EP1050680A2 - Joint d'arbre pour machine hydraulique - Google Patents

Joint d'arbre pour machine hydraulique Download PDF

Info

Publication number
EP1050680A2
EP1050680A2 EP00109429A EP00109429A EP1050680A2 EP 1050680 A2 EP1050680 A2 EP 1050680A2 EP 00109429 A EP00109429 A EP 00109429A EP 00109429 A EP00109429 A EP 00109429A EP 1050680 A2 EP1050680 A2 EP 1050680A2
Authority
EP
European Patent Office
Prior art keywords
sealing element
hydraulic machine
machine according
channel
sealing
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
EP00109429A
Other languages
German (de)
English (en)
Other versions
EP1050680B1 (fr
EP1050680A3 (fr
Inventor
Steven Donders
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1050680A2 publication Critical patent/EP1050680A2/fr
Publication of EP1050680A3 publication Critical patent/EP1050680A3/fr
Application granted granted Critical
Publication of EP1050680B1 publication Critical patent/EP1050680B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/04—Draining

Definitions

  • the invention relates to a hydraulic machine according to the preamble of claim 1.
  • hydraulic machine is a Axial piston machine with a drive shaft, which by means of a Rolling bearing on a housing wall of the housing stored hydraulic machine and by means of a outside of the rolling bearing in an annular joint between the Drive shaft and the housing wall arranged sealing ring is sealed.
  • hydraulic machine is also a pump device for an internal Forced flushing of the roller bearing is provided.
  • the Pump device has one on the inside of the Roller arranged on the conveyor disc, the annular gap of the rolling bearing axially opposite through holes has, which with respect to the axis of rotation of the shaft in Extend divergent direction towards the rolling bearing.
  • acts on the conveyor disc which functions during operation at least partially in the hydraulic operating fluid, e.g. B. Hydraulic oil, like a centrifugal pump, is located that in the diverging through holes located fluid due to the centrifugal force in the direction of promotes the rolling bearing.
  • a return channel is provided on the side of the roller bearing, which extends back into the interior of the housing and in which the delivered fluid flows back into the interior can.
  • the first Sealing element lubricated by the flushing fluid and cooled, but there is also pressure fluctuations in the interior exposed to the machine housing, the Pressure fluctuations are essentially caused by the rolling bearing propagate undiminished to the first sealing element.
  • a pressure difference acts on the first sealing element, which is due to the inside of the first sealing element pending internal pressure and the housing surrounding air pressure results. If this pressure difference is one exceeds a certain permissible value is a Desirably good sealing function of the first sealing element no longer exist.
  • the sealing function can be performed by a sudden overuse or persistent Overuse can be affected. The latter are especially with such first sealing elements, the drive shaft of the machine with a sealing lip surrounded with increasing internal pressure against the Shell surface of the drive shaft is pressed. Unless already because of the high pressure in the interior basically impairments of the first sealing element arise, there is a risk of increased frictional wear on the sealing lip.
  • the invention has for its object in a hydraulic machine of the type specified at the outset Improve sealing of the drive shaft.
  • a second sealing element is arranged, the space in one the rolling bearing receiving interior and one between the first sealing element and the second sealing element arranged space separates, the space with a drainage line is connected, in which a pressure prevails, which is lower than the pressure in the interior.
  • the second sealing element thus forms a barrier that in is beneficial in two ways.
  • the partition wall forms a barrier against the hydraulic fluid contained in the main room Solid contamination, especially from abrasion resulting particles, thus neither in the adjoining room can still reach the sealing surface on the sealing ring can affect.
  • the second sealing element Since the second sealing element withstands the pressure fluctuations of the Interior is still exposed, is with a Leakage at the second sealing element can be expected, however this leakage does not affect the environment of the hydraulic Machine, because it is separated from the space by a Drainage line discharged. Since in the invention Design the first sealing element of the Pressure fluctuations or from increased pressures is exempt or the pressure fluctuations are reduced, a Leakage at the first sealing element avoided, so that the hydraulic machine is of clean function and also on Can be placed in locations where the avoidance of Leakage is required.
  • the invention is distinguished Design through a simple and inexpensive manufacturable construction, which is also of small size and therefore with all common machine types can be realized.
  • the configuration according to the invention comprises a pressure stage seal with a second sealing element that from the hydraulic fluid on the inside of it with a small amount of fluid is passed. With this amount of fluid it is a leakage amount or one Amount of fluid that bypasses the second sealing element happens.
  • the second sealing element Configurations can e.g. B. a radial shaft seal, a mechanical seal or a gap or Act labyrinth seal.
