JP2013096442A - Mechanical seal device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a mechanical seal device for reducing abnormal wear, as well as leakage, while stably rotating an intermediate ring.SOLUTION: This mechanical seal device 10 seals a fluid to be sealed between a rotary shaft 12 and a casing 14 for covering the rotary shaft 12. This device 10 includes: an intermediate ring 20 held by a rotary sealing ring 22 and a resting sealing ring 18 along the axial direction of the rotary shaft 12, sliding with both the rotary sealing ring 22 and the resting sealing ring 18, and relatively rotatably arranged with respect to both the rotary sealing ring 22 and the resting sealing ring 18; and a rotary disc 60 installed on the rotary shaft 12 so as to integrally rotate with the rotary shaft 12 and having an active surface 60a or 60b arranged in a predetermined fluid gap to face a passive surface 21a or 23a formed in the intermediate ring 20 so as to cross the rotary shaft 12.

Description

  The present invention relates to a mechanical seal device, and more particularly to an improvement of a mechanical seal device using an intermediate ring.

  For example, in a shaft seal for a high-temperature and high-speed rotary pump represented by a shaft seal for a boiler supply pump (BFP), the mechanical seal device is cooled in order to prevent the temperature of the sealed fluid made of hot water from decreasing. A system that does not perform is required.

  However, when a system that does not cool the sliding surface is used in a mechanical seal device for high temperature, high pressure, and high rotation pumps, the amount of deformation due to temperature and pressure of the members constituting the sliding surface increases, and the sliding surface The situation of the contact surface is an edge-like contact, and there is a problem that leakage occurs. Further, the sliding surface fluid evaporates due to sliding heat generation, and solid contact occurs on the sliding surface, which may lead to abnormal wear or damage.

  As a conventional technique for solving such a problem, for example, an arrangement in which an intermediate ring is arranged between a rotary seal ring and a stationary seal ring in order to suppress deformation of a sliding surface is known ( For example, see Patent Document 1).

  As another conventional technique, a blade row is installed on the sliding surfaces of the intermediate ring, the rotary seal ring, and the stationary seal ring to reduce the sliding torque between the intermediate ring, the rotary seal ring, and the stationary seal ring. (For example, see Patent Document 2).

  However, in the prior art in which the intermediate ring is arranged between the rotary seal ring and the stationary seal ring, the intermediate ring cannot rotate with respect to the static seal ring or rotates at the same rotational speed as the rotary seal ring. Or have repeated these conditions. That is, with the conventional technique, it has been difficult to stably rotate the intermediate ring at, for example, about 1/2 of the rotational speed of the rotary seal ring.

  In addition, in the conventional technology in which the blade row is installed on the sliding surface, it is difficult to control the sliding torque for the intermediate ring, the stationary seal ring, and the rotary seal ring. The problem that it is difficult, and the problem that leakage occurs from the sliding surface.

Japanese Patent No. 4147216 Japanese Examined Patent Publication No. 61-58704

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a mechanical seal device that can stably rotate an intermediate ring, has less abnormal wear, and has less leakage. .

In order to achieve the above object, a mechanical seal device according to the present invention comprises:
A mechanical seal device for sealing a sealed fluid between a rotating shaft and a casing covering the rotating shaft,
A rotating seal ring that rotates integrally with the rotating shaft;
A stationary seal ring attached to the casing so as not to rotate relative to the casing;
It is sandwiched between the rotary seal ring and the stationary seal ring along the axial direction of the rotary shaft, and slides with both the rotary seal ring and the stationary seal ring. An intermediate ring arranged to be rotatable relative to
The rotary shaft is attached to the rotary shaft so as to rotate integrally with the rotary shaft, and faces a first passive surface formed on the intermediate ring so as to intersect the rotary shaft with a predetermined first fluid gap. A rotating disk having a first active surface disposed thereon.

  In the mechanical seal device according to the present invention, the first active surface of the rotating disk is arranged to face the first passive surface formed on the intermediate ring with a predetermined first fluid gap. In the first fluid gap, the rotational force of the first active surface is transmitted to the first passive surface by the viscous force of the fluid flowing through the fluid gap, and the intermediate ring is rotated at a predetermined rotational speed (α ) To be rotated.

