EP0697066B1 - Kolbenpumpe - Google Patents

Kolbenpumpe Download PDF

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Publication number
EP0697066B1
EP0697066B1 EP94915567A EP94915567A EP0697066B1 EP 0697066 B1 EP0697066 B1 EP 0697066B1 EP 94915567 A EP94915567 A EP 94915567A EP 94915567 A EP94915567 A EP 94915567A EP 0697066 B1 EP0697066 B1 EP 0697066B1
Authority
EP
European Patent Office
Prior art keywords
thick material
material pump
pump according
piston
connecting rod
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
EP94915567A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0697066A1 (de
Inventor
Friedrich Schwald
Josef Schwall
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0697066A1 publication Critical patent/EP0697066A1/de
Application granted granted Critical
Publication of EP0697066B1 publication Critical patent/EP0697066B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/146—Piston-rod guiding arrangements

Definitions

  • the present invention relates to a thick matter pump for conveying viscous media, such as mortar, concrete, screeds, paints and plasters, both mineral structure and dispersion plasters and the like.
  • the thick matter pump according to the invention is described below in relation to its use as a mortar pump. However, it is pointed out that the design according to the invention can also be used for thick matter pumps which are provided for conveying other media.
  • Mortar pumps are used to move mortars, such as cement mortar, concrete spray mortar, basic plaster mortar, insulating plaster mortar, fire protection mortar and the like Wall is sprayed to promote.
  • a typical known mortar pump has a delivery rate of approx. 20-50 1 / min and a delivery pressure from up to 40 bar.
  • a hose and / or pipeline is used to convey it to the place of use.
  • the present invention is therefore based on the object of creating a reliably working thick matter pump for conveying viscous media, which is simple, compact and of comparatively low weight and works very reliably.
  • a pair of cams and tappets is not used, as in the prior art, but rather a connecting rod designed and mounted in a special way.
  • a circular eccentric disk is arranged on a drive shaft, which is driven by a suitable motor via a gearbox, on which a connecting rod is rotatably mounted.
  • the other end of the connecting rod is connected to the piston rod of the pump piston and is guided along the (fictitious) axis of the pump cylinder via a guide device.
  • This structure has the advantage that the power transmission between the eccentric disc (which has a relatively large diameter) and the connecting rod takes place with a comparatively low surface pressure, so that on the one hand the wear is considerably reduced and on the other hand the structure can be made compact.
  • the spring devices etc. required in the prior art can be completely dispensed with.
  • the connecting rod is rotatably mounted on the eccentric disc preferably by means of a roller bearing.
  • a deep groove ball bearing, a needle bearing or a cylindrical roller bearing is preferably used as the rolling bearing.
  • a plain bearing can also be used instead of the roller bearing.
  • the guide device is designed so that a connecting pin between the piston rod and the connecting rod is provided, the (fictitious) axis of which is arranged perpendicular to the cylinder axis and which is guided in guide grooves.
  • Rolling bearings whose outer diameter is slightly smaller than that are preferably plugged onto the journal Height of the guide groove so that the outer ring can roll on the respective wall of the guide groove.
  • This design creates a compact, simple and very reliable thick matter pump which is suitable for the transmission of high and highest torques.
  • the thick matter pump according to the invention can be constructed with a different number of cylinders.
  • a two-cylinder thick matter pump is particularly preferred, since a relatively uniform volume flow is achieved here in conjunction with the elastic properties of the delivery hose that is usually used.
  • a disk piston is usually used, on which a sealing sleeve is attached, which is made of leather, rubber or the like.
  • the thick matter pump is preferably designed as a single stroke pump, which means that material is pressed into the delivery line only when the piston moves away from the drive shaft.
  • the weight could be reduced by more than half compared to the token-operated thick matter pump known in the prior art. This not only results in a considerable saving in material, but also a significant simplification in the handling and transport of corresponding thick matter pumps.
