Two-position two-way high-pressure large-flow high-speed switch valve

Abstract

The invention relates to the technical field of switch valves, and particularly discloses a two-position two-way high-pressure large-flow high-speed switch valve. The coil assembly comprises an outer magnetic pole, one end of the outer magnetic pole is provided with a coil cover, and the inner wall of the other end of the outer magnetic pole is fixedly connected with an inner magnetic pole abutting against the coil cover through a magnetism isolating ring. A coil frame is arranged between the inner magnetic pole and the outer magnetic pole, a coil is arranged on the coil frame, and a pouring piece is arranged between the coil and the outer magnetic pole. The valve can realize two-way circulation, is short in response time and can bear high pressure.

Description

Technical Field

[0001] The present invention relates to the technical field of on-off valves for fluid control, and particularly to a two-position two-way high-pressure large-flow high-speed on-off valve. Background Art

[0002] In recent years, with the progress of technology, a digital hydraulic technology based on high-speed on-off control of fluids by high-speed on-off valves has been developing rapidly. There is an urgent need for such key basic components, high-speed on-off valves, especially large-flow on-off valves.

[0003] High-pressure large-flow high-speed on-off valves impose requirements of large thrust, fast response, and bidirectional flow on their driving components. Disc electromagnets have been widely used in fields such as engine fuel injection systems and compressor variable displacement control due to the relatively large electromagnetic force generated within a certain stroke. However, the disc electromagnets in the above applications are all in a low-pressure environment, and their electromagnets are all encapsulated by injection molding, and cannot be used in industrial control and construction machinery and other fields where both the inlet and outlet of the valve are required to withstand high pressure and cannot meet the requirement of bidirectional flow. Summary of the Invention

[0004] The purpose of the present invention is to provide a two-position two-way high-pressure large-flow high-speed on-off valve to solve the problems mentioned in the background art that the on-off valve using the existing (injection-molded) disc electromagnet cannot withstand high pressure and cannot flow bidirectionally.

[0005] The present invention adopts the following technical solutions to achieve the invention purpose: A two-position two-way high-pressure large-flow high-speed on-off valve includes a coil assembly. The coil assembly includes an outer magnetic pole. One end of the outer magnetic pole is provided with a coil cover, and the inner wall of the other end is fixedly connected to an inner magnetic pole arranged against the coil cover through a magnetic isolation ring. A coil frame is arranged between the inner magnetic pole and the outer magnetic pole, a coil is arranged on the coil frame, and a perfusion member is arranged between the coil and the outer magnetic pole.

[0006] In the above-mentioned two-position two-way high-pressure large-flow high-speed on-off valve, the magnetic isolation ring is a stainless-steel magnetic isolation ring, and the magnetic isolation ring is welded to the inner magnetic pole and the outer magnetic pole.

[0007] In the above-mentioned two-position two-way high-pressure large-flow high-speed on-off valve, an O-ring and a retaining ring are arranged outside the outer magnetic pole.

[0008] In the above-mentioned two-position two-way high-pressure large-flow high-speed on-off valve, it includes a housing. One end of the housing is connected to a sealing sleeve, and the other end is connected to a valve body. The end of the valve body is connected to a locking nut. The coil assembly is arranged in the housing and the sealing sleeve. The ends of the outer magnetic pole, the inner magnetic pole, and the magnetic isolation ring are flush, and an armature is arranged at the adjacent position. A spring is sleeved on the armature, the spring is arranged on a spring seat, and a valve core is arranged in the armature and inside the valve body.

[0009] In the aforementioned two-position two-way high-pressure large-flow high-speed switching valve, a sealing seat is provided between the end of the valve core and the locking nut.

[0010] In the aforementioned two-position two-way high-pressure large-flow high-speed switching valve, the outer diameter D of the valve core is equal to the aperture diameter D of the sealing seat.

[0011] In the aforementioned two-position two-way high-pressure large-flow high-speed switching valve, a stop seat is provided between the end of the valve core and the locking nut, and a gasket is arranged between the stop seat and the valve body.

[0012] In the aforementioned two-position two-way high-pressure large-flow high-speed switching valve, the outer diameter D of the valve core is equal to the aperture diameter D of the valve body.

[0013] In the aforementioned two-position two-way high-pressure large-flow high-speed switching valve, the sealing sleeve is connected to an electrical connector.

[0014] Compared with the prior art, the present invention has the following beneficial effects: 1. In the present invention, a non-magnetic stainless steel magnetic isolation ring is welded between the magnetic poles of the disc electromagnet, the internal magnetic circuit of the magnetic poles is reasonably arranged, and a high-pressure seal retaining ring combination structure is adopted outside the electromagnet, so that the port adjacent to the valve and the electromagnet can withstand high pressure, meeting the requirements that the outlet can also withstand high pressure and bidirectional oil flow.

