WO2014069098A1 - メカニカルシール装置 - Google Patents
メカニカルシール装置 Download PDFInfo
- Publication number
- WO2014069098A1 WO2014069098A1 PCT/JP2013/073824 JP2013073824W WO2014069098A1 WO 2014069098 A1 WO2014069098 A1 WO 2014069098A1 JP 2013073824 W JP2013073824 W JP 2013073824W WO 2014069098 A1 WO2014069098 A1 WO 2014069098A1
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- WIPO (PCT)
- Prior art keywords
- seal
- sealing
- ring
- fixing
- rotation
- Prior art date
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- 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
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
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- 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
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3464—Mounting of the seal
- F16J15/348—Pre-assembled seals, e.g. cartridge seals
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- 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
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
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- 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
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3496—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member use of special materials
Definitions
- the present invention relates to a mechanical seal device.
- Patent Document 1 discloses a mechanical seal having a radial end face width of 0.2 to 1.0 mm as shown in FIGS.
- Patent Document 1 since the sealing is performed by increasing the contact pressure by reducing the radial width of the sealing end face, there is a problem in that the seal face is severely worn and the seal sliding face is damaged. there were.
- An object of the present invention is to provide a mechanical seal capable of significantly reducing sliding heat generation while suppressing sealing wear while having sealing performance.
- the mechanical seal comprises: A mechanical seal device that seals the fluid inside the machine at the gap between the stuffing box and the rotating shaft, A seal cover attached to the stuffing box; A fixing seal ring attached to the seal cover and having a first seal surface; A rotary seal ring having a second seal surface attached to the rotary shaft and slidable on the first seal surface; A collar that rotates integrally with the rotating shaft; Either the sealing surface of the sealing ring for fixing or the sealing ring for rotation is formed so that the surface width in the radial direction is narrower than the other sealing surface, A gap is formed between a back surface of the rotation seal ring facing the second seal surface and the collar, and the rotation seal ring is elastically held in the axial direction of the rotation shaft and the collar. It is characterized by rotating in unison.
- the seal surface with a narrow surface width is low in rigidity, so that the seal surface is easily deformed. For this reason, when the sealing ring for rotation rotates, the sealing surface with a narrow surface width follows the opposing sealing surface flexibly. As a result, appropriate undulation occurs on the sliding surface, and a fluid lubricating film can be suitably formed on the sliding surface.
- the rotary seal ring is held elastically in the axial direction of the rotary shaft and rotates integrally with the collar. For this reason, since the vibration etc. at the time of the rotation sealing ring rotating can be absorbed, the wave
- the surface width of the sealing surface is narrow, the temperature difference between the sealing surface between the machine inside where there is a sealing fluid and the machine outside where there is no sealing fluid is reduced by sandwiching the sealing surface with a narrow surface width. Can do. As a result, it is possible to reduce the amount of deformation of the sealing surface due to heat between the machine inside and the machine outside.
- a groove for accommodating an elastic member and a spacer is formed on the inner periphery of the collar of the rotation sealing ring, and the spacer contacts the collar, and the back surface of the rotation sealing ring A gap is formed between the collar.
- the sealing surface formed so that the radial surface width is narrower than that of the other sealing surface is formed in a nose portion having a rectangular cross-sectional shape.
- the mechanical seal device having such a configuration, since the nose portion is rectangular, even if the sliding surface is worn, it is possible to keep the appropriate contact pressure without changing the surface width of the seal surface. Become.
- the surface width of the seal surface formed so that the surface width in the radial direction is narrower than that of the other seal surface is 1.1 to 2.0 mm.
- the balance ratio of the fixing seal ring is 0.8 to 1.20.
- the pressing force corresponding to the pressure of the internal fluid acts on the sealing ring for fixing. For this reason, since a contact pressure corresponding to the pressure of the internal fluid is generated on the sliding surface, an appropriate swell is generated corresponding to the pressure of the internal fluid. Therefore, a fluid lubrication film suitable for the sliding surface can be formed.
