JP2009127738A - Rotary joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an improved rotary joint having sufficient seal life and cleanliness while suppressing enlargement and providing lubrication of a seal part even under harsh conditions of high speed rotation. <P>SOLUTION: The rotary joint includes a rotary shaft 3 attachable with a rotating member in an upper end and having a penetrating passage 3A, a support 1 rotatably supporting the rotary shaft 3 via a bearing 2 and equipped with a fluid passage 12 opened facing the penetrating passage 3A, and a seal mechanism S communicating the penetrating passage 3A and the fluid passage 12 in a shaft seal state. The seal mechanism S is composed by providing in a radial interior and a radial exterior, a pair of contact type mechanical seals si, so having rotary seal rings 6 equipped in an integrally rotating state on another end of the rotary shaft 3, and annular seal parts 25, 26 capable of relatively moving in an axis P direction in a shaft seal state on the support 1 and comprising static seal rings 9, 10 pressed and energized toward the rotary shaft 3. The rotary seal rings 6 of the inner and outer mechanical seals si, so are mutually formed as one. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rotary joint suitable for a shaft-sealed device that requires a high degree of cleanliness, such as a semiconductor bevel polishing apparatus, a semiconductor wafer polishing apparatus, a vacuum chuck part spindle, and a semiconductor cleaning apparatus.

  Conventionally, this type of rotary joint is configured to have a lip-type sealing device made of synthetic resin or the like, as shown in FIG. That is, a turntable (which is a rotating member and not shown) on which a wafer is placed on one end (upper end in FIG. 4) can be attached, and a rotating shaft 32 having a through channel 31 along the longitudinal axis P direction; The rotary shaft 32 is rotatably supported via a bearing 33 acting on a rotary flange portion 41 fitted on the rotary shaft 32, and is provided in the through flow passage 31 at the other end (lower end in FIG. 4) of the rotary shaft 32. The rotary joint B includes a support body 35 including a fluid passage 34 that opens oppositely, and a seal device 36 that connects the through passage 31 and the fluid passage 34 in a shaft-sealed state.

  The sealing device 36 includes a sealing shaft portion 32A formed at the lower end portion of the rotating shaft 32, and a pair of upper and lower annular sealing members 37 and 38 that are fitted to the support body 35 in a state of being press-fitted to the shaft portion. The lip portions 37a, 38a of the annular seal members 37, 38 are in sliding contact with the outer peripheral surface 32a of the sealing shaft portion 32A. With this sealing device 36, the through flow path 31 serving as a suction flow path by nitrogen gas or negative pressure and the fluid path 34 can be connected in a sealed state regardless of the rotation of the rotating shaft 32. Reference numeral 39 denotes an intermediate flange having an upper annular seal member 37 fitted therein and provided with a seal cleaning liquid supply port 40.

  Problems have arisen when the rotary joint having the lip-type sealing device as described above is applied to, for example, a bevel polishing device disclosed in Patent Document 1. A bevel polishing device is a device that polishes the beveled part (also called the edge part), which is the outer peripheral edge of a disk-shaped semiconductor wafer, and removes unnecessary insulating films and metal films that have been peeled off. It is useful to prevent dust generation during processing. Advantages of the lip seal structure include no metal contamination and a compact design.

  In recent years, the rotational speed of a bevel polishing apparatus has been increased along with a reduction in process time such as throughput time. However, in a sealing apparatus constituted by a lip seal made of synthetic resin or the like, a synthetic resin seal is provided due to sliding characteristics. As a result, the wear rate becomes extremely fast and the seal life (durability) is shortened, and the resulting wear powder is remarkably increased, resulting in a problem in terms of cleanliness.

  On the other hand, like the rotary joint disclosed in Patent Document 2, the rotary seal ring (42) fitted to one end of the rotary shaft is supported by the support body so as to be sealed and movable in the axial direction. There is also known one having a mechanical seal formed by press-contacting a stationary sealing ring (43). This has the advantage of being able to handle high pressures and high peripheral speeds (high rotational speeds) compared to a lip seal structure sealing device, and is flexible in terms of operating conditions. However, in order to do so, there is a problem that the double seal structure is adopted and the size is greatly increased.

