US20040164496A1 - Sealing device - Google Patents

Sealing device Download PDF

Info

Publication number
US20040164496A1
US20040164496A1 US10/479,417 US47941704A US2004164496A1 US 20040164496 A1 US20040164496 A1 US 20040164496A1 US 47941704 A US47941704 A US 47941704A US 2004164496 A1 US2004164496 A1 US 2004164496A1
Authority
US
United States
Prior art keywords
sealing
sealing part
pressure
fuel
seal
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.)
Abandoned
Application number
US10/479,417
Other languages
English (en)
Inventor
Masatoshi Okada
Iwao Taira
Tadashi Abiko
Yosuke Kondo
Kazuki Takeno
Ichiro Yamane
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.)
Nok Corp
Original Assignee
Nok Corp
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 Nok Corp filed Critical Nok Corp
Assigned to NOK CORPORATION reassignment NOK CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TAKENO, KAZUKI, YAMANE, ICHIRO, ABIKO, TADASHI, KONDO, YOSUKE, TAIRA, IWAO, OKADA, MASATOSHI
Publication of US20040164496A1 publication Critical patent/US20040164496A1/en
Priority to US11/727,763 priority Critical patent/US8348639B2/en
Priority to US11/727,764 priority patent/US20070182103A1/en
Priority to US12/078,508 priority patent/US20080258405A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • 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
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes
    • 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
    • F16J15/002—Sealings comprising at least two sealings in succession
    • 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
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • 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
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
    • 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
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F16J15/3236—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips with at least one lip for each surface, e.g. U-cup packings

