EP0670946A1 - Systeme hydraulique de commande et d'alimentation en pression pour pompe a beton pour chantier autoroutier - Google Patents

Systeme hydraulique de commande et d'alimentation en pression pour pompe a beton pour chantier autoroutier

Info

Publication number
EP0670946A1
EP0670946A1 EP94926895A EP94926895A EP0670946A1 EP 0670946 A1 EP0670946 A1 EP 0670946A1 EP 94926895 A EP94926895 A EP 94926895A EP 94926895 A EP94926895 A EP 94926895A EP 0670946 A1 EP0670946 A1 EP 0670946A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
control
valves
comparison
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP94926895A
Other languages
German (de)
English (en)
Other versions
EP0670946B1 (fr
Inventor
Hartmut Benckert
Hans Renz
Werner MÜNZENMAIER
Gabriel Galambos
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Putzmeister Concrete Pumps GmbH
Original Assignee
Putzmeister AG
Putzmeister Werk Maschinenfabrik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Putzmeister AG, Putzmeister Werk Maschinenfabrik GmbH filed Critical Putzmeister AG
Publication of EP0670946A1 publication Critical patent/EP0670946A1/fr
Application granted granted Critical
Publication of EP0670946B1 publication Critical patent/EP0670946B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
    • E04G21/00—Preparing, conveying, or working-up building materials or building elements in situ; Other devices or measures for constructional work
    • E04G21/02—Conveying or working-up concrete or similar masses able to be heaped or cast
    • E04G21/04—Devices for both conveying and distributing
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
    • E04G21/00—Preparing, conveying, or working-up building materials or building elements in situ; Other devices or measures for constructional work
    • E04G21/02—Conveying or working-up concrete or similar masses able to be heaped or cast
    • E04G21/04—Devices for both conveying and distributing
    • E04G21/0418—Devices for both conveying and distributing with distribution hose
    • E04G21/0436—Devices for both conveying and distributing with distribution hose on a mobile support, e.g. truck
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/877—With flow control means for branched passages
    • Y10T137/87885—Sectional block structure

