CN211280979U - Solenoid valve for controlling brake pressure of wheel brake and support ring for the solenoid valve - Google Patents

Abstract

The present application provides a solenoid valve for controlling a brake pressure of a wheel brake and a support ring for the solenoid valve, the support ring of the solenoid valve including a first opening portion, a support portion, and a second opening portion sequentially arranged in a valve closing direction, and an inner sidewall defining an inner diameter of the support ring and an outer sidewall defining an outer diameter thereof; the first opening part is provided with a first inner diameter and a first outer diameter, the second opening part is provided with a second inner diameter and a second outer diameter, the supporting part is provided with a third inner diameter and a third outer diameter, and the third inner diameter is smaller than the first inner diameter and smaller than or equal to the second inner diameter; the support ring is fixedly mounted inside the valve insert through an outer side wall at least partially matched with an inner wall of the valve insert of the solenoid valve, and at least one through flow hole is formed between the outer side wall of the support ring and the inner wall of the valve insert so that cavities of the valve insert respectively arranged on two sides of the support ring in the valve closing direction are communicated. The present application may reduce friction occurring between the tappet end and the valve seat due to tappet wobble in the valve closed state.

Description

Solenoid valve for controlling brake pressure of wheel brake and support ring for the solenoid valve

Technical Field

The present invention relates to a solenoid valve for controlling a brake pressure of a wheel brake and a support ring for the solenoid valve.

Background

In an anti-lock system, a drive slip system or an electronic stability system of a vehicle, the brake pressure of at least one wheel brake can be controlled or regulated, for example, by means of a solenoid valve as a function of the slip present at the respective wheel.

A common solenoid valve used in these systems comprises a valve insert with a tappet, a housing fixed to the valve insert and defining an armature chamber, an armature actuating the tappet and movably accommodated in the armature chamber, an energizable solenoid coil for actuating the armature, a valve body controllable to open or close by the tappet, and a spring and a support ring. The tappet penetrates through the spring and the support ring in sequence along the valve closing direction, and grooves for connecting two ends of the support ring in the valve closing direction are formed in the outer side wall of the support ring, so that electromagnetic valve cavities on two sides of the support ring in the valve closing direction are communicated. By applying a magnetic force acting in the valve closing direction to the armature by energizing the electromagnetic coil, the armature movement is transmitted to the tappet to move the tappet in the valve closing direction and thereby close the valve seat of the valve body by the end of the tappet close to the valve body.

In the prior art, the outer diameter of the tappet is reduced in the valve closing direction, the support ring is designed to be a straight cylinder and fixed on the inner wall of the valve insert, the tappet is arranged to penetrate through the hollow cavity of the support ring in the open state of the electromagnetic valve when the electromagnetic coil is not energized and the tappet does not close the valve body, and the outer diameter of the part penetrating through the tappet of the support ring is smaller than the inner diameter of the support ring in the open state of the electromagnetic valve, so that the tappet can move in the valve closing direction in the support ring when the electromagnetic coil is energized; since the outer diameter of the tappet decreases in the valve closing direction, the distance between the outer surface of the tappet and the inner side wall of the backup ring gradually increases in the hollow cavity of the backup ring from the open end of the backup ring on the side away from the valve body to the other opposite open end of the backup ring in the valve closing direction, and when the electromagnetic valve is closed, the distance between the outer surface of the tappet and the inner side wall at the open end of the backup ring on the side away from the valve body is the closest, and hereinafter, the outer surface at which the distance of the tappet from the inner side wall of the backup ring is the smallest is simply referred to as "distance. The numerical relationship between the outer diameter of the tappet at the end closest to the opening of the support ring, the inner diameter of the support ring, and the running travel of the tappet in the valve closing direction during the passage from the valve-open state to the valve-closed state is known in the art.

When the valve is closed, the tappet can shake under the impact of fluid in the electromagnetic valve cavity, in the shaking process, the minimum distance position of the tappet closest to the inner side wall of the opening end of the supporting ring is firstly contacted and abutted with the inner side wall of the opening end of the supporting ring, and the force generated by the contact and abutment can relatively prevent the tappet from continuously shaking or offset a certain shaking amplitude. Due to the shaking of the tappet, friction is generated between the end part of the tappet and the valve seat of the valve body, so that the end part of the tappet is damaged, the closing between the end part of the tappet and the valve seat is influenced, and the effect of closing the valve body is further influenced. Therefore, there is a need to provide an improved technical solution to overcome the technical problems in the prior art.

