JP2006144902A - mechanical seal - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a mechanical seal having excellent follow-up capability to a stationary seal ring and capable of developing excellent sealing function. <P>SOLUTION: This mechanical seal 4 comprises a rotating seal ring 5 fixed to a rotating shaft and the stationary seal ring 7 fittedly held on the inner peripheral part of a metal seal case 6 through an O-ring 12 so as to be moved in the axial direction. A clearance between the seal case 6 and the stationary seal ring 7 is secondarily sealed while the seal ring 7 is allowed to move in the axial direction by engagedly holding the O-ring 12 on the outer peripheral surface part of the stationary seal ring 7 and pressingly bringing it into contact with the inner peripheral surface part of the seal case 6. A resin coating film 63 with a film thickness of 5 to 100 μm is formed on the inner peripheral surface part of the seal case 6 within a range where the O-ring 12 is relatively displaced following at least the axial movement of the stationary seal ring 7. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention includes a rotary seal ring fixed to the rotary shaft side, and a stationary seal ring held in a metal seal case through which the rotary shaft penetrates so as to be movable in the axial direction via an O-ring. The O-ring is engaged and held with the peripheral surface portion of the stationary seal ring and is brought into press contact with the peripheral surface portion of the seal case, thereby allowing the axial movement of the seal ring between the seal case and the stationary seal ring. The present invention relates to a mechanical seal configured to be secondarily sealed.

  As a conventional mechanical seal, a rotary seal ring fixed to a rotary shaft, a stationary seal ring held in a seal case through which the rotary shaft passes through a pair of O-rings so as to be movable in the axial direction, and a static seal ring And a spring that presses and urges the stationary sealing ring to the rotating sealing ring, and is sealed by the pair of O-rings between the sealing case and the stationary sealing ring. And a sealing gas passage that is a series of passages communicating with the seal case and the stationary sealing ring through the communication space and that opens between the sealing end faces that are the opposite end faces of the two sealing rings. In addition, a static pressure non-contact gas seal configured to maintain a non-contact state between the sealed end faces by introducing a seal gas having a predetermined pressure between the sealed end faces from the seal gas passage is well known. Some (for example, see Patent Document 1).

By the way, in such a static pressure type non-contact gas seal, it is preferable or necessary to keep the O-ring engaged with the peripheral surface portion of the stationary sealing ring in terms of sealing conditions and structure. There may not be.
WO99 / 27281 (FIG. 8)

  However, when the O-ring is engaged and held with the stationary seal ring, the O-ring slides in a state of being pressed against the peripheral surface portion of the seal case as the stationary seal ring moves in the axial direction. Occurs.

  That is, since the seal case is made of metal having excellent strength in terms of its function, the contact resistance with the O-ring is large, and the sliding with the stationary seal ring of the O-ring is not smoothly performed. As a result, the axial movement of the stationary sealing ring is not performed well, the followability of the stationary sealing ring is lowered, and a satisfactory sealing function cannot be exhibited. In particular, in the static pressure type non-contact gas seal as described above, when the supply of the seal gas is stopped, the stationary seal ring does not move smoothly in the direction of the rotary seal ring, and the static seal ring becomes a rotary seal ring. There is a risk of violent collision and damage or breakage of the sealed end face. Conversely, even if the supply of the sealing gas is stopped, if the stationary sealing ring does not move and there is a gap between the sealing end faces, the seal between the sealing end faces when the supply of the sealing gas is resumed. There is a possibility that the proper static pressure due to the gas is not generated and the sealing function is lost.

  Such a problem is configured to hold the end face contact type mechanical seal or the sealed end face in a non-contact state by generating dynamic pressure between the two seal rings so that the sealing function is exhibited by the relative rotational sliding contact. This also occurs in the non-contact type mechanical seal of the dynamic pressure type.

  An object of the present invention is to provide a mechanical seal that is excellent in followability of a stationary seal ring and that can exhibit a good sealing function without causing such problems.

