EP1120216B1 - Verfahren und Vorrichtung zum Mischen und Fördern von Beton - Google Patents

Verfahren und Vorrichtung zum Mischen und Fördern von Beton Download PDF

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Publication number
EP1120216B1
EP1120216B1 EP01101596A EP01101596A EP1120216B1 EP 1120216 B1 EP1120216 B1 EP 1120216B1 EP 01101596 A EP01101596 A EP 01101596A EP 01101596 A EP01101596 A EP 01101596A EP 1120216 B1 EP1120216 B1 EP 1120216B1
Authority
EP
European Patent Office
Prior art keywords
compressed air
mixing
conveying apparatus
motor
compressor element
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.)
Expired - Lifetime
Application number
EP01101596A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1120216A2 (de
EP1120216A3 (de
Inventor
Werner Foerster
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.)
Kaeser Kompressoren GmbH
Original Assignee
Kaeser Kompressoren 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
Priority claimed from DE10033663A external-priority patent/DE10033663A1/de
Application filed by Kaeser Kompressoren GmbH filed Critical Kaeser Kompressoren GmbH
Publication of EP1120216A2 publication Critical patent/EP1120216A2/de
Publication of EP1120216A3 publication Critical patent/EP1120216A3/de
Application granted granted Critical
Publication of EP1120216B1 publication Critical patent/EP1120216B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28C—PREPARING CLAY; PRODUCING MIXTURES CONTAINING CLAY OR CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28C5/00—Apparatus or methods for producing mixtures of cement with other substances, e.g. slurries, mortars, porous or fibrous compositions
    • B28C5/08—Apparatus or methods for producing mixtures of cement with other substances, e.g. slurries, mortars, porous or fibrous compositions using driven mechanical means affecting the mixing
    • B28C5/10—Mixing in containers not actuated to effect the mixing
    • B28C5/12—Mixing in containers not actuated to effect the mixing with stirrers sweeping through the materials, e.g. with incorporated feeding or discharging means or with oscillating stirrers
    • B28C5/1223—Mixing in containers not actuated to effect the mixing with stirrers sweeping through the materials, e.g. with incorporated feeding or discharging means or with oscillating stirrers discontinuously operating mixing devices, e.g. with consecutive containers
    • B28C5/123—Mixing in containers not actuated to effect the mixing with stirrers sweeping through the materials, e.g. with incorporated feeding or discharging means or with oscillating stirrers discontinuously operating mixing devices, e.g. with consecutive containers with pressure or suction means for discharging
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F35/00—Accessories for mixers; Auxiliary operations or auxiliary devices; Parts or details of general application
    • B01F35/75—Discharge mechanisms
    • B01F35/754—Discharge mechanisms characterised by the means for discharging the components from the mixer
    • B01F35/7543—Discharge mechanisms characterised by the means for discharging the components from the mixer using pneumatic pressure, overpressure or gas pressure in a closed receptacle or circuit system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28C—PREPARING CLAY; PRODUCING MIXTURES CONTAINING CLAY OR CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28C5/00—Apparatus or methods for producing mixtures of cement with other substances, e.g. slurries, mortars, porous or fibrous compositions
    • B28C5/08—Apparatus or methods for producing mixtures of cement with other substances, e.g. slurries, mortars, porous or fibrous compositions using driven mechanical means affecting the mixing
    • B28C5/0806—Details; Accessories
    • B28C5/0831—Drives or drive systems, e.g. toothed racks, winches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F35/00—Accessories for mixers; Auxiliary operations or auxiliary devices; Parts or details of general application
    • B01F35/30—Driving arrangements; Transmissions; Couplings; Brakes
    • B01F35/32—Driving arrangements
    • B01F35/32005—Type of drive
    • B01F35/32045—Hydraulically driven

