Electric control main valve

Abstract

The utility model discloses an electric control main valve which comprises a proportional reversing valve, a proportional pressure reducing valve oil inlet and return opening is formed in the lower side of the outer wall of the proportional reversing valve, a pilot control oil return opening is formed in the upper side of the outer wall of the proportional reversing valve, and an LS opening is formed in the position, located at one end of the pilot control oil return opening, of the upper side of the outer wall of the proportional reversing valve. The Degree core double-end proportional electromagnet is fixedly connected to the outer wall of the bottom of the proportional reversing valve, an electro-hydraulic reversing seat is fixed to one side of the proportional reversing valve, an electro-hydraulic spring end is fixed to the other side of the proportional reversing valve, and the Degree core double-end proportional electromagnet is located at the bottom of the electro-hydraulic spring end; and a head piece connecting block. The problems that at present, products used by most of domestic manufacturers are limited to the structure / principle characteristics of the products, performance optimization of the products cannot be met under some functions and (limit / special) working condition environments required by a high-altitude vehicle, and meanwhile, main engine plants cannot be switched and used in batches due to the fact that installation interchangeability of other types of valves is limited are solved.

Description

Technical Field

[0001] The utility model relates to the technical field of load-sensitive electro-hydraulic proportional multi-way valves, and particularly relates to an electronically controlled main valve. Background Technique

[0002] With the continuous development of industrial automation and the increasing combination of mechanical, electrical and hydraulic technologies, electro-hydraulic proportional multi-way valves will be applied in more fields, and the technical requirements for electro-hydraulic proportional multi-way valves are getting higher and higher. It is required to have higher control accuracy, faster response speed, simplified structure, less leakage and higher cost performance, which is of great significance for simplifying the operation of construction machinery, improving efficiency and operation accuracy, and realizing intelligent operation.

[0003] However, it still has the following disadvantages in actual use:

[0004] At present, the products used by most domestic manufacturers are limited by their own structural / principles characteristics and cannot meet the performance optimization under some functions and (extreme / special) working conditions required by aerial work platforms. At the same time, other types of valves are limited in installation interchangeability, resulting in the inability of the main engine factory to switch and use them in batches. Content of the Utility Model

[0005] Technical Solution to be Solved

[0006] The purpose of the utility model is to provide an electronically controlled main valve to solve the problem that the products used by most domestic manufacturers at present are limited by their own structural / principles characteristics and cannot meet the performance optimization under some functions and (extreme / special) working conditions required by aerial work platforms. At the same time, other types of valves are limited in installation interchangeability, resulting in the inability of the main engine factory to switch and use them in batches as mentioned in the above background technique.

[0007] Technical Solution

[0008] To solve the above technical problems, the utility model is realized through the following technical solutions:

[0009] The utility model provides an electronically controlled main valve, including:

[0010] A proportional direction valve, an AB signal acquisition port is fixedly connected to the outer wall of the proportional direction valve, a proportional pressure reducing valve inlet and return oil port is opened on the lower side of the outer wall of the proportional direction valve, a pilot control return oil port is opened on the upper side of the outer wall of the proportional direction valve, and an LS port is opened at one end of the upper side of the outer wall of the proportional direction valve and located at one end of the pilot control return oil port;

[0011] The Dechi 2-core double-headed proportional electromagnet is fixedly connected to the outer wall of the bottom of the proportional direction valve. One side of the proportional direction valve is fixedly connected with an electro-hydraulic direction seat, and the other side of the proportional direction valve is fixedly connected with an electro-hydraulic spring end. The Dechi 2-core double-headed proportional electromagnet is located at the bottom of the electro-hydraulic spring end;

[0012] The head piece connecting block is fixedly connected to the outer wall of the proportional direction valve on one side.

[0013] Furthermore, the oil port sizes of the inlet and return oil ports and the pilot control return oil port of the proportional pressure reducing valve can be G3 / 8, G1 / 2, G3 / 4, M18*1.5, M22*1.5, M27*2, etc.;

[0014] Furthermore, the outlet directions of the plugs of the Dechi 2-core double-headed proportional electromagnet are all on the same side and are 90° relative to the oil port mounting surface. The space height of the plugs of the Dechi 2-core double-headed proportional electromagnet conforms to the actual installation position of the whole vehicle without interference;

[0015] Furthermore, the electro-hydraulic spring end includes a main spool movably connected to one side, and a reversing screw is threadedly connected to the outer wall of the electro-hydraulic spring end;