  The present invention includes a rotary seal ring fixed to the rotary shaft side, and a stationary seal ring held in a metal seal case through which the rotary shaft penetrates so as to be movable in the axial direction via an O-ring. The O-ring is engaged and held with the peripheral surface portion of the stationary seal ring and is brought into press contact with the peripheral surface portion of the seal case, thereby allowing the axial movement of the seal ring between the seal case and the stationary seal ring. In a mechanical seal configured to be secondary-sealed, in order to achieve the above-mentioned object, in particular, a range in which the O-ring is relatively displaced on the peripheral surface portion of the seal case in accordance with at least the axial movement of the stationary seal ring. Then, it is proposed to form a resin coating film.

  In a preferred embodiment, such a mechanical seal is, for example, a communication space in which a pair of the O-rings are provided at a predetermined interval and sealed by a pair of O-rings between a seal case and a stationary sealing ring. The seal case and the stationary seal ring are formed with a series of passages communicating with each other through the communication space, and a seal gas passage opening between the seal end faces which are the opposite end faces of the seal rings is formed. It is proposed as a static pressure type non-contact gas seal configured to hold a seal gas between a sealed end face in a non-contact state by introducing a seal gas of a predetermined pressure from a gas passage between sealed end faces.

  If the fluid to be sealed should avoid mixing metal components (metal ions, etc.) or if there is a risk of metal corrosion, the fluid to be sealed should be a metal seal case. In order to prevent direct contact with the seal, a resin coating film may be formed on the peripheral surface portion of the seal case including the portion where the O-ring is relatively displaced at the portion where the fluid to be sealed contacts. preferable. In particular, in the above-described static pressure type non-contact gas seal, in order to prevent the generation of metal components due to the seal gas coming into contact with the seal case in addition to the fluid to be sealed, It is preferable to form a resin coating film on the inner peripheral part of the gas passage, including the part where the O-ring slides, at the part where the sealing gas and the fluid to be sealed contact.

  As a constituent material of the resin coating film, it is preferable to use a low friction plastic having a low contact resistance with the O-ring. Further, depending on the properties of the fluid to be sealed and the sealing conditions, the corrosion resistance, chemical resistance, etc. It is preferable to use one having excellent characteristics. In general, it is preferable to use a fluororesin such as polytetrafluoroethylene (PTEF) having excellent low friction and corrosion resistance. Moreover, it is preferable that the film thickness of a resin coating film is 5-100 micrometers, and it is optimal to set it as 20-40 micrometers. The surface of the resin coating film (at least the portion where the O-ring slides) is preferably machined into a smooth surface.

  ADVANTAGE OF THE INVENTION According to this invention, the relative displacement with respect to the seal case of O-ring accompanying the movement of a stationary sealing ring is performed smoothly, and the mechanical seal excellent in the followable | trackability of a stationary sealing ring can be provided. Therefore, in a mechanical seal such as a static pressure type non-contact gas seal, the sealing function is not impaired due to the follow-up failure of the stationary sealing ring, and a satisfactory sealing function can always be exhibited. Also, in the seal case, the part that comes into contact with the fluid to be sealed (including the part that comes into contact with the sealing gas in the case of a static pressure type non-contact gas seal), including the part that contacts the O-ring, is covered with a resin coating film. By doing so, it is possible to prevent the generation of metal ions due to the fluid to be sealed and / or the seal gas coming into contact with the metal seal case, and even under conditions where it is necessary to avoid the generation of metal ions. It is possible to exert a proper sealing function. In addition, by covering the seal case part that comes into contact with the sealed fluid with a resin coating film with excellent corrosion resistance and chemical resistance, even if the sealed fluid is corrosive, a metal seal The case is not corroded, and a good sealing function can be exhibited.

  FIG. 1 is a longitudinal front view showing an example of a processing apparatus equipped with a mechanical seal 4 according to the present invention, and FIG. 2 is an enlarged view of a main part thereof. In this processing apparatus, the driving unit 2 of the turntable 1 is covered with a cylindrical plastic cover 3, and a substrate such as a semiconductor wafer, a substrate of an electronic device, a liquid crystal substrate, a photomask, or a glass substrate is used as the turntable 1. When performing an appropriate process (cleaning process, chemical process, etc.) using the, a processing area A that is a sealed fluid area where the turntable 1 is disposed and an area in the plastic cover 3 that is an unsealed fluid area ( The cover area (atmosphere area) B is shielded and sealed by the sealing device 4 to keep the processing area A clean.

