Electro-hydraulic composite speed regulator

Abstract

The invention provides an electro-hydraulic composite speed regulator which comprises a transmission shaft, one end of the transmission shaft is connected with a hydraulic oil pump, the hydraulic oil pump is connected with a filter, one end of the filter is connected with an electro-hydraulic servo valve, the electro-hydraulic servo valve is connected with a feedback lever assembly, and one end of the feedback lever assembly is connected with a power output oil cylinder. The invention belongs to the technical field of electro-hydraulic speed regulators, and relates to an electro-hydraulic speed regulator which is formed by combining an electro-hydraulic execution part and a hydraulic speed regulation part, the electro-hydraulic execution part is used in cooperation with a speed regulation control part to achieve control over the rotating speed of a diesel engine, and the hydraulic speed regulation part automatically achieves control over the rotating speed of the diesel engine. And pneumatic power is also used, an alternative scheme is provided for hydraulic speed regulation, multi-mode rotating speed control and multi-mode rotating speed setting can be achieved, the application range is wide, and the beneficial effects of being large in output torque, high in regulation precision and short in response time are achieved.

Description

Technical Field

[0001] The invention belongs to the technical field of electro-hydraulic speed regulators, and in particular relates to an electro-hydraulic composite speed regulator. Background Art

[0002] The main function of the electro-hydraulic speed governor is to automatically adjust the speed of the diesel engine to ensure its stable operation under different working conditions. The speed governor automatically increases or decreases the fuel supply of the injection pump according to the changes in the diesel engine load, so that the diesel engine can run at a stable speed. Existing electro-hydraulic speed governors usually rely mainly on hydraulics to achieve the power output of the oil pump to achieve speed regulation or use manual speed regulation. Only setting up a hydraulic system makes the entire speed regulation system relatively simple. When a single hydraulic system faces a failure, it often lacks sufficient redundancy and alternative solutions. Therefore, an electro-hydraulic composite speed governor is invented. Summary of the invention

[0003] An embodiment of the present invention provides an electro-hydraulic composite speed regulator, comprising a transmission shaft; one end of the transmission shaft is connected to a hydraulic oil pump, a filter is connected to the hydraulic oil pump, one end of the filter is connected to an electro-hydraulic servo valve, a feedback lever assembly is connected to the electro-hydraulic servo valve, one end of the feedback lever assembly is connected to a power output cylinder, a rotor is installed at one end of the hydraulic oil pump, a flyweight is installed at one end of the rotor, a speed regulating spring is connected to the flyweight, one end of the speed regulating spring is connected to a connecting slide valve, the other end of the speed regulating spring is connected to a speed regulating cylinder, a recovery rod is connected to the speed regulating cylinder, the recovery rod is connected to a cylinder, and one end of the recovery rod is connected to a speed regulating slide valve.

[0004] Preferably, the hydraulic oil pump is provided with a one-way valve, and the number of the one-way valves is 4.

[0005] Preferably, an accumulator is provided between the one-way valve and the filter, and a pressure valve is provided between the one-way valve and the filter and at the accumulator.

[0006] Preferably, the electro-hydraulic servo valve is provided with an A port, a P port and a T port.

[0007] Preferably, the connecting slide valve is provided with an A1 port, a P1 port and a T1 port.

[0008] Preferably, a pressure reducing valve is connected to the speed regulating sliding valve.

[0009] Preferably, a manual speed adjustment knob is provided on the recovery rod.

[0010] Preferably, a speed reduction rod is installed between the power output cylinder and the speed regulating cylinder.

[0011] Preferably, the power output cylinder is connected with a buffer compensation device and a needle valve.

[0012] Preferably, a B1 port is provided on the buffer compensation device.

[0013] Preferably, a parking solenoid valve is connected to the speed regulating cylinder.

[0014] The beneficial effects brought by the present invention are as follows:

[0015] It can be seen from the above scheme that an embodiment of the present invention provides an electro-hydraulic composite speed governor, which is composed of an electro-hydraulic actuator part and a hydraulic speed control part. The electro-hydraulic actuator part and the speed control part are used in conjunction to realize the control of the diesel engine speed. The hydraulic speed control part automatically realizes the control of the diesel engine speed. The hydraulic speed control part not only uses hydraulic power but also uses pneumatic power, providing an alternative to hydraulic speed control, which can realize multi-mode speed control and multi-mode speed setting, has a wide range of applications, and has the characteristics of large output torque, high adjustment accuracy and short response time. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 A schematic diagram showing an electro-hydraulic composite speed regulator according to an embodiment of the present invention.