  • the low weight also makes it possible to connect these mortar pumps directly to the silo outlet of a conventional plaster mortar silo.
  • This exemplary embodiment is a two-cylinder mortar pump which has a housing 1 in which the pistons and a transmission device are arranged.
  • the two cylinders 3, 4 are arranged horizontally next to one another (in the position of use of the device) and each have a (fictitious.) Cylinder axis 6 and 7, respectively.
  • the (fictitious) cylinder axis of the cylindrical piston rod 9 coincides with the cylinder axis of the cylinders 6 and 7, respectively.
  • a sealing sleeve is attached to the disc piston, which is pressed onto the cylinder wall by means of an expansion ring. Furthermore, there are valve devices for controlling the suction and pressure stroke and an overpressure safety device intended. However, since the aforementioned devices are all known in the prior art, these parts are neither shown nor explained in detail.
  • a drive shaft 12 is mounted in bearings 13, 14, which are preferably designed as roller bearings.
  • a first eccentric disk 15 and a second eccentric disk 16 are fastened on the drive shaft 12. Both eccentric disks are designed as circular disks and are attached to the drive shaft 12 in such a way that an eccentricity "e” results between the (fictitious) axis of rotation 20 of the drive shaft 12 and the center 21 of the eccentric disks.
  • the two eccentric disks are offset from one another by 180 °.
  • a connecting rod 24, 25 is attached to each of the eccentric disks, both connecting rods having a circular recess 27, as can be seen in FIG. 1.
  • the connection between the connecting rods 24, 25 and the eccentric discs 15, 16 is such that the connecting rod can easily turn against the two eccentric discs even under high loads.
  • This rotatability can be achieved by using a plain bearing, which preferably enables a hydrodynamic or a hydrostatic or a mixed hydrodynamic / hydrostatic bearing of the connecting rod on the eccentric disc. It is also possible to design the friction partner eccentric disc / connecting rod bore in such a way that a low coefficient of friction and low wear is achieved. This can be done, for example, by manufacturing or coating one of the two friction partners from a suitable material, for example a bearing bronze. Furthermore, a friction-reducing layer such as a Teflon layer can also be used.
  • FIG. 3 Storage by means of a roller bearing, as shown in FIG. 3, is also preferred.
  • the inner ring 31 of a roller bearing, generally designated 30, is pressed onto the eccentric disk (eccentric disk 17 is shown).
  • the outer ring 32 of this roller bearing is pressed into the bore 27 of the connecting rod 25. Since the connection between the eccentric disc and the connecting rod is only loaded radially, but not axially, the pressing forces are sufficient to effect a secure connection between the eccentric disc and the connecting rod. If this should cause problems in individual cases, it is also possible to provide appropriate fastening devices, for example appropriately designed snap rings, in order to prevent the individual parts from axially shifting relative to one another.
  • a grooved ball bearing was chosen as the rolling bearing, since this can absorb axial forces and thus can reliably prevent axial displacement of the individual parts relative to one another.
  • a needle roller bearing a cylindrical roller bearing or, in the case of high loads, a spherical roller bearing can also be used.
  • the eccentric discs must be arranged on the drive shaft 12 in a rotationally fixed manner. This can be done with a feather key, which is arranged in a groove in the drive shaft and engages in a corresponding groove in the eccentric disc. With a feather key, however, another shaft-hub connection (known in the prior art), for example a spline, can be used. In the interest of a simple structure, it is also possible to weld the eccentric disks to the drive shaft, but precautions must then be taken in order to be able to install the drive shaft 12 with the bearings 13 and 14 in the housing 1.
  • the axis of the drive shaft 12 is offset in height with respect to the longitudinal axes 6, 7 of the cylinders 3, 4, the offset (cf. FIG. 1) corresponding to the distance "h".
  • this offset has advantages with regard to the spatial design, since the thick matter pump can thereby be finished as a whole with a flat construction.
