A PROCESS FOR ASSEMBLING A ROTARY VALVE

Abstract: A rotary valve assembly and a method of assembling such a valve has a sleeve 5 and a rotor 3 relative rotation between which from a neutral condition adjusts the valve. The sleeve and rotor are biased to the neutral condition by an encircling C-spring reacting on pins corresponding to projections lla and l2 relatively rotatable with the sleeve 5 and rotor 3 respectively. For setting-up the valve in its neutral condition the sleeve and rotor are mounted in a jig l5 with the projection lla of the jig engaging in a recess 27 of an adjustable component in the form of a second C-spring 24 which is initially rotatable on the sleeve 5. The sleeve 5 is rotated relative to the spring 24 and projections lla and l2 to determine the neutral condition by the characteristics of fluid applied through valve ports E, S, P₁, P₂. The spring 24 is now welded or otherwise secured to the sleeve 5. The spring 24 serves to frictionally engage the sleeve and alleviates displacement relative thereto following adjustment of the valve to the neutral condition and prior to welding. In a second embodiment the projection lla directly engages the sleeve 5 to restrain relative rotation therebetween and the pin l2 is carried by a C-spring to be rotationally adjustable on the rotor 3 for the purpose of setting-up the valve in its neutral condition prior to the pin l2 being welded to the rotor 3.

Description: TECHNICAL FIELD & BACKGROUND ART The present invention relates to rotary valves and is particularly concerned with a process for assembling such a rotary valve. More particularly the invention concerns a rotary valve of the type having a sleeve member, a rotor member within the sleeve member and relative rotation between which members about an axis and from a neutral condition causes an adjustment in the valve, C-spring means circumferentially biasing the sleeve member relative to the rotor member and the assembly to said neutral condition, the C-spring means being located around the axis and having a mouth within which is located a first abutment secured relative to the rotor member and a second abutment secured relative to the sleeve member, the abutments reacting against the C-spring means in the mouth thereof to enlarge the mouth during relative rotation between the rotor and sleeve members to effect the said biasing - such a rotary valve will hereinafter be referred to as "of the type specified". Rotary valves of the type specified are frequently employed in power assisted vehicle steering gears where relative rotation between the rotor and sleeve members in response to a steering input torque and from the neutral condition adjusts the valve to control the power assistance which is provided. The biasing of the C-spring means, either independently or in combination with other spring biasing such as a torsion rod as is well known in rotary valves, causes the rotary valve to revert to its neutral condition upon removal of the input torque; an example of a rotary valve of the type specified is to be found in our British Patent Specification No. 1,603,198. For efficient operation of a rotary valve of the type specified it is desirable that the valve is correctly set-up (sometimes referred to as "balanced") when in its neutral condition, that is to say that the spring biasing means which reacts between the rotor and sleeve members should bias those members rotationally relative to each other and to the neutral condition in which condition fluid flow, if any, through the valve should present predetermined, balanced, characteristics. A typical rotary valve of the type specified for a power assisted vehicle steering gear will provide open centre, open return characteristics in its neutral condition and in this condition a supply of fluid under pressure to a common inlet port of the valve should provide pressure drops which are balanced over outlet ports of the valve these ports corresponding to connections on the valve, for example, to opposite sides of a power assistance ram and to a fluid exhaust or return. A rotary valve which does not provide balanced characteristics in a neutral condition as aforementioned is undesirable as it will be appreciated that, particularly in a power assisted steering gear, the use of such a valve can adversely effect the characteristics of the steering gear to an unacceptable extent. U.S. 4,143,676 discloses a rotary valve of the type specified which is balanced by circumferential adjustment in the positioning of one of the abutments against which the C-spring means reacts by use of adjustment screws. It is an object of the present invention to provide a process for assembling a rotary valve of the type specified by which the characteristics of the valve in a neutral condition or the balancing of the valve can be determined to alleviate the disadvantages discussed above and in a manner which alleviates the requirement for the adjustment of screws. STATEMENTS OF INVENTION & ADVANTAGES According to the present invention there is provided a process for assembling a rotary valve having a sleeve member, a rotor member within the sleeve member and relative rotation between which members about an axis and from a neutral condition causes an adjustment in the valve, C-spring means circumferentially biasing the sleeve member relative to the rotor member and the valve to said neutral condition, the C-spring means being located around the axis and having a mouth within which is located a first abutment secured relative to the rotor member and a second abutment secured relative to the sleeve member, the abutments reacting against the C-spring means in the mouth