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WO2007069597A1 - Joint pour arbre tournant et procédé de production de celui-ci - Google Patents

Joint pour arbre tournant et procédé de production de celui-ci Download PDF

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Publication number
WO2007069597A1
WO2007069597A1 PCT/JP2006/324746 JP2006324746W WO2007069597A1 WO 2007069597 A1 WO2007069597 A1 WO 2007069597A1 JP 2006324746 W JP2006324746 W JP 2006324746W WO 2007069597 A1 WO2007069597 A1 WO 2007069597A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
rubber
case
outer case
rotary shaft
Prior art date
Application number
PCT/JP2006/324746
Other languages
English (en)
Japanese (ja)
Inventor
Takeshi Baba
Hironori Oida
Original Assignee
Mitsubishi Cable Industries, Ltd.
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
Priority claimed from JP2005358838A external-priority patent/JP2007162801A/ja
Priority claimed from JP2005358840A external-priority patent/JP2007162803A/ja
Priority claimed from JP2005358839A external-priority patent/JP2007162802A/ja
Priority claimed from JP2006050096A external-priority patent/JP2007225087A/ja
Application filed by Mitsubishi Cable Industries, Ltd. filed Critical Mitsubishi Cable Industries, Ltd.
Publication of WO2007069597A1 publication Critical patent/WO2007069597A1/fr

Links

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
    • F16J15/3204—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
    • 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
    • F16J15/3228—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip formed by deforming a flat ring

Definitions

  • the present invention relates to a rotary shaft seal and a method for manufacturing the rotary shaft seal, and more particularly to a rotary shaft seal used for a car air conditioner compressor and the like and a method for manufacturing the rotary shaft seal.
  • FIG. 39 and FIG. 40 illustrate the rotating shaft seal 31 proposed in Patent Documents 2 and 3, respectively
  • FIG. 41 is a cross-sectional view for explaining the operation of FIG. Side (high-pressure side) A has an inner flange part 32 and a cylindrical part 33 corresponding to the inner surface of the louver, and a rubber seal part 35 is formed by molding or the like on an approximately L-shaped outer case 34 As shown by solid lines in FIGS.
  • the end 33a on the low pressure side B of the cylindrical portion 33 of the outer case 34 is formed thin, and from the end 33a side, PTFE A seal element 36 and a metal inner case 37 are assembled, crimped as shown by arrow C, and the end 33a is bent into a small inner bowl shape as shown by a two-dot chain line.
  • a structure in which one case 34, seal element 36 and inner case 37 are assembled together To blink.
  • reference numeral 38 denotes a rubber lip portion, which is extended to the fluid storage chamber side (high pressure side) A and includes the seal portion 35 as a part thereof. Further, a screw groove 39 is formed in the seal element 36.
  • the seal portion 35 has a vertical wall portion 40 orthogonal to the U-shaped axis L that covers the inner flange portion 32 of the outer case 34.
  • the low pressure side wall portion of the vertical wall portion 40 and the outer periphery of the seal element 36 are provided.
  • the offset ring portion is subjected to the above-described force-clamping process in the direction of the arrow C so that the inner flange portion 32 and the inner case 37 are strongly pressed and held.
  • the rubber lip 38 has a sealing action when stationary and a PTFE shaft when the shaft rotates.
  • the graph shows the contact surface pressure P at which the contact inner peripheral edge 38a of the mulip portion 38 is in contact with the outer surface of the rotating shaft 29 on the vertical axis and the position on the horizontal axis.
  • the contact inner peripheral edge 38 a of the lip portion 38 is brought into sliding contact with the rotating shaft 29 evenly in the circumferential direction. Efforts have been made from design and manufacturing.
  • the fluid storage chamber side A has a high pressure.
  • the contact inner peripheral edge 38a (lip tip) contacts the rotating shaft 29 evenly with a large contact surface pressure P over the entire circumference (360 °). This makes it difficult for the lubricating oil in the sealing fluid to enter (introduce) the interface between the rotating shaft 29 and the contact inner peripheral edge 38a, and promotes wear of the contact inner peripheral edge 38a.
  • the inner peripheral edge 38a of the contact gradually wears, the sealability (sealability) deteriorates abruptly, and external leakage of the fluid occurs.
  • the tip (inner peripheral edge 38a) force of the rubber lip 38 is strongly pressed against the rotating shaft 29, and is uniformly pressed over the entire circumference of the rotating shaft 29. Therefore, the lubricating oil in the fluid such as refrigerant cannot enter the tip (the interface between the inner peripheral edge 38a and the rotary shaft 29, increases the frictional resistance, generates heat, and accompanying this, the tip of the lip 38 The part (inner peripheral edge 38a) wears out early.
  • Patent Document 1 Japanese Patent Laid-Open No. 2-240460
  • Patent Document 2 JP 2004-0119798
  • Patent Document 3 Japanese Patent Laid-Open No. 2003-343737
  • the present invention provides a rotary shaft seal that can cope with severe use conditions and can be manufactured at low cost by a simplified manufacturing process and that stably exhibits high sealing performance, and a method for manufacturing the same.
  • the purpose is to do.
  • the rotary shaft seal of the present invention includes a rubber seal portion (4) having a rubber lip portion (5) slidably contacting the rotary shaft (29).
  • the rubber seal (4) has a concave groove (18) in the middle of the radial direction of the high pressure compatible surface (27) corresponding to the fluid storage chamber side (A).
  • the rubber lip portion (5) and the outer peripheral rubber portion (14) are each formed in an annular shape, and the rubber lip portion (5) and the outer peripheral rubber portion (14) are connected in the concave peripheral groove (18).
  • a radial rib portion (41) is provided.
  • the rotary shaft seal of the present invention includes a rubber seal portion (4) having a metal outer case (2), a metal inner case (3), and a rubber lip portion (5) in sliding contact with the rotary shaft (29). And a sealing element (7), By molding the seal part (4), the outer case (2), the seal element (7), the inner case (3), and the seal part (4) are integrated, and the rubber sheet
  • the groove portion (4) is provided with a concave groove (18) at the radial intermediate position of the high pressure corresponding surface (27) corresponding to the fluid storage chamber side (A), and the rubber lip portion ( 5) and the outer peripheral rubber part (14) are each formed into an annular shape, and the radial rib part connecting the rubber lip part (5) and the outer peripheral rubber part (14) in the concave peripheral groove (18) ( 41).
  • the rotary shaft seal of the present invention includes a rubber seal portion (4) having a rubber lip portion (5) slidably contacting the rotary shaft (29).
  • the rubber seal part (4) has a concave groove (18) formed in the radial intermediate position of the high pressure corresponding surface (27) corresponding to the fluid storage chamber side (A), and the rubber lip is formed along the inner periphery. And forming at least one of the depth dimension (N), width dimension (S), and cross-sectional shape of the concave circumferential groove (18) in the circumferential direction.
  • the contact surface pressure (P) of the rubber lip portion (5) to the rotating shaft (29) is configured to be uneven in the circumferential direction.
  • the rotary shaft seal of the present invention includes a rubber seal portion (4) having a metal outer case (2), a metal inner case (3), and a rubber lip portion (5) in sliding contact with the rotary shaft (29). And a sealing element (7),
  • the rubber lip (5) is formed along the inner periphery by forming a concave groove (18) at the radial intermediate position of the high pressure compatible surface (27) corresponding to the fluid storage chamber side (A). Is formed in an annular shape, and at least one of the depth dimension (N), width dimension (S), and cross-sectional shape of the concave circumferential groove (18) is set to change in the circumferential direction.
  • the contact surface pressure (P) of the rubber lip portion (5) to the rotating shaft (29) is configured to be uneven in the circumferential direction.
  • the rotary shaft seal of the present invention includes a metal outer case (2), a metal inner case (3), and a rubber seal portion (4) having a rubber lip portion (5) in sliding contact with the rotary shaft, A seal element (7) that is in sliding contact with the rotating shaft;
  • the outer casing (2), the sealing element (7), the inner case (3), and the sealing portion (4) are integrated with each other by omitting the crimping of the metallic outer case (2). It is characterized by.
  • the rotary shaft seal of the present invention includes a metal outer case (2), a metal inner case (3), and a rubber seal portion (4) having a rubber lip portion (5) in sliding contact with the rotary shaft, A seal element (7) that is in sliding contact with the rotating shaft;
  • the seal part (4) is an integral structure.
  • the method of manufacturing the rotary shaft seal of the present invention includes a metal outer case (2), a metal inner case (3), a seal element (7), and the outer case (2) and inner case (3 )
  • the sealing element (7) is fitted into a mold cavity, and then the fluidized rubber material is filled into the cavity and solidified to form a seal portion (4).
  • the outer case (2), the inner case (3), and the seal element (7) are integrated together with the molding.
  • the rotary shaft seal of the present invention includes a metal outer case (2), a metal inner case (3), a rubber seal portion (4) having a rubber lip portion (5) slidably contacting the rotary shaft, A seal element (7) that is in sliding contact with the rotating shaft;
  • the above-mentioned outer case (2), seal element (7), inner case (3), and seal part (4) are integrated into a single structure, eliminating the need for crimping of the metal outer case (2).
  • the high pressure side (A) is connected to the low pressure side (B ) Having a first gap portion (54) formed larger than the outer case (2) and the inner case (3) with a rubber layer (57) interposed in the first gap portion (54). It is characterized by its shape.
  • the rotary shaft seal of the present invention includes a metal outer case (2), a metal inner case (3), and a rubber seal portion (4) having a rubber lip portion (5) in sliding contact with the rotary shaft, A seal element (7) that is in sliding contact with the rotating shaft;
  • the above-mentioned outer case (2), seal element (7), inner case (3), and seal part (4) are integrated into a single structure, eliminating the need for crimping of the metal outer case (2).
  • the high pressure side end (70) of the cylindrical portion (8) of the outer case (2) and the inner case ( The cylindrical portion (10) of 3) is characterized by being arranged in a different shape so that one of the high-pressure side end portions (60) is on the high-pressure side (A) than the other.
  • the rotary shaft seal of the present invention includes a metal outer case (2), a metal inner case (3), and a rubber seal portion (4) having a rubber lip portion (5) in sliding contact with the rotary shaft, A seal element (7) that is in sliding contact with the rotating shaft;
  • outer case (2), seal element (7), inner case (3), and seal part (4) are integrated into a single structure, eliminating the need for crimping of the metal outer case (2).
  • From the high pressure side end face (8a) of the cylindrical portion (8) of the outer case (2) move the high pressure side end (60) of the cylindrical portion (10) of the inner case (3) to the high pressure side (A).
  • the outer case (2) and the inner case (3) are integrated with each other through a rubber layer (13) formed by intrusion when the seal portion (4) is formed.
  • the metal outer case (2) is externally fitted so that the high-pressure side half (59) of the outer peripheral surface of the metal inner case (3) is exposed.
  • the seal case (7) is fitted in the outer case (2) and the inner case (3) and inserted into the mold cavity, and then fluidized rubber material Is filled into the cavity and solidified, and the seal part (4) is molded, and at the same time, the outer case (2), the inner case (3) and the seal element (7) are integrated.
  • the rotary shaft seal of the present invention includes a metal outer case (2), a rubber seal portion (4) having a rubber lip portion (5) in sliding contact with the rotary shaft, and a seal in sliding contact with the rotary shaft.
  • the outer case (2) and the sealing element (7) are formed by molding the seal portion (4) by omitting the inner case that is configured with the element (7) and is fitted in the outer case (2).