[0017] In the figure: 1. transmission shaft, 2. hydraulic oil pump, 3. non-return valve, 4. pressure valve, 5. accumulator, 6. filter, 7. electro-hydraulic servo valve, 8. feedback lever assembly, 9. pressure reducing valve, 10. speed control slide valve, 11. cylinder, 12. manual speed control knob, 13. recovery rod, 14. speed control cylinder, 15. speed control spring, 16. connecting slide valve, 17. fly hammer, 18. rotor, 19. parking solenoid valve, 20. speed reduction rod, 21. buffer compensation device, 22. needle valve, 23. power output cylinder. DETAILED DESCRIPTION

[0018] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution in the embodiment of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiment of the present invention. Obviously, the described embodiment is a part of the embodiment of the present invention, not all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0019] Reference Figure 1 , the dotted line represents the oil circuit, and the dotted line in the figure divides it into three parts, namely D, G and H, where D represents the electro-hydraulic actuator part, G represents the hydraulic governor part, and H represents the common part;

[0020] An electro-hydraulic composite speed regulator comprises a transmission shaft 1; a hydraulic oil pump 2 is connected to one end of the transmission shaft 1, a filter 6 is connected to the hydraulic oil pump 2, an electro-hydraulic servo valve 7 is connected to one end of the filter 6, a feedback lever assembly 8 is connected to the electro-hydraulic servo valve 7, a power output cylinder 23 is connected to one end of the feedback lever assembly 8, a rotor 18 is installed at one end of the hydraulic oil pump 2, a flyweight 17 is installed at one end of the rotor 18, a speed regulating spring 15 is connected to the flyweight 17, one end of the speed regulating spring 15 is connected to a connecting slide valve 16, the other end of the speed regulating spring 15 is connected to a speed regulating cylinder 14, the speed regulating cylinder 14 is connected to a recovery rod 13, the recovery rod 13 is connected to a cylinder 11, and one end of the recovery rod 13 is connected to a speed regulating slide valve 10;

[0021] As a preferred embodiment, further, the hydraulic oil pump 2 is provided with a one-way valve 3, and the number of the one-way valves 3 is 4;

[0022] It should be noted that the rotation of the diesel engine crankshaft drives the transmission shaft 1 to rotate, thereby driving the hydraulic oil pump 2 to rotate and output pressure oil. The four one-way valves 3 can realize the positive rotation of the hydraulic oil pump 2;

[0023] As a preference, further, an accumulator 5 is provided between the one-way valve 3 and the filter 6, and a pressure valve 4 is provided between the one-way valve 3 and the filter 6 and at the accumulator 5;

[0024] It should be noted that the accumulator 5 stores oil pressure to reduce pressure pulsation, and the pressure valve 4 keeps the pressure constant at a set value as a preferred embodiment. Furthermore, the electro-hydraulic servo valve 7 is provided with an A port, a P port and a T port;

[0025] As a preferred embodiment, further, the connecting slide valve 16 is provided with an A1 port, a P1 port and a T1 port;

[0026] As a preferred embodiment, further, the speed control sliding valve 10 is connected to a pressure reducing valve 9;

[0027] As a preference, further, a manual speed adjustment knob 12 is provided on the recovery lever 13;

[0028] As a preferred embodiment, further, a deceleration rod 20 is installed between the power output cylinder 23 and the speed regulating cylinder 14;

[0029] As a preferred embodiment, further, the power output cylinder 23 is connected with a buffer compensation device 21 and a needle valve 22;

[0030] As a preference, further, a B1 port is provided on the buffer compensation device 21;

[0031] Preferably, further, the speed regulating cylinder 14 is connected to a parking solenoid valve 19 .

