Integrated hydraulic transmission control method and device based on magnetic drive

Abstract

The invention provides a control method and device for integrated hydraulic transmission based on magnetic drive, and belongs to the field of mechanical automation. The method comprises the steps that the fixed oil outlet displacement of a reversing pump of the integrated hydraulic transmission device and the sectional area of a hydraulic oil cylinder are obtained, the expected oil outlet cylinder displacement of the hydraulic oil cylinder and the expected time from the actual oil outlet cylinder displacement to the expected oil outlet cylinder displacement are input through an upper computer, and the speed of a motor is adjusted. The device comprises a driving part, a reversing pump, an oil cylinder and a magnetic part, a reversing channel is arranged in the reversing pump, the driving part is in driving connection with the reversing pump, the reversing pump is fixed to the end of the oil cylinder, and the reversing channel is communicated with the oil cylinder. According to the integrated hydraulic transmission device, operation of the motor can be adjusted in real time according to requirements, then transmission oil outlet or oil return with the reversing pump is precisely controlled, efficient, high-precision and intelligently-controlled hydraulic power output can be achieved, and the integrated hydraulic transmission device is suitable for precise linear driving operation in the high-cleanliness, anti-explosion and corrosive environment.

Description

Technical Field

[0001] The present invention belongs to the technical field of mechanical automation and relates to a control method and a device for an integrated hydraulic transmission based on magnetic drive. Background Art

[0002] Traditional hydraulic pump station cylinder systems typically consist of components such as a drive (such as a motor or engine), a hydraulic pump, a cylinder, valves, and piping. These components are numerous, bulky, and complex to maintain. Furthermore, cylinder control suffers from slow response and low precision. Traditional hydraulic pump station cylinder systems involve numerous external piping connections, which not only complicates installation and maintenance but also easily leads to leaks, impacting system reliability and service life. Therefore, integrating the hydraulic pump station cylinder system and providing new drive control methods are urgently needed. Summary of the Invention

[0003] The purpose of the present invention is to address the above-mentioned problems in the existing technology and to propose a control method for an integrated hydraulic transmission based on magnetic drive.

[0004] The object of the present invention can be achieved by the following technical solutions: A control method of an integrated hydraulic transmission based on magnetic drive, comprising:

[0005] Acquiring parameter data of the integrated hydraulic transmission device, wherein the parameter data includes a fixed oil output of a reversing pump and a cross-sectional area of ​​a hydraulic cylinder;

[0006] Inputting the expected displacement of the hydraulic cylinder and the expected time from the actual displacement to the expected displacement through the host computer;

[0007] Calculating the theoretical number of motor revolutions according to the difference between the expected oil cylinder displacement and the actual oil cylinder displacement, the fixed oil output displacement of the reversing pump, and the cross-sectional area of ​​the hydraulic cylinder;

[0008] Calculating the theoretical speed of the motor according to the theoretical number of revolutions of the motor and the expected time, and adjusting the speed of the motor according to the theoretical speed of the motor;

[0009] In the process of adjusting the speed of the motor to the theoretical speed of the motor, the oil outlet displacement of the hydraulic cylinder is driven by magnetic force, and the number of motor revolutions is counted by the Hall sensor. When the number of motor revolutions is the theoretical number of motor revolutions and the motor speed is the theoretical speed of the motor, the actual oil outlet displacement of the hydraulic cylinder is equal to the expected oil outlet displacement.

[0010] As an optional embodiment of the present invention, when counting the number of revolutions of the motor by a Hall sensor, the method further includes:

[0011] Get real-time power data of integrated hydraulic transmissions;

[0012] Calculating the motor consumption torque based on the real-time power data and the motor operating speed;

[0013] Corresponding protective measures are taken according to whether the motor consumption torque is within a preset consumption torque range.

[0014] As an optional embodiment of the present invention, performing corresponding protection measures according to whether the motor consumption torque is within a preset consumption torque range includes:

[0015] When the motor consumption torque is within the preset consumption torque range, the motor keeps running;

[0016] When the motor consumption torque is higher than the maximum consumption torque of the preset consumption torque range, a gradual speed change measure is adopted for the motor;

[0017] When the motor consumption torque is less than the minimum consumption torque in the preset consumption torque range, the motor is controlled to stop running through a first level signal.

[0018] As an optional implementation scheme of the present invention, when the difference is a negative number, the motor is controlled to reverse by a second level signal to change the direction of displacement of the oil cylinder.