Definitions

  • the present invention relates to a sealing device to be used, for example, as seal for reciprocating movement for a high-pressure fuel pump for pressurizing fuel to a high pressure.
  • FIG. 9 A sealing device 101 shown in FIG. 9 is employed for the purpose of sealing high-pressure fuel supplied from a high-pressure fuel pump used for an engine, which performs fuel injection, to the high-pressure side H, which is the side to be sealed, of a shaft 110 reciprocating in the axial direction.
  • the sealing device 101 is disposed at the end of a housing 111 , so as to seal high-pressure fuel (gasoline, light oil, and so on), which is an object to be sealed, flown from the high-pressure side H and passed through a sliding portion of a shaft guiding portion of the housing 111 . Also, sealed on the low-pressure side L of the sealing device 101 is oil intended for lubrication and cooling.
  • high-pressure fuel gasoline, light oil, and so on
  • the sealing device 101 includes a metal ring 102 having a cylindrical portion 102 a to be fitted on the outer periphery of an end of the housing 111 , and a first and a second seal lips 103 , 104 formed of rubber-like resilient body, each extending from an inwardly directed flange section 102 b provided at the end of the low-pressure side L of the cylindrical portion 102 a of the metal ring 102 toward the high-pressure side H and the low-pressure side L for sliding on the shaft 110 .
  • the rubber-like resilient body is thin and when it is subjected to the pressure of the high-pressure fuel of 1 MPa or higher, it may be broken abruptly upon operation.
  • the rubber-like resilient body In the case of fuel containing alcohol, the rubber-like resilient body is swelled, and thus is lowered in hardness and strength, whereby abrupt breakage upon operation, or fuel leakage due to decrease of tightening margin of the seal lip may occur.
  • elimination of a drain port is contemplated for simplifying the pump construction.
  • elimination of the drain port may increase the pressure of the high-pressure fuel, it cannot be eliminated for limiting the working pressure of the high-pressure fuel to 0-0.6 MPa, and hence simplification of the pump construction cannot be achieved.
  • the present invention is a sealing device for sealing an annular gap formed between two opposing reciprocating surfaces, characterized by including a first sealing part having a resin sealing member coming into slidable sealing contact with one of the opposed surfaces and an urging member for urging the resin sealing member toward the one of the opposed surfaces, and
  • a second sealing part disposed on the side of the first sealing part opposite from the side to be sealed.
  • first and the second sealing parts are simple in construction, and thus may be downsized and designed for space-saving in comparison with the construction of the sealing device having the seal lip as in the conventional art.
  • the first sealing part includes a seal retaining member forming a side wall of a groove on the side of the mounting groove for accommodating the first sealing part fitted therein opposite from the side to be sealed, and the seal retaining member is formed with a second mounting groove for accommodating the second sealing part.
  • the second sealing part is a squeeze packing.
  • the second sealing part includes a resin sealing member which comes into slidable sealing contact with one of the opposed surfaces and an urging member for urging the resin sealing member toward the one of the opposed surfaces.
  • the second sealing part is a packing having a back-pressure leaking capability.
  • the second sealing part is a sealing member having a seal lip portion which comes into slidable sealing contact with the one of the opposed surfaces.
  • the sealing property of the device can further be improved.
  • FIG. 2 is a half cross-sectional view showing a peripheral system to which the sealing device according to the first embodiment is applied.
  • FIG. 3 is a drawing showing another example of the sealing device according to the first embodiment.
  • FIG. 4 is a drawing showing the sealing device according to the second embodiment.
  • FIG. 5 is a drawing showing the sealing device according to the third embodiment.
  • FIG. 6 is a drawing showing the sealing device according to the fourth embodiment.
  • FIG. 7 is a drawing showing the sealing device according to the fifth embodiment.
  • FIG. 8 is a drawing showing the sealing device according to the sixth embodiment.
  • FIG. 9 is a half cross-sectional view showing a sealing device according to the related art.
  • FIG. 1 shows a sealing device 1 according to a first embodiment
  • FIG. 2 shows a peripheral system to which the sealing device 1 in FIG. 1 is applied.
  • the sealing device 1 in FIG. 1 is used as a sealing device for reciprocating movement, which requires a high sealing property, to be used in a high-pressure fuel pump for pressurizing fuel to a high pressure in an engine of in-cylinder direct injection system that high-pressure fuel is directly injected in a cylinder for combustion, and is employed for seal the high-pressure fuel supplied on the high-pressure side H, which is to be sealed with respect to a axially reciprocating shaft 10 .
  • the sealing device 1 is attached at the end of a housing 11 for sealing a high-pressure fuel (gasoline, light oil, and so on), which is to be sealed, supplied from the high-pressure side H from passing a sliding portion of a shaft guiding portion of the housing 11 . Besides, on the low-pressure side L of the sealing device 1 , oil for lubrication and cooling is sealed.
  • a high-pressure fuel gasoline, light oil, and so on
  • the sealing device 1 includes a first sealing part 2 and a second sealing part 3 arranged in this order from the high-pressure side H at the end portion of the housing 11 having an enlarged inner diameter.
  • a mounting groove for accommodating the first sealing part 2 fitted therein is formed in such a manner that a shoulder portion formed by enlarging the inner diameter at the end of the housing 11 is defined as a sidewall of a groove on the high-pressure side, and a seal retainer 4 which serves as seal retaining member is disposed on the low-pressure side L.
  • the first sealing part 2 to be fitted in the mounting groove includes a resin ring 21 , which is a sealing member formed of resin, coming into slidable sealing contact with the shaft 10 , and an O-ring 22 , which is an urging member for urging the resin ring 21 toward the shaft 10 .
  • the resin ring 21 of the first sealing part 2 is annular shape having a rectangular cross-section, and is formed of a resin material of tetrafluoroethylene group. Using such material contributes to achieve properties superior in fuel resistance, heat resistance, abrasion proof, and slidability.
  • the inner peripheral surface of the resin ring 21 defines a sliding surface which comes into abutment with/slides over the shaft 10 .
  • the O-ring 22 is formed of rubber-like resilient body disposed on the backside, the side of the housing 11 (on the bottom side of the groove), of the resin ring 21 .
  • the resin ring 21 is urged toward the shaft 10 by an urging force generated as a reaction of the O-ring 22 when being crushed in the radial direction.
  • the O-ring 22 is formed of fluorinated rubber, acrylic rubber, or the like. Using such material contributes to achieve properties superior in fuel resistance and heat resistance.
  • fluorinated rubber which is superior also in low temperature resistance (For example, Viton GLT from Dupont), is used.
  • the seal retainer 4 forming a side wall of a groove on the low-pressure side of the mounting groove for accommodating the first sealing part 2 fitted therein is a ring-shaped member formed of metal or the like to be fitted in the inner periphery at the end of the housing 11 of enlarged diameter.
  • a second mounting groove for fitting the second sealing part 3 is formed on the inner periphery of the seal retainer 4 .
  • the second sealing part 3 is fitted so that sealing on the low-pressure side L is achieved by being abutted to and sliding on the shaft 10 .
  • the second sealing part 3 uses an X-ring 31 , which is a squeeze packing.
  • the squeeze packing used in the second sealing part 3 may be an O-ring, a D-ring, and the like.
  • Material of the squeeze packing is fluorinated rubber or acrylic rubber which is superior in fuel resistance and heat resistance. Preferably, fluorinated rubber is used.
  • the sealing device 1 thus constructed is applied to a system as shown in FIG. 2. That is, in FIG. 2, the shaft 10 moves reciprocally by the rotation of a cam 5 connected directly to the engine, and increases the pressure of the high-pressure fuel on the high-pressure side H.
  • the spring 6 keeps the shaft 10 constantly in contact with the cam 5 so that the operation of the cam 5 is connected directly to the shaft.
  • the sealing device 1 in this arrangement has a dual-sealing construction in which the high-pressure fuel on the high-pressure side H is sealed by the first sealing part 2 , oil such as engine oil coming from the cam 5 side on the low-pressure side L is sealed by the second sealing part 3 , and slight leakage of the high-pressure fuel due to failure of scraping at the first sealing part 2 can be sealed at the second sealing part 3 .
  • the sealing device 1 according to the present embodiment can be used at the working pressure of 0-2 MPa and is prevented from breaking even when being subjected to the pressure of the high-pressure fuel at 5 MPa or higher.
  • first and the second sealing part 2 , 3 are simple in construction, and thus may be downsized and designed for space-saving in comparison with the construction of the sealing device having the seal lip as in the conventional art.
  • the resin ring 21 of the first sealing part 2 is a rectangle in cross section.
  • resin rings 23 , 24 having cross sections shown in FIG. 3 may be employed.
  • the resin ring 23 shown in FIG. 3( a ) has a tapered surface on the low-pressure side L with the axial center of the sliding surface projected.
  • the resin ring 24 shown in FIG. 3( b ) has a tapered surface on the sliding surface on the high-pressure side H so as to deviate from the shaft as it get close to the high-pressure side. Accordingly, distribution of the sealing surface pressure seals the fluid to be sealed on the high-pressure side H, and the pressure accumulated between the first sealing part 2 and the second sealing part 3 can be discharged toward the high-pressure side H.
  • mounting the sealing device can be performed easily by firstly pressing the resin ring 21 and the O-ring 22 which constitute the first sealing part 2 to the side wall of a groove of the mounting groove on the high-pressure side, and then fitting the seal retainer 4 to the housing 11 with the X-ring 31 which constitutes the second sealing part 3 fitted in the seal retainer 4 .
  • FIG. 4 is a half cross-sectional view showing the sealing device 1 according to the second embodiment. Incidentally, since the configuration, material and the like of each member are the same as those in the first embodiment, description will be omitted.
  • the second sealing part 3 includes a second resin ring 32 that comes into slidable sealing contact with the shaft 10 which is similar to the first sealing part 2 , and a second O-ring 33 for urging the second resin ring 32 toward the shaft 10 .
  • FIG. 5 is a half cross section showing the sealing device 1 according to the third embodiment. Incidentally, since the configuration, material, and the like are the same as those in the first embodiment other than that the seal retainer 4 is not used, description will be omitted.
