EP0670946B1 - Hydraulic pressure-supply and control unit for a truck-mounted concrete pump - Google Patents

Abstract

The invention concerns a hydraulic pressure-supply and control unit for a truck-mounted concrete pump (10) comprising a concrete-discharge rig (14), with hydraulic traverse and elevation drives, plus a hydraulic support device (30), both of which are connected in as hydraulic consumers supplied with hydraulic pressure by a joint pressure-supply unit fitted with an operating-mode selector valve (74) by means of which the pressure-supply unit can be connected either to a control valve system in the support device or to one in the discharge rig. Fitted as a hydraulic link element and also as a physical support for the control valves (68 to 72) of the discharge-rig control unit, for the mode-selector valve (74) and for switching elements in the pressure-supply unit (77) is a one-piece connector block (73) having a P-line (119), a T-line (132), a control line (166) and another return line (167, 168) which are designed as bores running in the direction of linkage. Coming off these bores are connection channels which open out in valve connection zones (163, 163', to 163IV) in an array of bores of proportional-control valves. Zones (102') in a load-signalling line (102) which are connected in series to each other by load-comparator valves (114) are each formed by a longitudinal bore (188, 188' to 188IV) starting, plugged, at the free end (164) of the connector block (73) plus cross-channels connecting the longitudinal bores with the output (117) of a load-comparator valve and with the input (116) of the adjacent load-comparator valve on the supply side.

Description

The invention relates to a hydraulic pressure supply and Control unit for a truck-mounted concrete pump that has a multi-arm, overall, a placing boom rotatably arranged on a vehicle with a hydraulic rotary drive and the arms of the mast individually assigned hydraulic elevation drives, on the one hand, and a hydraulic support device, by means of which the vehicle outside the vehicle base area in corner points larger area can be supported against tilting, on the other hand, includes as hydraulic consumers, for their pressure supply a single designed as a load-sensing pump Pressure supply unit is provided, the pressure outlet alternatively to a by means of an operating mode preselection valve hydraulic control unit of the support device or to a hydraulic control unit of the placing boom can be connected, thus - for safety reasons - the support device and the Mast not controlled at the same time - can be "moved", according to the preamble of claim 1.

Such a hydraulic pressure supply and control unit is part of a truck-mounted concrete pump on the relevant Trade fair "BAUMA", April 1992, was presented and is also known from the document Ö + P Oil Hydraulics and Pneumatics, Vol. 36, No. 4, April 1992, Mainz, DE PAGES 242-251 'Development of the drive hydraulics for mobile concrete placing booms' . With the well-known Pressure supply and control unit includes the hydraulic Control unit of the placing boom, the rotary drive and the Elevation drives of the mast individually assigned, electro-hydraulic or electropneumatically piloted, hydraulic actuated control valves as well as pressure-controlled to which in the pressure prevailing respective partial consumers of the mast Load comparison valves, which are all hydraulic Longitudinal chain connected and mechanically closed a control valve block are summarized, the by each a control valve and a comparison valve formed valve groups, which are each assigned to one of the mast drives, spatially are arranged adjacent to each other. Here are the comparison valves via channels, the sections of a load feedback line form, serially connectable. These channels lead from a comparison output of the respective comparison valve to a load comparison connection of the neighboring one Comparison valve, that, from the comparison output of the former Seen from the valve, arranged on the supply unit side is. These comparison valves are of relatively higher Pressure at a load connection to that in the connected sub-consumer effective pressure is present than at their load comparison input into a the load connection with the comparison output connecting and blocking against the load comparison input and due to relatively higher pressure at the load comparison input than at Load connection to the load comparison input with the load comparison output connecting and this against the load connection shut-off function position controlled, whereby is achieved that in each case the highest, prevailing in one of the sub-consumers Pressure on the pressure supply unit reported and there for the needs-based adjustment of the delivery rate of the pump of the pressure supply unit can be sensed. The to the Valve block assembled valves have disc-shaped Housing defined in a base part in a Hole pattern arranged through holes that with one supply connection or one control connection each Valve are communicatively connected. Furthermore have holes through the valve housing through the tie rods are pluggable, by means of which the valves to each other can be fastened with hydraulic connections of the valves communicating holes through supply channels form that in the area of the connection levels at which the housings of adjacent valves abut one another, through which Mouth openings of the holes surrounding O-rings to the outside are tightly closed.

This design is in the direction of being aligned Seen housing bores, without any significant piping effort a hydraulic longitudinal chaining of those combined in the block Valves feasible and also a simple one individual design of the valve block to the special design the truck-mounted concrete pump in terms of the number of movable Arms of the placing boom possible.

A pressure supply and control unit of this type is, however also has a number of disadvantages: the numerous, resulting from the "sandwich" structure of the valve block Sealing points have, due to inevitable signs of aging on the sealing rings inevitably results in that the separation points of the valve block, at least after some time of use, leakage oil can leak to an increased extent, which also is unacceptable in small quantities. It must therefore be relative Frequently sealing rings are replaced, which in practice is an expansion of the valve block from the vehicle requires the relative to be able to release long tie rods. The same applies analogously to the replacement of a defective valve. Such maintenance work are very time consuming and associated with high costs, both in terms of maintenance and repair costs as also because of the high downtime of the truck-mounted concrete pump itself.

The object of the invention is therefore a pressure supply and To improve the control unit of the type mentioned at the outset, that it is less prone to failure and in the case of a Seal or valve damage with much less time and costs can be repaired.

This object is achieved by the characterizing Part of claim 1 mentioned features solved.

Hereafter is as a hydraulic interlinking element, which also as mechanical support for the control valves of the mast control unit, their operating mode selector valve and, if necessary, of Wiring elements of the pressure supply unit is used formed as a one-piece block of steel or aluminum Connection block provided, in which one with all high pressure connections of the control valves connected P-line, one connected to all return connections of the control valves Tank line, at least one control pressure for actuation the control line carrying the valves and at least one further Return line via which the control circuit of the pressure operated Valves to the tank of the pressure supply unit are closed than in the longitudinal direction of the connection block - the chaining direction - Extending, uniaxial bores formed are, from which connecting channels start, the valve-side Mouth openings within connection fields of the valves in the Bore pattern of proportional valves are arranged.

Furthermore, they are in series with one another via the comparison valves connectable sections of the load feedback line one introduced into the connection block from the free end of each and plugged longitudinal bores at this free end as well as each one individually with the load comparison output of one of the Comparison valves and with the load comparison input of the supply side transverse channels connecting adjacent comparison valve educated.

1. Die Anfälligkeit gegen ein Auftreten von Leckagen ist geringer, da die einstückige Ausbildung des Anschlußblocks, dessen Abstopfungen einem nennenswerten Verschleiß nicht unterworfen sind, die Vermeidung einer Vielzahl von Dichtstellen ermöglicht, wodurch die statistische Wahrscheinlichkeit für Beschädigungen solcher Dichtungen erheblich reduziert ist.

2. Ein Ventil oder eine Dichtung zwischen dem Gehäuse eines Ventils und dem Anschlußblock kann ausgewechselt werden, ohne daß der Anschlußblock aus dem Fahrzeug ausgebaut werden muß. Die zur Durchführung von Reparatur oder Wartungsarbeiten erforderlichen Zeiten, die auch Ausfallzeiten der Autobetonpumpe sind, werden, verglichen mit bekannten Druckversorgungs- und Steueraggregaten auf einen kleinen Bruchteil reduziert.