  • a rotary shaft seal characterized in that 7) and the seal portion (4) are integrated.
  • the rotary shaft seal manufacturing method of the present invention has a substantially cross-sectional shape in which a through hole (28) is formed along the outer periphery of the seal element (7) and has a cylindrical portion (8) and a low pressure side inner flange portion (9). Insert the seal element (7) into the mold cavity so that it contacts the inner flange (9) of the L-shaped metal outer case (2).
  • the fluidized rubber material The inside flange portion (2) of the outer case (2) is filled with a rubber material filled in the through hole (28) of the seal element (7) at the same time as the seal portion (4) is molded. It is characterized in that it is bonded to 9) and integrated as a whole.
  • the rotary shaft seal manufacturing method of the present invention includes forming a notch (22) or a concavo-convex part (23) on the outer peripheral edge (21) of the seal element (7), and connecting the cylindrical part (8) to the low pressure side.
  • the mold cavity is formed by fitting the sealing element (7) into contact with the inner flange (9) of the outer L-shaped metal outer case (2) having an inner flange (9). Then, after filling the cavity with the fluidized rubber material and molding the seal part (4), the notch part (22) or the uneven part (23 ), The rubber material filled in the recess (23a) is adhered to the inner flange (9) of the outer case (2), and the whole is integrated.
  • the rotating shaft seal manufacturing method of the present invention is such that the outer peripheral edge (21) of the seal element (7) is formed into a polygonal shape having a plurality of sides (24), and the cylindrical portion (8)
  • the sealing element (7) is fitted into the mold cavity so that it comes into contact with the inner flange (9) of a metal outer case (2) having a substantially L-shaped cross section with a flange (9).
  • the fluidized rubber material is filled into the cavity and the seal portion (4) is molded, and at the same time, the circular inner surface (8c) of the cylindrical portion (8) and the outer peripheral edge are formed.
  • the rubber material filled in the gap (25) between the side (24) of (21) is bonded to the inner flange (9) of the outer case (2) and integrated as a whole. To do.
  • the present invention it is possible to omit the crimping process, which is essential in a rotary shaft seal (used in a car air conditioner compressor or the like) having a conventional seal element, and the number of processing steps can be reduced.
  • the production process is simplified, and the rotary shaft seal with excellent sealing performance can be mass-produced with stable quality at low cost.
  • FIG. 1 is a cross-sectional view of a main part of a rotary shaft seal according to a first embodiment.
  • FIG. 2 is an enlarged cross-sectional view of a main part of the rotary shaft seal according to the first embodiment.
  • FIG. 3 is a simplified cross-sectional view of a main part for explaining the method for manufacturing the rotary shaft seal according to the first embodiment.
  • FIG. 4 is a front view of the rotary shaft seal according to the first embodiment.
  • FIG. 5 is a cross-sectional view of a main part of the rotary shaft seal according to the first embodiment.
  • FIG. 6 is an operation explanatory view showing the pressure receiving state of the rotary shaft seal of the first embodiment.
  • FIG. 8 is a cross-sectional view of a main part of Modification 1 of the rotary shaft seal according to the first embodiment.
  • FIG. 9 is a cross-sectional view of a main part of Modification 2 of the rotary shaft seal according to Embodiment 1.
  • FIG. 10 is a cross-sectional view of the main part of Modification 3 of the rotary shaft seal according to the first embodiment.
  • FIG. 12 is a cross-sectional view of a main part of a rotary shaft seal according to Embodiment 2.
  • FIG. 13 is an enlarged cross-sectional view of a main part of the rotary shaft seal according to the second embodiment.
  • FIG. 15 is a cross-sectional view of a main part of Modification 1 of the rotary shaft seal according to the second embodiment.
  • FIG. 16 is an essential part enlarged cross-sectional view of a first modification of the rotary shaft seal according to the second embodiment.
  • FIG. 17 is a cross-sectional view of a main part of a second modification of the rotary shaft seal according to the second embodiment.
  • FIG. 18 is an essential part enlarged cross-sectional view of a second modification of the rotary shaft seal according to the second embodiment.
  • FIG. 19 is an enlarged cross-sectional view of the main part of Modification 3 of the rotary shaft seal of Embodiment 2.
  • FIG. 20 is a cross-sectional view of a main part of Modification 4 of the rotary shaft seal according to Embodiment 2.
  • FIG. 21 is an essential part enlarged cross-sectional view of Modification 4 of the rotary shaft seal of Embodiment 2.
  • FIG. 22 is a simplified cross-sectional view of a main part for explaining the manufacturing method of the fourth modification of the rotary shaft seal of the second embodiment.
  • FIG. 23 is a cross-sectional view of the main part of Modification 5 of the rotary shaft seal according to Embodiment 2.
  • FIG. 24 is an essential part enlarged cross-sectional view of a fifth modification of the rotary shaft seal of the second embodiment.
  • FIG. 25 is an essential part enlarged cross-sectional view of Modification 6 of the rotary shaft seal according to Embodiment 2.
  • FIG. 26 is an enlarged cross-sectional explanatory diagram of a main part of the rotary shaft seal of the first embodiment.
  • FIG. 27 is a cross-sectional view of a main part of a rotary shaft seal according to Embodiment 3.
  • FIG. 28 is an enlarged cross-sectional view of a main part of a rotary shaft seal according to Embodiment 3.
  • FIG. 29 is a front view showing an example of a sealing element before assembling in the third embodiment.
  • FIG. 30 is a cross-sectional view of a main part of the rotary shaft seal according to the first embodiment.
  • FIG. 31 is a front view showing Modification Example 1 of the seal element before assembly of Embodiment 3.
  • FIG. 32 is a front view showing Modification Example 2 of the seal element before assembly of Embodiment 3.
  • FIG. 33 is a front view showing Modification Example 3 of the seal element before assembly of Embodiment 3.
  • FIG. 34 is a front view showing Modification Example 4 of the seal element before assembly of Embodiment 3.
  • FIG. 35 is a front view showing Modification Example 5 of the seal element before assembly of Embodiment 3.
  • FIG. 36 is a front view showing Modification Example 6 of the seal element before assembly of Embodiment 3.
  • FIG. 37 is a front view showing Modification Example 7 of the seal element before assembly of Embodiment 3.
  • FIG. 38 is a cross-sectional view of a main part showing a modification of Embodiment 3.
  • FIG. 39 is a cross-sectional view of a principal part showing a conventional rotary shaft seal.
  • FIG. 40 is a cross-sectional view of a principal part showing a rotary shaft seal of another conventional example.
  • FIG. 41 is an operation explanatory diagram of a conventional rotary shaft seal.
  • FIG. 1 is an enlarged cross-sectional view of the main part showing the rotary shaft seal 1 of Embodiment 1
  • FIG. 2 is an enlarged cross-sectional view of the main part shown in FIG. 1
  • FIG. 3 is a cross-sectional explanatory view of a main part showing the manufacturing method of the shaft seal 1 in a simplified manner.
  • 4 is a front view of FIG. 1
  • FIG. 5 is a cross-sectional view of FIG. 4 (a-a) and an enlarged view of the main part of the (b-b) cross-section.
  • the rotary shaft seal 1 includes a metal outer case 2, a metal inner case 3, and a rubber seal portion 4 having a rubber lip portion 5 slidably contacting the rotary shaft 29 (see Figs. 6 and 7), A seal element 7 having a screw groove 6 that is in sliding contact with the rotating shaft is provided! /
  • the metal outer case 2 is assembled as a whole with the caulking process in the direction of arrow C described with reference to FIGS. 39 and 40 completely omitted.
  • the seal portion 4 is formed by molding (injection molding or compression molding).
  • the outer case 2, the seal element 7, the inner case 3, and the seal portion 4 are molded. As a result, the structure is integrated.
  • the outer case 2 has a cylindrical portion 8 and an inner flange portion 9 on the low pressure side B, and has a substantially L-shaped cross section.
  • the inner case 3 has a substantially L-shaped cross section having a cylindrical portion 10 and an inner flange portion 11 on the low pressure side B. Also, the inner flange 11 of the inner case 3 slightly moves to the low pressure side B.
  • the projecting shape and the convex part 12 are formed, and the cylindrical part of the inner case 3 10 force The force is a structure assembled so as to fit into the cylindrical part 8 of the outer case 2
  • the sealing element 7 includes the outer case 2 and The inner case 3 is held by both inner flanges 9 and 11. In addition, as shown in FIG.
  • a rubber layer 13 formed by intrusion when the seal portion 4 is molded is interposed in the fitting gap portion G between the cylindrical portions 8 and 10.
  • the cylindrical portion 8 of the outer case 2 and the cylindrical portion 10 of the inner case 3 are integrated with each other by the rubber layer 13 formed and solidified at the time of molding.
  • This press-fitting may be performed by using a press machine or hitting with a hammer or the like. Note that even when an intermediate product as shown in FIG. 3 is produced by press-fitting in this way, the fluidized rubber material does not flow into the molding gap G. As a result, a stronger integrated structure is obtained (by the combined use of the mechanical integrated film and the integrated film formed by the thin rubber layer 13).
  • the seal part 4 is composed of HNBR alone or a compounded rubber material based on HNBR, or uses other rubber materials.
  • the original shape of the seal element 7 is an annular flat plate.
  • the cross section is L-shaped, and the screw groove (spiral groove) 6 side is the rotary shaft.
  • the seal element 7 is preferably a fluorine-based resin such as PTFE.
  • the seal element 7 has a partial force closer to the outer diameter.
  • the inner flange 9 and the force that is held tightly by the inner flange 11 are formed on the inner flange 11 of the inner case 3.
  • the part near the diameter is pressed strongly (surface pressure is high) to prevent internal leakage. Even if the convex portion 12 is not provided, the same effect can be obtained by enlarging the inner diameter of the inner case 3.
  • the screw groove 6 in the seal element 7 it has a bombing action (hydride port dynamic action) that pushes the fluid back to the fluid storage chamber side (high pressure side) A by the rotation of the rotating shaft, and seals during rotation. Improve ing.
  • the inner flange portion 32 of the conventional outer case 34 is disposed on the fluid storage chamber side (high pressure side) A.
  • the inner flange portion 9 of the outer case 2 is disposed on the low pressure side B.
  • the inner flange portion 11 of the inner case 3 is on the low pressure side. Located in B. In this way, on the low pressure side B, the seal element 7 is clamped and held between the inner flange portions 9 and 11.
  • the seal portion 4 includes an outer circumferential concave and convex wavy fitting cylindrical wall portion 15 that covers both the cylindrical portions 8 and 10 fitted to each other from the outer peripheral surface side, and a high pressure side end surface of both the cylindrical portions 8 and 10 8a, 10a, and a block-shaped portion 17 as a main portion 30 corresponding to the inside of the inner case 3, and a high-pressure side A of the main portion 30 (block-shaped portion 17)
  • a U-shaped concave circumferential groove 18 is formed on the high pressure corresponding surface 27, and the main portion 30 (block-like portion 17) has a rubber lip portion 5 near the inner peripheral end of the high pressure side A.
  • the axial direction position of the rubber lip portion 5 and the axial direction direction position of the end surface covering wall portion 16 are substantially matched.
  • the main portion 30 of the seal portion 4 is disposed in the inner case 3 and the virtual high-pressure corresponding surface 27 in which the concave circumferential groove 18 is not formed is formed in a shape orthogonal to the axis. Since the concave circumferential groove 18 is formed, the main portion 30 has a substantially U-shaped cross section.