[0016] Furthermore, an inner spring is sleeved on the circumferential outer wall of one end of the main spool extending into the inner cavity of the electro-hydraulic spring end. An outer spring is sleeved on the circumferential outer wall of the inner spring, and a spring retaining ring is movably connected to the circumferential inner wall of the inner spring;

[0017] Furthermore, the spring retaining ring is located at the connection between the electro-hydraulic spring end and the proportional direction valve. A proportional pressure reducing valve spool is fixed to the upper side of the inner cavity of the electro-hydraulic spring end, and a proportional pressure reducing valve sleeve is sleeved on the circumferential outer wall of the proportional pressure reducing valve spool;

[0018] Furthermore, a pressure extraction plug is fixed to the inner cavity of the electro-hydraulic spring end, which is vertically corresponding to the proportional pressure reducing valve spool. A fixed differential pressure reducing valve in the same direction as the pressure extraction plug is fixed to the inner cavity of the electro-hydraulic spring end;

[0019] Beneficial effects

[0020] Compared with the prior art, the advantages of the present utility model are as follows:

[0021] 1. In the present utility model, when one side of the coil of the Dechi 2-core double-headed proportional electromagnet is energized, it pushes the spool of the double proportional pressure reducing valve to commutate. The pilot control oil enters the electro-hydraulic spring end along the pilot oil path through the oil port of the proportional pressure reducing valve, thereby pushing the main spool to move to control the direction and flow rate of the oil. Since a fixed differential pressure reducing valve is provided in front of the reversing valve, the pressure after decompression has nothing to do with the supply oil pressure and is only determined by the spring force, and is proportional to the magnitude of the input signal current. When the opening of the valve port remains unchanged, the flow rate of the valve port does not change either, and its magnitude is also proportional to the input current. By using a load-sensitive electro-hydraulic pilot proportional multi-way valve, it solves the existing functional problems in the existing valve groups in the current aerial work platform field, such as insufficient current driving force, amplitude change action jitter, large opening current error of the commutator in low-temperature environments, etc., providing a new application option for the main valve of the aerial work platform and forming a new set of standard specifications.

[0022] Of course, it is not necessary for any product implementing the present utility model to achieve all the above-mentioned advantages simultaneously. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the technical solutions of the embodiments of the present utility model, the accompanying drawings required for describing the embodiments will be briefly introduced below. Obviously, the accompanying drawings in the following description are only some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0024] Figure 1 Schematic diagram of the proportional reversing valve of the present utility model;

[0025] Figure 2 Exploded view of the electro-hydraulic spring end of the present utility model;

[0026] Figure 3 Cross-section of the proportional reversing valve of the present utility model Figure 1 ;

[0027] Figure 4 Cross-section of the proportional reversing valve of the present utility model Figure 2 ;

[0028] Figure 5 Schematic diagram of the overall structure of the present utility model.

[0029] In the accompanying drawings, the list of components represented by each reference numeral is as follows:

[0030] 1. AB signal acquisition port; 2. Deutsch 2-core double-headed proportional solenoid; 3. Electro-hydraulic reversing seat; 4. Electro-hydraulic spring end; 5. Inlet and outlet ports of the proportional pressure reducing valve; 6. Pilot control oil return port; 7. LS port; 8. Main spool valve; 9. Outer spring; 10. Inner spring; 11. Spring retaining ring; 12. Proportional pressure reducing valve spool; 13. Proportional pressure reducing valve sleeve; 14. Pressure extraction plug; 15. Fixed differential pressure reducing valve; 16. Proportional reversing valve; 17. Head piece connecting block; 18. Reversing screw. Detailed implementation mode

[0031] To make the above objects, features, and advantages of the present utility model more obvious and understandable, the following will describe the detailed implementation mode of the present utility model in conjunction with the accompanying drawings.

[0032] In the following description, many specific details are set forth to fully understand the present utility model. However, the present utility model can also be implemented in other ways different from those described herein. Those skilled in the art can make similar generalizations without departing from the connotation of the present utility model. Therefore, the present utility model is not limited by the specific implementation modes disclosed below.

[0033] To make the purpose, technical solution, and advantages of the present utility model clearer, the following will further describe the implementation mode of the present utility model in detail in conjunction with the accompanying drawings.

