EP2430310B1 - Piston engine, in particular liquid piston engine - Google Patents
Piston engine, in particular liquid piston engine Download PDFInfo
- Publication number
- EP2430310B1 EP2430310B1 EP10710305A EP10710305A EP2430310B1 EP 2430310 B1 EP2430310 B1 EP 2430310B1 EP 10710305 A EP10710305 A EP 10710305A EP 10710305 A EP10710305 A EP 10710305A EP 2430310 B1 EP2430310 B1 EP 2430310B1
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- European Patent Office
- Prior art keywords
- piston
- delivery volume
- piston engine
- units
- engine according
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- 239000007788 liquid Substances 0.000 title claims description 6
- 230000003213 activating effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
Images
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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/02—Stopping, starting, unloading or idling control
- F04B49/03—Stopping, starting, unloading or idling control by means of valves
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
- F04B49/243—Bypassing by keeping open the inlet valve
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/08—Cylinder or housing parameters
- F04B2201/0807—Number of working cylinders
Definitions
- the invention relates to a piston engine, in particular a liquid piston machine, with a plurality of piston units, which have geometrically different sized delivery volume and are individually adjustable for the discrete setting of a total delivery volume of the piston engine.
- Piston engines of the type mentioned are known from the prior art. Piston engines are used in many fields of technology as pumps and / or as motors. To produce a variable volume flow or volume, optionally also a variable pressure (pump) or a speed and torque (motor), different principles are known. Common designs for continuously changing / adjusting the delivery volume of the piston units are, for example, piston machines with a swashplate, a sloping axis or a swashplate. In this case, the upper and lower dead center of the piston strokes is varied by an angular adjustment, thereby continuously adjusting the delivery volume. However, such embodiments have a low efficiency, especially in the partial load range.
- a piston engine in the form of a fuel pump is known, can be turned off in the individual piston units and thus the total delivery volume can be set discretely, wherein the delivery volume of the individual piston units are designed to increase the adjustment possibilities of different sizes.
- the piston engine according to the invention is characterized by the characterizing features of claim 1. Thereafter, the piston engine is designed such that the larger delivery volume of one of the piston units is in each case twice as large as the next smaller delivery volume of another of the piston units. It is therefore provided that the piston units have different sized delivery volumes and that the piston unit is designed with a larger delivery volume such that its delivery volume is twice as large as that of the other piston unit having the next smaller delivery volume. For example, in three piston units provided, the delivery volume of the second piston unit is twice as large as that of the first, and the delivery volume of the third piston unit twice as large as that of the second piston unit. The same results for any other number of piston units of the piston engine.
- each piston unit is assigned a switchable idle valve for parking the piston unit.
- the idle valve is designed such that opening of the idle valve prevents a pressure in the piston unit constructed and thus liquid is promoted. The idle valve thus leaves the volume in the piston unit "empty".
- the idle valve is further designed such that when opening the idle valve at the same time the outlet cross-section of the piston unit through which the volume to be pumped is to be pumped closed.
- the idle valve may also be designed such that it prevents an inflow of liquid into the piston unit, so that the piston unit runs empty.
- each piston unit can be driven by means of its own drive shaft, so that the drive shafts can be individually controlled or switched off.
- the piston units have a corresponding idle valve associated bypass channel. This leads back the unwanted, but still funded by the piston unit volume of a consumer, so that it is the piston engine "unconsumed" fed back.
- the piston engine has at least three piston units. As a result, it is already possible, as already stated above, to set eight different total delivery volumes of the reciprocating engine in equidistant steps / steps.
- the piston engine is designed as a radial and / or linear piston machine. As a result, both friction losses and losses due to leaks are reduced and ensures a high efficiency of the piston engine, especially in the partial load range.
- each piston unit has at least one piston axially displaceable in a cylinder. It is also conceivable that for each piston unit two cylinders are provided, each with a piston axially displaceable therein. These then form a piston group. Accordingly, the total delivery volume can be adjusted by changing the piston group delivery volume. Thus, it is also conceivable that of a piston group, only the delivery volume of one of the piston-cylinder units is turned off. hereby are further gradations for adjusting the total delivery volume of the reciprocating engine possible.
- the different sized delivery volume of the piston units are determined by different sized cross-sectional areas of the cylinder and piston. This geometric design makes it possible in a simple manner to provide and to ensure the different delivery volumes as described above.
