected to the control port of the hydraulic lock (306). The first working port of the hydraulic lock (306) extends to the phase oil circuit A (604), and the second working port extends to the phase oil circuit B (605).

4. The energy-saving pumping unit with two wells and mutual balance of machine and fluid according to claim 3 is characterized in that: The phase oil circuit A (604) is divided into two branches after being output from the first working port of the hydraulic lock (306), one of which is connected to the rodless chamber of the left hydraulic cylinder (401) after passing through the electric control valve A (307), and the other is connected to the rod chamber of the right hydraulic cylinder (402). The phase oil circuit B (605) is also divided into two branches after being output from the other working port of the hydraulic lock (306), one of which is connected to the rodless chamber of the right hydraulic cylinder (402) after passing through the electric control valve B (308), and the other is connected to the rod chamber of the left hydraulic cylinder (401).

5. The energy-saving pumping unit with two wells and mutual balance of machine and fluid according to claim 1 is characterized in that: The electric stop valve A (108) is arranged in series in the main oil circuit A (601) and is located between the left oil outlet of the double-rod power cylinder (107) and the rodless chamber of the left liquid cylinder (401). The electric stop valve B (109) is arranged in series in the main oil circuit B (602) and is located between the rod chamber of the left liquid cylinder (401) and the rod chamber of the right liquid cylinder (402). The electric stop valve C (110) is arranged in series in the main oil circuit C (603) and is located between the right oil outlet of the double-rod power cylinder (107) and the rodless chamber of the right liquid cylinder (402).

6. The energy-saving pumping unit with two wells and mutual balance of machine and fluid according to claim 1 is characterized in that: The control system (5) includes a programmable controller, wherein a signal input end of the programmable controller is connected to the signal output ends of the displacement sensor A (106), the displacement sensor B (403) and the displacement sensor C (404), respectively, and a control output end of the programmable controller is connected to the drive circuit of the motor (101), the temperature control device in the closed tube heat dissipation system (2), the electromagnetic reversing valve (305), the electric stop valve A (108), the electric stop valve B (109), the electric stop valve C (110), the electric control valve A (307) and the electric control valve B (308).

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