  The predetermined rotation speed (α) is smaller than the rotation speed of the rotation shaft and the rotation speed (β) of the rotary seal ring. For example, as the width of the first fluid gap is reduced and the facing area is increased, α is increased. On the contrary, as the width of the first fluid gap is increased and the facing area is decreased, the influence of the rotational force of the rotating disk is less likely to affect the rotation of the intermediate ring.

  That is, in the mechanical seal device according to the present invention, by adjusting the width and the facing area of the first fluid gap, the rotational force is converted into the viscous force of the fluid existing in the first fluid gap by the rotation of the rotating disk. The intermediate ring is forcibly rotated at a predetermined rotational speed (α). Therefore, it is possible to avoid a state in which the intermediate ring cannot be rotated with respect to the stationary seal ring, and the intermediate ring can be stably and forcibly rotated at a predetermined rotation speed (α).

  The predetermined rotational speed (α) is smaller than the rotational speed (β) of the rotary seal ring, and the heat generated on the sliding surface between the intermediate ring and the stationary seal ring directly causes the rotary seal ring to It is smaller than the heat generated on the sliding surface when it comes into contact with the stationary seal ring.

  Therefore, even if the mechanical seal device of the present invention is used in an environment of high temperature, high pressure and / or high speed rotation, abnormal wear of the rotary seal ring, stationary seal ring and intermediate ring is reduced, and their durability Will improve. Furthermore, in the mechanical seal device of the present invention, unlike the prior art, it is not necessary to form blade rows on the sliding surfaces of the rotary sealing ring, the intermediate ring, and the stationary sealing ring. There is little leakage.

  Preferably, the rotating disk is disposed between the rotating sealing ring and the stationary sealing ring along the axial direction of the rotating shaft so that the sealed fluid exists in the first fluid gap. It is located on the inner periphery or the outer periphery of. By using the sealed fluid as a fluid to be present in the first fluid gap, it is not necessary to have a fluid different from the sealed fluid in the first fluid gap, and the sealing structure is simplified.

  It is sufficient that at least one convex plate portion is formed on the inner peripheral side or the outer peripheral side of the intermediate ring, and if the first passive surface is formed on the surface of the convex plate portion, the operation of the present invention. There is an effect.

Preferably, at least two convex plate portions separated along the axial direction of the rotating shaft are formed on the inner peripheral side or the outer peripheral side of the intermediate ring, and between these two convex plate portions. A ring-shaped groove is formed, and at least a part of the rotating disk enters the groove,
One of the opposing inner wall surfaces of the concave groove is the first passive surface, the other is the second passive surface, and the surface opposite to the first active surface of the rotating disk is the second active surface,
The second active surface is disposed to face the second passive surface with a predetermined second fluid gap.

  The first and second active surfaces of the rotating disk and the first and second passive surfaces of the intermediate ring face each other not only through the first fluid gap but also through the second fluid gap. The transmission of the rotational force via the viscous force of the fluid existing in the cylinder is stabilized, and the intermediate ring can be rotated more stably.

FIG. 1 is a schematic longitudinal sectional view showing an upper half of a mechanical seal device according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the intermediate ring, rotating disk, and sleeve taken along line II-II of the mechanical seal device shown in FIG. It is a principal part expanded sectional view of the rotation sealing ring of a mechanical seal apparatus shown in FIG. 1, a stationary sealing ring, an intermediate | middle ring, a rotation disc, and a sleeve.

Hereinafter, the present invention will be described based on embodiments shown in the drawings.
A mechanical seal device 10 according to an embodiment of the present invention shown in FIG. 1 is used for, for example, a shaft seal for a boiler feed pump (BFP), but is not limited to a boiler feed pump, and other high temperature, high pressure and / or It can be suitably used as a shaft seal for a high-speed rotating device.

  The mechanical seal device 10 prevents the sealed fluid that flows through the internal gap 30 between the rotary shaft 12 that rotates about the shaft center Z and the casing 14 such as a pump from leaking to the outside 31 of the casing. And is attached to the inside of the seal cover 16.

  The seal cover 16 is detachably attached to the shaft end portion of the casing 14, and the attachment surface is sealed by an O-ring 24. The seal cover 16 constitutes a part of the casing 14 and may be formed integrally with the casing 14, but in order to facilitate maintenance of the mechanical seal device 10, It is preferable to fix it detachably.