[0019] As an optional implementation scheme of the present invention, the transmission ratio between the motor and the pump shaft of the reversing pump is 1:1.

[0020] As an optional embodiment of the present invention, when the motor consumption torque is higher than the maximum consumption torque of the preset consumption torque range, a gradual speed change measure is adopted for the motor, including:

[0021] Acquire motor temperature data, determine the motor temperature change rate based on the motor temperature data, and determine that the motor temperature change rate is abnormal if the motor temperature change rate is greater than a preset temperature change rate range;

[0022] Acquiring motor starting speed data, and determining that motor starting operation is obstructed if the motor starting speed data is greater than a preset motor starting speed range;

[0023] When the motor is in an abnormal temperature change speed or the starting operation is blocked, the starting speed of the motor is reduced until the motor consumption torque is within the preset consumption torque range, and then the speed is gradually increased to the motor theoretical speed.

[0024] The present invention further provides an integrated hydraulic transmission device, to which the above-mentioned magnetic drive-based integrated hydraulic transmission control method can be applied, comprising:

[0025] driving parts;

[0026] A reversing pump, wherein a reversing channel is provided in the reversing pump, and the driving member is drivingly connected to the reversing pump;

[0027] An oil cylinder, wherein the reversing pump is fixed to an end of the oil cylinder, and the reversing channel is connected to the oil cylinder, a transmission chamber is provided in the oil cylinder, an oil exchange pipe is provided in the transmission chamber, an oil space is formed between a cavity wall of the transmission chamber and the oil exchange pipe, one end of the oil exchange pipe is connected to one end of the oil space, and the other end of the oil exchange pipe is connected to the other end of the oil space through the reversing channel;

[0028] The magnetic part is located in the oil space, and is sleeved on the oil change pipe and can move relative to the oil change pipe. A transmission part that can move relative to the oil cylinder is provided on the outside of the oil cylinder, and the transmission part is magnetically connected to the magnetic part.

[0029] As an optional embodiment of the present invention, the magnetic part includes a plurality of first magnets distributed along the length direction of the oil change pipe; the transmission part includes a plurality of second magnets distributed along the length direction of the oil cylinder, and the first magnets and the corresponding second magnets are magnetically connected to each other.

[0030] As an optional embodiment of the present invention, a connecting port is fixedly arranged between the reversing pump and the oil cylinder, two overflow chambers are arranged in the connecting port, an overflow valve is arranged in the overflow chamber, the number of the reversing channels is two, and the overflow chambers are respectively connected to the corresponding reversing channels.

[0031] As an optional embodiment of the present invention, it further includes an oil storage tank, wherein an oil storage cavity is provided in the oil storage tank, oil is stored in the oil storage cavity, and the oil storage cavity is connected to the reversing pump.

[0032] Compared with the existing technology, the present invention can adjust the operation of the motor in real time according to demand, and then accurately control the oil output or return of the reversing pump. The integrated hydraulic transmission device can achieve high-efficiency, high-precision, and intelligently controlled hydraulic power output, which is suitable for precision linear drive operations in highly clean, explosion-proof and corrosive environments. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 This is a flow chart of a control method for an integrated hydraulic transmission based on magnetic drive according to an embodiment of the present invention;

[0034] Figure 2 is a schematic diagram of the three-dimensional structure of the integrated hydraulic transmission device of this embodiment;

[0035] Figure 3 yes Figure 2Schematic diagram of the cross-section structure in ;

[0036] Figure 4 It is a cross-sectional diagram of the connection between the driving part and the reversing pump;

[0037] Figure 5 It is an exploded diagram of the connection between the drive and the reversing pump;

[0038] Figure 6 It is a schematic diagram of the three-dimensional structure of the reversing pump;

[0039] Figure 7 yes Figure 6 One of the cross-sectional structural diagrams;

[0040] Figure 8 yes Figure 6 The second schematic diagram of the cross-sectional structure.