As described above, the rotary joint has advantages and disadvantages in both the lip seal structure and the mechanical seal structure, and there is still room for further improvement in terms of functioning well even under severe conditions like a bevel polishing apparatus. It was.
JP 2007-5661 A Japanese Patent No. 2918874

  An object of the present invention is to provide an improved rotary joint that has sufficient seal life and cleanliness while allowing the seal portion to be lubricated while suppressing an increase in size even under severe conditions where higher speed rotation is required. It is in the point to get.

The invention according to claim 1 is capable of attaching a rotating member at one end and having a through shaft 3 </ b> A along the axis P direction, and rotatably supporting the rotating shaft 3 via a bearing 2. And the support body 1 provided with the fluid path 12 which opens facing the said through-flow path 3A in the other end of the said rotating shaft 3, and the said through-flow path 3A and the said fluid path 12 are connected in the shaft-sealed state. A rotary joint having a seal mechanism S for connection;
The seal mechanism S is capable of relative movement in the direction of the axis P in a shaft-sealed state with the rotary seal 3 mounted on the other end of the rotary shaft 3 in an integrally rotated state, and the Contact-type mechanical seals si and so having annular seal portions 25 and 26 composed of stationary sealing rings 9 and 10 that are pressed and biased toward the rotating shaft 3 are overlapped in the radial direction with respect to the shaft center P. A pair is provided, and the rotary sealing ring 6 of the mechanical seal si inside the diameter and the rotary sealing ring 6 of the mechanical seal so outside the diameter are integrally formed. It is.

  According to a second aspect of the present invention, there is provided the rotary joint according to the first aspect, wherein the cleaning liquid is supplied to and discharged from the space portions 1a, 1b between the annular seal portions 25, 26 of the mechanical seals si, so. The cleaning mechanism B is equipped.

  According to a third aspect of the present invention, in the rotary joint according to the second aspect, a radial path for communicating the inner and outer annular seal portions 25 and 26 with the space portions 1a and 1b is bypassed in the direction of the axis P. An annular weir 1k is provided.

  According to a fourth aspect of the present invention, in the rotary joint according to the second or third aspect, the opening 20a on the counter-rotating shaft side of the fluid path 12 is formed on a lateral side surface 1s of the support body 1 with respect to the axis P. In addition, the supply port 22a and the discharge port 23a of the cleaning liquid in the support body 1 have the same position in the axial center P direction as the opening 20a of the fluid path 12, and the radial direction with respect to the axial center P. Are formed on the lateral side surface 1s with different angles.

  According to the first aspect of the present invention, since the contact type mechanical seal is a double seal structure provided inside and outside in the radial direction, it can cope with higher speed rotation (high peripheral speed) and has a conventional single structure. By applying the double seal structure to the part that has been supported by the mechanical seal and applying quenching, it is possible to significantly reduce wear powder. In addition, the internal and external rotating seal rings of the mechanical seal are formed as a single unit, so the number of parts can be reduced and the cost can be reduced compared to the case where they are formed separately. Can be planned. As a result, it is possible to obtain a rotary joint improved so as to have sufficient seal life and cleanliness while allowing the seal portion to be lubricated while suppressing an increase in size even under severe conditions where higher speed rotation is required. it can.

  According to the second aspect of the present invention, the space between the inner and outer mechanical seals can be maintained in a clean state by the liquid cleaning mechanism, and the advantage of cleanliness can be obtained more stably.

  According to the third aspect of the present invention, the annular weir provided in the space between the inner and outer mechanical seals causes the cleaning liquid that has passed through either the inner or outer mechanical seal to detour in the axial direction toward the other mechanical seal. Therefore, the flow of the cleaning liquid can be promoted in both the inner and outer annular seal portions, and sufficient lubrication and cooling operations can be given to the respective annular seal portions, and the effect of further improving the reliability and durability can be obtained. .

