CA2013356A1 - Two cylinder solids handling pump with piston reservoir - Google Patents
Two cylinder solids handling pump with piston reservoirInfo
- Publication number
- CA2013356A1 CA2013356A1 CA002013356A CA2013356A CA2013356A1 CA 2013356 A1 CA2013356 A1 CA 2013356A1 CA 002013356 A CA002013356 A CA 002013356A CA 2013356 A CA2013356 A CA 2013356A CA 2013356 A1 CA2013356 A1 CA 2013356A1
- Authority
- CA
- Canada
- Prior art keywords
- storage
- piston
- feed
- cylinder
- thick matter
- 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.)
- Abandoned
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
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
-
- 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
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
-
- 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
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
- F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Refuse Collection And Transfer (AREA)
- Consolidation Of Soil By Introduction Of Solidifying Substances Into Soil (AREA)
- Fluid-Pressure Circuits (AREA)
- Display Devices Of Pinball Game Machines (AREA)
- Medicines Containing Antibodies Or Antigens For Use As Internal Diagnostic Agents (AREA)
- Dram (AREA)
- Details Of Reciprocating Pumps (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
Abstract
Abstract The invention relates to a two-cylinder thick matter pump having a pis-ton storage which is filled during the thick matter feed with the feed cylinders and evacuated by the hydrocontrolled storage piston into the feed pipe between the strokes of the feed pistons to reduce the pressure drop and the undelivered amount in the feed pipe. The inventive proposal is that the hydrocontrol (2) of the storage piston (10) is served by a working piston (8) to be acted upon hydraulically on both sides, that is controlled with the feed cylinders and whose limits of travel, with the limits of travel of the storage piston ( 10), are fixed on the storage driv-ing cylinder (7) when the storage cylinder (4) is fully evacuated and is filled (Fig. 1).
Description
The present invention relates to a two-cylinder thicl; matter pump ha~ing a piston storage accordin~ to the preamble of claim 1.
With its piston storage the inventive two-c~linder thick matter pump compensates pressure and volume fluctuations in the feed pipe that arise between the strokes of the cooperating feed c~linders. These fluctuations.
that disturb the uniformity factor of the feed, are, for constructional reasons, larger in the case of mechanicall~ controlled feed cylinders, e.g.
feed c~linders whose pistons are driven with a crankshaft, than in the case of hydraulicall~ driven feed pistons, which allow the piston s :;rokes to be covered but cannot prevent pressure and volume fluctuations in the f eed pipe, either, when the piston of the feeding c~linder is switched over to the suction stroke and the piston of the feed c~-linder sucl;ing out of the prefilling vessel of the pump is switched over to the pressure stroke. In this switch-over phase the piston storage presses thici; matter into the feed pipe, thereb~- at least partly compensating the pressure and volume loss of the sw-itch-over phase.
The inventive two-cylinder thick matte:r pumps thus differ from pis-ton pumps ~h hich aim to improve the uniformit~v factor of the thick mat-ter feed with at least three or even more feed cylinders, because with such pump constructions thick matter must be sucl;ed out of the prefilling vessel with the second or additional feed c~linders, while with piston storages the additional feed volume passes from the feed pipe into the storage and from there back into the feed pipe during the switch-over phase of the feed c~linders. Thick matter pumps having more than two feed c~linders to compensate volume and pressure fluctuations in order to increase the uniformity factor in the feed pipe can reduce the pressure fluctuations at the e~pense of a simple mechanical construction and sim-ple control means, with a considerable increase in technical effort. but they cannGt avoid speed droops in the feed.
The invention relates in particular to thick matter pumps which feed sludge. This may be turbid coal slime for acting upon furnaces with fossil D ~
~, fuels ! sewage sludge. mortar and plaster compounds or the like. but par-ticularl~- media which tend to solidify in the rest phase of their feed and thus ca~e on the walls of feed paths that at times conduct no feed stream. Such media are above all hydraulically setting media and sludges with pozzolanic properties. It is often important to feed such substances at a high uniformity factor because pressure and volume fluctuations in following installations. e.g. in furnaces, cause difficulties or lead to con-siderable dynamic stresses, which is the case in particular wlth high lifts.
To compensate such fluctuations the invention employs a piston stor-age. Piston storages generally use a cylinder built onto the feed pipe and opening into it on one side while its other end is closed b~ a movable piston. Such piston storages differ from bubble storages by their piston, and from air domes by the fact that the pumping medium is closed off in the storage by a firm but movable wall. Piston storages permit virtually any feed pressures and can therefore be used together with pumps that reach considerable lifts.