  The drive unit 2 is connected to the rotary table 2 and extends in the up-down direction, a bearing that rotatably supports the rotary shaft 2a, a drive unit for the rotary shaft 2a, and supports these in the cover inner region B. A support machine frame 2b is provided, and the rotary table 1 is driven to rotate. The turntable 1 is made of silicon carbide and has a rotating body shape such as a circular plate disposed horizontally in the processing region A. Further, as shown in FIG. 1, the plastic cover 3 has a cylindrical shape with an upper end opening formed integrally with a chemical-resistant plastic (in this example, PTFE is used), and is disposed on the lower surface side of the turntable 1. The drive unit 2 is covered. As shown in FIG. 1, an appropriate labyrinth seal 1a can be provided between the turntable 1 and the plastic cover 3 as required. By providing such a labyrinth seal 1a, a chemical solution or the like is supplied from the labyrinth seal 1a of the seal gas 10 to the processing region A, which will be described later, from the processing region A to the in-cover region B. Etc. can be effectively prevented.

  As shown in FIGS. 1 and 2, the mechanical seal 4 includes a rotary seal ring 5 fixed to the rotary table 1 concentrically with the rotary axis thereof, and a support machine frame 2b of the drive unit 2 disposed in the plastic cover 3. A pair of O-rings 12, 12 are formed on the inner peripheral portion 6 a of the seal case 6 in a state of being concentric with the cylindrical seal case 6 attached to the rotary seal ring 5 and directly opposed to the rotary seal ring 5. A stationary seal ring 7 held so as to be movable in the axial direction, and a spring member interposed between the seal case 6 and the stationary seal ring 7 to press and urge the stationary seal ring 7 to the rotary seal ring 5 8, an annular cover step 3a formed on the inner peripheral portion of the plastic cover 3 and abutting against the seal case end 6b, the plastic cover 3, the seal case 6 and the stationary seal ring 7 to penetrate both seal rings. The dense end faces of 5 and 7 A series of sealing gas passages 9 opened between the end surfaces 5a and 7a, and the sealing gas passages 9 are jetted from the sealing gas passages 9 to keep them in a non-contact state between the sealing end surfaces 5a and 7a. However, it is a static pressure type non-contact gas seal configured to shield and seal between the two regions A and B.

  As shown in FIGS. 1 and 2, the seal case 6 is made of metal (for example, SUS316 or the like) including a cylindrical sealing ring holding portion 61 and an annular spring holding portion 62 projecting inwardly from the lower end portion thereof. Stainless steel). The seal case 6 has a lower end portion (lower end portion of the sealing ring holding portion 61) 6a abutted against the cover step portion 3a and an outer peripheral portion (outer peripheral portion of the sealing ring holding portion 61) inside the upper end side of the plastic cover 3. It is attached to the support machine frame 2b via a spring holding part 62 in a state where it is brought into close contact with a peripheral part (inner peripheral part above the cover step part 3a) via an O-ring 11 made of fluoro rubber.

  The rotary seal ring 5 is an annular body formed of a material (for example, silicon carbide) harder than the constituent material (for example, carbon) of the stationary seal ring 7, and as shown in FIG. It is fixed to. The lower end surface of the rotary sealing ring 5 is a sealed end surface (hereinafter also referred to as “rotational side sealing end surface”) 5a which is a smooth annular surface.

  As shown in FIG. 1, the stationary sealing ring 7 is an annular body having a sealing end surface (hereinafter, also referred to as “stationary sealing end surface”) 7a that is a smooth annular surface, and a pair of fluorines arranged in parallel in the vertical direction. It is fitted and held on the inner peripheral portion 6a of the seal ring holding portion 61 of the seal case 6 via the rubber O-rings 12 and 12 so as to be movable in the axial direction (movable in the vertical direction). The outer diameter of the stationary side sealing end surface 7a is set slightly smaller than the outer diameter of the rotation side sealing end surface 5a, and the inner diameter of the stationary side sealing end surface 7a is set slightly larger than the inner diameter of the rotation side sealing end surface 5a. Each O-ring 12 is engaged and held in an annular O-ring groove 7 b formed in the outer peripheral portion of the stationary seal ring 7 in a state of being pressed against the inner peripheral portion 6 a of the seal case 6. A secondary seal is provided between the stationary seal ring 7 and the seal case 6 while allowing axial movement (up-down movement). Further, a circular hole 7c extending in the axial direction is formed at the lower end of the stationary seal ring 7, and a metal (for example, stainless steel such as SUS316) implanted in the spring holding part 62 of the seal case 6 in the circular hole 7c. By engaging the drive pin 13 (made of steel), the stationary seal ring 7 is allowed to move relative to the seal case 6 while allowing its axial movement in a predetermined range. The number of the circular holes 7c and the drive pins 13 that engage with the circular holes 7c is arbitrary, and a plurality of them are provided as necessary.

