EP1706649A1

EP1706649A1 - Hydraulic controller arrangement

Info

Publication number: EP1706649A1
Application number: EP04802911A
Authority: EP
Inventors: Armin Stellwagen
Original assignee: Bosch Rexroth AG
Current assignee: Bosch Rexroth AG
Priority date: 2003-12-09
Filing date: 2004-12-08
Publication date: 2006-10-04
Anticipated expiration: 2024-12-08
Also published as: US7603940B2; WO2005057021A1; US20080282692A1; JP2007514106A; DE10357471A1; ATE384879T1; EP1706649B1; DE502004006088D1

Abstract

What is disclosed is a hydraulic controller arrangement for the pressure medium supply of a hydraulic consumer, e.g., of the rotating gear of a mobile work machine. At low pressure medium flow rates, the pressure medium flow rate draining from the consumer is backed up by means of a drain backup valve having the form of a pressure limiting valve and throttled accordingly, so that a back pressure is generated which is capable of preventing an advance of the mass actuated by the hydraulic consumer.

Description

description

Hydraulic control arrangement

The invention relates to a hydraulic control arrangement according to the preamble of the claim

1. Hydraulic control arrangements of this type, in which a pump is set as a function of the highest load pressure of the hydraulic consumers actuated in each case so that the pump pressure is above the highest load pressure by a predetermined pressure difference, are also referred to as LS systems. The basic principle of such LS controls is described, for example, in DE 199 04 616 AI by the applicant, so that explanations in this regard are unnecessary. Particularly in applications in which large masses are to be moved in a horizontal plane via the hydraulic consumers, such as, for example, in a slewing gear drive of a mobile working device, high pressures occur during acceleration due to the inertia, which, however, occurs when the mass is in motion, ie, if the slewing gear has reached its desired speed, quickly decrease. It can lead to the mass advancing for a short time if, for example, the friction of the mass on the surface on which it is moved is very low. This advance in mass is accompanied by an unwanted change in speed. In hydraulic drives with a regulated flow rate (LS control), this leads to a pressure drop in the flow line and braking of the mass, so that it has to be accelerated again in order to achieve the desired To reach speed. As a result, the movement of the mass is subject to vibrations due to the repeatedly occurring acceleration pressure. It is known that by throttling the pressure medium volume flow on the return side, a counter pressure can be generated, which prevents the mass from advancing and thus ensures the desired stability of the control. This throttling is usually realized in that an outlet control groove adapted to the inlet control groove generates a dynamic pressure which can be of different levels depending on the pressure medium volume flow. The problem is that with a very low pressure medium volume flow, it is difficult to match the outlet cross section to the inlet cross section because of the very small opening cross sections, so that the above-mentioned vibrations can occur at low speeds.

In contrast, the invention has for its object to provide a hydraulic control arrangement with which a vibration-free control of consumers is possible even with low pressure medium volume flows.

This object is achieved by a hydraulic control arrangement with the features of claim 1.

According to the invention is in the process of a hydraulic

Consumers arranged a drain backflow valve, via which an outlet branch line leading to the tank can be opened before or when opening the outlet cross-section. I.e. , in a first stroke range of a spool Directional control valve of the hydraulic control arrangement, the returning pressure medium is not guided over a drain control groove of the control slide but over the cross-section controlled by the drain backflow valve, which takes over the throttling of the return flow quantity. The drain backflow valve can be very easily adapted to the low pressure medium volume flows, so that the consumer can be controlled at low speeds without vibrations.

In a particularly preferred variant, a blocking device or the like is provided downstream or upstream of the drain backflow valve, via which the drain branch line can be shut off during a predetermined stroke of the control slide of the directional valve. This ensures that, for example, in the closed position of the control slide or during an initial stroke, the drain backflow valve can open the drain cross-section, so that the consumer is actuated solely via the cross-sections opened or closed by the control slide.

In a particularly compact embodiment, this locking device for shutting off the branch branch line is integrated in the directional control valve and is formed by a control edge of the control slide of this directional control valve.