  • the contact inner peripheral edge 5a of the rubber lip portion 5 that contacts the outer peripheral surface of the rotating shaft 29 is disposed at substantially the same position in the axial direction as the end surface 8a on the high pressure side A of the outer case 2. Is done.
  • the rubber lip portion 5 hardly protrudes to the high pressure side A, and the overall width W of the rotary shaft seal 1 can be remarkably reduced. It can be seen that there is a habit. That is, outer case
  • FIG. 6 a front view 4 as viewed from the axial direction (high pressure side A), and FIGS. 5 (a), (b), and 5 (a), (b) showing the cross section of FIG.
  • FIG. 6 corresponding to the section (a-a) in FIG. 4
  • FIG. 7 corresponding to the section (b--b) in FIG. 4
  • the high-pressure corresponding surface 27 of the rubber seal 4 is shown in FIG.
  • the above-described concave circumferential groove 18 is provided at a radial intermediate position, and the rubber lip portion 5 and the outer circumferential rubber portion 14 are formed in an annular shape along the inner and outer circumferences.
  • a feature of the rotary shaft seal 1 is that a plurality of radial rib portions 41 for connecting the (inner circumference) rubber lip portion 5 and the outer circumference rubber portion 14 are provided in the concave circumferential groove 18. . 4 and 5, four rib portions 41 are provided at a central angle of 90 °. It is free to reduce this to 2 or 3 or vice versa.
  • the edge of the rib 41 on the high pressure side A is shown in the figure when it is at the same position in the axial center direction as the high pressure compatible surface 27. Even if it makes it, it is free (illustration omitted).
  • FIG. 6 and FIG. 7 the force simultaneously drawing the graphs showing the contact surface pressure P as the vertical axis and the axial center position as the horizontal axis.
  • the contact surface pressure P is increased at the position where the rib 41 is absent where the contact surface pressure P is low.
  • the contact surface pressure P of the contact inner peripheral edge 5a to the rotating shaft 29 is made uneven (uneven) in the circumferential direction.
  • the lubricant in the fluid in the fluid storage chamber side A immediately enters (introduces) and spreads around the entire slidable contact area.
  • the frictional resistance of the inner peripheral edge 5a can be reduced, heat generation can be prevented, and wear can be suppressed.
  • the convex portion 12 may be continuously formed over the entire circumference.
  • the convex portions 12 are intermittently formed in the circumferential direction alternately, the seal element is formed.
  • the surface pressure for repressing (pressing) 7 increases, and it is possible to prevent the seal element 7 from rotating together with the rotating shaft. Furthermore, the part that comes into contact with the seal element 7 becomes like a saw tooth! It is more preferable because it has better holding power.
  • FIG. 8, FIG. 9, and FIG. 10 show modified examples 1 to 3 of the rotary shaft seal 1 of the first embodiment. 3 is shown.
  • the concave circumferential groove 18 is provided at the radial intermediate position of the high pressure corresponding surface 27 of the rubber seal portion 4.
  • the rubber lip portion 5 is formed in an annular shape along the inner periphery, and at least one of the depth dimension N, the width dimension S, and the cross-sectional shape of the recessed peripheral groove 18 is formed.
  • the contact surface pressure P to the rotating shaft 29 (see FIGS. 6 and 7) of the rubber lip 5 is set unevenly in the circumferential direction as shown in FIG. 11 (b).
  • FIGS. 8 to 11 the outer case 2, the inner case 3, and the seal element 7 as already described in FIGS. 1 to 7 are provided, and all the parts are integrated by molding. Except for the concave circumferential groove 18 and the rubber lip portion 5 that are desired to be configured, the description is omitted because they are the same as those shown in FIGS. However, as described in FIGS. 1 to 7, one of the outer case 2 and the inner case 3 is omitted, each shape is changed variously, the seal element 7 is omitted, and vice versa. Design changes such as making more than one are free.
  • Fig. 11 (a) it is divided into 3 arcs. Deploy. Of course, it is also preferable to divide and arrange four or more arc portions.
  • the shaded circular arc part 42 is a dimension with a large depth dimension N.
  • each width dimension is allocated as an appropriate ratio from (1: 9) to (9: 1).
  • each width dimension is divided into three arcs.
  • a hatched circular arc portion 42 represents a portion of a dimension S having a large width dimension S.
  • the former is large enough. This former is indicated by the hatched area in FIG. 11 (a). The ratio of the total circumferential range of each of the former and the latter is distributed as an appropriate ratio of (1: 9) to (9: 1). [0051] Note that in FIG. 10 and FIG. 9, it is preferable to divide into four or more parts.
  • FIG. 11 (b) will be additionally described.
  • Fig. 11 is a graph showing the contact pressure P on the surface of the rotating shaft 29 of the rubber lip 5 in a circular shape in the pressure receiving state (see Figs. 6 and 7).
  • Fig. 11 (a) the depth dimensions N and Z or Although the case where each of the width dimensions S is arranged in three parts is shown, Fig. 11 (b) shows how the contact surface pressure P changes in the circumferential direction when each part is arranged in six parts. This is an example. As shown in Fig. 11 (b), the contact surface pressure P becomes non-uniform (non-uniform) in the same direction.
  • lubricating oil is applied from the part of the small contact surface pressure (valley part) to the contact inner peripheral edge of the rubber lip part 5. Introduce and permeate between the edge 5a and the rotating shaft 29 (see Figures 6 and 8), and with rotation, lubricate the entire circumference of the sliding contact area to prevent frictional heat and prevent early wear. Can be prevented and a long life can be achieved.
  • the fluidized rubber material is injected into the mold, the seal portion 4 is molded, and the rubber layer 13 is formed in the fitting gap portion G with a uniform thickness all around.
  • the thickness dimension of the rubber layer 13 varies depending on the strength and type of rubber. However, if the thickness is preferably too small, uneven thickness of the rubber layer 13 (at the circumferential direction) is likely to occur. .
  • the inner peripheral surface of the outer case 2 and the inner peripheral surface of the inner case 3 are fitted in a press-fitted form, they are assembled by pressing with a press machine, a nonmmer, or the like. As shown in Fig. 3, an intermediate product as shown in Fig.
  • the outer case 2, the inner case 3, and the seal element 7 can be integrally formed at the same time as the seal portion 4 is formed in the mold, and the conventional crimping process is completely omitted. .
  • each component can be assembled at the time of rubber injection molding or compression molding of the seal portion 4.
  • the convex portion 12 is formed on the inner flange portion 11 of the inner case 3, the contact surface pressure of the inner case 3 and the inner flange portions 11 and 9 of the outer case 2 is (locally). ) It has the advantage that it can effectively prevent internal leakage as the rotary shaft seal 1 and can prevent co-rotation of the seal element 7 and the rotary shaft. Even if the convex portion 12 is not provided, the same effect can be obtained by enlarging the inner diameter of the inner case 3.
  • the caulking process of the metal outer case 2 is omitted, and the outer case 2 and the seal element 7 are molded by molding the seal portion 4. Since the inner case 3 and the seal part 4 have an integrated structure, it is possible to mass-produce high-quality products at low cost, simplify production facilities, and produce efficiently.
  • the rotary shaft seal 1 of Embodiment 1 is the above-mentioned rubber shaft seal provided with the rubber seal portion 4 having the rubber lip portion 5 that is in sliding contact with the rotary shaft 29.
  • sticker Part 4 has a concave groove 18 in the radial intermediate position of the high pressure corresponding surface 27 corresponding to the fluid storage chamber side A, and the rubber lip part 5 and the outer rubber part 14 are annularly formed along the inner and outer circumferences, respectively.
  • a radial rib portion 41 for connecting the rubber lip portion 5 and the outer peripheral rubber portion 14 is provided in the concave circumferential groove 18, and the deformation of the rubber lip portion 5 is different on the circumference.
  • the contact surface pressure P becomes uneven on the circumference (non-uniform), and the lubricating oil in the sealing fluid can easily be introduced and infiltrated into the sliding portion between the rubber lip 5 and the rotating shaft 29 ( Lubricating oil can easily be introduced and infiltrated from a small contact surface pressure part), and as it rotates, it spreads all around the sliding contact part, reducing the generation of frictional heat, and the rubber lip part 5 (contact inner peripheral edge 5a) Can prevent premature friction and prolong the service life. In particular, a good seal life can be obtained even under high speed and high pressure conditions.
  • the rotary shaft seal provided with the metal outer case 2, the metal inner case 3, the rubber seal portion 4 having the rubber lip portion 5 that is in sliding contact with the rotary shaft 29, and the seal element 7 is provided.
  • the outer case 2, the seal element 7, the inner case 3, and the seal portion 4 are integrated with each other by molding the seal portion 4, and the rubber seal portion 4 is on the fluid storage chamber side.
  • a concave circumferential groove 18 is formed in the middle position in the radial direction of the high pressure corresponding surface 27 corresponding to A, the rubber lip portion 5 and the outer circumferential rubber portion 14 are formed in an annular shape along the inner circumference and the outer circumference, and Since the radial rib portion 41 for connecting the rubber lip portion 5 and the outer peripheral rubber portion 14 is provided in the concave circumferential groove 18, high-quality products can be stably produced in large quantities at low cost, and the manufacturing equipment Can be simplified and can be produced efficiently.
  • the sealing element bombing action prevents external leakage during the rotation of the rotary shaft 29, and the contact surface pressure P becomes non-uniform (non-uniform) on the circumference.
  • Lubricating oil in the sealing fluid can easily be introduced and infiltrated into the sliding contact part with 29 (the lubricating oil can be easily introduced and infiltrated from the small contact surface pressure part), and the entire circumference of the sliding contact part is accompanied by rotation. It is possible to reduce the generation of frictional heat, prevent premature friction of the rubber lip part 5 (the contact inner peripheral edge 5a), and achieve a long life. In particular, a good seal life can be obtained even under high speed and high pressure conditions.
  • the rubber seal portion 4 is a high pressure compatible surface 2 corresponding to the fluid storage chamber side A.
  • a concave groove 18 is formed in the radial intermediate position of 7 to form the rubber lip portion 5 in an annular shape along the inner circumference, and the depth dimension N, width dimension S, and cross section of the concave groove 18. Small in shape At least one is set to change in the circumferential direction, and the contact surface pressure P of the rubber lip 5 to the rotating shaft 29 is configured to be uneven in the circumferential direction.
  • Lubricating oil is introduced and infiltrated into the sliding contact part with the rotating shaft 29 from the part of this part, and along with the rotation, the lubricating oil is spread all around the sliding contact part to prevent the generation of frictional heat. Abrasion can be prevented and long life can be achieved. In addition, there is an advantage that there is no problem of poor airtightness in the case where unevenness is provided on the sliding contact part itself (contact inner peripheral edge 5a itself).
  • the rotary shaft seal provided with the metal outer case 2, the metal inner case 3, the rubber seal portion 4 having the rubber lip portion 5 that is in sliding contact with the rotary shaft 29, and the seal element 7 is provided.
  • the outer case 2, the seal element 7, the inner case 3, and the seal portion 4 are integrated with each other by molding the seal portion 4, and the rubber seal portion 4 is on the fluid storage chamber side.
  • a concave circumferential groove 18 is formed in the radial intermediate position of the high pressure corresponding surface 27 corresponding to A to form the rubber lip portion 5 in an annular shape along the inner circumference, and the depth dimension N of the concave circumferential groove 18 At least one of the width dimension S and the cross-sectional shape is set so as to change in the circumferential direction, so that the contact surface pressure P of the rubber lip portion 5 to the rotating shaft 29 becomes uneven in the circumferential direction.
  • Easy and cheap, with simple manufacturing equipment Enables production it is also suitable for multi-volume production.
  • the lubricating oil is introduced and infiltrated into the sliding contact area with the rotating shaft 29, and the lubricating oil is spread over the entire circumference of the sliding contact area with the rotation. Can be prevented, premature wear can be prevented, and a long life can be achieved.
  • cylindrical portions 8 and 10 are press-fitted so that the inner peripheral surface of the cylindrical portion 8 of the outer case 2 and the outer peripheral surface of the cylindrical portion 10 of the inner case 3 are pressed against each other.
  • the strength of the outer case 2 and the inner case 3 is sufficiently high (even if the crimping process described in FIGS. 39 and 40 of the outer case 34 is omitted). A solid seal with sufficient strength can be obtained.
  • the outer case 2 has a substantially L-shaped cross section having a cylindrical portion 8 and a low pressure side inner flange portion 9, and the inner case 3 has a cross section having a cylindrical portion 10 and a low pressure side inner flange portion 11. It is generally L-shaped, and the sealing element 7 is held tightly by the inner flanges 9 and 11 above.
  • the outer case 2 and the inner case are interposed by the rubber layer 13 formed by intrusion into the fitting gap portion G of the cylindrical portions 8 and 10 when the seal portion 4 is molded.
  • the outer case 2 and the inner case 3 are integrated with the rubber layer 13 formed by press-fitting when the seal 3 is not formed or when the seal portion 4 is not molded, and the seal portion
  • the main portion 30 of 4 is disposed in the inner case 3 having a substantially L-shaped cross section, and the high-pressure corresponding surface 27 in a virtual state in which the concave circumferential groove 18 is not formed is formed in a shape orthogonal to the axial center. Because it has a twisted configuration, the outer case 2 and the inner case 3 can be integrated with sufficient strength, the possibility of internal leakage can be reduced by the rubber layer 13, and the posture of the seal element 7 is stable (without rattling). Rotating shaft 29 Not around him to force Hyde port dynamic (bombing) acts always stably paragraph shall during the rotation of the rotary shaft 29, it is possible to more reliably prevent external leakage (leakage).
  • the metal outer case 2, the metal inner case 3, and the seal element 7 are attached to the mold cavity with the seal element 7 attached by the outer case 2 and the inner case 3.
  • the fluidized rubber material is filled into the cavity and solidified, and the seal portion 4 is molded.
  • the outer case 2, the inner case 3, and the seal element 7 are integrated together. According to the manufacturing method of the rotating shaft seal, the complicated conventional crimping process can be omitted at all, the manufacturing process can be simplified and the cost can be reduced, and the seal for a compressor for a car air conditioner can be severe. It is possible to reliably produce a large number of rotary shaft seals that can sufficiently meet the various usage conditions (requirements).
  • FIG. 12 is an enlarged cross-sectional view of a main part showing the rotary shaft seal 1 of Embodiment 2
  • FIG. 13 is an enlarged cross-sectional view of the main part of FIG. 12
  • FIG. 14 is a rotary shaft seal of Embodiment 2.
  • FIG. 2 is a cross-sectional explanatory view of the relevant part showing the production method 1 in a simplified manner. Parts having the same names as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment.
  • the rotary shaft seal 1 includes a metal outer case 2, a metal inner case 3, a rubber seal portion 4 having a rubber lip portion 5 slidably contacting the rotary shaft (not shown), and the rotary shaft A seal element 7 having a screw groove 6 that is slidably in contact with the! / [0069]
  • the metal outer case 2 is assembled as a whole with the caulking process in the direction of arrow C as described in FIGS. 39 and 40 being completely omitted.
  • the seal portion 4 is formed by molding (injection molding or compression molding).
  • the outer case 2, the seal element 7, the inner case 3, and the seal portion 4 are molded. By this, it becomes a monolithic structure.
  • the outer case 2 has a cylindrical portion 8 and an inner flange portion 9 on the low pressure side B, and has a substantially L-shaped cross section.
  • the inner case 3 has a substantially L-shaped cross section having a cylindrical portion 10 and an inner flange portion 11 on the low pressure side B.
  • the inner flange portion 11 of the inner case 3 has a slightly protruding shape and convex portion 12 formed on the low pressure side B, and is fitted into the cylindrical portion 8 of the inner case 3 and the cylindrical portion 8 of the outer case 2.
  • the force sealing element 7 having the structure assembled as described above is held by the inner flange portions 9 and 11 of the outer case 2 and the inner case 3 together.
  • the fitting gap G between the cylindrical portions 8 and 10 has a thin rubber layer 13 formed by intrusion of a fluid rubber material when the seal portion 4 is formed. Intervene. This thin rubber layer 13 is formed by intrusion when the seal portion 4 is molded.
  • FIG. 12 to FIG. 14 are further explained.
  • the cylindrical portion 8 of the outer case 2 has a stepped portion 51 (near the center in the axial direction), and is a slightly large-diameter cylindrical high-pressure side half portion. 52, and the low-pressure side half 53, which is slightly smaller in diameter than that, also has a force, so the inner diameter D of the high-pressure side half 52 is the low-pressure side.
  • the first gap dimension T of the first gap portion 54 on the high pressure side A is set to a low value corresponding to the low pressure side half 53.
  • the fitting gap portion G is larger than the second gap dimension T of the second gap portion 55 on the compression side B.
  • the fitting gap G between the cylindrical portions 8 and 10 has the first gap portion 54 formed by intrusion of the fluid rubber material when the seal portion 4 is formed.
  • a thick rubber layer 56 and a rubber layer 57 composed of the thin rubber layer 13 in the second gap portion 55 are interposed. That is, the first gap portion 54 is formed larger on the high pressure side (A) than on the low pressure side (B).
  • the first gap portion 54 is filled with a rubber material.
  • the rubber material flow is smooth and the thin rubber layer 13 is formed reliably and stably.
  • the cylindrical parts 8 and 10 can be firmly integrated.
  • the outer case 2 and the inner case 3 are fitted with a small second gap dimension T in the low-pressure side half 58 of the inner case 3 and the inner case 3 has a high pressure.
  • the side half 59 is fitted to the (outer case 2) with a large first gap dimension T.
  • the second gap dimension T is set to 0.005 mm ⁇ T ⁇ 0.20 mm.
  • the first gap dimension T is set to 0.5 mm ⁇ T ⁇ 3.0 mm, and the first gap part 54
  • FIGS. 15 and 16 show a first modification of the rotary shaft seal 1 of the second embodiment, and correspond to FIGS. 12 and 13 showing the second embodiment, respectively.
  • the first gap dimension T is low
  • the fitting gap G is formed so as to be larger than the second gap dimension T.
  • the outer case 2 has a cylindrical portion 8 and an inner flange portion 9 on the low pressure side B, and has a substantially L-shaped cross section.
  • the inner case 3 has a substantially L-shaped cross section having a cylindrical portion 10 and an inner flange portion 11 on the low pressure side B.
  • the force seal element 7 has a structure in which the cylindrical portion 10 of the inner case 3 is assembled so as to fit into the cylindrical portion 8 of the outer case 2, and both inner flange portions of the outer case 2 and the inner case 3 9 and 11 are held firmly.
  • Figure 1 As shown in FIG. 6, a thin rubber layer 13 formed by the inflow of a flowing rubber material is interposed in the fitting gap G between the cylindrical portions 8 and 10 when the seal portion 4 is formed. ing. This thin rubber layer 13 is formed by intrusion when the seal portion 4 is molded.
  • the cylindrical part 8 of the outer case 2 has a bent part 63 (near the center in the axial direction or close to the high pressure side A).
  • the high-pressure side half 52 which gradually increases in diameter toward the high-pressure side A, and the low-pressure side half 53, which is slightly smaller in diameter, have a force, so the average inner diameter D of the high-pressure side half 52 is low.
  • the first gap dimension T (as an average value) of the first gap portion 54 on the high pressure side A corresponding to the high pressure side half 52 is set to the low pressure side corresponding to the low pressure side half 53.
  • the fitting gap G is formed so as to be larger than the second gap dimension T of the second gap portion 55 of B.
  • the first gap dimension T is large (having a triangular cross section).
  • the rubber material enters from the first gap 54, and then the second gap portion 5 having a small second gap dimension T 5
  • the rubber layer 13 is formed in a thin-walled shape with certainty and stability, and the cylindrical portions 8 and 10 can be firmly integrated.
  • the outer case 2 and the inner case 3 are fitted with a small second gap dimension T at the low-pressure side half 58 of the inner case 3 and the inner case 3 has a high pressure.
  • the side half 59 is fitted to the (outer case 2) with a large first gap dimension T.
  • the second gap dimension T is set to 0.005 mm ⁇ T ⁇ 0.20 mm.
  • the first gap dimension T shown as an average value is set to 0.5 mm ⁇ T ⁇ 3.0 mm, and
  • the length dimension L in the axial direction of the gap 54 is 30% of the length dimension L of the inner case 3.
  • connection rigidity between the case 2 and the inner case 3 will be insufficient.
  • L ⁇ 0.3 XL In this case, the permeation distance of the rubber portion is insufficient and internal leakage of the sealing fluid is likely to occur.
  • FIG. 17 and FIG. 18 show Modification 2 of the rotary shaft seal 1 of Embodiment 2, wherein the outer case 2 has a substantially cylindrical cross section having a straight cylindrical portion 8 and a low pressure side inner flange portion 9.
  • the cylindrical part 10 of the inner case 3 has an outer diameter D of the high-pressure side half part 59 and the low-pressure side half part 59.
  • the shape is set smaller than the outer diameter D of the part 58. In this way, the first gap on the high pressure side A
  • the fitting gap G is formed so that the dimension T is larger than the second gap dimension T on the low-pressure side B.
  • the cylindrical portion 10 of the inner case 3 has a stepped portion 64 (near the center in the axial direction), and has a slightly small cylindrical shape.
  • the high pressure side half 59 and the slightly larger diameter cylindrical low pressure side half 58 have a force, so the outer diameter D of the high pressure side half 59 is set smaller than the inner diameter D of the low pressure side half 58. Has been. In this way
  • the fitting gap G is formed.
  • the first gap portion 54 formed by intrusion of the fluid rubber material into the fitting gap portion G of the cylindrical portions 8 and 10 when the seal portion 4 is formed.
  • the thick rubber layer 56 and the thin rubber layer 13 in the second gap portion 55 are interposed.
  • the rubber material 13 is smoothly flown, the thin rubber layer 13 is formed reliably and stably, and the cylindrical portions 8 and 10 can be firmly integrated.
  • FIG. 19 is an enlarged cross-sectional view of a main part showing a third modification of the rotary shaft seal 1 of the second embodiment.
  • the first gap dimension T is formed to gradually increase from the low pressure side B to the high pressure side A.
  • the shape of the high-pressure side half 59 of the cylindrical portion 10 of the inner case 3 is tapered so that the diameter gradually decreases to the high-pressure side A, and the average outer diameter D of the high-pressure side half 59 is reduced to 58.
  • the fitting gap G is formed so that the first gap dimension (average value) T on the high pressure side A is larger than the second gap dimension T on the low pressure side B.
  • the cylindrical portion 10 of the inner case 3 has a bent portion 65 (near the center in the axial direction or close to the high pressure side A).
  • the first gap dimension T (as an average value) of the first gap part 54 corresponding to the high pressure side half 59 is changed to the second gap dimension T of the second gap part 58 corresponding to the low pressure side half 58. than
  • a gap G is formed so as to be larger.
  • FIG. 26 is an enlarged cross-sectional view of a main part of the rotary shaft seal 1 of Embodiment 1, and shows a portion corresponding to FIG. 13, FIG. 16, FIG. 18, or FIG.
  • the thick rubber layer 56 in FIG. 13, FIG. 16, FIG. 18, or FIG. 19 is omitted, and the straight shape of the outer case 2 and the inner case 3 is omitted.
  • the fitting parts of the cylindrical parts 8 and 10 form the uniform fitting gap part G with the above-mentioned minute second gap dimension T.
  • the end faces 8a and 10a of the cylindrical portions 8 and 10 are connected to the outer rubber end face 4a (the strength when the seal is attached). Etc.) for close proximity, and is placed inside the rubber material. That is, the wall thickness dimension T of the end face covering wall portion 16 is small, so that FIG.
  • the sealing fluid permeates through the end surface covering wall portion 16 and continues (as described above).
  • internal leakage internal leakage occurs through the layer 13.
  • At least the first gap portion 54 having the relatively large first gap dimension T is completely filled with rubber, and
  • the fluid (especially gas) on the high-pressure side A is surely prevented from entering and permeating through the rubber end face 4a, and no internal leakage (as indicated by arrow F in FIG. 26) occurs. Excellent sealing performance.
  • FIG. 20, FIG. 21, and FIG. 22 show Modification 4 of the rotary shaft seal 1 of Embodiment 2
  • FIG. 20 is an enlarged cross-sectional view of the main part
  • FIG. FIG. 22 is a cross-sectional view of relevant parts for explaining the manufacturing method.
  • the inner case 3 is arranged in a stepped manner so that the high pressure side end 60 of the cylindrical portion 10 of the inner case 3 is on the high pressure side A of the high pressure side end 70 of the cylindrical portion 8 of the outer case 2. That is, the dimensional force S in the axial direction of the outer case 2 is set to be small, and the high-pressure side end 60 of the cylindrical portion 10 of the inner case 3 is set higher than the high-pressure side end surface 8a of the cylindrical portion 8 of the outer case 2.
  • the high-voltage side half 59 of the inner case 3 is not externally fitted by the outer case 2 and is exposed, and is covered with a rubber member (cylindrical wall 15). That is, the high-pressure side half 59 of the outer peripheral surface of the metal inner case 3 is exposed and covered with a rubber member.
  • the (thin film-like) rubber layer 13 includes the inner peripheral surface of the cylindrical portion 8 of the outer case 2 and the low pressure side half portion 58 (of the outer peripheral surface) of the cylindrical portion 10 of the inner case 3. In between.
  • the rubber layer 13 is formed by intrusion during molding, and the gap size of the gap G is the same as the second gap size T in FIGS. 12 to 14 described above. . That is,
  • the length L of the exposed high-pressure side half 59 is the length of the inner case 3. 30% of dimension L
  • the cylindrical wall portion 15 (which also has a rubber force) is elastically compressed and deformed on the inner peripheral surface of the mounting member 61 such as the casing inner peripheral surface indicated by the phantom line, and the fitting is performed.
  • the cylindrical wall portion 15 is provided with an uneven wave portion, a sealing property (seal property) is maintained, and a dense space is provided between the uneven wave portion and the inner peripheral surface of the mounting member 61. Since the sealed fluid (gas) does not enter, the distance from the position of the high pressure side end of the rubber layer 13 (indicated by point Q in FIG. 21) to the sealed fluid on the high pressure side A The permeation distance of the rubber part is , (T + L)
  • L is the uneven wave part of the cylindrical wall part 15.
  • this L or (T + L) is sufficiently larger than the wall thickness dimension T of the end face covering wall portion 16 in FIG.
  • FIG. 23 and FIG. 24 show Modification 5 of the rotary shaft seal 1 of Embodiment 2
  • FIG. 23 is an enlarged sectional view of an essential part thereof
  • FIG. 24 is an enlarged sectional view of an essential part thereof.
  • the rotary shaft seal 1 has the same basic configuration as that described with reference to FIGS. 12 to 19, and will not be described repeatedly. Hereinafter, mainly different configurations will be described.
  • the high pressure side end 70 of the cylindrical portion 8 of the outer case 2 is arranged in a stepped manner so that the cylindrical portion 10 of the inner case 3 is on the high pressure side A of the high pressure side end 60. That is, the axial dimension of the inner case 3 is set to be small, and the high-pressure side end 70 of the cylindrical portion 8 of the outer case 2 is set to the high-pressure side A rather than the high-pressure side end surface 10a of the cylindrical portion 10 of the inner case 3.
  • the high-pressure side half 52 of the outer case 2 is not fitted by the inner case 3 and is exposed on the inner diameter side, and is covered with a rubber member. That is, the inner peripheral surface of the high-pressure side half 52 of the metal outer case 2 is exposed (uncovered), and the rubber member is covered.
  • the (thin film-like) rubber layer 13 is formed on the outer peripheral surface of the cylindrical portion 10 of the inner case 3.
  • the cylindrical portion 8 of the outer case 2 is interposed between the low pressure side half 53 (in the inner peripheral surface).
  • the rubber layer 13 is formed by intrusion during molding, and the gap size of the gap G is the same as the second gap size T in FIGS. 12 to 14 described above. . That is,
  • the length L of the exposed high-pressure half 52 is the length of the inner case 3.
  • the L means the shortest distance from the point Q to the concave circumferential groove 18. Therefore, this L or
  • FIG. 25 shows a sixth modification of the rotary shaft seal 1 of the second embodiment.
  • the rotary shaft seal 1 is configured such that the rotary shaft seal 1 of the second embodiment and the modified example 5 are combined.
  • the basic configuration is the same as that described with reference to FIGS. 12 to 24, and repeated description is omitted.
  • the first gap dimension T is gradually increased from the low pressure side B to the high pressure side A.
  • the shape of the high pressure side half 52 of the cylindrical portion 8 of the outer case 2 is tapered so that the diameter gradually increases to the high pressure side A, and the average inner diameter D of the high pressure side half 52 is reduced.
  • Pressure side half 53 is set larger than inner diameter D. In this way, on the high pressure side A (average value
  • the first gap dimension T is larger than the second gap dimension T on the low pressure side B.
  • a gap G is formed.
  • the high pressure side end portion 70 of the cylindrical portion 8 of the outer case 2 is the cylindrical portion 1 of the inner case 3.
  • the high pressure side end 60 of 0 is arranged in a different shape so as to be on the high pressure side A! /. That is, the dimensional force S in the axial direction of the inner case 3 is set to be smaller, and the high-pressure side end 70 of the cylindrical portion 8 of the outer case 2 is set to the high-pressure side A than the high-pressure side end surface 10a of the cylindrical portion 10 of the inner case 3
  • the high-pressure side half 52 of the outer case 2 is not fitted by the inner case 3, but is exposed on the inner diameter side, and is covered with a rubber member. That is, the inner peripheral surface of the high-pressure side half 52 of the metal outer case 2 is exposed (uncovered) and is covered with the rubber member.
  • the seal portion 4 can be HNBR alone or based on HNBR.
  • the composition is made of rubber material or other rubber material is used.
  • the original shape (free state) of the seal element 7 is an annular flat plate shape.
  • the screw element (spiral groove) has an L-shaped cross section. ) 6 side contacts the outer peripheral surface of the rotating shaft.
  • the seal element 7 is preferably a fluorine-based resin such as PTFE.
  • the seal element 7 has a partial force close to the outer diameter, and is held by the inner flange portion 9 and the inner flange portion 11, but the convex portion 12 is formed on the inner flange portion 11 of the inner case 3, and the seal element 7 The part near the outer diameter is pressed strongly (surface pressure is high) to prevent internal leakage. Further, the same effect can be obtained by enlarging the inner diameter of the inner case 3 without providing the convex portion 12.
  • the rotating shaft rotates to push the fluid back to the fluid storage chamber side (high pressure side) A (hydride port dynamic action), improving sealing performance during rotation I am letting.
  • the inner flange portion 32 of the conventional outer case 34 is arranged on the fluid storage chamber side (high pressure side) A Embodiment 2
  • the inner flange portion 9 of the outer case 2 is disposed on the low pressure side B.
  • the inner flange portion of the conventional inner case 37 was disposed on the fluid storage chamber side (high pressure side) A.
  • the inner flange portion 11 of the inner case 3 is 11. Is arranged on the low pressure side B. In this way, on the low pressure side B, the seal element 7 is pressure-bonded and held by the inner flange portions 9 and 11.
  • the seal portion 4 is an outer surface that covers the cylindrical portions 8 and 10 fitted to each other from the outer peripheral surface side.
  • a U-shaped concave groove 18 is formed on the end surface of the block-shaped portion 17 on the high-pressure side A, and the rubber lip portion is inclined obliquely from the inner peripheral end of the block-shaped portion 17 on the high-pressure side A toward the inner diameter. 5 is connected in an elongated shape.
  • the axial center position of the rubber lip portion 5 and the axial center position of the end surface covering wall portion 16 are substantially matched.
  • the block-shaped portion 17 and the rubber lip portion 5 have a substantially U-shaped cross section by forming the concave circumferential groove 18.
  • the contact inner peripheral edge 5a of the rubber lip portion 5 that contacts the outer peripheral surface of the rotating shaft is the end on the high pressure side A of the inner case 3 in the illustrations of FIGS. 12, 15, 17, and 20.
  • the surface 10a is disposed at substantially the same position in the axial direction.
  • a contact inner peripheral edge 5a is disposed at substantially the same position as the end face 8a on the high pressure side A of the outer case 2 in the axial direction. Although not shown, it may be preferable to dispose the inner peripheral edge 5a on the low pressure side B rather than the end face 10a or 8a.
  • the rubber lip portion 5 hardly protrudes toward the high pressure side A as compared with Figs. 39 to 41 of the conventional example, and the overall width W of the rotary shaft seal 1 can be significantly reduced.
  • the rotary shaft seal 1 of the second embodiment is compacted to a full width dimension W that is substantially the same as the full width dimension of the outer case 2.
  • the defect rate due to external factors can be significantly reduced during the manufacturing process of rotary shaft seals and during the assembly of car air conditioner compressors using such seals.
  • the convex portion 12 may be continuously formed over the entire circumference.
  • the convex portions 12 are intermittently formed in the circumferential direction alternately, the seal element is formed.
  • the surface pressure for repressing (pressing) 7 increases, and it is possible to prevent the seal element 7 from rotating together with the rotating shaft.
  • the part that comes into contact with the seal element 7 looks like a saw tooth! It is more preferable because it improves the adhesive strength.
  • the inner peripheral surface of the outer case 2 and the inner peripheral surface of the inner case 3 may be assembled so as to be fitted in a press-fitted shape.
  • assemble it so that it can be pushed in with a press or nommer, or assemble it so that it is pushed in when the mold is closed, and make an intermediate product as shown in Fig. 14 or Fig. 22 and place it in the mold.
  • the outer case 2, the inner case 3, and the seal element 7 can be integrally formed simultaneously with the formation of the seal portion 4 in the mold, and the conventional crimping process is completely omitted. . In other words, each component can be assembled at the time of rubber injection molding or compression molding of the seal portion 4.
  • the convex portion 12 is formed on the inner flange portion 11 of the inner case 3, the contact surface pressure of both inner flange portions 11, 9 of the inner case 3 and the outer case 2 (locally) ) It has the advantage that it can effectively prevent internal leakage as the rotary shaft seal 1 and can prevent co-rotation of the seal element 7 and the rotary shaft. Even if the convex portion 12 is not provided, the same effect can be obtained by enlarging the inner diameter of the inner case 3.