  • a U-packing 34 is used as a packing having a back-pressure leaking capability for the second sealing part 3 .
  • the packing having the back-pressure leaking capability used for the second sealing part 3 is not limited to the U-packing 34 , and other types of packing may be used.
  • Material to be used for this packing is fluorinated rubber or acrylic rubber, which are superior in fuel resistance and heat resistance. Preferably, fluorinated rubber is used.
  • the mounting groove for accommodating the first sealing part 2 fitted therein in this embodiment is divided at the portion indicated by a line A. Therefore, it is possible to divide the housing 11 at the portion of line A for fitting the resin ring 21 and the O-ring 22 of the first sealing part 2 .
  • the resin ring 21 which can hardly be deformed, and the. O-ring 22 can be attached easily.
  • the distance between the positions where the first sealing part 2 and the second sealing part 3 are disposed is set longer than the reciprocating stroke of the shaft 10 , and thus fuel can hardly reach the second sealing part 3 , thereby entrance of fuel into the second sealing part 3 is prevented.
  • FIG. 6 is a half cross-sectional view showing the sealing device 1 according to the fourth embodiment. Incidentally, since the configuration, material, and the like are the same as those in the third embodiment, description will be omitted.
  • the second sealing part 3 includes oil seals 35 , 36 as sealing members each having a seal lip portion.
  • the oil seal 35 is disposed on the high-pressure side H and the oil seal 36 is disposed on the low-pressure side L.
  • the oil seals 35 , 36 are both constructed by attaching a rubber-like resilient body on a metal ring by baking.
  • Material of the rubber-like resilient body used is fluorinated rubber or acrylic rubber which is superior in fuel resistance and heat resistance for the both oil seals 35 , 36 .
  • fluorinated rubber is used.
  • the tip of the inner diameter of the metal ring of the oil seal 35 on which the seal lip portion is attached by baking is set as small as possible, so as to prevent deformation of the seal lip portion and the pressure resistance is improved.
  • the distance between the tips of seal lip portions of the oil seals 35 , 36 is set shorter than the reciprocating stroke of the shaft 10 , and thus lubricating oil spreads over the both oil seals 35 , 36 .
  • the seal lip portion of the oil seal 35 extends toward the high-pressure side H. It is for sealing leakage of fuel on the high-pressure side H sufficiently by the oil seal 35 .
  • the seal lip portion of the oil seal 35 which comes into contact with the surface of the shaft 10 , is arcuate shape at the tip thereof. The arcuate shape can lower the sliding resistance with respect to the surface of the shaft 10 , so that abrasion is prevented even when sliding especially with fuel, and leakage of oil supplied from the low-pressure side L via the surface of the shaft 10 due to failure of scraping is prevented.
  • the seal lip portion of the oil seal 36 extends toward the low-pressure side L. It is for sealing leakage of oil on the low-pressure side L.
  • the oil seal 35 is covered at the fitting portion with the rubber-like resilient body to achieve rubber fitting for preventing leakage.
  • the oil seal 36 is constructed at the fitting portion of only the metal ring to achieve metal fitting for fixing the oil seals 35 , 36 .
  • the mounting groove for accommodating the first sealing part 2 fitted therein can be divided at the portion indicated by the line A as in the case of the third embodiment. Also, the distance between the positions where the first sealing part 2 and the second sealing part 3 are disposed is set longer than the reciprocating stroke of the shaft 10 . The effect thereof is as described in conjunction with the third embodiment.
  • FIG. 7 is a half cross-sectional view showing the sealing device 1 according to the fifth embodiment. Incidentally, since the configuration, material and the like of each member are the same as those in the third embodiment, description will be omitted.
  • the sealing device 1 in FIG. 7 employs an oil seal 37 as a sealing member having a seal lip portion for the second sealing part 3 .
  • a sub packing 38 as auxiliary sealing member is disposed on the high-pressure side H of the oil seal 37 .
  • the oil seal 37 is constructed by attaching a rubber-like resilient body on a metal ring by baking.
  • Material to be used for the rubber-like resilient body is fluorinated rubber or acrylic rubber, which are superior in fuel resistance and heat resistance.
  • fluorinated rubber is used.
  • the oil seal 37 is mounted using the metal ring fitted around the outer periphery of the housing 11 .
  • the seal lip portion of the oil seal 37 extends toward the low-pressure side L. It is for sealing leakage of oil on the low-pressure side L by the oil seal 37 .
  • the sub packing 38 is a U-packing or the like disposed in a square mounting groove on the high-pressure side H with respect to the oil seal 37 , and the outer peripheral surface of the packing is provided with a projection for increasing the surface pressure and thus improving the sealing property.
  • the inner peripheral surface of the sub packing 38 can sufficiently seal leakage of fuel on the high-pressure side H by sliding on the shaft 10 . Furthermore, since the housing 11 is positioned as close to the shaft 10 as possible on the low-pressure side L, the sub packing 38 is prevented from being deformed and thus pressure resistance is improved.
  • the same material as the rubber-like resilient body of the oil seal 37 is used for the sub packing 38 as well.
  • the mounting groove for accommodating the first sealing part 2 fitted therein may be divided at the portion indicated by the line A as in the case of the third embodiment. Also, the distance between the positions where the first sealing part 2 and the second sealing part 3 are disposed is set longer than the reciprocating stroke of the shaft 10 . The effects thereof are the same as described in conjunction with the third embodiment.
  • FIG. 8 is a half cross-sectional view showing the sealing part 1 according to the sixth embodiment. Incidentally, since the configuration, material, and the like are the same as those in the third embodiment, description will not be made.
  • an oil seal 39 is employed as a sealing member having a seal lip portion for the second sealing part 3 .
  • the oil seal 39 is constructed by attaching a rubber-like resilient body on a metallic ring by baking.
  • Material to be used for the rubber-like resilient body is fluorinated rubber or acrylic rubber, which are superior in fuel resistance and heat resistance.
  • fluorinated rubber is used.
  • the oil seal 39 is mounted using the metal ring fitted around the outer periphery of the housing 11 to achieve metal fitting for enhancing the fitting force.
  • an O-ring 39 a is interposed between the metal ring of the oil seal 39 and the housing 11 . It is for preventing leakage at the metal fitting portion by the O-ring 39 a.
  • the seal lip portion of the oil seal 39 extends separately toward the high-pressure side H and the low-pressure side L, and the respective portions are pressed against the surface of the shaft 10 by the garter spring.
  • the material of the rubber-like resilient body may be well distributed to the two seal lip portions when fabricating by providing the tip of the inner periphery of the metal ring at the root on which the rubber-like resilient body is attached by baking with a plurality of recesses formed by setting down the tip portion thereof in the circumferential direction or by providing a plurality of holes in the circumferential direction so that the area passing therethrough is extended on both sides.
  • the seal lip portion extending toward the high-pressure side H of the oil seal 39 sufficiently seals leakage of fuel on the high-pressure side H.
  • the seal lip portion extending toward the high-pressure side H has an arcuate shape at the tip portion of the lip that comes into contact with the surface of the shaft 10 . This arcuate shape can reduce sliding resistance with respect to the surface of the shaft 10 , so that abrasion can be prevented even when sliding especially with fuel.
  • leakage of oil supplied from the low-pressure side L via the surface of the shaft 10 due to failure of scraping is prevented.
  • seal lip portion extending toward-the low-pressure side L of the oil seal 39 seals leakage of oil on the low-pressure side L.
  • the mounting groove for accommodating the first sealing part 2 fitted therein can be divided at the portion indicated by the line A as in the case of the third embodiment.
  • the distance between the positions where the first sealing part 2 and the second sealing part 3 are disposed is set longer than the reciprocating stroke of the shaft 10 . The effect thereof is as described in conjunction with the third embodiment.
  • the first sealing part and the second sealing part disposed on the side of the first sealing part opposite from the portion to be sealed are provided, a dual-sealing structure in which slight leakage due to failure of scraping at the first sealing part is sealed by the second sealing part is realized. Therefore, it can be used at the working pressure of 0-2 MPa, and moreover, it is prevented from breaking even when being subjected to the pressure of the high-pressure fuel at 5 MPa or higher.
  • the first and the second sealing part are simple in construction, and thus may be downsized and designed for space-saving in comparison with the construction of the sealing device having the seal lip as in the conventional art.
  • seal retaining member forming a side wall of a groove on the side of the mounting groove for accommodating the first sealing part fitted therein is provided opposite from the side to be sealed, and the seal retaining member is formed with a second mounting groove for accommodating the second sealing part, a seal of dual-sealing construction is formed with a simple construction.
  • the second sealing part is a squeeze packing, improvement of sealing property is achieved.
  • the second sealing part includes the resin sealing member which comes into slidable sealing contact with one of the opposed surfaces and the urging member for urging the resin sealing member toward the one of the opposed surfaces, usage of the device under higher pressure is realized.
  • the second sealing part is the packing having the back-pressure leaking capability, even when the pressure is accumulated between the first sealing part and the second sealing part, the accumulated pressure can be released through the packing having the back-pressure leaking capability of the second sealing part, thereby the durability can be improved.
  • the second sealing part is the sealing member having the seal lip portion which comes into slidable sealing contact with the one of the opposed surfaces, the sealing property of the device can further be improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Sealing Devices (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
US10/479,417 2001-06-04 2002-06-04 Sealing device Abandoned US20040164496A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US11/727,763 US8348639B2 (en) 2001-06-04 2007-03-28 Sealing device
US11/727,764 US20070182103A1 (en) 2001-06-04 2007-03-28 Sealing device
US12/078,508 US20080258405A1 (en) 2001-06-04 2008-04-01 Sealing device