thereof to enlarge the mouth during relative rotation between the rotor and sleeve members to effect said biasing, and which process comprises an adjustment in the location of the circumferential position of one of said abutments relative to its respective sleeve or rotor member and positioning the rotor member circumferentially relative to the sleeve member to provide desired characteristics of the valve in the neutral condition, and securing the so-adjusted location relative to its respective sleeve or rotor member CHARACTERISED IN THAT said one abutment is carried to be displaced circumferentially in unison with its respective sleeve or rotor member by an adjustable spring component and the process comprises locating the spring component on the member with which said one abutment is to be circumferentially displaced in unison and with the spring component extending around the axis of the valve and biased into frictional engagement with the member on which it is located, displacing the spring component against its biasing to facilitate circumferential adjustment of the spring component on the member on which it is located in determining said adjusted location, and securing the spring component to the respective sleeve or rotor member on which it is located to rotate in unison therewith at said adjusted location. By the present invention it is envisaged that the rotor and sleeve members of the rotary valve will initially be assembled so that the abutments of those members will initially be located for engagement with the C-spring biasing and this initial location of the two abutments will determine a neutral condition of the valve. Following this initial assembly the valve can be tested by subjecting it to fluid under pressure (conveniently from an air pressure line although usually the rotary valve will be used in practice for controlling hydraulic fluid) and pressure readings taken over various ports of the valve to assess whether the valve is in a preferred neutral condition or otherwise. Where it is found that the valve is out of balance, one or other (or possibly both) of the locations for the abutments is displaced circumferentially relative to its respective rotor or sleeve member (to which that location or abutment will eventually be secured) by circumferential adjustment of the spring component so that, in effect, the sleeve is rotated partially relative to the rotor until a balanced or the predetermined neutral condition for the valve is achieved. In this latter condition the respective one or both of the abutments or the locations for those abutments is secured in position relative to its respective rotor or sleeve members by securing the spring component to that respective member. This initial adjustment of the rotor and sleeve members and effective positioning of the abutments (or the location for those abutments or the respective members) by adjustment of the spring component and the fluid pressure testing of the valve to determine the neutral condition is conveniently achieved in a jig. The jig will generally correspond to a housing in which the valve will be accommodated in practice but may have the facility to provide convenient access for the purpose of adjusting the spring component circumferentially relative to the respective sleeve or rotor member to which it is to be secured. One or other (or each) of the sleeve and rotor members can carry the spring component which component itself carries, or is intended to engage with, the abutment which is to be circumferentially displaceable in unison with the respective sleeve member or rotor member. Initially the spring component is circumferentially adjustable relative to its respective sleeve member or rotor member for the purpose of positioning the circumferential location of the abutment relative to the sleeve or rotor member with which that abutment is to be circumferentially displaceable as a unit; ultimately (that is following the determination of the preferred neutral condition) the spring component is fixedly secured relative to its sleeve or rotor member for rotation in unison with that member. Following the initial adjustment of the spring component to a position in which the valve demonstrates the desired characteristics in its neutral condition, the spring component is conveniently fixedly secured relative to its respective sleeve or rotor member by a simple locking screw, rivet or a simple welding, bonding or adhesive techniques. The spring component is conveniently in the form of a second C-spring means which extends around the axis of the valve assembly and is spring biased into frictional engagement with its respective sleeve or rotor member but can be displaced against its biasing to permit circumferential displacement between itself and its member as the rotary valve is being set up to provide the predetermined characteristics in the neutral condition. The spring biasing of the second C-spring means into frictional engagement with the respective rotor or sleeve member with which it is ultimately intended to be secured provides a convenient means by which it may be ensured that the spring component is temporarily held in position on its respective member following adjustment of the valve to the desired neutral condition and until such time as the spring component can be fixedly secured to its member, for example by adhesive or welding as aforementioned. Generally the first abutment which is secured for rotation with the rotor member will comprise a radial projection on the rotor member while the second abutment secured for rotation with the sleeve member will comprise an axial projection; with such an arrangement it is