Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T10/00—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope
  • B60T10/02—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope with hydrodynamic brake
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
  • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
  • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
  • F16J15/342—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities with means for feeding fluid directly to the face

Definitions

• Hydrodynamic machine in particular hydrodynamic retarder
• the present invention relates to a hydrodynamic machine, in particular a hydrodynamic retarder, in detail according to the preamble of claim 1.
• Hydrodynamic machines have been known for many decades. They have at least two paddle wheels, of which at least one rotates.
• At least one second impeller forms with the first impeller from a working space, which is either permanently filled with working fluid or optionally filled with working fluid to hydrodynamic torques or drive power from the first impeller to the second
• the hydrodynamic machine is a hydrodynamic retarder whose first paddle wheel
• Paddle wheels further vanes or vane rings are provided, the hydrodynamic machine is a hydrodynamic converter.
• the present invention is basically applicable to all of the aforementioned hydrodynamic machine designs.
• the present invention has for its object to provide a hydrodynamic machine, in particular a hydrodynamic retarder whose drive shaft is particularly reliable and permanently sealed against the housing of the hydrodynamic machine to avoid unwanted leakage of working fluid from the hydrodynamic machine.
• Under Drive shaft is to understand any form of a wave, whether hollow shaft or solid shaft or disc or annular shaft, which allows a drive at least one paddle wheel of the hydrodynamic machine.
• the object of the invention is achieved by a hydrodynamic machine with the features of claim 1.
• advantageous and particularly expedient embodiments of the invention are given.
• the hydrodynamic machine according to the invention which is designed in particular as a hydrodynamic retarder, has at least a first
• Both paddle wheels form one with a working medium optionally fillable or always filled
• Working space which in particular has a toroidal shape to hydrodynamically torque from the first impeller to the second impeller to
• the hydrodynamic machine operates as a retarder or as
• the hydrodynamic machine also has at least one housing which either encloses the other paddle wheel together with one of the two paddle wheels, whereby the housing is at least partially formed by one of the two paddle wheels, namely the "outer" paddle wheel, or both paddle wheels If the housing encloses both paddle wheels, this can in particular be kept stationary, likewise if the housing together with a stator, which is formed by one of the two paddle wheels, encloses the other paddle wheel.
• At least one drive shaft for mechanically driving the first or second impeller, the drive shaft being sealed against the housing by means of a mechanical seal to prevent leakage of working fluid between the drive shaft and the housing.
• the mechanical seal has at least one barrier liquid supply to supply a barrier fluid of the mechanical seal and by means of this
• the mechanical seal has at least a first sliding ring and a second sliding ring, which are arranged concentrically enclosing in the radial direction and each having a sealing surface which has a in
• the second mechanical seal is arranged on a larger diameter than the first mechanical seal and encloses this advantageous on the outside completely.
• barrier fluid channel to cool and / or lubricate the two sealing surfaces with barrier fluid.
• the barrier fluid channel is charged with barrier fluid from the barrier fluid supply, so that the
• Barrier fluid can flow through this barrier fluid channel, and can get over the mouth of the barrier fluid channel to the two sealing surfaces.
• a barrier liquid discharge is provided, in which the barrier liquid, after having cooled and / or lubricated the two sealing surfaces, flows in and is then discharged via the barrier liquid discharge from the mechanical seal and in particular from the hydrodynamic machine.
• the first slide ring and the second slide ring are made in one piece or mechanically connected to each other.
• the first sliding ring and the second slide ring are made in one piece or mechanically connected to each other.
• either the two sliding rings, in particular together with the same speed, with the drive shaft and / or a paddle wheel, and the counter-element is stationary.
• the counter element runs around with the drive shaft and / or a paddle wheel in particular at the same speed, and the two slip rings are held stationary.
• the two sealing surfaces seal the sealing gap together with a common one-piece counter-element, which is designed in particular as a counter ring from.
• the guide element is advantageously designed as an insert, in particular in an axial section through the hydrodynamic machine L-shaped insert, which is arranged in the radial direction between the first slide ring and the second slide ring.
• the barrier fluid from the barrier fluid supply flows particularly advantageously firstly in a first axial direction along the insert and then, after having cooled and / or lubricated the sealing surfaces, along a second, opposite axial direction in the direction of the barrier fluid discharge.
• the barrier fluid supply and the barrier fluid discharge can each be designed as at least partially extending in the radial direction channel, the two channels in the circumferential direction offset from one another, in particular by substantially or exactly 180 ° offset, can be arranged.
• the mechanical seal has a housing which encloses the two sliding rings and in particular the counter element.
• a bore can then be provided as a barrier liquid supply and a further bore as a barrier liquid discharge, which can be connected to the holes corresponding channels in the housing and / or in a paddle wheel of the hydrodynamic machine.
• a spring for example wave spring or sinusoidal spring is used, which the two slip rings in the direction of
• the spring may be inserted between a corresponding housing wall and the two sliding rings, wherein one of the two sliding rings, in particular the radially outer sliding ring, is advantageously pressurized via the insert by the spring.
• the insert can rest freely on the sealing ring, in particular in the axial direction.
• Each sliding ring can be provided with a separate spring.
• one, in particular a single spring acts on several or all sliding rings.
• Figure 1 shows a hydrodynamic machine in the form of a hydrodynamic retarder with seals of the drive shaft against the housing, which can be carried out according to the invention.
• FIG. 2 shows a detail of a hydrodynamic retarder in FIG
• FIG. 3 shows an axial section corresponding to FIG. 2 on the other
• FIG. 1 schematically shows a hydrodynamic retarder, wherein a section is shown schematically only through one side of the drive shaft 5. The other side is designed accordingly mirror image (not shown).
• Both blade wheels 1, 2 together form a toroidal working space 3, in which optionally a working medium, for example oil, water or a water mixture can be introduced to drive power, here
• a working medium for example oil, water or a water mixture
• Paddle wheel 2 to transmit the stator.
• the second impeller 2 forms a housing 4 together with a shell surrounding the first impeller 1 on the side facing away from the second impeller 2.
• the first impeller 1 is driven via the drive shaft 5.
• Drive shaft 5 is by means of a number of seals against the housing 4th 5
• the seal shown on the far right in FIG. 1 can be provided as a mechanical seal 6 designed according to the invention.
• FIG. 2 shows an axial section through a corresponding mechanical seal 6. It also recognizes the radially inner region of the first blade wheel 1 and the drive shaft 5 and a radially inner part of the housing 4. Also, a radially inner part of the working space 3 can still be seen.
• FIG. 3 shows a corresponding section, but in a sectional plane offset in the circumferential direction of the hydrodynamic retarder. Corresponding elements are numbered by the same reference numerals.
• the mechanical seal 6 has a first seal ring 8 and a second seal ring 9.
• the slip rings 8, 9 seal in the radial direction to the drive shaft fifth
• the mechanical seal 6 has a housing 16 which encloses and guides the two seal rings 8, 9. Between an end wall of the housing 16 and the two sliding rings 8, 9, two springs 17, each arranged in the form of a sinusoidal spring or wave spring, which are supported against the housing 16 and the slip rings 8, 9 with their sealing surfaces 10, 11 against the mating ring Press 13 to achieve the best possible sealing of the sealing gap.
• the two Springs 17 surround each other concentrically. Alternatively, a common spring could be provided, which acts on both slip rings 8, 9.
• the counter-ring 13 is also pressurized by a spring, here designated 8, in the direction of the seal rings 8, 9.
• a spring here designated 8
• the housing 16 is inserted together with the two sliding rings 8, 9 in the housing 4 of the hydrodynamic retarder and therefore does not run around.
• the counter ring 13 in the housing 16 is inserted together with the two sliding rings 8, 9 in the housing 4 of the hydrodynamic retarder and therefore does not run around.
• Drive shaft 5 is inserted and therefore runs together with the drive shaft 5 and the first paddle wheel 1 to.
• an insert 14 is introduced, which, as will be explained below, has a flow guidance function for the introduced into the mechanical seal 6 and funded to the sealing gap barrier liquid.
• the insert 14 has an L-shape in the section shown, wherein the comparatively longer leg is parallel to the axis of rotation 19 of the drive shaft 5 and the comparatively shorter leg perpendicular thereto.
• the comparatively shorter leg is introduced between the second slide ring 9 and the radially outer spring 17 such that the spring 17 exerts its pressure force on the insert 14 on the second slide ring 9, whereas in the embodiment shown, the radially inner spring 17 on their pressure force the first slide ring 8 without
• the barrier liquid is supplied via a supply channel 20 in the housing 4 of the
• the blocking fluid supply 7 can be embodied, for example, in the form of one or more bores in the housing 16 of the mechanical seal 6, wherein the at least one bore preferably extends at least partially in the radial direction.
• the barrier liquid From the barrier liquid supply 7, the barrier liquid, as indicated by the arrows, enters the radially inner gap between the insert 14 and the first seal ring 8, flows in this gap in the axial direction along the comparatively longer leg of the insert 14 to the free
• Blocking liquid discharge 15 is in turn carried out in the form of one or more holes in the housing 16 of the mechanical seal 6, wherein in this case for this purpose
• aligned bores for forming the barrier liquid discharge 15 are also provided in the second slide ring 9. From the barrier liquid discharge 15 in the mechanical seal 6 flows
• Barrier fluid then through a discharge channel 20 or a plurality thereof in the housing 4 of the hydrodynamic retarder.
• the illustrated embodiment of the mechanical seal 6 allows extremely efficient cooling of the two sealing surfaces 10, 11 at the same time optimal sealing of the drive shaft 5 relative to the housing 4 of the mechanical seal 6
• the blocking fluid supply 7 or the supply channel 20 can be connected, for example, to the working fluid supply of the hydrodynamic machine, in this case the hydrodynamic retarder, in order to achieve the highest possible pressure.
• the barrier liquid discharge 15 or the discharge channel 21 can be connected, for example, to the suction side of a pump (not shown), by means of which the working medium passes through the working space 3
• the pump is usually the

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Transportation (AREA)
• Transmission Of Braking Force In Braking Systems (AREA)
• Braking Arrangements (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=43708968

Family Applications (1)

Country Status (5)

Cited By (2)

Families Citing this family (3)

Citations (6)

Family Cites Families (6)

• 2009
  • 2009-12-15 DE DE102009058341A patent/DE102009058341A1/de not_active Withdrawn
• 2010
  • 2010-12-10 EP EP10798959.2A patent/EP2470404B1/de active Active
  • 2010-12-10 CN CN201080051704.1A patent/CN102892649A/zh active Pending
  • 2010-12-10 IN IN3264DEN2012 patent/IN2012DN03264A/en unknown
  • 2010-12-10 WO PCT/EP2010/007525 patent/WO2011082759A1/de not_active Ceased

Patent Citations (7)

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