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2001-168747 2001-06-04
JP2001168747 2001-06-04
JP2002-140744 2002-05-15
JP2002140744 2002-05-15
PCT/JP2002/005481 WO2002099320A1 (fr) 2001-06-04 2002-06-04 Dispositif d'etancheite

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US11/727,763 Division US8348639B2 (en) 2001-06-04 2007-03-28 Sealing device
US11/727,764 Division US20070182103A1 (en) 2001-06-04 2007-03-28 Sealing device

Publications (1)

Publication Number Publication Date
US20040164496A1 true US20040164496A1 (en) 2004-08-26

Family

ID=26616322

Family Applications (4)

Application Number Title Priority Date Filing Date
US10/479,417 Abandoned US20040164496A1 (en) 2001-06-04 2002-06-04 Sealing device
US11/727,763 Active 2026-07-11 US8348639B2 (en) 2001-06-04 2007-03-28 Sealing device
US11/727,764 Abandoned US20070182103A1 (en) 2001-06-04 2007-03-28 Sealing device
US12/078,508 Abandoned US20080258405A1 (en) 2001-06-04 2008-04-01 Sealing device

Family Applications After (3)

Application Number Title Priority Date Filing Date
US11/727,763 Active 2026-07-11 US8348639B2 (en) 2001-06-04 2007-03-28 Sealing device
US11/727,764 Abandoned US20070182103A1 (en) 2001-06-04 2007-03-28 Sealing device
US12/078,508 Abandoned US20080258405A1 (en) 2001-06-04 2008-04-01 Sealing device

Country Status (6)