SUMMERY OF THE UTILITY MODEL

The purpose of the present application is to minimize friction occurring between the end of the tappet and the valve seat due to the wobble of the tappet in the valve closed state.

In order to achieve the object defined above, the present application provides a solenoid valve for controlling a brake pressure of a wheel brake, comprising a valve insert having a movably guided tappet, a housing which is fixed to the valve insert and defines an armature chamber, an armature which actuates the tappet and is accommodated movably in the armature chamber, an energizable electromagnetic coil for actuating the armature, and a valve body which can be controlled by the tappet, the armature, the tappet and the valve body are sequentially arranged in the valve closing direction, the tappet comprises a guide section and a support section which are sequentially arranged along the valve closing direction, the outer diameter of the guide section matches the inner diameter of the valve insert, the outer diameter of the support section decreases in the valve closing direction, the maximum outer diameter of the supporting section is smaller than the outer diameter of the guiding section, and a step part is formed between the guiding section and the supporting section; the electromagnetic valve further comprises an elastic return element and a support ring fixed inside the valve insert, one end of the elastic return element is arranged on the step part, the other end opposite to the step part abuts against the support ring, the support ring is provided with a hollow part, and the tappet penetrates through the support ring through the elastic return element in the valve closing direction; the support ring comprises a first opening part, a support part and a second opening part which are sequentially arranged along the valve closing direction, an inner side wall for limiting the inner diameter of the support ring and an outer side wall for limiting the outer diameter of the support ring; the first opening portion has a first inner diameter D1 and a first outer diameter D1, the second opening portion has a second inner diameter D2 and a second outer diameter D2, the support portion has a third inner diameter D3 and a third outer diameter D3, wherein D3 is smaller than D1 and D3 is smaller than or equal to D2, and in a valve closed state, a distance between an outer surface of the tappet and an inner sidewall at the support portion of the support ring is minimized; the inner side wall of the support ring comprises a first inner side transition part formed between the first opening part and the support part and a second inner side transition part formed between the support part and the second opening part; the support ring is fixedly installed inside the valve insert through at least a part of the outer side wall matched with the inner wall of the valve insert, and at least one through flow hole is formed between the outer side wall of the support ring and the inner wall of the valve insert so that cavities of the valve insert respectively arranged on two sides of the support ring in the closing direction of the valve are communicated.

According to the present invention, in the valve closing direction, compared with the first opening of the support ring, the distance between the support part of the support ring and the tappet end is smaller, when the valve is closed, the tappet end settles into the valve seat along the valve closing direction, because the inner diameter of the support ring support part is smaller than the inner diameter of the first opening, the distance between the outer surface of the tappet and the inner wall of the support ring support part is the smallest, correspondingly, the distance between the "distance smallest" of the tappet and the tappet end is shorter than the distance of the prior art structure, under the impact of the fluid in the same electromagnetic valve cavity in the valve closing state, the tappet is shaken by a smaller amplitude, which is in contact with the inner wall of the support ring support part, thereby preventing the tappet from continuously shaking to a larger amplitude under a smaller shaking amplitude, by reducing the shaking amplitude of the tappet, thereby reducing friction between the tappet end and the valve seat.

For a better understanding of the nature and technical content of the present application, reference should be made to the following detailed description and accompanying drawings, which are provided for purposes of illustration and description and are not intended to limit the present application.

Drawings

The present application will be more fully understood from the detailed description given below in conjunction with the accompanying drawings, in which like reference numerals refer to like elements. Wherein:

fig. 1 shows a schematic longitudinal sectional view of a solenoid valve for controlling the brake pressure of a wheel brake according to an embodiment of the present application in a valve closing direction X and through the solenoid valve axis, wherein the valve body is in a closed state;

FIG. 2 shows an enlarged schematic view of a portion of the solenoid valve of FIG. 1 in the valve closed condition;

fig. 3(a) shows a schematic top view of the support ring of fig. 1 in the valve closing direction X;

FIG. 3(b) shows a schematic cross-sectional view of the support ring of FIG. 3(a) along line A-A;

FIG. 4(a) shows a schematic cross-sectional view of a support ring according to another embodiment of the present application in a valve closing direction X and through the support ring axis;

FIG. 4(b) shows a schematic cross-sectional view of a support ring according to yet another embodiment of the present application in the valve closing direction X and through the support ring axis;

fig. 5 shows a schematic cross-sectional view of a support ring according to a further embodiment of the present application in the valve closing direction X and through the support ring axis.

