KR102608298B1 - Solenoid valve for brake system - Google Patents

Abstract

A solenoid valve for a brake system is disclosed. The solenoid valve for a brake system according to an embodiment of the present invention includes a magnet core installed in the bore of the modulator block and having a through hole penetrating in the longitudinal direction, an armature installed at one end of the magnet core to enable forward and backward movement, and a magnet core. A valve seat installed at the other end and formed with an orifice, a plunger inserted into the through hole and sliding forward and backward by an armature to open and close the orifice, a filter member accommodated in the bore surrounding the other end of the magnet core and the valve seat, and downstream of the orifice. It includes a flow resistance member provided on the side to change the flow of fluid, a sleeve that accommodates one end of the armature and the magnet core, and a return spring that provides elastic restoring force to the plunger so that the orifice is opened.

Description

Solenoid valve for brake system}

The present invention relates to a solenoid valve for a brake system, and more specifically, to a solenoid valve for a brake system that can reduce noise caused by excessive differential pressure of fluid passing through an orifice during valve operation.

Vehicles are essentially equipped with a hydraulic brake system for braking, and recently, various types of systems have been proposed to obtain stronger and more stable braking force.

Examples of hydraulic brake systems include the Anti-Lock Brake System (ABS), which prevents wheel slippage during braking, and the Brake Traction Control System (BTCS), which prevents slippage of the driving wheels when the vehicle suddenly starts or accelerates. There is a Brake Traction Control System (ESC) and a Stability Control System (ESC: Electronic Stability System) that maintains the vehicle's driving condition stably by controlling brake fluid pressure by combining an anti-lock brake system and traction control.

To implement a brake system, a plurality of electronically controlled solenoid valves are installed in the modulator block, and the flow path (hydraulic circuit) formed within the modulator block is selectively opened and closed by these solenoid valves. Solenoid valves are divided into normally open type solenoid valves, which are normally open, and normally closed solenoid valves, which are normally closed.

A conventional normally open solenoid valve generally includes a magnet core with a longitudinal through hole formed in the center and an entrance and exit formed on the periphery, a dome-shaped sleeve installed on the upper part of the magnet core, an armature installed to be able to advance and retreat inside the sleeve, and an armature that advances and retracts the armature. It includes an excitation coil installed on the outside of the sleeve to do this.

Inside the through hole of the magnet core, there is a plunger that advances and retreats by the action of the armature, a valve seat with an orifice that opens and closes by the plunger, and a return spring that presses the plunger toward the armature to open the orifice when power is not applied to the excitation coil. This is installed.

This solenoid valve is installed in the modulator block and controls the fluid (oil) flow in the channel formed in the modulator block by selectively opening and closing the orifice through the operation of the armature and plunger.

Korean Patent Publication No. 2003-0067843 (2003.08.19.) However, when the conventional solenoid valve is operated, the behavior of the plunger that opens and closes the orifice becomes unstable due to excessive differential pressure between the inlet and outlet of the fluid passing through the orifice, resulting in vibration and noise.

The solenoid valve for a brake system according to an embodiment of the present invention is intended to reduce noise generated during operation.

According to one aspect of the present invention, a magnet core is installed in the bore of the modulator block and has a through hole penetrating in the longitudinal direction, an armature installed at one end of the magnet core to be capable of advancing and retreating, and an orifice installed at the other end of the magnet core. A valve seat is formed, a plunger that is inserted into the through hole and moves forward and backward by an armature to open and close the orifice, a filter member that surrounds the other end of the magnet core and the valve seat and is accommodated in the bore, and is provided on the downstream side of the orifice to filter the fluid. A solenoid valve for a brake system may be provided that includes a flow resistance member that changes the flow, a sleeve that accommodates one end of the armature and the magnet core, and a return spring that provides elastic restoring force to the plunger to open the orifice.

