JPS62216849A - Hydraulic pressure control valve - Google Patents

Abstract

PURPOSE:To improve the production efficiency by always obtaining the desired hydraulic characteristic by setting the length ranging from the contact surfaces between a pair of plungers to the shoulder part of the plunger longer than the length in the direction of axis line of a sleeve. CONSTITUTION:The length L2 between the contact surface 23a of a plunger 23 and a shoulder part 26 which contact each other is set longer than the length L1 in the direction of axis line of a sleeve 21 so that the plunger 23 projects from the sleeve 21. Therefore, the load varies in the variation portion DELTAl between a valve seat 5 and a valve piece 28 in the case when one of two plungers 23 and 23 shifts within the range of the dispersion of the spring 12. With such constitution, the delay of the valve opening time in operation and the rise of the cut point are prevented, and the desired hydraulic characteristic can be always obtained, and the production efficiency can be improved. Further, the hydraulic characteristic test after the completion of assembly can be omitted.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention is a hydraulic brake system for an automatic car. Related: Hydraulic pressure control valve I that makes it possible to secure braking force.

[Prior Art] As shown in FIG. 6, a conventional hydraulic pressure control valve includes a valve body 2 slidably provided within a cylinder body 1; Side ζ: Receiving input hydraulic pressure from the master cylinder, the other side! = A piston 3 that receives output hydraulic pressure, a valve seat 5 provided in the piston 3 passing through the piston 3, a valve seat 5 provided in the liquid, and the valve body 2 provided opposite to the valve seat 5. In a sleeve 6 supported at one end side, a plunger 7 with a reservoir movable is provided, and this plunger 7C is provided so as to be movable forward and backward with respect to the valve seat 5 via a spring 8 and a valve body support member 9. The valve body 10 is interposed between the valve body 10, the spring cover 11 that is in contact with the shoulder of the sleeve 6, and the valve seat 5.
A pair of hydraulic pressure control valve components 13, each consisting of a spring 12 that urges the valve away from the valve seat 5, are arranged symmetrically on the left and right, so that the hydraulic pressure from the master cylinder is applied to the two rear wheel brake cylinders C. There are known devices that control and supply Note that the spring seat 11 is attached to the valve body support member 9 (
Two pieces are fitted.

In such a hydraulic control valve, one of the pair of hydraulic control valve components 13 is placed in the cylinder body 1 (before being assembled) (2. Only the hydraulic control valve structure 13 is fitted, and the closing plate 14 is applied to the abutting surfaces 7a of the plungers 7, the abutting surfaces of the snow pro, and the open end of the test cylinder body 1' in FIG. A static pressure characteristic test was carried out on the pair of hydraulic control valve structures 13 shown in FIG. I'm working hard on this.

[Problems to be Solved by the Invention] However, as described above, in the conventional hydraulic pressure (i1 control valve C: The abutment of the plungers in the axial direction shown in FIG. When the length Lt of the sleeve 6 in the drawing direction is shorter than the length Lt of the sleeve 6, the fourth part 15 of the plunger 7 is sunk into the sleeve 6, so that C during the test.
: Even if the required pressure characteristics are within the allowable range, the pair of hydraulic control valve components 13 in the cylinder body 1
13, if there is variation in the L2 dimension of each of the pair of plungers 7, the pair of plungers 7 will shift from the neutral position to either side, causing the valve seat 5 and the valve body to 10 is too wide, the hydraulic pressure characteristics during operation will not fall within the allowable range of required hydraulic pressure characteristics, the valve opening timing during operation will be delayed, and the brake fluid supplied to the brake cylinder C2 of the front wheels may be delayed. The point at which the increase in hydraulic pressure of brake fluid supplied to the brake cylinder of the rear wheels starts to decrease in response to an increase in hydraulic pressure, that is, the cut point has risen, valve body 2
There were problems such as the need to incorporate a pair of hydraulic pressure control valve components into the system and test the hydraulic characteristics thereof.

The present invention solves these conventional problems and reduces the pressure by $1.
1 The purpose is to provide valve opening.

[Means for solving problems]

In order to achieve the above object, the present invention has the following configuration.