The invention starts with a known thick matter pump $hat works with a piston storage. The storage piston works with its side facing awa~-from the pumping medium on a pressure cushion consisting of a high-pressure gas. During the pressure stroke of the feed cylinders the storage cylinder fills up with pumping medium from the feed pipe, whereby the storage piston compresses the gas cushion. AS soon as the pressure col-lapses, or drops, in the feed pipe in the switch-over phase, the high-pressure gas cushion urges the piston in the opposite direction and press-es pumping medium out of the storage cylincler into the feed pipe. Such a piston storage can in fact improve the uniformity fac$ors of thicl; matter feed.
However, the disadvantage is that a complete evacuation of the stor-age cylinder is not ensured. This has various causes! but the consequence is that pumping medium tending to cake or harden prematurely impairs the storage relatively quickly and eventually blocks it. This not onl;Y re-duces the uniformity factor of the feed b~lt also results in disturbances in the feed which are relatively difficult to eliminate.
The invention is based on the problem of improving the uniformity factor of feed in a two-cylinder thicl~ matter pump having the general construction described at the outset, said irnprovement functioning per-fectly even with a pumping medium that tends to harden prematurely or cake on parts of the feed pipe.
,, . . . , ... . ~ .... . .... . ... .. . . ...... . . .. . . . . .
With its piston storage the inventive two-c~linder thick matter pump compensates pressure and volume fluctuations in the feed pipe that arise between the strokes of the cooperating feed c~linders. These fluctuations.
that disturb the uniformity factor of the feed, are, for constructional reasons, larger in the case of mechanicall~ controlled feed cylinders, e.g.
feed c~linders whose pistons are driven with a crankshaft, than in the case of hydraulicall~ driven feed pistons, which allow the piston s :;rokes to be covered but cannot prevent pressure and volume fluctuations in the f eed pipe, either, when the piston of the feeding c~linder is switched over to the suction stroke and the piston of the feed c~-linder sucl;ing out of the prefilling vessel of the pump is switched over to the pressure stroke. In this switch-over phase the piston storage presses thici; matter into the feed pipe, thereb~- at least partly compensating the pressure and volume loss of the sw-itch-over phase.
The inventive two-cylinder thick matte:r pumps thus differ from pis-ton pumps ~h hich aim to improve the uniformit~v factor of the thick mat-ter feed with at least three or even more feed cylinders, because with such pump constructions thick matter must be sucl;ed out of the prefilling vessel with the second or additional feed c~linders, while with piston storages the additional feed volume passes from the feed pipe into the storage and from there back into the feed pipe during the switch-over phase of the feed c~linders. Thick matter pumps having more than two feed c~linders to compensate volume and pressure fluctuations in order to increase the uniformity factor in the feed pipe can reduce the pressure fluctuations at the e~pense of a simple mechanical construction and sim-ple control means, with a considerable increase in technical effort. but they cannGt avoid speed droops in the feed.
The invention relates in particular to thick matter pumps which feed sludge. This may be turbid coal slime for acting upon furnaces with fossil D ~
~, fuels ! sewage sludge. mortar and plaster compounds or the like. but par-ticularl~- media which tend to solidify in the rest phase of their feed and thus ca~e on the walls of feed paths that at times conduct no feed stream. Such media are above all hydraulically setting media and sludges with pozzolanic properties. It is often important to feed such substances at a high uniformity factor because pressure and volume fluctuations in following installations. e.g. in furnaces, cause difficulties or lead to con-siderable dynamic stresses, which is the case in particular wlth high lifts.
To compensate such fluctuations the invention employs a piston stor-age. Piston storages generally use a cylinder built onto the feed pipe and opening into it on one side while its other end is closed b~ a movable piston. Such piston storages differ from bubble storages by their piston, and from air domes by the fact that the pumping medium is closed off in the storage by a firm but movable wall. Piston storages permit virtually any feed pressures and can therefore be used together with pumps that reach considerable lifts.