[0041] In the figure, 100, reversing pump; 101, reversing channel; 102, connecting port; 103, overflow chamber; 104, overflow valve; 105, return pipe; 106, one-way valve; 107, connecting seat; 108, connecting through hole; 109, connecting groove; 110, control chamber; 111, gear set; 112, transmission shaft; 113, sliding bearing; 114, pump head; 115, pump body;

[0042] 200, oil cylinder; 201, oil change pipe; 202, oil space; 203, magnetic part; 204, transmission part; 205, first magnet; 206, second magnet;

[0043] 300, oil storage tank; 301, oil storage chamber; 302, oil outlet;

[0044] 400, driving member; 401, accommodating cavity; 402, isolation sleeve; 403, stator installation cavity; 404, stator; 405, rotor installation cavity; 406, rotor; 407, circuit control board; 408, communication connection terminal; 409, housing. DETAILED DESCRIPTION

[0045] The following are specific embodiments of the present invention and the accompanying drawings to further describe the technical solutions of the present invention, but the present invention is not limited to these embodiments.

[0046] Example 1

[0047] Based on the technical problems raised in the background technology, this embodiment proposes a control method for an integrated hydraulic transmission based on magnetic drive, such as Figure 1 As shown, including:

[0048] S1, obtaining parameter data of an integrated hydraulic transmission device, wherein the parameter data includes a fixed oil output of a reversing pump and a cross-sectional area of ​​a hydraulic cylinder;

[0049] S2, inputting the expected displacement of the hydraulic cylinder and the expected time from the actual displacement to the expected displacement through the host computer;

[0050] S3, calculating the theoretical number of motor revolutions according to the difference between the expected oil cylinder displacement and the actual oil cylinder displacement, the fixed oil output displacement of the reversing pump, and the cross-sectional area of ​​the hydraulic cylinder;

[0051] S4, calculating the theoretical speed of the motor according to the theoretical number of revolutions of the motor and the expected time, and adjusting the speed of the motor according to the theoretical speed of the motor;

[0052] S5. In the process of adjusting the speed of the motor to the theoretical speed of the motor, the hydraulic cylinder's oil outlet displacement is driven by magnetic force, and the number of motor revolutions is counted by the Hall sensor. When the number of motor revolutions is the theoretical number of motor revolutions and the motor speed is the theoretical speed of the motor, the actual oil outlet displacement of the hydraulic cylinder is equal to the expected oil outlet displacement.

[0053] In this embodiment, the reversing pump adopts a gear pump. After the gear pump is integrated with the hydraulic cylinder, it is important to control the motor speed so as to drive the displacement of the oil in the cylinder through magnetic force. To this end, in this embodiment, the parameter data of the integration of the gear pump and the hydraulic cylinder are first obtained. The parameter data is the fixed data of the equipment itself, such as the fixed oil displacement of the gear pump (ml / rev) and the cross-sectional area of ​​the hydraulic cylinder (cm 2 ), these data will affect the speed regulation of the motor.

[0054] The user inputs the required cylinder displacement, i.e. the expected cylinder displacement, and the time required for the current hydraulic cylinder's actual cylinder displacement to reach the expected cylinder displacement through the host computer. This is determined by the user's needs. Since the pump shaft is driven by a motor, the theoretical number of motor revolutions can be calculated using the following formula:

[0055] Oil cylinder displacement (L) = motor revolutions (rev) × gear pump fixed oil displacement (ml / rev) ÷ hydraulic cylinder cross-sectional area (cm 2 ).

[0056] That is, from now on, the actual oil cylinder displacement is achieved through the rotation of the motor, and after the expected time, the actual oil cylinder displacement can reach the user's expected oil cylinder displacement.

[0057] According to the required displacement and expected time of the gear pump and hydraulic cylinder, the required number of motor revolutions and the theoretical motor speed (N) are automatically calculated to achieve precise control of the cylinder. After obtaining the number of motor revolutions, the theoretical motor speed can be obtained using the following formula:

[0058] Theoretical motor speed = number of motor revolutions ÷ expected time.

[0059] After the theoretical speed of the motor is calculated, the speed of the motor is adjusted. In this embodiment, after the gear pump and the hydraulic cylinder are integrated, magnetic coupling is adopted for both the gear pump and the hydraulic cylinder, and the oil in the hydraulic cylinder is transmitted by magnetic drive. The transmission ratio of the pump shaft of the motor and the gear pump is set to 1:1. When the motor rotates, the motor drives the gear pump, and the gear drives the oil out of the hydraulic cylinder based on magnetic force. Therefore, after the motor speed is adjusted to the calculated theoretical speed of the motor, the gear pump is driven at this speed, which can make the displacement of the hydraulic cylinder quickly meet the needs of users. In the process of adjusting the motor speed to the calculated theoretical speed of the motor, the number of revolutions of the motor rotor is identified by the Hall sensor, and the real-time motor operating speed is obtained in combination with the time it has been running.