3. Es können Ventile verwendet werden, die einen einfacheren Gehäuse-Aufbau haben und daher entsprechend billiger sind.

4. Da der Anschlußblock, gefertigt für eine Bestückung mit Proportionalventilen, auch für eine Bestückung mit einfacheren "Schwarz-Weiß-Ventilen" geeignet ist, kann eine Entscheidung darüber, mit welcher Art von Ventilen die Steuerung erfolgen soll, zu einem relativ späten Zeitpunkt getroffen werden, zu dem der Anschlußblock schon in das Fahrzeug eingebaut und verrohrt sein kann, was für den Hersteller der Autobetonpumpe den Vorteil einer wesentlich flexibleren Produktions-Planung und -Durchführung hat. Auch die Erstmontage des Druck-versorgungs- und Steueraggregats wird erheblich rationalisiert.

Advantages achieved in terms of functional reliability and ease of maintenance of the pressure supply and control unit according to the invention are at least the following:

1. The susceptibility to the occurrence of leaks is less, since the one-piece design of the connection block, the blockages of which are not subject to any significant wear, makes it possible to avoid a large number of sealing points, as a result of which the statistical probability of damage to such seals is considerably reduced.

2. A valve or seal between a valve body and the manifold can be replaced without having to remove the manifold from the vehicle. The times required to carry out repair or maintenance work, which are also downtimes of the truck-mounted concrete pump, are reduced to a small fraction compared to known pressure supply and control units.

3. Valves can be used which have a simpler housing structure and are therefore correspondingly cheaper.

4. Since the connection block, manufactured for equipping with proportional valves, is also suitable for equipping with simpler "black and white valves", a decision as to which type of valves the control should take place can be made at a relatively late point in time to which the connection block can already be installed and piped in the vehicle, which has the advantage of a much more flexible production planning and implementation for the manufacturer of the truck-mounted concrete pump. The initial assembly of the pressure supply and control unit is also considerably rationalized.

The proposed design of the terminal block according to claim 2 results in a space-saving arrangement of the longitudinal bores and transverse channels, which are also easy to implement in terms of production technology is. The same applies mutatis mutandis to that provided according to claim 3 Arrangement of the connection of the comparison valve of the operating mode selector valve with the load sensing input of the Pressure feedback line connecting pressure supply unit.

To make the most of the use of the connection block mediated assembly advantage, it is favorable if this, as provided in the preferred design, also a connection panel for a pressure compensator or throttle arrangement intended for load sensing and / or a pressure relief valve or others hydraulic circuit elements of the pressure supply unit Has.

The comparison valves assigned to the partial consumers are preferably designed as a non-return valve, which in the Control valves themselves can be integrated.

The comparison input is used to achieve a defined comparison pressure of the "last", comparison valve which over the individual line sections of the load feedback line in series switched comparison valve, which is removed from the pressure supply unit is arranged, connected to its tank.

Due to the interpretation provided according to claims 7 and 8 Pressure supply and control unit with proportional valves and these individual assigned pressure balances is a special one sensitive control of mast movements achievable, whereby in combination with the features of claim 9 Circuitry advantageous design of the control valves with regard to the feedback of consumer pressure on the Pressure compensators is specified. For by the features of the claim 10 specified version of the pressure supply and control unit with a variable displacement pump as the pressure source design of the specified by the features of claim 11 Flow control element and its control particularly useful, by which is achieved in a simple manner that the outlet pressure the pump always by a defined amount is considered the highest in one of the consumers or sub-consumers prevailing operating pressure.

In combination with this is due to the features of claim 12 an advantageously simple line routing for the via the proportional valve outflowing hydraulic medium specified.

If, expediently the pump of the pressure supply unit as a constant pump with pressure compensator as a load-sensing element provided the control valves for the movement control of the Masts are designed as so-called "black and white valves", it is particularly advantageous if, as in claim 15 provided within the connection panels opening control and Connection channels can be sealed by means of the valve housing - are "pluggable" - are.

The design of such "black and white valves" provided according to claim 16 is useful to a sensitive mast setting, however, a relatively gentle approach to the mast when rotating to achieve.

By load-holding circuits provided according to claim 17 ensured that both the support device and the Mast a position reached by control even after lifting the control maintained.

Due to the proposed type of control of the Operating mode preselection valve is against additional security triggered mast movements caused by malfunction-related Switch positions of the mast control valves result could without being controlled.

In combination with the control of the operating mode preselection valve in which for the setting operation of the support device suitable functional position related features of the claim 19, which are easy to implement in terms of circuitry, this only applies to the control of the mast movements, in a preferred one Combination with the features of claim 20, the can be realized with a relatively small additional technical effort are, but also for controlling the setting of the support device.

The electronic circuitry required for this Links are - if the purpose is known - relevant for one pre-trained specialist in electro-hydraulic control and control technology can be easily implemented.

Here it can be in the sense of quick actuation of the respective Mast or support control valves advantageous be, if by a first actuation of such Control valve also operated the preselection switch stage accordingly becomes.

If, as provided according to claim 22, actuation in the same direction two support cylinders that are diagonally opposite each other Corners of the support area are arranged, is excluded, so far as the circuitry is concerned Secured against that achieved by improper operation the support cylinder of the support device tilts of the vehicle provoked by a diagonal of the support surface can be.

Fig. 1a

eine Seitenansicht einer Autopumpe mit hydraulisch bewegbarem Verteilermast und hydraulisch betätigbarer Abstützvorrichtung, beide in ihren Transportkonfigurationen;

Fig. 1b

die Abstützvorrichtung der Autopumpe gemäß Fig. 1a in ihrer das Fahrzeug kippsicher abstützenden - betätigten - Konfiguration;

Fig. 2

ein vereinfachtes Hydraulik-Schaltbild der Antriebs- und Steuereinrichtungen des Verteilermasts und der Abstützvorrichtung der Autopumpe gemäß den Fig. 1a und 1b;

Fig. 3

ein Hydraulikschaltbild zur Erläuterung eines ersten Ausführungsbeispiels eines zur Bewegungssteuerung des Masts vorgesehenen Druckversorgungs- und Steueraggregats mit Konstantpumpe und Proportionalventilen;

Fig. 4

ein weiteres Ausführungsbeispiels eines zur Steuerung der Mast-Bewegungen geeigneten Druckversorgungs- und Steueraggregats mit einer Verstellpumpe als Druckquelle;

Fig. 5a

Bohrungsbilder von Anschlußfeldern eines Anschlußblocks, auf dem die Steuerventile der Druckversorgungs- und Steueraggregate gemäß den Fig. 3 und 4 in hydraulischer Längsverkettung montierbar sind;

Fig. 5b

das Hydraulik-Schaltbild des Anschlußblocks gemäß Fig. 5a;

Fig. 5c

Details der Gestaltung von Abschnitten einer Last-Rückmeldeleitung des Anschlußblocks gemäß den Fig. 5a und 5b und

Fig. 6

ein weiteres Ausführungsbeispiel eines zur Steuerung der Mastbewegungen vorgesehenen Druckversorgungs- und Steueraggregats, bei dem die Steuerventile als "Schwarz-Weiß-Ventile" ausgebildet sind.