The invention starts with a known thick matter pump $hat works with a piston storage. The storage piston works with its side facing awa~-from the pumping medium on a pressure cushion consisting of a high-pressure gas. During the pressure stroke of the feed cylinders the storage cylinder fills up with pumping medium from the feed pipe, whereby the storage piston compresses the gas cushion. AS soon as the pressure col-lapses, or drops, in the feed pipe in the switch-over phase, the high-pressure gas cushion urges the piston in the opposite direction and press-es pumping medium out of the storage cylincler into the feed pipe. Such a piston storage can in fact improve the uniformity fac$ors of thicl; matter feed.
However, the disadvantage is that a complete evacuation of the stor-age cylinder is not ensured. This has various causes! but the consequence is that pumping medium tending to cake or harden prematurely impairs the storage relatively quickly and eventually blocks it. This not onl;Y re-duces the uniformity factor of the feed b~lt also results in disturbances in the feed which are relatively difficult to eliminate.
The invention is based on the problem of improving the uniformity factor of feed in a two-cylinder thicl~ matter pump having the general construction described at the outset, said irnprovement functioning per-fectly even with a pumping medium that tends to harden prematurely or cake on parts of the feed pipe.
,, . . . , ... . ~ .... . .... . ... .. . . ...... . . .. . . . . .
2~ 33~3 This problem is solved according to the invention by the features of clalm 1. Further features of the invention are the subject of the sub-claims.
Since the storage piston is driven by a hydraulic working cylinder accordin~ to the invention, one can dispense with a gas cushion that loads the storage pis$on, replacing it by the storage driving piston di-rectly connected therewitht whose forced control with the feed cylinders of the thick matter pump ensures that the storage piston is returnsd in the storage cylinder for the storage to be filled, in the pumping phase, and presses the storage content in the opposite direction into the feed pipe, in the switch-over phase. The limits of travel of the storage driving piston are hydraulicall~r fixed and therefore also determine the limits of travel of the storage piston. whose outer extreme position in the storaga cvlinder is selected in such a way that the storage is completely evacuat-ed. Since these limits of travel are forced in each switch-over phase, the pumping medium contained in the storage can at no time solldify and block the storage.
The hydraulic medium required for supplying energy to the storage driving cylinder can come from the pressure generator of the thick mat-ter pump whose feed cylinders are directly driven by hydraulic working cylinders. This considerably simplifies the storage operation, which re-quires no external source of pressure gas. The forced control of the stor-age driving piston also eliminates the irregularities in the storage piston position which come about in particular when the lifting times of the îeed c~linders are variable, which is the case in many thick matter pumps for regulating the delivery.
Claim 2 proposes an embodiment of the invention which ensures b~r hydraulic means that the storage cylinder is briefly evacuated in accord-ance with the duration of the switch-over phase, and also makes it pos-sible to fill the storage cylinder in the pumping phase following the switch-over phase in such a way that the pumping medium penetrating into the storage cylinder does not cause a pressure drop in the feed pipe, which is effected b~r accordingly prolonging the time of filling of the storage up to a maximum time! that may correspond to the pumping phase but is selectable in individual cases. One thus obtains a virtually complete uniformity of the feed stream. The brief evacuation of the storage is ef-fected with the aid of the high-pressure hydraulic working medium of the storage drive, while the longer duration of the storage filling is effected 2~ 133~
, by regulating the stream into the storage driving piston ring space! in which the hydraulic pressure acts in the same direction as the pressure of the pumping medium on the storage piston and returns the storage driving piston. The storage piston return time can be regulated with the features of claim ~.
The embodiment of the invention as in claim 4 permits control of the hydraulic pressure on the piston side in the storage driving cylinder, and thus a fixing of the evacuation time of the storage cylinder. The hydrau-lic accumulator provided for this purpose also allows for compensation of wrong amounts of the hydraulic working medium for the storage opera-tion.
The above-described regulation of the filling time of the storage cyl-inder is made possible hydraulically in a simple way with the features of claim 5. The adjustment is performed by hand, which offers the advantage that the thick matter pump can be adapted at any time to the conditions of a specific case of application, in particular to changing preconditions which may be created by the particular pumping medium.
Claim 6, however, offers the advantage that an automatic adjustment of the flow control valve allows for the storage filling to be adapted to changing evacuation times of the feed cylinders, which OCCUI' particularly when the thick matter pump is adjusted to different deliveries.
The invention shall be e~plained in more detail in the following with reference to an exemplary embodiment that is shown in the connection diagrams, of which Fig. 1 shows schematically, i.e. free from all details that are unnec-essary for understanding the invention, the connection state during evac-uation of the piston storage into the feed pipe during the switch-over phase of the feed cylinders, and Fig. 2 shows the connection state during the filling of the piston storage out of the feed pipe in the pumping phase of the feed cylinders.