preferred that the radial projection is rigid with the rotor for circumferential displacement therewith and that the second abutment (or the position for the location of that abutment) is initially circumferentially adjustable relative to the sleeve member by the spring component. DRAWINGS Embodiments of a rotary valve assembly of the type specified and constructed in accordance with the present invention will now be described, by way of example only, with reference to the accompanying illustrative drawings in which: Figure 1 is an axial section through part of a rack and pinion power assisted steering gear which incorporates one embodiment of the rotary valve; Figure 2 is an axial section of the rotor and sleeve members incorporated in the valve in Figure 1 and which members are assembled in a jig for the purpose of determining and adjusting the characteristic of the valve in its neutral condition; Figure 2A is a perspective view of an end cap of the jig shown in Figure 2; Figure 3 is an end view of the sleeve member of the valve along the line III-III of Figure 2 and illustrates the adjustable spring component on that member; Figure 4 shows a section along the line IV-IV of Figure 3; Figure 5 is an axial section of rotor and sleeve members for a second embodiment of the rotary valve assembled in a jig similar to that shown in Figure 2 but with the adjustable spring component on the rotor member for the purpose of determining and adjusting the characteristic of the valve in its neutral condition, and Figure 6 is a section of the jig and rotary valve assembly shown in Figure 5 taken on the line VI-VI of that Figure. DETAILED DESCRIPTION WITH REFERENCE TO DRAWINGS The rack and pinion power assisted steering gear of which the arrangement shown in Figure 1 forms part may be considered to operate generally in accordance with conventional practice and has a steering input shaft 1 an inner end of which forms a rotor 3. The rotor 3 is received in a cylinder 4 of a valve sleeve 5 which latter is received in a cylinder 6 of a housing 7. The sleeve 5 is rotatably mounted in the cylinder 6 and is coupled to rotate in unison about axis 8 with a shaft 9 of a pinion 10 driving a rack bar (not shown) in conventional manner to effect a steering manoevre. The coupling between the pinion shaft 9 and the valve sleeve 5 is provided by an axially projecting spigot 11 engaging axially in a complementary sized recess 27 carried by the adjacent end of the sleeve 5. Projecting radially from the rotor 3 and in radial alignment with the projection 11 is a pin 12 secured for rotation with the rotor. Mounted on and extending around the rotor 3 in the radial plane of the pin 12 is a C-spring 13 having a mouth (not shown) within which is located the projection 11 and the pin 12 so that the mouth radially overlies and circumferentially opposed sides thereof abut both of these projections. The purpose served by the C-spring 13 is similar to that discussed in our British Patent Specification No. 1,603,198. It will be appreciated that during relative rotation between the rotor 3 and sleeve 5 (and thereby between the pin 12 and projection 11) about the axis 8 in one or the opposite senses of direction in response to a steering input torque, the abutment of the pin 12 and projection 11 with the opposite sides of the mouth of the C-spring l3 will cause that mouth to enlarge circumferentially. The C-spring is thereby energised and this acts to bias the pin 12 and projection ll into their positions in radial alignment with each other; these latter positions correspond to the rotor 3 and sleeve 5 being in a neutral condition of the rotary valve formed by these members. In the present example a conventional form of torsion bar l4 is shown housed in a central bore l7 of the rotor to couple the pinion shaft 9 to the input shaft l and additionally serve to bias the rotor and sleeve to the neutral condition in conventional manner; however for the purpose of an understanding of the present invention, the presence of the torsion bar l4 can be disregarded. In its use in a power assisted vehicle steering gear, the rotary valve formed by the rotor 3 and sleeve 5 will usually be of the closed centre or open centre type, more commonly the open centre type of valve is employed with an open centre return in its neutral condition. When in its neutral condition, it is desirable that the rotary valve is balanced with regard to the source of fluid under pressure which is applied to it so that the pressure differential between that source and outlets of the valve (say to opposite sides of a power assistance ram) are symmetrical; to achieve this it will be apparent that the position of the ports 3a in the rotor 3 must be accurately located circumferentially with respect to the ports (not shown) in the sleeve 5 with which they are to effect control of the fluid passing through the valve. This accurate location between the respective control ports must be determined bearing in mind the relative positions of the pin 12 and projection 11. An arrangement for achieving a required balancing of the rotary valve comprising the members 3 and 5 in a neutral condition will now be described with reference to Figures 2 to 4. Prior to incorporating the rotor 3 and its sleeve 5 in the steering gear shown in Figure l, these members are mounted in a jig l5 (which effectively substitutes for the housing 7) which comprises a cylindrical wall 15a within which the sleeve 5 is closely received, an end wall 15b secured to wall 15a and through an aperture in which the input shaft l extends, and an end cap 15c. The end cap 15c has a spigot 16 which co-operates co-axially with the bore 