The invention is explained in more detail below with reference to exemplary embodiments shown in the drawing with regard to structural and functional details. Show it:

Fig. 1a

a side view of a car pump with hydraulically movable placing boom and hydraulically actuated support device, both in their transport configurations;

Fig. 1b

the supporting device of the car pump according to FIG. 1a in its - actuated - configuration that supports the vehicle against tipping over;

Fig. 2

a simplified hydraulic circuit diagram of the drive and control devices of the placing boom and the support device of the car pump according to FIGS. 1a and 1b;

Fig. 3

a hydraulic circuit diagram for explaining a first embodiment of a pressure supply and control unit provided with a constant pump and proportional valves for motion control of the mast;

Fig. 4

a further embodiment of a pressure supply and control unit suitable for controlling the mast movements with a variable displacement pump as a pressure source;

Fig. 5a

Bore patterns of connection fields of a connection block on which the control valves of the pressure supply and control units according to FIGS. 3 and 4 can be mounted in a hydraulic longitudinal linkage;

Fig. 5b

the hydraulic circuit diagram of the terminal block according to Fig. 5a;

Fig. 5c

Details of the design of sections of a load feedback line of the terminal block according to FIGS. 5a and 5b and

Fig. 6

a further embodiment of a pressure supply and control unit provided for controlling the mast movements, in which the control valves are designed as "black and white valves".

The one shown in FIGS. 1a and 1b, generally designated 10 Truck-mounted concrete pump comprises, on a transport vehicle 11 mounted, a concrete feed pump 12, one around a vertical, Vehicle-fixed axle 13 rotatable, generally designated 14 Distribution boom with a total of four articulated arms 16,17,18,19 by means of hydraulic linear cylinders 21,22,23,24 µm - horizontal - Articulated axes 26,27,28 and 29 are pivotable, and one total designated 30 support device, which four has vertical hydraulic support cylinders 31 to 34 which to the free ends of horizontal arms 36 to 39 arranged are, in turn, by means of horizontally acting swivel cylinders 41 to 44 around vertical axles 51 to 54 fixed to the vehicle from a position parallel to the central chassis side members in e.g. the positions shown in FIG. 1b can be swung out are in which the concrete pump 10 far outside of Footprints of the vehicle wheels by extending the support cylinders 31 to 34 can be supported against tipping. Even those around vertical axis 13 rotatable rotating column 56 of the placing boom 14 is provided with a hydraulic rotary drive 57 which, like the detailed representation of Fig. 2, on the details of which now also referenced, removable, by means of two double-acting "parallel" hydraulic cylinders 58 and 59 realized is, by means of which a rack 61 or 62 in opposite directions is drivable with an externally toothed, with the Rotary column 56 fixed gear ring 64 on opposite one another Sides of the same are in meshing engagement.

The for the elevation movements of the articulated arms 16 to 19 of the Distribution masts 14 are provided linear cylinders, as in the Fig. 2 by way of example only for one of them, e.g. the "bottom" Linear cylinder 21 shown as a double-acting hydraulic cylinder trained, the piston 63 on the bottom side on her total cross-sectional area and on the rod side on one around Cross-sectional area of the piston rod reduced ring area with Drive pressure can be applied.

The correspondingly designed support cylinders 31 to 34 of the support device 30 are arranged so that they are in support operation on the larger area of their pistons 63 with the outlet pressure the operating pressure source. The double acting linear cylinders 58 and 59 of the rotary drive 57 are with that provided for the elevation drives 21 to 24, "symmetrical trained and have both sides out of the cylinder housing emerging piston rods, the ends of which by the side on Housing passing racks are interconnected.

The support cylinders 31 to 34 of the support device 30 and their for extending the horizontal arms that support the support cylinders 36 to 39 provided swivel cylinders 41 to 44, of which in Fig. 2, for the sake of simplicity of illustration only one at a time, e.g. the left front support cylinder 31 and the provided for the boom 26 provided pivot cylinder 41 are, a support control valve 66 and a Swivel control valve 67 operable, which is the basic function of 4/3-way valves provide the two alternative flow positions I and II have the "forward" and "reverse" operation assigned to the respective support or swivel cylinder are, as well as a neutral basic position zero, in which the piston 63 of the respective support or swivel cylinder in remains in its current position.

The for adjusting the elevation of the individual articulated arms 16 to 19 and the distribution mast 14 provided overall linear cylinder 21 to 24, of which in turn the simplicity in FIG. 2 only the one articulated on the rotating column 56 for the sake of it Linear cylinder 21 is shown and the common controllable linear cylinder 58 and 59 comprehensive rotary drive 57 of the placing boom 14 are only schematic for each one control valve indicated by a 4/3-way valve symbol 68 to 71 or 72 controllable, which in turn are two alternative Flow positions I and II have the alternative directions of movement the swivel arms 16 to 19 or rotary movements of the Distribution masts 14 are assigned in total, as well as a neutral Home position zero, in which the piston (s) of each connected elevation control cylinder or the linear cylinder 58 and 59 of the rotary drive 57 in his / her respective Current position (s) remains.

The control valve 72 for the rotary movements of the placing boom 14 about the vertical axis 13 of its rotary column 56 and the elevation control valves 68 to 71 for the elevation swivel drives 21 to 24 of the first articulated arm 16 which is articulated on the rotating column 56 of the second articulated arm, which is on the first articulated arm 16 is articulated, the third articulated arm 18, which on the second Articulated arm is articulated and the fourth articulated arm 19, the is articulated on the third articulated arm 18, in this order, in the sense of a longitudinal chaining of these valves 72.68 to 71, on a common, designated overall 73 Terminal block mounted, on which, seen in the direction of chaining, "before" the control valve 72 for the rotary movements of the placing boom 14 an operating mode preselection valve 74 is mounted, which, according to its basic function, is an 8/3-way valve, one has neutral neutral position 0, in which neither the support device 30 still the placing boom 14 is actuated and two has alternative flow positions I and II, in one of which - The flow position I - only the support device 30 with System pressure is supplied, and in their second functional position II only the hydraulic drives 58 and 59 or 21 to 24 of the placing boom 14 can be acted upon by drive pressure.

By the function of the operating mode selector valve explained so far 74 ensures that the placing boom 14 during the setting of the support device 30 does not move can be, and that these in turn are not operated can if the placing boom is moved.

The placing boom 14 and the support device 30 form in Frame of the entire hydraulic supply and control unit two hydraulic consumers, not together, but can only be operated individually, resulting in a high Operational reliability of the truck-mounted concrete pump 10 is achieved.

This security is with control technology not specifically shown Means further increased that whenever at least one of the control valves 68 to 72 of the placing boom 14 is / are operated simultaneously with this and only for as long this is the case - the mode selector valve 74 in the for the pressure supply of the placing boom drives 57 and 21 to 24 intended function position II is switched.

The operating mode preselection valve is also switched over 74 in its for the pressure supply of the support cylinder 31 to 34 and the pivot cylinder 41 to 44 of the support device 30 only then and for as long as at least one of the Control valves 66 and / or 67 of the support device 30 actuated will be. Otherwise the operating mode selector valve takes its Basic position 0, in which the hydraulic pump 76 of the a total of 77 designated pressure supply unit for circulation operation, or, if the pump 76 is designed as a variable displacement pump is set to the maximum delivery rate, whereby the Hydraulic medium is cooled.

So when the mode selector valve 74 is in its Home position 0, the placing boom 14 does not "collapse" - His arms 16 to 19 in the assumed elevation positions persist and the mast 14 does not turn, are for that, to adjust the elevation of each Articulated arms 16 to 19 provided hydraulic linear cylinders 21 to 24 and for the rotary drive 57 of the placing boom 14 this each individually assigned, designated 78 or 79 in total hydraulic load-holding circuits with those from FIG. 2 apparent hydraulic circuitry details provided, only for the sake of simplicity of illustration one of the holding circuits 78 for the elevation cylinders is shown is the same structure for the other elevation cylinders is realized as well as the load hold circuit 79 for the rotary drive 57.