The connection to the hydraulic pressure generator of the hydrauli-cally driven feed cylinders of the thick matter pump is shown at 1.
Switch signals are present at 2 for the limits of travel of the pistons in the feed cylinders or in hydraulic driving cylinders of the thick matter pump.
The feed cylinders of the thick matter pump (not shown) work alter-natingly on a feed pipe 3, one of the feed cylinders sucking the thick matter out of a prefilling vessel of the pump, while the other feed cylin-.. . .. .. . .. . . .. . . . ..
Since the storage piston is driven by a hydraulic working cylinder accordin~ to the invention, one can dispense with a gas cushion that loads the storage pis$on, replacing it by the storage driving piston di-rectly connected therewitht whose forced control with the feed cylinders of the thick matter pump ensures that the storage piston is returnsd in the storage cylinder for the storage to be filled, in the pumping phase, and presses the storage content in the opposite direction into the feed pipe, in the switch-over phase. The limits of travel of the storage driving piston are hydraulicall~r fixed and therefore also determine the limits of travel of the storage piston. whose outer extreme position in the storaga cvlinder is selected in such a way that the storage is completely evacuat-ed. Since these limits of travel are forced in each switch-over phase, the pumping medium contained in the storage can at no time solldify and block the storage.
The hydraulic medium required for supplying energy to the storage driving cylinder can come from the pressure generator of the thick mat-ter pump whose feed cylinders are directly driven by hydraulic working cylinders. This considerably simplifies the storage operation, which re-quires no external source of pressure gas. The forced control of the stor-age driving piston also eliminates the irregularities in the storage piston position which come about in particular when the lifting times of the îeed c~linders are variable, which is the case in many thick matter pumps for regulating the delivery.
Claim 2 proposes an embodiment of the invention which ensures b~r hydraulic means that the storage cylinder is briefly evacuated in accord-ance with the duration of the switch-over phase, and also makes it pos-sible to fill the storage cylinder in the pumping phase following the switch-over phase in such a way that the pumping medium penetrating into the storage cylinder does not cause a pressure drop in the feed pipe, which is effected b~r accordingly prolonging the time of filling of the storage up to a maximum time! that may correspond to the pumping phase but is selectable in individual cases. One thus obtains a virtually complete uniformity of the feed stream. The brief evacuation of the storage is ef-fected with the aid of the high-pressure hydraulic working medium of the storage drive, while the longer duration of the storage filling is effected 2~ 133~
, by regulating the stream into the storage driving piston ring space! in which the hydraulic pressure acts in the same direction as the pressure of the pumping medium on the storage piston and returns the storage driving piston. The storage piston return time can be regulated with the features of claim ~.
The embodiment of the invention as in claim 4 permits control of the hydraulic pressure on the piston side in the storage driving cylinder, and thus a fixing of the evacuation time of the storage cylinder. The hydrau-lic accumulator provided for this purpose also allows for compensation of wrong amounts of the hydraulic working medium for the storage opera-tion.
The above-described regulation of the filling time of the storage cyl-inder is made possible hydraulically in a simple way with the features of claim 5. The adjustment is performed by hand, which offers the advantage that the thick matter pump can be adapted at any time to the conditions of a specific case of application, in particular to changing preconditions which may be created by the particular pumping medium.
Claim 6, however, offers the advantage that an automatic adjustment of the flow control valve allows for the storage filling to be adapted to changing evacuation times of the feed cylinders, which OCCUI' particularly when the thick matter pump is adjusted to different deliveries.
The invention shall be e~plained in more detail in the following with reference to an exemplary embodiment that is shown in the connection diagrams, of which Fig. 1 shows schematically, i.e. free from all details that are unnec-essary for understanding the invention, the connection state during evac-uation of the piston storage into the feed pipe during the switch-over phase of the feed cylinders, and Fig. 2 shows the connection state during the filling of the piston storage out of the feed pipe in the pumping phase of the feed cylinders.
The connection to the hydraulic pressure generator of the hydrauli-cally driven feed cylinders of the thick matter pump is shown at 1.
Switch signals are present at 2 for the limits of travel of the pistons in the feed cylinders or in hydraulic driving cylinders of the thick matter pump.