Definitions

  • the invention relates to a hydraulic pressure supply and control unit for a truck-mounted concrete pump, which has a multi-armed boom that is rotatably arranged overall on a vehicle with a hydraulic rotary drive and individually assigned hydraulic elevation drives, as well as a hydraulic support device, by means of de ⁇
  • the vehicle can be supported against tilting outside the vehicle base area in the corner points of a larger area, on the other hand, as hydraulic consumers, for the pressure supply of which a single pressure supply unit designed as a load-sensing unit is provided, the pressure output of which is by means of an operating mode preselection
  • the valve can be connected to a hydraulic control unit of the support device or to a hydraulic control unit of the placing boom, so that - for safety reasons - the support device and the mast are not activated at the same time - "move gt "can be.
  • the hydraulic control unit of the distribution mast comprises the hydraulic drive and the elevation drives of the mast individually assigned, electro-hydraulically or electropneumatically piloted, hydraulically operated control valves and pressure-controlled to the pressures prevailing in the respective partial consumers of the mast corresponding load comparison valves, which are connected together in a hydraulic longitudinal linkage and mechanically combined to form a control valve block, the valve groups formed by a control valve and a comparison valve each, which are each assigned to one of the mast drives Lich arranged next to each other.
  • equalization valves can be connected in series with one another via channels which form sections of a load feedback line. These channels lead from a comparison output of the respective comparison valve to a load comparison connection of the adjacent comparison valve which, viewed from the comparison output of the first-mentioned valve, is arranged on the supply unit side.
  • comparison valves are due to the relatively higher pressure at a load connection, at which the pressure effective in the connected partial consumer is present, than at their load comparison input into a connection connecting the load connection to the comparison output and blocking the load comparison input, and due to relatively higher Pressure at the load comparison input is controlled as at the load connection into a functional position connecting the load comparison input to the load comparison output and isolating it from the load connection, as a result of which the highest pressure prevailing in one of the sub-consumers is controlled Pressure supply unit reported back and sensed there for the need-based adjustment of the delivery rate of the pump of the pressure supply unit.
  • valves joined to form the valve block have disc-shaped housings which have through bores arranged in a base part in a defined bore pattern and which are communicatively connected to a supply connection or a control connection of the respective valve. Furthermore, the valve housings have through bores, through which tie rods can be inserted, by means of which the valves can be fastened to one another in such a way that the bores which communicate with hydraulic connections of the valves form continuous supply channels which in the area of the connection planes , on which the housings of adjacent valves abut one another, and the O-rings surrounding the orifices of the bores are sealed off from the outside.
  • a pressure supply and control unit of this type also has a number of disadvantages: the numerous sealing points resulting from the "sandwich" structure of the valve block inevitably have the consequence, due to unavoidable signs of aging on the sealing rings, that the Separation points of the valve block, at least after some time of use, may leak leakage oil to an increased extent, which is unacceptable even in small quantities. Sealing rings must therefore be replaced relatively frequently, which in practice requires the valve block to be removed from the vehicle in order to be able to release the relatively long tie rods. The same applies analogously to the replacement of a defective valve.
  • Such maintenance work is very time-consuming and associated with high costs, both in terms of maintenance and repair work and because of the high downtime of the truck-mounted concrete pump itself.
  • the object of the invention is therefore to improve a pressure supply and control unit of the type mentioned in such a way that it is less susceptible to faults and can be repaired with considerably less time and cost in the event of a seal or valve damage.
  • a connection block designed as a one-piece block of steel or aluminum is provided, in which one block with all High-pressure connections of the control valves connected P-line, one connected to all return connections of the control valves
  • REPLACEMENTB ne tank line, at least one control pressure for the actuation of the valves leading control line 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 is closed, as in the longitudinal direction of the connection block - the chaining direction - extending, uniaxial Bores are formed, from which connecting channels originate, the valve-side openings of which are arranged within connecting fields of the valves in the bore pattern of proportional valves.
  • the sections of the load feedback line that can be serially connected to one another via the comparison valves are introduced into each of the longitudinal bores from the free end of the connection block and plugged at this free end, and these are individually connected to the load comparison output of one of the comparison valves and to the Load comparison input of the transverse channels connecting adjacent comparison valve on the supply side is formed.
  • 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, thereby reducing the statistical probability of damage to such seals is significantly reduced.
  • 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 automotive concrete pump, are reduced to a small fraction compared to known pressure supply and control units reduced.
  • Valves can be used which have a simpler housing structure and are therefore correspondingly cheaper.
  • 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 should be used for the control can be made relatively late
  • 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.
  • connection block provided in accordance with claim 2 results in a space-saving arrangement of the longitudinal bores and transverse channels, which is also easy to implement in terms of production technology.
  • connection block In order to make maximum use of the assembly advantage conveyed by the connection block, it is advantageous if, as provided in a preferred design, it also has a connection field for a pressure compensator or throttle arrangement provided for load sensing and / or a pressure limiting valve or other hydraulic circuit elements of the pressure supply unit .
  • the comparison valves assigned to the partial consumers are preferably designed as exchangeable non-return valves which can be integrated into the control valves themselves.
  • the comparison inlet of the "last" comparison valve of the comparison valves connected in series via the individual line sections of the load feedback line, which is arranged at a distance from the pressure supply unit, is connected to its tank.
  • control valves for the movement control of the mast are designed as so-called “black and white valves", it is particularly advantageous if, as provided in claim 15 , Control and connection ducts that open within the connection fields can be sealed and “blocked” by means of the valve housing.