The load-holding circuits 78 and 79 for the individual mast arm drives 21 to 34 or the rotary drive 57 of the placing boom 14 each comprise two pressure-controlled outlet valves 81 and 82, each individually between the A and B consumer connections 83 and 84 of the respective drive cylinder or the rotary drive 57 and the corresponding as A-connection 86 and B-connection 87 of the the linear drives 21 to 24 or the rotary drive 57 of the placing boom 14 assigned control valves 68 to 72 switched are. These exhaust valves 81 and 82 are with 2/2 valves spring-centered, blocking basic position 0, the by pressurizing their control chambers 85 into a passage position I are switchable. To the exhaust valves 81 and 82, an input check valve 88 or 89 is connected in parallel, due to the relatively higher pressure at the assigned A or B output of the respective control valve than in the connected one Pressure room, e.g. the rod-side pressure chamber 91 and the bottom-side pressure chamber 92 of one of the linear cylinders 21 to 24 is applied in the opening direction and is otherwise blocked. The Control chamber 88 of the upstream of the A consumer connection 83 Exhaust valve 81 is at the B input 87 'of the load hold circuit 78 or 79 connected, which in turn with the B connection 87 of the respective control valve is connected, the same the control chamber 88 of the upstream of the B consumer connection 84 Exhaust valve 82 with the A input 86 'of the load hold circuit 78 and 79, respectively. The load latch circuits 78 and 79 are directly connected to the linear cylinders 21 to 24 or the rotary drive 57 mounted while the related control valves 68 to 72 mounted on the remote terminal block 73 are. With this design of the load hold circuits 78 and 79 is determined by the pressure in that drive pressure space 91 or 92 prevails, displaced into the hydraulic fluid the outlet valve of the other pressure chamber 92 or 91 opened so that hydraulic fluid can flow out of it can.

Functionally corresponding to the load hold circuits 78 and 79 hydraulic locks are also useful for Support cylinder and the pivot cylinder of the support device 30 provided and in Fig. 2 only as unlockable check valves indicated.

Differences between the load hold circuits 78 of the elevation drives 21 to 24 of the distribution mast 14 and the load-holding circuit 79 of its rotary drive 57 exist so far than between the A and B consumer ports 83 and 88 and one leading back to the tank 93 of the pressure supply unit 77 Return line 94 switched pressure relief valves at the rotary actuator is designed for the same maximum pressure value, in the case of the linear cylinders 21 used as elevation drives to 24 however to different values, with the higher value for the bottom-side drive pressure chamber 92 of the linear cylinder 21 to 24 applies when the placing boom 14 is erected each with the high outlet pressure of the pressure supply source 77 is applied. This is also the case with the elevation drive cylinders 21 to 24 a further pressure limiter is provided, that can be supplied to the rod-side drive pressure chamber 91 Pressure limited to a lower value than the maximum value the output pressure of the hydraulic pump 76.

For a more detailed explanation of the hydraulic pump 76, a pressure control device designated overall by 96, the Operating mode selector valve 74 and control valves 68 to 72 for the mast movements comprising a total of 97 Pressure supply and control unit is now first with reference to FIG. 3.

For the pressure supply and control unit shown in FIG. 3 97 is assumed to be the primary pressure source provided hydraulic pump 76 designed as a constant pump which can be operated with a constant delivery rate Q. and within the scope of the pressure control device 96 with comprehensive Pressure supply unit 77 works as a load-sensing pump, such that at the pressure outlet 98 of the pressure supply unit 77 high-pressure supply provided with the by the respective hydraulic consumers - support device 30 or placing boom 14 - conditional load as required varies.

The relevant regulation mediates between the pressure output 98 and the tank 93 of the pressure supply unit 77 switched 3-way pressure compensator 99, which is in the manner of a pressure-controlled 2/2-way proportional valve is formed, the by a preloaded valve spring 101 and the one above each connected consumer dropping pressure that over a load feedback line, designated overall by 102 Pressure compensator 99 acts in the sense of increasing the flow resistance the adjusting throttle formed by the pressure compensator 99 is acted upon and by the pressure outlet 98 of the Pressure supply unit 77 pending pressure on the opposite end face 104 of the piston of the pressure compensator 99 acts in the sense of a reduction in flow resistance the throttle formed by the pressure compensator 99 is.

The via the load feedback line 102 to one end 103 corresponds to the pressure compensator 99 acting pressure if at the same time several of the drives 21 to 24 and / or 57 of the placing boom 14 are actuated, the highest pressure, the above one of these represented by its control valve Partial consumer drops.

The pressure supply unit 77 further includes a pressure relief valve 106, which is the output at the high pressure outlet 98 Print to a maximum value of e.g. 400 bar limited, as well a pressure reducing valve 107, which at a control pressure outlet 108 of the pressure supply unit 77 a - relatively low - as control pressure for the control valves 68 to 72 and for the Operating mode preselection valve 74 provides usable pressure around 25 bar.

That in the sense of the longitudinal chaining of the pressure supply unit 77 immediately downstream operating mode preselection valve 74, the control valve 72 following this in the chain for Rotary drive 57 of the distribution mast 14 and the individual mast arm drives 21 to 24 individually assigned control valves 68 to 71, of which in Fig. 3, the simplicity of illustration for the sake of it, only the "first", the one - sided on the Rotary column 56 of the distribution mast 14 articulated linear cylinder 21 associated control valve 68 is shown, with which the further control valves 69 to 71 are identical, are as proportional valves trained within their basic positions 0 alternative functional states that can be approached assigned different flow positions I and II constant changes in the flow cross-sections of each approved flow paths and in this respect a sensitive control of the individual drives.

In the mediating the pressure supply of the support device 30 Function position I of the operating mode preselection valve 74 the pressure outlet 98 of the pressure supply unit 77 is over a first flow path 109 of the mode selector valve 74 with a high-pressure supply line leading to the support device 30 111 connected and this one in the functional position I also released second flow path 112 with a load connection 113 as an exchange check valve shown comparison valve 114 connected, this is switched to a functional position in which the High-pressure supply line 111 of the support device 30 with to the one end 103 of the piston of the pressure compensator 99 of the pressure supply unit 77 leading feedback line 102 connected, but this against a to a load comparison connection 116 of the comparison valve 114 connected section 102 'of the total load feedback line leading back to the pressure compensator 99 is blocked, one of the comparison output 117 the control valve 72 for the rotary drive 57 of the placing boom 14 assigned, structurally and functionally analog comparison valve 114 goes out.

In the associated with the high pressure supply of the support device 30 Function position I of the operating mode selector valve 34 is further released in this functional position I. Flow path 118 one of the mode select valve 74 outgoing high pressure supply line 119 for the mast arm drives 57 and 21 to 24 provided high pressure supply line 119 with the tank 93 of the pressure supply unit 77 connected so that the placing boom drives are not activated can be.

In the assigned to the setting operation of the placing boom 14 Function position II of the operating mode preselection valve is over a first, released in this functional position II Flow path 121 of the pressure outlet 98 of the pressure supply unit 77 with the high pressure supply line 119 for the mast drives connected, while those for the support device 30 provided high-pressure supply line 111 via a in the Functional position II released second flow path 122 connected to the tank 93 of the pressure supply unit 77 and is therefore kept depressurized, so that in the functional position II of the operating mode preselection valve 74, the support device 30 cannot be operated.