[0032] Working principle:

[0033] 1. Electro-hydraulic actuator

[0034] The electro-hydraulic servo valve 7 is a reaction valve. In the initial state, that is, when the power is off, the electro-hydraulic servo valve 7 is in the lower position, and the pressure oil passes through the filter 6 from the P port of the electro-hydraulic servo valve 7 to the A port.

[0035] 1.1 Initial state

[0036] After power-on, the speed controller gives the maximum current value, so that the electro-hydraulic servo valve 7 is in the upper position, port A is connected to port T, the oil in the lower chamber of the power output cylinder 23 is connected to port T, and the power output cylinder 23 is retracted to the bottom under the action of the pressure oil in the upper chamber. At this time, the throttle is in position 0.

[0037] 1.2. Increase speed or load

[0038] When the speed of the diesel engine increases and the current set value decreases, the P port of the electro-hydraulic servo valve 7 is connected to the A port, and the power output cylinder 23 moves upward, pulling the injection pump to increase the fuel injection amount, thereby increasing the speed of the diesel engine; when the power output cylinder 23 moves upward, the feedback lever assembly 8 moves the electro-hydraulic servo valve 7 to the middle position; after the speed reaches the target value, the electro-hydraulic servo valve 7 is in the middle position, the oil port is closed, and the power output cylinder 23 remains in a stable position.

[0039] 1.3. Reduce speed or load

[0040] When the diesel engine speed is reduced, the electro-hydraulic servo valve 7A port is connected to the T port, the power output cylinder 23 moves downward, the fuel injection amount is reduced, and the diesel engine speed decreases; after the speed reaches the target value, the electro-hydraulic servo valve 7 is in the middle position and the oil port is closed.

[0041] 2. Hydraulic speed governor

[0042] The electro-hydraulic servo valve 7 loses power and is in the lower position. The pressure oil flows from the P port of the electro-hydraulic servo valve 7 to the A port through the filter 6.

[0043] The rotation of the diesel engine crankshaft drives the transmission shaft 1 to rotate, thereby driving the hydraulic oil pump 2 to rotate, and the shaft of the hydraulic oil pump 2 drives the rotor 18 and the flyweight 17 to rotate.

[0044] 2.1. Stable working conditions

[0045] In stable working condition, the spring force of speed regulating spring 15 is equal to the supporting force generated by the rotation of flyweight 17, and flyweight 17 is in vertical position. At this time, control connecting slide valve 16 is in middle position, that is, oil port is cut off. Power output cylinder 23 is kept in a fixed position, and diesel engine runs stably at a given speed.

[0046] 2.2. Increase speed or load

[0047] When the speed of the diesel engine is increased, that is, the spring force of the speed regulating spring 15 is increased, or the load of the diesel engine increases, resulting in a decrease in the speed, that is, the supporting force of the fly hammer 17 decreases. At this time, the spring force of the speed regulating spring 15 is greater than the supporting force of the fly hammer 17, and the fly hammer 17 moves inward, controlling the connecting slide valve 16 to move downward, the P1 port is connected to the A1 port, and the pressure oil drives the power output cylinder 23 to move upward, increasing the fuel injection amount of the diesel engine. With the increase in the fuel injection amount, the speed of the diesel engine rises, and the supporting force of the fly hammer 17 increases. When the fly hammer 17 returns to the vertical position, the connecting slide valve 16 is controlled to close the oil port, the power output cylinder 23 is stabilized in a new position, and the diesel engine runs stably under the new working condition.

[0048] 2.3. Reduce speed or load

[0049] When the speed of the diesel engine is reduced, i.e., the spring force of the speed regulating spring 15 is reduced, or the speed of the diesel engine is increased due to the reduction of the load, i.e., the supporting force of the fly hammer 17 is increased, the spring force is less than the supporting force of the fly hammer 17, the fly hammer 17 opens outward, the control connecting slide valve 16 moves upward, the A1 port is connected to the T1 port, the power output cylinder 23 moves downward under the action of the speed regulating spring 15, the fuel injection amount of the diesel engine is reduced, and the speed of the diesel engine decreases. When the supporting force of the fly hammer 17 is equal to the spring force of the speed regulating spring 15, and the control connecting slide valve 16 returns to the middle position, the diesel engine runs stably under the new working condition.

