FR2858372A1 - Hydraulic valve for anti-rolling control system of motor vehicle, has control rod and armature that, along with valve chamber and seat, form sub-assembly that is contained in casing arranged in hydraulic block - Google Patents

Abstract

The valve has a control rod (30) whose one end is connected to a conductor armature (32) surrounded by a solenoid (33) and another end has a throttling unit. The rod and armature along with a valve chamber (23) and a valve seat form a separated sub-assembly. The assembly is contained in a casing (21) arranged in a hydraulic block, either aligned with a longitudinal axis of a main casing or perpendicular to the axis. An independent claim is also included for an anti-rolling system for motor vehicle.

Description

The present invention relates to a hydraulic valve,

  in particular a hydraulic valve used in a hydraulic block of a control system for anti-roll of a motor vehicle.

  The active anti-roll system notably makes it possible to improve the comfort, to control the angle of roll when cornering and to influence the dynamic behavior of the vehicle. A hydraulic block of parallelepipedic general shape receiving the hydraulic valve can control a wheel axle position control system.

  The valve according to the invention is one of several identical valves o10 of such an antiroll system, this valve being connected to a fluid supply conduit and to a reservoir. This valve is used to generate pressure in a device for continuously adjusting the position of the wheel axle relative to the body. It can thus deviate all or part of the fluid supply back to this reservoir.

  The position of the wheel axis is constantly detected by sensors connected to a computer which sends a control signal to the control valves associated with the hydraulic unit to thus make corrections of the wheel axis angle substantially in time. real.

  These antiroll systems, as well as their operation, are well known to those skilled in the art and will not be described here in detail.

  There is also known such a hydraulic valve, comprising a main housing to be mounted in a hydraulic block of generally parallelepiped shape and comprising a valve chamber provided with a main inlet for placing in communication with a fluid pressurized by the valve. , and a main outlet to be connected to a tank via said block, a first throttle member being mounted axially displaceable in said valve chamber being urged towards an opening position of said main outlet by said pressure and to a closing position of said main outlet by resilient means disposed in said valve chamber, said pressurized fluid being able to pass through a channel provided in said first throttle member to a channel opening through an orifice in a valve chamber associated with electromagnetic means for controlling said first member 3 Said throttle chamber having an auxiliary outlet to be connected to said reservoir through said block, said electromagnetic control means comprising a control rod whose one end is connected to an armature surrounded by a solenoid while the other end constitutes a second variable throttle member when approaching and moving away from a seat formed around said orifice to cause said first throttle member to move in said valve chamber in a manner such that to continuously adjust the fluid pressure through said main outlet.

  Although this known valve is generally satisfactory, it has a large number of parts and is relatively complicated to manufacture and is of large size. In addition, all its constituent elements, including electromagnetic control means, are assembled to form a single assembly, and this valve lacks flexibility for its implementation in the hydraulic block.

  This is particularly troublesome in its use in a hydraulic block embedded in a motor vehicle in which each space must be optimized and, even better, bring more creative freedom to the manufacturer.

  The object of the invention is to overcome the disadvantages of this known valve to allow its implantation in a more flexible manner in a hydraulic block. The valve according to the invention is largely simplified and has fewer parts relative to the known valve, and it is also particularly well suited to relatively high pressures of the order of 200 bar.

  The object of the invention is a hydraulic valve of the kind mentioned above, characterized in that said electromagnetic control means form with said valve chamber and said valve seat a separate subassembly contained in a secondary housing adapted to be disposed in said block, either in alignment with the longitudinal axis of said main housing, or perpendicular to said axis.