[0060] Preferably, when counting the number of motor revolutions through the Hall sensor, it also includes: acquiring real-time power data of the integrated hydraulic transmission device; calculating the motor consumption torque through the real-time power data and the motor operating speed; and taking corresponding protective measures based on whether the motor consumption torque is within a preset consumption torque range.

[0061] After the external power supply is supplied, the motor rotates, and the number of revolutions (rev) of the motor rotor is identified by the Hall sensor. Combined with the running time (min), the motor speed (N) = rev / min is calculated.

[0062] The real-time power data (P) is obtained from the host computer, and the motor consumption torque T can be calculated.

[0063] The formula for motor torque consumption is: T = 9550 × P ÷ N; 9550 is a constant. Motor torque consumption, T, is one of the parameters used to determine whether the gear pump and hydraulic cylinder integrated system is operating normally. If T is not within the normal torque consumption range, the gear pump and hydraulic cylinder integrated system is considered to have a safety risk and requires further risk investigation.

[0064] Preferably, corresponding protection measures are taken according to whether the motor consumption torque is within the preset consumption torque range, including: when the motor consumption torque is within the preset consumption torque range, the motor keeps running; when the motor consumption torque is higher than the maximum consumption torque of the preset consumption torque range, a gradual speed change measure is adopted for the motor; when the motor consumption torque is less than the minimum consumption torque of the preset consumption torque range, the motor is controlled to stop running through a first level signal.

[0065] The preset torque consumption range is the normal torque consumption range and can be set according to actual working conditions. If the motor torque consumption is within the normal torque consumption range, it means that the gear pump and hydraulic cylinder integrated device are operating normally.

[0066] If the motor torque consumption is higher than the normal torque consumption range, it means that the motor speed needs to be controlled to protect the motor hardware safety.

[0067] If the motor's torque consumption is lower than the normal torque consumption range, it indicates that the motor may be idling, unable to drive the gear pump, and thus unable to drive the hydraulic cylinder's oil cylinder displacement. For such situations, the motor is associated with a first power supply, and the motor's operating state is changed by controlling the level signal of the first power supply. In this embodiment, the first level signal is the level signal of the first power supply. When the low level signal is set to correspond to 0V of the first power supply, the motor operates normally; when the high level signal is set to correspond to 5V of the first power supply, the motor stops suddenly.

[0068] Preferably, when the difference is a negative number, the motor is controlled to reverse by a second level signal to change the direction of displacement of the oil cylinder.

[0069] A negative difference indicates that oil return is required within the hydraulic cylinder. This involves associating the motor with a second power source, controlling the level of the second power source's signal to change the motor's forward and reverse rotation. In this embodiment, the second level signal corresponds to the second power source's level. When the low level corresponds to 0V, the motor rotates forward; when the high level corresponds to 5V, the motor rotates reversely. By changing the motor's rotational direction, the direction of the oil discharge cylinder's displacement is altered.

[0070] Preferably, the transmission ratio between the motor and the pump shaft of the reversing pump is 1:1.

[0071] Setting the transmission ratio of the motor to the gear pump to 1:1 not only makes it easier to control the oil output, but also makes the operating status clearer when the user views it through the host computer.

[0072] Preferably, when the motor consumption torque is higher than the maximum consumption torque of the preset consumption torque range, a gradual speed change measure is adopted for the motor, including: obtaining motor temperature data, judging the motor temperature change rate based on the motor temperature data, if the motor temperature change rate is greater than the preset temperature change rate range, judging that the motor temperature change rate is too fast; obtaining motor starting speed data, if the motor starting speed data is greater than the preset motor starting speed, judging that the motor starting operation is obstructed; when the motor is in an abnormal temperature change rate or the starting operation is obstructed, reducing the starting speed of the motor until the motor consumption torque is within the preset consumption torque range, and then gradually increasing the speed to the theoretical speed of the motor.

[0073] When the motor's torque consumption exceeds the maximum torque consumption within the preset torque consumption range, the motor temperature change rate can be used to determine the abnormality. The preset temperature change rate range is the normal temperature change rate range and can be set by the user based on actual operating conditions. The host computer obtains motor temperature data and calculates the motor temperature change rate within that time period based on the motor's operating time. If the motor temperature change rate exceeds the normal temperature change rate, the motor temperature change rate is abnormal.