[0050] Due to the inertia of the diesel engine, when accelerating or decelerating, the stopping action of the power output cylinder 23 of the hydraulic speed governor must precede the speed setting value of the diesel engine to achieve the stability of the speed control system. Therefore, the hydraulic speed governor also includes an instantaneous compensation part, namely the buffer compensation device 21 and the needle valve 22. The instantaneous compensation part will be removed after the adjustment is stable. For example, when refueling, the P1 port is connected to the A1 port, the piston in the buffer compensation device 21 moves to the right, the buffer spring of the left piston is released, and the buffer spring of the right piston is compressed. Therefore, the oil pressure at the left end of the buffer piston is greater than the oil pressure at the right end of the buffer piston, that is, the oil pressure at the A1 port is greater than the B1 port. The oil pressures at the A1 port and the B1 port simultaneously act on the control connection slide valve 16 to generate an upward force. When this force and the supporting force of the fly hammer 17 are equal to the speed control spring 15 force, the B1 port is controlled to be closed, and the power output cylinder 23 is stabilized at a new position. At this time, if the opening (i.e., flow area) of the needle valve 22 is properly adjusted, the balancing speed of the oil pressure at ports A1 and B1 is consistent with the speed of increasing the supporting force of the fly hammer 17. When the supporting force of the fly hammer 17 is just equal to the force of the speed regulating spring 15, the oil pressure difference is zero. Similarly, when the oil is reduced, port A1 is connected to port T1, the piston in the buffer compensation device 21 moves to the left, the buffer spring of the left piston is compressed, and the buffer spring of the right piston is released. Therefore, the oil pressure at port A1 is less than that at port B1, and the oil pressures at ports A1 and B1 act on the control connecting slide valve 16 at the same time, causing it to generate a downward force.

[0051] 2.4. Downhill

[0052] The deceleration lever 20 can automatically change the speed setting of the speed regulator by slightly weakening the elastic force of the speed increaser spring according to the stroke of the power piston in the power output cylinder 23 in the increasing direction. Conversely, when the power piston moves in the decreasing direction, it will increase the elastic force of the speed regulating spring 15. The deceleration lever 20 includes a fulcrum connected to the upper end of the piston rod in the speed regulating cylinder 14, a lever and fulcrum pin device connected between the fulcrum and the piston rod in the power output cylinder 23, an adjustable cam connected to the fulcrum pin, and a movable plunger located inside the piston rod in the speed regulating cylinder 14. The movement of the piston in the power output cylinder 23 is transmitted through the lever, which causes the cam in contact with the top of the movable plunger to rotate, thereby causing the speed regulating cylinder 14 to move upward (or downward).

[0053] 2.5 Speed ​​setting

[0054] The speed setting of the speed regulator is adjusted by changing the force of the speed regulating spring 15 by using the movement of the piston in the speed regulating cylinder 14 above the speed regulating spring 15. When the pressure oil in the speed regulator is introduced into the upper end of the piston in the speed regulating cylinder 14, the piston moves downward, compressing the speed regulating spring 15 to increase the speed. When the pressure oil is released from the speed regulating cylinder 14, the piston moves upward, releasing the speed regulating spring 15, and reducing the speed.

[0055] The flow of the speed regulator pressure oil into or out of the speed regulating cylinder 14 is controlled by the speed regulating slide valve 10. The operator changes the extension and contraction of the cylinder 11 to move the recovery rod 13 up and down, thereby controlling the movement of the speed regulating slide valve 10 connected to the recovery rod 13. The gas-liquid control system is stepless in the entire speed range.

[0056] When changing the speed of the cylinder 11 to increase or decrease, due to the transmission movement of the restoring rod 13 between the piston in the speed regulating cylinder 14 and the speed regulating slide valve 10, when the piston moves to a new position, the speed regulating slide valve 10 is pushed back to the middle position to close the control oil hole, so that the oil stops flowing into or out of the speed regulating cylinder 14, thereby stabilizing the piston at the appropriate position after the speed regulator sets the speed.