Detailed Description

The following describes in detail embodiments of the present invention with reference to the drawings. In the drawings, the same reference numerals indicate the same or corresponding features.

Referring to fig. 1, a schematic longitudinal sectional view along a valve closing direction X of a solenoid valve for controlling brake pressure of a wheel brake according to an embodiment of the present application is shown, in which a valve body is in a closed state. The solenoid valve comprises a valve insert 5 with a movably guided tappet 4, a housing 1 which is fixed to the valve insert 5 and defines an armature chamber 3, an armature 2 which actuates the tappet 4 and is accommodated movably in the armature chamber 3, an energizable electromagnetic coil (not shown) for actuating the armature 2, and a valve body 8 which can be controlled by the tappet 4, the armature 2, the tappet 4 and the valve body 8 being arranged in succession in a valve closing direction X.

The tappet 4 includes a guide section 41 and a support section 42 sequentially arranged along the valve closing direction X, an outer diameter of the guide section 41 matches with an inner diameter of the valve insert 5, an outer diameter of the support section 42 is reduced in the valve closing direction X, a maximum outer diameter of the support section 42 is smaller than an outer diameter of the guide section 41, and a stepped portion 43 is formed between the guide section 41 and the support section 42. The solenoid valve further comprises an elastic return element 6 and a support ring 7 fixed in the valve insert 5, wherein one end of the elastic return element 6 (for example, a spring) is disposed on the step 43, and the other end abuts against and is fixed on the support ring 7, the support ring 7 has a hollow portion, and the tappet 4 penetrates through the support ring 7 via the elastic return element 6 in the valve closing direction X.

With continued reference to fig. 1 to 3, the support ring 7 includes a first opening portion 71, a support portion 73, and a second opening portion 72, which are sequentially arranged along the valve closing direction X, as well as an inner side wall defining an inner diameter of the support ring 7 and an outer side wall defining an outer diameter of the support ring 7. The first opening portion 71 has a first inner diameter D1 and a first outer diameter D1, the second opening portion 72 has a second inner diameter D2 and a second outer diameter D2, and the support portion 73 has a third inner diameter D3 and a third outer diameter D3, wherein D3 is smaller than D1 and D1 is equal to D2, D3 is smaller than D1 and D1 is equal to D2.

The outer side wall of the support ring 7 comprises a first fixed outer side wall 710 at the first opening 71 and a second fixed outer side wall 720 at the second opening 72, which abut against the inner wall of the valve insert 5, the support ring 7 being fixed to the inside of the valve insert 5 by the first fixed outer side wall 710 and the second fixed outer side wall 720 (e.g. by interference fit); the first fixed outer side wall 710 is formed with at least one first groove 711 extending substantially along the valve closing direction X, the first groove 711 and the inner wall of the valve insert 5 opposite thereto are defined to form a first through-flow hole 91, the second fixed outer side wall 720 is formed with at least one second groove (not shown) extending substantially along the valve closing direction X, the second groove and the inner wall of the valve insert 5 opposite thereto are defined to form a second through-flow hole 92, and the first through-flow hole 91 and the second through-flow hole 92 are communicated with each other, so that the valve insert 5 has a through-flow passage in the valve closing direction X.

Referring to fig. 1 to 3, when the valve is closed, the tappet end is sunk into the valve body 8 in the valve closing direction X. In the prior art, the distance of the inner side wall at the first opening portion 71 of the backup ring from the outer surface of the tappet is the smallest, i.e., the position a of the tappet illustrated in fig. 2 is where the distance of the outer surface of the tappet from the inner side wall of the backup ring in the prior art is the smallest; in the embodiment of the present application shown in fig. 1 and 2, the distance between the inner sidewall of the support ring 7 at the support portion 73 and the outer surface of the tappet is the smallest compared to the first opening portion 71 of the support ring 7 in the valve closing direction X, i.e., the distance between the outer surface of the tappet and the inner sidewall of the support ring in the present application is the smallest at the position B of the tappet shown in fig. 2. In valve closing direction X, the distance from the B position of the tappet to the end of the tappet is smaller than the distance from the a position of the tappet to the end of the tappet, according to the lever principle, under the impact of fluid in the same electromagnetic valve cavity, the tappet 4 of the electromagnetic valve of the embodiment of the present application is shaken by a smaller amplitude, i.e., can be quickly contacted and abutted against the inner side wall at the supporting part 73 of the supporting ring 7, so that the tappet 4 can be prevented from continuously shaking under the smaller shaking amplitude, and by reducing the shaking amplitude of the tappet 4, the friction between the end of the tappet 4 and the valve seat 81 is reduced.