Inside the seal cover 16, a stationary seal ring 18, an intermediate ring 20, and a rotary seal ring 22 are arranged in this order along the rotary shaft 12 from the internal gap 30 toward the casing exterior 31. In the present embodiment, the material of the stationary seal ring 18, the intermediate ring 20, and the rotary seal ring 22 is not particularly limited, and is made of, for example, SiC, C, SiN, Al ₂ O ₃ , zirconia, and the like. The intermediate ring 20 and the rotary seal ring 22 may all be made of the same material, or may be different. Preferably, the stationary seal ring 18 and the rotary seal ring 22 are made of a material softer than the intermediate ring 20.

  As shown in FIG. 3, the tip sliding surface 18 a formed at the shaft end (right shaft end) on the intermediate ring side of the stationary seal ring 18 rotates and slides on the first sliding surface 20 a of the intermediate ring 20. It is like that. The second sliding surface 20b opposite to the first sliding surface 20a of the intermediate ring 20 is a tip sliding surface 22a formed at the shaft end (left shaft end) on the intermediate ring side of the rotary seal ring 22. It is designed to rotate and slide.

  On the outer peripheral side of the tip sliding surface 18a in the stationary seal ring 18, an outward projection 18b is formed. A holder 36 having an L-shaped cross section is attached to the outer periphery of the outer convex portion 18b. The cylindrical portion 36a of the holder 36 covers the outer peripheral surface of the outer convex portion 18b, and the tip end in the axial direction of the cylindrical portion 36a. Covers a part of the outer periphery of the intermediate ring 20. The ring plate portion 36b integrally formed substantially perpendicularly to the cylindrical portion 36a of the holder 36 is in contact with the back side surface 18c of the outward convex portion 18b.

  As shown in FIG. 1, the ring plate portion 36 b of the holder 36 is in contact with the tip end in the axial direction of a spring 32 as an elastic member, and the rear end of the spring 32 is a spring holding member formed on the seal cover 16. Retained in the hole. The holder 36 and the stationary sealing ring 18 are pressed in the axial direction by the elastic force of the spring 32, and the pressing force is transmitted from the stationary sealing ring 18 to the intermediate ring 20 and the rotary sealing ring 22, and each of these sliding surfaces 18a, Ensure contact at 20a and 20b, 22a (see FIG. 3).

  Further, the elastic force of the spring 32 holds the holder 36 and the stationary sealing ring 18 so as not to move relative to each other in the axial direction, and the tip of the cylindrical portion 36a in the holder 36 shown in FIG. It protrudes to the tip in the axial direction from the surface 18a and is always located on the outer periphery of the intermediate ring 20. The axial direction front-end | tip part of the cylinder part 36a in the holder 36 has the function to hold | maintain the intermediate ring 20 and the stationary sealing ring 18 in a concentric state by being located in the outer periphery of the intermediate ring 20. FIG.

  The springs 32 shown in FIG. 1 are arranged at a plurality of positions along the circumferential direction. A base end portion of a detent pin 34 is fixed to the seal cover 16 between the springs 32 along the circumferential direction. The distal end portion of the detent pin 34 engages with a detent groove or hole formed in the ring plate portion 36b of the holder 36 and the outward projecting portion 18b of the stationary sealing ring 18, so that the stationary sealing ring 18 and The holder 36 is attached to the seal cover 16 so as to be movable in the axial direction but not to be relatively rotatable. An O-ring 26 is attached between the stationary seal ring 18 and the seal cover 16 to prevent the sealed fluid from leaking in the direction of the spring 32 from between them.

  The rotary seal ring 22 is attached to the rotary shaft 12 so as to rotate integrally with the rotary shaft 12. Specifically, it is attached as follows. As shown in FIG. 1, a sleeve 40 is fixed to the rotary shaft 12 by a sleeve collar 44. An O-ring 42 is mounted between the sleeve 40 and the rotating shaft 12 to prevent the sealed fluid from leaking to the outside of the casing 31 from between these.

  The sleeve collar 44 is fixed to the rotating shaft 12 together with the sleeve 40 by a set screw 46 or the like, and rotates together with the rotating shaft 12. An O-ring 48 is attached between the sleeve collar 44 and the sleeve 40 to prevent the sealed fluid from leaking to the outside of the casing 31 from between these.