[0034] In the description of the present application, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application. In addition, the terms "first", "second", "third" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0035] Embodiment 1

[0036] Please refer to Figures 1-5 As shown, this embodiment is an electro-controlled main valve, including:

[0037] A proportional reversing valve 16, the outer wall of the proportional reversing valve 16 is fixedly connected with an AB signal acquisition port 1, the lower side of the outer wall of the proportional reversing valve 16 is provided with inlet and outlet ports 5 of the proportional pressure reducing valve, the upper side of the outer wall of the proportional reversing valve 16 is provided with a pilot control oil return port 6, and the upper side of the outer wall of the proportional reversing valve 16 is provided with an LS port 7 at one end of the pilot control oil return port 6;

[0038] The oil pressure output and input at the oil inlet and outlet 5 of the proportional pressure reducing valve and the pilot control oil return port 6 are fed back through the AB signal acquisition port 1, and the pressure value is detected through the LS port 7;

[0039] The Dechi 2-core double-headed proportional electromagnet 2 is fixedly connected to the outer wall at the bottom of the proportional directional valve 16. An electro-hydraulic directional seat 3 is fixedly connected to one side of the proportional directional valve 16, and an electro-hydraulic spring end 4 is fixedly connected to the other side of the proportional directional valve 16. The Dechi 2-core double-headed proportional electromagnet 2 is located at the bottom of the electro-hydraulic spring end 4;

[0040] By energizing one side coil of the Dechi 2-core double-headed proportional electromagnet 2, the proportional pressure reducing solenoid valve is energized, and the pilot control oil return port 6 can push the double proportional pressure reducing valve spool 12 to commutate through the oil inlet and outlet 5 of the proportional pressure reducing valve and enter the electro-hydraulic spring end 4 along the pilot oil circuit;

[0041] The head piece connection block 17 is fixedly connected to the outer wall of the proportional directional valve 16 on one side;

[0042] The entire device is connected to the mechanism to be connected through the head piece connection block 17;

[0043] The oil port sizes of the oil inlet and outlet 5 of the proportional pressure reducing valve and the pilot control oil return port 6 can be G3 / 8, G1 / 2, G3 / 4, M18*1.5, M22*1.5, M27*2, etc.;

[0044] The pilot control oil return port 6 is returned through the handle end of the electro-hydraulic directional seat 3;

[0045] The outlet directions of the plugs of the Dechi 2-core double-headed proportional electromagnet 2 are all on the same side and are 90° relative to the oil port mounting surface. The space height of the plugs of the Dechi 2-core double-headed proportional electromagnet 2 conforms to the actual installation position of the whole vehicle without interference;

[0046] Ensure that the installation does not affect the entire device;

[0047] The electro-hydraulic spring end 4 includes a main spool 8 movably connected to one side. A reversing screw 18 is threadedly connected to the outer wall of the electro-hydraulic spring end 4;

[0048] A inner spring 10 is sleeved on the circumferential outer wall of the end of the main spool 8 extending into the inner cavity of the electro-hydraulic spring end. An outer spring 9 is sleeved on the circumferential outer wall of the inner spring 10. A spring retaining ring 11 is movably connected to the circumferential inner wall of the inner spring 10;

[0049] The main spool 8 is pushed to move by the inner spring 9 and the outer spring 10;

[0050] The spring retaining ring 11 is located at the connection between the electro-hydraulic spring end 4 and the proportional directional valve 16. A proportional pressure reducing valve spool 12 is fixed to the upper side of the inner cavity of the electro-hydraulic spring end 4. A proportional pressure reducing valve sleeve 13 is sleeved on the circumferential outer wall of the proportional pressure reducing valve spool 12;

[0051] The inner spring 9 and the outer spring 10 are limited by a spring retaining ring 11, and the double proportional relief valve spool 12 is pushed to reverse by the oil inlet and outlet 5 of the proportional relief valve;

[0052] A pressure extraction plug 14 is fixed in the inner cavity of the electro-hydraulic spring end 4. The pressure extraction plug 14 is vertically corresponding to the proportional relief valve spool 12. A fixed-differential relief valve 15 in the same direction as the pressure extraction plug 14 is fixed in the inner cavity of the electro-hydraulic spring end 4;

[0053] The fluid direction is controlled by the pressure extraction plug 14, and the pressure after decompression is separated from the oil supply pressure by the fixed-differential relief valve 15;

[0054] Working principle: When one side coil of the Dechi 2-core double-headed proportional electromagnet 2 is energized, it pushes the double proportional relief valve spool 12 to reverse. The pilot control oil enters the electro-hydraulic spring end 4 along the pilot oil path through the proportional relief valve oil port, thereby pushing the main spool 8 to move to control the oil direction and flow rate. Since there is a fixed-differential relief valve 15 in front of the proportional reversing valve 16, the pressure after decompression has nothing to do with the oil supply pressure and is only determined by the spring force and is proportional to the input signal current magnitude; when the opening of the valve port remains unchanged, the valve port flow rate does not change either, and its magnitude is also proportional to the input current. A load-sensitive electro-hydraulic pilot proportional multi-way valve is adopted;

[0055] This step solves the existing functional problems in the existing valve groups in the aerial work vehicle field, such as insufficient current driving force, amplitude variation jitter, large opening current error of the commutator in low-temperature environments, etc., provides a new application option for the main valve of the aerial work vehicle, and forms a new set of specification standards.

[0056] In the description of the present invention, it should also be noted that unless otherwise clearly specified and limited, the terms "set", "installed", "connected", and "connected" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0057] Finally, it should be noted that the above are only the preferred embodiments of the present invention and are not used to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, for those skilled in the art, they can still modify the technical solutions recorded in the foregoing embodiments, or perform equivalent replacements for some of the technical features. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. An electrically controlled main valve, characterized in that: include: A proportional reversing valve (16), wherein an AB signal acquisition port (1) is fixedly connected to an outer wall of the proportional reversing valve (16), a proportional pressure reducing valve oil inlet and return port (5) is provided on the lower side of the outer wall of the proportional reversing valve (16), a pilot control oil return port (6) is provided on the upper side of the outer wall of the proportional reversing valve (16), and an LS port (7) is provided on the upper side of the outer wall of the proportional reversing valve (16) at one end of the pilot control oil return port (6); A DEUTSCH 2-core double-headed proportional electromagnet (2) is fixedly connected to the outer wall of the bottom of the proportional reversing valve (16); an electro-hydraulic reversing seat (3) is fixed on one side of the proportional reversing valve (16); an electro-hydraulic spring end (4) is fixed on the other side of the proportional reversing valve (16); and the DEUTSCH 2-core double-headed proportional electromagnet (2) is located at the bottom of the electro-hydraulic spring end (4); The head piece connecting block (17) is fixedly connected to the outer wall of the proportional reversing valve (16) on one side.

2. An electrically controlled main valve according to claim 1, characterized in that: The oil port sizes of the proportional pressure reducing valve oil inlet and return port (5) and the pilot control oil return port (6) can be G3 / 8, G1 / 2, G3 / 4, M18*1.5, M22*1.5, or M27*2.

3. The electrically controlled main valve according to claim 1, characterized in that: The outlet directions of the plug of the DEUTSCH 2-core double-headed proportional electromagnet (2) are all on the same side and are 90 degrees relative to the oil port installation surface. The spatial height of the plug of the DEUTSCH 2-core double-headed proportional electromagnet (2) conforms to the actual installation position of the vehicle and does not interfere.

4. The electrically controlled main valve according to claim 1, characterized in that: The electro-hydraulic spring end (4) comprises a main valve core (8) movably connected to one side, and a reversing screw (18) is threadedly connected to the outer wall of the electro-hydraulic spring end (4).

5. An electrically controlled main valve according to claim 4, characterized in that: The main valve core (8) extends into the inner cavity of the electro-hydraulic spring and has an inner spring (10) sleeved on its circumferential outer wall. An outer spring (9) is sleeved on the circumferential outer wall of the inner spring (10). A spring retaining ring (11) is movably connected to the circumferential inner wall of the inner spring (10).

6. An electrically controlled main valve according to claim 5, characterized in that: The spring retaining ring (11) is located at the connection between the electro-hydraulic spring end (4) and the proportional reversing valve (16); a proportional pressure reducing valve core (12) is fixed on the upper side of the inner cavity of the electro-hydraulic spring end (4); and a proportional pressure reducing valve sleeve (13) is sleeved on the circumferential outer wall of the proportional pressure reducing valve core (12).

7. The electrically controlled main valve according to claim 1, characterized in that: A pressure outlet plug (14) is fixed in the inner cavity of the electro-hydraulic spring end (4), the pressure outlet plug (14) corresponds vertically to the proportional pressure reducing valve core (12), and a differential pressure reducing valve (15) is fixed in the inner cavity of the electro-hydraulic spring end (4) in the same direction as the pressure outlet plug (14).

Images