- the different sized delivery volume can be determined by piston strokes of different sizes of the piston units.
- piston engine has been described above essentially as a piston pump, it is obvious to the person skilled in the art that the embodiments described above are also applicable to piston engines designed as piston engines.
- the FIG. 1 shows a schematic representation of a piston machine 1 for liquids, which is designed as a series piston pump 2.
- the piston engine 1 has three cylinders 3, 4 and 5 formed in a housing, in each of which a piston 6, 7 and 8 is mounted so as to be axially displaceable.
- the pistons 6, 7, 8 are thereby displaced by means of a drivable crankshaft 9 in the cylinders 3, 4, 5.
- the cylinder 3 and the piston 6, the cylinder 4 and the piston 7 and the cylinder 5 and the piston 8 each form a piston unit 10, 11 and 12 of the piston engine 1.
- the piston units 10, 11 and 12 have different delivery volumes, which are determined by the size of the respective cross-sectional area of the cylinders 3, 4, 5 and the pistons 6, 7, 8.
- volume V 11 of the piston unit 11 is twice as large as the volume V 10 of the piston unit 10
- volume V 12 of the piston unit 12 twice as large as the delivery volume V 11 of the piston unit 11.
- the larger delivery volume of each of the piston units is twice as large as that next smaller delivery volume of another piston unit.
- i corresponds to the number of piston units.
- Each of the piston units 10, 11, 12 and the cylinder 3, 4, 5 is assigned an idle valve 13, 14 and 15, respectively. From each of the idle valves 13, 14 and 15 performs a bypass channel 16, 17 and 18 of the corresponding piston unit 10, 11 and 12 funded volume "unused" out of the piston engine 1, if the respective idle valve 13, 14, 15 accordingly switched or opened. Conveniently, the bypass channels 16, 17 and 18 to a common - (not shown) - (return) channel merged. By opening the idle valves 13, 14 and / or 15, thus, the respective piston unit 10, 11 and 12 are turned off, so that the delivered by her delivery volume is not pumped forward or returned unused and thereby not the total delivery volume of the piston engine 1 is supplied.
- FIGS. 2 to 9 each show the delivery volume of the piston units 10, 11, 12 as well as the resulting from the corresponding setting of the idle valves 13, 14 and 15 total delivery volume of the reciprocating engine 1 or in-line piston pump 2.
- On the left side is in each case of the respective piston unit 10, 11, 12th provided (dashed) and the possible (blank) delivery volume of the piston units 10, 11 and 12.
- On the right side, respectively, the resulting total delivery volume V G is shown accordingly.
- FIG. 2 shows the corresponding delivery volume in the event that all bypass channels 16, 17 and 18 are released by means of the corresponding idle valve 13, 14 and 15 or all piston units 10, 11, 12 are turned off, so that used by the possible delivery volume and the total delivery volume V G is zero.
- the piston unit 10 thus activated, as in the FIG. 3 illustrated, the total delivery volume V G corresponds to the delivery volume of the piston unit 10th
- the piston unit 10 is turned off and the piston unit 11 is activated, so that the resulting total delivery volume corresponds to the delivery volume of the piston unit 11 and thus twice the delivery volume of the piston unit 10.
- the piston unit 10 is turned off and the piston unit 11 is activated according to FIG.
- FIG. 9 shows the setting of the piston engine 1 and the in-line piston pump 2 in the event that the maximum total flow rate U G, max is set.
- U G, max 7 * V 10 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Hydraulic Motors (AREA)
Description
Die Erfindung betrifft eine Kolbenmaschine, insbesondere eine Flüssigkeitskolbenmaschine, mit mehreren Kolbeneinheiten, die geometrisch bedingt unterschiedlich große Fördervolumen aufweisen und zur diskreten Einstellung eines Gesamtfördervolumens der Kolbenmaschine individuell abstellbar sind.The invention relates to a piston engine, in particular a liquid piston machine, with a plurality of piston units, which have geometrically different sized delivery volume and are individually adjustable for the discrete setting of a total delivery volume of the piston engine.