- the inner diameter ratio of the sealing ring for fixing is formed to be 1.09 to 1.30.
- the mechanical seal device having such a configuration, a relatively large gap is formed between the outer peripheral surface of the rotary shaft on the inner peripheral surface side of the fixing seal ring. As a result, the sealed fluid can be efficiently circulated toward the sliding surface, so that sliding heat generation can be efficiently removed.
- the inner circumferential surface of the fixing sealing ring is formed in a tapered shape so as to be inclined toward the outer circumferential side toward the first seal surface.
- the sealed fluid can be efficiently circulated toward the sliding surface, so that sliding heat generation can be efficiently removed.
- the mechanical seal device has a sealed fluid on a side close to the rotating shaft with respect to a sealing surface formed by sliding the sealing ring for rotation and the sealing ring for fixing. It is an outside type.
- At least one of the fixing seal ring and the rotation seal ring is made of SiC.
- FIG. 1 is a cross-sectional view of a mechanical seal device according to an embodiment of the present invention.
- FIG. 2 is a partially enlarged view of the cross-sectional view shown in FIG.
- FIG. 3 is a front view of the rotary seal ring shown in FIGS. 1 and 2.
- FIG. 4 is a graph showing the relationship between the sliding surface width and the specific wear amount.
- a mechanical seal device 1 is a seal device mounted on a general industrial pump or the like. As shown in FIGS. 1 and 2, the mechanical seal device 1 is configured as an outside type in which a sealed fluid exists on the side close to the rotation shaft with respect to the sealing surface, and includes the rotation shaft 70 and the stuffing box 80. The fluid on the machine interior A side is sealed with a gap between 1 and 2, the shaft hole 81 side (left side in the figure) of the stuffing box 80 is the machine interior A, and the opposite side in the axial direction (right side in the figure) is the machine exterior B.
- the mechanical seal device 1 of the present embodiment is preferably used in a use environment where the pressure of the sealed fluid is 1 MPa or less, but is not limited to this, and can be used in a pressure environment greater than 2 MPa.
- a shaft hole 81 is formed in the stuffing box 80, and a rotation shaft 70 rotatably supported by a bearing (not shown) passes through the shaft hole 81.
- the mechanical seal device 1 is attached to the outer surface 82 around the shaft hole 81 of the stuffing box 80 via the gasket 60. That is, the mechanical seal device 1 is attached to the stuffing box 80 by passing the installation groove (not shown) of the seal cover 10 through the embedded bolt 83 installed on the outer surface 82 of the stuffing box 80 and tightening the nut 84. It is attached.
- the gasket 60 is made of resin or metal, and prevents the sealed fluid in the machine interior space A from leaking between the seal cover 10 and the stuffing box 80.
- the mechanical seal device 1 has a seal cover 10, a sealing ring 40 for fixing, a sealing ring 30 for rotation, and a collar 20.
- the fixing seal ring 40 is fitted and installed on the inner peripheral side of the seal cover 10 so as to be movable in the axial direction.
- the seal cover 10 includes a fixing pin 48 that protrudes outward in the axial direction.
- the fixing pin 48 is inserted into a guide groove 47 formed in the flange portion 42 of the fixing seal ring 40.
- the seal cover 10 is provided with a plurality of spring seats in the circumferential direction, and holds a plurality of coil springs 49 in the circumferential direction between the opposing surfaces of the flange portion 42 of the fixing seal ring 40.
- the seal cover 10 is formed with a radial quenching liquid injection path 13 connected from the outer peripheral surface to the internal hole 11.
- the quenching liquid injection path 13 is formed with a pipe screw hole that can be connected to a pipe (not shown).
- the quenching liquid injected via the piping is injected from the quenching liquid injection path 13 to the outer peripheral side of the sealing ring 40 for fixing and the sealing ring 30 for rotation.