  • the design can be freely changed, and the rotary shaft seal 1 of the second embodiment and the modification 5 are combined. It may be configured. Further, the configuration may be such that Modification 2 and Modification 4 are combined. Further, the configuration may be such that Modification 3 and Modification 4 are combined.
  • the rubber layer 57 may not be interposed in the second gap portion 55.
  • the screw groove 6 may be omitted at all, or a plurality of large and small circular grooves may be formed concentrically. If the inner peripheral surface of the outer case 2 and the inner peripheral surface of the inner case 3 may be fitted in a press-fit manner, assemble them so that they can be pushed in with a press or a nonmmer. An intermediate product such as 14 and 22 is manufactured, set in a mold, and fluidized rubber material is injected into the mold to form a seal portion 4. Fluid rubber material enters the minute fitting gap G to form a rubber layer 13, and it is integrated by the rubber layer 13 and mechanically integrated by press fitting (press fitting). By cooperating with each other, it is possible to obtain a rotating shaft seal with a stronger unitary structure.
  • the outer case 2, the inner case 3, and the seal element 7 can be integrally formed at the same time as the seal portion 4 is formed in the mold, so that the conventional crimping process is completely omitted. ing. In other words, each component can be assembled at the time of rubber injection molding or compression molding of the seal portion 4.
  • the convex portion 12 is formed on the inner flange portion 11 of the inner case 3, the contact surface pressures of the inner case 3 and the inner flange portions 11, 9 of the outer case 2 (locally) ) As a rotary shaft seal 1, there is an advantage that internal leakage can be effectively prevented. Further, the same effect can be obtained by enlarging the inner diameter of the inner case 3 without providing the convex portion 12.
  • one or a plurality of radial ribs are provided in the concave circumferential groove 18, and the contact inner peripheral edge 5a of the rubber lip portion 5 and the outer peripheral surface of the rotating shaft are arranged.
  • the contact surface pressure with the shaft is changed in the rotational circumferential direction, making it easier for the lubricating fluid to enter between the inner peripheral edge 5a and the outer peripheral surface of the rotating shaft, reducing the generation of frictional heat and extending the service life. Is preferred.
  • the rotary shaft seal 1 of Embodiment 2 includes the metal outer case 2, the metal inner case 3, the rubber seal portion 4 having the rubber lip portion 5 slidably contacting the rotary shaft, and the rotational seal.
  • the rotary shaft seal equipped with the seal element 7 slidably contacting the shaft the caulking process of the metal outer case 2 is omitted, and the outer case 2, the seal element 7, the inner case 3, and the seal portion 4 are A first gap is formed on the high pressure side A larger than the low pressure side B between the inner peripheral surface of the cylindrical portion 8 of the outer case 2 and the outer peripheral surface of the cylindrical portion 10 of the inner case 3.
  • the outer case 2 and the inner case 3 are formed with the part 54 and the rubber layer 57 interposed in the first gap part 54, it is possible to cope with severe use conditions. Can be manufactured at low cost A. High sealing performance is demonstrated stably. In particular, the rubber layer 57 in the first gap portion 54 effectively prevents leakage from the gaps between the parts (internal leak), and exhibits further sealing performance.
  • the outer outer casing 2, the sealing element 7, the inner casing 3, and the sealing section 4 are formed by molding the sealing section 4 while omitting the crimping process of the metallic outer casing 2. Therefore, high-quality products can be mass-produced at a low cost, and the production equipment can be simplified and can be produced efficiently.
  • the inner peripheral surface of the cylindrical portion 8 of the outer case 2 and the cylindrical portion of the inner case 3 If the above-mentioned cylindrical parts 8, 10 are integrated by press-fitting so that the outer peripheral surface of 10 is pressed against each other, the integrated strength of the outer case 2 and the inner case 3 is sufficiently large ( Even if the caulking process described in FIG. 39 and FIG. 40 of the outer case 34 is omitted, a seal having a sufficient strength can be obtained.
  • the outer case 2 has a substantially L-shaped cross section having a cylindrical portion 8 and a low pressure side inner flange portion 9, and the inner case 3 has a cross section having a cylindrical portion 10 and a low pressure side inner flange portion 11.
  • the seal element 7 is clamped and held by the inner flange portions 9 and 11, and the seal portion 4 is formed in the fitting gap portion G of the cylindrical portions 8 and 10.
  • the outer case 2 and the inner case 3 are integrated with each other through the rubber layer 13 formed by intrusion into the outer case 2, so that the outer case 2 and the inner case 3 can be formed with sufficient strength.
  • the rubber layer 13 can reduce the possibility of internal leakage.
  • the posture of the seal element 7 is stable (not rattling), and does not move with the rotational frictional force of the rotating shaft, and always performs stable hide-port dynamic (bombing) operation while the rotating shaft is rotating. .
  • the metal outer case 2, the metal inner case 3, and the seal element 7 are placed in the mold cavity with the outer case 2 and the inner case 3 fitting the seal element 7 together.
  • the fluidized rubber material is filled into the cavity and solidified, and the seal portion 4 is molded.
  • the outer case 2, the inner case 3, and the seal element 7 are integrated together. According to the manufacturing method of the rotating shaft seal, the complicated conventional crimping process can be omitted at all, the manufacturing process can be simplified and the cost can be reduced, and the seal for a compressor for a car air conditioner can be severe. It is possible to reliably produce a large number of rotary shaft seals that can sufficiently meet the various usage conditions (requirements).
  • the rotary shaft seal of Embodiment 2 includes a metal outer case 2, a metal inner case 3, a rubber seal portion 4 having a rubber lip portion 5 that is in sliding contact with the rotary shaft, and a slide on the rotary shaft.
  • the caulking process of the metal outer case 2 is omitted, and the outer case 2, the sealing element 7, the inner case 3, and the sealing portion 4 Is formed between the inner peripheral surface of the cylindrical portion 8 of the outer case 2 and the outer peripheral surface of the cylindrical portion 10 of the inner case 3.
  • the first gap dimension T on the high-pressure side A (which gradually increases toward the high-pressure side) A is low.
  • a metal outer case 2, a metal inner case 3, a rubber seal portion 4 having a rubber lip portion 5 that is in sliding contact with the rotating shaft, and a seal element 7 that is in sliding contact with the rotating shaft are provided.
  • the caulking process of the metal outer case 2 is omitted, and the outer case 2, the seal element 7, the inner case 3, and the seal part 4 are integrated, and the outer case Since one of the high-pressure side end 70 of the cylindrical portion 8 and the high-pressure side end 60 of the cylindrical portion 10 of the inner case 3 is arranged in a stepped manner so as to be on the high-pressure side A than the other, it penetrates the rubber.
  • the outer casing 2, the seal element 7, the inner case 3, and the seal portion 4 are integrated with each other by omitting the crimping of the metal outer case 2.
  • the high pressure side end 60 of the cylindrical portion 10 of the inner case 3 protrudes from the high pressure side end surface 8a of the cylindrical portion 8 of the case 2 to the high pressure side A, and the inner peripheral surface of the cylindrical portion 8 of the outer case 2 A rubber layer 13 formed by intrusion when the seal portion 4 is formed is interposed between the outer pressure surface half portion 58 of the outer peripheral surface of the cylindrical portion 10 of the inner case 3 and the outer case 2.
  • Inner case 3 As a result, the rubber layer is securely and stably provided in the (fine) fitting gap G between the outer peripheral surface of the cylindrical portion 10 of the inner case 3 and the inner peripheral surface of the cylindrical portion 8 of the outer case 2.
  • the fluid that penetrates the rubber (gas) ) Has an advantage that internal leakage with a large transmission distance can be effectively prevented, and rubber covering formation by molding is easy.
  • the outer casing 2, the seal element 7, the inner case 3, and the seal portion 4 are integrated with each other by omitting the crimping process of the metal outer case 2.
  • the cylindrical portion 10 of the case 3 is higher than the high pressure side end surface 10a of the cylindrical portion 10 of the outer case 2.
  • the high pressure side end portion 70 of the cylindrical portion 8 of the outer case 2 is projected to the high pressure side A, and the outer peripheral surface of the cylindrical portion 10 of the inner case 3 is Between the outer case 2 and the low pressure side half 53 of the inner peripheral surface of the cylindrical portion 8 of the outer case 2 is interposed a rubber layer 13 formed by intrusion when the seal portion 4 is formed.
  • Inner case 3 thus, the rubber layer 13 can be surely infiltrated into the (fine) fitting gap G.
  • a metal outer case 2, a metal inner case 3, a rubber seal portion 4 having a rubber lip portion 5 slidably contacting the rotating shaft, and a seal element 7 slidably contacting the rotating shaft are provided.
  • the outer outer casing 2, the sealing element 7, the inner casing 3, and the sealing section 4 are formed by molding the sealing section 4 while omitting the crimping process of the metallic outer casing 2.
  • the outer case 2 has a substantially L-shaped cross section having a cylindrical portion 8 and a low pressure side inner flange portion 9, and the inner case 3 has a section having a cylindrical portion 10 and a low pressure side inner flange portion 11.
  • the seal element 7 is clamped and held by the inner flange portions 9 and 11 and the cylindrical portion 10 of the inner case 3 and the cylindrical portion 8 of the outer case 2 are low-pressure side half portions.
  • a configuration in which the outer case 2 and the inner case 3 are integrated by interposing a rubber layer 13 formed by intrusion when the sealing portion 4 is molded into the fitting gap portion G formed by 53. If this is the case, the inner case 3 can be fitted to the outer case 2 by the rubber pressure at the time of molding, and manufacturing is easy and the quality is stable.
  • the seal element 7 can be integrated while being securely held.
  • the metal outer case 2 and the metal inner case 3 are connected to each other in a small second space at the low-pressure side half 58 of the inner case 3.
  • the inner case 3 is fitted with a gap T and the high-pressure side half 59 of the inner case 3 is straight.
  • the rubber layer 13 having the second gap dimension T can be formed, and the amount of permeation leakage inside the rubber part (internal
  • the metal outer case 2 is fitted into the outer case 2 and the inner case 3 so that the high-pressure side half 59 of the outer peripheral surface of the metal inner case 3 is exposed.
  • the seal element 7 is attached in a crease shape, and is inserted into the mold cavity.Then, the fluidized rubber material is filled into the cavity, solidified, and the seal portion 4 is molded. If the outer case 2, the inner case 3 and the seal element 7 are integrated, the outer case 2 can be easily pressed, can be manufactured at low cost, and has a solid integrated structure. Is possible. Moreover, the amount of permeation leakage (internal leakage amount) inside the rubber part can be reduced.
  • the inner case 3 and the inner case 3 are fitted into the inner case 3 so that the high-pressure side half 52 of the inner peripheral surface of the outer case 2 is exposed.
  • the sealing element 7 is attached in the form of an adhesive and is inserted into the mold cavity, and then the fluidized rubber material is filled into the cavity and solidified, and the seal portion 4 is molded at the same time.
  • the manufacturing method is easy and inexpensive.
  • the inner case 3 is moved in the back direction (low pressure) by the rubber pressure during molding. It can be fitted to side B), making it easier to manufacture.
  • the entire structure can be firmly integrated, and the amount of permeation leakage (internal leakage) inside the rubber portion can be reduced.