  • Load-holding circuits provided in accordance with claim 17 ensure that both the support device and the mast maintain a position reached by actuation even after the actuation has been canceled.
  • the type of control of the operating mode preselection valve provided according to claim 18 provides additional security against triggering mast movements which could result from malfunction-related switching positions of the mast control valves without these being actuated.
  • the electronic circuitry connections required for this purpose can be realized without further ado by a specialist in electrohydraulic control technology who has been appropriately trained for this purpose.
  • the preselection switching stage is also actuated accordingly by the first actuation of such a control valve.
  • FIG. 1 a shows a side view of a car pump with a hydraulically movable distribution boom and a hydraulically actuated support device, both in their transport configurations;
  • FIG. 1b shows the support device of the car pump according to FIG. 1 a in its actuated configuration that supports the vehicle against tipping;
  • FIG. 2 shows 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. 1 a and 1 b;
  • FIG. 3 shows a hydraulic circuit diagram to explain a first exemplary embodiment of a pressure supply and control unit provided for controlling the movement of the mast, with a constant pump and proportional valves;
  • FIG. 4 shows a further exemplary embodiment of a pressure supply and control unit suitable for controlling the mast movements with a variable displacement pump as the pressure source;
  • connection block on which the control valves of the pressure supply and control units according to Figures 3 and 4 can be mounted in hydraulic longitudinal linkage.
  • FIG. 5b shows the hydraulic circuit diagram of the connection block according to FIG. 5a
  • Fig. 6 shows another 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 truck-mounted concrete pump shown in FIGS. 1 a and 1 b comprises, mounted on a transport vehicle 11, a concrete feed pump 12, a distribution boom, generally designated 14, rotatable about a vertical, vehicle-fixed axis 13 and having a total of four articulated arms 16, 17, 18, 19, which can be pivoted about - horizontal - articulated axes 26, 27, 28 and 29 by means of hydraulic linear cylinders 21, 22, 23, 24, and a support device, designated overall by 30, which has four vertical hydraulic support cylinders 31 to 34, which are arranged at the free ends of horizontal arms 36 to 39, which in turn, by means of horizontally acting pivoting cylinders 41 to 44, about vertical vehicle axes 51 to 54 fixed to the vehicle, from a position parallel to central chassis side members, for example in FIG lb positions can be swung out, in which the concrete pump 10 far outside the contact surfaces of the vehicle wheels by extending the support cylinder 31 to 34 can be supported against tipping.
  • the rotating column 56 of the placing boom 14, which can be rotated about the vertical axis 13, is also provided with a hydraulic rotary drive 57 which, like the detailed illustration in FIG. 2, to the details of which is now also referred to, can be removed by means of two double-acting "parallel" hydraulic cylinder 58 and 59 is realized, by means of which a rack 61 or 62 can be driven in opposite directions, which has an externally toothed ring gear 64 which is firmly connected to the rotating column 56 on opposite sides thereof are in meshing engagement.
  • the linear cylinders provided for the elevation movements of the articulated arms 16 to 19 of the placing mast 14 are, for example, only for one of them, e.g. the “bottom” linear cylinder 21 is shown as a double-acting hydraulic cylinder, the pistons 63 of which can be acted upon with drive pressure on the bottom over their entire cross-sectional area and on the rod side on an annular area reduced by the cross-sectional area of the piston rod.
  • the correspondingly designed support cylinders 31 to 34 of the support device 30 are arranged in such a way that they are subjected to the output pressure of the operating pressure source on the larger surface of their pistons 63 in the support operation.
  • the double-acting linear cylinders 58 and 59 of the rotary drive 57 are of symmetrical design with the "intended for the elevation drives 21 to 24 and have piston rods protruding from the cylinder housing on both sides, the ends of which are connected to one another by the toothed racks passing laterally on the housing.
  • the support cylinders 31 to 34 of the support device 30 and their pivot cylinders 41 to 44 provided for extending the horizontal arms 36 to 39 supporting the support cylinders, of which in FIG. 2, only one, for example the one, for the sake of simplicity of illustration the left front support cylinder 31 and the swivel cylinder 41 provided for its extension arm 26 can be actuated via a support control valve 66 or a swivel control valve 67, which convey the basic function of 4/3-way valves, the two alternative flow rates ⁇ have positions I and II, which are assigned to the "forward" and "backward" operation of the respective support or swivel cylinder, and a neutral basic position zero, in which the piston 63 of the respective support or pivot cylinder remains in its currently assumed position.
  • the linear cylinders 21 to 24 provided overall for adjusting the elevation of the individual articulated arms 16 to 19 and the placing boom 14, of which only the linear cylinder 21 articulated on one side on the rotating column 56 is shown in FIG. 2 again for the sake of simplicity and the rotary drive 57 of the placing boom 14 comprising the jointly controllable linear cylinders 58 and 59 can be controlled via a control valve 68 to 71 or 72, which is only schematically indicated by a 4/3-way valve symbol, which in turn has two have alternative flow positions I and II, which are assigned to alternative directions of movement of the swivel arms 16 to 19 or rotary movements of the placing boom 14 as a whole, and a neutral basic position zero, in which the piston (s) of the respectively connected elevation control cylinder or the Linear cylinders 58 and 59 of the rotary drive 57 remain in their / their respective instantaneous position (s).
  • the function of the operating mode preselection valve 74 explained so far ensures that the placing boom 14 cannot be moved during the setting of the supporting device 30, and that this in turn cannot be actuated when the placing mast is moved.
  • the placing boom 14 and the supporting device 30 form two hydraulic consumers within the framework of the entire hydraulic supply and control unit, which cannot be actuated jointly, but only individually, whereby a high level of operational safety of the truck-mounted concrete pump 10 is achieved.
  • control technology means that are not specifically shown, in that whenever at least one of the control valves 68 to 72 of the placing boom 14 is / are actuated, simultaneously with this and only as long as this is the case - the operating mode Selector valve 74 is switched to the function position II provided for the pressure supply of the placing boom drives 57 and 21 to 24.
  • the operating mode preselection valve 74 is only switched over to its for the pressure supply of the support cylinders 31 to 34 and the pivot cylinders 41 to 44 of the support device 30 only for as long as at least one of the control valves 66 and / or 67 of the support device 30 is / are operated. Otherwise, the operating mode preselection valve assumes its basic position 0, in which the hydraulic pump 76 of the pressure supply unit, which is denoted overall by 77, is set to circulating operation or, if the pump 76 is designed as a variable displacement pump, to the maximum delivery quantity, the Hydraulic medium is cooled.