- the injected quenching liquid cools the heat generated when the sliding surfaces of the sealing ring for fixing 40 and the sealing ring for rotation 30 slide, and cleans impurities adhering to each seal portion.
- this quenching function is not an indispensable function with respect to this invention, the presence or absence is not limited.
- the sealing ring 40 for fixing is fitted and installed on the inner peripheral side of the seal cover 10 so as to be axially movable.
- the fixing seal ring 40 is formed with a nose portion 46 having a rectangular cross-sectional shape on the outer end surface of the machine.
- the machine-side end surface of the nose portion 46 is formed on the seal surface 43, and this seal surface 43 is slidably in close contact with the seal surface 32 of the rotary seal ring 30.
- the surface width (the length in the radial direction) of the seal surface 43 of the fixing seal ring 40 is narrower than the surface width of the seal surface 32 of the rotation seal ring 30.
- the surface width a of the sealing surface 43 of the fixing sealing ring 40 shown in FIG. 3 is preferably 1.1 to 2.0 mm. More preferably, the surface width a of the sealing surface 43 of the fixing sealing ring 40 is 1.4 to 1.8 mm.
- the axial length of the nose portion 46 is preferably 1.0 to 2.0 mm.
- a staircase portion 41a having a step along the axial direction is formed on the outer peripheral surface of the sealing ring 40 for fixing.
- a stepped portion 44 a having a step along the axial direction is formed so as to face the stepped portion 41 a of the fixing seal ring 40.
- An annular space having a rectangular cross section is formed by the staircase portion 41a and the staircase portion 44a, and an O-ring 45 is disposed in the annular space.
- the O-ring 45 seals between the seal cover 10 and the fixing seal ring 40.
- fluorine rubber, nitrile rubber, EPDM, perfluoroelastomer, or the like is used as the material of the O-ring 45.
- the outer peripheral side of the sealing ring 40 for fixing is formed in a flange portion 42, and a guide groove 47 is formed in the flange portion 42 in the axial direction.
- a fixing pin 48 formed on the end surface of the seal cover 10 on the outside of the machine is inserted into the guide groove 47.
- the fixing pin 48 and the guide groove 47 are in a state in which they can move relative to each other in the axial direction, and are locked in the circumferential direction. It is movable in the direction, and is installed so as not to rotate in the circumferential direction (the rotation direction of the rotation shaft 70).
- a plurality of spring seats are provided in the circumferential direction on the surface of the flange portion 42 of the sealing ring 40 for fixing facing the seal cover 10.
- a coil spring 49 is held.
- the fixing seal ring 40 is pressed outward in the axial direction, that is, in the direction of the rotation seal ring 30.
- the fixing seal ring 40 is formed so that the innermost diameter ratio K defined by the following formula 1 is in the range of 1.09 to 1.30.
- K r s / r a (Equation 1) K is the innermost diameter ratio r a is the radius of the rotating shaft 70 rs is the inner diameter of the sealing ring 40 for fixing
- the inner peripheral surface of the fixing seal ring 40 is formed in a tapered shape so as to be inclined toward the outer peripheral side toward the seal surface 43.
- the fixing sealing ring 40 is formed so that the balance ratio BV defined by the following formula 2 is in the range of 0.8 to 1.20. .
- the balance ratio in the range of 0.8 to 1.20, a pressing force corresponding to the pressure of the internal fluid acts on the fixing seal ring 40.
- a contact pressure corresponding to the pressure of the internal fluid is generated on the sliding surface, an appropriate undulation is generated on the sliding surface corresponding to the pressure of the internal fluid. Therefore, a fluid lubrication film suitable for the sliding surface can be formed.
- BV (r b 2 ⁇ r i 2 ) / (r o 2 ⁇ r i 2 ) (Equation 2)
- BV is the balance ratio r i is the inner diameter ro of the seal surface 43
- the outer diameter r b of the seal surface 43 is the diameter (inner diameter) of the surface parallel to the axial peripheral surface of the stepped portion 44 a of the seal cover 10.