  As shown in FIG. 1, the spring member 8 is composed of a plurality of coil springs (only one is shown) interposed between the stationary seal ring 7 and the lower spring holding portion 62, and is stationary sealed. The ring 7 is pressed and urged to the rotary sealing ring 5 to generate a closing force that acts in the direction of closing the sealing end faces 5a and 7a.

  As shown in FIGS. 1 and 2, the seal gas passage 9 is formed in the cover side passage portion 91 formed in the plastic cover 3, the case side passage portion 92 formed in the seal case 6, and the stationary side sealing end surface 7a. The static pressure generating groove 93, the annular communication space 94 formed between the opposed peripheral surfaces of the stationary seal ring 7 and the seal case 6 and sealed by the O-rings 12 and 12, and the stationary seal ring 7 are passed through. And a sealing ring side passage portion 95 extending from the communication space 94 to the static pressure generating groove 93.

  As shown in FIG. 1, the cover-side passage portion 91 penetrates the plastic cover 3 in the vertical direction (the axial direction of the plastic cover 3), and its upper end (downstream end) is opened to the cover step 3a. The lower end (upstream end) is connected to an appropriate seal gas supply path (not shown).

  As shown in FIG. 1, the case side passage portion 92 penetrates the sealing ring holding portion 61 of the seal case 6 from the lower end portion thereof to the inner peripheral portion 6 a to connect the cover side passage portion 91 and the communication space 94. is doing. The downstream end of the case side passage portion 92 and the upstream end of the cover side passage portion 91 are sealed by a fluororubber O-ring 16 interposed between the cover step portion 3a and the seal case end portion 6b. In the state, it is connected in communication.

  The static pressure generating groove 93 is a shallow concave groove that is continuous or intermittently formed in a concentric ring shape with the stationary side sealing end surface 7a, and the latter is adopted in this example. That is, as shown in FIG. 3, the static pressure generating groove 93 is composed of a plurality of arc-shaped concave grooves 93a that are concentrically arranged in parallel with the stationary-side sealing end face 7a. The vertical width (interval between the O-rings 12, 12) of the communication space 94 is set according to the amount of axial movement (vertical movement) required to ensure the followability of the stationary seal ring 7. Even when the stationary seal ring 7 moves, the case side passage portion 92 and the communication space 94 are devised so as not to be disconnected. One end (upstream end) of the seal ring side passage portion 95 is opened on the outer peripheral surface of the stationary seal ring 7 (opened in the communication space 94) between the O ring grooves 7b and 7b, and the other end. The portion (downstream end) is branched into a plurality of branch portions 95a, and each branch portion 95a is opened to each arc-shaped concave groove 93a constituting the static pressure generating groove 93 as shown in FIG. An appropriate restrictor 96 (orifice, capillary tube, porous member, etc.) is provided at an appropriate position of the seal gas passage 9 (for example, an appropriate position of the sealed ring side passage 95 and upstream of the branch portion 95a). Even if the gap between the sealing end faces 5a and 7a fluctuates, the gap is automatically adjusted so that the gap is properly maintained. That is, when the clearance between the sealed end surfaces 5a and 7a becomes large due to vibration of the rotary device (rotary table 1), the amount of seal gas flowing out from the static pressure generating groove 93 between the sealed end surfaces 5a and 7a and the restrictor 96 are reduced. The amount of seal gas supplied to the static pressure generating groove 93 through the imbalance is imbalanced, the pressure in the static pressure generating groove 93 is reduced, and the opening force by the seal gas 10 is smaller than the closing force by the spring member 8. The gap between the sealing end faces 5a and 7a is changed to be small, and the gap is adjusted to an appropriate one. On the contrary, when the gap between the sealing end faces 5a and 7a becomes small, the pressure in the static pressure generating groove 93 rises by the throttle function by the throttle 96 similar to the above, and the opening force is larger than the closing force. Thus, the gap between the sealing end faces 5a and 7a is changed so as to increase, and the gap is adjusted to an appropriate one.