  • hydraulic linear cylinders 21 to 24 provided for setting the elevation of the individual articulated arms 16 to 19 and for the rotary drive 57 of the placing boom 14 these are individually assigned hydraulic load-holding circuits, designated overall with 78 or 79, with the hydraulic load holding circuits shown in FIG. 2 visible hydraulic circuitry details are provided, whereby, for the sake of simplicity of illustration, only one of the holding circuits 78 for the elevation cylinders is shown, which is also realized for the other elevation cylinders with the same structure and the load-holding circuit 79 for the rotary drive 57.
  • the load-holding circuits 78 and 79 for the individual mast arm drives 21 to 34 and 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 control valves 68 to 72 assigned to the linear drives 21 to 24 and the rotary drive 57 of the distributor mast 14, respectively as A-connection 86 and B-connection 87.
  • These outlet valves 81 and 82 are designed as 2/2-way valves with spring-centered, blocking basic position 0, which can be switched into a passage position I by pressurizing their control chambers 85.
  • An input check valve 88 or 89 is connected in parallel to the outlet valves 81 and 82, which, due to the relatively higher pressure at the associated A or B outlet of the respective control valve than in the connected pressure chamber, for example the rod-side pressure chamber 91 and the bottom-side pressure chamber 92 is acted upon by one of the linear cylinders 21 to 24 in the opening direction and is otherwise blocked.
  • the control chamber 88 of the outlet valve 81 connected upstream of the A consumer connection 83 is connected to the B inlet 87 'of the load holding circuit 78 or 79, which in turn is connected to the B inlet Connection 87 of the respective control valve is connected, the control chamber 88 of the outlet valve 82 connected upstream of the B consumer connection 84 to the A input 86 'of the load-holding circuit 78 and 79, respectively.
  • the load-holding circuits 78 and 79 are immediate mounted on the linear cylinders 21 to 24 or the rotary drive 57, while the relevant control valves 68 to 72 are mounted on the remote connection block 73.
  • a further pressure limiter is provided in the elevation drive cylinders 21 to 24, which limits the pressure that can be supplied to the rod-side drive pressure chamber 91 to a lower value than the maximum value of the outlet pressure of the hydraulic pump 76.
  • a pressure control device designated as a whole by 96, the operating mode preselection valve 74 and the control valves 68 to 72 for the mast movements which is referred to as a total of 97 pressure supply and control unit, we now refer to next referred to FIG. 3.
  • the hydraulic pump 76 provided as the primary pressure source is designed as a constant pressure pump which can be operated with a constant rate of delivery: -.- quantity Q and within the scope of which the pressure control device 96 is more comprehensive.
  • Pressure supply unit 77 works as a load-sensing pump, such that the supply high pressure provided at the pressure outlet 98 of the pressure supply unit 77 with the load caused by the respective hydraulic consumers - support device 30 or distribution boom 14 - as required varies.
  • the relevant regulation conveys a 3-way pressure compensator 99 connected between the pressure outlet 98 and the tank 93 of the pressure supply unit 77, which is designed in the manner of a pressure-controlled 2/2-way proportional valve which is actuated by a prestressed valve spring 101 and the pressure drop across the respective connected consumer, which acts via a load feedback line of the pressure compensator 99, designated 102 as a whole, in the sense of an increase in the flow resistance of the adjusting throttle formed by the pressure compensator 99 and is acted upon by the Pressure outlet 98 of the pressure supply unit 77 pressure present, which acts on the opposite end face 104 of the piston of the pressure compensator 99, in the sense of a reduction in the flow resistance of the throttle formed by the pressure compensator 99.
  • the pressure supply unit 77 further comprises a pressure limiting valve 106 which increases the pressure output at the high pressure outlet 98 to a maximum value of e.g. 400 bar, as well as a pressure reducing valve 107, which at a control pressure outlet 108 of the pressure supply unit 77 provides a - relatively low - pressure which can be used as control pressure for the control valves 68 to 72 and for the operating mode preselection valve 74 by 25 bar.
  • a pressure limiting valve 106 which increases the pressure output at the high pressure outlet 98 to a maximum value of e.g. 400 bar
  • a pressure reducing valve 107 which at a control pressure outlet 108 of the pressure supply unit 77 provides a - relatively low - pressure which can be used as control pressure for the control valves 68 to 72 and for the operating mode preselection valve 74 by 25 bar.
  • the operating mode preselection valve 74 immediately downstream of the pressure supply unit 77 in the sense of longitudinal linkage, the control valve 72 following it in the linkage for the rotary drive 57 of the placing boom 14 and the control valves 68 to each individually assigned to the individual mast arm drives 21 to 24 71, of which in FIG.
  • the pressure outlet 98 of the pressure supply unit 77 is via a first flow path 109 of the operating mode preselection valve 74 with a high pressure connection leading to the support device 30.
  • a high pressure supply line 119 for the mast arm starting from the operating mode preselection valve 74 is provided via a flow path 118 which is further released in this function position I.
  • Drives 57 and 21 to 24 provided high-pressure supply line 119 are connected to the tank 93 of the pressure supply unit 77, so that the distributor mast drives cannot be activated.
  • the pressure outlet 98 of the pressure supply unit 77 is connected to the high pressure supply line 119 for the mast drives via a first flow path 121 released in this functional position II the high-pressure supply line 111 provided for the support device 30 is connected to the tank 93 of the pressure supply unit 77 via a second flow path 122 which is released in the functional position II 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.
  • the control valve 72 assigned to the rotary drive 57 of the distribution boom 14 has a functional position I which is assigned to a rotation of the distribution mast in the counterclockwise direction and a functional position II which is assigned to the rotation of the distribution mast 14 in a clockwise direction.
  • the rotary drive 57 of the placing boom 14 is held firmly in the azimuthal position assumed by means of its load-holding circuit 79.
  • the supply line 124 which leads from the valve-side A-connection 86 to the consumer-side A-input 86 'of the rotary drive 57, is via a first flow path 126, released in this functional position I, with the pressure outlet 127 of a 2-way pressure compensator 128 connected, which is connected between the control valve 72 and the pressure outlet 98 of the pressure supply unit 77.
  • the second supply line 129 which leads from the B port 87 of the control valve 72 and leads to the consumer-side B input 87 'of the rotary drive 57, is via a second flow path 131, which is released in the functional position I of the control valve 72, with the flow path 131 Tank 93 of the pressure supply unit 77 return line 132 connected.