  According to other characteristics of the invention: said main and secondary housings are arranged aligned in a stepped hole passing through said hydraulic block from one side to the other; said main and secondary housings are arranged aligned in a respective bore made in said hydraulic block, the two bores being separated by a transverse wall formed in the hydraulic block and connected to each other by a central bore in said wall; ; said transverse wall of the hydraulic block forms a bearing surface for said resilient means of the valve; said main and secondary housings are placed in an L-shaped formation in a respective bore in said hydraulic block, said bores being connected to each other by a connecting channel; said connecting channel opens out on an annular space delimited between an annular groove on the main housing and the wall of the housing bore thereof, said groove comprising at least one through-hole for setting the part of the valve chamber; which is downstream of the first throttle in communication with said connecting channel; said central bore in said transverse wall of the hydraulic block receives an insert provided with a calibrated through hole; said control rod further comprises a guide flange near the end of said control rod and in contact with the wall of said valve chamber, and said flange is on its periphery provided with recesses forming passages for said fluid; - said recesses forming passages are regularly arranged on the periphery of said collar; said recesses forming passages comprise flats; said passage-forming recesses are three in a triangular arrangement; said second throttle member has a spherical surface whose radius is of the order of 1.9 mm.

  The invention also relates to an anti-roll system for a motor vehicle comprising at least one hydraulic valve as described above.

  Other features and advantages of the invention will emerge from the following description of several non-limiting embodiments of the invention, with reference to the appended figures in which: FIGS. 1A and 1B are longitudinal sectional views showing the hydraulic valve according to the invention, FIG. 1A showing the valve itself and FIG. 1B showing the electromagnetic control means constituting a subset of the valve illustrated in FIG. 1A; - Figure 2 is a longitudinal sectional view of an example of aligned mounting of the valve according to the invention in a hydraulic block; - Figure 3 is a longitudinal sectional view of another example of L-shaped mounting of the valve according to the invention in a hydraulic block; FIG. 4 is a perspective view of a control rod of the valve according to the invention; FIG. 5 is a front view of the control rod of FIG. 4; - Figure 6 is a partial sectional view showing one end of the control rod forming a throttle member in cooperation with a seat; FIG. 7 is another example in longitudinal section of the valve implanted in an aligned arrangement in a hydraulic block; and FIG. 8 is yet another longitudinal sectional example of the valve implanted in an aligned arrangement in a hydraulic block.

  In the figures, identical or equivalent elements will bear the same reference signs.

  Thus, the actual valve 1 (FIG. 1A) is able to be implanted in a hydraulic block 3 (FIG. 2) with its electromagnetic control means comprising a control valve 2 (FIG. 1B). These elements are particularly intended to be used in an anti-roll system of a motor vehicle.

  The valve 1 comprises a cylindrical main casing 4 provided with an inlet 5 opening into a valve chamber 6 and intended for placing the valve in communication with a flow of fluid, in particular mineral oil, supplied by a pump connected to a fluid reservoir (not shown).

  Valve 1 is connected in shunt to a conduit (not shown) connecting the pump to a wheel axle adjuster of a motor vehicle (not shown). In the example shown, several inputs 5 are arranged on the periphery of the housing 4.

  This main housing 4 is also provided with an outlet 7, called the main outlet, connecting this valve chamber 6 to the fluid reservoir.

  In the illustrated example, several outlets 7 are arranged around the periphery of the casing 4. To adjust the flow of the fluid through these outlets 7 by deflecting at least a portion of this flow to the reservoir to create a reduction of the pressure in the reservoir. conduit connected to a device for adjusting the axis of a wheel, a first throttle member 8 in the form of a cylindrical body is mounted axially displaceable in the valve chamber 6 i0 of the main casing 4, between a position d opening and a closed position of the outlets 7 in which it completely hides these.

  This first throttling element 8 is constantly biased towards the opening position of the outlets 7 by the pressure of the fluid upstream, and towards the closed position by an elastic means in the form of a helical spring 9 placed in the chamber valve, behind the first throttle member 8. One of the ends of the spring 9 bears against the bottom of a first central recess 10 provided in one of the end faces of the first throttle member 8, while its opposite end bears against a wall 11 which extends transversely to the longitudinal axis of the main housing 4.

  FIG. 1A shows the position of the first throttling element 8 before assembly of the assembly of FIG. 1A in the hydraulic block 3, that is to say in the absence of pressure at the inlets 5.

