WO1994025757A1 - Kolbenpumpe - Google Patents
Kolbenpumpe Download PDFInfo
- Publication number
- WO1994025757A1 WO1994025757A1 PCT/EP1994/001384 EP9401384W WO9425757A1 WO 1994025757 A1 WO1994025757 A1 WO 1994025757A1 EP 9401384 W EP9401384 W EP 9401384W WO 9425757 A1 WO9425757 A1 WO 9425757A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston pump
- piston
- pump according
- connecting rod
- drive shaft
- Prior art date
Links
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 piston pump and in particular a piston pump for conveying viscous media, such as mortar, concrete, screeds, paints and plasters, both mineral structure and dispersion plasters and the like.
- viscous media such as mortar, concrete, screeds, paints and plasters, both mineral structure and dispersion plasters and the like.
- the piston 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 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, from a first point, to which the mortar is delivered or manufactured, to a second point, to a second point cher the mortar is sprayed onto a wall, for example.
- a typical known mortar pump has a delivery rate of approx. 20-50 1 / min and a delivery pressure of up to 40 bar.
- a hose and / or pipeline is used to convey it to the place of use. It is known in the prior art to design such a mortar pump as a double piston pump with two horizontally arranged cylinders lying next to one another. These pumps are driven by an electric or internal combustion engine, the speed of which is transmitted to a rotating drive shaft via a gear. On the drive shaft there are two drive cams which are offset by 180 ° to one another and move the pistons in the conveying direction via a piston rod during the pressure stroke. The piston moves back during the suction stroke via a counter spring designed as a
- the present invention is therefore based on the object of creating a reliably operating piston pump, in particular for conveying viscous media, which is of compact construction and which has a comparatively low weight.
- 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 grooved ball bearing, a needle bearing or a cylindrical roller bearing is preferably used as the rolling bearing.
- the guide device is designed such that a connecting pin is provided between the piston rod and the connecting rod, 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 the height of the guide groove are preferably plugged onto the journal, so that the outer ring can roll on the respective wall of the guide groove.
- This design creates a compact, simple and very reliable piston pump that is suitable for the transmission of high and highest torques.
- the piston pump according to the invention can be constructed with a different number of cylinders.
- a two-cylinder 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 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 cam-operated piston pump known in the prior art. This not only results in a considerable saving in material, but also in a significant simplification of the handling and transportation of corresponding pumps.
- the low weight also makes it possible to connect these mortar pumps directly to the silo outlet of a conventional plaster mortar silo.
- Figure 1 is a side view of a piston pump according to the invention.
- FIG. 2 shows a top view of the exemplary embodiment according to FIG. 1 without a drive motor
- FIG. 3 shows a partially sectioned illustration of the exemplary embodiment according to FIG. 1;
- FIGS. 1 and 2 shows a top view of the guide device in the exemplary embodiment according to FIGS. 1 and 2;
- FIG. 5 shows a side view of the guide device according to FIG. 4.
- FIG. 1 to 5 schematically show an exemplary embodiment of the present invention.
- This The 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 fastened to the disk piston and is pressed onto the cylinder wall by means of an expansion ring. Furthermore, valve devices for controlling the suction and pressure stroke and an overpressure safety device are provided. 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. Furthermore, it is possible to design the eccentric disc / connecting rod bore friction partner in such a way that a low coefficient of friction and low wear is achieved. This can e.g. done by one of the two friction partners made of a suitable material, for example a bearing bronze, or coated with it. Furthermore, a friction-reducing layer such as a Teflon layer can also be used.
- FIG. 3 Storage by means of a roller bearing is also preferred, as shown in FIG. 3.
- 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 loaded only radially, but not axially, the pressing forces are sufficient to bring about 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 displacing one another. the.
- a grooved ball bearing was chosen as the roller bearing, since this can absorb axial forces and thus can reliably prevent axial displacement of the individual parts relative to one another.
- a grooved ball bearing instead of a grooved ball bearing, however, a needle bearing, a cylindrical roller bearing or, in the case of high loads, a pendulum 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 construction, 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 configuration, since the pump can thereby be finished as a whole with a flat construction.
- This design also has the advantage that the transmission of force 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 guidance of the connecting rod by the guide device will now be described in detail with reference to FIGS. 4 and 5.