  • this design has the advantage that the power transmission from the connecting rod to the piston rod takes place at a more favorable angle during the pressure stroke, so that the Proportion of the transverse force directed perpendicular to the cylinder axis is lower.
  • the connecting rod In its front area facing away from the eccentric disc, the connecting rod has a bore 40 in which a pin 41 is movably guided.
  • the piston rod 9 is fork-shaped in its front area and also has a bore 43 into which the pin 41 is pressed firmly.
  • the pin 43 is extended beyond the piston rod 9 on both sides and carries a roller bearing 45 and 46 at its respective ends 41a, 41b.
  • the roller bearings 45, 46 each have an inner ring which is pressed firmly onto the pin 41, and an outer ring.
  • Balls are preferably used as rolling elements, but it is also possible to use cylindrical rollers, pendulum rollers or needles. The use of plain bearings is also advantageous.
  • An upper guide track 50 and a lower guide track 52, 53 are arranged on each side of each connecting rod. These guideways form an essentially flat bearing surface on which the outer ring of the roller bearings 45, 46 can roll. This requires that the distance a (see Fig. 5) of the upper to the lower guideways is at least slightly larger than the outer diameter of the roller bearings 45, 46.
  • the length "1" of the guideways is dimensioned such that the roller bearings 45, 46 rest on the respective guideways during the entire stroke of the piston.
  • a plate 56 is provided which is fastened in the housing parallel to the plane of the connecting rod 24, a total of four plates being required in the double thick matter pump according to the exemplary embodiment explained here.
  • a slot 58 is provided in each plate, the length 1 and height a of which meet the criteria discussed above.
  • the guideways can also be designed in other ways, for example by appropriately designed U-bars, etc.
  • the support of the transverse forces resulting from the movement of the bolt via a roller bearing is the preferred embodiment of the invention.
  • the exemplary embodiment illustrated with reference to FIGS. 1 to 5 is intended for a speed of 50 min -1 and a delivery volume of 20 to 40 l / min work. With this design, a drive torque of up to approx. 700 Nm is required. Depending on the design and application, other values are also possible.
  • An electric motor an internal combustion engine, preferably a diesel engine or a pneumatically operated motor (e.g. in a potentially explosive atmosphere) is used for the drive, the output speed of which, if necessary, is reduced to the input speed via a suitable gear.
  • the drive can be designed to be variable in speed. There are several options for changing the speed:
  • a first possibility is to influence the output speed of the motor in a corresponding manner.
  • this can be effected continuously by changing the frequency or, in the case of a DC machine, by changing the excitation voltage.
  • a stepped change in speed can also be brought about in an electric motor by changing the pole.
  • the speed change can also be implemented by means of a manual transmission, in that gears are brought into engagement with one another in different ways, or are rotatable or non-rotatable with a wave to achieve different translations. Furthermore, it is also possible to use a gear with a continuously variable transmission ratio (adjusting gear) both in cooperation with an electric motor and with an internal combustion engine.
  • the drive shaft is not flanged directly to the motor, as is indicated in FIG. 2 by the drive shaft and the key shown there, but with two or more pulleys on the drive shaft to put on different diameters, and to provide appropriate pulleys on the drive shaft of the motor.
  • the speed can then be changed easily by moving the belt from one pulley to the other.
  • a corresponding chain drive can also be used.
  • the housing can be provided with wheels so that the thick matter pump can be attached to a towing vehicle, for example, or pushed in a simple manner.
  • a holding device on the housing of the thick matter pump, with which the thick matter pump directly at the outlet of a ready-mixed mortar container, For example, a silo can be arranged. This allows the mortar to be conveyed efficiently to the respective application site.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Saccharide Compounds (AREA)
  • Steroid Compounds (AREA)
EP94915567A 1993-05-02 1994-05-02 Kolbenpumpe Expired - Lifetime EP0697066B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4314132 1993-05-02
DE4314132A DE4314132A1 (de) 1993-05-02 1993-05-02 Kolbenpumpe
PCT/EP1994/001384 WO1994025757A1 (de) 1993-05-02 1994-05-02 Kolbenpumpe