  • the the second sealing element passing amount of fluid is expelled through the drainage line drained the space, which on the one hand Lubrication of the first sealing element is guaranteed and on the other hand that which passes through the second sealing element Fluid causes no pressure increase in the space.
  • the hydraulic machine 1 preferably has one two-part housing 2 on, with a cup-shaped Housing part that through an end wall 2a and a Circumferential wall 2b is formed, and with a lid 2c, the abuts the end of the peripheral wall 2b facing away from the end wall 2a and thus one at least partially with a hydraulic one Fluid-filled housing interior 3 closes and with the Circumferential wall 2b is screwed detachably.
  • a den Housing interior 3 axially with respect to the peripheral wall 2b penetrating drive shaft 5 is in the cover 2c and in the End wall 2a in at least one rolling bearing 6, 7 rotatably supported, the end wall 2a in one Through hole 8 penetrates the present Embodiment through a three-stage stepped bore is formed, in the inner and largest bore step 8a the roller bearing 7 and in its outer and smallest Bore step 8b a sealing element 9 in the form of a sealing ring each appropriate cross-sectional size is arranged.
  • pivot bearing 15 around a transverse to the drive shaft 5 extending pivot axis 15a is pivotally mounted, wherein the pistons 13 on one another by means of sliding shoes 17 support them facing inclined sliding surface 18.
  • the cylinder block 11 on a control disc 19 At the end of the housing interior 3 facing away from the drive part 14 is the cylinder block 11 on a control disc 19, the is supported on the inside of the lid 2c and each other has radially opposite control kidneys 21 which in known the passage of an inlet and Outlet channel 22, 23 in the lid 2c to the respective associated hydraulic working chambers 24 in the piston bores 12 Taxes.
  • an adjustment device 15b which the drive part 14 is adjustable, here pivotable, and can be determined in the respectively set position.
  • the first sealing element or sealing ring 9 is preferably around a lip ring with a different from one Base body 9a extending axially or obliquely inwards Sealing lip 9b. To secure the sealing ring 9 against axial migration outwards, it lies on a shoulder surface 25, which limits it on the outside.
  • a second sealing element 26 in the form of a locking or Sealing ring arranged on its the sealing ring 9 facing side a space 27 between it and the first sealing ring 9 axially limited.
  • the sealing element 26 is arranged in a middle bore step 8c, which after is delimited on the outside by a shoulder surface 28 on which the Sealing element 26 rests.
  • an axial lock provided in the present embodiment is formed in that the sealing ring 9 and that Sealing element 26 in the associated bore step 8b, 8c radial tension are pressed.
  • the sealing element 26 by a locking ring, e.g. B. made of metal or plastic, which is preferably inside a play of movement to the radially adjacent component, here the drive shaft 5 or one firmly seated on it Drive shaft sleeve 5a.
  • the movement game forms a throttle 29 or a throttled bypass 30 in the sense a compression seal 20, the function below is still explained.
  • the drainage space 31a can be an area of the associated hydraulic system, in which one differs only slightly from the ambient pressure There is pressure.
  • This can e.g. B. the suction line Machine or a feed pump or auxiliary pump 4, the in the present embodiment in the lid 2c is arranged and with an associated pump element the drive shaft 5 sits and is driven by the latter.
  • the drainage space 31a can also be a tank 33 for the hydraulic fluid of the machine 1 or one associated hydraulic system.
  • the Sealing ring 9 and the sealing element 26 in a special Receiving ring 35 arranged in a matching Ring recess 36 of the end wall 2a is used, which for Outside of the end wall 2a is open.
  • a securing element provided that by in the present embodiment a conventional locking ring 37 is formed, which in a Ring inner groove 38 sits in the ring recess wall and with its inside a the receiving ring 35 outside defining shoulder surface 39 forms.
  • a Ring recess 41 in the area of the outer edge of the Recording ring 35 is the required space for the Circlip 37 created.
  • the receiving ring 35 limits in its installed position with the inside of the outer ring 7a of the rolling bearing 7, which on its inside by a Shoulder surface 2d of the end wall 2a is limited.
  • the above-described configuration with the receiving ring 35 allows on the one hand the arrangement of the sealing ring 9 and Sealing element 26 in an attachment, so that the receiving ring 35 and the sealing elements 9, 26 on the one hand are easy to use and interchangeable with the receiving ring 35 form a prefabricated attachment.
  • the drive shaft sleeve 5a is in relation to the one that supports it Drive shaft section through an annular seal 42 sealed.
  • a sealing ring 43 for. B. a O-ring, very advantageous, the drive shaft section 5b sealingly surrounds and in an inner ring groove 44 in the Drive shaft sleeve 5a sits.
  • the drainage line 31 can partly in the housing 2 and inside of the machine 1 or through an external line 34, e.g. B. a pipe or hose can be formed.
  • Fig. 1 shows an external line 34 connected to a z. B. radial running drainage channel 44 in the end wall 2a connected.
  • the line 34 to the Extend tank 33 as indicated.