Additionally, the through hole of the magnet core includes a spring support jaw protruding inward to support the return spring, and the flow resistance member may be provided between the spring support jaw and the valve seat.

Additionally, the flow resistance member may be provided in the form of a coil spring.

In addition, the flow resistance member is provided in the form of at least one washer and may include a flat zone along the circumferential direction and a flow zone bent upward and downward from the flat zone in a block or concave direction.

In addition, a plurality of the flow resistance members are formed by stacking, and when stacked, a gap flow path can be formed as a space formed vertically between the flat zone and the euro zone or the euro zone and the euro zone.

The solenoid valve for a brake system according to an embodiment of the present invention provides a flow resistance member between the plunger and the magnet core on the downstream side of the orifice to disperse the flow of fluid exiting the orifice to reduce the flow rate and hydraulic pressure, thereby reducing the unstable behavior of the plunger. Operation noise generated by can be effectively reduced.

1 is a cross-sectional view showing a solenoid valve for a brake system according to an embodiment of the present invention.
Figure 2 is a diagram showing a flow resistance member of a solenoid valve for a brake system according to an embodiment of the present invention.
Figure 3 is an enlarged cross-sectional view showing an open operation state of a solenoid valve for a brake system according to an embodiment of the present invention.
Figure 4 is an enlarged cross-sectional view showing a closed operation state of a solenoid valve for a brake system according to an embodiment of the present invention.
Figure 5 is a cross-sectional view showing a solenoid valve for a brake system including a flow resistance member according to another embodiment of the present invention.
Figure 6 is an enlarged cross-sectional view showing the opening and closing operation state of a solenoid valve for a brake system including a flow resistance member according to another embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. Here, the embodiments introduced below are provided as examples so that the idea of the present invention can be sufficiently conveyed to those skilled in the art. Therefore, the present invention is not limited to the embodiments described below and may be embodied in other forms. Furthermore, in order to clearly explain the present invention, parts not related to the description are omitted from the drawings, and the width of the components is shown in the drawings. , length, thickness, etc. may be exaggerated for convenience. Like reference numerals refer to like elements throughout the specification.

1 is a cross-sectional view showing a solenoid valve for a brake system according to an embodiment of the present invention.

Referring to the drawing, the solenoid valve 100 for a brake system of this embodiment includes a magnet core 110 accommodated in the bore 101a of the modulator block 101, a filter member coupled to the magnet core 110 and the inside of the bore ( 120), the valve seat 140 and plunger 150 installed inside the magnet core 110, the sleeve 160 coupled to the outside of the magnet core 110, the armature 170 provided within the sleeve 160, the above It may include a return spring 180 that provides elastic force to the plunger 150 toward the armature 170, and an excitation coil assembly (not shown) installed on the outside of the sleeve 160.

The magnet core 110 is provided in a cylindrical shape and has a through hole 111 penetrating the center in the longitudinal direction. A spring support jaw 115 protruding inward is provided on the longitudinal center side of the through hole 111 to support the lower end of the return spring 180. A plunger 150 is inserted into the upper part centered on the spring support jaw 115 so as to be able to advance and retreat via a return spring 180, and a valve seat 140 with an orifice 141 is inserted and fixed at the lower part.

The filter member 120 is installed to enter the bore 101a of the modulator block 101 while being coupled to the magnet core 110. The filter member 120 has a peripheral portion 121 surrounding the lower outer surface of the magnet core 110, is located at the lower end of the magnet core 110, and is formed integrally with the peripheral portion 121 to be press-fitted into the through hole 111. Includes an insertion portion 125.

The peripheral portion 121 accommodates the lower portion of the magnet core 110 inside, and its outer surface is supported on the inner surface of the bore 101a of the modulator block 100. The insertion portion 125 is formed with a connection passage 126 in the center that communicates with the through hole 111 of the magnet core 110, and a valve seat press-fitted into the through hole 111 of the magnet core 110 ( 140) It is joined on the inside.