- the collar 20 is fixed to the rotating shaft 70 by the set screw 22 in a state where the collar 20 is positioned by the set plate 55.
- the set plate 55 is removed after the mechanical seal device 1 is assembled.
- the end face on the inner side of the rotary seal ring 30 is formed on the inner seal surface 32 that slides closely with the seal surface 43 of the fixing seal ring 40.
- a groove 35 is formed on the inner peripheral surface of the rotary seal ring 30 on the collar 20 side.
- a spacer 37 and an O-ring 36 are arranged in order from the collar 20 side along the axial direction.
- the spacer 37 abuts on the collar 20 and forms a gap b between the back surface 31 facing the seal surface 32 of the rotation sealing ring 30 and the collar 20.
- the spacer 37 is made of a material having excellent strength such as SUS or engineering plastic.
- the gap b formed between the back surface 31 and the collar 20 is preferably 0.4 mm to 3 mm. When the gap b is small, the effect of this embodiment tends to be small due to the accumulated tolerance due to the combination of components.
- the ratio (a / b) between the surface width a of the seal surface 43 of the fixing seal ring 40 and the gap b is preferably 0.35 to 5.
- the O-ring 36 is in close contact with the groove 35 of the rotation seal ring 30, the rotation shaft 70, and the spacer 37, and seals between the rotation seal ring 30 and the rotation shaft 70. Further, since the O-ring 36 is made of an elastic material, the rotation sealing ring 30 is held elastically in the axial direction and the radial direction. As the material of the O-ring 36, fluorine rubber, nitrile rubber, EPDM, perfluoroelastomer, or the like is used.
- the rotary seal ring 30 is locked along the axial direction by a collar 20 fitted and installed on the rotary shaft 70 via an O-ring 36 and a spacer 37.
- a guide groove 33 is formed in the rotational seal ring 30 in the axial direction.
- the fixing pin 21 installed on the end face on the inner side of the collar 20 is inserted.
- the fixing pin 21 and the guide groove 33 are relatively movable in the axial direction and locked in the circumferential direction, and the rotation sealing ring 30 rotates integrally with the collar 20.
- the rotation sealing ring 30 and the fixing sealing ring 40 are made of a material such as silicon carbide (SiC), carbon, cemented carbide or the like.
- the fixing seal ring 40 and the rotation seal ring 30 are made of SiC.
- the surface width of the seal surface 43 is narrower than usual. For this reason, when the pressure of the coil spring 49 that presses the fixing seal ring 40 in the direction of the rotation seal ring 30 is the same, the surface pressure between the seal surface 43 and the in-machine seal surface 32 can be increased. In other words, when the same surface pressure (seal surface pressure) is obtained, it is possible to reduce the pressing force of the coil spring 49 by narrowing the seal surface width, and it is possible to use a small spring. Become. As a result, the mechanical seal device 1 can be downsized.
- the surface width of the seal surface 43 is narrow, the rigidity of the seal surface 43 is low and easily deformed. For this reason, when the sealing ring 30 for rotation rotates, the sealing surface 43 follows the sealing surface 32 which opposes flexibly. As a result, appropriate undulation occurs on the sliding surface, and a fluid lubricating film can be suitably formed on the sliding surface.
- the rotation sealing ring 30 since the gap b is formed between the back surface 31 of the rotation sealing ring 30 and the collar 20, the rotation sealing ring 30 is elastically held in the axial direction of the rotation shaft 70 and the collar. 20 and rotate together. For this reason, since the vibration etc. at the time of the rotation sealing ring 30 rotating can be absorbed, the wave
- the surface width of the sealing surface 43 is narrow, the temperature difference can be reduced between the machine interior A side where the sealing fluid is present and the machine exterior B side where there is no sealing fluid with the seal surface 43 interposed therebetween. it can. As a result, the amount of deformation due to heat can be reduced on the machine interior A side and machine exterior B side of the seal surface 43.
