HYDRAULIC VALVE

Abstract

A drive lever comprising a first end for insertion into a slot of the hydraulic spool valve. The first end comprises at least two resilient members which resist radial compression (R.sub.1, R.sub.2) such that they exert a radially outward force (F.sub.1, F.sub.2) on one or more inner surfaces of the slot when inserted therein. This radially outward force (F.sub.1, F.sub.2) can account for any backlash that would otherwise be present between the drive lever and the slot due to manufacturing tolerances or wear.

Claims

1. A drive lever for actuating a hydraulic spool valve, the drive lever extending along a longitudinal axis (L) to a first end configured to engage a slot of a hydraulic spool valve, wherein the first end comprises at least two resilient members configured to exert a radially outward force (F.sub.1, F.sub.2) on one or more inner surfaces of a slot of a hydraulic spool valve.

2. The drive lever of claim 1, wherein the at least two resilient members are spaced radially apart.

3. The drive lever of claim 1, wherein the at least two resilient members are integrally formed and are separated by a slot.

4. The drive lever of claim 3, wherein the slot is a key-hole slot.

5. The drive lever of claim 2, wherein the at least two resilient members are separately formed and arranged to form a cantilever.

6. The drive lever of claim 5, wherein the cantilever is formed by a fastener being secured through the at least two resilient members and an intervening portion of the drive lever.

7. The drive lever of claim 6, wherein the fastener is a rivet.

8. The drive lever of claim 1, wherein the first end comprises a case hardened surface.

9. The drive lever of claim 1, wherein the at least two resilient members have a cambered outer surface.

10. A hydraulic spool valve assembly, comprising: the drive lever of claim 1; and a hydraulic spool valve, the hydraulic spool valve comprising a slot, wherein the first end is positioned within the slot and each of the at least two resilient members exerts a radially outward force (F.sub.1, F.sub.2) on one or more inner surfaces of the slot.

11. The hydraulic spool valve assembly of claim 10, wherein a portion of one or more of the inner surfaces of the slot is chamfered.

12. The hydraulic spool valve assembly of claim 10, wherein the drive lever is operatively connected to the hydraulic spool valve such that movement of the drive lever causes the hydraulic spool valve to move axially.

13. The hydraulic spool valve assembly of claim 10, comprising two or more hydraulic spool valves operatively connected to a respective drive lever and each respective drive lever is operatively connected to a common input lever, such that movement of the common input lever causes actuation of each respective drive lever and causes the two or more hydraulic spool valves to move axially.

14. A hydraulic actuator comprising: the hydraulic spool valve assembly of claim 12; a hydraulic cylinder; and a piston, wherein the piston is housed within the hydraulic cylinder, wherein the one or more hydraulic spool valves are in fluid communication with the hydraulic cylinder and piston such that axial movement of the one or more hydraulic spool valves causes fluid to enter and/or exit the hydraulic cylinder causing piston to move axially.

15. A method of connecting a drive lever to a hydraulic spool valve, the method comprising: inserting at least two resilient members of a drive lever into a slot in a hydraulic spool valve, the inserting causing radial compression (R.sub.1, R.sub.2) of the at least two resilient members, such that the at least two resilient members engage and exert a radially outward force (F.sub.1, F.sub.2) on the one or more inner surfaces of the slot.

Description

BRIEF DESCRIPTION OF DRAWINGS

[0023] One or more non-limiting examples will now be described, by way of example only, and with reference to the accompanying figures in which:

[0024] FIG. 1 illustrates a conventional drive lever and the problem of backlash in a hydraulic spool valve;

[0025] FIG. 2a illustrates a first example of a drive lever in accordance this disclosure;

[0026] FIG. 2b illustrates a magnified view of the first end of the drive lever of FIG. 2a;

[0027] FIG. 3a illustrates a second example of a drive lever in accordance with this disclosure;

[0028] FIG. 3b illustrates a magnified view of the first end of the drive lever of FIG. 3a; and

[0029] FIG. 4 schematically shows a duplex hydraulic actuator.