In the - spring-centered - basic position 0 of the operating mode selector valve 74 only one flow path 123 is released, through which the load port 113 of the mode selector valve 74 associated comparison valve 114 with the tank 93 of the pressure supply unit 77 is connected so that this Comparison valve 114 when via the feedback line section 102 'pressure reaches the load comparison port 116, passes into that of its alternative functional positions, in which the load connection 113 is shut off and the Feedback line section 102 ′ with that to the pressure compensator 99 leading load feedback line 102 is connected.

The control valve assigned to the rotary drive 57 of the placing boom 14 72 has a functional position I, the rotation of the Distribution masts are assigned counterclockwise and one Function position II, the rotation of the placing boom 14 in Is assigned clockwise. In the basic position 0 this Control valve 72 is the rotary drive 57 of the placing boom 14 by means of its load-holding circuit 79 in the one taken azimuthal position.

In the functional position I, the supply line 124 is the from the valve-side A-connection 86 to the consumer-side A-inlet 86 'of the rotary drive 57 leads, via a first, in with this functional position I released flow path 126 connected to the pressure outlet 127 of a 2-way pressure compensator 128, the between the control valve 72 and the pressure outlet 98 of the pressure supply unit 77 is switched. The second, from the B connector 87 of the control valve 72 outgoing to the consumer side B input 87 'of the rotary drive 57 leading supply line 129 is via a second one, in the functional position I of the control valve 72 released flow path 131 with the leading back to the tank 93 of the pressure supply unit 77 Return line 132 connected.

In the functional position II of the rotary drive control valve 72, the clockwise rotation of the placing boom 14 is assigned, "reversed" is that of the B connection 87 of the control valve 72 leading to the B inlet 87 'supply line 129 released via a first in this functional position II Flow path 133 with the high pressure outlet 127 of the Pressure compensator 128 connected and the other, from the A port 86 of the Control valve 72 outgoing supply line leading to A input 86 ' 124 via a second flow path 134 with the unpressurized tank 93 of the pressure supply unit 77 connected.

Both in the functional position I and in the functional position II of the rotary drive control valve 72 is still one third flow path 136 and 137 released, via which the pressure prevailing on the consumer side on the one hand at the load connection 113 of the comparison valve 114 assigned to the rotary drive 57 is pending and on the other hand also at the comparison input 138 of the the rotary drive control valve 72 hydraulically connected in series Pressure compensator 128, its reference input 139 with its pressure output 127 is connected. This pressure compensator 128, which in turn designed as a throttle with variable flow resistance by the force of a preloaded valve spring 141 and by the force which is in the same direction as that which comes from resulting load pressure at the comparison input 138 results in Sense of a reduction and by their initial pressure, the is also present at its reference entrance 139, in the sense of an enlargement its flow resistance is applied Effect that in the functional positions I and II of the rotary actuator control valve 72 which, depending on how fast the mast rotation should take place, different flow cross sections of the Flow paths 126 and 131 or 133 and 134 can correspond, the pressure drop across the rotary actuator control valve 72 is constant remains.

In the basic position 0 of the rotary drive control valve 72 its A-connection 86 and its B-connection 87 via a common one Drain line 142 with the return line 132 and thereby with the unpressurized tank 93 of the pressure supply unit 77 connected. Furthermore, one is in this basic position 0 additionally released flow path 143 of the load connection 113 of the comparison valve assigned to the rotary drive control valve 72 114 and the comparison connection 138 of the rotary drive 57 assigned pressure compensator 128 with the return line 132 or connected to the tank 93.

The pressure outlet 127 of this pressure compensator 128 is in the basic position 0 of the rotary drive control valve 72 against this connected partial consumer - the rotary drive 57 - blocked.

The other "partial consumers" of the placing boom 14 - the provided as drives for the mast arms 16 to 19 linear Drive cylinders 21 to 24 - associated elevation control valves 68 to 71 are together with a comparison valve 114 and a pressure compensator 128 in exactly the same way in that Interlinking system of the pressure supply and control unit 97 inserted as explained with reference to the rotary drive control valve 72, what can be referred to in this regard. Differently opposite the rotary drive control valve 72 is in the Elevation control valves 68 to 71 only that in their Home position 0 the starting from the respective control valve Supply lines 124 and 129 also against the tank 93 of the Pressure supply unit 77 are shut off, so that these supply lines 124 and 129 constantly with the hydraulic working medium stay filled.

Through the comparison valves 114, their load comparison connection 116 each with the comparison output 117 of the in the chain following comparison valve is connected, the comparison output 117 of the "first" assigned to the operating mode preselection valve 74 Comparison valve 114 with one end 103 the piston of the pressure compensator 99 of the pressure supply unit 77 is connected and the load comparison connection 116 of the "last" Elevation control valve 71, which is on the connection block 73rd arranged at the same time away from the mode selector valve 74 is connected to the tank 93, it is achieved that the highest value of the Pressure on the pressure compensator 99 is reported with which one the partial consumer of the placing boom 14 is operated, since the comparison valve 114 of the associated by this operating pressure Control valve in its load comparison port 116 functional position blocking against the next comparison valve arrives and the pending at its comparison output 117 Consumer operating pressure between "his" comparison valve and the pressure compensator 99 arranged comparison valves 114 in whose enable the load comparison input 116 and their Load connection 113 against the partial consumer blocking functional position holds. The result of this is that the pressure supply unit 77 - regulated by the pressure compensator 99 - always produces an output high pressure corresponding to the demand.

The operating mode preselection valve 74 and that for drive control provided control valves 68 to 72 of the pressure supply and Control unit 97 according to FIG. 3 can be actuated hydraulically Proportional valves with spring-centered basic position 0 trained, in which the control pressure to the respective deflections their slide with respect to the basic position and thus the flow cross sections of the respectively released flow paths are proportional, by electro-hydraulic or electro-pneumatic, if necessary also in the sense of an emergency operation manually operated pilot valves, not shown is adjustable.

Also in the one in FIG. 4, the details of which are now referred to be shown, another embodiment of a Pressure supply and control unit 97 'of a truck-mounted concrete pump 10 have their operating mode selector valve 74 and the control valves 68 to 72 the training described with reference to FIG. 3 and function and are individually assigned including them Comparison valves 114 and pressure compensators 128 in the same way "longitudinally" chained mounted on a common connection block, on which also the hydraulic wiring elements of the pump 76 'are arranged, namely the pressure relief valve 106, the pressure reducing valve 107 and a 2/2-way valve 154, the "local" is arranged in the same way as the pressure compensator 99 of the pressure supply and control unit 97 according to FIG. 3, in However, the frame of the device 97 'according to FIG. 4 has a different function Fulfills.

In a further difference from the exemplary embodiment according to FIG. 3 is the pump 76 'of the pressure supply unit 77' as a variable displacement pump trained, the output volume flow as required is adjustable. A suitable pump of this type is e.g. a swash plate pump, whose in Fig. 4 by the arrow 146 schematically represented swivel plate by a prestressed Spring 147 as long as there are no further forces on the swivel plate 146 attack, is pushed into a position that is maximum Delivery of the pump 76 'of the pressure supply unit 77 'corresponds.