  According to the invention of claim 4, the plurality of openings including the openings for supplying and discharging the cleaning liquid are arranged on the support body without changing the position in the axial center direction by changing the angle with respect to the axial center. Accordingly, it is possible to provide a rational rotary joint having a support body that can suppress an increase in size in the axial direction while forming a plurality of openings on the side peripheral surface.

  Embodiments of a rotary joint according to the present invention will be described below with reference to the drawings when applied to a bevel polishing apparatus or the like. 1 is a cross-sectional view of a rotary joint according to the first embodiment, FIG. 2 is an enlarged cross-sectional view of the main part of FIG. 1, FIG. 3 is a bottom view of the rotary joint of FIG. is there.

[Example 1]
As shown in FIG. 1, the rotary joint A according to the first embodiment has a bearing case (an example of a support body) 1 formed by fitting and connecting a lower case portion 1 </ b> A and an upper case portion 1 </ b> B with rolling bearings 2 and 2. The rotary shaft 3 is supported so as to be rotatable about the vertical axis P, and a circular plate 4 is bolted to the upper end of the rotary shaft 3 and extends between the lower portion of the rotary shaft 3 and the bearing case 1. The seal mechanism S is formed.

  A rotary sealing ring 6 is externally fitted to the lower end portion of the rotary shaft 3 so as not to move upward in a sealed state via an O-ring 5, and is externally fitted to the boss portion 6 a of the rotary sealing ring 6 so as to be integrally rotated. A drive flange 7 is loosely fitted to the rotary shaft 3 via a key 8 so as not to rotate relative to the rotary shaft 3. On the lower surface of the rotary seal ring 6, a first sliding surface 6A on the inner diameter side, a second sliding surface 6B on the outer diameter surface, and an annular recess that is recessed upward between the radial directions of both of them 6A, 6B. A portion 6b is formed. The first and second sliding surfaces 6A and 6B are formed on the same plane. A central hole 6 c that communicates with the central flow path 3 </ b> A of the rotary shaft 3 is formed in the rotary sealing ring 6.

  The lower case portion 1A is equipped with a first stationary sealing ring 9 that forms a pair with the first sliding surface 6A and a second stationary sealing ring 10 that forms a pair with the second sliding surface 6B. The first stationary sealing ring 9 is urged to lift the first stationary sealing ring 9 in a non-rotatable manner with the boss part 9A fitted in the flow path hole 12 of the lower case part 1A in a sealed state via the O-ring 11. It is comprised in the cylindrical member which has the center hole 9a while it consists of the flange part 9B and the 1st slidable contact ring 9C. The flange portion 9B is lifted and biased by a plurality of coil springs 13 dropped into the lower case portion 1A, and a laterally recessed portion 9b into which a pin 14 implanted in the lower case portion 1A enters is formed. An annular first sliding contact surface 15 which is an upper surface of the first sliding contact ring 9C formed integrally with the flange portion 9B is configured to contact the first sliding surface 6A in a pressed state.

  The second stationary sealing ring 10 urges the boss part 10A fitted in the outer housing portion 1b of the lower case part 1A in a sealed state via the O-ring 16 and the second stationary sealing ring 10 so as not to rotate. In addition to the flange portion 10B and the second sliding contact ring 10C, a large-diameter cylindrical member having a center hole 10a is formed. The flange portion 10B is lifted and biased by a plurality of coil springs 17 dropped into the lower case portion 1A, and a laterally recessed portion 10b into which a connecting bolt 18 that connects the upper and lower case portions 1A and 1B enters is formed. The annular second sliding contact surface 19 which is the upper surface of the second sliding contact ring 10C formed integrally with the flange portion 10B is configured to contact the second sliding surface 6B in a pressed state. .

  In other words, the inner sealing portion 1a formed by the lower case portion 1A and the rotary sealing ring 6 has a first sliding contact with the rotary sealing ring 6 having the first sliding surface 6A and the first sliding surface 6A. An inner seal portion si, which is a contact type mechanical seal provided with a first stationary sealing ring 9 having a surface 15, and an outer housing portion 1b formed by a lower case portion 1A, a rotary sealing ring 6, and an upper case portion 1B. A contact type mechanical seal provided with a rotary sealing ring 6 having a second sliding surface 6B and a first stationary sealing ring 9 having a second sliding contact surface 19 pressed against the second sliding surface 6B. A seal mechanism S having a double seal structure with the outer seal portion so is configured. That is, a pair of mechanical seals si and so are provided so as to overlap in the radial direction with respect to the axis P.

  As shown in FIGS. 1 and 3, the lower case portion 1 </ b> A has a main channel 20 that communicates with a flow channel hole 12 that is a fluid channel and opens sideways, and communicates with the channel hole 12 with a small diameter and opens sideways. The sub-flow path 21, the injection path 22, and the take-out path 23 are formed, and the upper case 1B is formed with a drain path 24 that communicates with the side of the drive flange 7 and that opens sideways. Yes. For example, a vacuum pipe (not shown) is connected to the opening 20 a of the main flow path 20, and a nitrogen gas pipe (not shown) is connected to the opening 21 a of the sub flow path 21. That is, the opening 20a on the counter-rotating shaft side of the flow path hole 12 is formed in the side peripheral surface 1s that is a lateral surface with respect to the shaft center P in the bearing case 1, and the opening that is a cleaning liquid supply port in the bearing case 1. 22a and the opening 23a, which is a discharge port, have the same position in the axial center P direction as the opening 20a of the flow path hole 12, and the side circumferential surface 1s has a different radial angle with respect to the axial center P. Is formed.

  An extraction pipe (both not shown) is connected to the opening 22 a of the injection path 22 and the opening 23 a of the extraction path 23, respectively, and an injection pipe for flowing a cleaning liquid such as fresh water through the seal mechanism S. That is, the liquid cleaning mechanism B is provided for supplying and discharging the cleaning liquid to and from the space portions 1a and 1b between the annular seal portions 25 and 26 of the inner and outer seal portions si and so.

  As shown in FIG. 1, it extends in the direction of the longitudinal axis P so as to separate the inner housing part 1a in which the first stationary sealing ring 9 is dropped and the outer housing part 1b in which the second stationary sealing ring 10 is dropped. An annular partition wall 1K is formed in the lower case portion 1A. A partition wall tip (an example of an annular weir) 1k, which is a tip of the annular partition 1K, extends beyond the first sliding surface 6A and the second sliding surface 6B that are formed in the same plane as each other, and the annular recess 6b. Is invading. That is, the partition tip 1k functions as an annular weir that bypasses the radial path that communicates the inner and outer annular seal portions 25 and 26 in the direction of the axis P.

  Accordingly, the fresh water supplied to the injection path 22 enters the inner accommodation portion 1a through the injection hole 22b having the same diameter as the coil spring 13 arrangement hole of the inner seal portion si, and the diameter of the outer seal portion so in the outer accommodation portion 1b. Although it flows into the extraction hole 23b through the inner part, fresh water circulates through a sufficiently high position by the presence of the partition wall tip 1k. That is, the fresh water that has entered the inner housing portion 1a surely flows in the vicinity of the inner annular seal portion 25, and once enters the outer housing portion 1b after passing through the annular recess portion 6b, and securely in the vicinity of the outer annular seal portion 26. As a result, the flow of clean water can be promoted in the inner and outer annular seal portions 25 and 26 to give each annular seal portion 25 and 26 a sufficient lubricating action and cooling action. In this configuration, the reliability and durability can be improved.

  The vacuum suction through the main channel 20 is for wafer chucking, and the nitrogen gas supply through the sub-channel 21 is for wafer release. The flow of fresh water through the injection path 22 and the extraction path 23 is for quench (described later), and the drain path 24 is for leakage recovery (detection) of the seal mechanism S (peripheral seal). By setting the vacuum suction to a position lower than the nitrogen gas supply hole, the particles generated in the seal mechanism S are effectively vacuum-sucked. Further, the exit (extraction hole 23b) of the quench is preferably provided above the annular seal portions 25 and 26 (seal surface), but the upper end is higher than the annular seal portions 25 and 26. By providing the tip portion 1k, a low-position outlet (extraction hole 23b) is realized while having a structure in which fresh water passes through the annular seal portions 25 and 26.

