EP0708245B1 - Gear pump - Google Patents
Gear pump Download PDFInfo
- Publication number
- EP0708245B1 EP0708245B1 EP95115849A EP95115849A EP0708245B1 EP 0708245 B1 EP0708245 B1 EP 0708245B1 EP 95115849 A EP95115849 A EP 95115849A EP 95115849 A EP95115849 A EP 95115849A EP 0708245 B1 EP0708245 B1 EP 0708245B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- gear pump
- piston head
- piston
- area
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Images
Classifications
-
- 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
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
- F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
Definitions
- the invention relates to a gear pump, preferably an external gear pump consisting of at least two combing, counter-rotating, mounted in a housing Gears, one of which is a gear with a drive connected is.
- Gear pumps are suitable for sufficient delivery accuracy for many hydraulic drives.
- they will often as lubricating oil pumps in internal combustion engines used.
- the oil pressure generated by the gear pump cools piston crowns, lubricates and cools the piston raceway, Main and connecting rod bearings and rocker arm and supplies the Camshaft bearings.
- the promotion of the liquid comes in that these are released into the Tooth gaps of meshing gears occurs, in the direction of rotation on the outside of the casing Pressure zone moves and through the mutual intervention the teeth are pushed out of the gaps into the pressure chamber becomes.
- the document FR 2 392 255 describes a rotor pump, a deformable one opposite the front of the rotors Rubber membrane is arranged, which at the same time that of Drive side forms opposite side wall and where with increasing pressure the distance between the membrane and the rotors enlarged.
- the membrane is thicker in the middle than on the edges, which affects the deformation profile affects; for rapid wear of the membrane material To avoid, there must be a permanent distance even in the basic state between the membrane and the front of the rotors can be set.
- the gears (4, 5) opposite axial Pump housing wall (7) is coaxial with that Gear (5) through hole (8), the Area similar to the area of the tip circle of the teeth of the Gear (5) is.
- the Pump housing wall (7) is in front of the through hole (8) connected to the pump housing wall (7) Hollow cylinder (9) arranged coaxially. The inside diameter of the hollow cylinder (9) agrees with the diameter of the Through hole (8).
- a hollow cylinder Piston (10) slidably supported, in the basic state whose piston crown (11) on the front of the Gear (5) is present. Since the area of the Piston plate (11) similar to the area of the tip circle of the Teeth of the gear (5) is the end face completely covered. Between the inside of the Piston crown (11) and the inside of the Hollow cylinder (9) is a cylindrical one Helical compression spring (12) used by their Spring force of the face of the gear (5) completely covering piston head (11) in axial Direction pressed against the front of the gear (5) becomes.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
Die Erfindung betrifft eine Zahnradpumpe, vorzugsweise eine Außenzahnradpumpe, bestehend aus mindestens zwei kämmenden, gegenläufigen, in einem Gehäuse gelagerten Zahnrädern, von denen ein Zahnrad mit einem Antrieb verbunden ist.The invention relates to a gear pump, preferably an external gear pump consisting of at least two combing, counter-rotating, mounted in a housing Gears, one of which is a gear with a drive connected is.
Aufgrund ihres vergleichsweise einfachen Aufbaus bei ausreichender Fördergenauigkeit eignen sich Zahnradpumpen für viele hydraulische Antriebe. Insbesondere werden sie vielfach als Schmierölpumpen bei Brennkraftmaschinen verwendet. Der von der Zahnradpumpe erzeugte Öldruck kühlt Kolbenböden, schmiert und kühlt die Kolbenlaufbahn, Haupt- und Pleuellager sowie Kipphebel und versorgt die Nockenwellenlager. Die Förderung der Flüssigkeit kommt dadurch zustande, daß diese in die freiwerdenden Zahnlücken der miteinander kämmenden Zahnräder eintritt, in Drehrichtung am Gehäusemantel außen herum in die Druckzone wandert und durch das wechselseitige Eingreifen der Zähne aus den Lücken in den Druckraum herausgedrückt wird. Da jede Zahnlücke vor der vollständigen Entleerung durch den Zahn des Gegenzahnrades abgeschlossen wird, entsteht hier eine sogenannte Quetschflüssigkeit, die zur Vermeidung von Energieverlusten und eines harten Ganges der Zahnradpumpe durch Bohrungen oder Nuten in den Druckraum abgeleitet werden muß. Die nach dem Verdrängerprinzip arbeitenden Zahnradpumpen haben die Eigenschaft, daß mit steigender Drehzahl die Fördermenge und der Flüssigkeitsdruck proportional zunehmen und demzufolge ohne Regelung der zulässige Dauerbetriebsdruck - bei wirtschaftlichem Einsatz und hinreichender Lebensdauer - überschritten wird. Um die Fördermenge mit steigender Drehzahl der Zahnradpumpe und damit den Dauerbetriebsdruck konstant halten zu können, ist es bekannt, in der an den Druckraum der Zahnradpumpe anschließenden Druckleitung ein Überdruckventil vorzusehen, das bei Überschreiten eines vorgegebenen Dauerbetriebsdrucks öffnet, der Druck abgesenkt wird und die überschüssige Fördermenge an Flüssigkeit von der Druckleitung über eine Rücklaufleitung in den Flüssigkeitsbehälter zurückströmt. Dieser Regelablauf ist in nachteiliger Weise mit einer nicht unerheblichen Verlustleistung der Zahnradpumpe verbunden, die beispielsweise bei einer Fördermenge von 10 l/min etwa 1300 W beträgt; mit steigender Fördermenge nimmt die Verlustleistung nur relativ geringfügig ab. Hinzu kommt, daß die zurückströmende Flüssigkeitsmenge zur Schaumbildung in dem Flüssigkeitsbehälter führt und demzufolge Schaum angesaugt wird.Because of their comparatively simple structure Gear pumps are suitable for sufficient delivery accuracy for many hydraulic drives. In particular, they will often as lubricating oil pumps in internal combustion engines used. The oil pressure generated by the gear pump cools piston crowns, lubricates and cools the piston raceway, Main and connecting rod bearings and rocker arm and supplies the Camshaft bearings. The promotion of the liquid comes in that these are released into the Tooth gaps of meshing gears occurs, in the direction of rotation on the outside of the casing Pressure zone moves and through the mutual intervention the teeth are pushed out of the gaps into the pressure chamber becomes. Because every tooth gap before complete emptying is completed by the tooth of the counter gear, This creates a so-called squeezing liquid, which is used for Avoidance of energy loss and a hard gear the gear pump through holes or grooves in the Pressure chamber must be derived. The after Gear pumps have the displacement principle Property that the flow rate increases with increasing speed and the fluid pressure increase proportionally and consequently without regulation the permissible continuous operating pressure - with economical use and sufficient Lifetime - is exceeded. To the flow rate with increasing speed of the gear pump and thus the To be able to keep constant operating pressure constant, it is known in the adjoining the pressure chamber of the gear pump Pressure line to provide a pressure relief valve that at If a specified continuous operating pressure is exceeded, the pressure is lowered and the excess flow rate increases Liquid from the pressure line via a return line in the liquid container flows back. This control flow is disadvantageously with a not inconsiderable Power loss of the gear pump connected, for example at a delivery rate of 10 l / min is about 1300 W; With increasing output only takes the power loss relatively slightly. Add to that the backflow Amount of liquid for foam formation in the Liquid container leads and consequently sucked foam becomes.
Die Druckschrift FR 2 392 255 beschreibt eine Rotorenpumpe,
bei der gegenüber der Stirnseite der Rotoren eine verformbare
Gummimembran angeordnet ist, welche gleichzeitig die der
Antriebsseite gegenüberliegende Seitenwand bildet und wobei
mit steigendem Druck sich der Abstand zwischen der Membran und
den Rotoren vergrößert. Die Membran ist in ihrer Mitte dicker
als an den Rändern, was sich auf das Verformungsprofil
auswirkt; um einen schnellen Verschleiß des Membranmaterials
zu vermeiden, muss auch im Grundzustand ein Dauerabstand
zwischen der Membran und der Stirnseite der Rotoren
eingestellt werden.The
Es ist die Aufgabe der vorliegenden Erfindung, die eingangs
beschriebene Zahnradpumpe so zu gestalten, dass eine deutliche
Abnahme der Verlustleistung erzielt wird und die Schaumbildung
unterbleibt.
Die Lösung dieser Aufgabe erfolgt durch eine Zahnradpumpe, die
die im Anspruch 1 aufgeführten Merkmale besitzt. In den
Ansprüchen 2 bis 5 sind weitere Ausgestaltungen der
Zahnradpumpe gemäß Anspruch 1 angegeben.It is the object of the present invention to begin with
To design the gear pump described so that a clear
Decrease in power loss is achieved and foam formation
is omitted.
This problem is solved by a gear pump
has the features listed in
Die erfindungsgemäß ausgebildete Zahnradpumpe ist in der Zeichnung beispielhaft dargestellt und wird nachstehend erläutert. Es zeigen:
- Fig. 1
- eine räumliche Darstellung der Bauelemente der Zahnradpumpe und
- Fig. 2
- eine räumliche Darstellung der Zahnradpumpe mit einem Ausbruch.
- Fig. 1
- a spatial representation of the components of the gear pump and
- Fig. 2
- a spatial representation of the gear pump with a breakout.
Bei der Zahnradpumpe (1) kommt die Förderung der Flüssigkeit in der Weise zustande, daß die Flüssigkeit auf der Saugseite (2) in den Pumpenraum in die freiwerdenden Zahnlücken der kämmenden, in dem Pumpengehäuse (3) angeordneten gegenläufigen Zahnräder (4, 5) eintritt, in Drehrichtung außen herum am Gehäusemantel zur Druckseite (6) des Pumpenraums wandert und durch das wechselseitige Eingreifen der Zähne aus den Zahnlücken herausgedrückt wird. Da jede Zahnlücke vor der vollständigen Entleerung durch den Zahn des jeweiligen Gegenzahnrades (4, 5) abgeschlossen wird, entsteht hier eine sogenannte Quetschflüssigkeit, die zur Vermeidung von Energieverlusten und eines harten Ganges der Zahnräder (4, 5) durch nicht dargestellte Bohrungen in den Druckraum abgeleitet wird. Die Zahnräder (4, 5), von denen das eine Zahnrad (4) mit einem nicht dargestellten Antriebselement verbunden ist, laufen mit engstem Spiel zwischeneinander und dem Pumpengehäuse (3) in radialer und axialer Richtung. In der der Antriebsseite der Zahnradpumpe (1) gegenüberliegenden axialen Pumpengehäusewand (7) befindet sich ein koaxial zu dem Zahnrad (5) angebrachtes Durchgangsloch (8), dessen Fläche ähnlich der Fläche des Kopfkreises der Zähne des Zahnrads (5) ist. Auf der Außenseite der Pumpengehäusewand (7) ist vor dem Durchgangsloch (8) ein mit der Pumpengehäusewand (7) verbundener Hohlzylinder (9) koaxial angeordnet. Der Innendurchmesser des Hohlzylinders (9) stimmt mit dem Durchmesser des Durchgangslochs (8) überein. In der Bohrung des Hohlzylinders (9) ist ein hohlzylinderförmiger Kolben (10) verschiebbar gelagert, wobei im Grundzustand dessen Kolbenboden (11) an der Stirnseite des Zahnrades (5) anliegt. Da die Fläche des Kolbenbodens (11) ähnlich der Fläche des Kopfkreises der Zähne des Zahnrads (5) ist, ist dessen Stirnseite vollständig abgedeckt. Zwischen der Innenseite des Kolbenbodens (11) und der Innenseite des Hohlzylinders (9) ist eine zylindrische Schrauben-Druckfeder (12) eingesetzt, durch deren Federkraft der die Stirnseite des Zahnrads (5) vollständig abdeckender Kolbenboden (11) in axialer Richtung gegen die Stirnseite des Zahnrads (5) gedrückt wird.With the gear pump (1) comes the promotion of Liquid in such a way that the liquid on the suction side (2) into the pump room in the released tooth gaps of the combing, in the Pump housing (3) arranged in opposite directions Gears (4, 5) enters, in the direction of rotation on the outside Housing jacket moves to the pressure side (6) of the pump chamber and by the mutual engagement of the teeth from the Tooth gaps is pushed out. Because every tooth gap before complete emptying through the tooth of each Counter gear (4, 5) is completed here a so-called squeezing liquid that is used to avoid of energy losses and a hard gear Gears (4, 5) through holes, not shown, in the pressure chamber is derived. The gears (4, 5), from which the one gear (4) with a not shown Drive element is connected, run with the tightest play between each other and the pump housing (3) in a radial and axial direction. In the the drive side of the Gear pump (1) opposite axial Pump housing wall (7) is coaxial with that Gear (5) through hole (8), the Area similar to the area of the tip circle of the teeth of the Gear (5) is. On the outside of the Pump housing wall (7) is in front of the through hole (8) connected to the pump housing wall (7) Hollow cylinder (9) arranged coaxially. The inside diameter of the hollow cylinder (9) agrees with the diameter of the Through hole (8). In the bore of the Hollow cylinder (9) is a hollow cylinder Piston (10) slidably supported, in the basic state whose piston crown (11) on the front of the Gear (5) is present. Since the area of the Piston plate (11) similar to the area of the tip circle of the Teeth of the gear (5) is the end face completely covered. Between the inside of the Piston crown (11) and the inside of the Hollow cylinder (9) is a cylindrical one Helical compression spring (12) used by their Spring force of the face of the gear (5) completely covering piston head (11) in axial Direction pressed against the front of the gear (5) becomes.
Bei Überschreiten einer bestimmten Fördermenge bzw. eines vorgegebenen Betriebsdrucks wird der Kolben (10) gegen die Federkraft der Schrauben-Druckfeder (12) in den Hohlzylinder (9) hineingeschoben, so daß sich zwischen dem Kolbenboden (11) und der Stirnseite des Zahnrades (5) ein Spalt öffnet, ein Druckabbau erfolgt und die überschüssige Fördermenge über diesen Bypass unmittelbar zur Saugseite (2) des Pumpenraums der Zahnradpumpe (1) strömen kann. Das hat zur Folge, daß die Verlustleistung vergleichsweise deutlich sinkt und eine erheblich kleinere Flüssigkeitsmenge im Kreislauf geführt werden muß. Es wird nur die Flüssigkeitsmenge angesaugt, die tatsächlich verbraucht wird. Beträgt z.B. bei einer herkömmlichen Zahnradpumpe bei einer Umdrehungszahl von 3000 U/min die Verlustleistung bei einer Fördermenge von 20 l/min 1240 W, so wird durch den Einsatz der erfindungsgemäß ausgebildeten Zahnradpumpe die Verlustleistung auf 960 W erniedrigt. Darüber hinaus wird die Schaumbildung der Flüssigkeit vermieden.If a certain delivery rate or one is exceeded The predetermined operating pressure, the piston (10) against the spring force of the compression coil spring (12) in the Hollow cylinder (9) inserted so that between the piston crown (11) and the face of the gear wheel (5) a gap opens, pressure is released and the Excess flow through this bypass immediately to the suction side (2) of the pump chamber of the gear pump (1) can flow. As a result, the power loss comparatively significantly decreases and a significantly smaller amounts of liquid are circulated got to. Only the amount of liquid that is drawn in is actually consumed. For example, at a conventional gear pump at a speed of 3000 rpm the power loss with a delivery rate of 20 l / min 1240 W, so the use of Gear pump designed according to the invention Power loss reduced to 960 W. Beyond that avoided the foaming of the liquid.
Claims (5)
- Gear pump consisting of at least two meshing, contrarotating gear wheels (4, 5) mounted in a housing (3), of which one gear wheel is connected to a drive, characterised by a hollow cylinder (9) connected to the side wall (7) of the gear pump (1) opposing the drive side, and arranged axially on the outer side of the housing (3) in front of a through-hole (8) of the side wall, in the hole of which hollow cylinder (9) a hollow cylindrical piston (10) is mounted axially displaceably, and the piston head (11) of which is adjacent to the end face of the gear wheels (4, 5) in the initial state, wherein the piston head (11) completely covers the end face of at least one of the gear wheels (5).
- Gear pump according to claim 1, characterised in that the central points of the piston head (11) and tip circle of the teeth of the gear wheel (5) are located on one axis and in that the area of the piston head (11) is similar to the area of the tip circle of the teeth of the gear wheel (5).
- Gear pump according to claim 1, characterised in that the area of the piston head (11) is similar to the area of the envelopes of the tip circles of the teeth of the gear wheels (4, 5) and the end faces of the gear wheels (4, 5) are completely covered.
- Gear pump according to any one of claims 1 to 3, characterised in that a spring element (12) is inserted, with a desired pressure value predetermined by spring bias, between the inner side of the piston head (11) and the inner side of the cylinder cover.
- Gear pump according to any one of claims 1 to 4, characterised in that the piston (10) can be displaced hydraulically.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4436518 | 1994-10-13 | ||
| DE4436518A DE4436518A1 (en) | 1994-10-13 | 1994-10-13 | Gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0708245A1 EP0708245A1 (en) | 1996-04-24 |
| EP0708245B1 true EP0708245B1 (en) | 2001-08-16 |
Family
ID=6530622
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP95115849A Expired - Lifetime EP0708245B1 (en) | 1994-10-13 | 1995-10-09 | Gear pump |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0708245B1 (en) |
| DE (2) | DE4436518A1 (en) |
| ES (1) | ES2161815T3 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112011102000A5 (en) | 2010-06-14 | 2013-04-04 | Schaeffler Technologies AG & Co. KG | External gear pump |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB722667A (en) * | 1952-02-01 | 1955-01-26 | Zenith Carburateur Soc Du | Improvements in or relating to gear pumps and applications thereof |
| US2786553A (en) * | 1954-01-11 | 1957-03-26 | Wilford E Beattie | Fluid pressure controlled gear brake |
| CH476212A (en) * | 1966-06-24 | 1969-07-31 | Schindler Werner | Displacement pump |
| FR2054775A6 (en) * | 1969-07-25 | 1971-05-07 | Bertin & Cie | |
| ZA782350B (en) * | 1977-05-26 | 1979-04-25 | Stainless Steel Pumps Ltd | Lobe-rotor pump |
-
1994
- 1994-10-13 DE DE4436518A patent/DE4436518A1/en not_active Withdrawn
-
1995
- 1995-10-09 ES ES95115849T patent/ES2161815T3/en not_active Expired - Lifetime
- 1995-10-09 EP EP95115849A patent/EP0708245B1/en not_active Expired - Lifetime
- 1995-10-09 DE DE59509508T patent/DE59509508D1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| ES2161815T3 (en) | 2001-12-16 |
| EP0708245A1 (en) | 1996-04-24 |
| DE4436518A1 (en) | 1996-04-18 |
| DE59509508D1 (en) | 2001-09-20 |
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