On the swivel plate 146, the piston rod 148 engages as double-acting linear cylinder trained swivel cylinder 149 on, the bottom-side drive pressure chamber 151 with the on Pressure outlet 98 of the variable displacement pump 76 'present outlet pressure is acted upon and its rod-side drive pressure chamber 155 to the load feedback line 102 of the pressure supply and Control unit 97 'is connected by the comparison output 117 of the operating mode preselection valve 74 Comparison valve 114 goes out.

The 2/2-way valve 154 is parallel to the variable displacement pump 76 ' switched between the pressure outlet 98 and the tank 93 and is locked in its locking by a preloaded valve spring 156 Home position 0 pushed.

At the pressure outlet 98 of the variable pump 76 'is via a throttle 150 connected to a relief flow path 152 which only in the basic position 0 of the operating mode selector valve 74 via a flow path released in this basic position 153 connected to the tank 93 of the pressure supply unit 77 ', in functional positions I and II of the operating mode selector valve is locked, however, so that in these functional positions I and II in the relief flow path can build up high pressure with which the piston of the valve 154th spring loaded and thereby an additional, with the restoring force of the spring 156 in the same direction, that 2/2-way valve exposed to urgent force in its blocking position is. On the end face opposite the spring side 157 of the piston of the 2/2-way valve, this is the outlet pressure the variable displacement pump 76 'and thereby one proportional to it Exposed force that the 2/2-way valve in its Flow position I urges and when the relief flow path 152 relieved of pressure via the operating mode selector valve 74 is, also in this flow position I - against the restoring force the spring 156 - holds.

The valve spring 156 of the 2/2-way valve, which with one of the Pressure compensator 99 corresponding to the exemplary embodiment according to FIG. 3 Structure can be realized is designed so that the valve 154 due to a relatively low control pressure - excess pressure on the end face 157 of its opposite the spring side Piston - from e.g. 10 bar reached its flow position I.

The spring 147 through which the swash plate 146 of the variable displacement pump 76 'in their maximum delivery rate of the variable displacement pump 76' corresponding position is pushed is designed so that it holds the swash plate 146 in this position as long as the Difference in pressures between the drive pressure chamber on the bottom 151 and the rod-side drive pressure chamber 155 of the Swing cylinder 149 is less than a threshold of about 20 bar.

That in terms of its versus the pressure supply and Control unit 97 according to FIG. 3 given structural differences explained pressure supply and control unit 97 'works as follows:

As long as a consumer at the pressure outlet 98 of the pressure supply unit 77 'is not connected, i.e. the operating mode preselection valve is in its home position 0, works the variable displacement pump 76 'in circulation mode, since the 2/2-way valve 154 through the building at its entrance 158 Back pressure that is opposite to the spring side of the valve piston Piston end face 157 acts in its flow position I arrives and thus pressure medium via the 2/2-way valve 154 can flow out to the tank 93. The one above the 2/2-way valve 154 falling pressure has in circulation mode of the pump 76 'the amount equivalent to the restoring force of the valve spring 156 of approx. 10 bar. This pressure, which is also in the bottom side Drive chamber 151 of the swivel cylinder 149 is coupled, is not sufficient, the swivel cylinder 149 against the restoring force the "spring attacking in the opposite direction" 147 to operate and turn the swash plate 146, thus by the spring 147 in the maximum delivery rate of the variable displacement pump 76 'corresponding position is maintained. The hydraulic fluid as long as a consumer mast 14 or Support device 30 - is not operated with the amounts circulated and circulating after a large volume flow can be cooled effectively.

Is activated by activating the operating mode preselection valve 74 When consumers are switched on, the pressure at the pressure outlet rises 98 of the pressure supply unit 77 ', since now the operating mode preselection valve 74 the return flow path 152 against the Tank 93 shuts off, as pressure medium via the 2/2-way valve 154 can no longer drain. By the output pressure of the variable pump 76 ', which in the bottom drive chamber 151 of the Swivel cylinder 149 is coupled, the swivel plate 146 now in the sense of a reduction in the output of the Variable pump 76 'can be pivoted. The related adjusting force counter and in the same direction with the power of the biased Spring 147 acts on the force caused by pressurization of the rod-side drive pressure chamber 155 of the swivel cylinder 149 with the via the load feedback line 102 in pressure coupled into this drive pressure chamber 155 results. The result of this activation of the swivel cylinder 159 is that the output pressure that the variable pump 76 'under load generated, the pressure used in the consumer always by an amount exceeds which is equivalent to the restoring force of the spring 147 in the selected explanatory example by 20 bar.

To explain the connection block 73 on which in the case of 3, the pressure compensator 99, in the case 4 the 2/2-way valve 154, this is adjacent to the operating mode preselection valve 74 following the control valve 72 for the rotary drive 57 of the placing boom 14 and to this the control valves 68 to 71, assembled in this order in hydraulic longitudinal linkage are now to the details of FIGS. 5a and 5b and 5c.

The connection block 73 is designed as a one-piece, elongated cuboid block made of steel or aluminum, on which, seen in the longitudinal direction, a connection field 161 for functional elements of the pressure supply unit 77 or 77 ', a connection field 162 for the assembly of the operating preselection valve 74 , A connection field 163 for the mounting of the control valve 72 for the rotary drive 57 of the placing boom 14 and the connection fields 163 ', 163 ", 163"' and 163 ^{IV are provided} for the elevation control valves 68 to 71, within which these functional elements and valves can be mounted and can thereby be connected in a pressure-tight manner to supply and control lines which are designed as continuous deep holes extending in the longitudinal direction of the connection block 73 or extending over a greater part of the length of the connection block 73.

Such longitudinal bores, which of the from the connector panel 161 for the pressure supply and control are located at the front 164 of the connection block 73 are introduced into it, are two with the tank 93 of the pressure supply unit 77 and 77 'connected return lines 132 and 132' which, hydraulic seen to form a single tank connection that extends up to extending the connection area 162 of the operating mode preselection valve 74 High pressure supply line 119, one up in the connection area 161 of the pressure supply unit 77 or Control line 166 extending to the control pressure outlet 108 of the pressure reducing valve 107 is connected, and two holes 167 and 168, which extend into the connection area 162 of the operating mode preselection valve 74 and as a control or are used as drain lines, which in turn connected to the tank 93 of the pressure supply unit 77 or 77 ' are.

With these longitudinal channels 132, 132 ', 119 and 166, 167 and 168, branch bores 169, 171 and 172 as well as 173, 174 and 176 communicate, which within the connection fields 163 and 163' to 163 ^{IV have an} identical bore pattern on the connection side of the control valves 72, shown in FIG. 5a and 68 to 71 of the boom movements lead.

Within these connection fields 163 and 163 'to 163 ^IV , the valve-side orifices 177 and 178 of the connection block 73 are also arranged at right angles to the course of the longitudinal bores crossing connection bores 179 and 181, the openings of which on the consumer side are the A and B connections 86 and 87, respectively Form control valve.

In the corners of the connection fields 161 to 163 ^IV arranged threaded holes 182, which are provided for fastening the valve housing to the connection block 73, are formed as blind bores, which only extend over a small part of the thickness of the connection block 73, so that in the through Central axes of the threaded holes marked longitudinal planes 180 and 185 longitudinal channels as the control line 167 can run.

