EP2657525A2 - Gear machine with an axial seal stretching into the area of radial exterior surface of the correponding bearing support - Google Patents

Gear machine with an axial seal stretching into the area of radial exterior surface of the correponding bearing support Download PDF

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Publication number
EP2657525A2
EP2657525A2 EP13161225.1A EP13161225A EP2657525A2 EP 2657525 A2 EP2657525 A2 EP 2657525A2 EP 13161225 A EP13161225 A EP 13161225A EP 2657525 A2 EP2657525 A2 EP 2657525A2
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EP
European Patent Office
Prior art keywords
seal
bearing body
gear machine
machine according
gear
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.)
Granted
Application number
EP13161225.1A
Other languages
German (de)
French (fr)
Other versions
EP2657525B1 (en
EP2657525A3 (en
Inventor
Kai Sutter
Marc Laetzel
Stefan Cerny
Dieter Haecker
Ruediger Weiss
Christoph Kessler
Andreas Leinberger
Sebastian Birk
Guido Bredenfeld
Dietmar Schwuchow
Michael Wilhelm
Heinz Martin
Andreas Klaiber
Markus Stahl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2657525A2 publication Critical patent/EP2657525A2/en
Publication of EP2657525A3 publication Critical patent/EP2657525A3/en
Application granted granted Critical
Publication of EP2657525B1 publication Critical patent/EP2657525B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the invention relates to a gear machine according to the preamble of claim 1.
  • the gear machine comprises a housing in which two gears are arranged, which mesh with each other in external engagement.
  • the housing has an inner space which extends in the region of the housing main body with a constant cross-sectional shape along a longitudinal axis, wherein said cross-sectional shape is adapted to the gears.
  • two bearing bodies are provided, which are arranged with respect to the longitudinal axis on both sides next to the gears.
  • the radial outer surface of the bearing body is sealingly adapted to the interior, wherein the bearing body are minimally movable in the longitudinal direction to compensate for manufacturing tolerances.
  • the gears are rotatably mounted with an associated shaft or axis in two bearing bodies, wherein the axes of rotation extend parallel to the longitudinal direction.
  • an elastic seal is provided which sealingly contacts the housing to a separate end or a separate bearing cap.
  • This elongated seal extends in an axial plane which is oriented perpendicular to the longitudinal direction, wherein it is designed so that it can compensate for the above-mentioned manufacturing tolerances. It has the shape of the numeral "3", wherein the arcuate portions surround the axes of rotation of the associated gears.
  • the metal of the bearing body lies directly on the metal of the housing.
  • a seal is made solely by the achieved highly accurate adaptation of the housing to the bearing body.
  • both the housing and the bearing bodies deform by the fluid pressure acting inside the gear machine. This deformation can lead to the bearing bodies no longer abutting one another, at least in sections, so that hydraulic fluid can flow in the area of the radial outer surface of the bearing body from the high-pressure side to the low-pressure side. This reduces the volumetric efficiency of the gear machine.
  • the object of the invention is to improve the volumetric efficiency of the gear machine.
  • this object is achieved in that the seal has at least one direction change, wherein it extends with an associated end region along the radial outer surface of the associated bearing body. Due to the end region of the seal, the joint in the region of the radial outer surface is no longer sealed off only metallically, but by means of a separate elastic seal. The deformations occurring on the housing and on the bearing body during operation can easily be absorbed by the end region of the seals. As a result, there is no open sealing gap through which hydraulic fluid can flow from the high pressure side to the low pressure side of the gear machine.
  • the said change of direction can optionally be formed sharp-edged or curved with a small radius.
  • the seal may extend along the radially outer surface of the associated bearing body at both opposite end portions, with the end portions disposed adjacent to different gears.
  • Radial outer surface of the bearing body exist in the case of leaks two possible flow paths for the hydraulic oil from the high pressure side to the low pressure side. Each gear is associated with such a flow path.
  • the seal may extend in the end region parallel to the longitudinal direction. However, it is conceivable that the seal is bent in the end or oblique to the longitudinal direction. In a course parallel to the longitudinal direction, the seal is particularly short and thus saving material. Furthermore, the corresponding receiving contour for the end region of the seal, which is preferably arranged in the bearing body, can be produced particularly easily.
  • the seal may have a circular cross-sectional shape at least in the end region.
  • a seal with a circular cross-sectional shape is particularly easy to produce. In addition, it does not matter during installation in which rotational position the seal is installed, so that assembly errors are avoided.
  • the seal may also be formed with a circular cross-sectional shape. This is particularly advantageous if it is possible to dispense with the support element described below at low operating pressure.
  • the seal in the region of the axial plane preferably has a cross-sectional shape, which is adapted to the support element.
  • a receiving groove may be provided in the radial outer surface of the associated bearing body.
  • the cross-sectional dimensions of the seal are limited downwards so that it can absorb the deformations on the housing and on the bearing body. Therefore, a special receiving space for the seal is required in the area of the radial outer surface.
  • the receiving groove can end at a distance to the associated gear.
  • In the tooth spaces between the teeth of the gear may be hydraulic fluid, which may be under high pressure.
  • the proposed distance is intended to prevent this hydraulic fluid from penetrating the end face associated with the gearwheel into the receiving groove, which would certainly cause an internal leakage of the gearwheel machine, which has a negative effect on its volumetric efficiency.
  • a support member may be provided which extends only in the region of the axial plane along the seal.
  • the seal should be shielded by the pressure of the hydraulic fluid, for example, 280 bar, as this could be destroyed.
  • the support element In the area of the axial plane, the support element is required because there very large manufacturing tolerances must be compensated. Accordingly, there are free spaces available around the seal in which the hydraulic fluid could reach the seal under full pressure. In the area of the radial outer surface of the bearing body, however, only small manufacturing tolerances must be compensated, so that the seal can be installed under bias in the associated receiving space without leaving any free space. Accordingly, it is possible to dispense with the support element there.
  • the seal may have the shape of the numeral "3" in the area of the axial plane, the arcuate sections of which surround the axes of rotation of the associated toothed wheels, the seal separating two pressure fields from one another. This prevents hydraulic fluid from flowing from the high pressure to the low pressure side along the axial plane. At the same time the bearing body is pressed by the pressure fields against the gears, so that the sealing joint between the bearing body and the gears is tightly closed.
  • the support element can be pressed by the pressure of one of the two pressure fields against the associated seal. As a result, a particularly good seal in the axial plane is achieved.
  • the seal may be integrally formed over its entire length.
  • the seal is thus particularly inexpensive to produce, preferably by injection molding. At the same time it has no interruptions, which could cause leaks.
  • Fig. 1 shows an exploded view of a gear machine 10 according to the prior art, which is to be improved by the present invention.
  • the gear machine 10 comprises a housing 31; 40; 41, which consists of a main body 31, at the two opposite ends 34, a bearing cap 40 and an end cover 41 are arranged.
  • the housing 31; 40; 41 is held together by four bolts 44, of which in Fig. 1 only one is shown.
  • the main body 31 defines an inner space 11 of the housing that extends in a constant cross-sectional shape along a longitudinal direction 17.
  • the inner space 11 is closed by the bearing cap 40 and the end cap 41, wherein between the main body 31 and the covers 40; 41 each a lid seal 42 is arranged in the form of an O-ring made of rubber.
  • the constant cross-sectional shape of the inner space 11 is at the tip circle diameter of the first and second gears 12; 13 adjusted sealing.
  • With respect to the longitudinal direction 17 on both sides next to the first and the second gear 12; 13 is a respective bearing body 50 is arranged, the radial outer surface 55 is sealingly adapted to the interior 11.
  • the bearing body 50 are located on the flat side surfaces of the first and second gear 12; 13 sealingly.
  • the bearing bodies 50 are mirror-symmetrical to one another.
  • the first gear 12 is connected to a shaft 14 which passes through the bearing cap 40 with a drive pin 15 from the housing 31; 40; 41 stands out.
  • the second gear 13 is connected to an axle 16.
  • a radial shaft seal 43 is arranged, which sealingly rests with its sealing lip on the shaft 14, so that there is no hydraulic fluid can escape.
  • the axis 16 and the shaft 14 are rotatably mounted in two bearing bodies 50 in an associated bearing bore 51. In the bearing bore 51, a separate bearing bush is arranged, so that when the gear machine 10 runs at low speed, no excessive wear on the corresponding plain bearings occurs.
  • the gear machine 10 When the gear machine 10 is operated as a pump, hydraulic fluid is sucked in at the low pressure port 32, flowing out of the gear machine 10 at the high pressure port 33.
  • the gear machine When the gear machine is operated as a motor, the hydraulic fluid flows from the high-pressure port 33 to the low-pressure port 32, wherein the drive pin 15 is set in rotational motion.
  • the seal 60 is elongated and made of rubber, wherein it at the associated bearing or end cover 40; 41 is present. It has the shape of the numeral "3", with their bent portions surrounding the associated shaft 14 and the associated axis 16 at a small distance. Consequently, said curved parts also surround the axes of rotation of the gears 12, 13.
  • the seal 60 two pressure fields are delimited from each other, each of the pressure at the low pressure or at the high pressure port 32; 33 have. By these pressure fields, the bearing body 50 against the gears 12; 13 pressed so that the joint between the bearing body 50 and gears 12; 13 is closed fluid-tight.
  • a groove adapted to the shape of the seal 60 is provided in the bearing bodies 50.
  • a support member 54 is received, wherein the seal 60 rests on the support member 54.
  • the pressure at the high pressure port 33 is applied, so that the seal 60 against the associated lid 40; 41 is pressed.
  • This arrangement is required at a high operating pressure, for example, 280 bar, so that the seal 60 is not destroyed by the fluid pressure. At lower operating pressure can be dispensed with the support element if necessary.
  • the seal 60 has a tolerance-compensating function.
  • the length of the main body 31 is chosen so that it is greater than the sum of the lengths of the two bearing body 50 and the gears 12; 13 is. This is certainly excluded that the gear machine 10 is stuck during operation. In the vast majority of gear machines 10 of a group of mass-produced gear machines 10 is then between the bearing body 50 and the associated lid 40; 41 a small gap exists, which must be bridged by the seal 60 fluid-tight.
  • the bearing bodies 50 within the main body 31 with respect to the longitudinal direction 17 are minimally movable.
  • Fig. 2 shows a perspective view of a bearing body 50 with a seal 60 according to the invention.
  • the other bearing body is mirror-symmetrical to the present bearing body 50, so that it can be dispensed with its separate description.
  • the illustrated seal 60 is integrally formed over its entire length and formed with a constant circular cross-sectional shape, being made of rubber. A separate support element is not provided.
  • the bearing body 50 shown is therefore suitable only for low operating pressures. If high operating pressures are sought, this is in Fig. 1 shown supporting element required. It is sufficient if this as in Fig. 1 extends only in the region of an axial plane which is perpendicular to the longitudinal direction (No. 17 in Fig. 1 ) is aligned. At the end portions 61 of the seal 60, so on the radial outer surface 55 of the bearing body 50, no support member is required.
  • the gasket 60 has been elongated at both ends, where a direction change 63 has been provided so that the gasket 60 extends with its Endbvers 61 along the radial outer surface 55 of the bearing body 50.
  • the change of direction 63 is carried out so that the seal 60 securely seals the corner between the interior of the main body and the bearing or the end cover.
  • the end portions 61 of the seal 60 extend parallel to the longitudinal direction 17, being received in a receiving groove 57 of the bearing body 50.
  • the receiving groove 57 is adapted to the seal 60, that the seal 60 is deformed during assembly such that it substantially completely fills the receiving groove 57 when the bearing body 50 is installed in the main body.
  • the receiving groove 57 terminates at a distance 62 to the voltage applied to the gears flat end face of the bearing body 60. This ensures that the seal 60 is not damaged by the gears. It is also achieved that virtually no pressurized hydraulic fluid can flow into the receiving groove 57 from the gears.
  • the in Fig. 2 illustrated bearing body is mirror-symmetrical with respect to the plane of symmetry 58, so that both end portions 61 of the seal are formed identical. Only the in Fig. 2 left half of the bearing body 50 shows the actual shape. In the Fig. 2 right half of the bearing body 50 is shown in simplified form.
  • gear machine 11 inner space 12 first gear 13 second gear 14 wave 15 drive journal 16 axis 17 Lssenraum 31 main body 32 Low pressure port 33 High pressure port 34 front end 35 sealing plug 40 bearing cap 41 End covers 42 cover gasket 43 Radial shaft seal 44 bolts 50 bearing body 51 bearing bore 54 support element 55 radial outer surface 56 Leak oil passage 57 receiving groove 58 plane of symmetry 60 poetry 61 end 62 Distance to the gear 63 change of direction

Abstract

The machine has a housing whose inner space is arranged with two gear wheels. A bearing portion (50) is extended with a constant cross-sectional shape along a longitudinal direction (17). A radial outer surface (55) of bearing portion is formed as a sealing for inner space of housing. An elongated and resilient sealing portion (60) of bearing portion is sealingly contacted with housing, and oriented in an axial plane perpendicular to longitudinal axis. A direction change portion (63) is extended with an associated end portion (61) along outer surface of bearing portion.

Description

Die Erfindung betrifft eine Zahnradmaschine gemäß dem Oberbegriff von Anspruch 1.The invention relates to a gear machine according to the preamble of claim 1.

Aus der DE 28 47 711 A1 ist eine Zahnradmaschine bekannt, die sowohl als Pumpe als auch als Motor betrieben werden kann. Die Zahnradmaschine umfasst ein Gehäuse, in dem zwei Zahnräder angeordnet sind, welche im Außeneingriff miteinander kämmen. Das Gehäuse weist einen Innenraum auf, der sich im Bereich des Gehäusehauptkörpers mit einer konstanten Querschnittsform entlang einer Längsachse erstreckt, wobei die genannte Querschnittsform an die Zahnräder angepasst ist. Weiter sind zwei Lagerkörper vorgesehen, die bezüglich der Längsachse zu beiden Seiten neben den Zahnrädern angeordnet sind. Die radiale Außenoberfläche der Lagerkörper ist dichtend an den Innenraum angepasst, wobei die Lagerkörper in Längsrichtung minimal beweglich sind, um Fertigungstoleranzen auszugleichen. Die Zahnräder sind mit einer zugeordneten Welle bzw. Achse in beiden Lagerkörpern drehbar gelagert, wobei deren Drehachsen parallel zur Längsrichtung verlaufen. Weiter ist eine elastische Dichtung vorgesehen, welche das Gehäuse an einem gesonderten End- bzw. einem gesonderten Lagerdeckel dichtend berührt. Diese langgestreckte Dichtung erstreckt sich in einer Axialebene, die senkrecht zur Längsrichtung ausgerichtet ist, wobei sie so ausgebildet ist, dass sie die oben angesprochenen Fertigungstoleranzen ausgleichen kann. Sie weist die Form der Ziffer "3" auf, wobei deren bogenförmige Abschnitte die Drehachsen der zugeordneten Zahnräder umgeben. Durch die Dichtung werden zwei Druckfelder, nämlich ein Hochdruck- und ein Niederdruckfeld, voneinander abgegrenzt, welche die Lagerkörper gegen die Zahnräder drücken, um eine Abdichtung zu bewirken.From the DE 28 47 711 A1 is a gear machine known, which can be operated both as a pump and as a motor. The gear machine comprises a housing in which two gears are arranged, which mesh with each other in external engagement. The housing has an inner space which extends in the region of the housing main body with a constant cross-sectional shape along a longitudinal axis, wherein said cross-sectional shape is adapted to the gears. Next, two bearing bodies are provided, which are arranged with respect to the longitudinal axis on both sides next to the gears. The radial outer surface of the bearing body is sealingly adapted to the interior, wherein the bearing body are minimally movable in the longitudinal direction to compensate for manufacturing tolerances. The gears are rotatably mounted with an associated shaft or axis in two bearing bodies, wherein the axes of rotation extend parallel to the longitudinal direction. Next, an elastic seal is provided which sealingly contacts the housing to a separate end or a separate bearing cap. This elongated seal extends in an axial plane which is oriented perpendicular to the longitudinal direction, wherein it is designed so that it can compensate for the above-mentioned manufacturing tolerances. It has the shape of the numeral "3", wherein the arcuate portions surround the axes of rotation of the associated gears. By the seal two pressure fields, namely a high pressure and a low pressure field, are delimited from each other, which press the bearing body against the gears to effect a seal.

An der radialen Außenoberfläche des Lagerkörpers liegt das Metall des Lagerkörpers unmittelbar auf dem Metall des Gehäuses auf. Eine Abdichtung wird allein durch die hochgenaue Anpassung des Gehäuses an den Lagerkörper erzielt. Es hat sich jedoch gezeigt, dass sich sowohl das Gehäuse als auch die Lagerkörper durch den im Inneren der Zahnradmaschine wirkenden Fluiddruck verformen. Diese Verformung kann dazu führen, dass die Lagerkörper zumindest abschnittsweise nicht mehr dicht aneinander anliegen, so dass Hydraulikfluid im Bereich der radialen Außenoberfläche des Lagerkörpers von der Hochdruckseite zur Niederdruckseite fließen kann. Hierdurch sinkt der volumetrische Wirkungsgrad der Zahnradmaschine.At the radial outer surface of the bearing body, the metal of the bearing body lies directly on the metal of the housing. A seal is made solely by the achieved highly accurate adaptation of the housing to the bearing body. However, it has been found that both the housing and the bearing bodies deform by the fluid pressure acting inside the gear machine. This deformation can lead to the bearing bodies no longer abutting one another, at least in sections, so that hydraulic fluid can flow in the area of the radial outer surface of the bearing body from the high-pressure side to the low-pressure side. This reduces the volumetric efficiency of the gear machine.

Die Aufgabe der Erfindung besteht darin, den volumetrischen Wirkungsgrad der Zahnradmaschine zu verbessern.The object of the invention is to improve the volumetric efficiency of the gear machine.

Gemäß dem selbständigen Anspruch wird diese Aufgabe dadurch gelöst, dass die Dichtung wenigstens einen Richtungswechsel aufweist, wobei sie sich mit einem zugeordneten Endbereich entlang der radialen Außenoberfläche des zugeordneten Lagerkörpers erstreckt. Durch den Endbereich der Dichtung wird die Fuge im Bereich der radialen Außenoberfläche nicht mehr nur metallisch, sondern mittels einer gesonderten elastischen Dichtung abgedichtet. Die am Gehäuse und am Lagerkörper während des Betriebs auftretenden Verformungen können von dem Endbereich der Dichtungen ohne weiteres aufgenommen werden. In der Folge ergibt sich kein offener Dichtspalt, durch den Hydraulikfluid von der Hochdruckseite zur Niederdruckseite der Zahnradmaschine fließen kann. Aufgrund des Richtungswechsels der Dichtung ist eine solche Undichtigkeit insbesondere im kritischen Eckbereich zwischen Axialebene und radialer Außenumfangsfläche des Lagerkörpers ausgeschlossen, da die Dichtung dort unterbrechungsfrei verläuft. Der genannte Richtungswechsel kann wahlweise scharfkantig oder mit einem geringen Radius gebogen ausgebildet sein.According to the independent claim, this object is achieved in that the seal has at least one direction change, wherein it extends with an associated end region along the radial outer surface of the associated bearing body. Due to the end region of the seal, the joint in the region of the radial outer surface is no longer sealed off only metallically, but by means of a separate elastic seal. The deformations occurring on the housing and on the bearing body during operation can easily be absorbed by the end region of the seals. As a result, there is no open sealing gap through which hydraulic fluid can flow from the high pressure side to the low pressure side of the gear machine. Due to the change in direction of the seal, such a leak is excluded, in particular in the critical corner region between the axial plane and the radial outer peripheral surface of the bearing body, since the seal runs without interruption there. The said change of direction can optionally be formed sharp-edged or curved with a small radius.

In den abhängigen Ansprüchen sind vorteilhafte Weiterbildungen und Verbesserungen der Erfindung angegeben.In the dependent claims advantageous refinements and improvements of the invention are given.

Die Dichtung kann sich an beiden gegenüberliegenden Endbereichen entlang der radialen Außenoberfläche des zugeordneten Lagerkörpers erstrecken, wobei die Endbereiche benachbart zu unterschiedlichen Zahnrädern angeordnet sind. An der radialen Außenoberfläche der Lagerkörper existieren im Fall von Undichtigkeiten zwei mögliche Fließwege für das Hydrauliköl von der Hochdruckseite zur Niederdruckseite. Dabei ist jedem Zahnrad ein derartiger Fließweg zugeordnet. Durch die vorgeschlagene Dichtung können beide Fließwege abgedichtet werden.The seal may extend along the radially outer surface of the associated bearing body at both opposite end portions, with the end portions disposed adjacent to different gears. At the Radial outer surface of the bearing body exist in the case of leaks two possible flow paths for the hydraulic oil from the high pressure side to the low pressure side. Each gear is associated with such a flow path. By the proposed seal both flow paths can be sealed.

Die Dichtung kann sich im Endbereich parallel zur Längsrichtung erstrecken. Gleichwohl ist es denkbar, dass die Dichtung im Endbereich gebogen oder schräg zur Längsrichtung verläuft. Bei einem Verlauf parallel zur Längsrichtung ist die Dichtung aber besonders kurz und damit Material sparend. Weiter kann die entsprechende Aufnahmekontur für den Endbereich der Dichtung, welche vorzugsweise im Lagerkörper angeordnet ist, besonders einfach hergestellt werden.The seal may extend in the end region parallel to the longitudinal direction. However, it is conceivable that the seal is bent in the end or oblique to the longitudinal direction. In a course parallel to the longitudinal direction, the seal is particularly short and thus saving material. Furthermore, the corresponding receiving contour for the end region of the seal, which is preferably arranged in the bearing body, can be produced particularly easily.

Die Dichtung kann zumindest im Endbereich eine kreisförmige Querschnittsform aufweisen. Eine Dichtung mit kreisförmiger Querschnittsform ist besonders einfach herstellbar. Darüber hinaus kommt es bei der Montage nicht darauf an, in welcher Drehlage die Dichtung eingebaut wird, so dass Montagefehler vermieden werden. Im Bereich der Axialebene kann die Dichtung ebenfalls mit einer kreisförmigen Querschnittsform ausgebildet sein. Diese ist insbesondere dann vorteilhaft, wenn bei niedrigem Betriebsdruck auf das nachfolgend beschriebene Stützelement verzichtet werden kann. Soweit das Stützelement zum Einsatz kommt, weist die Dichtung im Bereich der Axialebene vorzugsweise eine Querschnittsform auf, welche an das Stützelement angepasst ist.The seal may have a circular cross-sectional shape at least in the end region. A seal with a circular cross-sectional shape is particularly easy to produce. In addition, it does not matter during installation in which rotational position the seal is installed, so that assembly errors are avoided. In the region of the axial plane, the seal may also be formed with a circular cross-sectional shape. This is particularly advantageous if it is possible to dispense with the support element described below at low operating pressure. As far as the support element is used, the seal in the region of the axial plane preferably has a cross-sectional shape, which is adapted to the support element.

Für jeden Endbereich der Dichtung kann eine Aufnahmenut in der radialen Außenoberfläche des zugeordneten Lagerkörpers vorgesehen sein. Die Querschnittsabmessungen der Dichtung sind nach unten begrenzt, damit sie die Verformungen am Gehäuse und am Lagerkörper aufnehmen kann. Daher ist auch im Bereich der radialen Außenfläche ein besonderer Aufnahmeraum für die Dichtung erforderlich. Dieser könnte zwar im Gehäuse, namentlich in dessen Hauptkörper, vorgesehen sein, die vorgeschlagene Ausführung in Form einer Nut am Lagerkörper ist jedoch einfacher herstellbar.For each end region of the seal, a receiving groove may be provided in the radial outer surface of the associated bearing body. The cross-sectional dimensions of the seal are limited downwards so that it can absorb the deformations on the housing and on the bearing body. Therefore, a special receiving space for the seal is required in the area of the radial outer surface. Although this could be provided in the housing, especially in its main body, the proposed embodiment in the form of a groove on the bearing body is easier to produce.

Die Aufnahmenut kann mit Abstand zu dem zugeordneten Zahnrad enden. In den Zahnlücken zwischen den Zähnen des Zahnrades kann sich Hydraulikfluid befinden, welches unter hohem Druck stehen kann. Durch den vorgeschlagenen Abstand soll verhindert werden, dass dieses Hydraulikfluid von der dem Zahnrad zugeordneten Stirnseite her in die Aufnahmenut eindringt, hierdurch würde erst recht eine interne Undichtigkeit der Zahnradmaschine bewirkt, welche sich negativ auf deren volumetrischen Wirkungsgrad auswirkt.The receiving groove can end at a distance to the associated gear. In the tooth spaces between the teeth of the gear may be hydraulic fluid, which may be under high pressure. The proposed distance is intended to prevent this hydraulic fluid from penetrating the end face associated with the gearwheel into the receiving groove, which would certainly cause an internal leakage of the gearwheel machine, which has a negative effect on its volumetric efficiency.

Zwischen der Dichtung und dem zugeordneten Lagerkörper kann ein Stützelement vorgesehen sein, das sich ausschließlich im Bereich der Axialebene entlang der Dichtung erstreckt. Durch das Stützelement soll die Dichtung von dem Druck des Hydraulikfluids von beispielsweise 280 bar abgeschirmt werden, da diese hierdurch zerstört werden könnte. Im Bereich der Axialebene ist das Stützelement erforderlich, da dort sehr große Fertigungstoleranzen ausgeglichen werden müssen. Dementsprechend stehen dort um die Dichtung herum Freiräume zur Verfügung, in denen das Hydraulikfluid unter vollem Druck zur Dichtung gelangen könnte. Im Bereich der radialen Außenoberfläche des Lagerkörpers müssen hingegen nur kleine Fertigungstoleranzen ausgeglichen werden, so dass die Dichtung unter Vorspannung in den zugeordneten Aufnahmeraum eingebaut werden kann, ohne dass Freiräume verbleiben. Dementsprechend kann auf das Stützelement dort verzichtet werden.Between the seal and the associated bearing body, a support member may be provided which extends only in the region of the axial plane along the seal. By the support member, the seal should be shielded by the pressure of the hydraulic fluid, for example, 280 bar, as this could be destroyed. In the area of the axial plane, the support element is required because there very large manufacturing tolerances must be compensated. Accordingly, there are free spaces available around the seal in which the hydraulic fluid could reach the seal under full pressure. In the area of the radial outer surface of the bearing body, however, only small manufacturing tolerances must be compensated, so that the seal can be installed under bias in the associated receiving space without leaving any free space. Accordingly, it is possible to dispense with the support element there.

Die Dichtung kann im Bereich der Axialebene die Form der Ziffer "3" aufweisen, wobei deren bogenförmige Abschnitte die Drehachsen der zugeordneten Zahnräder umgeben, wobei die Dichtung zwei Druckfelder voneinander abgrenzt. Hierdurch wird verhindert, dass Hydraulikfluid entlang der Axialebene von der Hochdruck- zur Niederdruckseite fließt. Gleichzeitig wird der Lagerkörper von den Druckfeldern gegen die Zahnräder gedrückt, so dass auch die Dichtfuge zwischen dem Lagerkörper und den Zahnrädern dicht verschlossen ist.The seal may have the shape of the numeral "3" in the area of the axial plane, the arcuate sections of which surround the axes of rotation of the associated toothed wheels, the seal separating two pressure fields from one another. This prevents hydraulic fluid from flowing from the high pressure to the low pressure side along the axial plane. At the same time the bearing body is pressed by the pressure fields against the gears, so that the sealing joint between the bearing body and the gears is tightly closed.

Das Stützelement kann vom Druck eines der beiden Druckfelder gegen die zugeordnete Dichtung gedrückt werden. Hierdurch wird eine besonders gute Abdichtung im Bereich der Axialebene erreicht.The support element can be pressed by the pressure of one of the two pressure fields against the associated seal. As a result, a particularly good seal in the axial plane is achieved.

Die Dichtung kann über ihre gesamte Länge einstückig ausgebildet sein. Die Dichtung ist damit besonders kostengünstig herstellbar, vorzugsweise im Spritzgussverfahren. Gleichzeitig weist sie keine Unterbrechungen auf, welche Undichtigkeiten bewirken könnten.The seal may be integrally formed over its entire length. The seal is thus particularly inexpensive to produce, preferably by injection molding. At the same time it has no interruptions, which could cause leaks.

Die Erfindung wird im Folgenden anhand der beigefügten Zeichnungen näher erläutert. Es stellt dar:

Fig. 1
eine Explosionsdarstellung einer Zahnradmaschine gemäß dem Stand der Technik, welche durch die vorliegende Erfindung verbessert werden soll; und
Fig. 2
eine perspektivische Darstellung eines Lagerkörpers mit einer erfindungsgemäßen Dichtung.
The invention will be explained in more detail below with reference to the accompanying drawings. It shows:
Fig. 1
an exploded view of a gear machine according to the prior art, which is to be improved by the present invention; and
Fig. 2
a perspective view of a bearing body with a seal according to the invention.

Fig. 1 zeigt eine Explosionsdarstellung einer Zahnradmaschine 10 gemäß dem Stand der Technik, welche durch die vorliegende Erfindung verbessert werden soll. Die Zahnradmaschine 10 umfasst ein Gehäuse 31; 40; 41, welches aus einem Hauptkörper 31 besteht, an dessen beiden gegenüber liegenden Stirnenden 34 ein Lagerdeckel 40 und ein Enddeckel 41 angeordnet sind. Das Gehäuse 31; 40; 41 wird durch vier Schraubbolzen 44 zusammengehalten, von denen in Fig. 1 nur einer dargestellt ist. Fig. 1 shows an exploded view of a gear machine 10 according to the prior art, which is to be improved by the present invention. The gear machine 10 comprises a housing 31; 40; 41, which consists of a main body 31, at the two opposite ends 34, a bearing cap 40 and an end cover 41 are arranged. The housing 31; 40; 41 is held together by four bolts 44, of which in Fig. 1 only one is shown.

Der Hauptkörper 31 begrenzt einen Innenraum 11 des Gehäuses, der sich mit einer konstanten Querschnittsform entlang einer Längsrichtung 17 erstreckt. Stirnseitig wird der Innenraum 11, durch den Lagerdeckel 40 und den Enddeckel 41 verschlossen, wobei zwischen dem Hauptkörper 31 und den Deckeln 40; 41 je eine Deckeldichtung 42 in Form eines O-Ringes aus Gummi angeordnet ist. In dem Innenraum 11 sind das erste und das zweite Zahnrad 12; 13 aufgenommen, welche im Außeneingriff miteinander kämmen. Die konstante Querschnittsform des Innenraums 11 ist an den Kopfkreisdurchmesser des ersten und des zweiten Zahnrades 12; 13 dichtend angepasst. Bezüglich der Längsrichtung 17 zu beiden Seiten neben dem ersten und dem zweiten Zahnrad 12; 13 ist je ein Lagerkörper 50 angeordnet, dessen radiale Außenoberfläche 55 dichtend an den Innenraum 11 angepasst ist. Dabei liegen die Lagerkörper 50 an den ebenen Seitenflächen des ersten und des zweiten Zahnrades 12; 13 dichtend an. Die Lagerkörper 50 sind spiegelsymmetrisch zueinander ausgebildet.The main body 31 defines an inner space 11 of the housing that extends in a constant cross-sectional shape along a longitudinal direction 17. At the front, the inner space 11 is closed by the bearing cap 40 and the end cap 41, wherein between the main body 31 and the covers 40; 41 each a lid seal 42 is arranged in the form of an O-ring made of rubber. In the inner space 11, the first and the second gear 12; 13 recorded, which mesh with each other in external engagement. The constant cross-sectional shape of the inner space 11 is at the tip circle diameter of the first and second gears 12; 13 adjusted sealing. With respect to the longitudinal direction 17 on both sides next to the first and the second gear 12; 13 is a respective bearing body 50 is arranged, the radial outer surface 55 is sealingly adapted to the interior 11. The bearing body 50 are located on the flat side surfaces of the first and second gear 12; 13 sealingly. The bearing bodies 50 are mirror-symmetrical to one another.

Das erste Zahnrad 12 ist mit einer Welle 14 verbunden, welche durch den Lagerdeckel 40 hindurch mit einem Antriebszapfen 15 aus dem Gehäuse 31; 40; 41 herausragt. Das zweite Zahnrad 13 ist mit einer Achse 16 verbunden. In dem Lagerdeckel 40 ist ein Radialwellendichtring 43 angeordnet, welcher mit seiner Dichtlippe dichtend an der Welle 14 anliegt, so dass dort kein Hydraulikfluid austreten kann. Die Achse 16 und die Welle 14 sind in beiden Lagerkörpern 50 in einer zugeordneten Lagerbohrung 51 drehbar gelagert. In der Lagerbohrung 51 ist eine gesonderte Lagerbuchse angeordnet, damit dann, wenn die Zahnradmaschine 10 mit geringer Drehzahl läuft, kein übermäßiger Verschleiß an den entsprechenden Gleitlagern auftritt.The first gear 12 is connected to a shaft 14 which passes through the bearing cap 40 with a drive pin 15 from the housing 31; 40; 41 stands out. The second gear 13 is connected to an axle 16. In the bearing cap 40, a radial shaft seal 43 is arranged, which sealingly rests with its sealing lip on the shaft 14, so that there is no hydraulic fluid can escape. The axis 16 and the shaft 14 are rotatably mounted in two bearing bodies 50 in an associated bearing bore 51. In the bearing bore 51, a separate bearing bush is arranged, so that when the gear machine 10 runs at low speed, no excessive wear on the corresponding plain bearings occurs.

Am Hauptkörper 21 ist ein Nieder- und ein Hochdruckanschluss 32; 33 angeordnet. In dem in Fig. 1 dargestellten Auslieferungszustand sind diese mit je einem gesonderten Verschlussstopfen 35 verschlossen, wobei der Niederdruckanschluss 32 den größeren Durchmesser und mithin den größeren Verschlussstopfen 35 aufweist. Wenn die Zahnradmaschine 10 als Pumpe betrieben wird, wird Hydraulikfluid am Niederdruckanschluss 32 angesaugt, wobei es am Hochdruckanschluss 33 aus der Zahnradmaschine 10 herausströmt. Wenn die Zahnradmaschine als Motor betrieben wird, strömt das Hydraulikfluid vom Hochdruckanschluss 33 zum Niederdruckanschluss 32, wobei der Antriebszapfen 15 in Drehbewegung versetzt wird.On the main body 21 is a low and a high pressure port 32; 33 arranged. In the in Fig. 1 As shown delivery state these are each closed with a separate stopper 35, wherein the low-pressure port 32 has the larger diameter and thus the larger stopper 35. When the gear machine 10 is operated as a pump, hydraulic fluid is sucked in at the low pressure port 32, flowing out of the gear machine 10 at the high pressure port 33. When the gear machine is operated as a motor, the hydraulic fluid flows from the high-pressure port 33 to the low-pressure port 32, wherein the drive pin 15 is set in rotational motion.

Weiter ist auf die Dichtung 60 hinzuweisen, welche im Rahmen der vorliegenden Erfindung modifiziert wird. Die Dichtung 60 ist langgestreckt ausgebildet und besteht aus Gummi, wobei sie an dem zugeordneten Lager- bzw. Enddeckel 40; 41 anliegt. Sie besitzt die Form der Ziffer "3", wobei deren gebogene Abschnitte die zugeordnete Welle 14 bzw. die zugeordnete Achse 16 mit geringem Abstand umgeben. Mithin umgeben die genannten gebogenen Teile auch die Drehachsen der Zahnräder 12, 13. Durch die Dichtung 60 werden zwei Druckfelder voneinander abgegrenzt, welche jeweils den Druck am Niederdruck- bzw. am Hochdruckanschluss 32; 33 aufweisen. Durch diese Druckfelder werden die Lagerkörper 50 gegen die Zahnräder 12; 13 gedrückt, so dass die Fuge zwischen dem Lagerkörper 50 und Zahnrädern 12; 13 fluiddicht verschlossen ist. In den Lagerkörpern 50 ist eine an die Form der Dichtung 60 angepasste Nut vorgesehen. In der genannten Nut ist ein Stützelement 54 aufgenommen, wobei die Dichtung 60 auf dem Stützelement 54 aufliegt. Auf der gegenüberliegenden Seite des Stützelementes 54 steht der Druck am Hochdruckanschluss 33 an, so dass die Dichtung 60 gegen den zugeordneten Deckel 40; 41 gedrückt wird. Diese Anordnung ist bei einem hohen Betriebsdruck von beispielsweise 280 bar erforderlich, damit die Dichtung 60 durch den Fluiddruck nicht zerstört wird. Bei niedrigerem Betriebsdruck kann auf das Stützelement ggf. verzichtet werden.Furthermore, reference should be made to the seal 60, which is modified in the context of the present invention. The seal 60 is elongated and made of rubber, wherein it at the associated bearing or end cover 40; 41 is present. It has the shape of the numeral "3", with their bent portions surrounding the associated shaft 14 and the associated axis 16 at a small distance. Consequently, said curved parts also surround the axes of rotation of the gears 12, 13. By the seal 60 two pressure fields are delimited from each other, each of the pressure at the low pressure or at the high pressure port 32; 33 have. By these pressure fields, the bearing body 50 against the gears 12; 13 pressed so that the joint between the bearing body 50 and gears 12; 13 is closed fluid-tight. In the bearing bodies 50, a groove adapted to the shape of the seal 60 is provided. In said groove, a support member 54 is received, wherein the seal 60 rests on the support member 54. On the opposite side of the support member 54, the pressure at the high pressure port 33 is applied, so that the seal 60 against the associated lid 40; 41 is pressed. This arrangement is required at a high operating pressure, for example, 280 bar, so that the seal 60 is not destroyed by the fluid pressure. At lower operating pressure can be dispensed with the support element if necessary.

Neben der Abgrenzung der genannten Druckfelder hat die Dichtung 60 eine Toleranz ausgleichende Funktion. Die Länge des Hauptkörpers 31 ist so gewählt, dass sie auch bei ungünstigster Toleranzlage größer als die Summe der Längen der beiden Lagerkörper 50 und der Zahnräder 12; 13 ist. Damit ist sicher ausgeschlossen, dass die Zahnradmaschine 10 im Betrieb klemmt. Bei den weitaus meisten Zahnradmaschinen 10 einer Gruppe von serienmäßig hergestellten Zahnradmaschinen 10 ist dann zwischen dem Lagerkörper 50 und dem zugeordneten Deckel 40; 41 ein kleiner Spalt vorhanden, welcher durch die Dichtung 60 fluiddicht überbrückt werden muss. Zum Zwecke des Toleranzausgleichs sind die Lagerkörper 50 innerhalb des Hauptkörpers 31 bezüglich der Längsrichtung 17 minimal beweglich.In addition to the delimitation of the pressure fields mentioned, the seal 60 has a tolerance-compensating function. The length of the main body 31 is chosen so that it is greater than the sum of the lengths of the two bearing body 50 and the gears 12; 13 is. This is certainly excluded that the gear machine 10 is stuck during operation. In the vast majority of gear machines 10 of a group of mass-produced gear machines 10 is then between the bearing body 50 and the associated lid 40; 41 a small gap exists, which must be bridged by the seal 60 fluid-tight. For the purpose of tolerance compensation, the bearing bodies 50 within the main body 31 with respect to the longitudinal direction 17 are minimally movable.

Im Gegensatz dazu ist an der radialen Außenoberfläche 55 des Lagerkörpers 50 keine gesonderte Dichtung vorgesehen. Die radiale Außenoberfläche 55 der Lagerkörper 50 liegt vielmehr nur metallisch an der Innenoberfläche des Innenraums 11 an. Die Abdichtung wird allein durch die genaue Anpassung der Lagerkörper 50 an den Hauptkörper 31 erreicht.In contrast, no separate seal is provided on the radially outer surface 55 of the bearing body 50. The radial outer surface 55 of the bearing body 50 is rather only metallic on the inner surface of the inner space 11 at. The seal is achieved solely by the exact adaptation of the bearing body 50 to the main body 31.

Fig. 2 zeigt eine perspektivische Darstellung eines Lagerkörpers 50 mit einer erfindungsgemäßen Dichtung 60. Der andere Lagerkörper ist spiegelsymmetrisch zu dem vorliegenden Lagerkörper 50 ausgebildet, so dass auf seine gesonderte Beschreibung verzichtet werden kann. Fig. 2 shows a perspective view of a bearing body 50 with a seal 60 according to the invention. The other bearing body is mirror-symmetrical to the present bearing body 50, so that it can be dispensed with its separate description.

Die dargestellte Dichtung 60 ist über ihre gesamte Länge einstückig ausgebildet und mit einer konstanten kreisrunden Querschnittsform ausgebildet, wobei sie aus Gummi besteht. Ein gesondertes Stützelement ist nicht vorgesehen. Der gezeigte Lagerkörper 50 ist demnach nur für niedrige Betriebsdrücke geeignet. Sofern hohe Betriebsdrücke angestrebt werden, ist das in Fig. 1 gezeigte Stützelement erforderlich. Dabei reicht es aus, wenn sich dieses wie in Fig. 1 allein in Bereich einer Axialebene erstreckt, die senkrecht zur Längsrichtung (Nr. 17 in Fig. 1) ausgerichtet ist. An den Endbereichen 61 der Dichtung 60, also an der radialen Außenoberfläche 55 des Lagerkörpers 50, ist kein Stützelement erforderlich.The illustrated seal 60 is integrally formed over its entire length and formed with a constant circular cross-sectional shape, being made of rubber. A separate support element is not provided. The bearing body 50 shown is therefore suitable only for low operating pressures. If high operating pressures are sought, this is in Fig. 1 shown supporting element required. It is sufficient if this as in Fig. 1 extends only in the region of an axial plane which is perpendicular to the longitudinal direction (No. 17 in Fig. 1 ) is aligned. At the end portions 61 of the seal 60, so on the radial outer surface 55 of the bearing body 50, no support member is required.

Gegenüber der Fig. 1 wurde die Dichtung 60 an beiden Enden verlängert, wobei dort ein Richtungswechsel 63 vorgesehen wurde, so dass sich die Dichtung 60 mit ihren Endbreichen 61 entlang der radialen Außenoberfläche 55 des Lagerkörpers 50 erstreckt. Der Richtungswechsel 63 wird dabei so ausgeführt, dass die Dichtung 60 auch die Ecke zwischen dem Innenraum des Hauptkörpers und dem Lager- bzw. dem Enddeckel sicher abdichtet. Die Endbereiche 61 der Dichtung 60 erstrecken sich parallel zur Längsrichtung 17, wobei sie in einer Aufnahmenut 57 des Lagerkörpers 50 aufgenommen sind. Die Aufnahmenut 57 ist dabei so an die Dichtung 60 angepasst, dass die Dichtung 60 sich bei der Montage derart verformt, dass sie die Aufnahmenut 57 im Wesentlichen vollständig ausfüllt, wenn der Lagerkörper 50 in den Hauptkörper eingebaut ist.Opposite the Fig. 1 For example, the gasket 60 has been elongated at both ends, where a direction change 63 has been provided so that the gasket 60 extends with its Endbreichen 61 along the radial outer surface 55 of the bearing body 50. The change of direction 63 is carried out so that the seal 60 securely seals the corner between the interior of the main body and the bearing or the end cover. The end portions 61 of the seal 60 extend parallel to the longitudinal direction 17, being received in a receiving groove 57 of the bearing body 50. The receiving groove 57 is adapted to the seal 60, that the seal 60 is deformed during assembly such that it substantially completely fills the receiving groove 57 when the bearing body 50 is installed in the main body.

Die Aufnahmenut 57 endet mit Abstand 62 zu der an den Zahnrädern anliegenden ebenen Stirnfläche des Lagerkörpers 60. Hierdurch wird erreicht, dass die Dichtung 60 durch die Zahnräder nicht beschädigt wird. Weiter wird erreicht, dass von den Zahnrädern her nahezu kein unter Druck stehendes Hydraulikfluid in die Aufnahmenut 57 einströmen kann.The receiving groove 57 terminates at a distance 62 to the voltage applied to the gears flat end face of the bearing body 60. This ensures that the seal 60 is not damaged by the gears. It is also achieved that virtually no pressurized hydraulic fluid can flow into the receiving groove 57 from the gears.

Der in Fig. 2 dargestellte Lagerkörper ist spiegelsymmetrisch bezüglich der Symmetrieebene 58 ausgebildet, so dass beide Endbereiche 61 der Dichtung identisch ausgebildet sind. Nur die in Fig. 2 linke Hälfte des Lagerkörpers 50 zeigt die tatsächliche Gestalt. Die in Fig. 2 rechte Hälfte des Lagerkörpers 50 ist dagegen vereinfacht dargestellt.The in Fig. 2 illustrated bearing body is mirror-symmetrical with respect to the plane of symmetry 58, so that both end portions 61 of the seal are formed identical. Only the in Fig. 2 left half of the bearing body 50 shows the actual shape. In the Fig. 2 right half of the bearing body 50 is shown in simplified form.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1010 Zahnradmaschinegear machine 1111 Innenrauminner space 1212 erstes Zahnradfirst gear 1313 zweites Zahnradsecond gear 1414 Wellewave 1515 Antriebszapfendrive journal 1616 Achseaxis 1717 LängrichtungLängrichtung 3131 Hauptkörpermain body 3232 NiederdruckanschlussLow pressure port 3333 HochdruckanschlussHigh pressure port 3434 Stirnendefront end 3535 Verschlussstopfensealing plug 4040 Lagerdeckelbearing cap 4141 EnddeckelEnd covers 4242 Deckeldichtungcover gasket 4343 RadialwellendichtringRadial shaft seal 4444 Schraubbolzenbolts 5050 Lagerkörperbearing body 5151 Lagerbohrungbearing bore 5454 Stützelementsupport element 5555 radiale Außenoberflächeradial outer surface 5656 LecköldurchlassLeak oil passage 5757 Aufnahmenutreceiving groove 5858 Symmetrieebeneplane of symmetry 6060 Dichtungpoetry 6161 Endbereichend 6262 Abstand zum ZahnradDistance to the gear 6363 Richtungswechselchange of direction

Claims (10)

Zahnradmaschine (10), insbesondere Außenzahnradpumpe oder Außenzahnradmotor, mit einem Gehäuse (31; 40; 41), in dessen Innenraum (11) wenigstens zwei Zahnräder (12; 13) angeordnet sind, die im Außeneingriff miteinander kämmen, wobei der Innenraum (11) des Gehäuses (31; 40; 41) sich mit einer konstanten Querschnittsform entlang einer Längsrichtung (17) erstreckt, wobei die genannte Querschnittsform an die Zahnräder (12; 13) angepasst ist, wobei wenigstens ein Lagerkörper (50) vorgesehen ist, der bezüglich der Längsrichtung (17) neben den Zahnrändern (12; 13) angeordnet ist, wobei dessen radiale Außenoberfläche (55) an den Innenraum (11) dichtend angepasst ist, wobei er in Längsrichtung (17) beweglich ist, wobei die Zahnräder (12; 13) in dem wenigstens einen Lagerkörper (50) drehbar gelagert sind, wobei dem wenigstens einen Lagerkörper (50) eine langgestreckte, elastische Dichtung (60) zugeordnet ist, welche das Gehäuse (40; 41) dichtend berührt, wobei sich die Dichtung (60) abschnittsweise in einer Axialebene erstreckt, die senkrecht zur Längsachse (17) ausgerichtet ist,
dadurch gekennzeichnet, dass die Dichtung (60) wenigstens einen Richtungswechsel (63) aufweist, wobei sie sich mit einem zugeordneten Endbereich (61) entlang der radialen Außenoberfläche (55) des zugeordneten Lagerkörpers (50) erstreckt.Gear machine (10), in particular external gear pump or external gear motor, with a housing (31; 40; 41), in the interior of which (11) at least two toothed wheels (12; 13) are arranged, which mesh with each other in external engagement, the interior (11) the housing (31; 40; 41) extends in a constant cross-sectional shape along a longitudinal direction (17), said cross-sectional shape being conformed to the gears (12; 13), at least one bearing body (50) being provided with respect to Longitudinal direction (17) next to the toothed edges (12; 13) is arranged, wherein the radial outer surface (55) is sealingly adapted to the inner space (11), wherein it is movable in the longitudinal direction (17), wherein the gears (12; 13) in which at least one bearing body (50) is rotatably mounted, wherein the at least one bearing body (50) is associated with an elongated elastic seal (60) which sealingly contacts the housing (40; 41), wherein the seal section (60) extends in an axial plane, which is aligned perpendicular to the longitudinal axis (17),
characterized in that the seal (60) has at least one change of direction (63), wherein it extends with an associated end region (61) along the radial outer surface (55) of the associated bearing body (50). Zahnradmaschine nach Anspruch 1,
dadurch gekennzeichnet, dass sich die Dichtung (60) an beiden gegenüber liegenden Endbereichen (61) entlang der radialen Außenoberfläche (55) des zugeordneten Lagerkörpers (50) erstreckt, wobei die Endbereiche (61) benachbart zu unterschiedlichen Zahnrädern (12; 13) angeordnet sind.Gear machine according to claim 1,
characterized in that the seal (60) extends at both opposite end portions (61) along the radially outer surface (55) of the associated bearing body (50), the end portions (61) being adjacent to different gears (12; 13) , Zahnradmaschine nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass sich die Dichtung (60) im Endbereich (61) parallel zur Längsrichtung (17) erstreckt.Gear machine according to one of the preceding claims,
characterized in that the seal (60) in the end region (61) extends parallel to the longitudinal direction (17). Zahnradmaschine nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass die Dichtung (60) zumindest im Endbereich (61) eine kreisförmige Querschnittsform aufweist.Gear machine according to one of the preceding claims,
characterized in that the seal (60) at least in the end region (61) has a circular cross-sectional shape. Zahnradmaschine nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass für jeden Endbereich (61) der Dichtung eine Aufnahmenut (57) in der radialen Außenoberfläche (55) des zugeordneten Lagerkörpers (50) vorgesehen ist.Gear machine according to one of the preceding claims,
characterized in that a receiving groove (57) in the radial outer surface (55) of the associated bearing body (50) is provided for each end region (61) of the seal. Zahnradmaschine nach Anspruch 5,
dadurch gekennzeichnet, dass die Aufnahmenut (57) mit Abstand (62) zu dem zugeordneten Zahnrad (12; 13) endet.Gear machine according to claim 5,
characterized in that the receiving groove (57) at a distance (62) to the associated gear (12; 13) ends. Zahnradmaschine nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass zwischen der Dichtung (60) und dem zugeordneten Lagerkörper (50) ein Stützelement (54) vorgesehen ist, das sich ausschließlich im Bereich der Axialebene entlang der Dichtung (60) erstreckt.Gear machine according to one of the preceding claims,
characterized in that between the seal (60) and the associated bearing body (50), a support member (54) is provided, which extends only in the region of the axial plane along the seal (60). Zahnradmaschine nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass die Dichtung (60) im Bereich der Axialebene die Form der Ziffer "3" aufweist, wobei deren bogenförmige Abschnitte die Drehachsen der zugeordneten Zahnräder (12; 13) umgeben, wobei die Dichtung (60) zwei Druckfelder voneinander abgrenzt.Gear machine according to one of the preceding claims,
characterized in that the seal (60) in the region of the axial plane in the shape of the numeral "3", wherein the arcuate portions of the axes of rotation of the associated gears (12; 13) surrounded, wherein the seal (60) delimits two pressure fields from each other. Zahnradmaschine nach Anspruch 8, rückbezogen auf Anspruch 7,
dadurch gekennzeichnet, dass das Stützelement (54) vom Druck eines der beiden Druckfelder gegen die zugeordnete Dichtung (60) gedrückt wird.Gear machine according to claim 8, when dependent on claim 7,
characterized in that the support element (54) is pressed by the pressure of one of the two pressure fields against the associated seal (60). Zahnradmaschine nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass die Dichtung (60) über ihre gesamte Länge einstückig ausgebildet ist.Gear machine according to one of the preceding claims,
characterized in that the seal (60) is integrally formed over its entire length.
EP13161225.1A 2012-04-27 2013-03-27 Gear machine with an axial seal stretching into the area of radial exterior surface of the correponding bearing support Active EP2657525B1 (en)

Applications Claiming Priority (1)

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DE102012207078A DE102012207078A1 (en) 2012-04-27 2012-04-27 Gear machine with an axial seal, which extends in the region of the radial outer surface of the associated bearing body

Publications (3)

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EP2657525A2 true EP2657525A2 (en) 2013-10-30
EP2657525A3 EP2657525A3 (en) 2015-12-30
EP2657525B1 EP2657525B1 (en) 2017-10-18

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018019587A1 (en) * 2016-07-26 2018-02-01 Robert Bosch Gmbh External gear pump for a waste heat recovery system
EP3754196A1 (en) * 2019-06-17 2020-12-23 Hamilton Sundstrand Corporation Bearing with an eccentric seal groove
WO2023041642A1 (en) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Metering pump for delivering abrasive fluids

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017207486A1 (en) * 2017-05-04 2018-11-08 Robert Bosch Gmbh External gear machine, exhaust heat recovery system with an external gear machine
DE102019130723A1 (en) * 2019-11-14 2021-05-20 Fte Automotive Gmbh Liquid pump

Citations (1)

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Publication number Priority date Publication date Assignee Title
DE2847711A1 (en) 1978-11-03 1980-05-14 Bosch Gmbh Robert GEAR MACHINE (PUMP OR HYDROMOTOR)

Family Cites Families (2)

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Publication number Priority date Publication date Assignee Title
US3137239A (en) * 1962-04-27 1964-06-16 Borg Warner Pressure loaded pumps
US6902382B2 (en) * 2003-09-11 2005-06-07 Matthew Peter Christensen Gear motor start up control

Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
DE2847711A1 (en) 1978-11-03 1980-05-14 Bosch Gmbh Robert GEAR MACHINE (PUMP OR HYDROMOTOR)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018019587A1 (en) * 2016-07-26 2018-02-01 Robert Bosch Gmbh External gear pump for a waste heat recovery system
EP3754196A1 (en) * 2019-06-17 2020-12-23 Hamilton Sundstrand Corporation Bearing with an eccentric seal groove
US10962059B2 (en) 2019-06-17 2021-03-30 Hamilton Sundstrand Corporation Bearing with an eccentric seal groove
WO2023041642A1 (en) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Metering pump for delivering abrasive fluids

Also Published As

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EP2657525B1 (en) 2017-10-18
EP2657525A3 (en) 2015-12-30
DE102012207078A1 (en) 2013-10-31

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