[0074] The motor starting speed data can also be used to identify abnormalities. After applying external power, if the motor starting speed exceeds the preset motor starting speed range (the preset motor starting speed range is the standard motor starting speed range, which can be set by the user based on actual operating conditions), the motor starting speed is abnormal, and motor startup is hindered. Both of these abnormalities can result in excessive motor torque consumption. Therefore, when excessive motor torque consumption occurs or during initial startup, the motor starting speed is reduced and the motor torque consumption is calculated. When the motor torque consumption is within normal limits, the motor speed is gradually increased. After the cylinder displacement reaches the expected cylinder displacement, the motor speed is gradually reduced to terminate the motor operation.

[0075] Through the above method, the operation of the motor can be adjusted in real time according to demand, and the oil output or return of the reversing pump can be accurately controlled to achieve efficient, high-precision, and intelligently controlled hydraulic power output, which is suitable for precision linear drive operations in highly clean, explosion-proof, and corrosive environments.

[0076] Example 2

[0077] This embodiment also proposes an integrated hydraulic transmission device, which can apply the control method of the integrated hydraulic transmission based on magnetic drive described in Example 1. Figure 2-8 As shown, an integrated hydraulic transmission device includes:

[0078] Driving member 400;

[0079] The reversing pump 100 has a reversing channel 101 disposed therein, and the driving member 400 is drivingly connected to the reversing pump 100;

[0080] The oil cylinder 200 and the reversing pump 100 are fixed to the end of the oil cylinder 200, and the reversing channel 101 is connected to the oil cylinder 200. A transmission chamber is provided in the oil cylinder 200, and an oil exchange pipe 201 is provided in the transmission chamber. An oil space 202 is formed between the cavity wall of the transmission chamber and the oil exchange pipe 201. One end of the oil exchange pipe 201 is connected to one end of the oil space 202, and the other end of the oil exchange pipe 201 is connected to the other end of the oil space 202 through the reversing channel 101.

[0081] The magnetic part 203 is located in the oil space 202, and is sleeved on the oil change pipe 201 and can move relative to the oil change pipe 201. A transmission part 204 that can move relative to the oil cylinder 200 is provided on the outside of the oil cylinder 200, and the transmission part 204 is magnetically connected to the magnetic part 203.

[0082] In this embodiment, by directly fixing the reversing pump 100 at the end of the oil cylinder 200 and connecting the oil channel in the reversing pump 100 with the internal pipeline of the oil cylinder 200, a highly integrated design of the system is achieved, which not only reduces the number of components and pipeline connections, but also greatly saves space occupancy, making the entire device more compact; and the oil change pipe 201, the reversing channel 101 and the oil space 202 form a closed and effective oil circulation path, which can ensure smooth oil flow and reduce energy loss.

[0083] The magnetic part 203 is located in the oil space 202 and is sleeved on the oil change pipe 201. It can move relative to the oil change pipe 201. At the same time, a transmission part 204 is provided on the outside, which can move relative to the cylinder 200 and is magnetically connected to the magnetic part 203. This non-contact power transmission method avoids the friction loss and leakage problems caused by traditional mechanical seals, thereby improving the reliability and service life of the system.

[0084] Specifically, the magnetic part 203 includes multiple first magnets 205 distributed along the length direction of the oil exchange pipe 201; the transmission part 204 includes multiple second magnets 206 distributed along the length direction of the cylinder 200, and the first magnets 205 and the corresponding second magnets 206 are magnetically connected to each other.

[0085] In this embodiment, the first magnet 205 and the corresponding second magnet 206 are magnetically attracted to each other, which can significantly enhance the overall magnetic coupling effect of the magnetic drive part, improve the efficiency of magnetic force transmission, and enhance the stability and response speed of the system; and by changing the number of magnets in the magnetic part 203 and the transmission part 204, the load capacity of the system can be flexibly adjusted according to actual application requirements; increasing the number of magnets can enhance the magnetic field strength, thereby improving the carrying capacity of the magnetic drive part; conversely, reducing the number of magnets can reduce the load capacity.

[0086] Further preferably, a connecting port 102 is fixedly provided between the reversing pump 100 and the oil cylinder 200, two overflow chambers 103 are provided in the connecting port 102, an overflow valve 104 is provided in the overflow chamber 103, the number of reversing channels 101 is two, and the overflow chambers 103 are respectively connected to the corresponding reversing channels 101.

