EP2657525B1 - 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 PDFInfo
- Publication number
- EP2657525B1 EP2657525B1 EP13161225.1A EP13161225A EP2657525B1 EP 2657525 B1 EP2657525 B1 EP 2657525B1 EP 13161225 A EP13161225 A EP 13161225A EP 2657525 B1 EP2657525 B1 EP 2657525B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- seal
- bearing body
- gear machine
- gearwheels
- 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.)
- Active
Links
- 238000007789 sealing Methods 0.000 claims description 7
- 239000012530 fluid Substances 0.000 description 13
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000006978 adaptation Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Images
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
- 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
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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
- 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
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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
- 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 extends at both opposite end portions along the radially outer surface of the associated bearing body, the end portions being disposed adjacent to different gears.
- the seal extends in the end region parallel to the longitudinal direction.
- the seal is bent in the end or oblique to the longitudinal direction.
- the seal is particularly short and thus saving material.
- 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. This could indeed in the housing, especially in its main body, be provided, however, the proposed design in the form of a groove on the bearing body is easier to produce.
- 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 has 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 is 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. She 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 gearwheels 12, 13.
- the seal 60 delimits two pressure fields from one another, which in each case determine the pressure at the low pressure or 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 60th 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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Sealing Devices (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Shaping By String And By Release Of Stress In Plastics And The Like (AREA)
- Hydraulic Motors (AREA)
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
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.
Aus der
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 erstreckt sich an beiden gegenüberliegenden Endbereichen entlang der radialen Außenoberfläche des zugeordneten Lagerkörpers, 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 extends at both opposite end portions along the radially outer surface of the associated bearing body, the end portions being disposed adjacent to different gears. On 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 erstreckt sich im Endbereich parallel zur Längsrichtung. 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 extends 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. This could indeed in the housing, especially in its main body, be provided, however, the proposed design 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 weist im Bereich der Axialebene die Form der Ziffer "3" auf, 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 has 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 ist über ihre gesamte Länge einstückig ausgebildet. Die Dichtung ist damit besonders kostengünstig herstellbar, vorzugsweise im Spritzgussverfahren. Gleichzeitig weist sie keine Unterbrechungen auf, welche Undichtigkeiten bewirken könnten.The seal is 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.
- 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.
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
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
Am Hauptkörper 21 ist ein Nieder- und ein Hochdruckanschluss 32; 33 angeordnet. In dem in
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
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
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
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
Gegenüber der
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
Der in
- 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 (6)
- Gear machine (10), in particular external gear pump or external gear motor, having a housing (31; 40; 41), in the interior space (11) of which at least two gearwheels (12; 13) are arranged which mesh with one another in external engagement, the interior space (11) of the housing (31; 40; 41) extending with a constant cross-sectional shape along a longitudinal direction (17), the said cross-sectional shape being adapted to the gearwheels (12; 13), at least one bearing body (50) being provided which is arranged next to the gearwheels (12; 13) with regard to the longitudinal direction (17), the radial outer surface (55) of which bearing body is adapted sealingly to the interior space (11), the said bearing body (50) being movable in the longitudinal direction (17), the gearwheels (12; 13) being mounted rotatably in the at least one bearing body (50), the at least one bearing body (50) being assigned an elongate, elastic seal (60) which makes sealing contact with the housing (40; 41), the seal (60) extending in sections in an axial plane which is oriented perpendicularly with respect to the longitudinal axis (17), the seal (60) having at least one direction change (63), the said seal (60) extending with an associated end region (61) along the radial outer surface (55) of the associated bearing body (50), the seal (60) extending at the two opposite end regions (61) along the radial outer surface (55) of the associated bearing body (50), the end regions (61) being arranged adjacently with respect to different gearwheels (12; 13), the seal (60) extending parallel to the longitudinal direction (17) in the end region (61), the seal (60) being configured in one piece over its entire length, characterized in that the seal (60) has the shape of the numeral "3" in the region of the axial plane, its arcuate sections surrounding the rotational axes of the associated gearwheels (12; 13), the seal (60) separating two pressure fields from one another.
- Gear machine according to Claim 1, characterized in that the seal (60) has a circular cross-sectional shape at least in the end region (61).
- Gear machine according to either of the preceding claims, characterized in that a receiving groove (57) is provided for each end region (61) in the radial outer surface (55) of the associated bearing body (50).
- Gear machine according to Claim 3, characterized in that the receiving groove (57) ends at a spacing (62) from the associated gearwheel (12; 13).
- Gear machine according to one of the preceding claims, characterized in that a supporting element (54) is provided between the seal (60) and the associated bearing body (50), which supporting element (54) extends along the seal (60) exclusively in the region of the axial plane.
- Gear machine according to Claim 5, characterized in that the supporting element (54) is pressed against the associated seal (60) by the pressure of one of the two pressure fields.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
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)
Publication Number | Publication Date |
---|---|
EP2657525A2 EP2657525A2 (en) | 2013-10-30 |
EP2657525A3 EP2657525A3 (en) | 2015-12-30 |
EP2657525B1 true EP2657525B1 (en) | 2017-10-18 |
Family
ID=48049782
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13161225.1A Active EP2657525B1 (en) | 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 |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2657525B1 (en) |
DE (1) | DE102012207078A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021004717A1 (en) | 2021-09-20 | 2023-03-23 | Oerlikon Textile Gmbh & Co. Kg | Dosing pump for conveying abrasive fluids |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016213636A1 (en) * | 2016-07-26 | 2018-02-01 | Robert Bosch Gmbh | External gear pump for a waste heat recovery system |
DE102017207486A1 (en) * | 2017-05-04 | 2018-11-08 | Robert Bosch Gmbh | External gear machine, exhaust heat recovery system with an external gear machine |
US10962059B2 (en) * | 2019-06-17 | 2021-03-30 | Hamilton Sundstrand Corporation | Bearing with an eccentric seal groove |
DE102019130723A1 (en) | 2019-11-14 | 2021-05-20 | Fte Automotive Gmbh | Liquid pump |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3137239A (en) * | 1962-04-27 | 1964-06-16 | Borg Warner | Pressure loaded pumps |
DE2847711A1 (en) | 1978-11-03 | 1980-05-14 | Bosch Gmbh Robert | GEAR MACHINE (PUMP OR HYDROMOTOR) |
US6902382B2 (en) * | 2003-09-11 | 2005-06-07 | Matthew Peter Christensen | Gear motor start up control |
-
2012
- 2012-04-27 DE DE102012207078A patent/DE102012207078A1/en not_active Withdrawn
-
2013
- 2013-03-27 EP EP13161225.1A patent/EP2657525B1/en active Active
Non-Patent Citations (1)
Title |
---|
None * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021004717A1 (en) | 2021-09-20 | 2023-03-23 | Oerlikon Textile Gmbh & Co. Kg | Dosing pump for conveying abrasive fluids |
Also Published As
Publication number | Publication date |
---|---|
EP2657525A3 (en) | 2015-12-30 |
DE102012207078A1 (en) | 2013-10-31 |
EP2657525A2 (en) | 2013-10-30 |
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