  • a third flow path 136 or 137 is also released, via which the pressure prevailing on the consumer side is present on the one hand at the load connection 113 of the comparison valve 114 assigned to the rotary drive 57 and on the other hand also at the comparative inlet 138 of the pressure compensator 128 hydraulically connected in series with the rotary drive control valve 72, the reference inlet 139 of which is connected to its pressure outlet 127.
  • This pressure compensator 128, which in turn is designed as a throttle with variable flow resistance, which is reduced by the force of a preloaded valve spring 141 and by the force rectified with it, which results from the load pressure present at the comparative inlet 138, and by its outlet pressure , which is also at its reference input 139, is acted upon in the sense of increasing its flow resistance, has the effect that in the functional positions I and II of the rotary drive control valve 72, depending on how quickly the mast is to be rotated , different flow cross-sections of the flow paths 126 and 131 or 133 and 134 can correspond, the pressure drop across the rotary drive control valve 72 remains constant.
  • ERS ⁇ TZBL ⁇ FT (RULE 26) connected to the unpressurized tank 93 of the pressure supply unit 77. Furthermore, the load connection is via a flow path 143 additionally released in this basic position 0
  • the elevation control valves 68 to 71 assigned to the other "partial consumers" of the distribution mast 14 - the linear drive cylinders 21 to 24 provided as the drives for the mast arms 16 to 19 - are together with a comparison valve each
  • the comparison outlet 117 of the "first" comparison valve 114 assigned to the operating mode preselection valve 74 having one end face 103 of the piston of the pressure compensator 99 of the pressure supply unit 77 is connected and the load comparison port 116 of the "last" elevation control valve 71, which is on the connection block 73 arranged as it were at a distance from the operating mode preselection valve 74 and connected to the tank 93, it is achieved that the highest value of the pressure on the pressure compensator 99 is reported back via the load feedback line 102 with which the partial consumer of the placing boom 14 is operated, because this operating pressure brings the comparison valve 114 of the associated control valve into the functional position blocking its load comparison port 116 against the next comparison valve, and the consumer operating pressure present at its comparison outlet 117 determines the difference between "its" comparison valve ⁇ til and the pressure compensator 99 arranged comparison valves 114 in their releasing the load comparison input 116 and
  • the operating mode preselection valve 74 and the control valves 68 to 72 of the pressure supply and control unit 97 provided for drive control according to FIG. 3 are designed as hydraulically actuated proportional valves with spring-centered basic position 0, in which the control pressure in each case the deflections their slide valves are proportional with respect to the basic position and thus the flow cross sections of the respectively released flow paths, can be adjusted by electro-hydraulic or electro-pneumatic, if necessary also manually operated, not specifically shown pilot valves in the sense of an emergency operation.
  • a pressure supply and control unit 97 'of a truck-mounted concrete pump 10 shown in FIG. 4 the details of which are now referred to, the operating mode selector valve 74 and the control valves 68 to 72 thereof which are shown in FIG 3 described design and function and, including comparison valves 114 and pressure compensators 128 individually assigned to them, are in the same way 11 mounted longitudinally on a common connection block, on which the hydraulic circuit elements of the pump 76 'are also arranged, namely the pressure limiting valve 106, the pressure reducing valve 107 and a 2/2-way valve 154, the "local""arranged in the same way as the pressure compensator 99 of the pressure supply and control unit 97 according to FIG. 3, but fulfills a different function in the context of the device 97 'according to FIG. 4.
  • the pump 76 'of the pressure supply unit 77' is designed as a variable displacement pump, the output volume flow of which can be regulated as required.
  • a suitable pump of this type is e.g. a swash plate pump, the swash plate schematically represented by arrow 146 in FIG. 4 by a prestressed spring 147, so long as no further forces act on the swivel plate 146, is pushed into one position, the maximum delivery rate of the pump 76 'of the pressure supply unit 77' corresponds.
  • the piston rod 148 engages a swivel cylinder 149 designed as a double-acting linear cylinder, the bottom-side drive pressure chamber 151 of which is supplied with the output pressure at the pressure outlet 98 of the variable displacement pump 76 'and the ⁇ -rod-side drive pressure chamber 155 to the load feedback line 102 of the pressure supply and Control unit 97 'is connected, which starts from the comparison outlet 117 of the comparison valve 114 assigned to the operating mode preselection valve 74.
  • the 2/2-way valve 154 is connected to the displacement pump 76 'in parallel between its pressure outlet 98 and the tank 93 and is urged into its blocking basic position 0 by a preloaded valve spring 156.
  • a relief flow path 152 is connected to the pressure outlet 98 of the adjusting pump 76 'via a throttle 150, which only connected to the tank 93 of the pressure supply unit 77 'in the basic position 0 of the operating mode selector valve 74 via a flow path 153 released in this basic position, but is blocked in the functional positions I and II of the operating mode selector valve, so that in These function positions I and II can build up a high pressure in the relief flow path, with which the piston of the valve 154 acts on the spring side and thereby one, the 2/2-way valve in which is directed in the same direction as the restoring force of the spring 156 whose blocking position is subjected to urging force.
  • valve spring 156 of the 2/2-way valve which can be implemented with a structure corresponding to the pressure compensator 99 of the exemplary embodiment according to FIG. 3, is designed in such a way that the valve 154 is subjected to excess pressure due to a relatively low control pressure the end face 157 opposite the spring side ⁇ eine ⁇ piston - from, for example 10 bar reached its flow position I.
  • the spring 147 by means of which the swivel plate 146 of the variable displacement pump 76 'is urged into its position corresponding to the maximum delivery rate of the variable displacement pump 76', is designed such that it holds the swivel plate 146 in this position as long as the difference in the pressures between the the bottom-side drive pressure chamber 151 and the rod-side drive pressure chamber 155 of the swivel cylinder 149 are smaller than a threshold value of about 20 bar.
  • variable displacement pump 76 As long as a consumer is not connected to the pressure outlet 98 of the pressure supply unit 77 ', i.e. the operating mode preselection valve is in its basic position 0, the variable displacement pump 76 'operates in circulation mode, since the 2/2-way valve 154 due to the dynamic pressure building up at its inlet 158, which acts on the spring side the opposite piston end 157 of the valve piston acts, reaches its flow position I and can thereby discharge pressure medium via the 2/2-way valve 154 to the tank 93.
  • the pressure dropping across the 2/2-way valve 154 has the amount of approximately 10 bar equivalent to the resetting force of the valve spring 156 in the circulating operation of the pump 76 '.