  As shown in FIG. 3, an outward convex portion 22 b is formed on the outer peripheral side of the tip sliding surface 22 a in the rotary sealing ring 22. A holder 56 having an L-shaped cross section is mounted on the outer periphery of the outer convex portion 22b, and the cylindrical portion 56a of the holder 56 covers the outer peripheral surface of the outer convex portion 22b, and the tip end in the axial direction of the cylindrical portion 56a. Covers a part of the outer periphery of the intermediate ring 20. The ring plate portion 56b integrally formed substantially perpendicularly to the cylindrical portion 56a of the holder 56 is in contact with the back side surface 22c of the outward convex portion 22b.

  As shown in FIG. 1, the ring plate portion 56 b of the holder 56 is in contact with the axial front end of a spring 52 as an elastic member, and the rear end of the spring 52 is a spring holding member formed on the sleeve collar 44. Retained in the hole. The elastic force of the spring 52 is preferably weaker than the elastic force of the spring 32 described above. For example, 1/4 to 1/8 of the elastic force of the spring 32 is preferable.

  The elastic force of the spring 52 holds the holder 56 and the rotary seal ring 22 so as not to move relative to each other in the axial direction, and the tip end in the axial direction of the cylindrical portion 56a in the holder 56 shown in FIG. It is determined so that it protrudes to the tip in the axial direction and is always located on the outer periphery of the intermediate ring 20. The axial direction front-end | tip part of the cylinder part 56a in the holder 56 has the function to hold | maintain the intermediate | middle ring 20 and the rotation sealing ring 22 in a concentric state by being located in the outer periphery of the intermediate | middle ring 20. FIG.

  The springs 52 shown in FIG. 1 are arranged at a plurality of positions along the circumferential direction. A base end portion of a detent pin 54 is fixed to the sleeve collar 44 between the springs 52 along the circumferential direction. The distal end of the detent pin 54 engages with a detent groove or hole formed in the ring plate portion 56b of the holder 56 and the outer convex portion 22b of the rotary seal ring 22, so that the rotary seal ring 22 and The holder 56 is attached to the sleeve collar 44 so as to be movable in the axial direction and not relatively rotatable. An O-ring 50 is attached between the rotary sealing ring 22 and the sleeve collar 44 to prevent the sealed fluid from leaking in the direction of the spring 52 from between them.

  A sleeve holder 62 is attached by a plurality of bolts 64 to the shaft end of the sleeve 40 opposite to the joint end with the sleeve collar 44, and a rotating disk is interposed between the sleeve holder 62 and the sleeve 40. The inner edge 60 is attached to the sleeve 40 in a non-rotatable manner.

As shown in FIG. 2, the rotating disk 60 is composed of, for example, arc-shaped divided bodies 60 ₁ , 60 ₂ , and 60 ₃ that are divided into three or more in the circumferential direction, and these are combined in the circumferential direction. Thus, the rotating disk 60 is configured. Each arcuate divided body 60 ₁ , 60 ₂ , 60 ₃ is non-rotatably attached to the sleeve holder 62 and the sleeve 40 (that is, the rotating shaft 12) by a bolt 64. The reason why the rotary disk 60 is formed of three or more arc-shaped divided bodies is to facilitate insertion into the inner concave groove 20 c formed on the inner peripheral side of the intermediate ring 20.

  In the present embodiment, the pair of convex plate portions 21 and 23 are separated along the axial direction of the rotary shaft 12 on the inner peripheral side with respect to the sliding surfaces 20 a and 20 b formed at both axial ends of the intermediate ring 20. An inner concave groove 20c is formed between these convex portions. Passive surfaces 21a and 23a are formed on the side surfaces of the convex plate portions 21 and 23 on the concave groove 20c side, and concave portions 70 and 72 are formed on the side surface opposite to the concave groove 20c in the axial direction. Therefore, the sealing rings 18 and 22 are prevented from coming into contact with the sliding surfaces 18a and 22a.

  The groove 20c enters the rotating disk 60 so that the main body does not come into contact, and the active surfaces 60a and 60b formed on the front and back surfaces in the axial direction of the rotating disk have predetermined fluid gaps with respect to the passive surfaces 21a and 23a, respectively. It is arranged with. The outer peripheral surface 60c of the rotating disk 60 is also disposed with a predetermined fluid gap with respect to the groove bottom surface of the recessed groove 20c. These fluid gaps are preferably substantially the same, but are not necessarily the same. For example, the fluid gap between the outer peripheral surface 60c of the rotating disk 60 and the groove bottom surface of the concave groove 20c may be wider than the fluid gap between the active surfaces 60a and 60b and the passive surfaces 21a and 23a.

