EP0000516B1 - Dichtungsmanschette für hydraulische Kolben-Zylinder-Anlagen - Google Patents

Dichtungsmanschette für hydraulische Kolben-Zylinder-Anlagen Download PDF

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Publication number
EP0000516B1
EP0000516B1 EP78100391A EP78100391A EP0000516B1 EP 0000516 B1 EP0000516 B1 EP 0000516B1 EP 78100391 A EP78100391 A EP 78100391A EP 78100391 A EP78100391 A EP 78100391A EP 0000516 B1 EP0000516 B1 EP 0000516B1
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EP
European Patent Office
Prior art keywords
sealing
cup
piston
cylinder
annular
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.)
Expired
Application number
EP78100391A
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English (en)
French (fr)
Other versions
EP0000516A1 (de
Inventor
Junzo Hasegawa
Masatoshi Yamada
Kaoru Nakamura
Eiichi Yasuda
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.)
Toyota Motor Corp
Toyota Central R&D Labs Inc
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Toyota Motor Corp
Toyota Central R&D Labs Inc
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Filing date
Publication date
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Application filed by Aisin Seiki Co Ltd, Toyota Motor Corp, Toyota Central R&D Labs Inc filed Critical Aisin Seiki Co Ltd
Publication of EP0000516A1 publication Critical patent/EP0000516A1/de
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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
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/324—Arrangements for lubrication or cooling of the sealing itself