The feed cylinders of the thick matter pump (not shown) work alter-natingly on a feed pipe 3, one of the feed cylinders sucking the thick matter out of a prefilling vessel of the pump, while the other feed cylin-.. . .. .. . .. . . .. . . . ..
3 ~ ~
-der presses its previously sucl~ed in filling into feed pipe 3. Directl~Y fol-lowing the port of the feed cylinders, e.g. on the upper side of a bifur-cated pipe ~hat combines the feed of the two feed cylinders, a storage cylinder 4 is flange-mounted at 6. The opposite end of storage cylinder 4 is flange-mounted on a working cylinder 7 whose working piston 8 drives a storage piston 10 mounted on its piston rod 9 and closing storage cyl-inder 4 against flange 6.
Two seat valves 12 and 14 control hydraulic storage driving cylinder 7 and are indicated within the dot-dash line at 11. Seat valves 12 and 14 are piloted by a 2l2 directional valve. Piston space 11' closed by the full piston area of storage driving piston 7 is connected directly to a hydrau-lic accumulator 17 by a line 16 bypassing 2/2 directional valve 15. Line 16 feeds the 2/2 directional valve via a branch 18. Line 19 to hydraulic ac-cumulator 17 opens into line 16 before directional valve 15. Connection 20 to the line coming from the pressure generator is located before line 19.
The 2/2 directional valve is switched over with the aid of a hydraulic control line 2''. The switch-over takes place against the pressure from a line 24 which is relieved from the tank via a choker 23.
In the switch-over phase shown in Fig. 1. the ''/2 directional valve is changed over via line 22, so that hydraulic working medium reaches seat valve 12 via line 18 to block the hydra,llic connection to piston ring space 11 ' of storage driving cylinder 7 closed off from the ring area of storage driving piston 8. At the same time, seat valve 14 is relieved from the tank on its back via lines 30, 31, so that it unblocks the path via line 27 to tank 28. Bypassing the 2/2 directional valve, high-pressure hy-draulic working medium thus passes from hydraulic accumulator 17 to pis-ton side 15 of the storage driving piston, so that storage piston 10 press-es the volume OI pumping medium contained in storage cylinder 4 into feed pipe 3.
An on-off valve 3Z in storage driving cylinder 7, which is controlled hydraulically by piston 8, controls the limit of travel of storage driving piston 8 in cylinder 7. The switch point is selected in such a way that the total volume of storage cylinder 4 is pressed into feed pipe 3. The piston ring side of storage driving cylinder 7 is depressurized via line 27.
This makes it possible to transfer the storage content into feed pipe 3 while overcoming the feed pipe pressure.
As soon as working piston 8 has îully evacuated storage cylinder 4.
the switch signal of valve 32 Iriggered thereby switches over the 2/2 3 ~ Ç~
directional valve. In the following pumping phase (Fig. 2). in which seat valve 14 is closed via the storage pressure and seat valve 12 is opened b,v the storage pressure, the hydraulic working pressure is applied to both sides of storage driving piston 8. The hydraulic working medium pressure built up in ring space 25 acts in the same direction on storage driving piston 8 in cylinder 7 as the feed pipe pressure on storage piston 10 in storage cylinder 4. This moves storage driving piston 8 in the opposite direction, pressing hydraulic working medium via line 16 bypassing 2/2 directional valve 15 into hydraulic accumulator 17, which is fed from hy-draulic pressure generator 1. This allows storage cylinder 4 to be filled with medium from feed pipe 3 for compensation in the following swi~ch-over phase. Flow control valve 25 is used to adjust the return time of storage piston 10 to make it correspond to the duration of the feed stroke of the thick matter pump, in order to prevent a change in delivery due to the filling of the storage.
The return time of working piston 8 for filling storage 4 can be ad-justed by hand by adjusting flow control valve 25. However, this adjust-ment can also be performed automatically in order to adapt the return time of the storage piston to changing lifting times of the thick matter pump Instead of changing over the 2/2 directional valve hydraulically, one can also do this electrically via limit switches.
-der presses its previously sucl~ed in filling into feed pipe 3. Directl~Y fol-lowing the port of the feed cylinders, e.g. on the upper side of a bifur-cated pipe ~hat combines the feed of the two feed cylinders, a storage cylinder 4 is flange-mounted at 6. The opposite end of storage cylinder 4 is flange-mounted on a working cylinder 7 whose working piston 8 drives a storage piston 10 mounted on its piston rod 9 and closing storage cyl-inder 4 against flange 6.