Within the uniform - standardized - hole patterns corresponding to connection fields 163 to 163 ^IV , the load comparison connections 116 of the comparison valves 114 correspond to orifices 116 'of tap holes 183 and 183' to 183 ^IV and the comparative outputs 117 of the perpendicular to the plane of the orifices of the various connection bores of the connection block Comparison valves 114, the orifices 117 'of branch bores 184 and 184' to 184 ^IV , whose central axis lies in the same longitudinal plane 186 of the connection block 73 as the central axes 187 of the through transverse bores 179, which are used as A connection channels. Each of the comparison inputs 116 of the comparison valves 114 is associated with a longitudinal bore (FIG. 5c) 188 and 188 ′ to 188 ^IV , which is made in the end face 164 of the connection block 73 and extends into the plane extending at right angles to the longitudinal edges 189 of the connection block 73 191 or 191 'to 191 ^IV , of which only the planes 191 to 191 "are shown in FIG. 5c, in which the axis of the vertical tap hole 183 or 183' to 183 ^IV lies, the opening 116 'of which It forms the comparison inlet of the respective comparison valve 114. The respective longitudinal bore 188 or 188 'to 188 ^IV is connected to the branch bore via a transverse tap hole 192 or 192' to 192 ^IV , which is introduced from a long side of the connection block 73 and is sealed there 183 or 183 'to 183 ^IV connected, the opening 116' of which forms the load comparison port of the respective comparison valve 114 and via a further transver sale branch bore 193 or 193 'to 193 ^{IV is} connected to the branch bore 184 or 184' to 184 ^IV , the orifice 117 'of which forms the comparison outlet of the adjacent comparison valve 114 which, seen in the chaining direction, belongs to the subsequent control valve, which, however, seen in the feedback direction is the "preceding" comparison valve 114.

These longitudinal bores 188 or 188 'to 188 ^IV , via which only one comparison inlet 116 of one of the comparison valves 114 is communicatively connected to the comparison outlet 117 of an adjacent comparison valve 114, are sealed at the end face 164 of the connection block 73 by plugs, the comparison inlet 116 'of the last comparison valve 114, which is arranged at a distance from the connection field 161 of the pressure supply unit 77 or 77', is internally connected to a line leading to the tank 93 of the pressure supply unit.

The spur lines 183 and 184 or 183 'to 183 ^IV and 184' communicating via one of the longitudinal bores 188 or 188 'to 188 ^IV via one of the spur lines 192 and 193 or 192' to 192 ^IV and 193 'to 193 ^IV to 184 ^IV form the two control or comparison valves connecting sections 102 'of the load feedback line, designated 102 as a whole, the first section leading to the pressure supply unit 77 or 77' is expediently introduced into the connection block 73 from the unit side - Not shown - hole is formed, which is connected to the comparison output 117 of the comparison valve 114 of the operating mode selector valve 74.

The connection block 73 explained in detail with reference to FIGS. 5a to 5c is also suitable for the construction of the pressure supply and control unit 97 "shown as a further exemplary embodiment in FIG. 6, which differs from the pressure supply and control unit 97 shown in FIG. 3 essentially differs in that the control valve 72 'for the rotary drive 57 of the mast and the control valves 68' to 71 'for the elevation movements of the mast arms as so-called black-and-white valves, ie as valves whose 0 and I and 6, the connection block-side connection openings 117 'and 116' are sealed off by the respective valve housing within the connection fields 163 and 163 'to 163 ^IV , since valves corresponding to the function of the comparison valves 114 are not required and accordingly the pressure control valves 68 'to 72' assigned to them are not provided. In the scope of the pressure supply unit 77 and the design of the operating mode preselection valve 74 and its hydraulic circuitry, the pressure supply and control device 97 "according to FIG. 6 is identical to that according to FIG. 3, so that the corresponding reference numerals in FIG. 6 is sufficient as a reference to the description given in this regard using the exemplary embodiment according to FIG. 3.

In the device 97 "according to FIG. 6, the comparison input can 116 of the comparison valve 114 of the operating mode selector valve 74 connected to the tank 93 of the pressure supply unit 77 be.

The pressure supply and Control units are also in vehicles with a support device 30 and an articulated mast 14 can be used, in the end of the mast 14, a device is arranged which is spacious along running trajectories must be movable, such as a cleaning device for aircraft.

Claims (23)

1. A hydraulic pressure supply- and control-device for a mobile concrete pump (12), comprising a multi-armed distributing boom (14) positioned pivotably on a vehicle and having a hydraulic pivot drive (57) and hydraulic elevation drives individually assigned to the arms of the boom, as well as a hydraulic support device (30) by which the vehicle is supported at corners of a larger area outside the vehicle base area against tipping over, as hydraulic consumers for whose pressure supply a single load-sensing pressure supply device (77;77') is provided, whose pressure output is connectable alternatively to a hydraulic control unit of the support device or a hydraulic control unit of the distributing boom by way of an operating mode selector valve (74), further comprising electro-hydraulically or electro-pneumatically controlled, hydraulically actuated control valves which are individually assigned to the pivot drive (57) and the elevation drives of the boom (14), as well as pressure controlled load-comparative valves (68-72) which react to the pressures prevailing in the respective partial consumers of the boom, which are connected to each other in a hydraulic longitudinal chain and mechanically combined in the form of a control valve block (73), on which the valve groups formed by a control valve and a comparative valve (114) are positioned spacially adjacent to each other, wherein the comparative valves are connectable in series to each other by channels forming sections of a load feedback line (102), which lead from a comparative output of the respective comparative valve to a load-comparative terminal of that adjacent comparative valve, which is positioned at the supply device side, and wherein the comparative valve are driven by relatively higher pressure present at a load connection, at which the pressure acting in the connected partial consumer prevails, than at their load-comparative input, into a functional position connecting the load connection with the comparative output and blocking it with respect to the load-comparative input, and by relatively higher pressure at the load-comparative input than at the load connection into a functional position connecting the load-comparative input with the load-comparative output and blocking it with respect to the load connection, characterized in that a one-piece block made of steel or aluminum is provided as a hydraulic linking element as well as a mechanical carrier of the control valves (68 to 72) of the boom control unit, of the operating mode selector valve (74), and possibly of switching elements of the pressure supply device (77;77'), in which

   a) a P-line (119) connected to all high-pressure terminals of the control valves (68 to 72),

   b) a reservoir line (132) connected to all return terminals of the control valves,

   c) at least one control line (166) transmitting control pressure for the actuation of the valves (68 to 72 and 74), and