Definitions

  • the invention relates to a mixing and conveying device for discontinuous, interrupted by charging operations mixture and subsequent promotion of thick materials, especially mortar and concrete, with a connected to a delivery line, a motor-driven agitator mixing vessel containing charged with mixed and conveyed and compressed air for discharging the thick matter through the delivery line can be acted upon, and with a built in the mixing and conveying device or as a separate unit, driven by a combustion or electric motor rotary compressor for generating the compressed air. Furthermore, the invention relates to a method for controlling and operating such a mixing and conveying device.
  • Such mixing and conveying devices are used in the construction industry for mixing and conveying of thick materials, in particular high solids with low water content such.
  • the components of the thick stock usually sand, binder and water, fed through a feed opening to the mixing vessel and then mixed by the agitator.
  • the lid of the mixing tank is closed and the mixing tank is pressurized with compressed air.
  • the thick material is pressed in the form of plugs which are interrupted by compressed air bubbles through a delivery line which is connected to an outlet nozzle in the lower part of the mixing vessel.
  • the interruptions between the plug arise because the blades of the still running agitator sweep periodically the outlet opening in the delivery line.
  • To support the plug conveying is usually compressed air by another Blowed in line in the area of the outlet nozzle.
  • Such mixing and conveying devices are designed with integrated or separate compressor.
  • the drive of the agitator takes place either via a switchable belt drive and a cardan shaft between the drive motor and agitator or via a hydraulic motor on the agitator and a hydraulic pump on the drive motor.
  • the compressor Due to the lack of a switchable coupling between the drive motor and the compressor element, the compressor is also driven during the mixing phase, in which there is no compressed air demand for the promotion. Although the compressor is idling, it nevertheless consumes a significant proportion of the drive motor power that is not available for the mixing process.
  • the required drive torque for the agitator is highest at the beginning of the mixing phase and then decreases rapidly when the feed is mixed to a pasty mass.
  • the required drive torque for the agitator depends strongly on the speed of the agitator. A reduction in the speed of the agitator at the beginning of the Mixed phase would reduce the required drive torque and (to an even greater extent) the required drive power (as a product of torque and speed), however, there is no efficient way of reducing the speed of the agitator in the known mixing and conveying equipment.
  • a change in the speed of the agitator is therefore limited on a change in the drive motor speed and / or in hydraulic motors by a bypass control with high power losses possible.
  • a combustion engine is used as the drive motor, then a reduction in the speed due to the curve speed-torque curve narrow limits.
  • a reduced drive motor speed means a reduction in the output of the engine.
  • the drive power required for the agitator at the beginning of the mixing phase has a clear maximum.
  • the design or tuning of the drive motor and the agitator must be done for this most unfavorable operating point, otherwise the engine can be strangled by the agitator.
  • the available power of the drive motor is not fully used for mixing.
  • the agitator runs in the known mixing and conveying equipment in the funding phase with an unnecessarily high speed and with unnecessarily high drive power, especially when - as in some devices usual - in the funding phase, the speed of the drive motor is further increased to as much as possible Generate compressed air for the promotion.
  • the unnecessarily high The power requirement of the agitator is not available for the generation of compressed air, ie the delivery of thick material.
  • the object of the invention is to improve the known mixing and conveying equipment to the effect that the power of the drive motor optimally used both during the mixing phase and during the delivery phase, reduces the design effort, the manufacturing cost and maintenance and reliability and durability of the device.
  • one or more pneumatic motors which are supplied with a proportion, preferably 20 to 100%, of the compressed air generated by the compressor, and their speed and / or torque and / or Drive power can be adapted by suitable means for influencing the supply of compressed air to the or the compressed air motors and / or the removal of exhaust air from the or the compressed air motors to the various operating phases of the mixing and conveying process.
  • a multi-part agitator can be used, the individual parts are each driven separately from a compressed air motor.
  • multiple air motors operating on a common shaft or coupled by a suitable gearbox may drive a one-piece agitator.
  • pneumatic motors with multiple inlets for the compressed air and / or multiple outlets for the exhaust air, which are preferably connected to different separate work spaces and / or with different housing sections of the same work spaces and their speed and / or drive power and / or drive torque can be changed by switching on or off the supply of compressed air or discharge of exhaust air at one or more of these inputs and outlets.
  • Air motors are particularly suitable for this application because of their speed-torque characteristic. They can also provide drive torque well above their rated torque, with their speed decreasing with increasing drive torque.