Those skilled in the art will appreciate that the "distance minimum" refers to the amount of time that the valve is closed, the end of the tappet settles into the valve seat, the tappet has not been swept by the fluid in the valve cavity, and the distance between the outer surface of the tappet and the inner sidewall of the backup ring, at which time the tappet is generally considered to be out of contact with the inner sidewall of the backup ring; under the condition that the valve is continuously closed, the tappet is impacted by fluid in the valve cavity to shake, the tappet is contacted and supported to the inner side wall of the supporting part of the supporting ring in the shaking process, and under the supported state, the tappet is partially contacted with the inner side wall of the supporting ring, so that the tappet can be totally and completely not contacted or partially contacted with the inner side wall of the supporting ring when the valve is closed and under the condition that the valve is continuously closed. It will also be understood by those skilled in the art that the minimum distance between the tappet and the inner side wall of the support ring support when the valve is closed defines the amplitude of the tappet wobble, and in practical design and production, the minimum distance may be set according to the amplitude of the wobble allowed by the tappet of the solenoid valve, and will not be described herein.

It will also be understood by those skilled in the art that the situation in which there is no gap between the minimum distance B of the support section 42 of the tappet 4 from the inner side wall of the support portion 73 of the support ring 7 and the inner side wall of the support portion 73 of the support ring 7, but it is directly held at the support portion 73, is not excluded when the valve is closed, in which case the amplitude of the rocking of the tappet 4 is smaller. Other than this "distance minimum B", the other parts of the tappet 4 do not contact the inner side wall of the support ring 7.

As shown in fig. 3(a), the support portion 73 of the backup ring 7 is disposed relatively far from the first opening portion 71 and relatively close to the second opening portion 72, and the position where the support section 42 of the tappet 4 contacts and abuts against the support portion 73 of the backup ring 7 during rocking is further reduced in the valve closing direction X, and the distance from the B where the distance from the inner side wall of the support section 42 to the support portion 73 of the backup ring 7 is the smallest to the tappet end portion 44 is shortened, so that the rocking amplitude of the tappet 4 before contacting and abutting against the inner side wall of the support portion 73 is further reduced.

As shown in fig. 3(a) and 3(b), the number of the first flow-through holes 91 is equal to the number of the second flow-through holes 92, and the position of the first flow-through hole 91 corresponds to the position of the second flow-through hole 92 in the valve closing direction X, that is, the connecting line between the corresponding first flow-through hole 91 and the corresponding second flow-through hole 92 is approximately parallel to the straight line of the valve closing direction X in the valve closing direction X, and this arrangement makes the fluid in the solenoid valve chamber have the shortest path in the valve closing direction X and the opposite direction, thereby improving the passing efficiency of the fluid in the solenoid valve chamber; further, the first flow holes 91 have a plurality of (e.g., 3 or more) flow holes and are uniformly distributed along the circumferential direction of the inner wall of the valve insert 5, and correspondingly, the second flow holes 92 corresponding to the positions of the first flow holes 91 in the valve closing direction X also have the same number as the first flow holes 91 and are uniformly distributed along the circumferential direction of the inner wall of the valve insert 5, and since the flow holes are uniformly distributed in the circumferential direction of the valve insert 5, the fluid in the solenoid valve chamber is uniformly distributed and balanced on the basis of having the shortest passage in the valve closing direction X, so that the force applied to the tappet 4 is uniform, and the impact of the fluid in the chamber on the tappet 4 is objectively reduced to reduce the shaking of the tappet 4.

With reference to fig. 2 and fig. 3, the inner sidewall of the support ring 7 includes a first inner transition portion formed between the first opening portion 71 and the support portion 73, and a second inner transition portion formed between the support portion 73 and the second opening portion 72. The outer side wall of the support ring 7 further comprises a first outer transition portion formed between the first opening portion 71 and the support portion 73 and a second outer transition portion formed between the support portion 73 and the second opening portion 72. The first inner transition portion and the second inner transition portion are integrally formed as a smooth inner side wall of the support ring from the first opening portion through the support portion to the second opening portion, the first fixed outer side wall 710, the first outer transition portion, the second outer transition portion and the second fixed outer side wall 720 are integrally formed as a smooth outer side wall of the support ring 7 from the first opening portion 71 through the support portion 73 to the second opening portion 72, and the inner side wall and the outer side wall together form a side wall of the support ring 7. The thickness of the sidewall of the support ring 7 gradually increases from the support portion 73 to the two openings, and since the support ring 7 is fixedly mounted on the inner wall of the valve insert 5 via the first fixed outer sidewall 710 and the second fixed outer sidewall 720 at the two openings, the sidewall of the support ring 7 at the two openings is relatively thick, which is beneficial to increasing the strength of the support ring 7 itself and enabling the support ring 7 to be more firmly and stably fixed on the inner wall of the valve insert 5.

Referring to fig. 3 again, at least one first through hole 712 is formed through the sidewall of the support ring 7 between the first opening portion 71 and the support portion 73, and during the process that the fluid in the solenoid valve chamber flows from the second through hole 92 to the first through hole 91, a part of the fluid can also flow through the support ring 7 through the first through hole 712, so as to improve the circulation efficiency of the fluid through the support ring 7; furthermore, at least one second through hole 722 is also formed in the side wall of the support ring 7, which is located between the second opening portion 72 and the support portion 73, of the support ring 7 in a penetrating manner, so that the fluid in the electromagnetic valve cavity can flow through the support ring 7 in a more channel manner, and the flow efficiency of the fluid is further improved; the position of the first through going hole 712 may correspond to the position of said second through going hole 722, such that a shorter passage of fluid through the support ring 7 via the through going hole is obtained; still further, the first through holes 712 are multiple and uniformly distributed along the circumferential direction of the side wall of the support ring 7, and the second through holes 722 are multiple and uniformly distributed along the circumferential direction of the side wall of the support ring 7, so that while a short fluid channel is formed between the first through holes 712 and the second through holes 722 corresponding to each other in the valve closing direction X, the distribution of the fluid is more uniform, and the force applied to the tappet 4 penetrating through the support ring 7 is more uniform while the flow efficiency is further improved.

Please refer to fig. 4 and 5 for other embodiments of the support ring 7 of the present application. In fig. 4(a) and 4(b), the outer side wall of the support ring 7 is a straight cylinder as a whole (the outer diameters of the support ring 7 at the first opening portion 71, the second opening portion 72 and the support portion 73 are also made to be the same) and the outer diameter of the support ring 7 is matched with the inner diameter of the valve insert 5 to fixedly mount the support ring 7 inside the valve insert 5 through the outer side wall of the support ring 7.

In fig. 4(a), the first inner diameter D1 at the first opening portion 71 of the support ring 7 is larger than the third inner diameter D3 at the support portion 73, D3 is equal to the inner diameter D2 at the second opening portion 72, a smooth inner transition portion is formed between the first opening portion 71 and the support portion 73, and a substantially straight cylindrical inner portion is formed between the support portion 73 and the second opening portion 72, so that the inner side wall of the support ring 7 is substantially funnel-shaped as a whole. As will be understood by those skilled in the art, as one case of the embodiment shown in fig. 4(a), the support portion 73 may coincide with the second opening portion 72 in the valve closing direction X. Fig. 4(b) is a support ring structure of yet another embodiment of the present application. The first inner diameter D1 at the first opening portion 71 of the support ring 7 is equal to the second inner diameter D2 at the second opening portion 72, the first inner diameter D1 is larger than the third inner diameter D3 at the support portion 73, and the first opening portion 71, the support portion 73 and the second opening portion 72 are smoothly transited to form the inner side wall of the support ring 7 with a substantially hourglass shape through the connection of the first inner transition portion and the second inner transition portion.

Since the outer diameter of the support section 42 of the tappet 4 is reduced in the valve closing direction X, in both embodiments of fig. 4(a) and 4(B), the portion from the "distance minimum point" B of the tappet support section 42 to the tappet end 44 is not in contact with the inner side wall between the support portion 73 and the second opening portion 72, and the valve closing function can be realized. Due to the large contact area between the outer side wall of the support ring 7 and the inner wall of the valve insert 5 in fig. 4(a) and 4(b), the support ring 7 can be more firmly mounted inside the valve insert 5; meanwhile, the straight cylindrical outer side wall also enables the structure of the support ring 7 to be relatively simple, and the design and manufacture and the dimensional accuracy control are easier.

