Hydraulic adjusting electromagnetic valve with front end of double-spring structure

Abstract

The utility model discloses an electromagnetic valve with a front-end double-spring structure for hydraulic adjustment, which relates to the technical field of pilot valves and comprises a coil assembly, an electromagnet assembly and a main valve sleeve assembly, and the coil assembly and the main valve sleeve assembly are respectively assembled at two ends of the electromagnet assembly. The main valve sleeve assembly comprises a main valve sleeve, an end cover, a main valve element, a main spring, an auxiliary spring and a piston sleeve, one end of the main valve sleeve is assembled on the electromagnet assembly, the end cover is assembled at the other end of the main valve sleeve, the piston sleeve is fixedly assembled in the main valve sleeve, the main valve element is assembled in the main valve sleeve in a sliding mode, and the auxiliary spring is assembled in the main valve sleeve. The main valve element is located between the piston sleeve and the end cover, the piston sleeve is sleeved with the main spring and the auxiliary spring, and the end, away from the piston sleeve, of the main spring and the end, away from the piston sleeve, of the auxiliary spring make contact with the main valve element. The problems that a pilot valve is poor in performance stability and consistency and small in product pressure regulating interval distinction degree are solved.

Description

TECHNICAL FIELD

[0001] The utility model relates to pilot valve technical field, concretely is a front end double spring structure hydraulic pressure adjustment solenoid valve. BACKGROUND

[0002] The key component of suspension damping control is pilot valve. The existing pilot valve is basically external type, and the front end of the main valve has only one main spring. The initial compression amount of the main spring after assembly is affected by the axial dimensions of the main valve sleeve, gasket, end cover, piston sleeve and pilot valve sleeve. Because the stiffness of the main spring is usually large, the spring force value of the main spring after assembly is greatly different, which directly leads to poor pressure consistency and stability under small flow during valve body testing, and small pressure interval division. SUMMARY

[0003] The utility model discloses a front end double spring structure hydraulic pressure adjustment solenoid valve which overcomes the defects of the prior art.

[0004] The utility model discloses a front end double spring structure hydraulic pressure adjustment solenoid valve, which comprises a coil assembly, an electromagnet assembly and a main valve sleeve assembly. The coil assembly and the main valve sleeve assembly are respectively assembled at the two ends of the electromagnet assembly. The main valve sleeve assembly comprises a main valve sleeve, an end cover, a main valve core, a main spring, a secondary spring and a piston sleeve. One end of the main valve sleeve is assembled on the electromagnet assembly, and the other end is assembled with the end cover. The piston sleeve is fixedly assembled in the main valve sleeve. The main valve core is slidably assembled in the main valve sleeve. The main valve core is located between the piston sleeve and the end cover. The main spring and the secondary spring are sleeved on the piston sleeve. The ends of the main spring and the secondary spring away from the piston sleeve are in contact with the main valve core.

[0005] Further, two step surfaces are formed in the piston sleeve in the direction close to the main valve core. Two step surfaces are formed on the end surface of the main valve core close to the piston sleeve. The two ends of the main spring are respectively abutted on one of the step surfaces and one of the step surfaces. The two ends of the secondary spring are respectively abutted on the other step surface and the other step surface.

[0006] Further, the main valve sleeve assembly further comprises a piston rod, a pilot valve sleeve and a pilot valve core. The end surface of the piston sleeve away from the main valve core is provided with the pilot valve sleeve. The pilot valve core is slidably assembled in the main valve sleeve. The pilot valve sleeve is located between the pilot valve core and the piston sleeve. The pilot valve sleeve and the pilot valve core are assembled with a pilot spring. The end of the pilot valve core close to the piston sleeve is fixedly provided with the piston rod. The pilot valve sleeve is provided with a through hole for the piston rod to pass through.

[0007] Further, a tapered hole is formed in the piston sleeve near one end of the pilot valve sleeve along the axial direction of the piston sleeve, the diameter of the tapered hole gradually decreases in the direction away from the pilot valve sleeve, and the tapered hole is located on the moving path of the piston rod.

[0008] Further, the electromagnet assembly comprises a shell, a pole shoe body and a magnetic core shaft, the shell is assembled on the coil assembly, the pole shoe body is assembled in the shell, the main valve sleeve is assembled on the pole shoe body, the magnetic core shaft is slidingly arranged in the pole shoe body, and the pilot valve core is located on the moving path of the magnetic core shaft.

[0009] Further, the pole shoe body is sequentially provided with a guide bearing seat, a magnetic core and a magnetic core seat in the pole shoe body in the direction close to the main valve sleeve, and the magnetic core shaft sequentially penetrates the guide bearing seat, the magnetic core and the magnetic core seat.

[0010] Further, a guide bearing is arranged between the magnetic core shaft and the guide bearing seat, and a magnetic core seat guide bearing is arranged between the magnetic core shaft and the magnetic core seat.

