EP1927753A2 - Conveying unit - Google Patents
Conveying unit Download PDFInfo
- Publication number
- EP1927753A2 EP1927753A2 EP07117628A EP07117628A EP1927753A2 EP 1927753 A2 EP1927753 A2 EP 1927753A2 EP 07117628 A EP07117628 A EP 07117628A EP 07117628 A EP07117628 A EP 07117628A EP 1927753 A2 EP1927753 A2 EP 1927753A2
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- European Patent Office
- Prior art keywords
- pump
- delivery unit
- delivery
- housing
- pressure
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- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
- F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
Definitions
- duopumps hydraulic conveying units are known from the prior art (catalog Robert Bosch GmbH gear pumps mobile hydraulics Bosch Automation 70442 Stuttgart), which are also referred to as duopumps.
- the duopumps known from the prior art have two pump cells which are separated from one another by a dividing wall, wherein the two pump cells which are separate from one another have identical delivery volumes.
- a delivery unit for a hydraulic fluid which has at least two pump cells which have different delivery volumes from each other.
- the distribution of the delivery volumes of at least two pump cells z. B. in the ratio of 10:90, 20:80, 30:70 or 40:60 or the like are freely chosen.
- the larger of the two delivery volumes upon reaching a certain pressure, such. B. on the order of 10 bar, in which a transmission clutch comes to rest are switched off, so that only the smaller delivery volume of the two pump cells is active on the proposed pumping unit according to the invention and is driven via the drive shaft of the delivery unit.
- the smaller pump cell continues to promote and builds a maximum pressure of the order of z. B. 50 bar.
- the smaller pump cell is protected by a pressure relief valve, which is set to ensure that the gear coupling is pressed so that the required torque can be easily transferred.
- this can be done with at least two pump cells in external gear design, d. H. be realized with two meshing with each other on the outer circumference gears.
- the delivery unit proposed according to the invention can also be designed as an internally toothed pump.
- the short circuit ie the switching off of the larger of the two delivery volumes, which realizes the large delivery volume when the transmission clutch z. B. is hired, ie is moved within the clutch housing, can be operated with a hydraulically operated valve. This opens z. B. at pressures above 10 bar a Bypass to the suction line.
- a solenoid valve can be used, which is controlled via a housed in a control unit electronics and opens a bypass by a signal of a pressure sensor.
- the invention proposed pumping unit whose hydraulic components can be installed to form a unit.
- all or part of the hydraulic components pump, check valve and control valve and pressure sensor and the like can be accommodated in a pump housing.
- the delivery unit proposed according to the invention is one which is designed in such a high level of integration, then the delivery unit has as interface only a pump inlet for the hydraulic fluid and a pump outlet for the hydraulic fluid, with which an actuator in the form of a hydraulic cylinder for Example can be operated.
- the required connecting line could be realized instead of piping through channels in the pump housing.
- FIG. 1 From the illustration according to FIG. 1 is a perspective view of a known from the prior art delivery unit can be seen.
- the delivery unit 10 shown here is one in whose housing 12 a drive shaft 14 extends.
- the drive shaft 14 is of a in FIG. 1 not shown drive actuated.
- the delivery unit 10 comprises a first gear pair 16 and a second gear pair 18.
- the first gear pair 16 is separated from the second gear pair 18 in the housing 12 via a partition wall 20.
- the drive shaft 14 of the delivery unit 10 is mounted in shaft bearings 22.
- the further, underlying shaft is mounted in shaft bearings 24 within the housing 12 of the delivery unit 10.
- FIG. 1 shows that the delivery unit 10 shown there according to the prior art with respect to the first pump cell forming a first pair of gears 16 and the second gear pair 18, which forms a second pump cell, identical delivery volumes.
- the gear pairs 16, 18 When switching off one of the two delivery volumes, given by the gear pairs 16, 18, only 50% of the capacity of the in FIG. 1 shown known from the prior art delivery units are turned off.
- FIGS. 2, 2.1 and 2.2 shows a first embodiment of the invention proposed delivery unit including Hydraulikverscnies.
- FIG. 2 From the illustration according to FIG. 2 is a section through the inventively proposed delivery unit.
- FIG. 2 It can be seen that there presented a proposed delivery unit 30, which is also referred to as duo-pump there, a first pump cell 32 and a second pump cell 34 which are separated from each other by a partition wall 20. From the illustration according to FIG. 2 shows that the inventively proposed delivery unit 30 has a pump housing 12 which consists of several components, such. B. side walls and one cover part. These components of the housing 12 surround the drive shaft 14 and a further shaft which is mounted in the interior of the pump housing 12. From the illustration according to FIG. 2 It can be seen that the first pump cell 32 in this embodiment is composed of two wider building gears which mesh with each other as compared to the second pump cell 34, which is narrower in construction.