17 in the rotor 3 so that the end cap 15c can rotate about the spigot l6 and relative to the rotor 3 and the cylinder wall 15a. The sleeve 5 is restrained from rotation relative to the walls 15a and 15b by pins 18. In effect, the end cap 15c serves as a substitute for the pinion shaft 9 in Figure 1. This cap has an axially extending projection 11a intended to correspond to the projection 11 in Figure l) and couples the end cap l5c to the recess 27 in the end of the sleeve 5 so that the end cap l5c and sleeve 5 can rotate in unison about the axis 8. The projection 11a is formed as part of a bracket 20 (see Figure 2A) on the end cap l5c. The bracket 20 has opposed side walls 2l which form a recess 22 radially inwardly of and in radial alignment with the projection 11a. On fitting the end cap 15c as part of the jig, the radial pin l2 of the rotor 3 is axially received in the recess 22 as a close sliding fit between the walls 2l so that the end cap l5c and rotor 3 will rotate in unison about the axis 8. Mounted on the end face 23 of the sleeve 5 adjacent to the end cap l5c is an adjustment component in the form of a second C-spring 24 (best shown in Figures 3 and 4). The spring 24 has a mouth 25 formed by ears 26. Circumferentially spaced from the mouth 25, conveniently diametrically opposite thereto, is the recess 27 which is formed by circumferentially spaced and radially outwardly extending bosses 28 on the C-spring. The spring 24 is mounted on the end face 23 of the valve sleeve 5 within an axially extending cylindrical skirt 29 of the sleeve and so that the radially outer marginal edge part of the spring 24 is seated within an internal recess 30 of the skirt 29. The spring 24 is resiliently biased in a sense to circumferentially enlarge its mouth 25 so that its aforementioned marginal edge part is urged into engagement with the recess 30 as shown in Figure 4. Preferably the axially opposed side faces of the recess 30 converge as the depth of the recess increases (as shown in Figure 4) so that the biasing of the spring 24 urges the edge of that spring as a wedge fit into the recess 30. To permit the spring 24 to engage in the recess 30, clearance is provided in the skirt 29 to accommodate the ears 26 and the outer peripheral part of the spring between the bosses 28; more particularly the skirt 29 is shown in Figure 3 cut-away at 3l to accommodate the ears 26 and cut-away at 32 to accommodate the bosses 28. With the spring 24 mounted on the end face 23 of the sleeve 5 as aforementioned, the natural resilience of the spring urging it into frictional engagement with the recess 30 in the valve sleeve will normally, and to a limited extent, retain the C-spring against rotation about the axis 8 relative to the valve sleeve 5. By closing the mouth 25 of the C-spring (by nipping together the ears 26 with an appropriate tool) it will be apparent that the diameter of the C-spring is effectively reduced; the retaining pressure between the C-spring and the recess 30 can thereby be relieved to an extent that the C-spring 24 may, as determined by the circumferential clearance of the cut-away region 3l or 32, be partically rotated about the axis 8 relative to the valve sleeve 5. The recess 27 in the second C-spring 24 is located on the end face of the valve sleeve 5 in axial alignment with the projection 11a of the end cap and this recess 27 axially receives the projection 11a as a reasonably close sliding fit as shown in Figure 2. Consequently, with the spring 24 frictionally secured to the sleeve 5(by the natural biasing of the spring 24 into engagement with the recess 30), the spring 24 may be considered as rotating in unison with the sleeve 5; from this it follows that the coupling of the end cap 15c (through the projection 11a and recess 27) with the valve sleeve 5 can cause the valve sleeve and end cap l5c to rotate in unison and that the end cap and valve sleeve could be rotated by rotation of the shaft l through the rotor 3 and radially extending pin l2. In practice the cut-away parts 3l and 32 (particularly 32) in the skirt 29 of the valve sleeve will be positioned on that sleeve and with respect to the central ports in the sleeve (which ports co-operate with the ports 3a on the rotor to effect control of the fluid) so that when the sleeve and rotor are fitted into the jig as shown in Figure 2, the circumferential orientation between the rotor and sleeve as determined by the engagement of the radial pin l2 in the recess 22 and the engagement of the axial projection 11a in the recess 27, will approximate to the valve being in its intended neutral condition. With the valve sleeve and rotor fitted in the jig l5 as described above, the characteristics of the rotary valve in its neutral condition and as they will occur in practice can be simulated in the jig 15 by the provision, in the cylinder wall 15a as shown in Figure 2, of a common fluid pressure port S, ports Pl and P2 (which may be intended for connection to opposite sides of a power assistance ram) and a common return port E (intended for communication to reservoir). The ports in the wall 15a will interconnect and be controlled by the rotary valve in conventional manner. It will be predetermined that if the rotary valve is in its desired neutral condition, when fluid pressure is applied to the port S there will be resultant known or balanced pressures at the ports P1, P2 and E. Accordingly a predetermined fluid pressure is applied at port S (conveniently from an air line) and the resultant pressures at P1, P2 and E determined. If these latter pressures do not correspond to those which would be expected with the rotary valve in its neutral condition, it