Definitions

  • the invention generally relates to a sealing cup for a hydraulic piston-cylinder device as described in the preamble of claim 1 and adapted for use in vehicular devices.
  • piston-cylinder assem- bHes having pistons slidably movable in a cylinder bore.
  • annular sealing member is used which is generally referred to as a piston cup or a sealing cup.
  • such a piston cup comprises an annular base, an inner sealing lip extending from the annular base and having an inner sealing surface adapted to be engaged with the piston, and an outer sealing lip extending from the annular base and having an outer sealing surface adapted to be engaged with the inner wall surface of the cylinder bore.
  • the piston cup is mounted on the piston and is slidably moved along the wall surface of the cylinder bore, however, in another arrangement, the piston cup may be mounted on the cylinder and the piston is moved with respect to the piston cup.
  • the inner sealing surface on the inner sealing lip is of a frusto conical shape which is inclined radially inwardly from the base so that the lip is radially outwardly expanded upon engagement with the piston.
  • the outer sealing surface on the outer sealing lip is of a frustoconical shape which is inclined radially outwardly from the base whereby the lip is deformed radially inwardly upon engagement with the cylinder bore wall.
  • the outer sealing surface on the outer sealing lip is defined in an area adjacent to the free end of the lip.
  • an annular groove in the sealing surface serves to maintain a slight gap with respect to the co-operating surface or at least provide an area of smaller contact pressure when the sealing surface is brought into contact with the co-operating wall surface under pressure or by elasticity of the sealing cup, so that a small amount of oil is always retained between the sealing surface and the co-operating surface to provide an adequate lubrication.
  • What is essential for the invention is to provide a pressure relief in the area of the maximum contact pressure, making the formation of a lubrication cushion possible.
  • a brake master cylinder device which comprises a cylinder CY having a longitudinally or axially extending cylinder bore, and a first piston P 1 and a second piston P 2 both received in the cylinder bore for axial slidable movement.
  • the first piston P 1 is connected with an actuating push rod PR which is in turn connected with a brake actuating member such as a brake pedal BP so that the first piston P 1 is axially displaced through an actuation of the brake pedal BP.
  • first and second pistons P i and P 2 there is defined a rear pressure chamber RC, while a front pressure chamber FC is defined between the second piston P 2 and the closed end of the cylinder bore opposite to push rod PR.
  • the first piston P 1 is formed at its intermediate portion with a circumferential recess to define a rear oil chamber ROC.
  • the second piston P 2 is formed at its intermediate portion with a circumferentiai recess to define a front oil chamber FOC.
  • first oil reservoir RT On the cylinder CY, there are mounted a first oil reservoir RT, and second oil reservoir RT 2 .
  • the first oil reservoir RT 1 is connected through a passage CH, with the rear pressure chamber RC and through a passage CH 3 with rear oil chamber ROC.
  • the second oil reservoir RT 2 is connected respectively through passage CH 2 and CH 4 with the front pressure chamber FC and the front oil chamber FOC.
  • the rear and front pressure chambers RC and FC are connected respectively through suitable conduits with rear and front wheel cylinders (not shown).
  • the first piston P has a primary sealing cup PC, and a secondary sealing cup SC.
  • the primary sealing cup PC i is mounted on the first piston P i at the end adjacent to the rear pressure chamber RC while the secondary sealing cup SC is mounted at the opposite end.
  • the second piston P 2 has a pair of floating sealing cups FC 1 and FC 2 and a primary sealing cup PC 2 .
  • the primary sealing cup PC 2 is mounted on the second piston P 2 at an end adjacent to the front pressure chamber FC, while the floating cups FC, and FC 2 are mounted at the opposite end.
  • the first piston P i is axially displaced through the push rod PR to such a position that the passage CH, is closed by the primary sealing cup PC,.
  • a hydraulic pressure is produced in the rear pressure chamber RC and the second piston P 2 is then axially displaced under the pressure in the rear pressure chamber RC to produce a pressure in the front pressure chamber FC.
  • the pressure in the chambers RC and FC is transmitted to the rear and front wheel cylinders to actuate the same.
  • the primary sealing cups PC 1 and PC 2 on the first and second pistons P i and P 2 function to seal the rear and front pressure chambers RC and FC.
  • the secondary sealing cup SC on the first piston P 1 functions to seal the inside of the cylinder CY from the atmosphere.
  • the floating cups FC 1 and FC 2 function to separate the front oil chamber FOC from the rear pressure chamber RC.
  • Figure 2 shows a typical example of so-called conventional SAE type sealing cup which is suitable for use as a primary cup or a floating sealing cup which is subjected to a hydraulic pressure in operation.
  • the sealing cup comprises an annular body of a resilient material having a cross-section including a base 23, an outer sealing lip 21 and an inner sealing lip 22.
  • the inner sealing lip 22 is inclined radially inwardly from the base 23 to provide a frustoconical configuration.
  • the outer sealing lip 21 is inclined radially outwardly from the base to provide a frustoconical shape and has an outer sealing surface 24 which is adapted to be brought into engagement with the wall surface of the cylinder bore.
  • FIG 3 there is shown an embodiment of the present invention in which the feature of the present invention is incorporated in the conventional sealing cup as shown in Figure 2.
  • the sealing or piston cup comprises an annular body of a resilient material having a cross-section including a base 3, an outer diverging sealing lip 1 and an inner converging sealing lip 2.
  • the outer sealing lip 1 has an outer sealing surface 4 on which a circumferentially extending recess or groove 4a is formed.
  • the recess 4a is of a substantially V-shaped configuration and defined by two annular surfaces having straight-line axial profiles intersecting at an obtuse angle.
  • One of the top edges of the V-shape coincident with the free edge A of the sealing surface 4 where the pressure of contact with the inner wall of the cylinder bore is the greatest.
  • the other of the top edges of the V-shape is located as shown by F at a point offset toward the edge A from a point H, which is defined as a point of intersection of the outer sealing surface 4 of the outer sealing lip 1 with a line perpendicular to the inner surface of the lip 1 passing through a point E of intersection between the inner surface of the lip 1 and the inner surface of the base 3.
  • the groove 4a has a bottom C which is located between the points A and F.
  • the particular location of the groove 4a having a V-shape cross section provides advantageous results.
  • the outer sealing lip 1 is subjected to a hydraulic pressure which functions to force the sealing lip 1 radially outwardly.
  • the V-shaped groove 4a provides an area of smaller contact pressure so that a film of hydraulic oil can always be maintained in the area to provide an adequate lubrication. It is therefore possible to prevent any increase in the drag force against the slidable movement of the piston and ensure a smooth piston operation.
  • FIG. 6 Referring at first to Figures 6 and 7, there is shown a conventional SAE type sealing cup having a base 23, an outer sealing lip 21 and an inner sealing lip 22.
  • the broken line CY designates a contour line of the cylinder wall, and the broken line P a contour line of the piston.
  • the outer sealing lip 21 has an edge portion of which outer diameter is larger than the diameter of the cylinder bore.
  • the inner sealing lip 22 has an edge portion of which inner diameter is smaller than the diameter of the piston on which the sealing cup is mounted.
  • Figures 8 and 9 show an embodiment of the present invention and respectively corresponds to Figures 6 and 7.
  • the sealing cup is formed at the sealing surface 4 on the outer sealing lip 1 with a V-shaped groove 4a which may for example be 0.1 mm deep.
  • the pressure of contact of the outer sealing lip 1 with the cylinder CY is decreased at the area of the V-shaped groove, so that it becomes possible to maintain an oil film in this area.
  • the pressure of contact between the outer sealing lip 1 and the cylinder bore wall is increased to some extent, resulting in the increase in sealing effect.
  • it has been confirmed that such an increase in the contact pressure does not cause any increase in the drag force.
  • Figures 4 and 5 show test results on the sealing cups as shown in Figures 6 and 8.
  • Figure 4 there are shown changes in drag forces in accordance with the piston movement
  • Figure 5 there is shown a change in hydraulic pressure in accordance with the piston movement.
  • the drag force can be significantly decreased in the sealing cup embodying the features of the present invention. Since the groove 4a is formed in a manner that one of the top edges thereof coincides with the free edge of the sealing surfaces, the aforementioned results can be obtained without having any adverse effect on the sealing property.
  • the sealing cup has a cross-section including a base 123, an outer sealing lip 121 extending from the base 123, and an inner sealing lip 122 extending also from the base 123.
  • the outer sealing lip 121 has outer surfaces 124, 125 which are adapted to be brought into slidable contact with the cylinder wall.
  • the inner sealing lip 122 has an inner surface 126 which engages the piston P.
  • the inner surface 126 of the inner sealing lip 122 has a diameter smaller than that of the piston portion where the sealing cup is mounted.
  • the outer surface 124 of the outer sealing lip 121 has a maximum diameter which is larger than the diameter of the cylinder bore. It will therefore be noted that the outer and inner sealing lips 121 and 122 are deformed as shown in Figure 1 when the sealing cup is assembled in the piston-cylinder device. Due to the deformation, the sealing lips 121 and 122 respectively engage the cylinder CY and the piston P.
  • the sealing lips 121 and 122 and the base 123 have greater thickness as compared with the sealing cup as shown in Figures 6 through 9 so that a larger contact pressure is produced upon installation of the sealing cup. Therefore, even when the maximum diameter of the outer sealing lip 121 is substantially the same as the cylinder bore diameter, a sealing pressure will be produced between the cylinder and the outer sealing lip since the sealing cup will be radially expanded when it is mounted on the piston.
  • the outer sealing lip 101 is formed at the outer surface 105 with a V-shaped groove 104 which is located in the vicinity of the free edge thereof.
  • the groove 104 may be for example 0.1 mm deep as in the previously discussed embodiment.
  • the contact pressure between the outer sealing lip 101 and the cylinder CY is decreased to substantially zero at the area of the V-shaped groove 104 so that it becomes possible to maintain a slight amount of oil in this area for facilitating lubrication.
  • there is an increase in the peak contact pressure at the edge portion of the outer sealing lip 101 so that there will be no decrease in the sealing effect due to the provision of the V-shaped groove 104.
  • the clutch master cylinder device is composed of cylinder CY having a cylinder bore and a piston P received in the cylinder bore for axial movement.
  • the piston P is connected with a push rod PR which is in turn connected with the clutch actuating pedal CP so that the piston P can be axially moved upon actuation of the clutch pedal CP.
  • the cylinder CY has an end cap PL which closes the cylinder bore at the end opposite to the push rod PR.
  • annular shoulder CYP In the cylinder bore, there is formed an annular shoulder CYP and a primary sealing cup PC is mounted on the cylinder CY at the shoulder CYP.
  • the piston P carries a secondary sealing cup SC.
  • the sealing cup PC comprises an annular body having a cross-section including a base 223, an outer sealing lip 221 adapted to engage the cylinder CY and an inner sealing lip 222 adapted to engage the piston P.
  • the sealing cup PC is mounted on the cylinder CY with the base 223 in engagement with the shoulder. CYP and maintained in position against detachment by the cap PL.
  • the inner lip 222 is therefore slidable --with-respect to the piston P.
  • the outer sealing lip 221 has an outer diameter larger than the cylinder bore diameter so that the lip 221 is radially inwardly deformed or bent upon installation on the cylinder CY.
  • the inner sealing lip 222 has an inner sealing surface 225 adapted to be brought into engagement with the piston P.
  • the inner sealing surface 225 on the inner sealing lip 222 has a free edge I and an annular inclined portion inclined inwardly with respect to the sealing lip and extending from the edge I to a point A where the surface 225 is recessed to a bottom point C so as to form a V-shaped groove 224 of for example 0.2 mm deep.
  • the annular inclined portion between the edge I and the point A is inclined with respect to the axis of the cylinder CY by an angle 0.
  • This portion provides a wedge shaped gap with piston P where the sealing cup PC is installed in the device.
  • oil is allowed to enter the gap upon sliding movement of the piston P so as to form a lubricating film of oil on the sliding surface.
  • the angle 8 when the cup is unmounted must be between 1° ⁇ 15° as measured in Figure 15.
  • the V-shaped groove 224 again functions to provide an area wherein the pressure of contact is low so that it is possible to maintain oil in this area for facilitating lubrication. It is therefore possible to maintain a smooth operation of the piston P.
  • a primary sealing cup which includes a base 233, an outer sealing lip 231 and an inner sealing lip 232.
  • the inner sealing lip 232 is adapted to engage the piston P and the outer sealing lip 231 is adapted to engage the cylinder CY.
  • the outer sealing lip 231 includes an outer surface having a free edge I and an annular inclined portion extending from the edge I to a point A where the outer surface is recessed to a point C to form a V-shaped groove 234 of for example 0.15 mm deep.
  • a wedge shaped clearance K is formed between the peripheral wall of said inclined portion and said cylinder when the cup is mounted, as shown in Figure 17.
  • the inclined portion the edge I and the point A is inclined with respect to the axis of the cylinder by an angle between 1° ⁇ 15° as measured in clockwise direction in Figure 16. More preferably, the angle should be between 1° ⁇ 7°.
  • the V-shaped groove 234 functions to facilitate lubrication as in the previous embodiments.
  • FIG 18 (A) there is shown an example in which the present invention is embodied in a so-called OPEL type sealing cup.
  • a V-shaped groove 4A is formed on the outer sealing surface with one of the top edges of the V-shape coincident with the free edge A of the sealing surface.
  • the surface IA is inclined by an angle of 3° as measured in clockwise direction in the plane of the drawing. This design is also effective to provide a sealing property.
  • Fig. 9 shows a modified embodiment of the present invention in which a chamfered portion 247 is provided at the tip part of said inclined portion 246.
  • the chamfered portion 247 is inclined with respect to a line (L) which is parallel to the axis of the cylinder by an angle a, that when the cup is unmouned is negative with respect to the angle 8 of said inclined portion 246.
  • chamfered portion 247 is inclined in a way that the tip portion 248 thereof is apart from the wall when mounted where the sealing cup is slidably contacted.
  • the anaJe (a) -15° to 45°.
  • sealing or piston cup of the present invention may be incorporated in any type of piston-cylinder device other than the brake or clutch master cylinder device as described.
  • it may be incorporated in a proportioning valve which- functions to determine the rear wheel brake pressure at a valve smaller than but proportioned to the front wheel brake pressure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (7)

1. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder, die
einen Ringkörper aus nachgiebigem Material und einer Kreisringbasis (3),
eine von der Kreisringbasis vorstehende ringförmige innere Dichtungslippe (2), die eine innere Dichtungsfläche hat, die sich an eine abzudichtende Wandung anliegen kann,
eine von der Kreisringbasis vorstehende äußere ringförmige, die innere Dichtungslippe im Abstand umgebende Dichtungslippe (21), die eine äußere Dichtungsfläche (4) hat, die mit einer abzudichtenden Wandoberfläche zusammenwirken kann, aufweist.
wobei von der inneren und äußeren Dichtungsfläche mindestens eine gegenüber der entsprechenden abzudichtenden Kolben- (P) bzw. Zylinderwand (Cy) verschiebbar ist, und
die bewegliche Dichtungsfläche (2, 4) eine einzige sich über den gesamten Umfang erstreckende Nut besitzt, wodurch Schmieröl in der Nut zurückgehalten wird, welches den Widerstand gegen die Bewegung des Dichtungsringes vermindert, dadurch gekennzeichnet, daß die Nut (4a) v-förmig gestaltet und durch zwei Ringoberfiächen definiert ist, die geradlinige Axialprofile besitzen, welche sich unter einem stumpfen Winkel schneiden, wobei die Nut an dem Punkt beginnt, der den maximalen Dichtungsdruck erzeugt, wenn der Dichtungsring montiert ist, und wobei sich der Punkt (D) maximaler Tiefe der eckigen Nut in einem Bereich befindet, der, im nichtmontierten Zustand des Dichtungsrings, einen Außen- oder Innendurchmesser aufweist, welcher größer als der Innendurchmesser der Zylinderwand bzw. kleiner als der Außendurchmesser der Kolbenwand ist.
2. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder nach Anspruch 1, dadurch gekennzeichnet, daß die größte Tiefe der Nut (4a) wie folgt festgelegt ist:
Figure imgb0011
3. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder nach Anspruch 2, dadurch gekennzeichnet, daß an einem Endabschnitt eines Vorderteils an der inneren und/oder äußeren Dichtfläche ein ringförmiger geneigter Abschnitt vorgesehen ist, der, je nachdem, ob er auf der äußeren oder auf der inneren Dichtungslippe vorgesehen ist, nach außen bzw. nach innen geneigt ist und sich um den Umfang des Endabschnitts erstreckt, und daß
der Winkel 8 zwischen dem ringförmigen geneigten Abschnitt und der Zylinderachse im nichtmontierten Zustand des Dichtungsrings wie folgt festgelegt ist:
Figure imgb0012
wobei der geneigte Abschnitt so g2no:gt ist, daß er im Einbauzustand zwischen der Außenwand des geneigten Abschnitts und dem Kolben oder dem Zylinder einen keilförmigen Freiraum (K) bildet, der sich in einer Richtung von der Basis weg öffnet.
4. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder nach Anspruch 2, dadurch gekennzeichnet, daß an einem Endabschnitt des geneigten Abschnitts (246) ein abgekanteter Abschnitt (247) vorgesehen ist,
dessen Winkel a mit der Achse des Zylinders im nichtmontierten Zustand des Dichtungsrings negative in bezug auf den Winkel 0 des geneigten Abschnitts (246) zur Achse des Zylinders und größer als der des geneigten Abschnitts hierzu ist und
wie folgt festgelegt ist:
Figure imgb0013
wobei der abgekantete Abschnitt das Schmieröl im Einbauzustand des Dichtungsrings in einem dreieckigen Freiraum zwischen der Außenwand des abgekanteten Abschnitts und dem Kolben oder dem Zylinder zurückhält und diese Flüssigkeit zu dem keilförmigen Freiraum führt.
5. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder nach Anspruch 3, dadurch gekennzeichnet, daß der Winkel 0 des ringförmigen geneigten Abschnitts (246) wie folgt festgelegt ist:
Figure imgb0014
6. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder nach Anspruch 4, dadurch gekennzeichnet, daß der Winkel a des abgekanteten Abschnitts (247) wie folgt festgelegt ist:
Figure imgb0015
EP78100391A 1977-07-15 1978-07-13 Dichtungsmanschette für hydraulische Kolben-Zylinder-Anlagen Expired EP0000516B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP52085385A JPS5854307B2 (ja) 1977-07-15 1977-07-15 ピストンカツプ
JP85385/77 1977-07-15

Publications (2)

Publication Number Publication Date
EP0000516A1 EP0000516A1 (de) 1979-02-07
EP0000516B1 true EP0000516B1 (de) 1981-10-28

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EP78100391A Expired EP0000516B1 (de) 1977-07-15 1978-07-13 Dichtungsmanschette für hydraulische Kolben-Zylinder-Anlagen

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US (1) US4345771A (de)
EP (1) EP0000516B1 (de)
JP (1) JPS5854307B2 (de)
DE (1) DE2861260D1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19505012A1 (de) * 1995-02-15 1996-08-22 Teves Gmbh Alfred Dichtmanschette für hydraulische Anlagen
DE19802463B4 (de) * 1997-03-08 2012-08-30 Festo Ag & Co. Kg Dichtungsring

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DE3022627C2 (de) * 1980-06-18 1982-09-09 FAG Kugelfischer Georg Schäfer & Co, 8720 Schweinfurt Nutring oder Dichtmanschette
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JPS6133179U (ja) * 1984-07-30 1986-02-28 サンデン株式会社 飲料抽出装置
US4781024A (en) * 1985-03-07 1988-11-01 Aisin Seiki Kabushiki Kaisha Static cup seal assembly for master cylinder end
ATE78567T1 (de) * 1988-03-23 1992-08-15 Cooper Ind Inc Ventilschaftdichtung.
DE4111887C2 (de) * 1991-04-09 1999-10-21 Mannesmann Ag Abdichtung eines druckmittelbetriebenen Arbeitszylinders
US5127661A (en) * 1991-04-25 1992-07-07 Parker Hannifin Corporation Fluid seal
WO1996023151A1 (en) * 1995-01-23 1996-08-01 Greene, Tweed Of Delaware, Inc. Improved fluid pressure activated piston return spring seal
US5575484A (en) * 1995-06-30 1996-11-19 Greene, Tweed Of Delaware, Inc. Fluid pressure activated piston return spring seal
DE10028672A1 (de) * 2000-06-09 2001-12-13 Fte Automotive Gmbh Dichtelement für hydraulische Kolben-Zylinder-Anordnungen
JP4695681B2 (ja) * 2008-09-19 2011-06-08 日信工業株式会社 シリンダ装置
DE102011018782A1 (de) * 2011-04-27 2012-10-31 Lucas Automotive Gmbh Hauptbremszylinder für eine Fahrzeugbremsanlage

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19505012A1 (de) * 1995-02-15 1996-08-22 Teves Gmbh Alfred Dichtmanschette für hydraulische Anlagen
DE19802463B4 (de) * 1997-03-08 2012-08-30 Festo Ag & Co. Kg Dichtungsring

Also Published As

Publication number Publication date
JPS5854307B2 (ja) 1983-12-03
DE2861260D1 (en) 1982-01-07
JPS5420261A (en) 1979-02-15
US4345771A (en) 1982-08-24
EP0000516A1 (de) 1979-02-07

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