- the second pump cell 34 is associated with a second output 38 in the pump housing 12.
- the output over which the compressed hydraulic fluid exits the first, wider pumping cell 32 is shown in the sectional view of FIG Figure 2.2 indicated by reference numeral 36.
- Reference numeral 36 thus includes the in sectional view II.2 - II.2 in FIG. 2 presented and in Figure 2.2
- a common inlet of hydraulic fluid from a fluid supply, indicated by reference numeral 40 is located centrally between the externally toothed gearwheels, which are clamped together, according to the first gear pair 16, which form the first pump cell 32.
- the ratio of the delivery volumes of the invention proposed aggregate 30 can be adjusted to each other. It can be according to the width of the meshing, externally toothed gears of the first pump cell 32 and the second pump cell 34 delivery volumes of the second pump cell 34 to the first feed pump cell 32 of 10:90, 20:80, 30:70, 40:60 or in others gradations realize any intervening.
- the size of the delivery volumes 32, 34 from the two pump cells 32 and 34 is only dependent on the width of the meshing externally toothed gears in the axial length, ie seen coaxially with the drive shaft 14.
- FIG. 2 Registered cutting profile IL2 - IL2 corresponds to the representation according to Figure 2.2 to reproduce the first output 36 and the common inlet 40;
- the in FIG. 2 Section II.1 - II.1 shows the section according to the illustration FIG. 2 , 1 , Out FIG. 2 , 1 shows that both the drive shaft and the further shaft of the present invention proposed delivery unit 30 are sealed by at least one circumferential seal 48.
- the pump housing 12 is held together by a plurality of preferably designed as expansion screws through-bolts.
- the first output 36 and the second output 38 open into a pressure line 42.
- the first pump cell 32 and the second pump cell 34 are connected via a common inlet 40, which in Figure 2.2 is shown opening into the housing 12 of the invention proposed delivery unit 30, filled with hydraulic fluid.
- a check valve 46 In the pressure line 42, which is pressurizable by both outputs 36, 38 and due to a first switching valve 50 only by the second output 38 when switching off the first pump cell 82, there is a check valve 46.
- the check valve 46 separates the pressure line of the first output 36 of the second output 38 of the second pump cell 34 of the delivery unit 30 proposed according to the invention, when via the first switching valve 50, the first output 36 of the first pump cell 32 with the input 62 is connected.
- a hydraulic pressure is generated only by the narrow-built second pump cell 34, in which case the concerns of the clutch to be actuated an automatic transmission has already been done, which takes place at a pressure level in the order of 3 to 10 bar, which via a delivery of hydraulic fluid through both delivery volumes, ie, the first, broader pump cell 32 and the second, narrower pump cell 34, the delivery unit 30 is accomplished.
- the switching off or short-circuiting of the first output 36 to the hydraulic input 62 of the delivery unit 30 proposed according to the invention is carried out by the first switching valve 50 at an reached pressure of about 10 bar, in which the clutch is applied.
- a further pressure build-up takes place by means of the delivery unit 30 proposed according to the invention exclusively through the second pump cell 34 to a pressure level in the order of magnitude of approximately 50 bar. Said pressure level is sufficient to maintain a pressing of a clutch to a clutch bell or to a clutch disc and to ensure the proper transmission of torque.
- pressing d. H.
- a pressure sensor 54 By means of a pressure sensor 54, the pressure increase is detected.
- the detected by the pressure sensor 54 switching signal is used as a signal for actuating the first switching valve 50 via an electronic unit, which may be included in a control unit, not shown.
- an electronic unit which may be included in a control unit, not shown.
- the actuating cylinder 44 which is actuated by the hydraulic fluid compressed by the conveying unit 30 proposed by the invention, is connected directly behind the switching valve 56.
- the individual components such. B. the check valve 46, the pressure sensor 54, the pressure relief valve 52, the first switching valve 50 and the switching valve 56 for actuating the clutch cylinder 44, are completely integrated into the pump housing 12 of the delivery unit 30.
- the integrated housing 60 has only one designated by reference numeral 62 input and designated by reference numeral 64 output to which the actuating cylinder 44 is connected.
- the in the representations according to the FIGS. 2 and 2.2 illustrated connecting lines can be designed as bores or the like within the pump housing 12 of the invention proposed delivery unit.