  • compressed air motors are on the one hand able to provide the relatively high drive torque for the agitator at the beginning of the mixing phase put.
  • their speed drops, so that the required for the agitator drive torque compared to known drives with a substantially constant speed is lower.
  • the lower drive torque at a lower speed means that compressed air motors reduce or prevent the maximum drive power occurring in known devices at the beginning of the mixing phase.
  • Compressed air motors must therefore be designed with a comparable mixing effect for a lower power than drives with belt transmission and cardan shaft or hydraulic motor and pump.
  • the use of compressed air motors is advantageous in particular because it leads to a decoupling of the rotational speeds of the drive motor and agitator.
  • the drive motor can run both in the mixing phase and in the delivery phase at full power and high speed to deliver as much compressed air for the drive of the agitator and / or for the promotion of thick matter.
  • the rotary compressors (screw compressors, vane compressors) commonly used in mixing and conveying equipment have compression chambers, which are formed between the rotor (s) and the compressor element housing and which open cyclically during the rotation of the rotor (s), at suction-side control edges close off the suction area, reduce it, open on the pressure-side control edges to the pressure side and push it out to the pressure side against the operating pressure. Openings or connections can be made in the fixed housing regions delimiting the compression chambers, by means of which compressed air with a temporally substantially constant pressure between intake and operating pressure can be taken or supplied to the compression chambers already closed by the suction region in the compressor element. The choice of the position of these connections determines the height of this intermediate pressure.
  • connection of these connections with the inlets and / or outlets of the compressed-air motors it is possible to change the pressure difference between the inlets and outlets of the compressed-air motors in a targeted manner.
  • the inlets and / or outlets can be throttled.
  • the pressure difference between the inlet and outlet of the air motors can be influenced by a variable bypass.
  • the compressed air is supplied to the or the compressed air motors at least temporarily with a pressure which substantially corresponds to the operating pressure of the compressor.
  • the compressed air is supplied to the compressed air motors at least temporarily preferably at a temperature which substantially corresponds to the compression end temperature of the compressor, which is usually between 70 ° C and 100 ° C in oil-injected rotary compressors.
  • the compressed air is taken to a point where she has not experienced any appreciable cooling. This allows a relatively high inlet temperature to be processed, so that the outlet temperature of the compressed air from the compressed air motors for thermodynamic reasons safely above the ambient temperature and no harmful condensation can occur.
  • the maximum operating volume is used.
  • the compressed air may also be advantageous to heat the compressed air prior to its delivery to the compressed air motors in a heat exchanger to a temperature above the compression end temperature of the compressor so as to further increase the working capacity of the compressed air as it expands in the air motors.
  • the compressed air can be heated, for example, by heat exchange with the cooling fluid or the exhaust gas flow of the internal combustion engine.
  • the compressed air can be supplied to the compressed air motors with an oil content for lubrication, preferably with 0.5 to 50 mg of oil per kilogram of air.
  • the desired oil content in the compressed air for the compressed air motors is preferably achieved in that the removal of the compressed air takes place at a suitable location before the fine separation of the oil in the compressor, z. B. in front of the coalescing filter in the oil separation tank.
  • the compressed air can be supplied to the pneumatic motors at least temporarily with a pressure which is between the suction and the operating pressure.
  • the compressed air can be removed at a suitable point of the compressor element.
  • the supply of compressed air to the compressed air motor via one or more valves can be opened and / or throttled and / or closed and / or switched between different sampling points.
  • the air emerging from the air motors is preferably returned to the circuit of the compressor.
  • This has, inter alia, the advantage that the oil does not escape to lubricate the air motors in the environment, but is returned to the compressor circuit.
  • One possibility is the return to the intake of the rotary compressor, z. B. in the inlet valve.
  • Another possibility of removing the exhaust air from the compressed air motor is to connect the outlet of the compressed air motor at the delivery passage with the compressed air supply of the mixing vessel.
  • the return or removal of the exhaust air can be opened and / or throttled and / or closed and / or switched between different return points via one or more valves.
  • the compressed air is supplied to a compressed air motor substantially at the operating pressure of the compressor, while its exhaust air is returned to the suction region or alternatively to the compressor element at a point where there is a pressure between suction and operating pressures the switchover between the two alternative feedbacks takes place via at least one valve.