Country Link
US (4) US20040164496A1 (de)
EP (3) EP1394452A4 (de)
JP (1) JP4254534B2 (de)
KR (1) KR20040008208A (de)
CN (1) CN1320295C (de)
WO (1) WO2002099320A1 (de)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060228239A1 (en) * 2001-07-19 2006-10-12 Hitachi, Ltd. High pressure fuel pump for internal combustion engine
EP1715194A2 (de) 2005-04-20 2006-10-25 Weber-Hydraulik GmbH Hydraulische Zylindereinheit
US20060249914A1 (en) * 2005-05-06 2006-11-09 Dulin Robert D Enhanced reliability sealing system
US7234704B2 (en) 2004-02-09 2007-06-26 Ludwig Ehrhardt Gmbh Wiping and/or sealing element as well as process for sealing a piston and clamping and/or support element
US20080203672A1 (en) * 2007-02-28 2008-08-28 National Coupling Company, Inc. Pressure-energized shaft seal
US20090008883A1 (en) * 2006-01-16 2009-01-08 Denso Corporation High-Pressure Fuel Pump and Seal System For High-Pressure Fuel Pump
US20090152966A1 (en) * 2007-10-11 2009-06-18 Carl Freudenberg Kg Bearing seals
US20090302549A1 (en) * 2005-06-14 2009-12-10 Nok Corporation Lip Type Seal
US20110227292A1 (en) * 2009-08-28 2011-09-22 Yoshihisa Takano Contaminant sealing device
US20120138416A1 (en) * 2010-12-02 2012-06-07 Aktiebolaget Skf Method and device for sealing different oil environments
US20130193647A1 (en) * 2010-12-23 2013-08-01 Eagle Industry Co., Ltd. Magnetic fluid seal device
US20140239598A1 (en) * 2013-02-22 2014-08-28 Advics Co., Ltd. Rotating pumping apparatus with seal mechanism
WO2014184783A1 (en) * 2013-05-17 2014-11-20 Magna Powertrain Inc. Low-drag sealing method for thermal management valve
US20150060716A1 (en) * 2013-09-05 2015-03-05 Definox Sas Gate valve with floating seal
US8985085B2 (en) 2011-07-28 2015-03-24 Pratt & Whitney Canada Corp. Oil seal arrangement for rotary internal combustion engine
US20160084247A1 (en) * 2013-07-01 2016-03-24 Delphi International Operations Luxembourg S.À R.L. High Pressure Pump
US9366138B2 (en) 2011-07-28 2016-06-14 Pratt & Whitney Canada Corp. Rotary internal combustion engine with phasing gear
US9482357B2 (en) 2013-05-29 2016-11-01 Baker Products Ltd. Temperature controlled purge valve for use in water systems
US20180313313A1 (en) * 2015-10-23 2018-11-01 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump, manufacturing method thereof, and method of bonding two members
US10215283B2 (en) 2014-12-12 2019-02-26 Nok Corporation Sealing device
US20190113143A1 (en) * 2017-10-12 2019-04-18 Schaeffler Technologies AG & Co. KG Compact rotary valve body for coolant control valve
US20190301612A1 (en) * 2018-03-30 2019-10-03 GM Global Technology Operations LLC Vented lip seal
US20200124190A1 (en) * 2018-10-17 2020-04-23 Toflo Corporation Ball valve
US11162589B2 (en) * 2018-10-26 2021-11-02 Parker-Hannifin Corporation Exclusion and pulsation seal for hydraulic fracturing pump

Families Citing this family (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1394452A4 (de) 2001-06-04 2007-09-19 Nok Corp Dichtungsvorrichtung
JP2005299808A (ja) 2004-04-13 2005-10-27 Nok Corp ポンプ用シール
DE502005005515D1 (de) * 2004-11-03 2008-11-13 Ludwig Ehrhardt Gmbh Abstreif- und/oder Dichtungselement sowie Verfahren zum Abdichten eines Kolbens und Spann- und/oder Stützelement
JP4809702B2 (ja) * 2006-03-22 2011-11-09 Ｎｔｎ株式会社 油圧式オートテンショナ
DE102006055298A1 (de) * 2006-11-23 2008-06-05 Elringklinger Ag Dichtungsanordnung
DE102006059345A1 (de) * 2006-12-15 2008-06-26 Robert Bosch Gmbh Abdichtvorrichtung für eine Antriebswelle eines Wischerantriebs, System zum Aufbau entsprechender Abdichtungsvorrichtungen und entsprechender Wischerantrieb
JP5040338B2 (ja) * 2007-02-06 2012-10-03 Ｎｏｋ株式会社 密封装置及び油圧シリンダ
JP5326265B2 (ja) * 2007-09-26 2013-10-30 Ｎｏｋ株式会社 密封装置
JP5326384B2 (ja) * 2008-07-03 2013-10-30 Ｎｏｋ株式会社 密封装置
DE102009027463A1 (de) * 2009-07-03 2011-01-05 Deckel Maho Pfronten Gmbh Verfahren und Werkzeugmaschine zum zerspanenden Bearbeiten eines Werkstücks
US8820708B2 (en) 2009-07-17 2014-09-02 Fisher Controls International Llc Seal assemblies for use with fluid valves
EP2483097B2 (de) * 2009-10-02 2023-10-04 Volvo Lastvagnar AB Radnabeneinheit
DE102009054721B4 (de) * 2009-12-16 2017-07-06 Robert Bosch Gmbh Welle in einem Wellenlager, insbesondere Antriebswelle für eine Scheibenwischvorrichtung
CN101776150B (zh) * 2010-03-08 2013-05-08 北京交通大学 一种磁性液体与C型滑环及Yx型密封圈组合的往复密封装置
FR2959522B1 (fr) * 2010-04-29 2016-12-09 Unicum Trans De Puissance Dispositif d'etancheite de moteur pour couverture de piscine
CN101825177B (zh) * 2010-05-07 2013-06-05 大全集团有限公司 密封圈
DE102010039439A1 (de) * 2010-08-18 2012-02-23 Robert Bosch Gmbh Dichtring für eine Kolbenpumpe
DE102010045671A1 (de) * 2010-09-17 2012-03-22 Carl Freudenberg Kg Dichtprofil
US20120313329A1 (en) * 2011-06-10 2012-12-13 Freudenberg-Nok General Partnership Vented Dual Lip Seal And Method Of Making
JP5585945B2 (ja) * 2011-09-27 2014-09-10 株式会社村田製作所 シール構造及び接合装置
EP2885539B1 (de) 2012-06-22 2021-05-26 Nuovo Pignone S.r.l. Kolbenkompressor, druckverpackung und verfahren dafür
DE102012217260A1 (de) * 2012-09-25 2014-03-27 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
ITMI20131370A1 (it) * 2013-08-08 2015-02-09 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
WO2015032533A1 (en) * 2013-09-04 2015-03-12 Continental Automotive Gmbh High pressure pump
DE102014202796A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014202794A1 (de) 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014205105A1 (de) * 2014-03-19 2015-09-24 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102014214294A1 (de) * 2014-07-22 2016-01-28 Robert Bosch Gmbh Kraftstoffhochdruckpumpe, insbesondere Steckpumpe
DE102014214296A1 (de) * 2014-07-22 2016-01-28 Robert Bosch Gmbh Kraftstoffhochdruckpumpe, insbesondere Steckpumpe
EP3196514B1 (de) * 2014-07-24 2021-01-27 Eagle Industry Co., Ltd. Pumpe mit mechanischer dichtung
CN105909797A (zh) * 2016-06-22 2016-08-31 珠海格力节能环保制冷技术研究中心有限公司 一种油封、密封结构以及电机
CN106090287A (zh) * 2016-08-23 2016-11-09 成都欧浦特控制阀门有限公司 一种可靠性高的气动球阀
CN106090286A (zh) * 2016-08-23 2016-11-09 成都欧浦特控制阀门有限公司 一种密闭性好的球阀
FR3057639B1 (fr) * 2016-10-18 2019-03-15 Foundation Brakes France Etrier de frein electromecanique comprenant un organe d'entrainement portant un joint comportant plusieurs bourrelets d'etancheite
CN106499558A (zh) * 2017-01-04 2017-03-15 北京亚新科天纬油泵油嘴股份有限公司 一种防泄漏防油污的柱塞偶件及应用其的喷油泵
CN107181173A (zh) * 2017-06-19 2017-09-19 峨眉山长宇电气有限公司 一种箱变边缘密封结构
CN109386418B (zh) * 2017-08-07 2022-02-25 罗伯特·博世有限公司 柱塞泵和高压燃油泵
DE102018100637B3 (de) 2018-01-12 2019-06-06 Dürr Systems Ag Dichtung und Beschichtungsmittelpumpe mit einer solchen Dichtung
IT201800008016A1 (it) * 2018-08-09 2020-02-09 Truma Geraetetechnik Gmbh & Co Kg Gruppo di tenuta per un dispositivo di conduzione di gas
AU2019349421A1 (en) * 2018-09-25 2021-04-29 Schlumberger Technology B.V. Piston load ring seal configurations
DE102019212262A1 (de) 2019-08-15 2021-02-18 Elringklinger Ag Dichtungsanordnung, Hochdruckpumpe und Verfahren zur Herstellung einer Dichtungsanordnung
JP7468244B2 (ja) 2020-08-20 2024-04-16 株式会社デンソー 高圧燃料ポンプ
KR102559250B1 (ko) * 2023-01-04 2023-07-26 (주)일신오토클레이브 실링 카트리지 및 이를 구비하는 실링구 커버

