EP1046003B1

EP1046003B1 - Control valve for a hydraulic motor

Info

Publication number: EP1046003B1
Application number: EP99900440A
Authority: EP
Inventors: Carl Christian Dixen
Original assignee: Sauer Danfoss Holding ApS
Current assignee: Danfoss Power Solutions Holding ApS
Priority date: 1998-01-12
Filing date: 1999-01-08
Publication date: 2004-04-21
Anticipated expiration: 2019-01-08
Also published as: AU1960399A; DE69916573T2; WO1999035424A1; DE69916573D1; DE19800720A1; EP1046003A1; DE19800720C2

Description

The invention concerns a control valve for a hydraulic motor according to the preamble of claim 1.

Such a control valve is known from DE 44 13 216 C2.

Another control valve is known from DE 38 02 672 C2. The housing bore has a central annular pump groove connected with a pump connection, having on either side an annular motor groove connected with a motor connection and on the outside of this an annular tank groove connected with a tank connection. The slide has two annular distributor grooves, each arranged in the area of an annular motor groove, from which distributor grooves originate inflow pockets extending in the direction of the annular pump grooves for forming the inflow throttles and return pockets extending in the direction of the annular tank grooves for forming the return throttles. As the inflow throttles and return throttles belonging together close and open synchronously, a deadband occurs - based on the neutral position, in which the inflow pressure increases from a standby value to the required working pressure, and immediately after the deadband a control area occurs, in which both inflow throttle and return throttle are active. This is particularly important, when the motor, at least in one working direction, is loadable by an external force, for example by a crane boom, a lifting platform, a stacker truck etc., in connection with which the return throttle must prevent a too fast lowering.

However, the known control valve cannot be used, when in the return path a pressure-relief valve is provided, which opens on occurrence of the overpressure and must drain off pressure fluid for as long as it takes to relieve the overpressure. The reason is that in the neutral position of the control valve the return throttle is closed, so that the overpressure fluid cannot flow off. Exactly with the motors being of interest here, which can be loaded by an external force, however, pressure-relief valves are required. When, however, the return throttle is not completely closed, meaning that in the neutral position an opening remains, this leads to a reduction of the working area.

The task of the invention is to provide a control valve of the kind mentioned in the introduction, which permits a good control and the use of a pressure-relief valve at the same time.

According to the invention, this task is solved by the features of the characterizing clause of claim 1.

In this embodiment the return throttle has a characteristic, in which a displacement of the control valve from the neutral position initially causes a closing and subsequently an opening movement. Thus, in the neutral position, pressure fluid drained off by the pressure-relief valve can be lead off to the tank. In spite of this, the return throttle is fully active over the whole control area following the deadband. Since the slide has additional pockets with a limited axial length, which in the neutral position bypass the present connection between annular motor groove and annular tank groove, the normal return pocket is thus supplemented by an additional pocket. The desired characteristic thus occurs from the combined effect of both pockets.

It is expedient that the return throttle reaches the closed position at a distance from the end of the deadband. Across this distance the return throttle is therefore closed, so that the pressure increase on passing through the deadband is disturbed as little as possible.

It is also favourable that on moving out of the neutral position the return throttle first closes and then opens again, before the inflow throttle starts opening. As it is difficult to reach the tolerances of a simultaneous opening of return throttle and inflow throttle, the order mentioned is recommended, as the pressure increase does not stop until the inflow throttle is open. In many cases, however, it is also favourable to let the inflow throttle open before the return throttle.

Additionally it is advantageous that the additional pocket axially overlaps both a return pocket and a load pressure sensing opening and is displaced in relation to both in the circumferential direction. As both pockets and the load pressure sensing opening only need small dimensions, they can be arranged on the slide surface without difficulty.

In the following the invention is described on the basis of preferred embodiments on the basis of the drawings, showing:

Fig. 1: the opening characteristic of a return throttle and an inflow throttle with a control valve according to the invention
Fig. 2: a section through a constructive embodiment of such a control valve.

Fig. 1 shows the opening cross section F in mm² across the adjustment distance s in mm of the slide of a control valve. The first quadrant Q1 refers to a return throttle, the second quadrant Q2 refers to an inflow throttle. The latter is closed over a deadband c and then opens as shown by the curve Z. The curve for the return throttle, however, comprises two sections R1 and R2. The section R1 shows that the return throttle opens almost simultaneously with the inflow throttle, or rather, at a distance b from the neutral position, that is, temporally shortly before the inflow throttle. According to the section R2 the return throttle is open in the neutral position and closes after passing through a section a of the deadband, so that an adjustment distance section b-a remains, in which the return throttle is completely closed.

In the neutral position pressure fluid drained off by a pressure relief valve can therefore be lead off to the tank. The normal operation, which starts at the end of the deadband c, remains unchanged, as the return throttle is completely closed at the end of the deadband.

Fig. 2 shows a valve housing 1 with a housing bore 2, in which a slide 3 is axially adjustable. A displacement from the neutral position, for example to the right, as suggested by the arrow s, leads to the diagram in Fig. 1. The control valve made this way is connected in series with a compensation valve 4, which maintains a constant pressure drop at the inflow throttle of the control valve. In stead of this flow control, the control valve can also be part of a pressure control or have another desired function.

The housing bore 2 has a central annular pump groove 5 connected with a pump connection P. On both sides are annular motor grooves 6 and 7 connected with motor connections A and B, respectively. Further outwards are arranged annular tank grooves 8 and 9 connected with a tank connection T. The slide 3 is provided with two annular distributor grooves 10 and 11, which are arranged in the area of the annular motor grooves 6 and 7. From these

originate inflow pockets

12 and 13 directed towards each other, which form

inflow throttles

14 and 15 together with the annular pump groove 5. In the direction of the annular tank

groove return pockets

16 and 17 are extending, which form

return throttles

18 and 19 together with the annular tank grooves 8 and 9.

Additional pockets

20 and 21 also belong to the return throttles, which pockets in the neutral position each bypass a

connection

22 and 23 between the annular motor groove 6 and the annular tank groove 8 or the annular motor groove 7 and the annular tank groove 9, respectively. The

additional pockets

20 and 21 can be provided once or multiple times. Most often, they are distributed evenly on the circumference.

Fig. 2 also shows the dead zone c, which the slide 3 must pass when leaving the neutral position, before the

inflow pocket

12 or 13 reaches the annular pump groove 5. The distance b is the distance to be passed by the slide 3 when leaving the neutral position, before the

return pocket

16 or 17 reaches the annular tank groove 8 or 9. The

additional pockets

20, 21 can pass a distance a before getting inactive. For example, the values a, b and c can be as follows: a = 1.2 mm, b = 1.4 mm, c = 1.5 mm.

Further, load

pressure sensing openings

24, 25, 26 and 27 are arranged on the slide surface, which, like the

return pockets

16 and 17 and the

additional pockets

20 and 21, only have a limited extension in the circumferential direction, so that the two pockets and one load pressure sensing opening can be arranged in axial overlapping.

The pressure-relief valve arranged in the return side motor path can be an independent spring loaded non-return valve, but can also be an additional function of another valve, for example a load retaining valve.

Claims

Control valve for a hydraulic motor with a slide (3) extending in a housing bore (2), the slide having on both sides of a neutral position working areas, each allocated to a working direction, in which working areas an inflow throttle (14, 15) and approximately at the same time also a return throttle (18, 19) open after passing through a deadband (c), the return throttle (18, 19) being open in the neutral position and closes on passing through the deadband (c), wherein the housing bore (2) has a central annular pump groove (5) connected with the pump connection (P), having on either side an annular motor groove (6, 7), each connected with a motor connection (A, B), and on the outside of this an annular tank groove (8, 9), each connected with a tank connection, the slide (3) has two annular distributor grooves (10, 11), each arranged in the area of an annular motor groove (6, 7), characterised in that from the distributor grooves originate inflow pockets (12, 13) extending in the direction of the annular pump groove (5) to form the inflow throttles (14, 15) and return pockets (16, 17) extending in the direction of the annular tank grooves (8, 9) to form part of the return throttles (18, 19), and that the slide (3) has additional pockets (20, 21) with a limited axial length and belonging to the return throttles (18, 19), which in the neutral position bypass the present connection (22, 23) between annular motor groove (6, 7) and annular tank groove (8, 9) such that the return throttle (18, 19) is open in the neutral position but closes on passing through the deadband.
Control valve according to claim 1, characterised in that the return throttle (18, 19) reaches the end position at a distance from the end of the deadband.
Control valve according to claim 1 or 2, characterised in that on moving out of the neutral position the return throttle (18, 19) first closes and then opens again, before the inflow throttle (14, 15) starts opening.
Control valve according to one of the claims 1 to 3, characterised in that the additional pocket (20,21) axially overlaps both a return pocket (16,17) and a load pressure sensing opening (24,26) and is displaced in relation to both in the circumferential direction.