  • the return line at the outlet of the compressed air motor is connected to the intake of the compressor, so that the maximum pressure difference is available for the compressed air engine between inlet and outlet. If this were not the case, then the compressed air motor would have to be unnecessarily large dimensions.
  • the return line is connected at the outlet of the air motor with a connection to the housing of the compressor element, at which an intermediate pressure prevails, preferably about 2 to 60% of the operating pressure.
  • the return of the exhaust air in already completed compression chambers in the compressor element is particularly advantageous because the supply of the compressed air motor takes place in an inner circuit, so that is substantially the entire intake flow of the compressor element as compressed air for the promotion of thick stock available.
  • the compressor element can therefore be dimensioned substantially smaller than would be the case in a return of the exhaust air of the compressed air motor in the environment or in the intake of the compressor element.
  • the compressed air is supplied to a compressed air motor substantially with the operating pressure of the compressor, while its exhaust air is fed into the intake of the compressor or in the environment or alternatively in the mixing vessel, wherein the switching between the two alternatives by at least a valve takes place.
  • the exhaust air of the compressed air motor is guided in the intake of the compressor or in the environment, so that the maximum pressure difference is available for the compressed air engine between inlet and outlet. If the exhaust air of the compressed air motor is returned to the suction of the Pompressors, then an internal circuit, so that no dusty ambient air, as usually arises when filling the mixing tank, must be cleaned by the inlet filter, resulting in a much longer service life of the filter. If the exhaust air discharged into the environment, z. B. via a blow-off silencer, so the return line can be omitted.
  • the exhaust air from the compressor is fed into the mixing tank, where there is a pressure between the suction and operating pressure of the compressor.
  • the operating pressure of the compressor sets in dependence on the total compressed air consumption and is divided into an advantageous self-adaptation to the respective delivery process in a pressure difference between the inlet and outlet of the air motor and a difference between the mixing vessel and the environment.
  • the exhaust air of the pressure motor is oil-containing, it can be passed through an oil separation element from which the separated oil is returned to the compressor's circuit before it enters the environment or before it enters the mixing tank.
  • a method for controlling and operating a mixing and conveying device in which the compressed air generated by the compressor during the mixing phase substantially only for supplying the or the agitator driving air motors is used and during the delivery phase both for the promotion of thick matter and for the supply of the or the agitator driving air motors.
  • compressed air motors can be used to drive the agitator, of which all but during the mixing phase, not all are supplied with compressed air during the delivery phase.
  • the pressure difference between the inlet and outlet of at least one air motor is influenced so that the speed and / or torque and / or the drive power of the agitator during the mixing phase are higher than in the delivery phase of.
  • the pressure difference between the inlet and outlet of the compressed air motors or during the mixing phase is set higher than in the delivery phase.
  • the pressure difference between the inlet and outlet of the compressed air or the motors can also be influenced by the fact that the exhaust air of the air motor or is passed during the conveying process in the mixing vessel. In this builds up a pressure whose height affects the pressure difference and thus the speed and / or torque and / or the drive line of the or the air motors.
  • the solution according to the invention allows greater design flexibility, because only an inlet and exhaust air line must be installed between the compressor and mixing tank. If the exhaust air of the compressed air motor in the delivery phase in the mixing vessel and in the mixing phase passed into the environment, then even only a compressed air line is required between the compressor and mixing unit, whereby in this embodiment, a conventional or only slightly modified construction site compressor can be used. This results in only minor restrictions for the relative arrangement of compressor and mixing tank. It also reduces maintenance and increases reliability. The vibrations and noise emissions of a switchable belt drive with cardan shaft are eliminated.
  • An internal combustion engine 1 drives via a clutch 2, the compressor element 3. This sucks in ambient air through the inlet valve 4, compresses them under injection of oil, which is supplied via the injection line 5, and conveys the compressed air-oil mixture via the pressure line 6 in the Oil separation tank 7. Here, most of the oil is separated from the air stream and collects in the lower part of the oil separation tank 7. From there it is pressed by the operating pressure through the cooler 8 back into the injection line 5.
  • a bypass 9 with a thermo valve 10 controls the final temperature of the oil or the compression end temperature.
  • a pressure line 11 compressed air is passed with operating pressure to the compressed air motor 12, which drives the agitator 13 in mixing tank 14.
  • a 2/2-way valve 15 is provided, with which the compressed air supply of the compressed air motor 12 can be released and interrupted.