[0011] Further, the shell is assembled on the coil assembly through a shell clasp, and a coil sealing ring and a shell sealing ring are sleeved on the shell.

[0012] Further, a pole shoe body sealing ring is arranged between the shell and the pole shoe body.

[0013] Further, a gasket is arranged between the main valve sleeve and the end cover.

[0014] The beneficial effects of the present utility model are as follows:

[0015] When the electromagnetic valve works, the flow changes from small to large, at small flow, the piston spring can effectively provide support for the main valve core, so as to control the gap between the main valve core and the end cover; at large flow, the main spring is involved, and the two springs jointly provide support for the main valve core, so as to control the gap between the main valve core and the end cover; the stiffness of the plug spring is designed to be much smaller than that of the main spring, so the difference of the spring support force of the main valve core in the initial state is very small, and the consistency and stability of the performance in the initial state are effectively controlled; moreover, because the spring force value of the main valve core under large and small flow is adjusted in a large interval, the product pressure adjustment interval is further increased. BRIEF DESCRIPTION OF DRAWINGS

[0016] Figure 1 It is an internal structure schematic view of the electromagnetic valve with the front-end double-spring structure for hydraulic pressure adjustment;

[0017] Figure 2 It is a structure schematic view of the piston sleeve in the electromagnetic valve with the front-end double-spring structure for hydraulic pressure adjustment;

[0018] Figure 3 It is the assembly diagram of piston sleeve and auxiliary spring in the utility model;

[0019] Figure 4 It is the structure diagram of main valve sleeve assembly of the electromagnetic valve for hydraulic pressure adjustment with front end double spring structure in the utility model;

[0020] Figure 5 It is the structure diagram of the electromagnetic valve for hydraulic pressure adjustment with front end double spring structure in the utility model;

[0021] In the figure, 1-coil assembly, 2-housing clasp, 3-coil sealing ring, 4-housing, 5-housing sealing ring, 6-pole shoe body seal, 7-pole shoe body, 8-main valve sleeve, 9-gasket, 10-end cover, 11-main valve core, 12-main spring, 13-auxiliary spring, 14-piston sleeve, 15-piston rod, 16-pilot valve sleeve, 17-pilot spring, 18-pilot valve core, 19-magnetic core seat, 20-magnetic core seat guide bearing, 21-magnetic core shaft, 22-magnetic core, 23-guide bearing seat, 24-guide bearing, 25-electromagnet assembly, 26-main valve sleeve assembly. DETAILED DESCRIPTION

[0022] Example One

[0023] As Figures 1 to 5As shown, a front-end double-spring structure hydraulic regulating solenoid valve, comprising a coil assembly 1, an electromagnet assembly 25 and a main valve sleeve assembly 26, the coil assembly 1 and the main valve sleeve assembly 26 are respectively assembled at both ends of the electromagnet assembly 25, the main valve sleeve assembly 26 comprises a main valve sleeve 8, an end cover 10, a main valve core 11, a main spring 12, a secondary spring 13 and a piston sleeve 14, one end of the main valve sleeve 8 is assembled on the electromagnet assembly 25, the other end is assembled with the end cover 10, a central hole is formed through the end cover 10, the piston sleeve 14 is fixedly assembled in the main valve sleeve 8, the main valve core 11 is slidingly assembled in the main valve sleeve 8, the main valve core 11 is located between the piston sleeve 14 and the end cover 10, the main valve core 11 is provided with a flow guide small hole, the main spring 12 and the secondary spring 13 are sleeved on the piston sleeve 14, one end of the main spring 12 away from the piston sleeve 14 and one end of the secondary spring 13 away from the piston sleeve 14 both contact the main valve core 11, the flow of the solenoid valve changes from small to large during operation, when the flow is small, the secondary spring 13 can effectively provide support for the main valve core 11, so as to control the gap between the main valve core 11 and the end cover 10; when the flow is large, the main spring 12 intervenes, the main spring 12 and the secondary spring 13 jointly provide support for the main valve core 11, and control the gap between the main valve core 11 and the end cover 10; the rigidity of the secondary spring 13 is designed to be much smaller than that of the main spring 12, so the difference in spring support force of the main valve core 11 in the initial state is very small, effectively controlling the consistency and stability of the performance in the initial state; moreover, because the spring force value adjustment interval of the main valve core 11 is large under small and large flow, the product pressure adjustment interval is increased.