  • FIG. 27 is an enlarged cross-sectional view of a main part showing the rotary shaft seal 1 of Embodiment 3
  • FIG. 28 is an explanatory view
  • FIG. 29 is a side view of the main part.
  • the rotary shaft seal 1 includes a metal outer case 2, a rubber seal portion 4 having a rubber lip portion 5 that is in sliding contact with the rotary shaft (not shown), and a screw groove 6 that is in sliding contact with the rotary shaft. And a sealing element 7 having
  • the metal outer case 2 is completely integrated by omitting the crimping process in the direction of arrow C as described in Figs. 39 and 40, and omitting the inner case 37. It is assembled as a structure.
  • the sealing part 4 is a force formed by molding (injection molding or compression molding).
  • the outer case 2, the seal element 7, and the sealing part 4 are integrally formed by the molding.
  • the outer case 2 has a cylindrical portion 8 and an inner flange portion 9 on the low pressure side B, and has a substantially L-shaped cross section.
  • the seal element 7 has an annular flat plate shape in a free state, and has a hole portion 26 at the center, and a screw groove 6 is formed from an inner peripheral edge of the hole portion 26.
  • a plurality of (four in FIG. 29) through-holes 28 are formed at an equal pitch along the vicinity of the outer peripheral edge 27. As shown in FIGS. 27 and 28, the through hole 28 is a portion corresponding to the inner flange portion 9 of the outer case 2.
  • the seal element 7 is fitted in the outer case 2 having a substantially L-shaped cross section, and is in contact with one surface of the inner flange portion 9 (on the high pressure side A).
  • a plurality of through holes 28 are formed so as to correspond to intermediate positions in the radial direction.
  • the seal part 4 has a U-packing cross section, and the shallow concave groove 18 is arranged so as to face the high-pressure side (fluid storage chamber side) A.
  • This U-packing type The cylindrical portion 8 of the outer case 2 is embedded from the low pressure side B in the vicinity of the outer peripheral surface 29 of the seal portion 4 in an integrated manner.
  • the contact inner peripheral edge (lip tip portion) 5a of the rubber lip portion 5 of the seal portion 4 is positioned on the axis-perpendicular plane P substantially the same as the high-pressure side end surface 8a of the cylindrical portion 8 of the outer case 2. Yes. That is, the contact inner peripheral end is on the axis orthogonal plane P that is substantially the same as the axis orthogonal plane that is orthogonal to the axis L (of the rotation axis) and is in contact with the high pressure side end surface 8a of the cylindrical portion 8.
  • An edge 5a is provided. Therefore, the overall width dimension W in the axial direction is significantly smaller than the conventional Fig. 39 to Fig. 41 etc.
  • the overall cross-sectional shape is a substantially rectangular shape.
  • the contact inner peripheral edge (lip tip) 5a of the rubber lip portion 5 of the seal portion 4 is substantially the same axis as the high pressure side end surface 8a of the cylindrical portion 8 of the outer case 2. It is also preferable to locate the lower pressure side B than the orthogonal plane P. In other words, it is in contact with the low-pressure side B, which is perpendicular to the axis orthogonal plane P, which is substantially the same as the axis orthogonal plane P that is perpendicular to the axis L (rotary axis) and is in contact with the high-pressure end face 8a of the cylindrical portion 8.
  • An inner peripheral edge 5a is provided. Therefore, the overall width dimension W in the axial direction is significantly smaller than the conventional Fig. 39 to Fig. 41 etc.
  • the overall cross-sectional shape is substantially rectangular as in FIG.
  • the small column portion 30 into which the fluid rubber material has entered (filled) and solidified into the above-described through hole 28 is a surface of the high-pressure side A of the inner flange portion 9 of the outer case 2 like a shell column.
  • the seal element 7 can be firmly integrated with the outer case 2 and the seal portion 4 by bonding. As a result, when used in a car air conditioner compressor, etc., even if the seal element 7 rotates with the rotating shaft due to frictional force, the seal element 7 is securely held and firmly integrated. The structure can be maintained.
  • FIG. 30 is a sectional view of the rotary shaft seal 1 of the first embodiment, and the same reference numerals indicate the same configuration.
  • an inner case 3 having a substantially L-shaped cross section having a convex portion is added.
  • the inner case 3 has a cylindrical portion 10 and an inner flange portion 11.
  • the cylindrical portion 10 is fitted into the cylindrical portion 8 of the outer case 2, and the convex portion 12 of the inner flange portion 11 presses the seal element 7.
  • the seal element 7 is held in a negative pressure state in cooperation with the inner flange portion 9 of the outer case 2.
  • the rotary shaft seal 1 of the first embodiment is also produced by omitting the caulking process in the direction of arrow C in FIGS. 39 and 40, and when the seal portion 4 is molded, the fitting gap between the cylindrical portions 8 and 10 is It is a structure in which all parts are integrated with a thin rubber layer 13 formed by solidifying the fluid rubber material that has entered the part G.
  • the seal part 4 is composed of HNBR alone or a compounded rubber material based on HNBR, or uses other rubber materials.
  • the original shape of the seal element 7 is an annular flat plate shape.
  • the seal element 7 is preferably a fluorine-based resin such as PTFE.
  • the seal element 7 has a partial force close to the outer diameter.
  • the flange 9 is attached and held on the low pressure side of the block-shaped main body 17 of the rubber seal 4 and the small column (shell-shaped) At 30, the unity is further strengthened. Since the screw groove 6 is formed in the seal element 7, the rotating shaft rotates to push the fluid back to the fluid storage chamber side (high pressure side) A (hydride port dynamic action), and it is rotating. Improves hermeticity.
  • the inner flange portion 32 of the conventional outer case 34 is disposed on the fluid storage chamber side (high pressure side) A Embodiment 3
  • the inner flange portion 9 of the outer case 2 is disposed on the low pressure side B.
  • the conventional inner case 37 is completely omitted from the rotary shaft seal 1 of the third embodiment.
  • the seal portion 4 includes an outer circumferential uneven corrugated fitting cylindrical wall portion 15 that covers the cylindrical portion 8 also with an outer peripheral surface side force, an end surface covering wall portion 16 that covers the high-pressure side end surface 8a of the cylindrical portion 8, and an outer A block-shaped main body portion 17 that occupies most of the low-pressure side B inside the case 2, and a connecting portion 42 connected to the high-pressure side A of the block-shaped main body portion 17 to the end face covering wall portion 16.
  • the rubber lip portion 5 extending in the oblique direction of the inner diameter is integrally formed to form a shallow U-shaped concave circumferential groove 18.
  • the position of the rubber lip portion 5 in the axial center direction and the position of the end surface covering wall portion 16 in the axial center direction are substantially matched. Further, the contact inner peripheral edge 5a of the rubber lip portion 5 that contacts the outer peripheral surface of the rotating shaft (not shown) is disposed at substantially the same position as the end surface 8a on the high pressure side A of the outer case 2 in the axial direction. In the case shown in FIG. 38, the axial direction position of the rubber lip portion 5 is arranged on the low pressure side B than the axial direction position of the end surface covering wall portion 16.
  • the contact inner peripheral edge 5a of the rubber lip portion 5 that contacts the outer peripheral surface of the rotating shaft is closer to the low pressure side B (in the axial direction) than the end surface 8a of the high pressure side A of the outer case 2. It is arranged in! / In this regard, when compared with FIGS. 39 to 41 of the conventional example, the rubber lip portion 5 hardly protrudes to the high pressure side A, and the overall width W of the rotary shaft seal 1 can be remarkably reduced.
  • the rotary shaft seal 1 of the third embodiment is compacted to a full width dimension W substantially the same as the full width dimension of the outer case 2.
  • the defect rate due to external factors can be significantly reduced during the manufacturing process of rotary shaft seals and during the assembly of car air conditioner compressors using such seals.
  • the rubber contact (adhesion) portion of the outer case 2 is preliminarily formed by shot peening or the like It is preferable to increase the rubber adhesion by increasing the surface roughness, and in particular, increase the surface roughness of the high-pressure side surface of the inner flange 9 to increase the adhesion to the tip surface of the small column 30. It is good to increase.
  • a plurality of through holes 28 are formed along the outer periphery of the seal element 7, and the cylindrical portion 8 and the low-pressure side inner flange portion 9
  • the seal element 7 is fitted into the outer flange 9 of the outer case 2 having a substantially L-shaped cross section and is inserted into the mold cavity (not shown), and then fluidized rubber. Fill the cavity by injection molding or compression molding and mold the seal part 4 at the same time with the rubber material filled in the above-mentioned through holes 28.
  • the high pressure side of the inner flange part 9 of the outer case 2 Adhere to one side and integrate the whole.
  • the outer case 2 and the seal element 7 can be integrally formed at the same time as the seal portion 4 is formed in the mold, and the conventional crimping process is completely omitted, and the number of components is minimized. I'll do it.
  • FIG. 31 and FIG. 32 show Modifications 1 and 2 of the rotating shaft seal 1 of Embodiment 3, respectively, which replace FIG. 29 described above. That is, the through hole 28 of the seal element 7 is illustrated as being circular in FIG. 29, but may be rectangular in FIG. 31, and in FIG. 32, the through hole 28 is arcuate (or fan-shaped). However, the shape of the through hole 28 can be variously modified in addition to this.
  • FIG. 33 and FIG. 34 show modified examples 3 and 4 of the rotary shaft seal 1 of Embodiment 3, respectively, and FIG. 38 uses the seal element 7 shown in FIG. 33 or FIG.
  • An example of a rotating shaft seal is shown. That is, in FIG. 33 or FIG. 34 and FIG. 38, the outer peripheral edge 21 corresponding to the corner portion 20 between the cylindrical portion 8 and the inner flange portion 9 of the seal element 7 force outer case 2 is substantially triangular.
  • the shape notch 22 (FIG. 33) or the substantially semicircular notch 22 (FIG. 34) is formed. In FIG. 33 or FIG. 34, each notch 22 is shown with a dotted pattern. Of course, the shape of the notch 22 You can change or increase or decrease the number.
  • the rubber force notch portion 22 of the seal portion 4 is filled by molding, and the rubber of the seal portion 4 becomes the corner portion 20. Also, the inner flange 9 is bonded and integrated (see FIG. 38).
  • FIG. 35 shows a fifth modification of the rotary shaft seal 1 of the third embodiment, and an example of the rotary shaft seal using this seal element 7 can be shown in common with FIG. That is, in FIG. 38 and FIG. 35, the wavy uneven portion 23 is formed on the outer peripheral edge 21 corresponding to the corner portion 20 between the cylindrical portion 8 and the inner flange portion 9 of the seal element 7 force outer case 2 in FIGS. ing.
  • the concave portions 23a of the concave and convex portions 23 are indicated by a dotted pattern.
  • Figure 35 shows an example of a rounded uneven wave shape for the uneven part 23, but it is also possible to make this an uneven triangular wave shape with a triangular shape, trapezoid or tooth shape, or a complex uneven pattern (not shown). ).
  • the rubber of the seal portion 4 is filled in the concave portion 23a of the concave and convex portion 23 by molding, so that the seal portion 4 The rubber is bonded and integrated to the inner surfaces of the corner 20 and the inner flange 9 (see FIG. 38).
  • Fig. 36 shows a modified example 6 of the rotary shaft seal 1 of the third embodiment, in which the outer peripheral edge 21 corresponding to the corner portion 20 of the cylindrical portion 8 and the inner flange portion 9 is the sealing element 7 Formed in a polygonal shape, the gap 25 between the polygonal side 24 and the circular inner surface 8c of the cylindrical part 8 is filled with the rubber force of the seal part 4 by the above-mentioned molding, and the inner flange part Bonded to 9 (corner 20) and integrated as a whole.