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3351350A (en) * 1966-06-22 1967-11-07 Koppers Co Inc High pressure rod seal
US3942806A (en) * 1973-05-17 1976-03-09 Firma Busak & Luyken Kg, Sealing ring structure
USRE31171E (en) * 1978-05-26 1983-03-08 Textron, Inc. Hydraulic piston rod seal
US4449718A (en) * 1982-07-10 1984-05-22 Busak & Luyken Packing for hydraulic pistons or piston rods
US4807890A (en) * 1985-10-15 1989-02-28 Esco Elevators, Inc. Sealing combination
US4828272A (en) * 1987-03-21 1989-05-09 Danfoss A/S Sealing apparatus with elastic seal ring and plastic slide ring
US4893823A (en) * 1988-12-21 1990-01-16 Greene, Tweed & Co. Seal assembly
US4995485A (en) * 1988-08-05 1991-02-26 Nhk Spring Co., Ltd. Sealing structure of an accumulator
US5143382A (en) * 1991-03-04 1992-09-01 W. S. Shamban & Company Pressure relieving slipper seal system
US5149107A (en) * 1989-03-29 1992-09-22 W. S. Shamban & Company Elastomer energized sealing and exclusion device
US5392964A (en) * 1992-05-06 1995-02-28 Dietrich Reimelt Kg Rotary feeder for flowable materials
US5607166A (en) * 1995-12-15 1997-03-04 Gorman Company, Inc. Low friction fluid seal device with hinge and roll structure