  • the exhaust air of the compressed air motor is passed via an exhaust duct 16 to a 3/2-way valve 17.
  • the exhaust air is passed via line 18 into the inlet valve 4, in the other switching position in a return port 19 on the housing of the compressor element 3.
  • the return port 19 is provided with an opening in a housing portion of the compressor element 3 connected to the operating in the compression chambers, an intermediate pressure of about 50% of the operating pressure prevails.
  • the mixing vessel 14 can be charged via an opening 20 with mixed and conveyed material, closed by a cover 21 and set with the lid 21 under pressure.
  • the lid 21 is opened and the 2/2-way valve 22 is closed for the conveying air.
  • the compressor essentially generates compressed air for supplying the compressed air motor 12.
  • the 2/2-way valve 15 is open and releases the compressed air to the compressed air motor.
  • the 3/2-way valve 17 connects the outlet of the air motor with the inlet valve 4 of the compressor.
  • the air motor is supplied with the maximum pressure difference, so that it operates at a relatively high speed, relatively high torque and relatively high drive power.
  • the lid 21 Before switching to the delivery phase, the lid 21 must be closed.
  • Fig. 2 flows in the delivery phase compressed air from the oil separator 7 through a coalescing filter 23, the open 2/2-way valve 22 and the pressure lines 24 and 25 in the mixing vessel 14 and the delivery line 26.
  • the 3/2-way valve is in the other switching position and lets the exhaust air of the compressed air motor now flow into the return port 19 of the compressor element. There prevails an intermediate pressure, so that the compressed air motor is present a smaller pressure difference than during the mixing phase. This reduces both the compressed air consumption of the compressed air motor, as well as its speed, its torque and its drive power.
  • the compressed air for supplying the compressed air motor in the delivery phase in an inner circuit, consisting of the compressor element 3, the pressure line 11, the exhaust duct 16, the 3/2-way valve 17 and return port 19 on the compressor element 3, is guided, is essentially the entire intake flow of the compressor element to promote the thick material available.
  • Fig. 3 shows an alternative control scheme in which instead of the 2/2-way valve 15 and the 3/2-way valve 17, a 3/3-way valve 27 is used to control the air motor 12.
  • a 3/3-way valve 27 is used to control the air motor 12.
  • an additional adjustable throttle point 28 is shown in the line to the return port 19 through which a further adjustment of the speed, torque or drive power of the compressed air motor in the delivery phase is possible.
  • the valves 22 and 27 are shown in the switching position for idle or standstill of the mixing and conveying device.
  • a check valve 29 is arranged, which in the mixing phase, d. H. when the return line is closed by the valve 27 and no exhaust air of the compressed air motor 12 flows via the return port 19 into the compressor element, prevents pulsating flows between the compression chambers and the return line.
  • the air motor operates at the beginning of the mixing phase, when the mix still opposes the agitator a relatively high resistance, with lower speed and higher torque, than at the end of the mixing phase.
  • This adjustment results automatically by the course of the speed-torque curve of the air motor and proves to be advantageous over known drives, which operate during the mixing process at a substantially constant speed.
  • FIG. 5 shows an alternative embodiment, in which the compressed air is led directly from the compressor element 3 to the compressed air motor 12 both in the mixing phase and in the delivery phase.
  • the outlet of the compressed air motor 12 is connected to a 3/3-way valve 17.
  • the valve enables the position Standstill A, Mixing B and conveying C.
  • position A the exhaust air duct 16 is blocked and compressed air motor 12 is at a standstill.
  • position B the exhaust air of the compressed air motor 12 is guided through the exhaust duct 16 into the inlet valve 4.
  • the maximum possible pressure difference across the pneumatic motor 12 so that it operates at a relatively high speed, relatively high torque and relatively high drive power.
  • a bypass line 34 is provided with a throttle valve 35 between the inlet and outlet of the pneumatic motor 12, with which the pressure difference across the compressed air motor 12 can be limited.
  • the throttle valve 35 may be z. B. act to a minimum pressure valve that opens when exceeding a certain pressure difference and limits this to a certain value.
  • FIG. 6 shows a further possibility for interconnecting the components.
  • the exhaust duct 16 of the compressed air motor 12 is here analogous to Fig. 5 with a 3/3-way valve 17, which has the same switching capabilities connected.
  • the difference from the embodiment in Fig. 5 is that the mixing process (valve position B), the compressed air is given through the exhaust duct 16 via a blow-off muffler 33 directly into the environment.
  • an oil separation element 31 can be integrated into the exhaust air line 16.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Accessories For Mixers (AREA)
  • Preparation Of Clay, And Manufacture Of Mixtures Containing Clay Or Cement (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP01101596A 2000-01-27 2001-01-25 Verfahren und Vorrichtung zum Mischen und Fördern von Beton Expired - Lifetime EP1120216B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE20001472 2000-01-27
DE20001472U 2000-01-27
DE10033663 2000-07-11
DE10033663A DE10033663A1 (de) 2000-01-27 2000-07-11 Verfahren und Vorrichtung zum Mischen und Fördern von Beton