will be apparent that some adjustment is necessary in the relative positioning of the control ports between the sleeve and the rotor by effectively rotationally adjusting the sleeve 5 relative to the rotor 3 (and relative to the axial projection 11a bearing in mind that the engagement of the projection 11a with the sleeve 5 determines the neutral condition). Accordingly, to effect the aforementioned adjustment, the pressure exerted by the C-spring 24 and which frictionally secures that spring relative to the valve sleeve 5 is relieved by nipping together the ears 26 of the spring with an appropriate tool as previously discussed. The tool can conveniently be applied to the C-spring through an access opening 40 provided in the cylinder wall 15a. With the diameter of the C-spring 24 reduced, the spring 24 can be displaced circumferentially relative to the sleeve 5 (the latter being restrained from rotation by the pins l8) and within the extent of the cut-away region 32. During this circumferential displacement of the spring 24 relative to the sleeve 5, the end cap l5c and rotor 3 are also circumferentially displaced relative to the sleeve 5 (by the engagement of the projection 11a with the recess 27 in the spring 24 and the engagement of the pin l2 with the recess 22 in radial alignment with the projection 11a). As a consequence, the control ports between the valve sleeve and valve rotor are circumferentially adjusted until the control ports are positioned in the desired neutral condition of the rotary valve (as determined by observation of the pressures at the ports P1, P2 and E). With the valve so adjusted to its predetermined neutral condition, the restraint on the C-spring 24 is removed to allow that spring to expand under its natural resilience into frictional engagement with the recess 30; this effectively retains the spring 24 on the valve sleeve 5 with the recess 27 of the spring accurately located at a position in which it engages with the projection 13a (and will therefore engage with the axial projection 11 in the steering gear assembly of Figure l) with the valve and sleeve members in their desired neutral condition. Having so adjusted the rotary valve, the rotor 3 and sleeve 5 are removed from the jig l5 without disturbing the relationship between the C-spring 24 and the valve sleeve. The C-spring 24 is now fixedly secured to the valve sleeve, conveniently by a laser welding technique or by adhesive bonding. Effectively the adjustment component provided by the C-spring 24 now becomes an integral part of the valve sleeve in which the recess 27 is to be coupled with the axial projection ll of the steering gear in Figure 1. Consequently when the sleeve an d rotor of the valve assembly are incorporated in the power assisted steering gear shown in Figure l with the projection 11 axially received in the recess 27 to provide the coupling between the pinion shaft 9 and the sleeve 5 (while the C-spring l3 biases the pin l2 and projection 11 into radial alignment) it will be known that the rotary valve is in its desired neutral condition. The above described and illustrated embodiment utilises circumferential displacement of the position of the location for the coupling of the projection 11 relative to the valve sleeve for setting up the valve in its desired neutral condition. However, in a second embodiment the rotary valve can be set-up to its desired neutral condition by having an initially fixed coupling between the projection 11a and valve sleeve 5 in the jig and providing means whereby the pin l2 can, in effect, be circumferentially displaced relative to the rotor 3 and thereafter that pin fixedly secured to the rotor when the assembly has been adjusted to its desired neutral condition. Such a second embodiment will now be described with reference to Figures 5 and 6 in which the pin l2 is carried by (preferably an integral part of) a C-spring 50 which encircles the rotor 3 and is received in an annular recess 5l in the rotor. The spring 50 is normally biased into frictional engagement with the rotor 3 in the recess 5l but can be displaced against its biasing to diametrically enlarge the spring by opening the mouth of the spring with an appropriate tool (not shown) applied to the opposed ends 50a of the spring - the aforementioned tool is conveniently applied through the opening 40 in the jig wall as previously discussed. By relieving pressure on the spring 50, the rotor 3 can be circumferentially displaced relative to the pin l2. In this second embodiment the projection 11a of the end cap l5c of the jig is received as a reasonably close sliding fit in a complementary recess 52 in the end face of the sleeve 5 so that the sleeve 5 is thereby restrained from rotation relative to the end cap l5c. In addition the jig walls 15a and 15b (not shown in Figure 5) are restrained from rotation relative to the end cap l5c and the C-spring 50 is restrained from rotation relative to the end cap l5c (by engagement of the projection l2 closely within the confines of the opposed side walls 2l of the bracket 20 on the end cap of the jig). With pressure relieved on the spring 50 as previously mentioned, the rotor 3 can be circumferentially displaced relative to the pin l2 and to the sleeve 5 until the rotary valve is adjusted to its desired neutral condition as previously explained. In this latter condition the spring 50 is permitted to frictionally engage the rotor and the so adjusted rotor and sleeve are removed from the jig and the pin 12/spring 50 fixedly secured relative to the rotor 3, for example by locking screws, adhesive or welding, prior to the valve assembly being incorporated in the gear of Figure 1.