A piston (42) is provided slidably inside the valve body, receives input hydraulic pressure from the master cylinder on the -1 side, and has a piston (42) provided on the other end (= receiving the output hydraulic pressure) passing through this piston. one end side of the hydraulic pressure path 11n;
a valve seat provided therein; and a sleeve formed in a stepped circular shape and having a shoulder portion, provided opposite to the valve seat, and slidably provided within a sleeve supported at one end of the valve body. a plunger connected to the plunger, a valve body connected to the plunger so as to be able to advance and retreat with respect to the valve seat C2, and a valve body that is provided so as to bias the valve body in a direction to separate it from the valve seat, A pair of hydraulic ffTl+ 611 valve structures consisting of a sleeve and a spring that contacts the shoulder of the plunger is prepared, and the plungers of the hydraulic control valve structure are in contact with each other. The pressure control valve components are arranged in series, and the length from the contact surface of the plunger to the shoulder of the plunger is within a range that maintains the required lift profile of the valve body, based on the axial length of the sleeve. [Embodiment] An embodiment of the present invention will be described below with reference to Figs. , the same reference numerals are given, and the explanation thereof is omitted. In this four-fold example, the shapes and dimensions of the sleeve and the plunger, as well as the shape of the valve body, have been changed from the conventional one. ffD Inner circumference C of the pair of sleeves 21:
As shown in FIG. 3, an annular projection (flange) 22 is provided on the contact surfaces of the pair of sleeves 21 that contact each other. As shown, a small diameter portion 24 located on the side l of the valve seat 5 and a medium diameter portion 25 located on the opposite side are formed, whereby the plunger 23
A shoulder portion 26 is formed in the pair of plungers, and L2 is the length in the axial direction of the sleeve 21, which is a distance 9? )L, longer than (set (see Figures 2 to 4)).

Next, the operation of the ±hydraulic pressure i11 control valve configured as described above will be explained.

A pair of hydraulic control valve structures 27 using a mass, a sleeve 21, and a plunger 23 are prepared, and the ? The II pressure suppression control valve body 27 is tested in the same manner as the hydraulic characteristic test shown in FIG. As a result, a pair of hydraulic control valve structures 27° 27 that passed this test were placed inside the cylinder body 1 (with the contact surfaces 23a of the plungers 23 in contact with each other back to back). The cylinder body 1 is arranged symmetrically, and the two opening C plugs 1a of the cylinder body 1 are attached.

Hydraulic pressure control valve configured in this way (in the second case, S IJ
- Since the jib plunger 23 protrudes from the plunger 21, when the two plungers are arranged symmetrically in the cylinder body, the two plungers will move within the range of variation of each spring 12, and the solenoid will move. Valve seat 5 for the amount of movement
Although the distance angle Δt between the valve body 28 and the plunger 23 changes,
The shoulder portion 26 of the valve seat 5 does not fall into the sleeve circle (C), so that the load of the spring 12 changes in accordance with the change of Δt to ensure that the value is 0 or more. The spring back shape when the valve body 28 is seated is
@8 Figure 1 - It will show the same value as the % injection test.

In this way, in this embodiment C2, the 7N portion 26 of the plunger 23 always protrudes from the end surface of the sleeve 21, so even though it passed the hydraulic characteristic test f;
During operation during use, the gap between the valve seat 5 and the valve body 28 becomes too wide, and the required hydraulic pressure characteristics are no longer outside the allowable range, so that the valve opening timing during operation is delayed. The cut point does not go too high, and a good quality hydraulic control valve can be constructed by combining any hydraulic control valve components 27 that have passed the hydraulic characteristic test, improving manufacturing efficiency. Hydraulic pressure characteristics f after installing the pair of hydraulic pressure control valve components in the cylinder body l! Ev:, the experience is deafening, and after draining the fluid from the cylinder body 1, it is possible to incorporate this cylinder body IC1 & pressure control valve structure 27. This has been done, and the fluid optical filling at f: is good when assembled to the vehicle.

There is still a hydraulic fti control valve arrangement 27 in the cylinder body 1.
(Secondly, insert the plunger 2 into the sleeve 21 in advance.)
After enlarging 3 to make a sleeve plunger ■ miniature body, this sleeve plunger 5 pieces, piston 3, valve body 2
8 etc. into the valve body 2 and assemble it to complete the hydraulic control valve ♂ 11 valve ÷ O main body 27. fit into a circle,
This (from the second, g6EV + knee shows the conventional hydraulic control valve (
2, the hydraulic pressure flil1M into the cylinder body 1
Since there are 4 sets of valve components and 4 sets of valve components, and there is no stopper on the inner peripheral surface of the sleeve 6, the plunger 7 is pulled out from the sleeve 6, and the valve body 10 is also removed from the predetermined position, and this valve body 10C. There is a risk of scratches, and there is a risk of foreign objects getting mixed in with the hydraulic control valve, resulting in poor performance of the hydraulic pressure control valve. Since the tαα general periphery of the plunger 23 is caught by the protrusion 22 of the valve body 21, the plunger 23 will not be removed from the sleeve 21 and will not fall off.
It is possible to prevent foreign matter from entering the hydraulic control valve, and furthermore, the outer circumference S of the impact surface 23 of the plunger 23 is reduced in diameter from the maximum outer diameter part of the plunger 23 and is convoluted with the middle diameter part 25. Therefore, the function of the plunger 23 is not hindered at all (and, as a result, the performance of the hydraulic pressure fill M valve can be fully demonstrated).