- the nose portion 46 is rectangular, even if the sliding surface is worn, it is possible to keep the appropriate contact pressure without changing the surface width of the seal surface 43.
- the balance ratio BV of the fixing seal ring 40 is in the range of 0.8 to 1.20, and the pressing force corresponding to the pressure of the internal fluid acts on the fixing seal ring 40. For this reason, since a contact pressure corresponding to the pressure of the internal fluid is generated on the sliding surface, an appropriate undulation is generated on the sliding surface corresponding to the pressure of the internal fluid. Therefore, a fluid lubrication film suitable for the sliding surface can be formed.
- a relatively large gap is formed between the outer peripheral surface of the rotary shaft 70 and the inner peripheral surface of the fixing seal ring 40.
- the inner peripheral surface of the sealing ring 40 for fixation is formed in a taper shape toward the sealing surface, the sealed fluid can be efficiently circulated toward the sliding surface. Therefore, sliding heat generation can be efficiently removed.
- Patent Document 1 in a sealing device having a narrow sliding surface width, it is considered that sealing must be performed with a very high contact pressure in order to ensure sealing performance. It was. Conventionally, if the sliding surface width is narrow, a liquid film is not formed between the sliding surfaces, and the amount of wear increases due to solid contact. Was considered undesirable.
- the present invention has found that when the sliding surface width is set to an optimal surface width, sliding heat generation can be greatly reduced, and a design incorporating this is conducted by trial and error, and a new type of solution that solves problems in the prior art. A mechanical seal device was realized.
- the shape and installation configuration of the sealing ring 40 for fixing and the sealing ring 30 for rotation may be arbitrarily changed.
- the nose portion is formed in the fixing seal ring 40, but the nose portion 40 may be formed in the rotation seal ring 30.
- the outside type mechanical seal device has been described.
- the present invention can also be applied to an inside type mechanical seal device.
- Examples 1 to 3 In Examples 1 to 3, the mechanical seal device described in the first embodiment was created, and the fixing seal ring 40 and the rotation seal ring 30 were made of SiC. As shown in Table 1, the sliding surface width of the sealing ring for fixing is 1.20 mm in Example 1, the sliding surface width is 1.50 mm in Example 2, and the sliding surface width is 1 in Example 3. 80 mm.
- Comparative Examples 1 to 3 Comparative Examples 1 and 2 differ from Examples 1 to 3 described above, as shown in Table 1, in Comparative Example 1, the sliding surface width is 1.00 mm, and in Comparative Example 2, the sliding surface width is 2.25 mm. It was. In Comparative Example 3, the sliding surface width is 1.5 mm.
- a gap is formed between the back surface of the rotary seal ring and the collar. Absent. That is, in Comparative Example 3, unlike the first embodiment described above, an O-ring is disposed in a groove formed at a radial intermediate position on the back surface of the rotary seal ring, so that the gap between the rotary seal ring and the collar is reduced. Sealed with.
- Example 1 to 3 no leakage occurred.
- the wear amount was 1.00E-10 (mm2 / N) or less, and the wear characteristics were good.
- the fluid lubrication region has a fluid film formed on the sliding surface.
- the wear amount was 2.00 E-14 (mm2 / N) or less, and the wear characteristics were particularly good.
- Comparative Example 1 no leakage occurred, but the wear amount was 1.00E-7 (mm2 / N). In Comparative Example 1, since the sliding surface width is too narrow, a fluid film is not formed on the sliding surface, which is considered to be an abrasive wear region.
- Comparative Example 2 Although the wear amount was 1.00E-15 (mm2 / N), leakage occurred. In Comparative Example 2, since the sliding surface width is too wide, the rigidity of the sealing surface becomes high, and the sealing surface formed in the nose portion cannot flexibly follow the opposing sealing surface. Conceivable.
- Comparative Example 3 sliding traces were seen locally, and a chip was generated at the end of the nose of the fixed sliding ring, indicating that it was in strong contact with a part, and leakage occurred. .