In addition, a separate bypass passage 123 is formed on the peripheral portion 121 of the filter member 120 outside the connection passage 126. This peripheral part 121 includes a first filtering part 121a that filters foreign substances in the oil passing through the first flow path 102 of the modulator block 101, and a first filtering part 121a that filters foreign substances in the oil passing through the second flow passage 103. A second filtration unit 121b is provided. The first and second filtering units 121a and 121b are provided on the peripheral portion 121 at a position opposite to the first flow path 102 and the second flow path 103, respectively. The first passage 102 is provided in the longitudinal direction of the solenoid valve and communicates with the solenoid valve, and the second passage 103 is arranged in the transverse direction of the solenoid valve, that is, at a right angle to the first passage 102 and communicates with the solenoid valve. do.

The bypass passage 123 formed in the filter member 120 is between the first passage 102 and the second passage 103 so that the hydraulic pressure transmitted through the second passage 103 flows into the first passage 102. is formed That is, the bypass flow path 123 is formed to allow oil to flow separately from the flow path that flows through the through hole 111 of the magnet core 110 during a braking operation, and a check valve 130 is installed here. The check valve 130 may include an opening/closing ball 131 installed in the bypass passage 123 to be able to advance and retreat. The opening/closing ball 131 may open the bypass passage 123 during a braking operation and close the bypass passage 123 when braking is terminated.

The plunger 150 is installed to advance up and down in the through hole 111 on the upper side of the spring support jaw 115 of the magnet core 110. The plunger 150 has an opening 151 at the bottom that opens and closes the orifice 141. Additionally, the plunger 150 is pressed toward the armature 170 by the return spring 180 so that the orifice 141 can be kept open when power is not applied to the excitation coil assembly (not shown). In order for the return spring 180 to be stably installed to provide elastic force to the plunger 150, a stepped portion 155 stepped outward to support one end of the return spring 180 may be provided on the upper outer surface of the plunger 150. there is. That is, as described above, a stepped spring support jaw 115 is provided in the through hole 111 of the magnet core 110 to support the other end of the return spring 180, so the lower end of the return spring 180 is It is supported on the spring support jaw 115, and the upper end is supported on the step portion 155 on the outer surface of the plunger 150.

The sleeve 160 is provided as a cup-shaped cylinder and is coupled to the outer surface of the magnet core 110. The sleeve 160 includes a dome-shaped closing portion 161 to close the upper part of the magnet core 110, and the lower part is tightly and tightly coupled to the outer wall of the magnet core 110 through laser or arc welding. In this embodiment, it is illustrated that the magnet core 110 with the sleeve 160 assembled is caulked in the bore 101a of the modulator block 101 to fix the solenoid valve 100. However, the present invention is not limited to this. For example, a flange portion (not shown) may be extended to the sleeve to surround the magnet core 110, and this flange portion may be coupled to the modulator block 101 to secure the solenoid valve.

The armature 170 is located inside the upper interior of the sleeve 160, that is, within the dome-shaped closing portion 161, and is installed to be able to advance and retreat up and down. This armature 170 operates to close the orifice 141 by pressing and moving the plunger 150 when power is applied to the excitation coil assembly (not shown). When the power to the excitation coil assembly is turned off, the armature 170 is moved to release the pressure by the plunger 150 elastically supported by the return spring 180, thereby opening the orifice 141.

The solenoid valve 100 according to this embodiment flows fluid to the downstream side of the orifice 141 in order to stably operate the plunger 150, which behaves unstable due to excessive differential pressure of the fluid passing through the orifice 141 during operation. A flow resistance member 190 that changes can be provided.

More specifically, referring to FIGS. 2 and 3, the flow resistance member 190 is provided in the form of a washer and has a ring hole 191 on the inside to allow the plunger 150 to pass through comfortably, and a magnet core 110 on the outside. It is provided in a circular size that can be inserted into the space between the through hole 111 and the valve seat 140.