  In these fluid gaps, the rotational force of the active surfaces 60 a and 60 b is transmitted to the opposing passive surfaces 21 a and 23 a due to the viscous force of the fluid flowing through the fluid gap, and the intermediate ring 20 is transferred to the stationary seal ring 18. And determined to rotate at a predetermined rotational speed (α).

  The predetermined rotational speed (α) is a speed smaller than the rotational speed of the rotary shaft 12 and the rotational speed (β) of the rotary seal ring 22, and the width and the opposing area of the fluid gap, or the uneven shape of the surface or the surface roughness. It can be controlled by adjusting the hydrophilic substance application. For example, as the width of the fluid gap is reduced and the facing area is increased, α tends to approach β. Conversely, as the width of the fluid gap is increased and the facing area is reduced, the influence of the rotational force of the rotating disk 60 is smaller. It becomes difficult to influence the rotation of the intermediate ring 20.

  That is, in the mechanical seal device 10 according to the present embodiment, by adjusting the width of the fluid gap, the facing area, and the like, the rotational force of the rotating disk 60 is rotated as the viscous force of the fluid existing in the fluid gap. The intermediate ring 20 is transmitted to the intermediate ring 20 and is forcibly rotated at a predetermined rotational speed (α). Therefore, it is possible to avoid a state in which the intermediate ring 20 cannot rotate with respect to the stationary sealing ring 18, and the intermediate ring 20 can be stably and forcibly rotated at a predetermined rotational speed (α). become.

  The predetermined rotational speed (α) is lower than the rotational speed (β) of the rotary seal ring 22, and heat generated on the sliding surface between the intermediate ring 20 and the stationary seal ring 18 is generated by the rotary seal ring. When the 22 is directly brought into contact with the stationary seal ring 18, the heat generated on the sliding surface is smaller than that generated on the sliding surface.

  Therefore, in the mechanical seal device 10 of the present embodiment, abnormal wear of the rotary seal ring 22, the stationary seal ring 18, and the intermediate ring 20 is reduced even when used in an environment of high temperature, high pressure and / or high speed. , These durability will be improved. Furthermore, in the mechanical seal device 10 of the present embodiment, unlike the prior art, it is not necessary to form blade rows on the sliding surfaces of the rotary sealing ring 22, the intermediate ring 20, and the stationary sealing ring 18, so There is little leakage of sealed fluid.

  The predetermined rotation speed (α) of the intermediate ring 20 described above has a ratio (α / β) to the rotation speed (β) of the rotary seal ring 22 of less than 1, preferably 1/4 to 3/4, particularly preferably. Is determined to be within ½ ± 1/10.

  Specific values of the fluid gap include the sliding area of the rotary sealing ring 22, the stationary sealing ring 18 and the intermediate ring 20, the material, the areas of the convex plate portions 21 and 21, the fluid viscosity, the rotational speed, the fluid temperature, and the fluid density. , Etc., and is not particularly limited, but preferably about 0.1 to 0.5 mm.

  In the present embodiment, the rotary disk 60 is arranged in the axial direction of the rotary shaft 12 so that the sealed fluid existing in the internal gap 30 is introduced into the fluid gap between the rotary disk 60 and the intermediate ring 20. Along the rotary sealing ring 22 and the stationary sealing ring 18, the intermediate ring 20 is disposed on the inner circumference. By introducing the sealed fluid into the fluid gap, it is not necessary to have a fluid different from the sealed fluid in the fluid gap, and the sealing structure is simplified.

  The present invention is not limited to the above-described embodiment, and can be variously modified within the scope of the present invention.

  For example, in addition to the pair of convex plate portions 21 and 23, other convex plate portions may be provided further apart in the axial direction on the inner peripheral side of the intermediate ring 20, and each concave portion between the convex plate portions may be provided. Two or more rotating rings 60 may be arranged in the groove with a predetermined fluid gap. Alternatively, it is sufficient that at least one convex plate portion 21 or 23 is formed on the inner peripheral side of the intermediate ring 20, and a single passive surface 21 a or 23 a is formed on the surface of the convex plate portion 21 or 23. If it exists, the effect of this invention can be show | played. Note that any one of the single passive surfaces 21a or 23a may be the first passive surface, and the surface of the rotating disk 60 facing the first passive surface is the first active surface.