- Comparative Example 3 since no gap is formed between the back surface of the rotary seal ring and the collar, vibrations or the like when the rotary seal ring rotates cannot be absorbed and is generated on the sliding surface. It is thought that the swell could not be retained.
- Example 1 to 3 when the temperature of the sliding surface was measured, the temperature inside the machine was 80 ° C. and the temperature outside the machine was 79.8 ° C. Also from this result, it can be seen that in Examples 1 to 3, the sliding surface has a very small friction coefficient, and is a fluid lubrication region in which a fluid film is formed on the sliding surface.
- the present invention can be used for general industrial pumps, for example.
- any apparatus having a rotating shaft it can be used as a shaft seal device for the rotating shaft.
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Abstract
Description
スタッフィングボックスと回転軸との間隙で機内部の流体をシールするメカニカルシール装置であって、
前記スタッフィングボックスに取り付けられるシールカバーと、
前記シールカバーに取り付けられ、第1シール面を備える固定用密封環と、
前記回転軸に取り付けられ、前記第1シール面に摺動可能な第2シール面を備える回転用密封環と、
前記回転軸と一体に回転するカラーとを有し、
前記固定用密封環または前記回転用密封環の何れか一方のシール面は、他の一方のシール面よりも半径方向の面幅が狭くなるように形成されており、
前記回転用密封環の前記第2シール面に対向する背面と前記カラーとの間には隙間が形成されており、前記回転用密封環が前記回転軸の軸方向に弾性に保持されて前記カラーと一体に回転することを特徴とする。
本実施形態に係るメカニカルシール装置1は、一般産業用ポンプ等に装着されるシール装置である。メカニカルシール装置1は、図1および図2に示すように、密封面に対して回転軸に近接する側に被密封流体が存在するアウトサイド型に構成されており、回転軸70とスタッフィングボックス80との間隙で、機内部A側の流体をシールする。なお、図1および図2においては、スタッフィングボックス80の軸孔81側(図示左側)が機内部Aであり、その軸方向反対側(図示右側)が機外部Bである。
Kは、最内径比
raは、回転軸70の半径
rsは、固定用密封環40の内径
BVは、バランス比
riは、シール面43の内径
roは、シール面43の外径
rbは、シールカバー10の階段部44aの軸周面に平行な面の径(内径)
実施例1~3では、上記の第1実施形態で説明したメカニカルシール装置を作成し、固定用密封環40および回転用密封環30をSiCで構成した。なお、表1に示すように、実施例1では固定用密封環の摺動面幅を1.20mm、実施例2では摺動面幅を1.50mm、実施例3では摺動面幅を1.80mmとした。
比較例1および2は、上記の実施例1~3とは異なり、表1に示すように、比較例1では摺動面幅を1.00mm、比較例2では摺動面幅を2.25mmとした。比較例3では、摺動面幅を1.5mmとしたが、上記の第1実施形態で説明したメカニカルシール装置とは異なり、回転用密封環の背面とカラーとの間に隙間が形成されていない。すなわち、比較例3では、上記の第1実施形態とは異なり、回転用密封環の背面の径方向中間位置に形成される溝にOリングを配置して、回転用密封環とカラーとの間で密封した。
表1に示すように、摩耗および漏れ量の評価を行った。なお、摩耗の良否判定は、比摩耗量が1.00E-8(mm2/N)以下を良判定とした。
10・・・シールカバー
20・・・カラー
30・・・回転用密封環
31・・・背面
32・・・シール面
35・・・溝
36・・・Oリング
37・・・スペーサ
40・・・固定用密封環
41・・・テーパ部
43・・・シール面
46・・・ノーズ部
70・・・回転軸
80・・・スタッフィングボックス
A ・・・機内部
BV・・・バランス比
K ・・・最内径比
Claims (9)
- スタッフィングボックスと回転軸との間隙で機内部の流体をシールするメカニカルシール装置であって、
前記スタッフィングボックスに取り付けられるシールカバーと、
前記シールカバーに取り付けられ、第1シール面を備える固定用密封環と、
前記回転軸に取り付けられ、前記第1シール面に摺動可能な第2シール面を備える回転用密封環と、
前記回転軸と一体に回転するカラーとを有し、
前記固定用密封環または前記回転用密封環の何れか一方のシール面は、他の一方のシール面よりも半径方向の面幅が狭くなるように形成されており、