[0024] Example two

[0025] Based on example one, as shown, Figures 1 to 3 the piston sleeve 14 is sequentially formed with two step surfaces in the direction close to the main valve core 11, the end surface of the main valve core 11 close to the piston sleeve 14 is formed with two step surfaces, the two ends of the main spring 12 are respectively abutted on one step surface and one step surface, and the two ends of the secondary spring 13 are respectively abutted on the other step surface and the other step surface, thereby completing the installation of the main spring 12 and the secondary spring 13, the secondary spring 13 is located in the main spring 12, and the main valve core 11 is supported by the secondary spring 13 and the main spring 12; after the main valve sleeve assembly 26 is assembled, the secondary spring 13 is in a compressed state, the free length of the main spring 12 is less than the total length of the installation cavity by 0.3mm, and the main valve core 11 is pressed by the secondary spring 13 to ensure that the upper end surface of the main valve core 11 is in close contact with the end cover 10.

[0026] Example three

[0027] Based on example two, as shown, Figures 1 to 5As shown, the main valve sleeve assembly 26 further comprises a piston rod 15, a pilot valve sleeve 16 and a pilot valve core 18, the end of the piston sleeve 14 away from the end face of the main valve core 11 is provided with the pilot valve sleeve 16, the pilot valve core 18 is slidingly assembled in the main valve sleeve 8, the pilot valve sleeve 16 is located between the pilot valve core 18 and the piston sleeve 14, the pilot spring 17 is assembled between the pilot valve sleeve 16 and the pilot valve core 18, the piston rod 15 is fixed to the end of the pilot valve core 18 close to the piston sleeve 14, the pilot valve sleeve 16 is provided with a through hole for the piston rod 15 to pass through, the end of the piston sleeve 14 close to the pilot valve sleeve 16 is provided with a tapered hole along the axial direction of the piston sleeve 14, the diameter of the tapered hole gradually decreases along the direction away from the pilot valve sleeve 16, the tapered hole is located on the moving path of the piston rod 15, the electromagnet assembly 25 comprises a housing 4, an armature body 7 and a magnetic core shaft 21, the housing 4 is assembled on the coil assembly 1, the armature body 7 is assembled in the housing 4, the main valve sleeve 8 is assembled on the armature body 7, the magnetic core shaft 21 is slidingly arranged in the armature body 7, the pilot valve core 18 is located on the moving path of the magnetic core shaft 21, the armature body 7 is sequentially assembled with a guide bearing seat 23, a magnetic core 22 and a magnetic core seat 19 in the direction close to the main valve sleeve 8, the magnetic core shaft 21 sequentially passes through the guide bearing seat 23, the magnetic core 22 and the magnetic core seat 19, the coil assembly 1 is controlled by the current input from the outside, which belongs to the prior art and will not be described here, the magnetic circuit formed between the housing 4, the armature body 7 and the magnetic core 22 and the magnetic core seat 19 drives the magnetic core shaft 21 on the magnetic core 22 to move, the movement of the magnetic core shaft 21 drives the pilot valve core 18 to move towards the pilot valve sleeve 16 against the elastic force of the pilot spring 17 and the pressure formed by the piston sleeve 14 entering the liquid, when the gap between the pilot valve core 18 and the pilot valve sleeve 16 gradually decreases, at the same time, the piston rod 15 is pushed by the pilot valve core 18, the gap between the front end inclined surface of the piston rod 15 and the inclined surface of the inner hole of the piston sleeve 14 decreases, the flow cutting effect increases, the liquid flow into the piston sleeve 14 decreases, and the liquid pressure close to the piston sleeve 14 of the main valve core 11 connected through the flow channel on the piston sleeve 14 increases, the liquid pressure at this point is superimposed with the spring force of the main spring 12 and the auxiliary spring 13, which exceeds the hydraulic pressure of the liquid flowing from the end cover 10 into the main valve core 11, the main valve core 11 moves towards the end cover 10, the gap between them decreases, the flow cutting effect increases, resulting in a linear decrease in the flow of the liquid flowing from the outside, forming a controllable flow pressure regulating mechanism. It should be noted that the stiffness of the auxiliary spring 13 is usually smaller than that of the main spring 12, which provides support force for the main valve core 11 at small flow to regulate the flow gap; as the flow increases, the front end of the main valve core 11 is pushed backward by the increasing liquid pressure, the auxiliary spring 13 is compressed, the inner hole bottom surface of the main valve core 11 contacts the main spring 12, and the main spring 12 is gradually compressed, at this time, the auxiliary spring 13 and the main spring 12 provide support force for the main valve core 11 to regulate the flow gap.

[0028] In summary, this dual-spring structure at the front end ensures that the spring support force of the main valve core 11 is small in the initial state after assembly, thereby ensuring product consistency and stability. Furthermore, the optimized main valve core 11 has a large spring force adjustment range under large and small flow rates, which further increases the product's pressure regulation range differentiation.