Kolbenmaschinen der eingangs genannten Art sind aus dem Stand der Technik bekannt. Kolbenmaschinen werden in vielen Bereichen der Technik als Pumpen und/oder als Motoren eingesetzt. Zur Erzeugung eines variablen Volumenstroms beziehungsweise -volumens, gegebenenfalls auch eines variablen Drucks (Pumpe) beziehungsweise eine Drehzahl und Drehmoment (Motor), sind unterschiedliche Prinzipien bekannt. Gängige Bauarten zur kontinuierlichen Veränderung/Einstellung des Fördervolumens der Kolbeneinheiten sind beispielsweise Kolbenmaschinen mit einer Schrägscheibe, einer Schrägachse oder einer Taumelscheibe. Dabei wird durch eine Winkelverstellung der obere und der untere Totpunkt der Kolbenhübe variiert und dadurch das Fördervolumen kontinuierlich verstellt. Jedoch weisen derartige Ausführungsformen einen geringen Wirkungsgrad insbesondere im Teillastbereich auf. Dieser geringe Wirkungsgrad erklärt sich im Wesentlichen durch die Leckage an der entsprechenden Steuer-/ Schräg- oder Taumelscheibe, der Reibung an der Steuer-/ Schräg- oder Taumelscheibe sowie durch einen ständig notwendigen Steuerstrom zum Halten von Steuer-/-Schräg- oder Taumelscheibe. Neben einer kontinuierlichen Veränderung des Fördervolumens oder der Förderzeit der Kolbeneinheiten ist es auch bekannt, diskrete Veränderungen des Fördervolumens durch das Abstellen beziehungsweise Abschalten einzelner Kolbeneinheiten durchzuführen.Piston engines of the type mentioned are known from the prior art. Piston engines are used in many fields of technology as pumps and / or as motors. To produce a variable volume flow or volume, optionally also a variable pressure (pump) or a speed and torque (motor), different principles are known. Common designs for continuously changing / adjusting the delivery volume of the piston units are, for example, piston machines with a swashplate, a sloping axis or a swashplate. In this case, the upper and lower dead center of the piston strokes is varied by an angular adjustment, thereby continuously adjusting the delivery volume. However, such embodiments have a low efficiency, especially in the partial load range. This low efficiency is mainly explained by the leakage at the corresponding control / oblique or swash plate, the friction on the control / oblique or swash plate and by a constantly necessary control current for holding control / oblique or swash plate. In addition to a continuous change in the delivery volume or the delivery time of the piston units, it is also known to perform discrete changes in the delivery volume by switching off or switching off individual piston units.
Aus der
Die erfindungsgemäße Kolbenmaschine zeichnet sich durch die kennzeichnenden Merkmale des Anspruchs 1 aus. Danach ist die Kolbenmaschine derart ausgebildet, dass das größere Fördervolumen einer der Kolbeneinheiten jeweils doppelt so groß ist wie das nächst kleinere Fördervolumen einer anderen der Kolbeneinheiten. Es ist also vorgesehen, dass die Kolbeneinheiten unterschiedlich große Fördervolumen aufweisen und dass die Kolbeneinheit mit einem größeren Fördervolumen derart ausgebildet ist, dass ihr Fördervolumen doppelt so groß ist, wie das der anderen Kolbeneinheit, die das nächst kleinere Fördervolumen aufweist. So ist beispielsweise bei drei vorgesehenen Kolbeneinheiten das Fördervolumen der zweiten Kolbeneinheit doppelt so groß wie das der ersten, und das Fördervolumen der dritten Kolbeneinheit doppelt so groß wie das der zweiten Kolbeneinheit. Entsprechendes ergibt sich für eine andere beliebige Anzahl von Kolbeneinheiten der Kolbenmaschine. Hierdurch ist es möglich, das Gesamtfördervolumen der Kolbenmaschine diskret in äquidistanten Stufen zu verändern beziehungsweise einzustellen. Bei dem oben genannten Ausführungsbeispiel mit drei Kolbeneinheiten ist es möglich, acht unterschiedliche Gesamtfördervolumen von Null bis zum Siebenfachen des Fördervolumens der Kolbeneinheit mit dem kleinsten Fördervolumen einzustellen. Zweckmäßigerweise werden dazu die Kolbeneinheiten derart abgestellt, dass die Stufe bei der Erhöhung oder Verringerung des Gesamtfördervolumens jeweils dem Fördervolumen der Kolbeneinheit mit dem kleinsten Fördervolumen entspricht. Dadurch wird eine Kolbenmaschine geschaffen, deren Gesamtfördervolumen in äquidistanten Stufen variabel einstellbar ist, und die auch im Teillastbereich einen hohen Wirkungsgrad aufweist.The piston engine according to the invention is characterized by the characterizing features of claim 1. Thereafter, the piston engine is designed such that the larger delivery volume of one of the piston units is in each case twice as large as the next smaller delivery volume of another of the piston units. It is therefore provided that the piston units have different sized delivery volumes and that the piston unit is designed with a larger delivery volume such that its delivery volume is twice as large as that of the other piston unit having the next smaller delivery volume. For example, in three piston units provided, the delivery volume of the second piston unit is twice as large as that of the first, and the delivery volume of the third piston unit twice as large as that of the second piston unit. The same results for any other number of piston units of the piston engine. This makes it possible to discretely change or set the total delivery volume of the piston engine in equidistant stages. In the above-mentioned embodiment with three piston units, it is possible to set eight different total delivery volumes from zero to seven times the delivery volume of the piston unit with the smallest delivery volume. For this purpose, the piston units are expediently turned off in such a way that when the total delivery volume is increased or decreased, the stage corresponds in each case to the delivery volume of the piston unit with the smallest delivery volume. This creates a piston machine whose total delivery volume can be variably adjusted in equidistant stages, and which also has high efficiency in the partial load range.