- 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 region and also has a bore 43 into which the pin 41 is firmly pressed.
- 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 firmly attached to the Pin 41 is pressed, 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 support surface on which the outer ring of the roller bearings 45, 46 can roll. For this it is necessary that the distance a (see FIG. 5) of the upper to the lower guide tracks 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, with the double piston pump as a whole according to the exemplary embodiment explained here four plates are required.
- a slot 58 is provided in each plate, the length 1 and height a of which correspond to 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 to work at a speed of 50 min " and a delivery volume of 20 to 40 1 / min. With this design, a drive torque of up to approximately 700 Nm required, but other values are also possible, depending on the design and application.
- An electric motor an internal combustion engine, preferably a diesel engine or a pneumatically operated engine (e.g. in a potentially explosive environment) 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. In an electric motor, this can be done continuously by changing the frequency or, in the case of a DC machine, by a change in 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 gearwheels are brought into engagement with one another in different ways or are connected to a shaft in a rotatable or rotationally fixed manner in order to achieve different gear ratios. Furthermore, it is also possible to use a transmission 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 feather key shown there, but on the drive shaft two or to put on more pulleys with different diameters, and to provide corresponding 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 piston pump can be attached to a towing vehicle, for example, or pushed in a simple manner. It is also possible to provide a holding device on the housing of the piston pump with which the piston pump can be arranged directly at the outlet of a ready-mixed mortar container, for example a silo. This allows the mortar to be conveyed rationally to the respective application site.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Steroid Compounds (AREA)
- Saccharide Compounds (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP94915567A EP0697066B1 (de) | 1993-05-02 | 1994-05-02 | Kolbenpumpe |
DE59401274T DE59401274D1 (de) | 1993-05-02 | 1994-05-02 | Kolbenpumpe |
PL94311302A PL173575B1 (pl) | 1993-05-02 | 1994-05-02 | Pompa tłokowa |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DEP4314132.3 | 1993-05-02 | ||
DE4314132A DE4314132A1 (de) | 1993-05-02 | 1993-05-02 | Kolbenpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1994025757A1 true WO1994025757A1 (de) | 1994-11-10 |
Family
ID=6486736
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1994/001384 WO1994025757A1 (de) | 1993-05-02 | 1994-05-02 | Kolbenpumpe |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP0697066B1 (de) |
AT (1) | ATE146258T1 (de) |
CZ (1) | CZ253495A3 (de) |
DE (2) | DE4314132A1 (de) |
PL (1) | PL173575B1 (de) |
WO (1) | WO1994025757A1 (de) |
Families Citing this family (8)
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 |
US20180030967A1 (en) * | 2016-07-29 | 2018-02-01 | 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 |
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 |
Citations (3)
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. |
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 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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. |
IT1213730B (it) * | 1987-11-23 | 1989-12-29 | Soilmec Spa | Pompa idraulica a stantuffo tuffante aspirante-premente |
-
1993
- 1993-05-02 DE DE4314132A patent/DE4314132A1/de not_active Withdrawn
-
1994
- 1994-05-02 WO PCT/EP1994/001384 patent/WO1994025757A1/de not_active Application Discontinuation
- 1994-05-02 AT AT94915567T patent/ATE146258T1/de not_active IP Right Cessation
- 1994-05-02 PL PL94311302A patent/PL173575B1/pl unknown
- 1994-05-02 CZ CZ952534A patent/CZ253495A3/cs unknown
- 1994-05-02 EP EP94915567A patent/EP0697066B1/de not_active Expired - Lifetime
- 1994-05-02 DE DE59401274T patent/DE59401274D1/de not_active Expired - Fee Related
Patent Citations (3)
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. |
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 |
Also Published As
Publication number | Publication date |
---|---|
ATE146258T1 (de) | 1996-12-15 |
PL311302A1 (en) | 1996-02-05 |
EP0697066A1 (de) | 1996-02-21 |
EP0697066B1 (de) | 1996-12-11 |
CZ253495A3 (en) | 1996-10-16 |
DE59401274D1 (de) | 1997-01-23 |
DE4314132A1 (de) | 1994-11-03 |
PL173575B1 (pl) | 1998-03-31 |
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