- the Verbohrungen can z. B. in the in FIG. 2 be illustrated, arranged on the housing 12 lids designed to give an example. Furthermore, partial integration of the check valve 46, the first switching valve 50 and the pressure sensor 54 is possible within the scope of the integrated housing 60. The degree of integration of hydraulic components in the housing 12 of the delivery unit 30 is dependent on the particular application in each case.
- FIGS. 3, 3.1 and 3.2 The figure sequence of FIGS. 3, 3.1 and 3.2 is a further embodiment of the present invention proposed delivery unit can be seen.
- the representation according to FIG. 3 is removable, that analogous to in FIG. 2 illustrated embodiment, the delivery unit 30, the first pump cell 32 and the second pump cell 34 includes.
- the delivery unit 30, the first pump cell 32 and the second pump cell 34 includes.
- 34 forming, meshing, externally toothed gears can delivery volumes of the pumping unit (duo pump) in a ratio between 10:90, 20:80, 30:70, 40:60 and other intermediate Grading ratios are set.
- the first pump cell 32 is separated from the second pump cell 34 by the partition wall 20.
- the section III.1 - III.1 corresponds to the illustration in FIG.
- first switching valve 50 designed as a pressure-controlled switching valve 70.
- the pressure-controlled switching valve 70 releases the bypass of the first pump cell 32 to the suction line, ie to the input 62.
- the in FIG. 2 shown pressure sensor 54 is no longer required over the in FIG. 2 illustrated embodiment of the high-pressure pump 3, the first switching valve 50 is actuated with the required signal with the interposition of the control unit.
- 3.1 and 3.2 illustrated embodiment of the delivery unit 30 is the switching valve 56 of the actuating cylinder 44 immediately downstream.
- a pressure limiting valve 52 is provided, via which hydraulic fluid, which is not required when the clutch is pressed, flows back into the hydraulic reservoir or the inlet.
- FIGS. 4 and 4.1 show a schematic representation of the formation of the delivery unit (duo pump) in réelle leopardrad-construction.
- FIG. 4 is a schematic sectional view of a designed as an internally toothed pump delivery unit, here by reference numerals 80 identified.
- An internally toothed duo-pump 80 has a suction side identified by reference numeral 82 as well as a printed page indicated by reference numeral 84.
- the first pump cell 32 and the second pump cell 34 are analogous to the embodiments of the delivery unit proposed according to the invention according to the Figure sequences 2, 2.1, 2.2 and 3.3.1.3.2.
- the first pump cell 32 and the second pump cell 34 are separated from each other by the partition wall 20.
- the housing of the internally toothed duo pump 80 has a bore 92 in which the drive shaft 14 is received.
- Each of the pump cells 32, 34, separated by the partition wall 20, comprises an outboard ring gear 86, 86 'having internal teeth and an internal pinion 88, 88' having external teeth.
- the pinion 88, 88 ' is arranged in an eccentricity 94 to the axis of the ring gears 86, 86'.
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Abstract
Description
Zur Druckversorgung und zur Betätigung von Getriebekupplungen, die z. B. an automatischen Kraftfahrzeuggetrieben vorgesehen sind, werden Förderaggregate, wie z. B. Ölpumpen, für das Hydraulikfluid benötigt, die zum Verstellen der Kupplungen im Rahmen eines Anstellvorganges ein großes Fördervolumen bei niedrigem Druck benötigen. Dieses niedrige Druckniveau liegt in der Größenordnung zwischen 3 und 10 bar. Zum Halten beziehungsweise Anpressen der Kupplung ist ein wesentlich höherer Druck erforderlich, der in der Größenordnung von bis zu 50 bar liegt, der jedoch kleine Volumenströme des Hydraulikmediums erforderlich macht. Demzufolge ist eine kostengünstige Pumpe erforderlich, die auf einfache und unkomplizierte Weise bei Erreichen von Drücken oberhalb der Grenze von etwa 10 bar von einem hohen Fördervolumenstrom, der zum Anstellen der Kupplung erforderlich ist, auf einen geringeren Fördervolumenstrom umschaltet, um die Förderverluste zu vermeiden beziehungsweise zu verringern.For pressure supply and for the operation of transmission clutches z. B. are provided on automatic motor vehicle transmissions, delivery units, such. As oil pumps, needed for the hydraulic fluid, which require a large displacement at low pressure for adjusting the clutches in the context of a Anstellvorganges. This low pressure level is on the order of 3 to 10 bar. To hold or pressing the clutch a much higher pressure is required, which is in the order of up to 50 bar, but makes small volume flows of the hydraulic medium required. Accordingly, a low-cost pump is required, which switches in a simple and straightforward manner when reaching pressures above the limit of about 10 bar of a high flow rate, which is required for hiring the clutch to a lower flow rate to prevent the delivery losses or to reduce.
Aus dem Stand der Technik sind Förderaggregate, so z. B. Ölpumpen, bekannt, die als Zahnradpumpen ausgelegt sind, bei denen drei Zahnräder miteinander kämmen. Die bei der aus dem Stand der Technik bekannten Pumpe eingesetzten drei Zahnräder sind nebeneinander liegend angeordnet, so dass jeweils ein Außenzahnrad mit dem Innenzahnrad eine Pumpenzelle bildet. Bei Erreichen eines Druckniveaus in der Größenordnung von etwa 10 bar kann eine der beiden außenliegenden Pumpenzellen über ein Schaltventil mit dem Saugstrang kurzgeschlossen werden, so dass in dieser abgeschalteten Pumpenzelle kein Druckaufbau erzeugt wird. Diese Ausführungsvariante eines Förderaggregates hat den Nachteil, dass aufgrund der nebeneinander liegenden Anordnung zweier Außenzahnräder an einem Innenzahnrad ein großes Einbaumaß erforderlich wird, da durch die Anordnung der Zahnräder die Pumpe sehr breit baut. Ein weiterer Nachteil dieser aus dem Stand der Technik bekannten Ölpumpe liegt darin, dass durch das Abschalten einer jeweils außen liegenden Pumpenzelle die Fördermenge lediglich halbiert wird. Ist jedoch z. B. eine Reduzierung von wesentlich mehr als nur 50 % der vorhandenen Förderkapazität erforderlich, z. B. eine Reduzierung der Fördermenge auf etwa nur 10 bis 15 % der gesamten maximal förderbaren Fördermenge, so ist diese Anforderung über die aus dem Stand der Technik bekannte Pumpenanordnung nicht realisierbar.From the prior art delivery units, such. As oil pumps, known which are designed as gear pumps, in which three gears mesh with each other. The three gears used in the known from the prior art pump are arranged side by side, so that in each case an external gear forms a pump cell with the internal gear. Upon reaching a pressure level in the order of about 10 bar one of the two outer pump cells can be short-circuited via a switching valve with the suction train, so that no pressure build-up is generated in this pump cell off. This embodiment of a delivery unit has the disadvantage that due to the juxtaposition of two external gears a large installation dimension is required on an internal gear, since the arrangement of the gear wheels makes the pump very wide. Another disadvantage of this known from the prior art oil pump is that the flow rate is only halved by switching off a respective outer pump cell. However, if z. B. a reduction of much more than 50% of the existing production capacity required, z. As a reduction of the flow rate to about only 10 to 15% of the total maximum deliverable flow, so this requirement is not feasible on the well-known from the prior art pump assembly.
Des Weiteren sind aus dem Stand der Technik Hydraulikförderaggregate bekannt (Katalog Robert Bosch GmbH Zahnradpumpen Mobilhydraulik Bosch Automation 70442 Stuttgart), die auch als Duopumpen bezeichnet werden. Die aus dem Stand der Technik bekannten Duopumpen weisen zwei durch eine Trennwand voneinander getrennte Pumpenzellen auf, wobei die beiden voneinander getrennten Pumpenzellen identische Fördervolumina aufweisen.Furthermore, hydraulic conveying units are known from the prior art (catalog Robert Bosch GmbH gear pumps mobile hydraulics Bosch Automation 70442 Stuttgart), which are also referred to as duopumps. The duopumps known from the prior art have two pump cells which are separated from one another by a dividing wall, wherein the two pump cells which are separate from one another have identical delivery volumes.