  In the static pressure generating groove 93, a clean seal gas 10 having a pressure higher than that of both the regions A and B and containing no particles is contained in the seal gas passage 9 (the cover side passage portion 91, the case side passage portion 92, the communication space 94, and the sealing ring). From the side passage portion 95). As the sealing gas 10, a gas that does not have any adverse effect even if it flows into the regions A and B is appropriately selected according to the sealing conditions. In this example, clean nitrogen gas that is inert to various substances and harmless to the human body is used. The seal gas 10 is generally supplied during operation of the rotary table 1 (during driving of the rotary shaft 2a), and the supply is stopped after the operation is stopped. The operation of the rotary table 1 is started after the supply of the seal gas 10 is started and after the sealed end surfaces 5a and 7a are maintained in a proper non-contact state, and the supply of the seal gas 10 is stopped. This is performed after the operation of the rotary table is stopped and after the rotary shaft 2a is completely stopped. It should be noted that the supply of the seal gas 10 can be continuously performed as necessary, regardless of whether or not the turntable 1 is operated.

  When the sealing gas 10 is supplied to the static pressure generating groove 93, the sealing gas 10 introduced into the static pressure generating groove 93 generates an opening force that acts in the direction of opening the sealing end surfaces 5a and 7a. This opening force is due to the static pressure generated by the seal gas 10 introduced between the sealed end faces 5a and 7a. Therefore, the sealing end surfaces 5a and 7a are held in a non-contact state in which the opening force and the closing force (spring load) by the spring member 8 acting in the direction of closing the sealing end surfaces 5a and 7a are balanced. That is, the seal gas 10 introduced into the static pressure generating groove 93 forms a static pressure fluid film between the sealed end surfaces 5a and 7a. Due to the presence of this fluid film, the outer peripheral side region (processing region) of the sealed end surfaces 5a and 7a is formed. ) Between A and the inner peripheral side region (cover inner region) B is shield-sealed. The pressure of the sealing gas 10 and the spring force (spring load) of the spring member 8 are appropriately set according to the sealing conditions so that the gap between the sealed end faces 5a and 7a is appropriate (generally 5 to 15 μm). Is done.

  By the way, the stationary seal ring 7 moves in the axial direction by supplying and stopping the seal gas 10 and adjusting the gap by the throttle 96, and the proper sealing function is exhibited by performing the movement smoothly and smoothly. Is done. Thus, the followability of the stationary seal ring 7 is such that the O-rings 12 and 12 engaged and held by the stationary seal ring 7 smoothly displace (slide) the inner peripheral surface 6a of the seal case 6. However, the seal case 6 is made of metal and has a large friction coefficient between the inner peripheral surface 6a and the O-rings 12 and 12 made of fluorine rubber or the like, and the O-rings 12 and 12 Are loaded in a compressed state between the seal case 6 and the stationary seal ring 7 so as to exert a secondary seal function, and the O-rings 12 and 12 are pressed against the inner peripheral surface 6a of the seal case 6. For this reason, the displacement (sliding) of the O-rings 12 and 12 accompanying the movement of the stationary seal ring 7 is difficult to perform smoothly, and the followability of the stationary seal ring 7 may be reduced.

  Therefore, in the mechanical seal 4 of the present invention, as shown in FIG. 2, a low-friction resin coating film 63 is formed on the inner peripheral surface 6a of the seal ring holding portion 61 which is a seal case portion on which the O-rings 12 and 12 slide. It is formed so that the O-rings 12 and 12 can be smoothly slid and the followability of the stationary seal ring 7 is improved.