The structure of the control arrangement can be further simplified, even if the dam valve and the

Drain branch line in the directional control valve, preferably integrated in its control spool.

In a particularly simple embodiment, the drain backflow valve is a formed by a spring against a valve seat biased closing body, for example a ball.

In the known solutions, the load pressure is tapped at the associated consumer via a load reporting channel which passes through an end section of the control slide. In such constructions, it is advantageous if this load reporting channel and part of the branch pipe running in the control slide are arranged in the control slide parallel and laterally offset to the valve axis.

An alternative to this solution can be found in the

Control spool also a sleeve can be used, in the axis of which the branch pipe runs during the

Load detection channel is formed by one or more longitudinal grooves provided on the outer circumference of the sleeve.

With double-acting consumers, a drain backflow valve can be assigned to each working connection of the directional valve.

Other advantageous developments of the invention are the subject of further dependent claims.

Preferred exemplary embodiments of the invention are explained in more detail below with the aid of schematic drawings. FIG. 1 shows a longitudinal section through a first

Embodiment of a proportionally adjustable directional valve with drain valve for a LS control arrangement; FIG. 2 shows a longitudinal section corresponding to FIG. 1 with a control slide of the directional control valve rotated by 90 ° compared to FIG. 1; 3 shows a circuit symbol of the directional control valve from FIG. 1 and FIG. 4 shows a partial view of a directional control valve of a further exemplary embodiment of a hydraulic control arrangement.

FIG. 1 shows a longitudinal section through a continuously adjustable directional valve 1 of an LS control arrangement. Via this directional valve 1, on the one hand, a metering orifice is formed, via which the pressure medium volume flow to the consumer is set. Furthermore, this directional control valve determines the direction of the pressure medium flow to and from the consumer and thus its direction of movement. The metering orifice is an individual pressure compensator upstream or downstream, whereby one speaks of an LUDV system in the case of downstream pressure compensators and a conventional LS system in the case of upstream pressure compensators, which does not allow flow pressure-independent flow distribution (LUDV). The LUDV control represents a special case of an LS control. As explained in more detail below, according to the invention, the pressure medium draining from the consumer is throttled via a drain backflow valve 57, 86 in order to prevent pressure fluctuations in the case of low pressure medium volume flows.

The directional control valve 1 shown in FIG. 1 is accommodated in a valve disk 2 of a valve block of a mobile working device, for example an excavator. The valve disc 2 has a valve bore 4, in which a control slide 6 is biased into a neutral position via valve springs (not shown) which engage on the end face. A pressure port P, two working ports A, B, a tank port T and an LS port LS are formed on the valve disk 2. The valve bore 4 is radial to annular spaces (from the left to the right in FIG. 1) 8, 10, 12, 14, 16, 18, 20 and 22 expanded, the annular spaces 8, 10, 12 control oil spaces, the two annular spaces 14, 20 tank spaces, the annular space 18 a pressure space and the space 16 a consumer room and the

Room 20 should also be a consumer room that the

LS connection (control oil rooms 8, 10, 12) the tank connection

(Tank rooms 14, 22), the work connections A, B (drainage space 16, flow space 20) and the pressure connection P (pressure space 18) are assigned.

The control slide 6 has axially spaced

Control grooves, through the two control collars 24, 26 formed in the central region, two ends

Guide collars 28, 30 and a tank collar 32 are formed.

Control edges 34, 36 are formed on the mutually facing ring end faces of the control collars 24, 26, which are each designed with fine control notches 38. The connection from P to A or from P to B can be controlled via these control edges 34, 36 during the axial displacement of the control slide 6. In the shown neutral position of the control spool, this connection is blocked.

Tank control edges 40, 42, which are also provided with fine control notches 44 (see FIG. 2), are provided on the outer ring end faces of the control collars 24, 26. In the neutral division shown, the connection is from T to A or from

T to B blocked by the tank control edges 40, 42.