  • This pressure which is also coupled into the bottom-side drive chamber 151 of the swivel cylinder 149, is not sufficient to actuate the swivel cylinder 149 against the resetting force of the "spring acting in the opposite direction” and to rotate the swivel disk 146, and so on is held in the position corresponding to the maximum delivery quantity of the variable displacement pump 76 'by the spring 147.
  • the hydraulic fluid is constantly circulated in circulating mode with the amount of large volume flow and can be effectively cooled.
  • Tensioned spring 147 acts the force which results from pressurizing the rod-side drive pressure chamber 155 of the swivel cylinder 149 with the pressure coupled into this drive pressure chamber 155 via the load feedback line 102.
  • the result of this actuation of the swivel cylinder 159 is that the output pressure which the variable displacement pump 76 'generates under load exceeds the pressure used in the consumer ⁇ tet ⁇ by an amount which is equivalent to the restoring force of the spring 147, in the selected explanatory example around 20 bar.
  • connection block 73 on which, in the case of the exemplary embodiment according to FIG. 3, the pressure compensator 99, in the case of the exemplary embodiment according to FIG. 4, the 2/2-way valve 154, which is adjacent to the operating mode preselection valve 74, following this Control valve 72 for the rotary drive 57 of the distributor mast 14 and, following this, the control valves 68 to 71, which are mounted in this order in hydraulic longitudinal linkage, are now referred to the details of FIGS. 5a and 5b and 5c.
  • connection block 73 is formed 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 latter
  • Operating preselection valve 74, a connection field 163 for the assembly of the control valve 72 for the rotary drive 57 of the distributor mast 14 and the connection fields 163 ', 163 ", 163'” and 163 IV for the elevation control valves 68 to 71 are provided, within which these functional elements and valves can be mounted and can therefore be connected pressure-tight to supply and control lines which are deep holes extending in the longitudinal direction of the connection block 73 or extending over a larger part of the length of the connection block 73 are executed.
  • Such longitudinal bores which differ from those of the connection field 161 for the pressure side and pressure control remote from the end 164 of the connection block 73 are introduced into these, two return lines 132 and 132 'connected to the tank 93 of the pressure supply unit 77 and 77', which, viewed hydraulically, are a single tank connection form the high-pressure supply line 119 which extends into the connection area 162 of the operating mode preselection valve 74, a control line 166 which extends up to the connection area 161 of the pressure supply unit 77 or 77 'and which connects to the control pressure outlet 108 of the pressure reducing valve 107 is connected, as well as two bores 167 and 168 which extend into the connection area 162 of the operating mode preselection valve 74 and are used as control or leakage oil lines, which in turn are connected to the tank 93 of the pressure supply unit 77 or 77 'are connected.
  • connection fields 163 and 163' to 163 IV have an identical bore pattern on the one shown in FIG. 5a
  • the control valves 72 and 68 to 71 of the placing boom movements open.
  • valve-side orifices 177 and 178 are also arranged at right angles to the course of the longitudinal bores of connection bores 179 and 181, the openings on the consumer side of which connect the A and B connections 86 and 87, respectively of the respective control valve.
  • Threaded bores 182 arranged in the corners of the connection fields 161 to 163 IV which are provided for fastening the valve housings to the connection block 73, are designed as blind bores which only extend over a small part of the thickness of the connection block 73, so that in the through the central axes of the threaded bores marked longitudinal planes 180 and 185 longitudinal channels such as the control line 167 can run.
  • the load comparison connections 116 of the comparison valves 114 correspond to orifices 116 'of branch holes 183 and 183' to 183 which run perpendicular to the plane of the orifices of the various connection bores of the connection block IV and the comparative outputs 117 of the comparison valves 114, the orifices 117 'of branch bores 184 and 184' to 184 IV , the central axis of which lies in the same longitudinal plane 186 of the connection block 73 as the central axes 187 of the continuous transverse bores 179 which are used as A connection channels.
  • Each of the comparison inputs 116 of the comparison valves 114 is assigned 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 longitudinal bore 189 (FIG. 5c) and which extends into the longitudinal edge 189 of the connection block 73 extending plane 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 perpendicular right-hand bore 183 or 183' to 183 IV lies, whose mouth opening 116 'forms the comparison input of the respective comparison valve 114.
  • the respective longitudinal bore 188 or 188 'to 188 IV is via a transverse tap hole 192 or 192' to 192 IV , which is introduced from a long side of the connecting block 73 and is sealed there, with the tap hole 183 or 183 '. bi ⁇ 183 IV connected, the mouth opening 116 'forms the load comparison port of the respective comparison valve 114 and connected via a further transversal tap hole 193 or 193' to 193 IV with the tap hole 184 or 184 'to 184 IV whose mouth opening 117 'forms the comparison outlet of the adjacent comparison valve 114, which, seen in the chaining direction, belongs to the subsequent control valve, but that, seen in the feedback direction, is the "preceding" comparison valve 114.
  • 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, so that it differs from that in FIG. 3 shown pressure supply and control unit 97 essentially distinguishes in that the control valve 72 'for the rotary drive 57 de ⁇ Ma ⁇ ts 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 flow paths released in the different functional positions 0 and I and II have a defined flow cross section.
  • the control valve 72 'for the rotary drive 57 de ⁇ Ma ⁇ ts 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 flow paths released in the different functional positions 0 and I and II have a defined flow cross section.
  • black and white valves ie as Valves whose flow paths released in
  • connection block-side connection openings 117 'and 116' are sealed off by the respective valve housings within the connection fields 163 and 163 'to 163 IV , since they are functionally the same Valves corresponding to comparison valves 114 are not required and, accordingly, pressure compensators assigned to the movement control valves 68 'to 72' are also not provided.
  • the pressure supply and control device 97 ′′ according to FIG. 6 is identical to that according to FIG. 3, so that the Indication of the corresponding reference numerals in FIG. 6 as a reference to the relevant description given on the basis of the exemplary embodiment according to FIG. 3 suffices.
  • the comparison inlet 116 of the comparison valve 114 of the operating mode preselection valve 74 can be connected to the tank 93 of the pressure supply unit 77.
  • the pressure supply and control units explained with reference to FIGS. 1-6 can also be used in vehicles with a support device 30 and an articulated mast 14, in which a device is arranged at the end of the mast 14, which device is arranged along spacious trajectories
  • a cleaning device for airplanes must be movable, for example.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • On-Site Construction Work That Accompanies The Preparation And Application Of Concrete (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