  Further, in this example, the resin coating film 63 is formed not only on the seal case portion 6a where the O-rings 12 and 12 contact and slide but also on the seal case portion where the sealed fluid and the seal gas 10 contact. That is, as shown in FIG. 2, a series of resin coating films 63 are formed on the outer surface portion of the sealing ring holding portion 61 and the inner surface portion of the sealing ring side passage portion 92 of the seal case 6 so as to seal the fluid to be sealed and the sealing gas. 10 is devised so as not to contact the metal part of the seal case 6 directly. By doing in this way, generation | occurrence | production of the metal ion by the to-be-sealed fluid and the sealing gas 10 contacting the metal sealing case 6 is prevented, and the process in the process area A may become defective by a metal ion. Can be prevented. Among the components of the processing apparatus and the mechanical seal 4 equipped in the processing apparatus, all of the members that contact the fluid to be sealed and the seal gas 10 except the seal case 7 do not generate metal ions. Or coated with a non-metallic material. That is, the rotary seal ring 5 is made of silicon carbide, the stationary seal ring 7 is made of carbon, and the O-rings 11, 12, 16 are made of fluororubber. Further, the turntable 1 and the cover 3 are also made of a non-metallic material such as PTFE, or the portion facing the region to be processed A and the portion contacting the seal gas 10 are resin-coated with PTFE or the like. is there. On the other hand, all of the spring member 8 and the drive pin 13 made of metal are disposed in the in-cover region B. Therefore, even when the object to be processed does not like metal ions such as a semiconductor wafer, the processing can be performed satisfactorily.

  By the way, as a constituent material of the resin coating film 63, it is preferable to use a low friction plastic such as a fluororesin having a small coefficient of friction with the O-ring 12, and in this example, PTFE is used.

  The thickness of the resin coating film 63 is preferably 5 to 100 μm, and most preferably 20 to 40 μm. By setting such a film thickness, a uniform film thickness can be obtained without variations in the film thickness, and variations in contact resistance with the O-rings 12 and 12 can be avoided, and the followability of the stationary seal ring 7 can be avoided. Can be greatly improved. Furthermore, it is preferable that the surface of the resin coating film 63, particularly the surface of the portion 63a with which the O-rings 12 and 12 are in contact, be machined into a highly accurate smooth surface.

  By the way, the mechanical seal 4 is devised so that the gas flow from the cover side passage portion 91 to the case side passage portion 92 is performed in the axial direction of the plastic cover 3. The plastic cover 3 is not deformed in the radial direction by the pressure of the seal gas 10 regardless of the wall thickness (in the radial direction). Therefore, the material and shape (thickness) of the plastic cover 3 can be freely set according to the use conditions of the processing apparatus without considering the strength against the pressure of the seal gas 10. Even when the labyrinth seal 1a as described above is provided between the cover 3 and the turntable 1, the plastic cover 3 is not deformed, so that the function of the labyrinth seal 1a is not impaired.

  The configuration of the present invention is not limited to the above-described embodiment, and can be appropriately improved and changed without departing from the basic principle of the present invention.

  The present invention can also be applied to an end surface contact type mechanical seal in which both sealing rings are in relative rotational sliding contact. However, according to the present invention, a non-contact type mechanical seal in which followability of a stationary seal ring is important (such as the above-described static pressure type non-contact gas seal or a dynamic pressure generating groove formed on one sealed end surface to form a gap between the sealed end surfaces is described. It can be more suitably applied to a dynamic pressure type non-contact type mechanical seal configured to be held in a non-contact state by the generated dynamic pressure.

  Further, the above-described mechanical seal is configured as a static pressure type non-contact gas seal 4 that holds the sealed end faces 5a and 7a in a non-contact state only by a static pressure by the seal gas 10, but as shown in FIG. It is also possible to configure the composite endless gas seal 104 to hold the sealed end faces 5a and 7a in a non-contact state by generating a dynamic pressure in addition to a static pressure during this time, and to apply the present invention. It is. In such a composite non-contact gas seal, whether the followability of the stationary seal ring 7 is a more important factor for the sealing function.