  However, as shown in the above-described embodiment, the active surfaces 60a and 60b formed on both sides of the rotating disk 60 in the axial direction and the side surface of the groove 20c between the pair of convex plate portions 21 and 23 of the intermediate ring 20 are provided. It is preferable that the passive surfaces 21a and 23a formed in the above face each other. By comprising in this way, transmission of the rotational force through the viscous force of the fluid which exists in these fluid gaps is stabilized, and it becomes possible to rotate the intermediate ring 20 more stably.

  Further, in the present invention, grooves, irregularities, etc. for increasing the viscous force of the fluid may be formed on at least one of the active surfaces 60a and 60b and the passive surfaces 21a and 23a constituting the fluid gap. In the present invention, the groove depth of the concave groove 20 c formed in the intermediate ring 20 is not particularly limited, and may be positioned close to the outer peripheral surface of the intermediate ring 20. In that case, the outer diameter of the rotating disk 60 can also be increased according to the groove depth, and the facing area between the active surfaces 60a and 60b and the passive surfaces 21a and 23a in the fluid gap increases.

  Furthermore, in the present invention, the active surfaces 60a and 60b formed on the rotating disk 60 only need to intersect the axis Z of the rotating shaft 12, but the intermediate ring 20 is not moved in the axial direction as much as possible. From the viewpoint, the active surfaces 60a and 60b and the passive surfaces 21a and 23a are preferably substantially perpendicular to the axis Z.

  Further, in the embodiment described above, the outside-side mechanical seal device has been described, but the structure of the present invention can also be applied to an inside-type mechanical seal device. In the above-described embodiment, the convex portions 21 and / or 23 and the concave groove 20 c are formed on the inner peripheral side of the intermediate ring 20, but these convex portions and / or concave grooves are on the outer peripheral side of the intermediate ring 20. You may form in. In that case, the rotating ring 60 described above is disposed on the outer peripheral side of the intermediate ring 20.

DESCRIPTION OF SYMBOLS 10 ... Mechanical seal apparatus 12 ... Rotating shaft 14 ... Casing 16 ... Seal cover 18 ... Static sealing ring 18a ... Sliding surface 20 ... Intermediate ring 20a, 20b ... Sliding surface 20c ... Concave groove 21, 23 ... Convex plate part 21a, 23a ... Passive surface (one is the first passive surface, the other is the second passive surface)
22 ... Rotating sealing ring 22a ... Sliding surface 32, 52 ... Spring 36, 56 ... Holder 60 ... Rotating disk 60a, 60b ... Active surface (one is the first active surface and the other is the second active surface)
60c ... outer peripheral surface

Claims (4)

A mechanical seal device for sealing a sealed fluid between a rotating shaft and a casing covering the rotating shaft,
A rotating seal ring that rotates integrally with the rotating shaft;
A stationary seal ring attached to the casing so as not to rotate relative to the casing;
It is sandwiched between the rotary seal ring and the stationary seal ring along the axial direction of the rotary shaft, and slides with both the rotary seal ring and the stationary seal ring. An intermediate ring arranged to be rotatable relative to
The rotary shaft is attached to the rotary shaft so as to rotate integrally with the rotary shaft, and faces a first passive surface formed on the intermediate ring so as to intersect the rotary shaft with a predetermined first fluid gap. And a rotating disk having a first active surface disposed thereon.   The rotary disk is arranged between the rotary seal ring and the stationary seal ring along the axial direction of the rotary shaft so that the sealed fluid exists in the first fluid gap. Or the mechanical-seal apparatus of Claim 1 arrange | positioned and located in an outer periphery.   The at least 1 convex board part is formed in the inner peripheral side or the outer peripheral side of the said intermediate ring, The said 1st passive surface is formed in the surface of the said convex board part. Mechanical seal device. At least two convex plate portions separated along the axial direction of the rotating shaft are formed on the inner peripheral side or the outer peripheral side of the intermediate ring, and a ring shape is formed between these two convex plate portions. Is formed, and at least a part of the rotating disk enters the inside of the groove,
One of the opposing inner wall surfaces of the concave groove is the first passive surface, the other is the second passive surface, and the surface opposite to the first active surface of the rotating disk is the second active surface,
The mechanical seal device according to any one of claims 1 to 3, wherein the second active surface is disposed to face the second passive surface with a predetermined second fluid gap.

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