  Incidentally, the material example of the rotary sealing ring 6 is Sic, the material example of the first stationary sealing ring 6 is Sic, and the material example of the second stationary sealing ring 10 is carbon. Further, liquid contact (gas contact) members such as the first and second sliding surfaces 6A and 6B, the first sliding contact surface 15 and the second sliding contact surface 19 are PEEK, PTFE, SiC, CVD in addition to various metals. -You may produce by the metal material etc. which gave the coating of SiC, PEEK, or PTFE, PFA.

  The rotary joint according to the present invention has the following advantages. Since the inner and outer stationary sealing rings 6 and 10 are separate from each other, and the rotary sealing rings 6 of the inner and outer seal portions si and so have a double seal structure as the inner and outer integral parts. Compared with means for separately configuring the seal portions si and so, the radial dimension can be reduced while the pair of seal portions si and so are effectively functioning in the radial direction. Further, it is possible to design a high-speed rotation region (1500 rpm or more: 1.3 m / s or more at the nominal peripheral speed of the mechanical seal).

  In addition, the double seal structure can cope with higher speed rotation (high peripheral speed), and the double seal structure is applied to the part that was supported by the conventional single structure mechanical seal. To supply water, steam, or the like from the opposite side of the fluid to be sealed). In addition, the rotary sealing ring of the inner and outer mechanical seals is formed as a single unit, and compared with the case where they are formed separately, the number of parts can be reduced and the cost can be reduced. .

Sectional drawing which shows the structure of the rotary joint by Example 1. FIG. 1 is an enlarged sectional view showing the main part of FIG. Bottom view of the rotary joint of FIG. Sectional view showing a conventional rotary joint

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Support body 1a, 1b Space part 1k Annular weir 1s Side surface 2 Bearing 3 Rotating shaft 3A Through flow path 6 Rotating sealing ring 9, 10 Stationary sealing ring 12 Fluid path 20a Fluid path opening 22a Cleaning liquid supply port 23a Cleaning liquid supply Discharge port 25, 26 Annular seal B B Liquid cleaning mechanism P Shaft center S Seal mechanism si, so Contact type mechanical seal

Claims (4)

A rotary shaft that can be attached to one end and has a through passage along the axial center direction, and rotatably supports the rotary shaft via a bearing, and the penetrating portion at the other end of the rotary shaft A rotary joint comprising: a support body including a fluid path that opens to face the flow path; and a seal mechanism that connects the through flow path and the fluid path in a shaft-sealed state;
The seal mechanism is provided with a rotary sealing ring that is mounted on the other end of the rotary shaft in an integrally rotated state, and can be relatively moved in the axial direction in a shaft-sealed state with respect to the support body, and toward the rotary shaft. A pair of contact type mechanical seals having an annular seal portion composed of a stationary sealing ring that is pressed and biased are provided in a state of overlapping in the radial direction with respect to the shaft center, and rotation of the mechanical seal inside the diameter is performed. A rotary joint in which a sealing ring and a rotary sealing ring of the mechanical seal on the outer diameter side are integrally formed.   The rotary joint according to claim 1, wherein a liquid cleaning mechanism is provided for supplying and discharging a cleaning liquid to and from a space between the annular seal portions of each mechanical seal.   The rotary joint according to claim 2, wherein an annular weir is provided in the space portion to bypass a radial path for communicating the inner and outer annular seal portions in the axial direction.   An opening on the counter-rotating shaft side of the fluid path is formed on a lateral side surface of the support body with respect to the axis, and a supply port and a discharge port for the cleaning liquid in the support body are connected to the opening of the fluid path. The rotary joint according to claim 2 or 3, wherein the position in the axial direction is the same, and the radial angle with respect to the axial center is different from each other.

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