Erfindungsgemäß wird ein Förderaggregat für ein Hydraulikfluid vorgeschlagen, welches mindestens zwei Pumpenzellen aufweist, die voneinander verschiedene Fördervolumina aufweisen. Je nach Anwendungsfall kann die Aufteilung der Fördervolumina der mindestens zwei Pumpenzellen z. B. im Verhältnis von 10:90, 20:80, 30:70 oder 40:60 oder dergleichen frei gewählt werden. In Kombination mit einem Steuerventil kann das größere der beiden Fördervolumina bei Erreichen eines bestimmten Druckes, so z. B. in der Größenordnung von 10 bar, bei dem eine Getriebekupplung zum Anliegen kommt, abgeschaltet werden, so dass an dem erfindungsgemäß vorgeschlagenen Förderaggregat nur noch das kleinere Fördervolumen der beiden Pumpenzellen aktiv ist und über die Antriebswelle des Förderaggregates angetrieben wird. Die kleinere Pumpenzelle fördert weiter und baut einen maximalen Druck in der Größenordnung von z. B. 50 bar auf. Die kleinere Pumpenzelle ist über ein Druckbegrenzungsventil abgesichert, welches so eingestellt ist, dass gewährleistet ist, dass die Getriebekupplung so angepresst ist, dass das erforderliche Drehmoment problemlos übertragen werden kann.According to the invention, a delivery unit for a hydraulic fluid is proposed which has at least two pump cells which have different delivery volumes from each other. Depending on the application, the distribution of the delivery volumes of at least two pump cells z. B. in the ratio of 10:90, 20:80, 30:70 or 40:60 or the like are freely chosen. In combination with a control valve, the larger of the two delivery volumes upon reaching a certain pressure, such. B. on the order of 10 bar, in which a transmission clutch comes to rest, are switched off, so that only the smaller delivery volume of the two pump cells is active on the proposed pumping unit according to the invention and is driven via the drive shaft of the delivery unit. The smaller pump cell continues to promote and builds a maximum pressure of the order of z. B. 50 bar. The smaller pump cell is protected by a pressure relief valve, which is set to ensure that the gear coupling is pressed so that the required torque can be easily transferred.
Außer den obenstehend genannten Aufteilungen der Fördervolumina der mindestens zwei im erfindungsgemäß vorgeschlagenen Förderaggregat untergebrachten Pumpenzellen in den genannten Bereichen, sind selbstverständlich auch andere Fördervoluminaverhältnisse möglich. Des Weiteren wird darauf verwiesen, dass neben dem hier erwähnten ersten Druckniveau von 10 bar und einem Höchstdruckniveau von 50 bar bei Betrieb der kleineren der beiden Pumpenzellen auch andere Umschaltdrücke beziehungsweise Höchstförderdrücke je nach Auslegung des erfindungsgemäß vorgeschlagenen Druckaggregates verwirklicht werden können. Dies ist im Einzelfall abhängig vom Anwendungsfall.Apart from the abovementioned divisions of the delivery volumes of the at least two pumping cells accommodated in the proposed delivery unit according to the invention in the areas mentioned, other delivery volume ratios are, of course, also possible. Furthermore, it is pointed out that in addition to the first mentioned pressure level of 10 bar and a maximum pressure level of 50 bar when operating the smaller of the two pump cells, other switching pressures or maximum delivery pressures can be realized depending on the design of the proposed invention printing unit. In individual cases, this depends on the application.
Durch das erwähnte Druckbegrenzungsventil ist es sichergestellt, dass die zu betätigende Getriebekupplung so angepresst ist und eine derartige Anpresskraft erfährt, dass im Zusammenspiel mit einer Kupplungsglocke das erforderliche Drehmoment problemlos übertragen werden kann. Nicht benötigtes Hydraulikfluid strömt über das Druckbegrenzungsventil ab, wobei die Verluste aufgrund des in diesem Betriebszustand lediglich aktiven kleineren der beiden Fördervolumina sehr gering sind. Können die Pumpenzellen, d. h. die Fördervolumina, in einem Gehäuse des Förderaggregates hintereinander angeordnet werden, kann das Förderaggregat sehr kompaktbauend ausgeführt werden, was zu günstigen Einbauverhältnissen führt, im Gegensatz zu der aus dem Stand der Technik bekannten Pumpenanordnung mit drei nebeneinander liegend angeordneten Zähnen.By the mentioned pressure relief valve, it is ensured that the gearbox clutch to be actuated is pressed and undergoes such a contact force, that in conjunction with a clutch bell, the required torque can be easily transferred. Unnecessary hydraulic fluid flows out via the pressure limiting valve, the losses being very low due to the smaller of the two delivery volumes being active in this operating state. Can the pump cells, d. H. the delivery volumes are arranged one behind the other in a housing of the delivery unit, the delivery unit can be made very compact, resulting in favorable installation conditions, in contrast to the known from the prior art pump assembly with three juxtaposed teeth.
In einer Ausführungsform des erfindungsgemäß vorgeschlagenen Förderaggregates kann dies mit mindestens zwei Pumpenzellen in Außenverzahnungsbauweise, d. h. mit zwei am Außenumfang miteinander kämmenden Zahnrädern realisiert werden. Darüber hinaus kann das erfindungsgemäß vorgeschlagene Förderaggregat auch als innenverzahnte Pumpe ausgeführt sein.In one embodiment of the delivery unit proposed according to the invention, this can be done with at least two pump cells in external gear design, d. H. be realized with two meshing with each other on the outer circumference gears. In addition, the delivery unit proposed according to the invention can also be designed as an internally toothed pump.
Die Kurzschlussschaltung, d. h. das Abschalten des größeren der beiden Fördervolumina, die das große Fördervolumen realisiert, wenn die Getriebekupplung z. B. angestellt wird, d. h. innerhalb des Kupplungsgehäuses verfahren wird, kann mit einem hydraulisch betätigten Ventil betätigt werden. Dieses öffnet z. B. bei Drücken oberhalb von 10 bar einen Bypass zum Saugstrang. In einer anderen Ausführungsform kann ein Magnetventil eingesetzt werden, welches über eine in einem Steuergerät untergebrachte Elektronik angesteuert wird und durch ein Signal eines Drucksensors einen Bypass öffnet.The short circuit, ie the switching off of the larger of the two delivery volumes, which realizes the large delivery volume when the transmission clutch z. B. is hired, ie is moved within the clutch housing, can be operated with a hydraulically operated valve. This opens z. B. at pressures above 10 bar a Bypass to the suction line. In another embodiment, a solenoid valve can be used, which is controlled via a housed in a control unit electronics and opens a bypass by a signal of a pressure sensor.
Zur Verringerung des Montageaufwandes des erfindungsgemäß vorgeschlagenen Förderaggregates können dessen hydraulische Komponenten zu einer Einheit verbaut sein. Dazu können ganz oder teilweise die Hydraulikkomponenten Pumpe, Rückschlagventil sowie Steuerventil sowie Drucksensor und dergleichen in einem Pumpengehäuse untergebracht sein. Handelt es sich bei dem erfindungsgemäß vorgeschlagenen Förderaggregat um ein solches, welches in einer derart hohen Integrationsstufe ausgebildet ist, so weist das Förderaggregat als Schnittstelle lediglich einen Pumpeneingang für das Hydraulikfluid sowie einen Pumpenausgang für das Hydraulikfluid auf, mit dem ein Betätigungsorgan in Gestalt eines Hydraulikzylinders zum Beispiel betätigt werden kann. In dieser Ausführungsform des erfindungsgemäß vorgeschlagenen Förderaggregates könnte die erforderliche Verbindungsleitung anstatt über Verrohrungen durch Kanäle im Pumpengehäuse realisiert werden. Des Weiteren ist hervorzuheben, dass aufgrund der Bauweise des Pumpengehäuses des erfindungsgemäß vorgeschlagenen Förderaggregates je nach Anwendungsfall aufgrund des scheibenförmigen Aufbaus des Förderaggregates unterschiedlich breit dimensionierte Pumpenzellen, d. h. unterschiedlich breit dimensionierte innenverzahnte oder außenverzahnte Zahnräder, eingesetzt werden können, um das Verhältnis der Aufteilung der Fördervolumina der mindestens zwei Pumpenzellen auf den jeweils vorgesehenen Anwendungsfall optimal abzustimmen.To reduce the assembly costs of the invention proposed pumping unit whose hydraulic components can be installed to form a unit. For this purpose, all or part of the hydraulic components pump, check valve and control valve and pressure sensor and the like can be accommodated in a pump housing. If the delivery unit proposed according to the invention is one which is designed in such a high level of integration, then the delivery unit has as interface only a pump inlet for the hydraulic fluid and a pump outlet for the hydraulic fluid, with which an actuator in the form of a hydraulic cylinder for Example can be operated. In this embodiment of the delivery unit proposed according to the invention, the required connecting line could be realized instead of piping through channels in the pump housing. Furthermore, it should be emphasized that due to the design of the pump housing of the invention proposed delivery unit depending on the application due to the disc-shaped construction of the delivery unit different sized pump cells, d. H. different width-dimensioned internally toothed or externally toothed gears, can be used to optimally tune the ratio of the distribution of the delivery volumes of the at least two pump cells to the respective intended application.
Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben. Es zeigt:
- Figur 1
- eine perspektivische Darstellung eines aus dem Stand der Technik bekannten Förderaggregates mit zwei Pumpenzellen, die identische Fördervolumina aufweisen,
- Figur 2, 2.1 und 2.2
- Schnittansicht einer Ausführungsform des Förderaggregates mit Hydraulikschema,
- Figur 3, 3.1 und 3.2
- Schnitte durch eine weitere Ausführungsform des erfindungsgemäß vorgeschlagenen Förderaggregates ohne Drucksensor und
- Figur 4 und 4.1
- Schnitte durch ein als innenverzahnte Pumpe ausgebildetes Förderaggregat gemäß der vorliegenden Erfindung.
- FIG. 1
- a perspective view of a known from the prior art delivery unit with two pump cells having identical delivery volumes,
- FIGS. 2, 2.1 and 2.2
- Sectional view of an embodiment of the delivery unit with hydraulic scheme,
- FIGS. 3, 3.1 and 3.2
- Sections through a further embodiment of the present invention proposed delivery unit without pressure sensor and
- FIGS. 4 and 4.1
- Cuts by a trained as internal gear pump delivery unit according to the present invention.
Aus der Darstellung gemäß
Aus der Darstellung gemäß
Die Figurensequenz der
Aus der Darstellung gemäß
Aus der Schnittdarstellung gemäß der
Aus der Darstellung gemäß
Der in
Der Darstellung gemäß der
Der erste Ausgang 36 und der zweite Ausgang 38 münden in eine Druckleitung 42. Die erste Pumpenzelle 32 und die zweite Pumpenzelle 34 werden über einen gemeinsamen Zulauf 40, der in
Das Abschalten beziehungsweise Kurzschließen des ersten Ausganges 36 mit dem Hydraulikeingang 62 des erfindungsgemäß vorgeschlagenen Förderaggregates 30 erfolgt durch das erste Schaltventil 50 bei einem erreichten Druck von etwa 10 bar, bei dem die Kupplung anliegt. Nach Betätigung des ersten Schaltventiles 50 erfolgt ein weiterer Druckaufbau durch das erfindungsgemäß vorgeschlagene Förderaggregat 30 ausschließlich durch die zweite Pumpenzelle 34 bis auf ein Druckniveau in der Größenordnung von etwa 50 bar. Das genannte Druckniveau ist ausreichend, um ein Anpressen einer Kupplung an eine Kupplungsglocke oder an eine Kupplungsscheibe aufrechtzuerhalten und die einwandfreie Übertragung eines Drehmomentes sicherzustellen. Beim Anpressen, d. h. beim Betrieb der zweiten Pumpenzelle 34 des Förderaggregates 30, wird nicht benötigtes Fluid über ein Druckbegrenzungsventil 52 in Richtung Saugleitung, d. h. Eingang 62 und das dort angeschlossene Hydraulikreservoir, geführt. Mittels eines Drucksensors 54 wird der Druckanstieg erfasst. Das durch den Drucksensor 54 erfasste Schaltsignal dient als Signal zum Betätigen des ersten Schaltventiles 50 über eine Elektronik, die in einem nicht dargestellten Steuergerät aufgenommen sein kann. Über den Drucksensor 54 wird z. B. ein Druckniveau > 10 bar, d. h. im vorliegenden Falle ein beispielhaft herausgegriffenes Umschaltdruckniveau, erfasst, bei dem durch Betätigen des ersten Schaltventiles 50 der erste Ausgang 36 des erfindungsgemäß vorgeschlagenen Förderaggregates 30 mit dem Eingang 62 kurzgeschlossen wird.The switching off or short-circuiting of the
Das Aktivieren des in
Um unnötigen Verrohrungsaufwand in Gestalt von Hydraulikleitungen und dergleichen zu verhindern, können die einzelnen Komponenten, wie z. B. das Rückschlagventil 46, der Drucksensor 54, das Druckbegrenzungsventil 52, das erste Schaltventil 50 sowie das Schaltventil 56 zur Betätigung des Kupplungszylinders 44, komplett in das Pumpengehäuse 12 des Förderaggregates 30 integriert werden. Dies ist in der Darstellung gemäß
Der Figurensequenz der
Der Darstellung gemäß
In der in den
Auch in der in den
Die
Der Darstellung gemäß
Der Darstellung gemäß
Claims (10)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200610056843 DE102006056843A1 (en) | 2006-12-01 | 2006-12-01 | delivery unit |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1927753A2 true EP1927753A2 (en) | 2008-06-04 |
EP1927753A3 EP1927753A3 (en) | 2014-01-22 |
EP1927753B1 EP1927753B1 (en) | 2017-08-09 |
Family
ID=39198195
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07117628.3A Expired - Fee Related EP1927753B1 (en) | 2006-12-01 | 2007-10-01 | Conveying unit |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1927753B1 (en) |
DE (1) | DE102006056843A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010119336A3 (en) * | 2009-04-16 | 2012-01-19 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
US9611847B2 (en) | 2009-04-16 | 2017-04-04 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
US9902251B2 (en) | 2016-01-26 | 2018-02-27 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008054767A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | Conveying device, particularly gear wheel pump, has housing, with two housing units, where conveyor elements are formed as gear wheels and are inserted between two housing units |
DE102008054751A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | External gear pump for supplying of fuel in fuel-injection system of internal combustion engine, has two rotatable gear wheels which are engaged together, where bearing surface is arranged radially outward to gear wheel |
DE102008054755A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | Conveying device, particularly gear wheel pump, has housing, where surfaces of housing units have mounting surfaces for mounting conveyor elements |
DE102008054758A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | delivery unit |
DE102009028164A1 (en) | 2009-07-31 | 2011-02-03 | Robert Bosch Gmbh | Pump i.e. gear pump, for common-rail-fuel injection system of internal combustion engine of motor vehicle, has compressible damping element arranged on pressure channel of pump and made of plastic or elastomer |
DE102009028442A1 (en) | 2009-08-11 | 2011-02-17 | Robert Bosch Gmbh | Toothed wheel pump for use in common-rail-fuel injection system for combustion engine, has suction side and pressure side, where pressure-sided reverse flow channel manufactures hydraulic connection between pressure side and conveyor spaces |
DE102009028444A1 (en) | 2009-08-11 | 2011-02-17 | Robert Bosch Gmbh | Pressure limiting valve for hydraulic system, has two inputs and two outputs, where valve unit engages closing position, when both inputs obtains approximately low pressure |
DE102009047610A1 (en) | 2009-12-08 | 2011-06-09 | Robert Bosch Gmbh | External gear pump |
DE102012111637A1 (en) * | 2012-11-30 | 2014-06-05 | Trw Automotive Gmbh | Pump unit, especially for motor vehicles |
KR101680648B1 (en) * | 2015-09-10 | 2016-11-30 | 명화공업주식회사 | Dual pump system |
CN114876789B (en) * | 2022-01-25 | 2024-01-23 | 重庆正丰汇机械制造有限公司 | Variable-speed multi-gear pump and application method thereof |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3958494A (en) * | 1974-09-30 | 1976-05-25 | Moog Inc. | Multiple displacement hydraulic motor drive apparatus |
DE3837599A1 (en) * | 1988-11-05 | 1990-05-10 | Daimler Benz Ag | Gear pump having two pairs of gear wheels arranged next to one another in the pump casing |
DE19933484A1 (en) * | 1999-07-16 | 2001-01-18 | Bayerische Motoren Werke Ag | Pump unit for lubrication system of internal combustion engine, in which on of internal rotors has device for controlled interruption of drive connection |
EP1441126A2 (en) * | 2003-01-24 | 2004-07-28 | Kabushiki Kaisha Toyota Jidoshokki | Multistage gear pump |
-
2006
- 2006-12-01 DE DE200610056843 patent/DE102006056843A1/en not_active Ceased
-
2007
- 2007-10-01 EP EP07117628.3A patent/EP1927753B1/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3958494A (en) * | 1974-09-30 | 1976-05-25 | Moog Inc. | Multiple displacement hydraulic motor drive apparatus |
DE3837599A1 (en) * | 1988-11-05 | 1990-05-10 | Daimler Benz Ag | Gear pump having two pairs of gear wheels arranged next to one another in the pump casing |
DE19933484A1 (en) * | 1999-07-16 | 2001-01-18 | Bayerische Motoren Werke Ag | Pump unit for lubrication system of internal combustion engine, in which on of internal rotors has device for controlled interruption of drive connection |
EP1441126A2 (en) * | 2003-01-24 | 2004-07-28 | Kabushiki Kaisha Toyota Jidoshokki | Multistage gear pump |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010119336A3 (en) * | 2009-04-16 | 2012-01-19 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
US9611847B2 (en) | 2009-04-16 | 2017-04-04 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
US9902251B2 (en) | 2016-01-26 | 2018-02-27 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
US10919376B2 (en) | 2016-01-26 | 2021-02-16 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
Also Published As
Publication number | Publication date |
---|---|
DE102006056843A1 (en) | 2008-06-05 |
EP1927753A3 (en) | 2014-01-22 |
EP1927753B1 (en) | 2017-08-09 |
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