   d) at least one further return line (167,168), by which the control circuit of the pressure-actuated valves is completed to the reservoir (93) of the pressure supply device (77;77'), are designed as single-axis bores extending in a lengthwise direction of the terminal block (73) - the direction of linking -, from which connection channels originate whose valve-sided ports are positioned within terminal arrays (163,163' to 163^IV) of the valves in the bore layout of proportional valves, and that the sections (102') of the load feedback line (102), which are serially connectable to each other by the comparative valves (114), are formed by individual longitudinal bores (188,188' to 188^IV) introduced into the terminal block (73) from its free end (164) and plugged there, as well as by cross channels (192,192' to 192^IV, 183,183' to 183^IV, 193,193' to 193^IV, and 184,184' to 184^IV) connecting these longitudinal bores (188,188' to 188^IV) individually to the load-comparative output (117) of one of the comparative valves (114) as well as to the load-comparative input (116) of the supply-sided adjacent comparative valve.
2. The pressure supply- and control-device of claim 1, characterized in that the cross channels communicating with each of the plugged longitudinal bores (188,188' to 188^IV) are formed by a first cross bore (192,192' to 192^IV, 193,193' to 193^IV), which is introduced into the terminal block (73) originating at a longitudinal plane extending perpendicularly with respect to the terminal plane of the valves, penetrates through the longitudinal bore, and is plugged at this longitudinal plane, and by a second cross bore (183,183' to 183^IV, 184,184' to 184^IV) leading to said first cross-bore, being introduced into the terminal block (73) from the connection side, and extending perpendicularly with respect to the terminal plane.
3. A pressure supply- and control-device of claim 1 or claim 2, characterized in that the load feedback line (102) leading from the comparative valve (114) of the operating mode selector valve (74) to the load sensing input of the pressure supply device is formed by a longitudinal bore introduced into the terminal block (73) originating at its supply side.
4. The pressure supply- and control-device of one of claims 1 to 3, characterized in that a terminal array (161) for a pressure balance (99) or restrictor arrangement (154), provided for the load sensing, and/or a pressure limiting valve (106) and/or a pressure reducing valve (107) of the pressure supply device (77,77'), used for the dissipation of control pressure, is also provided on the terminal block (73).
5. The pressure supply- and control-device of one of claims 1 to 4, characterized in that the comparative valves (114) are designed as shuttle check valves.
6. The pressure supply- and control-device of one of claims 1 to 5, characterized in that the comparative input (116) of the comparative valve (114) which is positioned remotely with respect to the pressure supply device (77;77') is connected with the reservoir (93) of the pressure supply device.
7. The pressure supply- and control-device of one of claims 1 to 6, wherein the control valves for the pivot and elevation drives of the boom are designed as proportional valves, characterized in that pressure balances (128) individually assigned to the control valves are provided, which control the pressure medium flow through the respective control valve to a constant pressure drop over the respective control valve.
8. The pressure supply- and control-device of claim 7, characterized in that the pressure balances (128) individually assigned to the control valves (68 to 72) are designed as 2-way flow control valves which are hydraulically connected in series with the respective control valve.
9. The pressure supply- and control-device of claim 7 or 8, characterized in that the control valves (68 to 72) have additional flowpaths (136,137) which are open in the alternative flow positions (I and II) and blocked in the neutral position (0), by way of which the consumer pressure prevails at the comparative input (138) of the respective pressure balance (128), whose reference input is subjected to the output pressure of the pressure supply device as a reference pressure.
10. The pressure supply- and control-device according to one of claims 1 to 9, characterized in that the pump (76') of the pressure supply device (77') is designed as a controllable pump, e.g. a pivot disc pump, having a pressure-controlled flow rate control element (149), which is supplied with the output pressure of the comparative valve (114) of the operating mode selector valve (74) as control pressure, to which it is subjected in the sense of enlarging the flowrate of the pump.
11. The hydraulic pressure supply- and control-device of claim 10, characterized in that a double-acting hydraulic linear cylinder is provided as the flow rate control element (149) of the controllable pump (76'), whose piston, which acts upon the flow rate setting element (146) of the pump (76), is moveable in the sense of decreasing the flow rate of the pump (76') by subjecting the bottom drive-pressure space (151) of the flow rate setting element (149) to the output pressure of the pump against the action of the output pressure of the comparative valve (114) of the operating mode selector valve (74) introduced into its rod-sided drive pressure space (155) and against the restoring force of a pre-stressed spring (147), that a 2/2-way valve (154) designed as a pressure controlled proportional valve is connected parallel to the pump (76'), which attains its blocking neutral position (0) by the action of a pre-stressed valve spring (156) and possibly bilateral pressure subjection of its valve piston on its spring-sided face and the opposing face (157) to the output pressure of the pump (76') and its flow position (I) having a flow cross section of the flowpath proportional to the excursion by subjection of only the face (157) of the valve piston opposing the spring side to the output pressure of the pump (76'), and that the prestressing of the valve spring (156) is significantly smaller than that of the return spring (147) of the flow rate setting element (146) of the pump (76') and corresponds to approximately half that value.
12. The hydraulic pressure supply- and control-device of claim 11, characterized in that the spring-sided face of the piston of the 2/2-way proportional valve (154) is suited to be relieved of its pressure towards the reservoir (93) of the pressure supply device (77 ) by way of a flowpath (153) opened only in the neutral position (0) of the operating mode selector valve (74).
13. The hydraulic pressure supply- and control-device of one of claims 1 to 9, characterized in that the pump (76) of the pressure supply device (77) is designed to be a fixed displacement pump having a 3-way pressure balance (99) as a load-sensing element.
14. The hydraulic pressure supply- and control-device of claim 13, characterized in that the control valves (68 to 72) for the motion control of the boom (14) are designed to be switching valves, which open flowpaths having defined flow cross sections in their different functional positions (I and II) assigned to alternative directions of motion of the boom drives.
15. The hydraulic pressure supply- and control-device of claim 14, characterized in that the ports (177' and 178') of the terminal block (73), by way of which the line sections (102') of the load feedback line (102) open to the terminal side of the terminal block (73) within the terminal arrays (163,163 to 163^IV) of the control valves (68 to 71) and the terminal-sided ports of the cross bore (173) originating at the control line (166) as well as the cross bores (174,176) originating at additional return lines (167,168) open within the terminal arrays (163,163' to 163^IV), are tightly blocked in their mounted state by way of the valve bodies of the control valves (68 to 71).
16. The hydraulic pressure supply- and control-device of claim 14 or 15, characterized in that the control valves (68 to 71) for the elevation drives of the boom (14) are designed as 4/3-way valves having a blocking neutral position (0), and the control valve (74) for the pivot drive of the boom is designed as a 4/3-way valve which connects both consumer terminals of the pivot drive to the reservoir (93) of the pressure supply device (77) in its neutral position (0).
17. The hydraulic pressure supply- and control-device according to one of claims 1 to 16, characterized in that load maintaining circuits (78,79) positioned at the consumer side are provided, which keep the return lines of the individual partial consumers of the support device (30) and the boom (14) blocked in the non-actuated state (0) of the operating mode selector valve (74).
18. The hydraulic pressure supply- and control-device of one of claims 1 to 17, characterized in that the operating mode selector valve (74) attains its functional position (II) assigned to the boom control operation only when

    a) a preselector control stage is actuated by which the boom (14) is selected as a hydraulic consumer and

    b) at least one of the control valves of the boom (14) is selected,

    and remains in its neutral position (0) otherwise.
19. The hydraulic pressure supply- and control-device of claim 18, characterized in that the operating mode selector valve (74) attains its functional position assigned to the setting operation of the support device (30) by an actuation of the preselector control stage, by which the support device (30) is selected as a hydraulic consumer, and remains there as long as the support device (30) is kept selected as a hydraulic consumer.
20. The hydraulic pressure supply- and control-device of claim 18, characterized in that the operating mode selector valve (74), too, attains its functional position (I) assigned to the setting operation of the support device (30) when

    a) the preselector control stage is actuated in the sense of selecting the support device (30) as a hydraulic consumer and

    b) at least one of the control valves (67,68) of the support device (30) is selected,

    and remains in its neutral position (0) otherwise.
21. The hydraulic pressure supply- and control-device of one of claims 18 to 20, characterized in that the preselector control stage is actuated by a first actuation of one control valve of the boom (14) or the support device (30).
22. The hydraulic pressure supply- and control-device of one of claims 1 to 21, characterized in that an actuation in the same sense (extension or retraction) of two support cylinders which are arranged at diagonally opposing corners of the support area of the mobile concrete pump (10) is not possible.
23. A pressure supply- and control-device, especially according to one of claims 1 to 22, characterized by its use on a vehicle having a hydraulic support device (30) and a hydraulically-driven boom, at the end of which a work device is arranged moveable over a large range.

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