Family Cites Families (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2905489A (en) * 1956-11-01 1959-09-22 Garlock Packing Co High-pressure fluid seals
US2935365A (en) * 1958-01-02 1960-05-03 Gen Motors Corp Seal
US3214182A (en) * 1962-02-27 1965-10-26 Henry J Herbruggen Packing ring
US3272520A (en) * 1965-03-18 1966-09-13 Air Prod & Chem Shaft seal assembly
US3268235A (en) * 1965-03-29 1966-08-23 Alphonse A Jacobellis Piston accumulator seal
US3584884A (en) * 1968-09-10 1971-06-15 Western Electric Co Pressure elongatable support apparatus
US3540741A (en) * 1968-09-18 1970-11-17 Singer General Precision Seal assembly for a hydraulically operated cylinder
US3636824A (en) * 1970-01-13 1972-01-25 Garlock Inc Unitary piston assembly including a body member serving both as a holder for sealing rings and as piston-bearing means
DE2057027C3 (de) * 1970-11-20 1974-04-25 Fichtel & Sachs Ag, 8720 Schweinfurt Hydraulisch beaufschlagte Dichtung
US3958903A (en) * 1972-08-14 1976-05-25 Capelli Raymond A Positive displacement device
US3885800A (en) * 1973-04-23 1975-05-27 Ato Inc Seal ring system
US3909016A (en) * 1973-12-26 1975-09-30 Shamban & Co W S Seal assembly with pivotable slipper seal
US3921991A (en) * 1974-01-17 1975-11-25 Parker Hannifin Corp Combination fluid seal and rod wiper
US4020910A (en) * 1976-05-19 1977-05-03 Rapidex, Inc. Sealing between relatively rotating members in boring apparatus
US4060023A (en) * 1976-06-04 1977-11-29 George Vegella Dual lip rod wiping seal
JPS5467154A (en) * 1977-11-08 1979-05-30 Japanese National Railways<Jnr> High pressure seal
JPS60104872A (ja) * 1983-11-09 1985-06-10 Nippon Pillar Packing Co Ltd 非常用軸封装置
DE3502799A1 (de) * 1984-07-11 1986-07-31 Martin Merkel GmbH & Co KG, 2102 Hamburg Wellendichtung
JPS62183165A (ja) 1986-02-07 1987-08-11 Hitachi Ltd 半導体装置の製造方法
JPS62183165U (de) * 1986-05-14 1987-11-20
JPS6491163A (en) 1987-10-01 1989-04-10 Seiko Epson Corp Toner cartridge
JPH0198968A (ja) 1987-10-12 1989-04-17 Tosoh Corp ヒス・インスリンの測定方法
JPH0191163U (de) * 1987-12-09 1989-06-15
JPH0198968U (de) * 1987-12-24 1989-07-03
JP2817963B2 (ja) * 1989-08-30 1998-10-30 日本発条株式会社 ダイスプリング装置
JP3302708B2 (ja) * 1991-09-06 2002-07-15 日本発条株式会社 ガスクッション装置
JPH0624270A (ja) 1992-07-08 1994-02-01 Honda Access:Kk 車両端部確認装置
JPH0663965A (ja) 1992-08-24 1994-03-08 Hiromi Hizume 金型による印字方法及び装置
JPH0624270U (ja) * 1992-08-28 1994-03-29 エヌオーケー株式会社 パッキン
JPH0663965U (ja) * 1993-02-19 1994-09-09 エヌオーケー株式会社 シール装置
US5797594A (en) * 1995-07-22 1998-08-25 Tokico, Ltd. Hydraulic shock absorber
WO1997031206A1 (fr) * 1996-02-23 1997-08-28 Tomoichiro Iwane Garniture mecanique d'etancheite
US5682861A (en) * 1996-05-23 1997-11-04 Caterpillar Inc. Fluid seal for cyclic high pressures within a fuel injection
US6290235B1 (en) * 1997-07-02 2001-09-18 Parker-Hannifin Corporation Sealing system for a reciprocating shaft
US5992768A (en) * 1997-12-08 1999-11-30 Caterpillar Inc. Fluid seal for cyclic high pressures within a fuel injector
JP4081800B2 (ja) 1998-03-05 2008-04-30 Ｎｏｋ株式会社 密封装置
US6547250B1 (en) * 2000-08-21 2003-04-15 Westport Research Inc. Seal assembly with two sealing mechanisms for providing static and dynamic sealing
EP1348864A4 (de) * 2001-01-05 2005-03-16 Hitachi Ltd Hochdruckkraftstoffförderpumpe
EP1394452A4 (de) 2001-06-04 2007-09-19 Nok Corp Dichtungsvorrichtung
CA2409316C (en) * 2002-10-22 2009-03-24 Dean Foote Seal assembly for reciprocating shaft

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3351350A (en) * 1966-06-22 1967-11-07 Koppers Co Inc High pressure rod seal
US3942806A (en) * 1973-05-17 1976-03-09 Firma Busak & Luyken Kg, Sealing ring structure
USRE31171E (en) * 1978-05-26 1983-03-08 Textron, Inc. Hydraulic piston rod seal
US4449718A (en) * 1982-07-10 1984-05-22 Busak & Luyken Packing for hydraulic pistons or piston rods
US4807890A (en) * 1985-10-15 1989-02-28 Esco Elevators, Inc. Sealing combination
US4828272A (en) * 1987-03-21 1989-05-09 Danfoss A/S Sealing apparatus with elastic seal ring and plastic slide ring
US4995485A (en) * 1988-08-05 1991-02-26 Nhk Spring Co., Ltd. Sealing structure of an accumulator
US4893823A (en) * 1988-12-21 1990-01-16 Greene, Tweed & Co. Seal assembly
US5149107A (en) * 1989-03-29 1992-09-22 W. S. Shamban & Company Elastomer energized sealing and exclusion device
US5143382A (en) * 1991-03-04 1992-09-01 W. S. Shamban & Company Pressure relieving slipper seal system
US5392964A (en) * 1992-05-06 1995-02-28 Dietrich Reimelt Kg Rotary feeder for flowable materials
US5607166A (en) * 1995-12-15 1997-03-04 Gorman Company, Inc. Low friction fluid seal device with hinge and roll structure