[0057] (1) Increase the speed

[0058] The cylinder 11 extends to move the left end of the restoring rod 13 downward, thereby pushing the speed regulating slide valve 10 downward, opening the control oil hole, and allowing the pressure oil to flow into the speed regulating cylinder 14. The piston in the speed regulating cylinder 14 moves downward, compressing the speed regulating spring 15. The increased force of the speed regulating spring 15 causes the flyweights to close, opening the main control oil hole, and the power piston rises, increasing the fuel amount and increasing the speed of the diesel engine.

[0059] When the piston in the speed regulating cylinder 14 moves downward, it drives the right end of the recovery rod 13 to press downward, and then drives the speed regulating slide valve 10 to move upward together, and the piston continues to move downward until the speed regulating slide valve 10 rises to the center position, closes the control oil hole and stops the pressure oil from entering the speed regulating cylinder 14. Therefore, the piston stops moving downward and stays at a new position. At this time, the flyweight is in a vertical position, and the diesel engine is stable at a given speed.

[0060] (2) Reduce the speed

[0061] When the speed is lowered, the adjustment process of the speed regulator is exactly the opposite of the adjustment process when the speed is increased.

[0062] (3) Manual speed control

[0063] When the cylinder 11 is damaged and the remote speed regulation cannot be performed, the manual speed regulating knob can be used to achieve the speed increase or decrease. The push rod under the manual speed regulating knob directly presses on the recovery rod 13 to play the role of speed regulation.

[0064] 2.6 Parking

[0065] A parking solenoid valve 19 is installed on the speed governor. It is not energized when the engine is started, and the oil circuit is closed, so that the speed governor can build up sufficient oil pressure.

[0066] When the vehicle needs to be stopped under normal operation, the parking solenoid valve 19 is energized, the oil circuit is opened, the oil in the speed regulating cylinder 14 flows into the oil pool, and the piston in the speed regulating cylinder 14 moves upward under the action of the speed regulating spring 15 to lift the connecting slide valve 16, open the control oil hole, and allow the oil to flow from the buffer system into the oil tank.

[0067] The above are preferred embodiments of the present invention. It should be pointed out that, for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications should also be regarded as within the scope of protection of the present invention.

Claims

1. An electro-hydraulic composite speed regulator, comprising a transmission shaft (1), characterized in that ； One end of the transmission shaft (1) is connected to a hydraulic oil pump (2), the hydraulic oil pump (2) is connected to a filter (6), one end of the filter (6) is connected to an electro-hydraulic servo valve (7), the electro-hydraulic servo valve (7) is connected to a feedback lever assembly (8), one end of the feedback lever assembly (8) is connected to a power output cylinder (23), one end of the hydraulic oil pump (2) is mounted with a rotor (18), one end of the rotor (18) is mounted with a flyweight (17), a speed regulating spring (15) is connected to the flyweight (17), one end of the speed regulating spring (15) is connected to a connecting slide valve (16), the other end of the speed regulating spring (15) is connected to a speed regulating cylinder (14), the speed regulating cylinder (14) is connected to a recovery rod (13), the recovery rod (13) is connected to a cylinder (11), and one end of the recovery rod (13) is connected to a speed regulating slide valve (10).

2. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: The hydraulic oil pump (2) is provided with a one-way valve (3), and the number of the one-way valves (3) is four.

3. The electro-hydraulic composite speed regulator according to claim 2, characterized in that: An accumulator (5) is arranged between the one-way valve (3) and the filter (6), and a pressure valve (4) is arranged between the one-way valve (3) and the filter (6) and at the accumulator (5).

4. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: The electro-hydraulic servo valve (7) is provided with an A port, a P port and a T port.

5. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: The connecting slide valve (16) is provided with an A1 port, a P1 port and a T1 port.

6. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: The speed regulating sliding valve (10) is connected to a pressure reducing valve (9).

7. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: The recovery rod (13) is provided with a manual speed regulating knob (12).

8. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: A speed reduction pull rod (20) is installed between the power output oil cylinder (23) and the speed regulating cylinder (14).

9. The electro-hydraulic composite speed regulator according to claim 1, characterized in that: The power output cylinder (23) is connected to a buffer compensation device (21) and a needle valve (22); The speed regulating cylinder (14) is connected to a parking solenoid valve (19).

10. The electro-hydraulic composite speed regulator according to claim 9, characterized in that: The buffer compensation device (21) is provided with a B1 port.

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