  That is, in the composite non-contact gas seal 104 shown in FIG. 4, the dynamic pressure generating groove 19 is formed on the sealing end surface (rotation side sealing end surface) 5a of the rotary sealing ring 5 which is one sealing end surface. The dynamic pressure generating groove 19 is configured to generate a dynamic pressure between the sealed end faces 5a and 7a. The shape of the dynamic pressure generating groove 19 can be appropriately set according to the sealing conditions and the like. In this example, the dynamic pressure generating groove 19 is formed on the rotation-side sealing end surface 5a as shown in FIG. 6 or FIG. The first groove portion 20a that extends from the portion facing the static pressure generating groove 93 in the outer diameter direction and in the direction opposite to the rotation direction (a direction) of the rotary seal ring 5 and the inner diameter direction and the rotary seal ring 5 A plurality of grooves 20 composed of second groove portions 20b extending in a slanting direction in the direction opposite to the rotation direction (a direction) are configured in parallel with the circumferential direction of the sealed end surface 5a. Each groove 20 is a groove having a shallow depth of 1 to 10 μm, and has an outermost diameter side end portion (an outer diameter side end portion of the first groove portion 20a) and an innermost diameter side end portion (the second groove portion 20b). The inner diameter side end portion) is located in the overlapping region of both sealed end faces 5a and 7a. That is, as shown in FIG. 5, the inner and outer diameters E and F of the dynamic pressure generating groove 19 are the outer diameter of the sealing end surface (stationary sealing end surface) 7a of the stationary sealing ring 7 (≦ the outer diameter of the rotating sealing end surface 5a) A. And B <F <A, D <E <C with respect to the inner diameter (≧ the inner diameter of the rotation-side sealing end surface 5a) D and the outer diameter B and the inner diameter C of the static pressure generating groove 93 (arc-shaped concave groove 93a). It is set appropriately within the range having the relationship. In this example, the condition of 0.5 ≦ (F−B) / (A−B) ≦ 0.9 or 0.5 ≦ (C−E) / (C−BD) ≦ 0.9 is satisfied. Is set. As shown in FIG. 6, each groove 20 has a substantially square shape in which the first groove portion 20a and the second groove portion 20b coincide with each other at the base end portion, or as shown in FIG. The base end portions of the portion 20a and the second groove portion 20b have a zigzag shape that folds in the circumferential direction. The other configuration of the composite non-contact gas seal 104 is the same as that of the static pressure non-contact gas seal 4 shown in FIGS.

  According to such a composite non-contact gas seal 104, dynamic pressure is generated by the dynamic pressure generating groove 19 in addition to the static pressure by the seal gas 10 between the sealed end faces 5a and 7a. The sealed end faces 5a and 7a are kept in a non-contact state. Therefore, even when a situation occurs in which the sealed end faces 5a and 7a cannot be held in an appropriate non-contact state depending on the static pressure generated by the seal gas 10, the proper non-contact state can be maintained by the dynamic pressure. Further, the required supply amount of the seal gas 10 can be reduced by the static pressure by the seal gas 10 as compared with the static pressure type non-contact gas seal that is maintained in a non-contact state only by the static pressure. Further, since the dynamic pressure generating groove 19 is not opened outside the overlapping region of the sealed end surfaces 5a and 7a, the innermost diameter side end and the outermost diameter side end of each groove 20 are introduced between the sealed end surfaces 5a and 7a. In addition to functioning as a weir for the sealed gas 10, the leakage gap formed between the sealed end faces 5 a and 7 a is reduced. As a result, the amount of leakage of the sealing gas 10 introduced between the sealing end faces 5a and 7a to the processing region (sealed gas region) A side is suppressed, and the trapping characteristic of the sealing gas 10 by the dynamic pressure generating groove 19 is extremely good. It becomes something. Therefore, the consumption of the sealing gas 10 can be reduced, and even if there are particles accompanying the sealing gas 10, the intrusion can be suppressed as much as possible. Depending on the configuration of the processing apparatus equipped with the composite non-contact gas seal 104, usage conditions, etc., the rotary table 1 or the rotary shaft 2a may be rotated in both directions instead of in one direction. The dynamic pressure generating groove 19 may be shaped so that dynamic pressure can be generated even if the rotary seal ring 5 rotates in either the forward direction or the reverse direction. The shape of the dynamic pressure generating groove 19 can be arbitrarily set according to the sealing conditions and the like, and various shapes have been proposed conventionally. For example, a dynamic pressure generating groove unit composed of a first dynamic pressure generating groove and a second dynamic pressure generating groove, which are arranged in the radial direction and symmetrical with respect to the diameter line on the rotation-side sealing end surface 5a, is predetermined in the circumferential direction. A plurality of sets are formed in parallel at intervals, and when the rotary seal ring 5 rotates in the forward direction, dynamic pressure is generated by the first dynamic pressure generating groove, and the rotary seal ring 5 rotates in the reverse direction. In some cases, the dynamic pressure is generated by the second dynamic pressure generating groove. As each of the first and second dynamic pressure generating grooves, for example, an L-shaped groove having a constant groove depth and groove width can be employed.