  • the seal element 7 has a circular outer peripheral edge 21 but is eccentric, and the rotary shaft is inserted.
  • the center point O of the outer peripheral edge 21 is eccentric with respect to the axial center L of the center hole 4 4, so the cylindrical inner surface 8c (of the outer case 2) indicated by the two-dot chain line and the seal element 7
  • the gap 25 with the outer peripheral edge 21 is formed in a crescent shape. When the gap 25 is filled with the rubber force of the seal part 4 by molding, the whole is integrated. At the same time, the rotation of the seal element 7 with the rotating shaft can be prevented.
  • FIGS. 33 to 35 and FIG. A notch 22 or an uneven portion 23 is formed on the outer peripheral edge 21 of 7.
  • the seal element 7 is fitted into the mold cavity so as to contact the inner flange 9 of the L-shaped outer case 2 having the cylindrical portion 8 and the low pressure side inner flange 9.
  • the fluidized rubber material is filled into the cavity, and the seal portion 4 is molded.
  • the outer case 2 is filled with the rubber material filled in the notch 22 or the recess 23a of the uneven portion 23.
  • the rotary shaft seal 1 (see Fig. 38) is manufactured by bonding to the inner flange 9 and integrating the whole.
  • FIG. 36 A method for manufacturing the rotary shaft seal 1 having the seal element 7 shown in Fig. 36 or 37 will be described.
  • the seal element is described. 7 is formed in a polygonal shape (see FIG. 36) having a plurality of sides 24, or is formed in an eccentric circular shape as shown in FIG. 37, and is similarly formed on the inner flange portion 9 of the outer case 2.
  • the seal element 7 is fitted into the mold so as to come into contact with the mold, and is inserted into the mold cavity.Then, the fluidized rubber material is filled into the cavity, and the seal section 4 is molded.
  • the design can be freely changed, and the through hole 28 shown in Fig. 29, Fig. 31 or Fig. 32 is provided.
  • the case of having the notch 22 shown in 34 is also preferable.
  • the case of having the through hole 28 shown in FIG. 29, FIG. 31 or FIG. 32 and the case of the eccentricity of FIG. 37 can be freely combined (used together).
  • a plurality of radial ribs are provided in the concave circumferential groove 18, and the contact inner peripheral edge 5a of the rubber lip 5 and the outer peripheral surface of the rotary shaft are arranged.
  • the contact surface pressure is changed in the rotational circumferential direction, making it easier for the lubricating fluid to enter between the inner peripheral edge 5a and the outer peripheral surface of the rotating shaft, reducing the generation of frictional heat and extending the service life. Is preferred.
  • the above-described screw groove 6 of the seal element 7 may be omitted or a concentric circle may be formed. Even so, it's free.
  • the rotary shaft seal 1 of Embodiment 3 includes the metal outer case 2, the rubber seal portion 4 having the rubber lip portion 5 that is in sliding contact with the rotary shaft, and the seal element that is in sliding contact with the rotary shaft.
  • the outer case 2, the seal element 7, and the seal portion 4 are integrally formed by molding the seal portion 4 while omitting the inner case fitted in the outer case 2. Because of the structure, it is possible to mass-produce high-quality products with the smallest number of parts at low cost and simplify the manufacturing equipment.
  • the outer case 2 has a substantially L-shaped cross section having a cylindrical portion 8 and a low-pressure side inner flange portion 9. Further, the seal element 7 has a through hole 28 at a portion corresponding to the inner flange portion 9. Since the rubber of the seal part 4 is filled in the through hole 28 and bonded to the inner flange part 9 by molding, it can be manufactured at a low cost with the smallest number of parts. It reliably prevents the element 7 from rotating with the rotating shaft (so-called co-rotation) and exhibits excellent sealing performance (sealability).
  • the outer case 2 has a substantially L-shaped cross section having a cylindrical portion 8 and a low pressure side inner flange portion 9. Further, the seal element 7 has a corner portion between the cylindrical portion 8 and the inner flange portion 9. A notch 22 or an uneven portion 23 is formed on the outer peripheral edge 21 corresponding to 20, and the rubber force of the seal portion 4 by the molding, the notch portion 22 or the recessed portion 23 of the uneven portion 23 3a And is bonded to the inner flange 9 so that it can be manufactured at a low cost with a small number of parts, reliably preventing the seal element 7 from rotating together, and having excellent sealing performance (sealability) ).
  • the outer case 2 has a substantially L-shaped cross section having a cylindrical portion 8 and a low pressure side inner flange portion 9, and the seal element 7 has a corner portion between the cylindrical portion 8 and the inner flange portion 9.
  • An outer peripheral edge 21 corresponding to 20 is formed in a polygonal shape, and the seal portion 4 is formed in the gap portion 25 between the side 24 of the polygonal shape and the circular inner surface 8c of the cylindrical portion 8 by the molding.
  • the rubber is filled and bonded to the inner flange 9 so that it can be manufactured at a low cost with a small number of parts, and the seal element 7 can be prevented from rotating together with the rotating shaft. Excellent sealing performance (sealability).
  • the rotary shaft seal 1 of Embodiment 3 includes the outer case 2 which is connected to the cylindrical portion 8 and the low pressure side. It has a substantially L-shaped cross section having a flange portion 9, and the seal portion 4 has a U packing shape in cross section, and the outer case 29 from the low pressure side B near the outer peripheral surface 29 of the seal portion 4 of the U packing shape.
  • 2 is an integral structure in which the cylindrical portion 8 is embedded in an insertion shape, and the contact inner peripheral edge 5a of the rubber lip portion 5 is located on the axial orthogonal plane P substantially the same as the high pressure side end surface 8a of the cylindrical portion 8.
  • the rubber lip 5 (contact inner peripheral edge 5a) is excessive on the outer peripheral surface of the rotating shaft. Contact with surface pressure can prevent premature wear, and overall width dimension W can be reduced.
  • the lip 5 prevents the lip 5 from being damaged or deformed.
  • the rubber lip 5 can be prevented from being damaged or deformed during the manufacturing process of the rotary shaft seal 1 or when the seal 1 is assembled to a compressor or the like, and the defect rate due to external factors is markedly increased. Can be reduced.
  • the rotary shaft seal of Embodiment 3 When the rotary shaft seal of Embodiment 3 is used in a compressor for a car air conditioner, it can exhibit excellent sealing performance (sealability) and durability even under severe usage conditions of high speed, high pressure and high temperature. It is preferable.
  • the through-hole 28 is formed along the outer periphery of the seal element 7, and the cross section is substantially L-shaped having the cylindrical portion 8 and the low-pressure side inner flange portion 9.
  • the sealing element 7 is fitted into the metal outer case 2 so as to be in contact with the inner flange portion 9 of the metal outer case 2 and is inserted into the mold cavity, and then the fluidized rubber material is placed inside the cavity.
  • the seal portion 4 is molded, and at the same time, the rubber material filled in the through hole 28 of the seal element 7 is adhered to the inner flange portion 9 of the outer case 2 to integrally seal the whole.
  • a metal outer case 2 having a substantially L-shaped cross section having a cylindrical portion 8 and a low pressure side inner flange portion 9 formed with a notch portion 22 or an uneven portion 23 on the outer peripheral edge 21 of the seal element 7.
  • the seal element 7 is fitted into the inner flange portion 9 so as to contact the inner flange portion 9, and is inserted into the mold cavity.
  • the fluidized rubber material is filled into the cavity, and the seal portion 4 is At the same time as molding, the rubber material filled in the notch 22 or the concave portion 23a of the concave and convex portion 23 is adhered to the inner flange portion 9 of the outer case 2 so that the whole is integrated.
  • the conventional caulking process (as shown by arrow C in Fig. 39 and Fig. 40) can be omitted, the manufacturing process can be simplified, and high-performance seals that can withstand harsh usage conditions can be produced in large quantities with stable quality. Production becomes possible.
  • the outer peripheral edge 21 of the seal element 7 is formed in a polygonal shape having a plurality of sides 24, and a metal outer case 2 having a substantially L-shaped cross section having a cylindrical portion 8 and a low-pressure side inner flange portion 9.
  • the sealing element 7 is fitted into the inner flange portion 9 so as to be in contact with the inner flange portion 9 and is inserted into the mold cavity, and then the fluidized rubber material is filled into the cavity to form the seal portion 4.
  • the rubber material filled in the gap portion 25 between the circular inner surface 8c of the cylindrical portion 8 and the side 24 of the outer peripheral edge 21 is adhered to the inner flange portion 9 of the outer case 2.
  • the manufacturing method integrates the whole, the conventional crimping process (as shown by arrow C in Fig. 39 and Fig. 40) can be omitted, the manufacturing process can be simplified, and it can withstand harsh usage conditions. High-performance seals can be mass-produced with stable quality It becomes ability. Industrial applicability
  • the present invention is useful for a rotary shaft seal and a method for manufacturing the rotary shaft seal, and particularly for a rotary shaft seal used for a compressor for a car air conditioner and the like and a method for manufacturing the rotary shaft seal.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

L'invention concerne un joint (1) pour un arbre tournant qui comporte une enveloppe métallique extérieure (2), une enveloppe métallique intérieure (3), une section de joint en caoutchouc (4) ayant une section de lèvre en caoutchouc (5), en contact à glissement avec un arbre tournant (29), et un élément de joint (7). Quand on moule la section de joint (4), l'enveloppe extérieure (2), l'élément de joint (7), l'enveloppe intérieure (3) et la section de joint (4) sont conformés en une structure monobloc.
PCT/JP2006/324746 2005-12-13 2006-12-12 Joint pour arbre tournant et procédé de production de celui-ci WO2007069597A1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2005358838A JP2007162801A (ja) 2005-12-13 2005-12-13 回転軸シール
JP2005358840A JP2007162803A (ja) 2005-12-13 2005-12-13 回転軸シールとその製法
JP2005358839A JP2007162802A (ja) 2005-12-13 2005-12-13 回転軸シールとその製法
JP2005-358838 2005-12-13
JP2005-358840 2005-12-13
JP2005-358839 2005-12-13
JP2006-050096 2006-02-27
JP2006050096A JP2007225087A (ja) 2006-02-27 2006-02-27 回転軸シールとその製法

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101952624A (zh) * 2008-02-20 2011-01-19 卡尔·弗罗伊登伯格公司 密封装置和其中的径向轴密封圈
EP3842671B1 (fr) * 2019-12-23 2024-05-15 KACO GmbH + Co. KG Joint d'étanchéité d'arbre, en particulier joint d'étanchéité d'arbre radial, pourvu d'au moins un élément d'étanchéité

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10159985A (ja) * 1996-11-26 1998-06-16 Koyo Seiko Co Ltd オイルシール

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10159985A (ja) * 1996-11-26 1998-06-16 Koyo Seiko Co Ltd オイルシール

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101952624A (zh) * 2008-02-20 2011-01-19 卡尔·弗罗伊登伯格公司 密封装置和其中的径向轴密封圈
CN101952624B (zh) * 2008-02-20 2014-10-08 卡尔·弗罗伊登伯格公司 密封装置和其中的径向轴密封圈
EP3842671B1 (fr) * 2019-12-23 2024-05-15 KACO GmbH + Co. KG Joint d'étanchéité d'arbre, en particulier joint d'étanchéité d'arbre radial, pourvu d'au moins un élément d'étanchéité

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