The tank collar 32 has an LS control edge 46, via which the connection from the tank chamber 14 to the control oil chamber 12 can be opened and closed. In the neutral position shown, this connection is open. In the right-hand end section of the control slide 6 in FIG. 1, an axial bore 48 is made on the end face and is blocked off by a screw plug 50. This axial bore 48 is stepped back to a valve seat 52 against which a ball 54 is biased by a spring 56. This allows the connection between a transverse bore 58 and a transverse bore 60 to be shut off, into which the axial bore 48 opens. The transverse bore 60 in turn opens into control grooves 62 formed on the outer circumference of the control collar 24. In the neutral position shown, these cut off the connection between the tank space 22 and the flow space 20, whereby they are open to the tank space 22, so that the ball 54 is filled with tank pressure on all sides is loaded and biased against its valve seat 52.

The ball 54 biased against the valve seat 52 forms a drain backflow valve 57, via which - as will be explained in more detail below - after a small

Displacement of the control slide 6, an outlet cross section to the tank T can be opened. In the control gangs 24, 26 these are in

LS radial bores 66, 68 penetrating in the radial direction, which open into an axially extending LS channel 70, which is designed as a blind hole and in

The area of the LS radial bores 68 ends. The LS channel 70 is widened to the left towards a receiving bore into which a sleeve 72 is inserted.

The sleeve 72 is provided on its circumferential region lying at the top and bottom in FIG. 2 in each case with a longitudinal groove 74 which extends up to an annular groove 75 to which an LS bore 76 of the control slide 6 is open is. On the right end face of the sleeve 72 in FIG. 1, a recess 73 and end recesses 77 are formed, by means of which the longitudinal grooves 74 are connected to the LS channel 70, so that when the control slide 6 is shifted from the neutral position shown, that in the consumer space 16 and / or load pressure present in the consumer chamber 20 can be reported via the LS radial bores 66 and 68, the LS channel 70, the longitudinal grooves 74 and the LS bore 76 into the control oil chamber 10, which is connected to the LS connection.

The sleeve 72 is closed on the end face by a screw plug 79 and fixed in the axial direction in the bore 78.

In the sleeve 72 - similar to the right end section of the control slide 6 - an axially extending bore 78 is provided, which is stepped back towards the right to a valve seat 80 against which a ball 82 is prestressed by means of a spring 84. The ball 82 preloaded against the valve seat 80 forms a second drain backflow valve 86. The locking screw 79 supports the spring 84 with an extension projecting into the bore 78.

The part of the bore 78 which receives the spring 84 is connected to the tank chamber 14 via a transverse channel 88 which passes through the control slide 6 and the sleeve 72. The radially recessed part of the bore 78 arranged beyond the valve seat 80 is connected to the tank space 14 (neutral position) or the consumer space 16 via a transverse bore 90, radial bores 91 in the control slide and control grooves 92 arranged on the outer circumference of the control slide 6. The control grooves 92 can open the connection from the pre-pressure space 16 to the drain valve 86. FIG. 3 shows the hydraulic switching symbol of the directional valve 1 explained with reference to FIG. 1. In its spring-loaded basic position, the working connections A, B are blocked off from the pressure connection P and the tank connection T. When the control spool 6 is shifted to the left from the neutral position shown, the connection of the pressure port P to the working port A can be opened - the pressure chamber of the consumer connected to port A is supplied with pressure medium. The pressure medium draining from the consumer is first returned to the tank connection T with a slight axial displacement of the control slide 6 via the working connection B and the drain backflow valve 57 opened against the force of the spring 56, so that the pressure medium quantity flowing back from the consumer is throttled via this drain backflow valve 57, so that the mass moved by the consumer is prevented from advancing and vibration-free activation of the consumer is guaranteed.

With a further axial displacement of the control slide 6 to the left, the return flow is throttled via a drain control edge of the directional control valve 1 - with an axial displacement to the left, this drain control edge is formed by the tank control edge 40, via which the connection from B to T is opened. Accordingly, when the control slide 6 is shifted to the right, the drain backflow valve 86 throttles the pressure medium flow; after a further axial shift of the control slide to the right in FIGS. 1 and 2, the return flow is throttled via the tank control edge 42 of the control collar 26, via which the connection from port A to port T is controlled.