[0015] 2. In the present invention, a balanced cone valve structure is proposed. In the normally closed solenoid valve, the outer diameter of the valve core is the same as the aperture diameter of the sealing seat, and the outer diameter of the valve core in the normally closed solenoid valve is the same as the aperture diameter of the valve body. The characteristics of the formed switching valve are as follows: (1) The design of the electromagnet only needs to consider the constant traction force of the valve core and is not affected by high and low pressures; (2) The valve has the functions of bidirectional flow and bidirectional sealing and can be applied to a wider range of working conditions; (3) The balanced cone valve structure reduces the driving force required to drive the valve core to move and improves the response time.

[0016] 3. The valve flow rate of the switching valve of the present invention can reach 40 L / min (under a pressure difference of 1 MPa), and the response time reaches less than 5 ms; it can flow bidirectionally and can withstand a high pressure of more than 35 MPa. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is a schematic structural diagram of Embodiment 1 of the present invention; Figure 2 is a schematic structural diagram of the coil assembly of the present invention (the arrows in the figure indicate the welding positions); Figure 3 is a schematic structural diagram of the valve core of Embodiment 1 of the present invention; Figure 4 is a schematic diagram of the working state of Embodiment 1 of the present invention; Figure 5It is a schematic structural diagram of Embodiment 2 of the present invention; Figure 6 It is a schematic structural diagram of the spool of Embodiment 2 of the present invention; Figure 7 It is a schematic diagram of the working state of Embodiment 2 of the present invention.

[0018] The reference numerals in the drawings are: electrical connector 1, O-ring 2, sealing sleeve 3, housing 4, coil assembly 5, washer 6, armature 7, spring 8, spring seat 9, snap ring 10, spool 11, valve body 12, gasket 13, sealing seat 14, locking nut 15, gasket 16, stop seat 17; inner magnetic pole 51, magnetic isolation ring 52, outer magnetic pole 53, coil 54, coil holder 55, potting member 56, coil cover 57. Detailed implementation manners

[0019] Next, the technical solutions in the embodiments of the invention will be clearly and completely described in conjunction with the drawings in the embodiments of the invention. Obviously, the described embodiments are only a part of the embodiments of the invention, rather than all the embodiments.

[0020] Embodiment 1. A two-position two-way high-pressure large-flow high-speed switching valve. This switching valve is normally closed, and the structure is as Figure 1 shown, including a housing 4. One end of the housing 4 is connected to a sealing sleeve 3, and the other end is connected to a valve body 12. The end of the valve body 12 is connected to a locking nut 15; a coil assembly 5 is arranged in the housing 4 and the sealing sleeve 3. The ends of the outer magnetic pole 53, the inner magnetic pole 51 and the magnetic isolation ring 52 are flush, and an armature 7 is provided at the adjacent position. A spring 8 is sleeved on the armature 7, and the spring 8 is arranged on a spring seat 9. A spool 11 is arranged in the armature 7 and inside the valve body 12; the sealing sleeve 3 is connected to an electrical connector 1; the corresponding flow channels, O-rings 2, snap rings 10, etc. are arranged according to Figure 1 shown.

[0021] In this two-position two-way normally closed solenoid valve, the existing injection-molded encapsulated disc electromagnet that can only be used in a low-pressure environment is improved to a disc electromagnet that can withstand high pressure. The structure is referred to as Figure 2 shown. The coil assembly 5 includes an outer magnetic pole 53. One end of the outer magnetic pole 53 is provided with a coil cover 57, and the inner wall of the other end is fixedly connected to an inner magnetic pole 51 that abuts against the coil cover 57 through a magnetic isolation ring 52; a coil holder 55 is arranged between the inner magnetic pole 51 and the outer magnetic pole 53, a coil 54 is arranged on the coil holder 55, and a potting member 56 is arranged between the coil 54 and the outer magnetic pole 53.

[0022] The magnetic isolation ring 52 is a stainless-steel magnetic isolation ring. Using a non-magnetic-conducting stainless-steel magnetic isolation ring makes the internal magnetic circuit of the disc electromagnet reasonably arranged.

[0023] The magnetic isolation ring 52 is welded to the inner magnetic pole 51 and the outer magnetic pole 53; and with reference to Figure 2As described above, an O-ring 2 and a retaining ring 10 are provided outside the outer magnetic pole 53 to form a high-pressure sealing retaining ring combination structure. Through the above two settings, the port adjacent to the valve and the electromagnet can withstand high pressure, meeting the requirements that the outlet can also withstand high pressure and the oil can flow bidirectionally.

[0024] A sealing seat 14 is provided between the end of the valve core 11 and the locking nut 15.

[0025] A balanced poppet valve structure is adopted inside this switching valve. Refer to Figure 3 As shown, the outer diameter D1 of the valve core 11 is equal to the aperture D2 of the sealing seat 14. In this way, whether the high pressure enters from the bottom axial port or from the side radial port, the hydraulic pressure acting on the valve core 11 always remains balanced (cancels out to zero). In this way, neither high pressure nor low pressure will affect the movement of the valve core 11, and the traction force required for the valve core 11 to move always remains the same under high-pressure and low-pressure working conditions. The characteristics of adopting this valve structure are as follows: (1) The design of the electromagnet only needs to consider the constant traction force of the valve core and is not affected by high and low pressures; (2) The valve has the functions of bidirectional flow and bidirectional sealing, and can be applied to a wider range of working conditions; (3) The balanced poppet valve structure reduces the driving force required to drive the valve core to move and improves the response time.

[0026] The working principle of this switching valve is referred to Figure 1 As shown, when not energized, the valve core 11 is subjected to a downward spring force to generate a sealing pressure, causing it to closely adhere to the sealing seat 13, closing the flow channel, and the inlet and outlet are not in communication; after energization, the coil 54 generates a magnetic field, magnetizing the inner magnetic pole 51, the outer magnetic pole 52, the coil cover 57, and the armature 7, causing the armature 7 to be subjected to an upward electromagnetic force. The electromagnetic force overcomes the spring force and pulls the valve core 11 upward to produce a gap with the sealing seat 13, opening the flow channel, and the inlet and outlet communicate, refer to Figure 4 As shown.

[0027] After actual measurement, the valve flow rate of the above two-position two-way normally closed solenoid valve can reach 40 L / min (under a pressure difference of 1 MPa), and the response time reaches less than 5 ms; it can flow bidirectionally and can withstand a high pressure of more than 35 MPa.

[0028] Embodiment 2. A two-position two-way high-pressure large-flow high-speed switching valve. This switching valve is normally open and is configured as Figure 5 shown, including a housing 4. One end of the housing 4 is connected to a sealing sleeve 3, and the other end is connected to a valve body 12. The end of the valve body 12 is connected to a locking nut 15; a coil assembly 5 is provided in the housing 4 and the sealing sleeve 3. The ends of the outer magnetic pole 53, the inner magnetic pole 51, and the magnetic isolation ring 52 are flush, and an armature 7 is provided at the adjacent position. A spring 8 is sleeved on the armature 7, and the spring 8 is provided on a spring seat 9. A valve core 11 is provided in the armature 7 and inside the valve body 12; the sealing sleeve 3 is connected to an electrical connector 1; the corresponding flow channels, O-rings 2, retaining rings 10, etc. are arranged according to Figure 1as shown

[0029] Refer to as Figure 2 As shown, the coil assembly 5 includes an outer magnetic pole 53. One end of the outer magnetic pole 53 is provided with a coil cover 57, and the inner wall of the other end is fixedly connected to an inner magnetic pole 51 arranged by abutting against the coil cover 57 through a magnetic isolation ring 52; a coil holder 55 is arranged between the inner magnetic pole 51 and the outer magnetic pole 53, a coil 54 is arranged on the coil holder 55, and a perfusion member 56 is arranged between the coil 54 and the outer magnetic pole 53.

[0030] The magnetic isolation ring 52 is a stainless - steel magnetic isolation ring. Using a non - magnetic - conducting stainless - steel magnetic isolation ring enables a reasonable layout of the inner magnetic circuit of the disc - type electromagnet poles.

[0031] The magnetic isolation ring 52 is welded to the inner magnetic pole 51 and the outer magnetic pole 53; and refer to Figure 2 As described, an O - ring 2 and a retaining ring 10 are provided outside the outer magnetic pole 53 to form a high - pressure sealing retaining - ring combination structure. Through the above two settings, the port adjacent to the electromagnet of the valve can withstand high pressure, meeting the requirements that the outlet can also withstand high pressure and bidirectional oil flow.

[0032] A sealing seat 14 is provided between the end of the valve core 11 and the lock nut 15.