L'invention concerne un système hydraulique de commande et d'alimentation en pression pour pompe à béton pour chantier autoroutier (10), qui comprend comme consommateurs hydrauliques, un mât distributeur (14) pourvu de moteurs hydrauliques d'orientation et d'élévation, ainsi qu'un dispositif hydraulique d'appui (30), pour l'alimentation en pression desquels est prévu un système commun d'alimentation en pression pouvant être raccordé, à l'aide d'une soupape de présélection du mode opératoire (74), soit à un système de soupape de commande du dispositif d'appui, soit à un système de soupape de commande du mât distributeur. Un bloc de raccordement (73) monobloc sert à la fois d'élément de raccordement hydraulique et de support mécanique pour les soupapes de commande (68 à 72) de l'unité de commande du mât, de la soupape de présélection du mode opératoire (74) et d'éléments de commutation du système d'alimentation en pression (77). Ce bloc de raccordement (73) comprend une conduite de type P (119), une conduite de type T (132), une conduite de commande (166) et une autre conduite de retour (167, 168) qui se présentent sous forme d'alésages s'étendant dans le sens de raccordement et d'où partent des canaux de raccordement qui débouchent à l'intérieur de zones de raccordement (163, 163' à 163IV) des soupapes et forment un ensemble d'alésages de soupapes proportionnelles. Chacune des sections (102') d'une ligne de rétrosignal de charge (102) connectées en série par l'intermédiaire de soupapes de comparaison de charge (114) est formée par un alésage oblong (188, 188' à 188IV) partant d'une extrémité libre (164) du bloc de raccordement (73), extrémité où il est bouché et par des canaux transversaux qui relient les alésages oblongs à une sortie de comparaison de charge (117) d'une soupape de comparaison et à l'entrée (116) de la soupape de comparaison adjacente, située côté alimentation.
EP94926895A 1993-09-07 1994-08-26 Systeme hydraulique de commande et d'alimentation en pression pour pompe a beton pour chantier autoroutier Expired - Lifetime EP0670946B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4330137A DE4330137A1 (de) 1993-09-07 1993-09-07 Hydraulisches Druckversorgungs- und Steueraggregat für eine Autobetonpumpe
DE4330137 1993-09-07
PCT/EP1994/002836 WO1995007399A1 (fr) 1993-09-07 1994-08-26 Systeme hydraulique de commande et d'alimentation en pression pour pompe a beton pour chantier autoroutier