For better understanding, these pressure medium flows are explained again with reference to FIGS. 1 and 2.

In the neutral position, the working connections A, B are blocked off from the pressure connection P and the tank connection T. The drain backflow valves 57, 86 are acted upon by the tank pressure in the opening direction and are pressed against the valve seat 52, 80 by the force of the spring. When the control slide 6 is shifted to the right, the connection from P to B is initially opened via the fine control notches 38 (metering orifice), so that the consumer is supplied with pressure medium via the working connection B. After an initial stroke of the control slide 6, the control groove 92 is opened towards the consumer space 16 and closed towards the tank space 14, so that the drain backflow valve 86 is acted upon in the opening direction by the pressure in the pressure medium return, ie in the consumer space 16. The drain backflow valve 86 opens when the pressure in the consumer space 16 has reached the pressure equivalent of the spring 84 (for example 15 bar) - the pressure medium flow flowing from the consumer is correspondingly backed up and the quantity of pressure medium flowing is throttled. When the drain backflow valve 86 is open, the pressure medium flows from the consumer space 16 into the tank space 14 and from there to the tank connection T via the flow cross section which is opened by the control groove 92 and the open drain control valve 86. As mentioned above, the control groove 92 controls the connection to the drain backflow valve 86 only after one certain stroke, so that in the neutral position of the directional valve 1 an automatic movement of the consumer is prevented. This could happen, for example, when an excavator is parked on a slope and the slewing gear tries to turn downwards, downhill due to its own weight.

With a further displacement of the valve slide 2, the metering orifice is opened further and the pressure medium volume flow and thus the speed of the consumer are increased accordingly. After the connection to the drain valve 86 has been opened further, the connection from the consumer space 16 into the tank space 14 is opened via the fine control notches 44 of the tank control edge 42, so that the drainage cross section opened by the tank control edge 42 now takes on the throttling of the amount of pressure medium flowing off. The drain backflow valve 86 remains open. The load pressure at the consumer is

Radial bore, the LS channel, the front recess 77, the recess 73, the longitudinal grooves 74, the ring groove 75 and the LS bore 76 reported in the Steuerδlraum 10. When the control slide 1 is moved back, the drain cross-section is initially controlled by the control edge 42, whereupon the drain throttling takes place in the manner described above by the drain pressure valve 86 being backed up by the drain pressure medium. After a further partial stroke, the control groove 92 controls its

Connection to the consumer space 16, the control groove 92 opening towards the tank space 14 and corresponding tank pressure being present at the drain backflow valve 86, so that it is moved back into its closed position. In the event of an axial displacement of the control slide 6 from the neutral position in FIG. 1 to the left, the connection from the pressure chamber 18 to the outlet chamber 16 is opened, ie the metering orifice is then determined by the inlet cross-section opened by the control edge 34. The pressure medium discharge from the consumer is determined after a small initial stroke, in the manner described above, first by the action of the drain backflow valve 57 and after the further partial stroke by the discharge cross-section controlled via the control edge 40 and the associated fine control notches 44.

In the variant described above, the drain backflow valve 86 is integrated in the sleeve 72 inserted into the control slide 6 and the LS channel 70 is aligned with it.

FIG. 4 shows a variant in which the LS channel 70 is formed by a bore which is offset parallel to the control slide axis and which is closed at the end by a screw plug 96. At a parallel distance from it, the bore 78 with the valve seat 80 for the ball 82 of the drain backflow valve 86 is arranged in the end section of the control slide 6. The bore 78 is also closed at the end by a screw plug 98. The bore 80 is then connected to the circumferential control groove 62 via an angular channel 100. Otherwise, the control slide 6 from FIG. 4 essentially corresponds to that from FIGS. 1 and 2.