DETAILED DESCRIPTION

[0030] FIG. 1 shows a conventional hydraulic spool valve assembly 30 comprising hydraulic spool valve 20 and drive lever 10 having a longitudinal axis L. The spool valve assembly may form part of a duplex hydraulic actuator as illustrated in FIG. 4. Backlash between a first end 12 of the drive lever 10 and an inner surface 22a of the slot 22 of the hydraulic spool valve 20, in which the first end 12 of drive lever 10 sits, is indicated by reference numeral 26. This backlash 26 arises due to manufacturing tolerances or wear of the components over time. The backlash 26 is simply a gap between the first end 12 and the internal width of the slot 22 in which it sits. The backlash 26 results in the drive lever 10 having an amount of play within the slot 22, i.e. the drive lever 10 can move back and forth a small distance without causing a corresponding movement of the hydraulic spool valve 20. This backlash 26 can lead to hysteresis in performance and undesirable force fight in the case of multiple hydraulic systems (e.g. duplex, triplex etc.). This effect can be minimized by the use of tight tolerances and selective assembly but this is an expensive and time consuming process. Moreover, the backlash that arises due to wear over time can only be corrected by replacing parts so as to achieve a better fit again.

[0031] The hydraulic spool valve 20 has a shaft 21 that extends axially and, in use, is moved axially back and forth so as to alter the fluid connections of the valve of which it is a part. The shaft 21 is an elongate cylinder (typically of generally circular cross-section, although this is not essential) with various chambers formed along its length. The hydraulic spool valve 20 includes a pressure chamber 23 in the middle, located between a first return chamber 24 and a second return chamber 25. Depending on the axial position of the hydraulic spool valve 20, the pressure chamber 23 will connect a high pressure inlet to a selected high pressure outlet. In a typical arrangement, a hydraulic spool valve may be used to direct the high pressure fluid from the inlet to a selected side of a piston within a (downstream) hydraulic cylinder in order to cause movement of the piston within the hydraulic cylinder. At the same time, the axial position of the hydraulic spool valve determines which of the first and second return chambers 24, 25 is connected to a corresponding return line. In a typical arrangement of a hydraulic spool valve, the return line and return chambers 24, 25 allow fluid from the non-pressurised side of the hydraulic cylinder to drain back to a reservoir as the piston moves.

[0032] In accordance with this disclosure, FIGS. 2a and 3a show two examples of hydraulic spool valve assemblies 30 having drive lever 10 connections to a hydraulic spool valve 20 which aim to reduce the backlash 26 between the first end 12 of the drive lever 10 and the slot 22.

[0033] As shown in FIGS. 2a and 2b, first end 12 comprises two resilient members 14a, 14b that oppose each other and are spaced radially apart (i.e. along axis R, which is perpendicular to longitudinal axis L of the drive lever 10). Resilient members 14a, 14b are integrally formed together and are separated by a key-hole slot 16. A key-hole slot 16 is so-called because it features a straight portion and circular portion (as shown), which creates an outline similar to that of a key-hole. Resilient members 14a, 14b are so-called because they are resistant to compression in a radially inward direction (R.sub.1, R.sub.2)(i.e. along axis R).

[0034] When disconnected from the hydraulic spool valve 20 (i.e. when not inserted into slot 22), the distance between the opposed outer surfaces of resilient members 14a, 14b (i.e. the outer diameter of the first end 12) is set to be slightly larger than the width of slot 22. In this manner, the resilient members 14a, 14b are compressed radially inward when engaged with inner surfaces 22a of the slot 22. Due to the aforementioned resilience, the resilient members 14a, 14b will thus each apply a radially outward force (F.sub.1, F.sub.2) against the inner surfaces 22a of the slot 22 in response to the compression (i.e. along axis R, in opposite directions R.sub.1 and R.sub.2). This radially outward force accounts for any backlash that could be present between the slot 22 and drive lever 10 due to manufacturing tolerances or subsequent wear of the resilient member 14a, 14b and/or the inner surfaces 22a of the slot 22 during use. The radially outward force is also great enough such that contact between each resilient member 14a, 14b and the inner surfaces 22a of the slot 22 is maintained during movement of drive lever 10.

[0035] Resilient members 14a, 14b feature a cambered (i.e. curved or rounded) outer surface and the inner surfaces 22a of slot 22 feature a chamfered portion 22b, which co-operate to aid insertion of the drive lever 10 into slot 22. When inserted into the slot 22, the cambered surface of the resilient members 14a, 14b will cam against the chamfered portion 22b and be pushed together in the radial direction (i.e. compressed together). This prevents the need for a separate squeezing operation (i.e. pushing the resilient members together) to insert the resilient member 14a, 14b into slot 22.

[0036] FIGS. 3a and 3b show resilient members 114a, 114b, which have the same attributes and operate in the same manner as resilient members 14a, 14b. However, unlike resilient members 14a, 14b, resilient members 114a, 114b are not integrally formed, but rather are two separate members that are fastened to an intervening portion (10a) of the drive lever 10 using a rivet 116. In this manner, resilient members 114a, 114b form cantilevers, which resist compression in a radially inward direction (R.sub.1 and R.sub.2).

[0037] Such an arrangement of resilient members may be less stiff than those of FIGS. 2a and 2b, meaning resilient members 114a, 114b can be pushed together (i.e. compressed radially inwardly) with less force than resilient members 14a, 14b. This may facilitate insertion of drive lever 10 into slot 22, but may also decrease transmission stiffness. To this end, it will be noted that FIGS. 3a and 3b do not show a chamfered portion 22b of slot 22, as the reduced compression force means it may not be necessary to aid insertion as with FIGS. 2a and 2b. However, it is to be understood that the examples of FIGS. 3a and 3b can include a chamfered portion 22b within the scope of this disclosure.

[0038] Referring to both the examples of FIGS. 2a and 3a, in order to facilitate wear resistance and improve durability of the connection between the drive lever 10 and hydraulic spool valve 20, the outer surface of the first end 12 (and resilient members 14a, 14b, 114a, 114b) may be case hardened by any suitable method known in the art. Alternatively or in addition, a friction reducing coating can also be applied to the outer surface of the first end 12 (and resilient members 14a, 14b, 114a, 114b).

[0039] FIG. 4 schematically shows a duplex hydraulic actuator system with a first hydraulic system 41 and a second hydraulic system 45. First hydraulic system 41 has a first hydraulic spool valve 42 which is actuated via first drive lever 43 by common input lever 44. Second hydraulic system 45 has a second hydraulic spool valve 46 which is actuated via second drive lever 47 by common input lever 44.

[0040] The first and second drive levers 43, 45 may be as described above and/or as shown in FIG. 2a or 3a.

[0041] Hydraulic cylinder 50 houses piston 49. Four fluid chambers are formed between the piston 49 and the cylinder 50, namely first fluid chamber 51, second fluid chamber 52, third fluid chamber 53 and fourth fluid chamber 54.

[0042] When (the upper end of) common input lever 44 is moved to the right (in the figure), the two hydraulic spool valve 42, 46 are moved to the right. First hydraulic spool valve 42 thus connects pressure line 61 to line 58, causing hydraulic fluid to flow into fourth chamber 54. At the same time, line 57 is connected to return line 62 allowing hydraulic fluid to flow out of third chamber 53. Simultaneously, second hydraulic spool valve 46 connects pressure line 59 to line 56, causing hydraulic fluid to flow into second chamber 52. At the same time, line 55 is connected to return line 60 allowing hydraulic fluid to flow out of first chamber 51. Piston 49 is therefore caused to move to the left.

[0043] When (the upper end of) common input lever 44 is moved to the left (in the figure), the two hydraulic spool valves 42, 46 are moved to the left. First hydraulic spool valve 42 thus connects pressure line 61 to line 57, causing hydraulic fluid to flow into third chamber 53. At the same time, line 58 is connected to return line 62 allowing hydraulic fluid to flow out of fourth chamber 54. Simultaneously, second hydraulic spool valve 46 connects pressure line 59 to line 55, causing hydraulic fluid to flow into first chamber 51. At the same time, line 56 is connected to return line 60 allowing hydraulic fluid to flow out of second chamber 51. Piston 49 is therefore caused to move to the right.

[0044] It can be appreciated from FIG. 4 that any backlash in either of the valves will cause one hydraulic spool valves 42, 46 to connect its pressure line to the cylinder before the other valve has moved. This can cause a buildup of pressure in one of the four fluid chambers 51-54 while the piston 49 is unable to move within cylinder 50. This pressure build up may for example cause damage to the seals or to the fluid transfer lines. By contrast, when the backlash accounting designs of FIGS. 2a and 3a are employed for both the hydraulic spool valves 42, 46, there will be no backlash and the two valves will operate in synchrony with no force fight. Furthermore, the simple mechanical nature of the present disclosure does not require the additional hydraulic circuitry of the system disclosed in EP 3 128 216.