  • the channel 44 extending from the intermediate space 27 exists from a channel section 44a, which extends to the cylindrical Shell surface of the receiving ring 35 extends in the Area one in the lateral surface of the receiving ring 35 or arranged in the inner wall of the annular recess 36 annular groove 45, of which there is a channel section 44b for line connection extends.
  • Ring seals 46 are in themselves known manner each formed by a sealing ring, the in an annular groove in the inner wall of the annular recess 36 or in the lateral surface of the receiving ring (not shown) sits.
  • a special channel 47 forming a bypass 30 arranged in the end wall 2a, which the roller bearing 7 or bypasses the bearing bore and the housing interior 3 with connects the space 27.
  • This alternative Design can be exclusive or in addition to above-described bypass design on the second Sealing element 26 may be present. Even with the variant a throttle 29 is provided in the channel 47, preferably within a running in the receiving ring 35 Channel section 47a.
  • Channel 47 preferably penetrates the radial dividing line between the receiving ring 35 and the end wall 2a, the throttle 29 in the inside channel section 47a emerging from the receiving ring 35 is arranged so that it is made from this side or processed or as a separate component in the form of a Nozzle 29a can be used, e.g. B. by a Screw connection or an adhesive connection.
  • the channel 47 is preferably Z-shaped, the Central section 47b of the Z-shape runs radially and through a radial channel extension 47c is accessible from the outside, so that the individual channel sections are radial and axially parallel in each case from an associated outside End wall 2a can be drilled.
  • the mouth of the with 47c denoted axially parallel channel section in the Housing interior 3 is because of a special one Breakline course not shown in Fig. 2.
  • the Channel extension 47c may include a closure member 48, e.g. B. in Form of a pin that can be screwed into an internal thread 49 or nozzle can be formed, with which the channel 47 optionally is lockable or in terms of its cross-sectional size is adjustable.
  • the closure element 48 has on its outer end of a lathe tool engaging member 51 to it to screw in or out.
  • the channel extension 47c is preferably by a closure element 48 lockable, e.g. B. by means of a screw plug 52nd
  • the second sealing element 26 is preferably also around a sealing ring, in particular Radial shaft seal ring, with one from a base body 26a to the interior 3a extending tubular sealing lip 26b.
  • Sealing element 9 To increase the operational safety and service life of the Sealing element 9 are permissible values of the pressure difference on Sealing element 9 required. It is also used to increase the Operational safety and service life of the sealing elements 9 and / or 26 an adequate supply of lubricant required. It ensures lubrication and cooling the sealing lips of the sealing element or elements 9 and / or 26. Zu for this purpose the hydraulic fluid to be sealed by means of the bypass 30, in which a throttle 29 is located, past the sealing element 26 into the intermediate space 27 headed. This can be a leak or a leak act targeted continuous flow rate that the Bypass 30 in the above-described embodiments enables.
  • Such a bypass 30 can also be used for exemplary embodiments a channel or a bore in the sealing element 26 itself or be formed in its sealing lip 26.
  • the throttle set-up is preferably adjustable Lubricant quantity for the sealing elements 9 and / or 26 regulated.
  • the set amount of lubricant is like this chosen that possibly occurring and in the course of Operating time may also have increasing leaks no significant effects on the sealing element 9 or 26 on the operation of the sealing system. That as Leakage or through the associated bypass 30 in the Intermediate space 47 fluid contributes to lubrication and Cooling of the sealing elements 9 and 26.
  • the Pressure drop from the housing interior 3 or interior 3a to Interspace 27 or the drainage line 31 is the Lubricant supply to the sealing system ensured.
  • the pressure in the Drainage line 31 or in the space 27 via a Injector can be lowered, the z. B. in the field of Suction line of the machine or the auxiliary pump 4, in particular is arranged in the area of the suction connection.
  • the Drain opening 53 in the space 27 of the sealing system can be arranged so that the space is almost is completely filled with the hydraulic fluid.
  • the compression seal 20 also design as a multi-stage compression seal.
  • the entire pressure difference inside the machine becomes Environment degraded in several stages.
  • the mode of action of individual stages is analogous to that described above single stage sealing system. That in the immediate vicinity of Surrounding sealing element, here sealing element 9, takes on the actual function of complete, dust-dry waterproofing. Only the one immediately before this Gasket lying gap 27 is beyond that described Drainage line 31 with a region of low pressure Machine 1 or an associated system connected. All further seals each run over one matched bypass 30.
  • the multi-stage seal Compression seal self-venting.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP20000109429 1999-05-07 2000-05-03 Joint d'arbre pour machine hydraulique Expired - Lifetime EP1050680B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1999121501 DE19921501C2 (de) 1999-05-07 1999-05-07 Hydraulische Maschine mit einem außenseitig von einem Wälzlager angeordneten Dichtelement
DE19921501 1999-05-07

Publications (3)

Publication Number Publication Date
EP1050680A2 true EP1050680A2 (fr) 2000-11-08
EP1050680A3 EP1050680A3 (fr) 2001-03-28
EP1050680B1 EP1050680B1 (fr) 2005-10-19

Family

ID=7907584

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000109429 Expired - Lifetime EP1050680B1 (fr) 1999-05-07 2000-05-03 Joint d'arbre pour machine hydraulique

Country Status (2)

Country Link
EP (1) EP1050680B1 (fr)
DE (2) DE19921501C2 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012003922A3 (fr) * 2010-07-06 2012-04-12 Robert Bosch Gmbh Machine hydrostatique, en particulier machine à pistons axiaux
WO2014206714A1 (fr) * 2013-06-25 2014-12-31 Robert Bosch Gmbh Joint d'étanchéité à amortissement mécanique pour machine à piston axial
WO2015018583A1 (fr) * 2013-08-08 2015-02-12 Robert Bosch Gmbh Machine à plateau oscillant utilisée comme pompe à pistons axiax et/ou comme moteur à pistons axiaux
WO2015197402A1 (fr) * 2014-06-25 2015-12-30 Robert Bosch Gmbh Machine à plateau oscillant
WO2015197403A1 (fr) * 2014-06-25 2015-12-30 Robert Bosch Gmbh Machine à plateau oscillant
DE102014212201A1 (de) 2014-06-25 2015-12-31 Robert Bosch Gmbh Hydrostatische Maschine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006038073A1 (de) * 2006-08-16 2008-02-21 Robert Bosch Gmbh Kolbenmaschineneinheit mit einer hydrostatischen Kolbenmaschine und einer Hilfspumpe
DE102007020298A1 (de) * 2007-04-20 2008-10-23 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
DE102010031154B4 (de) * 2010-07-09 2018-05-17 Continental Automotive Gmbh Pumpe zur Förderung eines Fluids, umfassend eine erste und eine zweite in Kontakt stehende Antriebswellendichtung, die einen variabel einstellbaren Drosselkanal zwischen der ersten und zweiten Antriebswellendichtung aufweist

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19613609A1 (de) 1996-04-04 1997-10-09 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit internem Spülkreislauf

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02283870A (ja) * 1989-04-05 1990-11-21 Zahnradfab Friedrichshafen Ag 軸方向ピストンポンプ
US5199718A (en) * 1992-04-13 1993-04-06 Vickers, Incorporated Rotary machine shaft seal
JPH07208327A (ja) * 1993-12-06 1995-08-08 Vickers Inc 軸シールを備えた回転式流体圧力エネルギー変換装置
US5984315A (en) * 1996-10-09 1999-11-16 Denison Hydraulics Inc. Reclamation system for a hydraulic pump system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19613609A1 (de) 1996-04-04 1997-10-09 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit internem Spülkreislauf

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012003922A3 (fr) * 2010-07-06 2012-04-12 Robert Bosch Gmbh Machine hydrostatique, en particulier machine à pistons axiaux
WO2014206714A1 (fr) * 2013-06-25 2014-12-31 Robert Bosch Gmbh Joint d'étanchéité à amortissement mécanique pour machine à piston axial
WO2015018583A1 (fr) * 2013-08-08 2015-02-12 Robert Bosch Gmbh Machine à plateau oscillant utilisée comme pompe à pistons axiax et/ou comme moteur à pistons axiaux
WO2015197402A1 (fr) * 2014-06-25 2015-12-30 Robert Bosch Gmbh Machine à plateau oscillant
WO2015197403A1 (fr) * 2014-06-25 2015-12-30 Robert Bosch Gmbh Machine à plateau oscillant
DE102014212201A1 (de) 2014-06-25 2015-12-31 Robert Bosch Gmbh Hydrostatische Maschine

Also Published As

Publication number Publication date
DE19921501A1 (de) 2000-11-16
DE19921501C2 (de) 2003-05-08
EP1050680B1 (fr) 2005-10-19
DE50011350D1 (de) 2006-03-02
EP1050680A3 (fr) 2001-03-28

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