Publications (3)

Publication Number Publication Date
EP1120216A2 EP1120216A2 (de) 2001-08-01
EP1120216A3 EP1120216A3 (de) 2003-04-02
EP1120216B1 true EP1120216B1 (de) 2006-05-24

Family

ID=26006341

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01101596A Expired - Lifetime EP1120216B1 (de) 2000-01-27 2001-01-25 Verfahren und Vorrichtung zum Mischen und Fördern von Beton

Country Status (4)

Country Link
US (1) US6354726B2 (es)
EP (1) EP1120216B1 (es)
DE (1) DE50109837D1 (es)
ES (1) ES2266028T3 (es)

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GB0323120D0 (en) * 2003-10-03 2003-11-05 Carroll Autoload Ltd Mixing apparatus
US20050195681A1 (en) * 2004-02-18 2005-09-08 Henry Gembala Lightweight concrete mixer
ITVI20040226A1 (it) * 2004-09-24 2004-12-24 Peron Srl Unipersonale Dispositivo e macchina per lo stoccaggio e o il trasporto di un prodotto per la realizzazione di sottofondi per pavimentazione
US7766537B2 (en) * 2005-02-18 2010-08-03 Henry Gembala Lightweight foamed concrete mixer
CN102398310B (zh) * 2010-09-15 2013-03-06 中联重科股份有限公司 混凝土搅拌运输车的搅拌筒的操纵系统
KR101415890B1 (ko) * 2013-07-05 2014-08-06 강원대학교산학협력단 보통콘크리트에 공기를 혼입하고 소산하는 과정을 통해 고성능 콘크리트를 제조하는 고성능 콘크리트 제조장치 및 이의 제조방법
EP3065925B1 (en) * 2013-11-07 2021-07-21 Air Krete, Inc. A progressive bubble generating system used in making cementitous foam
DE202013010597U1 (de) * 2013-11-27 2014-02-20 Bms Bau-Maschinen-Service Ag Mörtelpumpe
CN106965318B (zh) * 2017-05-05 2019-04-09 重庆中兴商品混凝土有限责任公司 一种用于混凝土搅拌的搅拌设备
IT201900019031A1 (it) * 2019-10-16 2021-04-16 Atos Spa Dispositivo e metodo di controllo per la protezione di pompe a cilindrata fissa in circuiti idraulici

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US3237865A (en) * 1963-07-30 1966-03-01 Amlico Furnaspray Corp Apparatus for protecting refractory linings
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Also Published As

Publication number Publication date
DE50109837D1 (de) 2006-06-29
EP1120216A2 (de) 2001-08-01
US20010028600A1 (en) 2001-10-11
ES2266028T3 (es) 2007-03-01
EP1120216A3 (de) 2003-04-02
US6354726B2 (en) 2002-03-12

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