Weiterhin ist vorgesehen, dass jeder Kolbeneinheit ein schaltbares Leerlaufventil zum Abstellen der Kolbeneinheit zugeordnet ist. Das Leerlaufventil ist derart gestaltet, dass durch Öffnen des Leerlaufventils verhindert wird, dass ein Druck in der Kolbeneinheit aufgebaut und damit Flüssigkeit gefördert wird. Das Leerlaufventil lässt also das in der Kolbeneinheit befindliche Volumen "leer laufen". Vorteilhafterweise ist das Leerlaufventil weiterhin derart gestaltet, dass bei Öffnen des Leerlaufventils gleichzeitig der Austrittsquerschnitt der Kolbeneinheit, durch den das zu fördernde Volumen gepumpt werden soll verschlossen wird. Alternativ kann das Leerlaufventil auch derart ausgestaltet sein, dass es ein Einströmen von Flüssigkeit in die Kolbeneinheit verhindert, so dass die Kolbeneinheit leer läuft. Natürlich sind auch ganz andere Abschaltmechanismen für die jeweilige Kolbeneinheit denkbar. Beispielswiese kann jede Kolbeneinheit mittels einer eigenen Antriebswelle angetrieben werden, sodass die Antriebswellen einzeln angesteuert beziehungsweise abgestellt werden können.It is further provided that each piston unit is assigned a switchable idle valve for parking the piston unit. The idle valve is designed such that opening of the idle valve prevents a pressure in the piston unit constructed and thus liquid is promoted. The idle valve thus leaves the volume in the piston unit "empty". Advantageously, the idle valve is further designed such that when opening the idle valve at the same time the outlet cross-section of the piston unit through which the volume to be pumped is to be pumped closed. Alternatively, the idle valve may also be designed such that it prevents an inflow of liquid into the piston unit, so that the piston unit runs empty. Of course, completely different shutdown mechanisms for the respective piston unit are conceivable. For example, each piston unit can be driven by means of its own drive shaft, so that the drive shafts can be individually controlled or switched off.
Nach einer Weiterbildung der Erfindung weisen die Kolbeneinheiten einen dem entsprechenden Leerlaufventil zugeordneten Bypass-Kanal auf. Dieser führt das unerwünschte, aber dennoch durch die Kolbeneinheit geförderte Volumen an einem Verbraucher vorbei zurück, sodass es der Kolbenmaschine "unverbraucht" wieder zugeführt wird.According to a development of the invention, the piston units have a corresponding idle valve associated bypass channel. This leads back the unwanted, but still funded by the piston unit volume of a consumer, so that it is the piston engine "unconsumed" fed back.
Weiterhin ist vorgesehen, dass die Kolbenmaschine mindestens drei Kolbeneinheiten aufweist. Dadurch ist es bereits möglich, wie oben bereits gesagt, acht unterschiedliche Gesamtfördervolumen der Kolbenmaschine in äquidistanten Schritten/Stufen einzustellen.Furthermore, it is provided that the piston engine has at least three piston units. As a result, it is already possible, as already stated above, to set eight different total delivery volumes of the reciprocating engine in equidistant steps / steps.
Zweckmäßigerweise ist die Kolbenmaschine als Radial- und/oder Reihenkolbenmaschine ausgebildet. Dadurch werden sowohl Reibverluste als auch Verluste aufgrund von Leckagen verringert und ein hoher Wirkungsgrad der Kolbenmaschine insbesondere im Teillastbereich gewährleistet.Conveniently, the piston engine is designed as a radial and / or linear piston machine. As a result, both friction losses and losses due to leaks are reduced and ensures a high efficiency of the piston engine, especially in the partial load range.
Vorteilhafterweise weist jede Kolbeneinheit mindestens einen in einem Zylinder axial verlagerbaren Kolben auf. Es ist auch denkbar, dass zu jeder Kolbeneinheit zwei Zylinder mit jeweils einem darin axial verlagerbaren Kolben vorgesehen sind. Diese bilden dann eine Kolbengruppe. Entsprechend kann das Gesamtfördervolumen durch Verändern des Kolbengruppen-Fördervolumens eingestellt werden. So ist es weiterhin auch denkbar, dass von einer Kolbengruppe lediglich das Fördervolumen einer der Kolben-Zylinder-Einheiten abgestellt wird. Hierdurch sind weitere Abstufungen zur Einstellung des Gesamtfördervolumens der Kolbenmaschine möglich.Advantageously, each piston unit has at least one piston axially displaceable in a cylinder. It is also conceivable that for each piston unit two cylinders are provided, each with a piston axially displaceable therein. These then form a piston group. Accordingly, the total delivery volume can be adjusted by changing the piston group delivery volume. Thus, it is also conceivable that of a piston group, only the delivery volume of one of the piston-cylinder units is turned off. hereby are further gradations for adjusting the total delivery volume of the reciprocating engine possible.
Zweckmäßigerweise werden die unterschiedlich großen Fördervolumen der Kolbeneinheiten durch unterschiedlich große Querschnittsflächen der Zylinder und Kolben bestimmt. Durch diese geometrische Gestaltung ist es auf einfache Art und Weise möglich, die unterschiedlichen Fördervolumen wie oben beschrieben vorzusehen und zu gewährleisten.Conveniently, the different sized delivery volume of the piston units are determined by different sized cross-sectional areas of the cylinder and piston. This geometric design makes it possible in a simple manner to provide and to ensure the different delivery volumes as described above.
Alternativ oder zusätzlich können die unterschiedlich großen Fördervolumen durch unterschiedlich große Kolbenhübe der Kolbeneinheiten bestimmt werden.Alternatively or additionally, the different sized delivery volume can be determined by piston strokes of different sizes of the piston units.
Auch wenn oben stehend im Wesentlichen die Funktion der Kolbenmaschine als Kolbenpumpe beschrieben wurde, ist es für den Fachmann selbstverständlich, dass die oben beschriebenen Ausführungsformen auch auf Kolbenmaschinen, die als Kolbenmotor ausgebildet sind, anwendbar sind.Although the function of the piston engine has been described above essentially as a piston pump, it is obvious to the person skilled in the art that the embodiments described above are also applicable to piston engines designed as piston engines.
Im Folgenden soll die Erfindung anhand eines Ausführungsbeispiels näher erläutert werden. Dazu zeigen
- Figur 1
- ein Ausführungsbeispiel einer vorteilhaften Kolbenpumpe in einer schematischen Darstellung und
Figuren 2 bis 9- einstellbare Gesamtfördervolumen der Kolbenpumpe.
- FIG. 1
- an embodiment of an advantageous piston pump in a schematic representation and
- FIGS. 2 to 9
- adjustable total delivery volume of the piston pump.
Die
Allgemein lässt sich das Fördervolumen der Kolbeneinheiten 10, 11, 12 somit ausdrücken als
Jeder der Kolbeneinheiten 10, 11, 12 beziehungsweise der Zylinder 3, 4, 5 ist dabei ein Leerlaufventil 13, 14 beziehungsweise 15 zugeordnet. Von jedem der Leerlaufventile 13, 14 und 15 führt ein Bypass-Kanal 16, 17 und 18 das von der entsprechenden Kolbeneinheit 10, 11 beziehungsweise 12 geförderte Volumen "ungenutzt" aus der Kolbenmaschine 1 heraus, sofern das jeweilige Leerlaufventil 13, 14, 15 entsprechend geschaltet beziehungsweise geöffnet ist. Zweckmäßigerweise werden die Bypass-Kanäle 16, 17 und 18 zu einem gemeinsamen - hier nicht dargestellten - (Rücklauf-)Kanal zusammengeführt. Durch Öffnen der Leerlaufventile 13, 14 und/oder 15, kann somit die jeweilige Kolbeneinheit 10, 11 beziehungsweise 12 abgestellt werden, sodass das von ihr erbrachte Fördervolumen nicht gepumpt sondern ungenutzt weitergeleitet beziehungsweise zurückgeleitet und dadurch nicht dem Gesamtfördervolumen der Kolbenmaschine 1 zugeführt wird.Each of the
Durch entsprechendes Abstellen der Kolbeneinheiten 10, 11, 12 beziehungsweise Einstellen der Leerlaufventile 13, 14, 15 lässt sich somit auf einfache Art und Weise das Gesamtfördervolumen VG der Kolbenmaschine 1 diskret in äquidistanten Stufen verstellen. Dies lässt sich am besten mittels der folgenden Formel darstellen:
Der jeweilige Sprung zwischen den unterschiedlichen Gesamtfördervolumen entspricht dabei aufgrund der oben beschriebenen vorteilhaften Ausbildung der Kolbenmaschine 1 jeweils dem Fördervolumen der Kolbeneinheit mit dem kleinsten Fördervolumen, vorliegend also V10. Das maximale Gesamtfördervolumen VG,max entspricht dabei:
Die
Wird das Leerlaufventil 13 geschlossen, die Kolbeneinheit 10 also aktiviert, wie in der
Gemäß
Wird gemäß
Durch Abstellen der Kolbeneinheiten 10 und 11 und Aktivieren der Kolbeneinheit 12 ergibt sich ein Gesamtfördervolumen VG = V12, das wiederum um eine Stufe größer als das vorhergehende Fördervolumen ist.Turning off the
Um das Gesamtfördervolumen um eine weitere Stufe zu erhöhen, wird gemäß
Um das Fördervolumen um noch eine weitere Stufe zu erhöhen, wird gemäß Figur 8 die Kolbeneinheit 10 abgestellt und die Kolbeneinheit 11 aktiviert.In order to increase the delivery volume by a further step, the
Die
Mittels der vorteilhaft ausgebildeten Kolbenmaschine 1 ist es somit auf einfache Art und Weise möglich, ein Gesamtfördervolumen VG diskret in äquidistanten Schritten (V10) einzustellen, wobei bereits bei drei unterschiedlich ausgebildeten Kolbeneinheiten 10, 11, 12 acht unterschiedliche Gesamtfördervolumen eingestellt werden können, bei gleichbleibend hohem Wirkungsgrad.By means of the advantageously designed piston engine 1, it is thus possible in a simple manner to set a total delivery volume V G discretely in equidistant steps (V 10 ), whereby eight different total delivery volumes can already be set for three differently designed
Claims (8)
- Piston engine (1), in particular liquid piston engine, having a plurality of piston units (10, 11, 12) which have delivery volumes (V10, V11, V12) of different size, as a result of geometry, and can be switched off individually for the discrete setting of an overall delivery volume (VG) of the piston engine (1), characterized in that the larger delivery volume (V11, V12) of one of the piston units (11, 12) is in each case twice as large as the next smaller delivery volume (V10, V11) of another of the piston units (10, 11).
- Piston engine according to Claim 1, characterized in that each piston unit (10, 11, 12) is assigned a switchable idling valve (13, 14, 15) for switching off.
- Piston engine according to one of the preceding claims, characterized in that the piston units (10, 11, 12) have a bypass channel (16, 17, 18) which is assigned to the corresponding idling valve (13, 14, 15).
- Piston engine according to one of the preceding claims, characterized by at least three piston units (10, 11, 12).
- Piston engine according to one of the preceding claims, characterized in that it is configured as a radial and/or in-line piston engine, in particular as a radial or in-line piston pump (2).
- Piston engine according to one of the preceding claims, characterized in that each piston unit (10, 11, 12) has at least one piston (6, 7, 8) which can be displaced axially in a cylinder (3, 4, 5).
- Piston engine according to one of the preceding claims, characterized in that the delivery volumes (V10, V11, V12) of different size are defined by cross-sectional areas of different size of the cylinders (3, 4, 5) and pistons (6, 7, 8).
- Piston engine according to one of the preceding claims, characterized in that the delivery volumes (V10, V11, V12) of different size are defined by piston strokes of different size.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009003066A DE102009003066A1 (en) | 2009-05-13 | 2009-05-13 | Piston machine, in particular liquid piston machine |
PCT/EP2010/053689 WO2010130495A1 (en) | 2009-05-13 | 2010-03-22 | Piston engine, in particular liquid piston engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2430310A1 EP2430310A1 (en) | 2012-03-21 |
EP2430310B1 true EP2430310B1 (en) | 2013-01-09 |
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ID=42269652
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10710305A Not-in-force EP2430310B1 (en) | 2009-05-13 | 2010-03-22 | Piston engine, in particular liquid piston engine |
Country Status (5)
Country | Link |
---|---|
US (1) | US20120036992A1 (en) |
EP (1) | EP2430310B1 (en) |
CN (1) | CN102422021A (en) |
DE (1) | DE102009003066A1 (en) |
WO (1) | WO2010130495A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010053091A1 (en) * | 2010-12-01 | 2012-06-06 | Linde Aktiengesellschaft | Multi-stage piston compressor |
US9571482B2 (en) | 2011-07-21 | 2017-02-14 | Intel Corporation | Secure on-line sign-up and provisioning for Wi-Fi hotspots using a device management protocol |
US9307408B2 (en) | 2012-12-27 | 2016-04-05 | Intel Corporation | Secure on-line signup and provisioning of wireless devices |
US9951771B2 (en) * | 2013-04-08 | 2018-04-24 | Danfoss Power Solutions Inc. | Selectable flow hydraulic gear pump |
GB2553800B (en) * | 2016-09-14 | 2018-10-24 | Energwave Nautilus Ltd | Producing compressed air from ocean waves |
DE102019208179A1 (en) * | 2019-06-05 | 2020-12-10 | Robert Bosch Gmbh | Pump, especially high pressure fuel pump |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0378967B1 (en) * | 1989-01-19 | 1993-01-27 | GebràDer Sulzer Aktiengesellschaft | Piston compressor |
US5078580A (en) * | 1991-03-29 | 1992-01-07 | Dresser-Rand Company | Plural-stage gas compressor |
CN1082143C (en) * | 1993-11-08 | 2002-04-03 | Crt公共铁路技术公司 | Control device for a variable volume pump |
US5988165A (en) * | 1997-10-01 | 1999-11-23 | Invacare Corporation | Apparatus and method for forming oxygen-enriched gas and compression thereof for high-pressure mobile storage utilization |
US6065440A (en) * | 1999-07-07 | 2000-05-23 | Pasquan; Raymond F. | Internal combustion engine with binary cylinder sizing for variable power output |
US6932583B2 (en) * | 2001-04-16 | 2005-08-23 | Siemens Diesel Systems Technology | Multiple stage pump with multiple external control valves |
DE10153189A1 (en) | 2001-10-27 | 2003-05-15 | Bosch Gmbh Robert | Fuel pump, fuel system, method for operating a fuel system and internal combustion engine |
CN2751106Y (en) * | 2004-11-12 | 2006-01-11 | 郑州知信机电科技开发有限公司 | Proportional control high-pressure double liquid injection pump |
WO2008025395A1 (en) * | 2006-09-01 | 2008-03-06 | Robert Bosch Gmbh | Control device for a hydraulic piston machine with a variable volume flow |
US7779627B1 (en) * | 2009-02-05 | 2010-08-24 | Ries James D | Variable-displacement piston-cylinder device |
DE102009038462A1 (en) * | 2009-08-21 | 2011-03-03 | Dürr Systems GmbH | Tumbling piston pump for metering a coating agent |
-
2009
- 2009-05-13 DE DE102009003066A patent/DE102009003066A1/en not_active Withdrawn
-
2010
- 2010-03-22 CN CN2010800207810A patent/CN102422021A/en active Pending
- 2010-03-22 WO PCT/EP2010/053689 patent/WO2010130495A1/en active Application Filing
- 2010-03-22 EP EP10710305A patent/EP2430310B1/en not_active Not-in-force
- 2010-03-22 US US13/266,955 patent/US20120036992A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
EP2430310A1 (en) | 2012-03-21 |
CN102422021A (en) | 2012-04-18 |
WO2010130495A1 (en) | 2010-11-18 |
US20120036992A1 (en) | 2012-02-16 |
DE102009003066A1 (en) | 2010-11-18 |
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