Claims: A process for assembling a rotary valve having a sleeve member (5), a rotor member (3) within the sleeve member (5) and relative rotation between which members about an axis (8) and from a neutral condition causes an adjustment in the valve, C-spring means (13) circumferentially biasing the sleeve member (5) relative to the rotor member (3) and the valve to said neutral condition, the C-spring means (13) being located around the axis (8) and having a mouth within which is located a first abutment (12) secured relative to the rotor member (3) and a second abutment (11) secured relative to the sleeve member (5), the abutments (11,12) reacting against the C-spring means (13) in the mouth thereof to enlarge the mouth during relative rotation between the rotor and sleeve members to effect said biasing, and which process comprises an adjustment in the location of the circumferential position of one of said abutments (11, 12) relative to its respective sleeve or rotor member (5, 3) and positioning the rotor member (3) circumferentially relative to the sleeve member (5) to provide desired characteristics of the valve in the neutral condition, and securing the so-adjusted location relative to its respective sleeve or rotor member (5, 3) CHARACTERISED IN THAT said one abutment (11,12) is carried to be displaced circumferentially in unison with its respective sleeve or rotor member by an adjustable spring component (24) and the process comprises locating the spring component (24) on the member (3, 5) with which said one abutment is to be circumferentially displaced in unison and with the spring component (24) extending around the axis of the valve and biased into frictional engagement with the member on which it is located, displacing the spring component (24) against its biasing to facilitate circumferential adjustment of the spring component on the member on which it is located in determining said adjusted location, and securing the spring component (24) to the respective sleeve or rotor member (5, 3) on which it is located to rotate in unison therewith at said adjusted location. A process as claimed in claim 1 in which the adjustable spring component comprises second C-spring means (24) and which comprises locating the second C-spring means to frictionally engage radially in a circumferential recess (30) in the sleeve or rotor member by which it is carried. A process as claimed in either claim 1 or claim 2 in which said one abutment comprises a projection (11) and the adjustable spring component (24) comprises means (27) which engages with said projection (11) to rotate in unison therewith. A process as claimed in claim 3 in which the means which engages the said projection (11) comprises a location recess (27) in the adjustable spring component (24) within which the projection (11) is closely received. A process as claimed in either claim 3 or claim 4 in which the second abutment comprises an axially extending projection (11) and said projection engages with the location means (27) on the adjustable spring component (24) for rotation in unison therewith and with the sleeve member (5). A process as claimed in either claim 1 or claim 2 in which said one abutment comprises a projection (12) and said projection is carried by the adjustable spring component (50). A process as claimed in claim 6 in which the first abutment comprises a radially extending projection (12) carried by the adjustable spring component (50) for rotation in unison with the rotor member (3). A process as claimed in any one of the preceding claims which comprises securing the spring component (24) to the respective sleeve or rotor member on which it is located to rotate in unison therewith by at least one of locking screw means, rivetting, welding, bonding or adhesive. A process as claimed in any one of the preceding claims which comprises locating the valve in a jig (15) which provides a housing for the sleeve and rotor members (5, 3) and provides access to the spring component (24) for facilitating the circumferential adjustment of that component relative to the respective sleeve or rotor member on which it is located. A process as claimed in claim 9 which comprises subjecting the valve in the jig (15) to fluid pressure and determining fluid pressure characteristics at ports (P1, P2) of the valve, and circumferentially adjusting the spring component (24) for said fluid pressure characteristics to be consistent with the valve being in its neutral condition and securing the spring component (24) to the respective sleeve or rotor member (5, 3) on which it is located to rotate in unison therewith at the adjusted position.

Inventors: RAYNER, ALAN
Applicants: TRW CAM GEARS LIMITED
Application year: 1987
Main classification: B62D5
IPC codes: B62D5