In addition, the flow resistance member 190 is alternately provided with flat zones 193 and euro zones 195 at predetermined intervals along the circumferential direction. The flat zone 193 is a portion provided flat, and the euro zone 195 is a portion provided with a bend in a convex or concave round shape between the flat zones 193. When a plurality of flow resistance members 190 are stacked up and down, a space is formed between the flat zone 193 and the euro zone 195 or the euro zone 195 and the euro zone 195, and this space is formed between the flat zone 193 and the euro zone 195. becomes a moving gap channel (197). The euro zone 195 and the flat zone 193 can be manufactured by pressing a metal material prepared in the form of a washer. In this embodiment, a total of four euro zones 195 and flat zones 193 are placed on the same plane at 90-degree intervals, but the present invention is not limited to this and various variations and modifications are possible.

The flow resistance member 190 may be provided inside the lower through hole 111 of the magnet core 110 by stacking at least one flow resistance member 190. The number of stacked flow resistance members 190 is not particularly limited, but it is good that they do not shake according to the flow of fluid when inserted into the space between the through hole 111 of the magnet core 110 and the valve seat 140. . In other words, the larger the round radius of the euro zone 195 compared to the flat zone 193, the fewer the number of flow resistance members 190 installed, and the smaller the round radius, the more the number of flow resistance members 190 installed can be increased.

Additionally, the flow resistance members 190 may be arranged to be staggered at a predetermined angle when stacked. For example, when the euro zone 195 and the flat zone 193 are provided at 90-degree intervals as in this embodiment, the flow resistance members 190 stacked up and down are spaced at 45-degree intervals from each other as shown in FIG. 2. can be placed. When placed at 90-degree intervals, they overlap equally and no flow path is formed up and down.

Typically, the solenoid valve is press-installed with the valve seat 140 on the magnet core 110 and then assembled with the filter member 120 in a post-process, so the flow resistance member 190 is installed on the magnet core 110 with the valve seat 140. ) can be inserted and installed before assembling. In this assembly process, when the flow resistance member 190 is pre-assembled and placed into the magnet core 110 and the valve seat 140 is pressed in, the press-fitting speed of the valve seat 140 is increased by the elastic resistance of the well resistance member 190. And since the pressing force can be kept constant, process efficiency and assembly time can be effectively shortened.

Hereinafter, the opening and closing operation of the solenoid valve for the brake system provided as described above will be described.

In the normally open type (NO type) solenoid valve, when power is not applied to the excitation coil assembly (not shown), the return spring 180 pushes the plunger 150 toward the armature 170, so the plunger 150 Since the end opening 151 is spaced apart from the orifice 141, the internal flow path of the solenoid valve is maintained in an open state.

Therefore, the fluid flowing in through the first flow path 102 sequentially passes through the bore 101a, the connecting flow path 126, the valve seat 140, the orifice 141, and the through hole 111, and flows into the second flow path. It flows to (103).

More specifically, the fluid sequentially passes through the insertion portion 125, the valve seat 140, and the orifice 141 of the filter member 120, as shown by the arrows in FIG. 3, and then passes through the flow resistance member 190. ) The flow is dispersed as it zigzags through the gap channel (197) formed between the flat zone (193) and the euro zone (195). That is, the fluid flows from the downstream side of the orifice 141 to the upstream side of the orifice 141 by the flow resistance member 190 provided in the space formed by the magnet core 110, the valve seat 14, and the plunger 150. The flow rate and hydraulic pressure are further reduced, and as a result, the unstable behavior of the plunger 150 is reduced and the generated vibration and noise are reduced.

Figure 4 shows a state in which the opening/closing port 151 of the plunger 150 closes the orifice 141. In this case, the fluid does not pass through the orifice 141 and stays inside the valve seat 140.