[0087] In this embodiment, by providing two overflow chambers 103 on the connection port 102 and installing a relief valve 104 in each overflow chamber 103, damage to the system caused by excessive pressure can be effectively prevented. When the system pressure exceeds a set value, the relief valve 104 automatically opens and directs excess oil to other designated locations, thereby preventing damage to system components caused by overpressure. For example, when the oil in the cylinder 200 expands due to a rise in temperature, the internal pressure will increase.

[0088] Preferably, an oil storage tank 300 is further included. An oil storage chamber 301 is provided in the oil storage tank 300 . Oil is stored in the oil storage chamber 301 , and the oil storage chamber 301 is communicated with the reversing pump 100 .

[0089] Further preferably, a return pipe 105 is provided in the reversing pump 100 , and both ends of the return pipe 105 are respectively connected to the oil storage chamber 301 and the overflow chamber 103 .

[0090] In this embodiment, a complete oil circulation path is established by disposing a return pipe 105 within the reversing pump 100 and connecting it to the oil reservoir 301. This structure allows excess oil in the cylinder 200 to return to the oil reservoir 301 via the return pipe 105, thereby ensuring continuous oil circulation throughout the hydraulic system and maintaining stable system operation. Furthermore, if the system's oil level decreases due to operational needs or leakage, the reserved oil in the oil reservoir 301 can be promptly replenished to ensure the normal operation of hydraulic actuators (such as the cylinder 200).

[0091] Further preferably, a one-way valve 106 is provided in the reversing pump 100 . The one-way valve 106 is provided on the connecting pipeline between the oil storage chamber 301 and the two reversing channels 101 . The one-way valve 106 can realize one-way flow from the oil storage chamber 301 to the reversing channel 101 .

[0092] In this embodiment, a one-way valve 106 is provided between the oil reservoir 301 and the two reversing channels 101. During normal operation, the one-way valve 106 between the oil reservoir 301 and the reversing channels 101 is closed, preventing oil from flowing back into the oil reservoir 301. At this time, the reversing pump 100 controls the flow of oil to deliver it to the cylinder 200. When the oil pressure in the cylinder 200 is low, the one-way valve 106 opens, allowing the oil in the oil reservoir 301 to flow into the cylinder 200.

[0093] Further preferably, the oil storage tank 300 includes an oil outlet end 302 connected to the oil storage chamber 301, and the driving member 400 includes a shell 409 fixedly connected to the oil storage tank 300, and an accommodating chamber 401 is formed in the shell 409, and an isolation sleeve 402 is fixedly arranged in the accommodating chamber 401, and a stator mounting chamber 403 is formed between the isolation sleeve 402 and the cavity wall of the accommodating chamber 401, and a stator 404 is fixedly arranged in the stator mounting chamber 403, and a rotor mounting chamber 405 is formed in the isolation sleeve 402, and a rotor 406 is rotatably arranged in the rotor mounting chamber 405, and the rotor 406 is fixed to the transmission shaft 112 in the reversing pump 100, and the oil outlet end 302 is sealedly connected to the isolation sleeve 402 to realize the communication between the oil outlet end 302 and the rotor mounting chamber 405, and the rotor mounting chamber 405 is connected to the reversing channel 101.

[0094] In this embodiment, the stator 404 and the rotor 406 are force-coupled through a magnetic field, achieving contactless power transmission, avoiding friction loss and leakage problems caused by traditional mechanical seals, and extending the service life of the equipment; the presence of the isolation sleeve 402 not only achieves separation between the stator 404 and the rotor 406, but also optimizes the flow path of the oil: after the oil flows out of the oil storage tank 300, it passes through the oil outlet 302 into the rotor mounting cavity 405 inside the isolation sleeve 402 and then flows to the reversing pump 100, reducing unnecessary resistance loss and improving the overall efficiency of the system.

[0095] It is worth mentioning that, in order to facilitate the processing of the internal pipelines in the reversing pump 100 , the reversing pump 100 includes a pump head 114 and a pump body 115 that are fixedly connected.

[0096] Further preferably, a circuit control board 407 is fixedly installed in the stator installation cavity 403 , and a communication connection terminal 408 is provided on the driving member 400 to communicate with the circuit control board 407 .