Two seat valves 12 and 14 control hydraulic storage driving cylinder 7 and are indicated within the dot-dash line at 11. Seat valves 12 and 14 are piloted by a 2l2 directional valve. Piston space 11' closed by the full piston area of storage driving piston 7 is connected directly to a hydrau-lic accumulator 17 by a line 16 bypassing 2/2 directional valve 15. Line 16 feeds the 2/2 directional valve via a branch 18. Line 19 to hydraulic ac-cumulator 17 opens into line 16 before directional valve 15. Connection 20 to the line coming from the pressure generator is located before line 19.
The 2/2 directional valve is switched over with the aid of a hydraulic control line 2''. The switch-over takes place against the pressure from a line 24 which is relieved from the tank via a choker 23.
In the switch-over phase shown in Fig. 1. the ''/2 directional valve is changed over via line 22, so that hydraulic working medium reaches seat valve 12 via line 18 to block the hydra,llic connection to piston ring space 11 ' of storage driving cylinder 7 closed off from the ring area of storage driving piston 8. At the same time, seat valve 14 is relieved from the tank on its back via lines 30, 31, so that it unblocks the path via line 27 to tank 28. Bypassing the 2/2 directional valve, high-pressure hy-draulic working medium thus passes from hydraulic accumulator 17 to pis-ton side 15 of the storage driving piston, so that storage piston 10 press-es the volume OI pumping medium contained in storage cylinder 4 into feed pipe 3.
An on-off valve 3Z in storage driving cylinder 7, which is controlled hydraulically by piston 8, controls the limit of travel of storage driving piston 8 in cylinder 7. The switch point is selected in such a way that the total volume of storage cylinder 4 is pressed into feed pipe 3. The piston ring side of storage driving cylinder 7 is depressurized via line 27.
This makes it possible to transfer the storage content into feed pipe 3 while overcoming the feed pipe pressure.
As soon as working piston 8 has îully evacuated storage cylinder 4.
the switch signal of valve 32 Iriggered thereby switches over the 2/2 3 ~ Ç~
directional valve. In the following pumping phase (Fig. 2). in which seat valve 14 is closed via the storage pressure and seat valve 12 is opened b,v the storage pressure, the hydraulic working pressure is applied to both sides of storage driving piston 8. The hydraulic working medium pressure built up in ring space 25 acts in the same direction on storage driving piston 8 in cylinder 7 as the feed pipe pressure on storage piston 10 in storage cylinder 4. This moves storage driving piston 8 in the opposite direction, pressing hydraulic working medium via line 16 bypassing 2/2 directional valve 15 into hydraulic accumulator 17, which is fed from hy-draulic pressure generator 1. This allows storage cylinder 4 to be filled with medium from feed pipe 3 for compensation in the following swi~ch-over phase. Flow control valve 25 is used to adjust the return time of storage piston 10 to make it correspond to the duration of the feed stroke of the thick matter pump, in order to prevent a change in delivery due to the filling of the storage.
The return time of working piston 8 for filling storage 4 can be ad-justed by hand by adjusting flow control valve 25. However, this adjust-ment can also be performed automatically in order to adapt the return time of the storage piston to changing lifting times of the thick matter pump Instead of changing over the 2/2 directional valve hydraulically, one can also do this electrically via limit switches.
Claims (7)
1. A two-cylinder thick matter pump having a piston storage which is filled during the thick matter feed with the feed cylinders and evacuated by the hydrocontrolled storage piston into the feed pipe between the strokes of the feed pistons to reduce the pressure drop and the undeliv-ered amount in the feed pipe, characterized in that the hydrocontrol (2) of the storage piston (10) is served by a working piston (8) to be acted upon hydraulically on both sides, that is controlled with the feed cylin-ders and whose limits of travel, with the limits of travel of the storage piston (10), are fixed on the storage driving cylinder (7) when the stor-age cylinder (4) is fully evacuated and is filled.
2. The two-cylinder thick matter pump of claim 1, characterized in that the storage driving piston area serving to evacuate the storage cylinder (4) is loaded with high hydraulic pressure during the switch-over phase of the feed cylinders and relief of the storage driving piston ring area, while the storage driving piston ring area and the storage piston (10) are pressurized by the pumping medium, in the pumping phase, and the storage driving piston (8) recedes into its starting position against the hydraulic pressure on the storage driving piston area for the following switch-over phase of the feed cylinders.