It will be appreciated by those skilled in the art that the through-flow apertures are formed between the outer side wall of the support ring and the inner side wall of the valve insert in fig. 4(a) and 4(b) to meet the basic requirements of fluid passage.

Referring to fig. 5, a schematic cross-sectional view of a support ring 7 along a valve closing direction X according to another embodiment of the present application, a first inner diameter D1 at a first opening portion 71 of the support ring 7 is larger than third inner diameters D3 and D3 at a support portion 73 and equal to a second inner diameter D2 at a second opening portion 72, and a smooth inner sidewall of the support ring 7 in a substantially funnel shape is formed from the first opening portion 71 to the second opening portion 72 through the support portion 73; the first outer diameter d1 at the first opening portion 71 of the support ring 7 is larger than the third outer diameter d3 at the support portion 73, d3 is equal to the second outer diameter d2 at the second opening portion 72, a first fixed outer side wall matched with the inner wall of the valve insert 5 is formed at the first opening portion 71 and used for fixing the support ring 7 on the inner wall of the valve insert 5, a smooth and approximately funnel-shaped outer transition portion is formed from the edge of the first fixed outer side wall close to the valve body side to the second opening portion 72 through the support portion 73, and the first fixed outer side wall and the outer transition portion jointly form the outer side wall of the support ring 7. The support ring 7 structure of this embodiment can realize the purpose of this application equally, and its structural feature can practice thrift material, reduce cost simultaneously, also provides more circulation spaces for the fluid in the solenoid valve cavity.

Likewise, it will be understood by those skilled in the art that the through-flow holes are formed between the first outer fixed side wall of the support ring in fig. 5 and the inner side wall of the valve insert 5 to meet the basic requirements of fluid passage.

In other possible embodiments of the present application, it can be understood by those skilled in the art that the outer diameter of the tappet becomes smaller in the valve closing direction X, the inner diameter D3 of the supporting portion 73 of the supporting ring 7 is larger than the inner diameter D2 of the second opening portion 72, and the dimensions of D3 and D2 are determined to satisfy the requirement that the tappet 4 can pass through the supporting ring 7 when the valve is closed and the requirement that the tappet 4 can shake under the impact of fluid in the valve cavity is met, which will not be described herein.

The above detailed description is merely illustrative of the present application and is not intended to be limiting. Various changes and modifications may be effected therein by one of ordinary skill in the pertinent art without departing from the scope of the present application, and it is intended that all equivalents thereof fall within the scope of the present application, which is defined by the claims.

Claims (18)

1. A solenoid valve for controlling the brake pressure of a wheel brake, comprising a valve insert (5) with a movably guided tappet (4), a housing (1) which is fixed to the valve insert (5) and defines an armature chamber (3), an armature (2) which actuates the tappet (4) and is accommodated movably in the armature chamber (3), an energizable magnet coil for actuating the armature (2), and a valve body (8) which can be controlled by the tappet (4), the armature (2), the tappet (4) and the valve body (8) being arranged in succession in a valve closing direction (X),

the tappet (4) comprises a guide section (41) and a support section (42) which are sequentially arranged along the valve closing direction (X), the outer diameter of the guide section (41) is matched with the inner diameter of the valve insert (5), the outer diameter of the support section (42) is reduced in the valve closing direction (X), the maximum outer diameter of the support section (42) is smaller than the outer diameter of the guide section (41), and a step part (43) is formed between the guide section (41) and the support section (42);

the electromagnetic valve further comprises an elastic return element (6) and a support ring (7) fixed inside the valve insert (5), one end of the elastic return element (6) is arranged on the step part (43), the other end opposite to the step part (43) abuts against the support ring (7), the support ring (7) is provided with a hollow part, and the tappet (4) penetrates through the support ring (7) through the elastic return element (6);

the support ring (7) comprises a first opening portion (71), a support portion (73) and a second opening portion (72) which are arranged in sequence in the valve closing (X) direction, and an inner side wall which defines an inner diameter of the support ring (7) and an outer side wall which defines an outer diameter of the support ring (7);

the first opening (71) has a first inner diameter (D1) and a first outer diameter (D1), the second opening (72) has a second inner diameter (D2) and a second outer diameter (D2), and the support (73) has a third inner diameter (D3) and a third outer diameter (D3), wherein the third inner diameter (D3) is smaller than the first inner diameter (D1) and the third inner diameter (D3) is smaller than or equal to the second inner diameter (D2), or the third inner diameter (D3) is smaller than the first inner diameter (D1) and the third inner diameter (D3) is larger than the second inner diameter (D2);

the support ring (7) is fixedly mounted inside the valve insert (5) through at least a part of an outer side wall matched with an inner wall of the valve insert (5), and at least one through hole is formed between the outer side wall of the support ring (7) and the inner wall of the valve insert (5) so that cavities of the valve inserts (5) respectively arranged on two sides of the support ring (7) in the valve closing direction (X) are communicated.