[0097] In this embodiment, the circuit control board 407 is integrated into the stator mounting cavity 403, which not only reduces the need for external wiring, but also improves the integration and compactness of the system. The circuit control board 407 can analyze and process the collected data, and send or receive instructions to the external control system through the communication connection terminal 408 to achieve precise control of the hydraulic system.

[0098] Specifically, a connecting seat 107 is integrally provided on the isolation sleeve 402, and a connecting through-hole 108 connected to the mounting cavity of the rotor 406 is provided on the connecting seat 107. A connecting groove 109 is provided on the other side of the connecting seat 107. The connecting groove 109 is fixed to the reversing pump 100. A connecting cavity is formed between the connecting groove 109 and the end face of the reversing pump 100. The connecting cavity is respectively connected to the connecting through-hole 108 and the reversing channel 101. The transmission shaft 112 passes through the connecting seat 107 and extends into the reversing pump 100.

[0099] In this embodiment, a connecting seat 107 is integrally provided on the isolation sleeve 402, and a connecting hole 108 connected to the rotor mounting cavity 405 is provided on the connecting seat 107, thereby realizing the connection between the reversing pump 100 and the oil storage tank 300. The connecting cavity serves as a transition area, and can also ensure a smooth transition of the oil from the connecting hole 108 to the reversing channel 101, thereby avoiding resistance and leakage problems in the flow of oil.

[0100] Further preferably, a control chamber 110 is provided in the reversing pump 100, and a gear set 111 is provided in the control chamber 110. The control chamber 110 is connected to the two reversing channels 101 to control the rotation direction of the gear set 111 to realize the switching of the oil circuit direction in the reversing channel 101. The driving gear in the gear set 111 is fixed to the transmission shaft 112.

[0101] In this embodiment, the oil flow direction of the two reversing channels 101 can be switched by rotating the gear set 111 (including the driving gear and the driven gear). Integrating the control chamber 110 and the gear set 111 into the pump body 115 not only saves space but also reduces external piping connections, reduces the risk of leakage, and improves the reliability and stability of the system. When the gear set 111 rotates in a certain direction, the oil enters the control chamber 110 from one reversing channel 101 and, after being acted upon by the gear set 111, flows to the other reversing channel 101. Conversely, when the gear set 111 rotates in the opposite direction, the oil flow direction also changes accordingly.

[0102] When the oil pressure in the cylinder 200 is low, the one-way valve 106 will use the pressure difference generated between the two reversing channels 101 to drive the corresponding one-way valve 106 to open according to the rotation direction of the gear set 111, so that the oil in the oil storage chamber 301 flows to the cylinder 200.

[0103] It is worth mentioning that the transmission shaft 112 and the pump body 115 are connected via a sliding bearing 113 , so that when the transmission shaft 112 rotates relative to the reversing pump 100 , it can also play a sealing role.

[0104] It should be noted that all directional indications in the embodiments of the present invention (such as up, down, left, right, front, back, etc.) are only used to explain the relative position relationship, movement status, etc. between the various components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0105] In addition, it should be noted that the descriptions of "first", "second", "one", etc. in the present invention are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of the present invention, the meaning of "multiple" is at least two, such as two, three, etc., unless otherwise clearly defined. The terms "connected", "fixed", etc. should be understood in a broad sense. For example, "fixed" can be a fixed connection, a detachable connection, or an integral whole; 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, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to the specific circumstances.

[0106] In addition, the technical solutions between the various embodiments of the present invention can be combined with each other, but it must be based on the fact that ordinary technicians in this field can implement it. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0107] The specific embodiments described herein are merely illustrative of the spirit of the present invention. Persons skilled in the art may make various modifications, additions, or substitutions to the described specific embodiments without departing from the spirit of the present invention or exceeding the scope of the appended claims.

Claims

1. A control method for an integrated hydraulic transmission based on magnetic drive, characterized in that: include: Acquiring parameter data of the integrated hydraulic transmission device, wherein the parameter data includes a fixed oil output of a reversing pump and a cross-sectional area of ​​a hydraulic cylinder; Inputting the expected displacement of the hydraulic cylinder and the expected time from the actual displacement to the expected displacement through the host computer; Calculating the theoretical number of motor revolutions according to the difference between the expected oil cylinder displacement and the actual oil cylinder displacement, the fixed oil output displacement of the reversing pump, and the cross-sectional area of ​​the hydraulic cylinder; Calculating the theoretical speed of the motor according to the theoretical number of revolutions of the motor and the expected time, and adjusting the speed of the motor according to the theoretical speed of the motor; In the process of adjusting the speed of the motor to the theoretical speed of the motor, the oil outlet displacement of the hydraulic cylinder is driven by magnetic force, and the number of motor revolutions is counted by the Hall sensor. When the number of motor revolutions is the theoretical number of motor revolutions and the motor speed is the theoretical speed of the motor, the actual oil outlet displacement of the hydraulic cylinder is equal to the expected oil outlet displacement.