前記回転用密封環の前記第2シール面に対向する背面と前記カラーとの間には隙間が形成されており、前記回転用密封環が前記回転軸の軸方向に弾性に保持されて前記カラーと一体に回転することを特徴とするメカニカルシール装置。 - 前記回転用密封環の前記カラー側内周には、弾性部材およびスペーサを収容する溝が形成してあり、前記スペーサが前記カラーに当接して、前記回転用密封環の前記背面と前記カラーとの間に隙間が形成されることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記他の一方のシール面よりも半径方向の面幅が狭くなるように形成されたシール面が、断面形状が矩形のノーズ部に形成されていることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記他の一方のシール面よりも半径方向の面幅が狭くなるように形成されたシール面の面幅が、1.1~2.0mmに形成されていることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記固定用密封環のバランス比が、0.8~1.20に形成されていることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記固定用密封環の最内径比が、1.09~1.30に形成されていることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記固定用密封環の内周面が、前記第1シール面に向かって外周側に傾斜するようにテーパ状に形成されていることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記回転用密封環と前記固定用密封環が摺動することによって形成される密封面に対して、前記回転軸に近接する側に被密封流体が存在するアウトサイド型であることを特徴とする請求項1に記載のメカニカルシール装置。
- 前記固定用密封環および前記回転用密封環の少なくとも何れか一方が、SiCで構成されていることを特徴とする請求項1に記載のメカニカルシール装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/402,937 US20150226333A1 (en) | 2012-11-02 | 2013-09-04 | Mechanical seal device |
EP13852012.7A EP2843270B1 (en) | 2012-11-02 | 2013-09-04 | Mechanical seal device |
JP2014544367A JP6140179B2 (ja) | 2012-11-02 | 2013-09-04 | メカニカルシール装置 |
CN201380026282.6A CN104487744A (zh) | 2012-11-02 | 2013-09-04 | 机械密封装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012242767 | 2012-11-02 | ||
JP2012-242767 | 2012-11-02 |
Publications (1)
Publication Number | Publication Date |
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WO2014069098A1 true WO2014069098A1 (ja) | 2014-05-08 |
Family
ID=50627015
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/073824 WO2014069098A1 (ja) | 2012-11-02 | 2013-09-04 | メカニカルシール装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150226333A1 (ja) |
EP (1) | EP2843270B1 (ja) |
JP (1) | JP6140179B2 (ja) |
CN (1) | CN104487744A (ja) |
WO (1) | WO2014069098A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020045902A (ja) * | 2018-09-19 | 2020-03-26 | ユナイテッド テクノロジーズ コーポレイションUnited Technologies Corporation | ガスタービンエンジン用のシールアセンブリ |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105782457B (zh) * | 2016-05-09 | 2018-10-12 | 曾军 | 机械密封浮动型静止式补偿环直接保温结构 |
JP6803259B2 (ja) * | 2017-02-17 | 2020-12-23 | 三菱重工サーマルシステムズ株式会社 | 熱媒体加熱装置、及び車両用空調装置 |
JP2021142478A (ja) * | 2020-03-12 | 2021-09-24 | 住友重機械プロセス機器株式会社 | 撹拌装置 |
CN111951616B (zh) * | 2020-08-18 | 2022-05-06 | 怀化学院 | 幼教用看图识物装置 |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61141864U (ja) * | 1985-02-25 | 1986-09-02 | ||
JPS62153462U (ja) * | 1986-03-20 | 1987-09-29 | ||
JPH0369366U (ja) * | 1989-11-02 | 1991-07-10 | ||
JPH05106744A (ja) * | 1991-10-16 | 1993-04-27 | Mitsubishi Electric Corp | メカニカルシール |
JPH07260009A (ja) * | 1994-03-22 | 1995-10-13 | Nippon Pillar Packing Co Ltd | 非接触形軸封装置 |