Publications (2)

Publication Number Publication Date
EP0697066A1 EP0697066A1 (de) 1996-02-21
EP0697066B1 true EP0697066B1 (de) 1996-12-11

Family

ID=6486736

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94915567A Expired - Lifetime EP0697066B1 (de) 1993-05-02 1994-05-02 Kolbenpumpe

Country Status (6)

Country Link
EP (1) EP0697066B1 (pl)
AT (1) ATE146258T1 (pl)
CZ (1) CZ253495A3 (pl)
DE (2) DE4314132A1 (pl)
PL (1) PL173575B1 (pl)
WO (1) WO1994025757A1 (pl)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109496250A (zh) * 2016-07-29 2019-03-19 瓦格纳喷涂技术有限公司 对准流体输送系统中的往复运动
CN110067368A (zh) * 2019-03-27 2019-07-30 林清武 一种应用滚辊径向运动的无人机外墙面刷漆装置

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10348457A1 (de) * 2003-10-14 2005-05-19 Helmut Obieglo Excentergetriebe für Hochleistungsverdrängungsmaschinen
CN101876205B (zh) * 2009-10-29 2014-04-16 陈青松 一种粉刷机驱动装置
DE102012102615B4 (de) 2011-03-30 2023-05-17 Minebea Mitsumi Inc. Heizkörperthermostat
WO2012155068A2 (en) * 2011-05-11 2012-11-15 Nereid S.A. A positive displacement multi-cyclinder pump
DE102014017242B4 (de) 2014-02-20 2019-01-03 Tankol Gmbh Verdrängerpumpe für hohe Drücke bei nicht schmierenden Medien
CN112160560B (zh) * 2020-11-16 2021-04-27 深圳中大建筑装饰有限公司 一种装修用墙面均匀滚涂式涂漆装置
CN113513461A (zh) * 2021-05-31 2021-10-19 广东天物新材料科技有限公司 水泵结构和包含该水泵结构的蒸汽装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191111507A (en) * 1911-05-12 1912-06-12 Still & Sons Ltd W M Speed Reduction Gear for Driving a Reciprocating Member from a Rotary Member, specially applicable for Operating Dust Extractors.
DE618484C (de) * 1934-03-27 1935-09-09 Georg Domina Kolbenpumpe fuer steinhaltigen Beton
US2133048A (en) * 1936-11-28 1938-10-11 Oil Well Supply Co Pump
US2238944A (en) * 1938-05-24 1941-04-22 Ransome Concrete Machinery Co Concrete conveying apparatus
US2239853A (en) * 1939-06-14 1941-04-29 Lource Charles Harold Steel reciprocating pump
US2362525A (en) * 1943-01-13 1944-11-14 Emsco Derrick & Equip Co Slush pump
FR1378242A (fr) * 1963-10-03 1964-11-13 Perfectionnements aux machines à piston
DE1900884U (de) * 1964-07-16 1964-09-17 Carl Platz G M B H Mehrfach kolbenpumpe.
US4067666A (en) * 1976-07-19 1978-01-10 Whiteman Manufacturing Company Concrete pumping apparatus
US4494415A (en) * 1982-03-25 1985-01-22 Hydra-Rig, Incorporated Liquid nitrogen pump
IT1213730B (it) * 1987-11-23 1989-12-29 Soilmec Spa Pompa idraulica a stantuffo tuffante aspirante-premente

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109496250A (zh) * 2016-07-29 2019-03-19 瓦格纳喷涂技术有限公司 对准流体输送系统中的往复运动
US12140140B2 (en) 2016-07-29 2024-11-12 Wagner Spray Tech Corporation Aligning reciprocating motion in fluid delivery systems
CN110067368A (zh) * 2019-03-27 2019-07-30 林清武 一种应用滚辊径向运动的无人机外墙面刷漆装置

Also Published As

Publication number Publication date
EP0697066A1 (de) 1996-02-21
DE4314132A1 (de) 1994-11-03
WO1994025757A1 (de) 1994-11-10
ATE146258T1 (de) 1996-12-15
DE59401274D1 (de) 1997-01-23
PL173575B1 (pl) 1998-03-31
CZ253495A3 (en) 1996-10-16
PL311302A1 (en) 1996-02-05

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