2. The control method of the integrated hydraulic transmission based on magnetic drive according to claim 1, characterized in that: When counting the number of motor revolutions through the Hall sensor, it also includes: Get real-time power data of integrated hydraulic transmissions; Calculating the motor consumption torque based on the real-time power data and the motor operating speed; Corresponding protective measures are taken according to whether the motor consumption torque is within a preset consumption torque range.

3. The control method of the integrated hydraulic transmission based on magnetic drive according to claim 2, characterized in that: The corresponding protection measures are performed according to whether the motor consumption torque is within the preset consumption torque range, including: When the motor consumption torque is within the preset consumption torque range, the motor keeps running; When the motor consumption torque is higher than the maximum consumption torque of the preset consumption torque range, a gradual speed change measure is adopted for the motor; When the motor consumption torque is less than the minimum consumption torque in the preset consumption torque range, the motor is controlled to stop running through a first level signal.

4. The control method of the integrated hydraulic transmission based on magnetic drive according to claim 1, characterized in that: When the difference is a negative number, the motor is controlled to reverse through the second level signal to change the direction of displacement of the oil cylinder.

5. The control method of the integrated hydraulic transmission based on magnetic drive according to claim 3, characterized in that: The transmission ratio between the motor and the pump shaft of the reversing pump is 1:

1.

6. The control method of the integrated hydraulic transmission based on magnetic drive according to claim 3, wherein when the motor consumption torque is higher than the maximum consumption torque of the preset consumption torque range, a gradual speed change measure is adopted for the motor, comprising: Acquire motor temperature data, determine the motor temperature change rate based on the motor temperature data, and determine that the motor temperature change rate is abnormal if the motor temperature change rate is greater than a preset temperature change rate range; Acquiring motor starting speed data, and determining that motor starting operation is obstructed if the motor starting speed data is greater than a preset motor starting speed range; When the motor is in an abnormal temperature change speed or the starting operation is blocked, the starting speed of the motor is reduced until the motor consumption torque is within the preset consumption torque range, and then the speed is gradually increased to the motor theoretical speed.

7. An integrated hydraulic transmission device, characterized in that: The control method of the integrated hydraulic transmission based on magnetic drive according to any one of claims 1 to 6 comprises: driving parts; A reversing pump, wherein a reversing channel is provided in the reversing pump, and the driving member is drivingly connected to the reversing pump; An oil cylinder, wherein the reversing pump is fixed to an end of the oil cylinder, and the reversing channel is connected to the oil cylinder, a transmission chamber is provided in the oil cylinder, an oil exchange pipe is provided in the transmission chamber, an oil space is formed between a cavity wall of the transmission chamber and the oil exchange pipe, one end of the oil exchange pipe is connected to one end of the oil space, and the other end of the oil exchange pipe is connected to the other end of the oil space through the reversing channel; The magnetic part is located in the oil space, and is sleeved on the oil change pipe and can move relative to the oil change pipe. A transmission part that can move relative to the oil cylinder is provided on the outside of the oil cylinder, and the transmission part is magnetically connected to the magnetic part.

8. The integrated hydraulic transmission device according to claim 7, characterized in that: The magnetic part includes a plurality of first magnets distributed along the length direction of the oil exchange pipe; the transmission part includes a plurality of second magnets distributed along the length direction of the oil cylinder, and the first magnets and the corresponding second magnets are magnetically connected to each other.

9. The integrated hydraulic transmission device according to claim 7, characterized in that: A connecting port is fixedly provided between the reversing pump and the oil cylinder. Two overflow chambers are provided in the connecting port. An overflow valve is provided in the overflow chamber. There are two reversing channels, and the overflow chambers are respectively connected to the corresponding reversing channels.

10. The integrated hydraulic transmission device according to claim 9, characterized in that: It also includes an oil storage tank, in which an oil storage cavity is provided. Oil is stored in the oil storage cavity, and the oil storage cavity is connected to the reversing pump.

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