[0029] Example 4

[0030] Based on Example 3, such as Figure 1 As shown, a guide bearing 24 is provided between the magnetic core shaft 21 and the guide bearing seat 23, and a magnetic core seat guide bearing 20 is provided between the magnetic core shaft 21 and the magnetic core seat 19 to complete the sliding assembly of the magnetic core shaft 21. The outer shell 4 is assembled onto the coil assembly 1 by the outer shell retaining ring 2. The outer shell 4 is fitted with a coil sealing ring 3 and an outer shell sealing ring 5 to improve the sealing performance of the outer shell 4 installation. A pole shoe sealing ring 6 is provided between the outer shell 4 and the pole shoe body 7 to improve the sealing performance between the outer shell 4 and the pole shoe body 7. A gasket 9 is provided between the main valve sleeve 8 and the end cover 10.

Claims

1. A front-end double-spring structure hydraulic pressure regulating solenoid valve, comprising a coil assembly (1), an electromagnet assembly (25) and a main valve sleeve assembly (26), the coil assembly (1) and the main valve sleeve assembly (26) are respectively assembled at both ends of the electromagnet assembly (25), characterized in that, The main valve sleeve assembly (26) comprises a main valve sleeve (8), an end cover (10), a main valve core (11), a main spring (12), a secondary spring (13) and a piston sleeve (14), one end of the main valve sleeve (8) is assembled on the electromagnet assembly (25), the other end is assembled with the end cover (10), the piston sleeve (14) is fixedly assembled in the main valve sleeve (8), the main valve core (11) is slidingly assembled in the main valve sleeve (8), the main valve core (11) is located between the piston sleeve (14) and the end cover (10), the main spring (12) and the secondary spring (13) are sleeved on the piston sleeve (14), and one end of the main spring (12) away from the piston sleeve (14) and one end of the secondary spring (13) away from the piston sleeve (14) are in contact with the main valve core (11).

2. The electromagnetic valve for hydraulic pressure regulation with a front end double spring structure according to claim 1, characterized in that, The piston sleeve (14) is formed with two stepped surfaces in sequence in the direction close to the main valve core (11), the end surface of the main valve core (11) close to the piston sleeve (14) is formed with two stepped surfaces, the two ends of the main spring (12) are respectively abutted on one of the stepped surfaces and one of the stepped surfaces, and the two ends of the secondary spring (13) are respectively abutted on the other stepped surface and the other stepped surface.

3. The electromagnetic valve for hydraulic pressure regulation with a front end double spring structure according to claim 1, characterized in that, The main valve sleeve assembly (26) further comprises a piston rod (15), a pilot valve sleeve (16) and a pilot valve core (18), the end surface of the piston sleeve (14) away from the main valve core (11) is provided with the pilot valve sleeve (16), the pilot valve core (18) is slidingly assembled in the main valve sleeve (8), the pilot valve sleeve (16) is located between the pilot valve core (18) and the piston sleeve (14), the pilot spring (17) is assembled between the pilot valve sleeve (16) and the pilot valve core (18), one end of the pilot valve core (18) close to the piston sleeve (14) is fixedly provided with the piston rod (15), and the pilot valve sleeve (16) is provided with a through hole for the piston rod (15) to pass through.

4. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 3, characterized by The end of the piston sleeve (14) close to the pilot valve sleeve (16) is provided with a tapered hole in the axial direction of the piston sleeve (14), the diameter of the tapered hole gradually decreases in the direction away from the pilot valve sleeve (16), and the tapered hole is located on the movement path of the piston rod (15).

5. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 3, characterized by The electromagnet assembly (25) comprises a shell (4), a pole shoe body (7) and a magnetic core shaft (21), the shell (4) is assembled on the coil assembly (1), the pole shoe body (7) is assembled in the shell (4), the main valve sleeve (8) is assembled on the pole shoe body (7), and the magnetic core shaft (21) is slidingly arranged in the pole shoe body (7). The pilot valve core (18) is located on the movement path of the magnetic core shaft (21).

6. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 5, characterized by The pole shoe body (7) is sequentially assembled with a guide bearing seat (23), a magnetic core (22) and a magnetic core seat (19) in the direction close to the main valve sleeve (8), and the magnetic core shaft (21) sequentially passes through the guide bearing seat (23), the magnetic core (22) and the magnetic core seat (19).

7. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 6, characterized by The magnetic core shaft (21) is provided with a guide bearing (24) between the guide bearing seat (23), and the magnetic core shaft (21) is provided with a magnetic core seat guide bearing (20) between the magnetic core seat (19).

8. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 7, characterized by The shell (4) is assembled on the coil assembly (1) through a shell clasp (2), and the shell (4) is sleeved with a coil sealing ring (3) and a shell sealing ring (5).

9. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 5, characterized by The shell (4) is provided with a pole shoe body sealing ring (6) between the pole shoe body (7).

10. The electromagnetic valve for hydraulic pressure regulation of a front end double spring structure according to claim 1, characterized by The main valve sleeve (8) is provided with a gasket (9) between the end cover (10).

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