US5967525A (en) * | 1997-08-29 | 1999-10-19 | John Crane Sealol Inc. | Drive mechanism for a rotating mechanical split seal and method of assembly thereof |
JP2001173800A (ja) | 1999-12-22 | 2001-06-26 | Nippon Pillar Packing Co Ltd | メカニカルシール |
WO2010001683A1 (ja) * | 2008-07-04 | 2010-01-07 | イーグル工業株式会社 | ダブルメカニカルシール装置 |
JP2010216489A (ja) * | 2009-03-13 | 2010-09-30 | Eagle Ind Co Ltd | メカニカルシール装置 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58160666A (ja) * | 1982-03-17 | 1983-09-24 | Eagle Ind Co Ltd | スタ−ンチユ−ブシ−ル |
US5076589A (en) * | 1990-03-01 | 1991-12-31 | Bw/Ip International, Inc. | Mechanical seal |
US5490679A (en) * | 1993-12-20 | 1996-02-13 | John Crane Inc. | Seal ring design |
DE19620950C2 (de) * | 1996-05-24 | 1999-08-26 | Freudenberg Carl Fa | Gleitringdichtung |
CN102472388B (zh) * | 2010-07-01 | 2015-04-22 | 伊格尔工业股份有限公司 | 挤压密封件 |
-
2013
- 2013-09-04 WO PCT/JP2013/073824 patent/WO2014069098A1/ja active Application Filing
- 2013-09-04 US US14/402,937 patent/US20150226333A1/en not_active Abandoned
- 2013-09-04 CN CN201380026282.6A patent/CN104487744A/zh active Pending
- 2013-09-04 EP EP13852012.7A patent/EP2843270B1/en active Active
- 2013-09-04 JP JP2014544367A patent/JP6140179B2/ja active Active
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61141864U (ja) * | 1985-02-25 | 1986-09-02 | ||
JPS62153462U (ja) * | 1986-03-20 | 1987-09-29 | ||
JPH0369366U (ja) * | 1989-11-02 | 1991-07-10 | ||
JPH05106744A (ja) * | 1991-10-16 | 1993-04-27 | Mitsubishi Electric Corp | メカニカルシール |
JPH07260009A (ja) * | 1994-03-22 | 1995-10-13 | Nippon Pillar Packing Co Ltd | 非接触形軸封装置 |
US5967525A (en) * | 1997-08-29 | 1999-10-19 | John Crane Sealol Inc. | Drive mechanism for a rotating mechanical split seal and method of assembly thereof |
JP2001173800A (ja) | 1999-12-22 | 2001-06-26 | Nippon Pillar Packing Co Ltd | メカニカルシール |
WO2010001683A1 (ja) * | 2008-07-04 | 2010-01-07 | イーグル工業株式会社 | ダブルメカニカルシール装置 |
JP2010216489A (ja) * | 2009-03-13 | 2010-09-30 | Eagle Ind Co Ltd | メカニカルシール装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2843270A4 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020045902A (ja) * | 2018-09-19 | 2020-03-26 | ユナイテッド テクノロジーズ コーポレイションUnited Technologies Corporation | ガスタービンエンジン用のシールアセンブリ |
Also Published As
Publication number | Publication date |
---|---|
JP6140179B2 (ja) | 2017-05-31 |
CN104487744A (zh) | 2015-04-01 |
EP2843270A1 (en) | 2015-03-04 |
EP2843270A4 (en) | 2015-12-30 |
JPWO2014069098A1 (ja) | 2016-09-08 |
EP2843270B1 (en) | 2017-06-21 |
US20150226333A1 (en) | 2015-08-13 |
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