In addition, in the conventional hydraulic control valve shown in FIG. 6, since the valve body 10 is formed solid by molding means, large rfi sink marks occur when the valve body 10 is molded. Since the surface of the hemispherical head of the valve body 10 does not form a correct spherical surface, the valve seat 5 [2] When the valve body 10 is seated, the valve does not completely close, and the gap between the valve seat 5 and the valve body 10 There was a risk of liquid leakage. In addition, due to the change of the valve body 10, the valve body 10C: 7 lunges 10 shown in FIG. 6 are provided.
The perpendicularity of the valve body 10 to the axis of the valve body 10 may be inaccurate, which may cause liquid leakage between the valve seat 5 and the valve body 10 when the valve is closed.

However, since the valve body 28Fi is formed into a hollow shape by molding means, as shown in FIG. 1 of the valve body 28 of the flange 28eL provided on the valve body 28.
It is possible to accurately ensure the perpendicularity to lfft+M 28 b r2, and in turn, it is possible to prevent liquid leakage between the valve seat 5 and the valve body 28 when the valve is closed.

〔Effect of the invention〕

According to the invention, Ih of the sleeve of the hydraulic control valve arrangement
h rJ From the length in the force direction, a pair of plan-7yas each other C
Since the length from the abutting surface to the shoulder of the plunger has been set thick, the hydraulic characteristics of the pair of hydraulic control valve components were tested individually for each hydraulic pressure control valve component. Even if these approved products are assembled into the cylinder body with optional C:M1, the shoulder of the plunger will always protrude from the end face of the sleeve, the gap between the valve seat and the valve body will not be too wide, and the valve opening timing will be delayed. , can prevent the cut point from rising,
It is possible to obtain the always-required hydraulic pressure customization, improve production efficiency, and eliminate the need to perform hydraulic characteristic tests after completing the second set of hydraulic control valves. , this cylinder body: Since the hydraulic pressure control valve structure can be incorporated, the fluid is completely drained when the hydraulic pressure control valve assembly is completed, and when assembled to the electronic picture. : Improved fluid filling properties.

[Brief explanation of drawings]

Fig. 1 is a longitudinal cross-sectional view showing an embodiment of the present invention, Fig. 2 is a longitudinal cross-sectional view of the plunger, Fig. 3 is a longitudinal cross-sectional view of the sleeve, and Fig. 4 is a longitudinal cross-sectional view of the sleeve. A vertical cross-sectional view showing the state, Figure 5 is a vertical cross-sectional view of the valve body, and Figure 6 is a vertical cross-sectional view of the valve body.
Furthermore, FIG. 7 is a longitudinal cross-sectional view of a conventional hydraulic pressure control valve, and FIG. 7 is a longitudinal 0? FIG. 8 is a longitudinal cross-sectional view showing a state in which a conventional hydraulic pressure side (end) valve structure is tested for hydraulic customization. 1...Cylinder 4' body, 2...Valve body, 3...Piston, 4...Lost pressure point, 5. ... fang sheet, 11 ... spring path, 12 ... spring, 21 ... sleeve, 23 ... plunger, 26 ... claw Part 11, 27... Hydraulic pressure 1++ control valve component, 28...
...Valve body.

Claims (1)

[Claims] A piston that is slidably provided inside the valve body, receives input hydraulic pressure from the master cylinder at one end, and receives output hydraulic pressure at the other end, and a hydraulic piston provided through the piston. a passage, a valve seat provided at one end of the hydraulic passage; a stepped cylindrical shape having a shoulder, provided opposite to the valve seat and supported at one end of the valve body; a plunger slidably disposed in a sleeve circle formed by the valve seat; a valve body connected to the plunger so as to be movable forward and backward relative to the valve seat; A pair of hydraulic control valve structures are provided, each of which includes a spring that abuts the sleeve and the shoulder of the plunger via a spring seat, and the cylinders are arranged such that the plungers of the hydraulic control valve structures abut against each other. The pair of hydraulic control valve components are arranged in series in the body, and the length from the contact surface of the plunger to the shoulder of the plunger is determined by the axial length of the sleeve to determine the required lift of the valve body. A hydraulic control valve characterized in that the amount is set to a large value within a range.