Here, this embodiment illustrates that the fluid moves from the first flow path 102 to the second flow path 103, but the present invention is not limited to this and the fluid can move in the opposite direction, and in this case, the second flow path ( Some of the fluid flowing in through 103 may pass through the bypass passage 123 formed on the peripheral portion 121 of the filter member 120 and flow into the second passage 112.

Meanwhile, Figures 5 and 6 show a flow resistance member 190' of a solenoid valve according to another embodiment of the present invention. This embodiment will be described focusing on differences from the previous embodiment, and since the same reference numerals perform the same function, detailed description will be omitted.

Unlike the flow resistance member 190 according to one embodiment, the flow resistance member 190' according to this embodiment has a coil spring shape rather than a stacked type. The flow resistance member 190' in the form of a coil spring provided in the space formed by the magnet core 110, valve seat 140, and plunger 150 on the downstream side of the orifice 141 is between the spirally wound springs. Since a spiral flow path 198 through which fluid flows is formed, the flow rate and hydraulic pressure of the fluid passing through the orifice 141 are reduced compared to the upstream side of the orifice 141, and as a result, the unstable behavior of the plunger 150 is reduced. Vibration and noise are reduced.

In addition, solenoid valves are usually installed by press-fitting the valve seat 140 into the magnet core 110 and then assembling the filter member 120 in a post-process, so the flow resistance member 190' is attached to the magnet core 110. It can be inserted and installed before assembling the sheet 140. In this assembly process, when the flow resistance member 190' is pre-assembled and placed into the magnet core 110 and the valve seat 140 is pressed in, the valve seat 140 is formed by the elastic resistance of the well resistance member 190'. Since the press-in speed and press-in force can be kept constant, process efficiency and assembly time can be effectively shortened.

100: Solenoid valve 101: Modulator block
110: Magnet core 111: Through hole
120: filter member 121: peripheral portion
125: Insertion part 126: Connection passage
140: valve seat 150: plunger
160: Sleeve 170: Armature
180: Return spring 190,190': Flow resistance member
193: Flat Zone 195: Euro Zone
197: gap flow path 198: spiral flow path

Claims (5)

A magnet core installed in the bore of the modulator block and having a through hole penetrating in the longitudinal direction,
An armature installed at one end of the magnet core capable of advancing and retreating,
A valve seat installed at the other end of the magnet core and having an orifice formed thereon,
A plunger inserted into the through hole and sliding forward and backward by the armature to open and close the orifice;
a filter member that surrounds the other end of the magnet core and the valve seat and is accommodated in the bore;
A flow resistance member in the form of a coil spring provided on the downstream side of the orifice to change the flow of fluid;
a sleeve accommodating one end of the armature and the magnet core;
A solenoid valve for a brake system including a return spring that provides an elastic restoring force to the plunger to open the orifice. A magnet core installed in the bore of the modulator block and having a through hole penetrating in the longitudinal direction,
An armature installed at one end of the magnet core capable of advancing and retreating,
A valve seat installed at the other end of the magnet core and having an orifice formed thereon,
A plunger inserted into the through hole and sliding forward and backward by the armature to open and close the orifice;
a filter member that surrounds the other end of the magnet core and the valve seat and is accommodated in the bore;
A flow resistance member provided on the downstream side of the orifice to change the flow of fluid in the form of at least one washer including a flat zone along the circumferential direction and a flow zone bent upward and downward from the flat zone in a block or concave direction;
a sleeve accommodating one end of the armature and the magnet core;
A solenoid valve for a brake system including a return spring that provides an elastic restoring force to the plunger to open the orifice. According to claim 1 or 2,
The through hole of the magnet core is
It includes a spring support jaw protruding inward to support the return spring,
The flow resistance member is
A solenoid valve for a brake system provided between the spring support jaw and the valve seat. delete According to paragraph 2,
The flow resistance member is
A solenoid valve for a brake system in which a plurality of pieces are stacked, and when stacked, a gap flow path is formed in a space formed vertically by the flat zone and the euro zone or the euro zone and the euro zone.

Images