[0033] A balanced cone - valve structure is adopted inside this switching valve. Refer to Figure 6 As shown, the outer diameter D1 of the valve core 11 is equal to the aperture D3 of the valve body 12. In this way, whether the high pressure enters from the bottom axial port or from the side radial port, the hydraulic pressure acting on the valve core 11 always remains balanced (cancels out to zero). In this way, whether the pressure is high or low, it will not affect the movement of the valve core 11, and the traction force required for the movement of the valve core 11 under high - pressure and low - pressure working conditions always remains the same. The characteristics of adopting the structure of this valve are as follows: (1) The design of the electromagnet only needs to consider the constant traction force of the valve core and is not affected by high and low pressures; (2) The valve has the functions of bidirectional flow and bidirectional sealing, and can be applied to a wider range of working conditions; (3) The balanced cone - valve structure reduces the driving force required to drive the valve core to move and improves the response time.

[0034] The working principle of this switching valve refers to Figure 1 As shown, when not energized, the valve core 11 is subjected to a downward spring force, causing it to separate from the valve body 12 to generate a gap, and the inlet and outlet communicate; after being energized, the coil 54 generates a magnetic field, magnetizing the inner magnetic pole 51, the outer magnetic pole 52, the coil cover 57, and the armature 7, causing the armature 7 to be subjected to an upward electromagnetic force. After the electromagnetic force overcomes the spring force and provides a sealing pressure, the valve core 11 tightly adheres to the valve body 12, closing the flow channel, and the inlet and outlet do not flow. Refer to Figure 7 as shown.

[0035] After actual measurement, the valve flow rate of the above two-position two-way normally open solenoid valve can reach 40 L / min (under a pressure difference of 1 MPa), and the response time is less than 5 ms; it can flow bidirectionally and can withstand a high pressure of more than 35 MPa.

[0036] As mentioned above, it is only a preferred specific implementation manner of the invention, but the protection scope of the invention is not limited thereto. Any person skilled in the technical field, within the technical scope disclosed by the invention, according to the technical solution and concept of the invention, makes equivalent replacements or changes, and should be covered within the protection scope of the invention.

Claims

1. A two-position, two-way, high-pressure, large-flow, high-speed on-off valve, characterized in that: The invention comprises a coil assembly (5), wherein the coil assembly (5) comprises an outer magnetic pole (53), one end of the outer magnetic pole (53) is provided with a coil cover (57), and the inner wall of the other end is fixedly connected to an inner magnetic pole (51) provided against the coil cover (57) via a magnetic isolation ring (52); a coil frame (55) is provided between the inner magnetic pole (51) and the outer magnetic pole (53), a coil (54) is provided on the coil frame (55), and a casting piece (56) is provided between the coil (54) and the outer magnetic pole (53).

2. The two-position two-way high-pressure large-flow high-speed on-off valve according to claim 1 is characterized in that: The magnetic isolation ring (52) is a stainless steel magnetic isolation ring, and the magnetic isolation ring (52) is welded to the inner magnetic pole (51) and the outer magnetic pole (53).

3. The two-position two-way high-pressure large-flow high-speed on-off valve according to claim 2 is characterized in that: An O-ring (2) and a retaining ring (10) are provided outside the outer magnetic pole (53).

4. The two-position two-way high-pressure large-flow high-speed on-off valve according to claim 1 is characterized in that: The invention comprises a housing (4), one end of the housing (4) is connected to a sealing screw sleeve (3), the other end of the housing (4) is connected to a valve body (12), and the end of the valve body (12) is connected to a locking nut (15); a coil assembly (5) is arranged in the housing (4) and the sealing screw sleeve (3), the ends of an outer magnetic pole (53), an inner magnetic pole (51) and a magnetic isolation ring (52) are flush and an armature (7) is arranged at adjacent positions, a spring (8) is arranged on the armature (7), the spring (8) is arranged on a spring seat (9), and a valve core (11) is arranged in the armature (7) and inside the valve body (12).

5. The two-position two-way high-pressure large-flow high-speed on-off valve according to claim 4 is characterized in that: A sealing seat (14) is provided between the end of the valve core (11) and the locking nut (15).

6. The two-position, two-way, high-pressure, large-flow, high-speed on-off valve according to claim 5, characterized in that: The outer diameter D (1) of the valve core (11) is equal to the hole diameter D (2) of the sealing seat (14).

7. The two-position two-way high-pressure large-flow high-speed on-off valve according to claim 4 is characterized in that: A stop seat (17) is provided between the end of the valve core (11) and the locking nut (15), and a gasket (16) is provided between the stop seat (17) and the valve body (12).

8. The two-position, two-way, high-pressure, large-flow, high-speed on-off valve according to claim 7 is characterized in that: The outer diameter D (1) of the valve core (11) is equal to the hole diameter D (3) of the valve body (12).

9. The two-position two-way high-pressure large-flow high-speed on-off valve according to claim 4 is characterized in that: The sealing screw sleeve (3) is connected to the electrical connector (1).

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