Publications (2)

Publication Number Publication Date
EP0670946A1 true EP0670946A1 (fr) 1995-09-13
EP0670946B1 EP0670946B1 (fr) 1998-10-14

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ID=6496991

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Application Number Title Priority Date Filing Date
EP94926895A Expired - Lifetime EP0670946B1 (fr) 1993-09-07 1994-08-26 Systeme hydraulique de commande et d'alimentation en pression pour pompe a beton pour chantier autoroutier

Country Status (7)

Country Link
US (1) US5640850A (fr)
EP (1) EP0670946B1 (fr)
JP (1) JP3662022B2 (fr)
KR (1) KR100431351B1 (fr)
DE (2) DE4330137A1 (fr)
ES (1) ES2124426T3 (fr)
WO (1) WO1995007399A1 (fr)

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JP2022519053A (ja) * 2019-01-30 2022-03-18 プツマイスター エンジニアリング ゲーエムベーハー 車両
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CN112610556A (zh) * 2020-12-07 2021-04-06 湖南挖挖工程科技有限公司 泵车总车一体化阀块结构及泵车总车

Also Published As

Publication number Publication date
US5640850A (en) 1997-06-24
WO1995007399A1 (fr) 1995-03-16
KR100431351B1 (ko) 2004-08-18
JPH08503755A (ja) 1996-04-23
ES2124426T3 (es) 1999-02-01
JP3662022B2 (ja) 2005-06-22
EP0670946B1 (fr) 1998-10-14
DE59407096D1 (de) 1998-11-19
DE4330137A1 (de) 1995-03-09

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