3. The two-cylinder thick matter pump of either of claims 1 and 2, characterized in that the time of return of the storage driving piston (8) into the starting position for the switch-over phase of the feed cylinders can be regulated by adjusting the stream into the storage driving piston ring space (11').
4. The two-cylinder thick matter pump of one or more of claims 1 to 3, characterized in that a hydraulic accumulator ( 17) is built into the hydraulic line (16) to the storage driving piston space.
5. The two-cylinder thick matter pump of one or more of claims 1 to 4, characterized in that a flow control valve (26) serving to adjust the return time of the storage driving piston (8) is adjustable by hand in such a way that the limit of travel of the storage piston (10) is reached toward the end of the pumping phase.
6. The two-cylinder thick matter pump of one or more of claims 1 to 5, characterized in that the flow control valve (25) is controllable auto-matically in accordance with the piston speed of the pump.
7. The two-cylinder thick matter pump of one or more of claims 1 to 6, characterized in that the storage driving piston (8) is controlled using seat valves (12, 14) and a directional valve (15) serve which is controlled by the feed cylinders and by an on-off valve (32) that serves to fix the limits of travel of the storage driving piston (8).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3910189.4 | 1989-03-29 | ||
| DE3910189A DE3910189A1 (en) | 1989-03-29 | 1989-03-29 | TWO-CYLINDER FUEL PUMP WITH PISTON ACCUMULATOR |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2013356A1 true CA2013356A1 (en) | 1990-09-29 |
Family
ID=6377396
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002013356A Abandoned CA2013356A1 (en) | 1989-03-29 | 1990-03-28 | Two cylinder solids handling pump with piston reservoir |
Country Status (12)
| Country | Link |
|---|---|
| EP (1) | EP0389785B1 (en) |
| JP (1) | JPH02283872A (en) |
| KR (1) | KR900014753A (en) |
| AT (1) | ATE111564T1 (en) |
| AU (1) | AU633550B2 (en) |
| CA (1) | CA2013356A1 (en) |
| DD (1) | DD296992A5 (en) |
| DE (2) | DE3910189A1 (en) |
| ES (1) | ES2063180T3 (en) |
| FI (1) | FI901568A0 (en) |
| RU (1) | RU2045686C1 (en) |
| ZA (1) | ZA902341B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04134673U (en) * | 1991-06-07 | 1992-12-15 | 株式会社フジタ | Concrete pumping pressure fluctuation prevention device |
| DE4224162A1 (en) * | 1992-07-22 | 1994-01-27 | Korthaus Ernst | Concrete distribution system |
| DE4336087A1 (en) * | 1993-10-22 | 1995-04-27 | Korthaus Ernst | Thick-matter accumulator |
| US7841849B2 (en) | 2005-11-04 | 2010-11-30 | University Of Southern California | Dry material transport and extrusion |
| US8308470B2 (en) | 2005-11-04 | 2012-11-13 | University Of Southern California | Extrusion of cementitious material with different curing rates |
| MX2008005842A (en) * | 2005-11-04 | 2008-09-12 | Univ Southern California | Material delivery system using decoupling accumulator. |
| CN102094779B (en) * | 2010-12-28 | 2012-01-04 | 长沙中联重工科技发展股份有限公司 | Concrete pump and method for adjusting driving pressure value for swinging actuator in concrete pump |
| US10648462B2 (en) * | 2013-10-29 | 2020-05-12 | Thermtech Holdings As | System for feeding and pumping of less pumpable material in a conduit line |
| DE102014212021A1 (en) | 2014-06-23 | 2015-12-24 | Putzmeister Solid Pumps Gmbh | Apparatus and method for damping pressure fluctuations in the delivery line of a slurry pump |
| CN110821775B (en) * | 2019-09-27 | 2021-10-15 | 日昌升建筑新材料设计研究院有限公司 | Multi-cylinder parallel type mine tailing slurry hydraulic pumping system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT234514B (en) * | 1961-08-17 | 1964-07-10 | Martin Sebastiani | Thick matter or mortar pump |
| DE2052583A1 (en) * | 1970-10-27 | 1972-05-04 | Bors, Heinz J., Campione (Schweiz) | Device for conveying viscous substances, especially concrete, mortar and the like |