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7665976B2 (en) 2001-07-19 2010-02-23 Hitachi, Ltd. High pressure fuel pump for internal combustion engine
US20060228239A1 (en) * 2001-07-19 2006-10-12 Hitachi, Ltd. High pressure fuel pump for internal combustion engine
US7234704B2 (en) 2004-02-09 2007-06-26 Ludwig Ehrhardt Gmbh Wiping and/or sealing element as well as process for sealing a piston and clamping and/or support element
EP1715194A2 (de) 2005-04-20 2006-10-25 Weber-Hydraulik GmbH Hydraulische Zylindereinheit
US20060272498A1 (en) * 2005-04-20 2006-12-07 Marcus Fischer Hydraulic cylinder unit
EP1715194A3 (de) * 2005-04-20 2008-05-21 Weber-Hydraulik GmbH Hydraulische Zylindereinheit
US7762177B2 (en) * 2005-04-20 2010-07-27 Weber-Hydraulic Gmbh Hydraulic cylinder unit
US20060249914A1 (en) * 2005-05-06 2006-11-09 Dulin Robert D Enhanced reliability sealing system
US7942423B2 (en) * 2005-06-14 2011-05-17 Nok Corporation Lip type seal
US20090302549A1 (en) * 2005-06-14 2009-12-10 Nok Corporation Lip Type Seal
US20090008883A1 (en) * 2006-01-16 2009-01-08 Denso Corporation High-Pressure Fuel Pump and Seal System For High-Pressure Fuel Pump
US8573112B2 (en) * 2006-01-16 2013-11-05 Nok Corporation High-pressure fuel pump and seal system for high-pressure fuel pump
US20080203672A1 (en) * 2007-02-28 2008-08-28 National Coupling Company, Inc. Pressure-energized shaft seal
US20090152966A1 (en) * 2007-10-11 2009-06-18 Carl Freudenberg Kg Bearing seals
US20110227292A1 (en) * 2009-08-28 2011-09-22 Yoshihisa Takano Contaminant sealing device
US8800740B2 (en) * 2010-12-02 2014-08-12 Aktiebolaget Skf Method and device for sealing different oil environments
US20120138416A1 (en) * 2010-12-02 2012-06-07 Aktiebolaget Skf Method and device for sealing different oil environments
US9845889B2 (en) * 2010-12-23 2017-12-19 Eagle Industry Co., Ltd. Magnetic fluid seal device
US20130193647A1 (en) * 2010-12-23 2013-08-01 Eagle Industry Co., Ltd. Magnetic fluid seal device
US9366138B2 (en) 2011-07-28 2016-06-14 Pratt & Whitney Canada Corp. Rotary internal combustion engine with phasing gear
US8985085B2 (en) 2011-07-28 2015-03-24 Pratt & Whitney Canada Corp. Oil seal arrangement for rotary internal combustion engine
US20140239598A1 (en) * 2013-02-22 2014-08-28 Advics Co., Ltd. Rotating pumping apparatus with seal mechanism
US9638328B2 (en) * 2013-02-22 2017-05-02 Advics Co., Ltd. Rotating pumping apparatus with seal mechanism
US9897217B2 (en) 2013-05-17 2018-02-20 Magna Powertrain Inc. Low-drag sealing method for thermal management valve
WO2014184783A1 (en) * 2013-05-17 2014-11-20 Magna Powertrain Inc. Low-drag sealing method for thermal management valve
US9482357B2 (en) 2013-05-29 2016-11-01 Baker Products Ltd. Temperature controlled purge valve for use in water systems
US20160084247A1 (en) * 2013-07-01 2016-03-24 Delphi International Operations Luxembourg S.À R.L. High Pressure Pump
US9528611B2 (en) * 2013-09-05 2016-12-27 Definox Sas Gate valve with floating seal
US20150060716A1 (en) * 2013-09-05 2015-03-05 Definox Sas Gate valve with floating seal
US10215283B2 (en) 2014-12-12 2019-02-26 Nok Corporation Sealing device
US20180313313A1 (en) * 2015-10-23 2018-11-01 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump, manufacturing method thereof, and method of bonding two members
US10590897B2 (en) * 2015-10-23 2020-03-17 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump, manufacturing method thereof, and method of bonding two members
US20190113143A1 (en) * 2017-10-12 2019-04-18 Schaeffler Technologies AG & Co. KG Compact rotary valve body for coolant control valve
US10591069B2 (en) * 2017-10-12 2020-03-17 Schaeffler Technologies AG & Co. KG Compact rotary valve body for coolant control valve
US20190301612A1 (en) * 2018-03-30 2019-10-03 GM Global Technology Operations LLC Vented lip seal
US20200124190A1 (en) * 2018-10-17 2020-04-23 Toflo Corporation Ball valve
US11047492B2 (en) * 2018-10-17 2021-06-29 Toflo Corporation Ball valve
US11162589B2 (en) * 2018-10-26 2021-11-02 Parker-Hannifin Corporation Exclusion and pulsation seal for hydraulic fracturing pump

Also Published As

Publication number Publication date
US20070182103A1 (en) 2007-08-09
US20080258405A1 (en) 2008-10-23
CN1513095A (zh) 2004-07-14
KR20040008208A (ko) 2004-01-28
EP2290268A2 (de) 2011-03-02
EP1394452A1 (de) 2004-03-03
EP2290268A3 (de) 2011-07-06
CN1320295C (zh) 2007-06-06
EP2290268B1 (de) 2017-09-13
US20070169621A1 (en) 2007-07-26
EP2290267A3 (de) 2011-11-16
US8348639B2 (en) 2013-01-08
EP2290267B1 (de) 2018-04-11
WO2002099320A1 (fr) 2002-12-12
JP4254534B2 (ja) 2009-04-15
EP1394452A4 (de) 2007-09-19
EP2290267A2 (de) 2011-03-02
JPWO2002099320A1 (ja) 2004-09-16

Similar Documents

Publication Publication Date Title
US8348639B2 (en) Sealing device
US8123229B2 (en) Lip type seal
US7513506B2 (en) Plunger seal for pump
EP1348868B1 (de) Fluidpumpe und hochdruckkraftstoffförderpumpe
US9512924B2 (en) Sealing structure
KR20140092250A (ko) 밀봉장치 및 그 사용방법
JP4853633B2 (ja) 密封装置
JP4081800B2 (ja) 密封装置
JP2005147317A (ja) 密封装置及び燃料噴射ポンプ
JP2010242874A (ja) 往復動用密封装置
JP5326384B2 (ja) 密封装置
JP2010054021A (ja) シーリングシステム
US7188841B1 (en) Secondary piston seal
JP2010014205A (ja) 密封装置
JP3911848B2 (ja) 密封装置
JP2005023791A (ja) 密封装置
JP2000055207A (ja) 密封装置
JP2021173346A (ja) 密封構造
JP2005337424A (ja) 密封装置
JP2005265161A (ja) 燃料噴射ポンプ用シール
JP2002349390A (ja) 内燃機関の高圧燃料ポンプのシール装置
JP2016223557A (ja) バルブステムシール
JP2006336672A (ja) ガソリン噴射ポンプ用シール

Legal Events

Date Code Title Description
AS Assignment

Owner name: NOK CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:OKADA, MASATOSHI;TAIRA, IWAO;ABIKO, TADASHI;AND OTHERS;REEL/FRAME:014966/0088;SIGNING DATES FROM 20031215 TO 20031219

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION