EP0000517A1 - Dichtungsmanschette - Google Patents

Dichtungsmanschette Download PDF

Info

Publication number
EP0000517A1
EP0000517A1 EP78100392A EP78100392A EP0000517A1 EP 0000517 A1 EP0000517 A1 EP 0000517A1 EP 78100392 A EP78100392 A EP 78100392A EP 78100392 A EP78100392 A EP 78100392A EP 0000517 A1 EP0000517 A1 EP 0000517A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
cup
piston
angle
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
EP78100392A
Other languages
English (en)
French (fr)
Other versions
EP0000517B1 (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
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 Aisin Seiki Co Ltd, Toyota Motor Corp, Toyota Central R&D Labs Inc filed Critical Aisin Seiki Co Ltd
Publication of EP0000517A1 publication Critical patent/EP0000517A1/de
Application granted granted Critical
Publication of EP0000517B1 publication Critical patent/EP0000517B1/de
Expired legal-status Critical Current

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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

  • This invention generally relates to a sealing cup adapted for use in vehicular devices and more particularly to improvements in a sealing cup to be mounted on any piston and cylinder for recaiving the fluid pressure and for fluidtightly sealing the same.
  • the brake device of these days has to satisfy the following requirements to provide an improved brake cup; that the brake pedal will be smoothly depressed with little resistance and that the vehicle can, be stopped by a small depression of the brake pedal.
  • one of the major drawbacks of the conventional brake cup is, although satisfactory as regards the sealing, that it is obliged to increase the resistance of slide due to shortage of the oil film formed between the slide surfaces. Therefore, a large foot force is necessary to pressurize the brake fluid, causing a poor pressurizing efficiency of brake fluid. In addition, a stable movement of the piston provided with the conventional brake cup will not be secured due to possible vibration like stickslip vibration with the result of unstable brake application.
  • a wedge-shaped clearance of a predetermined angle and shape is formed for example betwwen the cylinder and the leading edge of the piston cup upon the fitting thereof between the piston and the cylinder, thereby permitting the oil admission into the wedge-shaped clearance when the piston cup slides in accordance with the piston movement.
  • the lubrication of oil is increased and the oil film is formed.on the sliding .surfaces of the cylinder or the piston thereby decreasing the slide resistance.
  • an angle ⁇ of the leading edge of the outer peripheral wall of the piston cup with respect to the cylinder axis is made smaller than an angle e of the remaining part of the peripheral wall thereof with respect to the cylinder axis when the piston cup is fitted between the piston and the cylinder, and the angle ⁇ is made 1° ⁇ ⁇ ⁇ 15°.
  • the angle ⁇ of the leading edge of the sealing cup is defined as inclination when unmounted toward a wall where the sealing cup is slidably contacted.
  • Figs. 1 t6 4 wherein so-called ring cups are illustrated; cups of Figs. 1 and 3 are called S.A.E type while the cups of Figs. 2 and 4 are called Opel type.
  • Each of these conventional ring cups comprises an outer lip 1 substantially similar to the frustum of a cone, an inner lip 2, and a base 3.
  • S.A.E type cup of Figs. 1 and 3 comprises a tip A at the maximum diameter portion of the outer lip 1 at which the maximum pressure is applied by contact of the cup with a cylinder CY.
  • the fluid film may not be formed between the sealing portion of the outer lip 1 and the cylinder CY because there is no provision of a leading edge to provide clearance in the case of the S.A.E type cup as shown in Fig. 3, thereby causing the sealing portion 4 to be brought into direct contact with the cylinder CY and increasing the slide resistance therebetween.
  • a piston cup of the invention comprises an outer lip 1 provided with a leading edge 6.
  • the angle ⁇ of the leading edge 6 relative to the axis parallel to the cylinder axis is smaller when unmounted than the angle ⁇ of the remaining portion 4 to the said axis 1° ⁇ ⁇ ⁇ 15°.
  • the portion A is at a position where the outer diameter of the piston cup is larger than the inner diameter of the cylinder.
  • the wedge-shaped clearance is constituted between the leading edge 6 and the cylinder wall to form the oil film therebetween when the piston cup slides on the cylinder wall.
  • the slide resistance of the cup will be decreased to realize various advantages such as a stable movement of the piston, improvement in the pressure increasing efficiency, and improvement in the durability of the cup.
  • the piston cup of Fig. 7(A) comprises an outer wall 7 of the inner lip 2 which includes a portion smaller in diameter than the outer diameter of the piston and the sealing wall 4 of the outer lip 1 which includes a portion larger in diameter than the inner diameter of the cylinder. Consequently, the piston cup receives bending force at the inner-lip 2 thereof and at the outer lip 1 thereof when installed within the cylinder CY, as shown in Fig. 7(B) wherein the sealing pressure of the cup in contact with the cylinder CY and the piston P is also illustrated.
  • Fig. 7(B) shows that the tip B of the outer lip 1 is being apart from the cylinder wall.
  • Fig. 8(B) shows that the leading edge is in contact with the cylinder wall when the piston cup is installed and Fig. 8(C) shows that when the inner pressure is applied the tip B of the leading edge is apart from the cylinder wall and the pressure at a portion of the edge is below the inner pressure.
  • the fluid wedge operation of the piston cup having the inclination angle ⁇ (Fig. 9(A)) when mounted has been proved effective in the fluid lubrication theory, i.e. the minimum thickness of the fluid film should be a few microns to dozens of microns in order to realize the fluid wedge. operation in the most effective way, so that the inclination angle ⁇ is a few degrees.
  • the tip angle ⁇ preferably be designed as 1° ⁇ ⁇ ⁇ 7° from Fig. 9(B). It is to be noted in Fig. 9(B) that the angle ⁇ may be designed as 1° ⁇ ⁇ ⁇ 10° in order to accomplish the fluid wedge effect.
  • Fig. 10 shows the test results of slide resistance with the angle ⁇ being different -30°, -10°, and 5° when the length l of the edge 6 is nearly equal to 0.15 x (L:length of the sealing wall 4) and the angle 0 is 15°.
  • the angle ⁇ may be varied within the range of 10° ⁇ ⁇ ⁇ 30°.
  • the leading edge angle ⁇ may be 1° ⁇ ⁇ ⁇ 15° so as to realize the fluid wedge effect.
  • the minimum limit of the angle range should be ⁇ 1° and the decrease of the angle ⁇ (the increars of the absolute value of the angle ⁇ ) will not realize the fluid wedge effect.
  • the major factors for accomplishing the fluid wedge operation are the angle, the shape, and the size of the clearance formed between the leading edge of the piston cup and the cylinder (or the piston) when the cup is installed between the cylinder and the piston.
  • the shape and the size of the clearance are primarily determined by the angle of the leading edge 6 of the lip and the pressure applied to the inside of cup, and secondarily by the tightening clearance of the cup, and the shape and the elasticity of the portion other than the leading edge thereof.
  • Figs. 13 and 14 shows the piston cup of the invention which is being used as secondary cup of the brake device.
  • the brake master cylinder will be explained with reference to Fig. 13.
  • the tandem master cylinder CY comprises a first piston PI and a second piston P2 each slidably fitted therein.
  • the first piston PI is provided with a secondary cup SC and a primary cup PC1.
  • the second piston P2 is provided with a primary cup PC2 and floating cups FC1 and FC2.
  • a fluid chamber RC of the rear wheel side is pressurized.
  • the second piston P2 is also moved left due to pressure in the chamber RC so that the primary cup PC2 closes a compensation hole CH2, fluidically connected to a reservoir tank RT2 thereby pressurizing fluid chamber FC of the front wheel side.
  • the secondary cup SC mounted on the first piston P1 serves to seal between the inside of the cylinder CY and" the outside thereof.
  • the primary cups PC1 and PC2 of the pistons PI and P2 serve to receive the fluid pressure.
  • the floating cups FC1 and FC2 serve to sear betwaen the rear side chamber RC and the front side chamber FC.
  • the secondary cup SC comprises an outer lip 11 having an unbroken curve at the outer periphery thereof, and a leading edge 16 at the tip thereof.
  • the leading, eage 16 has an inclination of the angle 5° with respect to tne line passing a point A and parallel to the cylinder axis.
  • Fig. 15 shows the piston cup of the invention which is used as a primary cup of the brake device.
  • the wedge-shaped clearance is similarly formed upon sliding movement of the primary cup so as to decrease the slide resistance.
  • the piston cup of the invention may be used as primary cup of the clutch device.
  • the piston cup of the invention may be employed in a proportioning valve device which will increase the wheel brake pressure with a reduced ratio relative to the master brake pressure.
  • the piston cup used in the proportioning valve device There are two kinds of the piston cup used in the proportioning valve device; in one of which the outer lip of the cup slides with respect to the inner wall of cylinder and in the other of which the inner lip of the cap slides with respect to the outer wall of piston.
  • the applicants of the invention have found that the leading edge ingle ⁇ of any cup should be 1 ⁇ ⁇ ⁇ 15° so as to effect the fluid wedge operation in the must effective way. Otherwise, the angle ⁇ of the cup may be 1° ⁇ ⁇ ⁇ 7° in consideration of the inner pressure applied thereto and the tightening clearance thereof.
  • Fig. 16 shows a modified embodiment of the present invention in which a further inclined surface 47 is provided on a leading edge 46 of the sealing cup.
  • the surface 47 is inclined with respect to a line (L) in the direction opposite to the inclination indicated by ⁇ and such the inclination is designated by ⁇ ' in Fig. 16. It is noted that the surface 47 is inclined in a way that the tip portion thereof is apart from the wall when mounted where the sealing cup is slidably contacted.
  • the angle ( ⁇ ') is selected from the range of 0° to 45 0 .
  • the preferable range of the angle ( ⁇ ') is 15° to 45°.

Landscapes

  • 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)
EP78100392A 1977-07-15 1978-07-13 Dichtungsmanschette Expired EP0000517B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP95011/77 1977-07-15
JP1977095011U JPS5835892Y2 (ja) 1977-07-15 1977-07-15 ピストンカツプ

Publications (2)

Publication Number Publication Date
EP0000517A1 true EP0000517A1 (de) 1979-02-07
EP0000517B1 EP0000517B1 (de) 1981-05-13

Family

ID=14126009

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78100392A Expired EP0000517B1 (de) 1977-07-15 1978-07-13 Dichtungsmanschette

Country Status (4)

Country Link
US (1) US4189160A (de)
EP (1) EP0000517B1 (de)
JP (1) JPS5835892Y2 (de)
DE (1) DE2860697D1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5169286A (en) * 1989-03-09 1992-12-08 Yutaka Yamada Variable capacity centrifugal water pump with movable pressure chamber formed by impeller
DE19505012A1 (de) * 1995-02-15 1996-08-22 Teves Gmbh Alfred Dichtmanschette für hydraulische Anlagen

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258927A (en) * 1978-12-13 1981-03-31 Garlock Inc. Shaft seal with retractable polytetrafluoroethylene-lined sealing lip
US4867043A (en) * 1986-06-30 1989-09-19 Tayco Developments, Inc. End cap for fluid cylinder
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
JP4699594B2 (ja) * 2000-10-10 2011-06-15 カヤバ工業株式会社 流体圧用パッキン

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2815995A (en) * 1954-06-28 1957-12-10 Acushnet Process Company Lip type seal for sealing hydraulic and pneumatic pressure systems
GB944921A (en) * 1959-01-10 1963-12-18 Girling Ltd Improvements in seals

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA529112A (en) * 1956-08-14 The Garlock Packing Company Of Canada Sealing devices
US2664952A (en) * 1948-03-15 1954-01-05 Guiberson Corp Casing packer cup
US2686402A (en) * 1948-12-31 1954-08-17 Charles A Samuel Hydraulic brake wheel cylinder piston
US2720924A (en) * 1950-02-20 1955-10-18 Cicero C Brown Connecting devices for well tools
US2884291A (en) * 1953-10-05 1959-04-28 Kelsey Hayes Co Sealing cup
US2867457A (en) * 1954-07-16 1959-01-06 Gen Motors Corp Fluid seal
DE1046966B (de) * 1956-04-30 1958-12-18 Freudenberg Carl Kg Lippendichtung
GB1019523A (en) * 1964-01-22 1966-02-09 Angus George Co Ltd Improvements in and relating to packing rings
US3527507A (en) * 1968-02-12 1970-09-08 Garlock Inc Unitary bearing element with improved,integral scraper-sealing lip
DE2002082A1 (de) * 1969-11-26 1971-06-03 Mini U Generaldirektor Der Deu Lippendichtring fuer Luftkupplungen
US3653670A (en) * 1970-05-11 1972-04-04 Cascade Corp Spring-loaded seal with symmetrical cross section

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2815995A (en) * 1954-06-28 1957-12-10 Acushnet Process Company Lip type seal for sealing hydraulic and pneumatic pressure systems
GB944921A (en) * 1959-01-10 1963-12-18 Girling Ltd Improvements in seals

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5169286A (en) * 1989-03-09 1992-12-08 Yutaka Yamada Variable capacity centrifugal water pump with movable pressure chamber formed by impeller
DE19505012A1 (de) * 1995-02-15 1996-08-22 Teves Gmbh Alfred Dichtmanschette für hydraulische Anlagen

Also Published As

Publication number Publication date
US4189160A (en) 1980-02-19
JPS5835892Y2 (ja) 1983-08-12
JPS5421785U (de) 1979-02-13
DE2860697D1 (en) 1981-08-20
EP0000517B1 (de) 1981-05-13

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