  In addition, the resin coating film 63 is a contact portion of the O-ring 12 in the seal case 6 under the sealing conditions that do not need to suppress the generation of metal ions, and the O-ring 12 moves with the movement of the stationary seal ring 7. Therefore, it may be formed only in the portion 6a that is relatively displaced (sliding). Further, the material of the resin coating film 63 is appropriately selected according to the properties of the sealed fluid and the sealing conditions on condition that the contact resistance with the O-ring 12 is reduced. For example, when there is a possibility that the sealed fluid may corrode the sealing case 6, a resin coating film 63 made of a material having corrosion resistance and chemical resistance is formed at the contact portion of the sealing case 6 with the sealed fluid. . In this case, a mechanical seal constituent member other than the seal case 6 or a part thereof, or a member or part that contacts the fluid to be sealed, is made of a material having corrosion resistance and chemical resistance or is coated with such a material. . In this way, even when the fluid to be sealed is corrosive, a good sealing function can be exhibited.

It is a vertical front view which shows an example of the mechanical seal which concerns on this invention. It is an enlarged view of the principal part of FIG. It is a top view of the stationary sealing ring in the said seal. It is a vertical front view equivalent to FIG. 2 which shows the modification of the mechanical seal which concerns on this invention. It is an enlarged view of the principal part of FIG. FIG. 5 is a half-top view of a rotary seal ring showing an example of a dynamic pressure generating groove. FIG. 6 is a half-top view of a rotary seal ring showing a modification of the dynamic pressure generating groove.

Explanation of symbols

2a Rotating shaft 4 Mechanical seal (static pressure non-contact gas seal)
DESCRIPTION OF SYMBOLS 5 Rotating sealing ring 5a Sealing end surface of rotating sealing ring 6 Seal case 6a Inner peripheral surface of seal case 7 Stationary sealing ring 7a Sealing end surface of stationary sealing ring 7b O-ring groove 8 Spring member 9 Seal gas passage 10 Seal gas 12 O-ring 61 Seal ring holding part 63 Resin coating film 92 Case side passage part 93 Static pressure generating groove 94 Communication space 95 Seal ring side passage part

Claims (7)

A rotary seal ring fixed to the rotary shaft side, and a stationary seal ring held in a metal seal case through which the rotary shaft penetrates so as to be movable in the axial direction via the O-ring. Is engaged with and held in contact with the peripheral surface portion of the stationary seal ring and pressed against the peripheral surface portion of the seal case, so that the seal case and the stationary seal ring are secondarily sealed while allowing the axial movement of the seal ring. In a mechanical seal configured to
A mechanical seal characterized in that a resin coating film is formed on a peripheral surface portion of a seal case at least in a range in which the O-ring is relatively displaced as the stationary seal ring moves in the axial direction. A pair of the O-rings are provided at a predetermined interval to form a communication space sealed by the pair of O-rings between the seal case and the stationary sealing ring, and the communication space is provided in the sealing case and the stationary sealing ring. Forming a seal gas passage that opens between the seal end faces that are opposite end faces of both seal rings, and introduces a seal gas having a predetermined pressure between the seal end faces. 2. The mechanical seal according to claim 1, wherein the mechanical seal is a hydrostatic non-contact gas seal configured to hold a space between sealed end faces in a non-contact state. The mechanical coating according to claim 1, wherein a resin coating film is formed on a portion of the peripheral surface portion of the seal case where the fluid to be sealed comes into contact, including a portion where the O-ring is relatively displaced. sticker. A resin coating film is formed on the peripheral surface portion of the seal case and the inner peripheral portion of the seal gas passage, including the portion where the O-ring slides, at the portion where the seal gas and the fluid to be sealed contact. The mechanical seal according to claim 2. 5. The mechanical seal according to claim 1, wherein the resin coating film has a thickness of 5 to 100 μm. 6. The mechanical seal according to claim 5, wherein the resin coating film has a thickness of 20 to 40 [mu] m. The surface of the resin coating film, at least a portion where the O-ring slides is machined into a smooth surface, wherein the surface is a smooth surface. Item 7. The mechanical seal according to item 5 or item 6.

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