The exemplary embodiment shown in FIG. 4 has a somewhat simpler construction in terms of device technology, but is somewhat more complex to manufacture, since the introduction of the offset bores and the

Angle channel 100 is more difficult to implement than at the solution in which the channel guide is essentially integrated into the sleeve 72.

Disclosed is a hydraulic control arrangement for supplying pressure medium to a hydraulic consumer, for example the rotating mechanism of a mobile machine. In the case of low pressure medium volume flows, the pressure medium volume flowing out of the consumer is accumulated and throttled accordingly by means of a drain backflow valve designed as a pressure limiting valve, so that a back pressure is generated which can prevent the mass actuated by the hydraulic consumer from advancing.

LIST OF REFERENCE NUMBERS

Directional control valve Valve disc Valve bore Control spool Control oil chamber Control oil chamber Control oil chamber Tank chamber Consumer chamber Pressure chamber Consumer chamber Tank chamber Control collar Control collar Guide collar Guide collar Tank collar Control edge Control edge Fine control edge Tank control edge Tank control edge Fine control notch LS control edge Axial bore Locking screw Valve seat Ball Spring Drain valve Radial star spigot Drill hole Drosseisteuerkante

LS-radial bore

LS-channel

shell

recess

longitudinal groove

ring groove

LS-bore

front recess

drilling

Screw

valve seat

Bullet

feather

Drain backup valve

Querkanal

bore star

control groove

Screw

angle channel

Claims

claims

1.Hydraulic control arrangement for supplying pressure medium to a hydraulic consumer, via which a load with a large mass can be moved, with a pump which can be controlled as a function of the load pressure on the consumer and via the pressure medium via a proportionally adjustable directional valve (1) to and from the consumer Via a discharge cross-section opened by a discharge control edge (40, 42) of the directional control valve (2), a drainage channel (T) can be guided, characterized in that a drainage backflow valve (57, 86) is arranged in the pressure medium flow path between the consumer and the tank channel (T) , via which an outlet branch line (62, 60, 52, 58; 92, 90, 80, 88) leading to the tank channel can be opened essentially before the outlet cross section is opened.

2. Hydraulic control arrangement according to claim 1, wherein in the drain branch line (62, 60, 52, 58; 92, 90, 80, 88) upstream or downstream of the drain backflow valve (57, 84) a blocking device (94) for shutting off the

Drain branch line (62, 60, 52, 58; 92, 90, 80, 88) is provided during a predetermined stroke of a control slide (6) of the directional valve (1).

3. Control arrangement according to claim 2, wherein the locking device is formed by a control edge (64, 94) of the control slide (6).

4. Control arrangement according to one of the preceding claims, wherein the drain backflow valve (57, 86) and the drain branch line (62, 60, 52, 58; 92, 90, 80, 88) are integrated in a control slide (6) of the directional valve (1).

5. Control arrangement according to claim 3 and 4, wherein the control edge (64, 94) by a control groove (62,

92) is formed, in which a radial bore (60, 90)

Drain branch line (62, 60, 52, 58; 92, 90, 80, 88) opens.

6. Control arrangement according to one of the claims 2 to 5, wherein the drain valve (57, 86) is a pressure relief valve with a valve body (54, 82) biased against a valve seat (52, 80).

7. Control arrangement according to one of the claims 4 to 6, wherein the drain backflow valve (57, 86) is arranged in a sleeve (72) inserted into the control slide (6), on the outer circumference of which a section through a longitudinal groove of the load signaling channel (74) extends.

8. Control arrangement according to one of the claims 4 to 6, wherein the drain backflow valve (57, 86) in a section (78) of the drain branch line (62, 60, 52, 58; 92, 90, 80) running parallel to a load reporting channel (70), 88) is arranged, the section (78) of the outlet branch line (62, 60, 52, 58; 92, 90, 80, 88) and / or the load signaling channel (70) running at a parallel distance from the control slide axis.

9. Control arrangement according to one of the preceding claims, wherein the directional control valve (1) has two working connections A, B and each working connection is assigned a drain valve (57, 86).