2. Solenoid valve for controlling the brake pressure of a wheel brake according to claim 1, characterized in that the first inner diameter (D1) is equal to the second inner diameter (D2) and the first inner diameter (D1) is larger than the third inner diameter (D3).

3. A solenoid valve for controlling the braking pressure of a wheel brake according to claim 1, characterised in that the first outer diameter (d1) is equal to the second outer diameter (d2) and equal to the third outer diameter (d3), the outer side wall of the support ring (7) where the largest outer diameter is located is interference-matched with the inner wall of the valve insert (5) so that the support ring (7) is fixed inside the valve insert (5), a groove extending substantially in the valve closing direction (X) is formed on the outer side wall of the support ring (7), and the groove and the inner wall of the valve insert (5) opposite the groove enclose the throughflow orifice.

4. Solenoid valve for controlling the brake pressure of a wheel brake according to claim 1,

the first outer diameter (d1) is equal to the second outer diameter (d2) and the first outer diameter (d1) is greater than the third outer diameter (d 3);

the outer side wall of the support ring (7) comprises a first fixed outer side wall (710) at the first opening (71) and a second fixed outer side wall (720) at the second opening (72) matching with the inner wall of the valve insert (5), the support ring (7) is fixed inside the valve insert (5) by the first fixed outer side wall (710) and the second fixed outer side wall (720);

the first fixed outer side wall (710) is provided with at least one first groove body (711) extending along the valve closing direction (X), the first groove body (711) and the inner wall of the valve insert (5) opposite to the first groove body (711) are formed in a surrounding mode to form a first through flow hole (91), the second fixed outer side wall (720) is provided with at least one second groove body extending along the valve closing direction (X), the inner wall of the valve insert (5) opposite to the second groove body is formed in a surrounding mode to form a second through flow hole (92), and the first through flow hole (91) and the second through flow hole (92) are communicated so that the valve insert (5) is provided with a through fluid channel in the valve closing direction (X).

5. Solenoid valve for controlling the brake pressure of a wheel brake according to claim 4, characterized in that the first inner diameter (D1) is equal to the second inner diameter (D2) and the first inner diameter (D1) is larger than the third inner diameter (D3).

6. The solenoid valve for controlling brake pressure of a wheel brake as claimed in claim 5, characterized in that the number of the first through-flow holes (91) is equal to the number of the second through-flow holes (92), and the position of the first through-flow holes (91) corresponds to the position of the second through-flow holes (92) in the valve closing direction (X).

7. The solenoid valve for controlling the brake pressure of a wheel brake as claimed in claim 6, characterized in that the first throughflow hole (91) is plural and evenly distributed along the circumference of the inner wall of the valve insert (5), and the second throughflow hole (92) is plural and evenly distributed along the circumference of the inner wall of the valve insert (5).

8. The solenoid valve for controlling braking pressure of a wheel brake as claimed in claim 4, characterized in that the support portion (73) is relatively distant from the first opening portion (71) and relatively close to the second opening portion (72).

9. A solenoid valve for controlling the braking pressure of a wheel brake according to claim 4, characterized in that the thickness of the sidewall of the support ring (7) is gradually increased from the support portion (73) to both opening portions.

10. The solenoid valve for controlling the braking pressure of a wheel brake according to claim 4, characterized in that at least one first through hole (712) is perforated in the sidewall of the support ring (7) located between the first opening portion (71) and the support portion (73).

11. The electromagnetic valve for controlling the brake pressure of a wheel brake according to claim 10, characterized in that at least one second through hole (722) is bored through a side wall of the backup ring (7) located between the second opening portion (72) and the support portion (73), and the position of the first through hole (712) corresponds to the position of the second through hole (722) in the valve closing direction (X).