| US3963385A (en) * | 1975-05-05 | 1976-06-15 | Caban Angel M | Valve assembly for concrete pumps |
| GB2119865A (en) * | 1982-03-27 | 1983-11-23 | John Harbridge | Piston pump or transformer |
-
1989
- 1989-03-29 DE DE3910189A patent/DE3910189A1/en not_active Withdrawn
-
1990
- 1990-02-20 DE DE59007097T patent/DE59007097D1/en not_active Expired - Fee Related
- 1990-02-20 ES ES90103245T patent/ES2063180T3/en not_active Expired - Lifetime
- 1990-02-20 EP EP90103245A patent/EP0389785B1/en not_active Expired - Lifetime
- 1990-02-20 AT AT90103245T patent/ATE111564T1/en not_active IP Right Cessation
- 1990-03-27 ZA ZA902341A patent/ZA902341B/en unknown
- 1990-03-28 CA CA002013356A patent/CA2013356A1/en not_active Abandoned
- 1990-03-28 AU AU52329/90A patent/AU633550B2/en not_active Ceased
- 1990-03-28 DD DD90339162A patent/DD296992A5/en not_active IP Right Cessation
- 1990-03-28 RU SU904743431A patent/RU2045686C1/en active
- 1990-03-29 KR KR1019900004457A patent/KR900014753A/en not_active Application Discontinuation
- 1990-03-29 FI FI901568A patent/FI901568A0/en not_active IP Right Cessation
- 1990-03-29 JP JP2084736A patent/JPH02283872A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE59007097D1 (en) | 1994-10-20 |
| DE3910189A1 (en) | 1990-10-04 |
| AU633550B2 (en) | 1993-02-04 |
| KR900014753A (en) | 1990-10-24 |
| FI901568A0 (en) | 1990-03-29 |
| EP0389785A3 (en) | 1991-01-16 |
| ZA902341B (en) | 1990-12-28 |
| ATE111564T1 (en) | 1994-09-15 |
| EP0389785A2 (en) | 1990-10-03 |
| EP0389785B1 (en) | 1994-09-14 |
| RU2045686C1 (en) | 1995-10-10 |
| AU5232990A (en) | 1990-10-04 |
| JPH02283872A (en) | 1990-11-21 |
| ES2063180T3 (en) | 1995-01-01 |
| DD296992A5 (en) | 1991-12-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA2013356A1 (en) | Two cylinder solids handling pump with piston reservoir | |
| US5993181A (en) | Process and device for feeding concrete or other thick materials | |
| US5336052A (en) | Viscous material pump | |
| EP0614016A4 (en) | Hydraulic drive unit of hydraulic working machine. | |
| JP2002518633A (en) | Hydrostatic wave energy conversion system | |
| CZ281492B6 (en) | Hydraulic drive of press, particularly a press for forming metal sheet | |
| CN101796307A (en) | Hydraulic drive, in particular for machine tools, and method for controlling the hydraulic drive | |
| US5263828A (en) | Two-cylinder thick matter pump having a piston storage | |
| EP0985087B1 (en) | Hydraulic drive system with constant pressure in pressure conduit | |
| FI112791B (en) | Method and apparatus for saving electrical energy in a hydraulic lift actuator | |
| WO2017178261A1 (en) | Method for transmitting or conveying fluid or semi-fluid materials by means of a double piston pump and double piston pump therefor | |
| US4565123A (en) | Tension control for baling machine | |
| US6957567B2 (en) | Method and system for the controlled application of fluid pressure to a load, especially for pressure testing pipe | |
| FI105896B (en) | The main actuator of the tamping press | |
| EP0868612B1 (en) | Hydraulic unit | |
| US6116025A (en) | Dynamic, automatic stroke reversal system for reciprocating, linearly driven pumping units | |
| US20030102179A1 (en) | Hydraulic drive system with constant pressure in pressure conduit | |
| HU176079B (en) | Machine for delivering and applying plastering materials | |
| EP0844198A1 (en) | Device for lifting and/or tilting containers | |
| SU1062171A2 (en) | Hydraulic grapple | |
| SU1481336A1 (en) | Scraper with gas-lubricated bucket | |
| CN86203297U (en) | Combined slurry pump | |
| US6415703B1 (en) | Method for controlling the motion velocity of a hydraulically driven machine, a drive system for a hydraulically driven machine | |
| CN117759586A (en) | Pumping system, control method and device of pumping system and pump truck | |
| JPS61238497A (en) | Press for composite green compact |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |