EP2657525A2 - Machine à roue dentée dotée d'un joint axial qui s'étend dans la zone de la surface extérieure radiale du corps de palier associé - Google Patents

Machine à roue dentée dotée d'un joint axial qui s'étend dans la zone de la surface extérieure radiale du corps de palier associé 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
Authority
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)
English (en)
Other versions
EP2657525A3 (fr
EP2657525B1 (fr
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2657525A2 publication Critical patent/EP2657525A2/fr
Publication of EP2657525A3 publication Critical patent/EP2657525A3/fr
Application granted granted Critical
Publication of EP2657525B1 publication Critical patent/EP2657525B1/fr
Not-in-force 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

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (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)
  • Sealing Devices (AREA)
EP13161225.1A 2012-04-27 2013-03-27 Machine à roue dentée dotée d'un joint axial qui s'étend dans la zone de la surface extérieure radiale du corps de palier associé Not-in-force EP2657525B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012207078A DE102012207078A1 (de) 2012-04-27 2012-04-27 Zahnradmaschine mit einer Axialdichtung, die sich in den Bereich der radialen Außenoberfläche des zugeordneten Lagerkörpers erstreckt

Publications (3)

Publication Number Publication Date
EP2657525A2 true EP2657525A2 (fr) 2013-10-30
EP2657525A3 EP2657525A3 (fr) 2015-12-30
EP2657525B1 EP2657525B1 (fr) 2017-10-18

Family

ID=48049782

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13161225.1A Not-in-force EP2657525B1 (fr) 2012-04-27 2013-03-27 Machine à roue dentée dotée d'un joint axial qui s'étend dans la zone de la surface extérieure radiale du corps de palier associé

Country Status (2)

Country Link
EP (1) EP2657525B1 (fr)
DE (1) DE102012207078A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018019587A1 (fr) * 2016-07-26 2018-02-01 Robert Bosch Gmbh Pompe à engrenages extérieurs pour un système de récuperation de chaleur perdue
EP3754196A1 (fr) * 2019-06-17 2020-12-23 Hamilton Sundstrand Corporation Palier doté d'une rainure d'étanchéité excentrique
WO2023041642A1 (fr) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Pompe de dosage pour transporter des fluides abrasifs

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017207486A1 (de) * 2017-05-04 2018-11-08 Robert Bosch Gmbh Außenzahnradmaschine, Abgaswärmerückgewinnungssystem mit einer Außenzahnradmaschine
DE102019130723A1 (de) * 2019-11-14 2021-05-20 Fte Automotive Gmbh Flüssigkeitspumpe

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2847711A1 (de) 1978-11-03 1980-05-14 Bosch Gmbh Robert Zahnradmaschine (pumpe oder hydromotor)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2847711A1 (de) 1978-11-03 1980-05-14 Bosch Gmbh Robert Zahnradmaschine (pumpe oder hydromotor)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018019587A1 (fr) * 2016-07-26 2018-02-01 Robert Bosch Gmbh Pompe à engrenages extérieurs pour un système de récuperation de chaleur perdue
EP3754196A1 (fr) * 2019-06-17 2020-12-23 Hamilton Sundstrand Corporation Palier doté d'une rainure d'étanchéité excentrique
US10962059B2 (en) 2019-06-17 2021-03-30 Hamilton Sundstrand Corporation Bearing with an eccentric seal groove
WO2023041642A1 (fr) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Pompe de dosage pour transporter des fluides abrasifs

Also Published As

Publication number Publication date
EP2657525A3 (fr) 2015-12-30
EP2657525B1 (fr) 2017-10-18
DE102012207078A1 (de) 2013-10-31

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