12. The solenoid valve for controlling the brake pressure of a wheel brake according to claim 11, characterized in that the first through holes (712) are plural and evenly distributed along the circumferential direction of the side wall of the support ring (7), and the second through holes (722) are plural and evenly distributed along the circumferential direction of the side wall of the support ring (7).

13. A support ring (7) for a solenoid valve for controlling a wheel brake pressure, characterized in that the support ring (7) comprises a first opening portion (71), a support portion (73), and a second opening portion (72) which are arranged in this order in a valve closing direction (X), and an inner side wall defining an inner diameter of the support ring (7) and an outer side wall defining an outer diameter of the support ring (7);

the first opening portion (71) having a first inner diameter (D1) and a first outer diameter (D1), the second opening portion (72) having a second inner diameter (D2) and a second outer diameter (D2), the support portion (73) having a third inner diameter (D3) and a third outer diameter (D3), wherein,

the first outer diameter (d1), the second outer diameter (d2) and the third outer diameter (d3) are equal, the outer side wall is approximately in a straight cylinder shape on the whole, at least one groove which approximately extends along the valve closing direction (X) is formed on the outer side wall, and the groove is connected with two ends of the outer side wall;

the third inner diameter (D3) is smaller than the first inner diameter (D1) and the third inner diameter (D3) is smaller than or equal to the second inner diameter (D2), or the third inner diameter (D3) is smaller than the first inner diameter (D1) and the third inner diameter (D3) is larger than the second inner diameter (D2).

14. A support ring (7) for a solenoid valve for controlling a wheel brake pressure, characterized in that the support ring (7) comprises a first opening portion (71), a support portion (73), and a second opening portion (72) which are arranged in this order in a valve closing direction (X), and an inner side wall defining an inner diameter of the support ring (7) and an outer side wall defining an outer diameter of the support ring (7);

the first opening portion (71) having a first inner diameter (D1) and a first outer diameter (D1), the second opening portion (72) having a second inner diameter (D2) and a second outer diameter (D2), the support portion (73) having a third inner diameter (D3) and a third outer diameter (D3), wherein,

the first outer diameter (D1) is equal to the second outer diameter (D2) and the first outer diameter (D1) is greater than the third outer diameter (D3), the third inner diameter (D3) is less than the first inner diameter (D1) and the third inner diameter (D3) is less than or equal to the second inner diameter (D2), or the third inner diameter (D3) is less than the first inner diameter (D1) and the third inner diameter (D3) is greater than the second inner diameter (D2);

the outer side wall of the support ring (7) comprises a first fixed outer side wall (710) at the first opening (71) and a second fixed outer side wall (720) at the second opening (72) matching the inner wall of the valve insert (5), the outer diameters of the first fixed outer side wall (710) and the second fixed outer side wall (720) being equal and equal to the first outer diameter (d 1);

the first fixed outer side wall (710) is formed with at least one first groove (711) extending substantially along the valve closing direction (X) and connecting both ends of the first fixed outer side wall (710), and the second fixed outer side wall (720) is formed with at least one second groove extending substantially along the valve closing direction (X) and connecting both ends of the second fixed outer side wall (720).

15. The support ring (7) of a solenoid valve for controlling a wheel brake pressure according to claim 14, characterized in that the first inner diameter (D1) is equal to the second inner diameter (D2) and the first inner diameter (D1) is greater than the third inner diameter (D3).

16. The support ring (7) of a solenoid valve for controlling a brake pressure of a wheel brake as claimed in claim 15, characterized in that the number of the first grooves (711) is equal to the number of the second grooves, the position of the first grooves (711) corresponds to the position of the second grooves in the valve closing direction (X), the first grooves (711) are plural and uniformly distributed along the circumference of the first fixed outer sidewall (710), and the second grooves are plural and uniformly distributed along the circumference of the second fixed outer sidewall.

17. The support ring (7) of a solenoid valve for controlling a brake pressure of a wheel brake according to claim 14, wherein at least one first through hole (712) is perforated in a sidewall of the support ring (7) between the first opening portion (71) and the support portion (73), and the first through holes (712) are plural and uniformly distributed along a circumferential direction of the sidewall of the support ring (7).

18. The support ring (7) of a solenoid valve for controlling a wheel brake pressure according to claim 17, characterized in that at least one second through hole (722) is bored through a side wall of the support ring (7) located between the second opening portion (72) and the support portion (73), and the position of the first through hole (712) corresponds to the position of the second through hole (722) in the valve closing direction (X).

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