  The first throttle member 8 has on its opposite end face a second central recess 12 having a cylindrical inner wall 13 followed by a conical wall 14 whose apex is directed towards the spring 9. A central bore 15 is made at the top of this conical wall to form a channel connecting the first central recess 10 to the second central recess 12. The transverse wall 11 also has a central bore 16 forming a channel to the electromagnetic control means illustrated in Figure 1B.

  In the example illustrated in FIGS. 1A and 2, the transverse wall 11 is constituted by an attached plate which is crimped to the corresponding end of the main casing 4. Furthermore, the opposite end of the main casing 4 is closed. by a transverse wall 17 in one piece with the main housing. This transverse wall 17 projects radially so as to form a flange 18.

  The main housing also usually has grooves 19 on its periphery receiving gaskets 20.

  Thus, during the operation of the antiroll system, a fluid flow is continuously supplied to the inlets 5 of the valve 1, the pressure acts on the upstream end of the first throttle member 8 to move it to the right in the figure 1A so that a large flow can exit through the outlets 6 and be discharged to the tank. By way of example, this large flow can reach a value of the order of 30 l / min. At the same time, a small flow rate of the order of 0.2 l / min passes through the channel 15 in the first throttle member 8 and the channel 16 in the transverse wall 11 to reach the electromagnetic control means which will now be described. with reference to FIG.

  The electromagnetic control means are in the form of a control valve 2 comprising a housing 21 separated from the main housing 4 of the valve and here called secondary housing.

  This secondary housing 21 has a generally cylindrical shape and is provided with an inlet 22 receiving the low-flow fluid which exits the valve 1 through the central channel 16 thereof. This inlet 22 is connected to a valve chamber 23 by a channel 24 which opens there through an orifice 25 which widens towards the valve chamber so as to form a seat 26 of the valve.

  The valve chamber 23 is provided with outlets 27 which form auxiliary outlets to the tank via the hydraulic block 3. In the illustrated example, filters 28 are arranged at these auxiliary outlets 27.

  A throttle member said second throttle member 29 is formed at one end of a control rod 30 housed in a central bore 31 of the secondary housing 21 and whose opposite end protrudes out of the housing to be connected to an armature 32 surrounded by a solenoid 33. The armature 32 is placed in the extension of the housing 21 in a tubular nonmagnetic element 34 closed at one of its ends, while its opposite end is fixed on the periphery of the housing 21 to encapsulate the armature 32. This tubular element 34 is an integral part of the secondary housing.

  This second throttling element, which has the shape of a spherical cap, is disposed in the valve chamber 23 facing the valve seat 26 which has a complementary shape so as to define together a variable passage section for the small flow in function of the actuation of the solenoid 33 which acts on the armature 32 to urge the control rod 30 to bring said second throttle member 29 of the seat 26 so as to continuously adjust the fluid passage section to the valve chamber 23.

  To be well adapted to a pressure of up to 200 bar, this spherical cap has a radius R of the order of 1.9 mm, while the valve seat 26 has a conical shape.

  In order to radially stabilize the control rod 30 within the valve chamber 23, the rod has a guide flange 35 in contact with the wall of the valve chamber. In order to allow the fluid to flow freely behind the flange during the movements of the control rod, the flange is on its periphery provided with recesses 36 (see FIGS. 4 and 5). These recesses are evenly spaced and are preferably defined by flats interconnecting circular sections 37 forming guide surfaces. They are preferably three in number and placed in a triangular arrangement.

  Each variation of the small flow rate by adjusting the fluid passage section to the valve chamber 23 causes a corresponding displacement of the first throttle member 8 of the valve 1 to more or less obstruct the valve outlets 7. according to a demand for force by the anti-roll system.

  According to an important characteristic of the invention, the electromagnetic control means form with the valve chamber and the valve seat 26 a separate subassembly contained in the secondary housing 21, 34 and adapted to be disposed in the parallelepiped hydraulic block. 3 is in alignment with the longitudinal axis AA of the main housing 4 (see Figures 2, 7 and 8), or perpendicular to this axis (see Figure 3). This subassembly may also be arranged to be offset, but parallel to the longitudinal axis A-A of the main housing 4 to better adapt its implementation according to the environment around the hydraulic block.

  This gives a very great flexibility for the location of all the components of the valve in the hydraulic block 3 and all the assembly becomes easily adaptable to the volume available for the anti-roll system of a motor vehicle.

  FIG. 2 shows an example of installation of the valve 1 in alignment with the subassembly containing the electromagnetic means in the hydraulic block 3. The block 3 is provided with a stepped transverse hole 38 which passes through the block of part in part to form a housing in which the valve 1 is introduced on one side and the electromagnetic valve 2 on the other, so that the central channel 16 in the transverse wall 11 of the valve 1 opens directly into the inlet 22 of the valve 2.

  The hydraulic block 3 also has a fluid supply channel 39 opening into a circular space 40 delimited between the inner wall 15 of the bore 38 and a groove 41 having the inputs 5 of the valve. The block also comprises a fluid discharge channel 42 in another circular space 41 at the outlets 6 of the valve, and a fluid outlet channel 44 connected to the outlets 27 of the valve chamber 23.

  Figure 3 shows an example of installation of the valve 1 in which the subset with the electromagnetic means is disposed in the hydraulic block 3 perpendicular to the axis A-A of the main housing 4 of the valve. An L-shaped arrangement of the valve is thus obtained with its electromagnetic control means. The valve 1 is received in a blind bore 45 in the hydraulic block 3, while the electromagnetic valve is received in another bore 46 in the block, the latter bore extending perpendicularly to the first.

  The bore 46 communicates with the bore 45 via a connecting channel 47 opening into a third annular space 48 delimited between an annular groove 49 on the main housing 4 and the wall of the bore 45. The groove 49 comprises at least a through hole 50 for setting the valve chamber portion 6 which is downstream of the first throttle member in communication with the channel 47.

  This through hole 50 provides the same function as the central bore 16 forming a channel in the transverse wall 11 of FIGS. 1A and 2. The plate constituting this transverse wall can advantageously be omitted in the embodiment shown in FIG. 3 and in FIG. In this case, the bottom 51 of the blind bore 45 constitutes this transverse wall against which the spring 9 of the valve bears.

  Furthermore, the evacuation channel 44 is connected to the outlets 27 of the secondary housing 21 and advantageously joins the evacuation channel 42 connected to the main outlets 7 of the main housing 4.

  According to a variant (not shown in the figures) of the L-shaped arrangement of the valve with its electromagnetic control means, the transverse wall 11 of the valve 1 is constituted by a plate like that illustrated in FIGS. 1A and 2, whereas the channel 47 in Figure 3 is performed in the hydraulic block 3 so as to open in front of the plate 11 in the bore 45 of the block. With respect to what is illustrated in Figure 3, the channel 47 is simply moved to the left and the through hole 50 in the main housing 4 is of course deleted.

  FIG. 7 shows a variant of the aligned assembly described with reference to FIG. 2. In this case, two bores 52, 53 aligned one on the other have been made in the hydraulic block 3, one 52 to receive the valve 1, and the other 53 to receive the secondary housing 21, 34 containing the electromagnetic control means. These two bores are separated from each other by a transverse wall 54 formed in the hydraulic block 3 and connected to each other by a central bore 55.

  As in the embodiment shown in FIG. 3, the transverse wall 54 forms a bearing surface for the spring of the valve 1 which thus bears directly against the bottom 56 of the bore 52.

  FIG. 8 shows a variant of the embodiment of FIG. 7. The only difference lies in the fact that the central bore 55 has been widened to receive a cylindrical insert 57 having a calibrated through central hole 30.

  Thus, thanks to the invention, a great flexibility is obtained and the subassembly comprising the electromagnetic control means can be arranged in an optimum manner and, in particular, the solenoid 33 can be arranged on one of the faces of the hydraulic block. , while the valve itself is mounted on another face perpendicular to the first.

  Of course, the invention is not limited to the examples illustrated and described, and even if it is particularly well suited to be used in a hydraulic block of an anti-roll system of a motor vehicle, it can find other applications. in which there is a need for flexibility in mounting on a hydraulic block to adapt it to a limited and specific space environment.

Claims (13)

  1. Hydraulic valve, comprising a main housing (4) to be mounted in a hydraulic block (3) of generally parallelepipedal shape and comprising a valve chamber (6) provided with a main inlet (5) for setting in communication with a fluid pressurized by the valve, and a main outlet (7) to be connected to a tank via said block (3), a first throttle (8) being mounted axially displaceable in said chamber valve (6) being urged toward an open position of said main outlet (7) by said pressure and to a closed position of said main outlet by resilient means (9) disposed in said valve chamber (6). ), said pressurized fluid being able to pass through a channel (15) provided in said first throttle member to a channel (24) opening through an orifice (25) into a valve chamber (23) associated with electromagnetic meanscontrol (30, 32) of said first throttle (8), said valve chamber (23) having an auxiliary output (27) to be connected to said reservoir through said block (3), said electromagnetic means of control comprising a control rod (30) whose one end is connected to an armature (32) surrounded by a solenoid (33), while the other end constitutes a second variable throttle member (29) in approaching and moving away from a seat (26) formed around said orifice (25) to cause said first throttle (8) to move in said valve chamber (6) to continuously adjust the fluid flow through said main outlet, characterized in that said electromagnetic control means (30, 32) form with said valve chamber (23) and said valve seat (26) a separate subassembly contained in a housing secondary school (21, 34) suitable for be disposed in said block (3), either in alignment with the longitudinal axis (A-A) of said main housing (4), or perpendicular to said axis.   2. Hydraulic valve according to claim 1, characterized in that said main and secondary housings (4, 21) are arranged aligned in a stepped hole (38) passing through said hydraulic block (3) from one side.   3. Hydraulic valve according to claim 1, characterized in that said main and secondary housings (4, 21) are arranged aligned in a respective bore (52, 53) made in said hydraulic block, the two bores being separated by a wall 5 (54) formed in the hydraulic block (3) and connected to each other by a central bore (55) in said wall (54).   4. Hydraulic valve according to claim 3, characterized in that said transverse wall (54) of the hydraulic block (3) forms a bearing surface for said resilient means (9) of the valve (1).   5. Hydraulic valve according to claim 1, characterized in that said main and secondary housings (4, 21) are placed in an L-shaped formation in a respective bore (45, 46) in said hydraulic block (3), said bores (45, 46) being connected to each other by a connecting channel (47).   6. Hydraulic valve according to claim 5, characterized in that said connecting channel (47) opens on an annular space (48) defined between an annular groove (49) on said main housing (4) and the wall of the a housing bore (45) thereof, said groove (49) having at least one through-hole (50) for the valve chamber portion (6) which is located downstream of the first throttle member (8); ) in communication with said connecting channel (47).   7. Hydraulic valve according to any one of claims 3, 4 or 6, characterized in that said central bore (55) in said transverse wall (54) of the hydraulic block (3) receives an insert (57) 25 provided with a calibrated through hole.   8. Hydraulic valve according to any one of the preceding claims, characterized in that said control rod (30) further comprises a guide flange (35) near the end of said control rod and in contact with the wall of said valve chamber (23), and in that said flange (35) is on its periphery provided with recesses (36) forming passages for said fluid.   9. Hydraulic valve according to claim 8, characterized in that said recesses (36) forming passages are regularly arranged on the periphery of said flange (35).   10. Hydraulic valve according to claim 8 or 9, characterized in that said recesses (36) forming passages comprise flats.   11. Hydraulic valve according to claim 9 or 10, characterized in that said recesses (36) forming passages are three in a triangular arrangement.   12. Hydraulic valve according to any one of the preceding claims, wherein said second throttle member (29) has a spherical surface, characterized in that the radius (R) of this spherical surface is of the order of 1.9 mm.   13. anti-roll system for a motor vehicle, characterized in that it comprises a hydraulic valve according to one of claims 1 to 12.