JP2003097728A - Mechanical seal device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily assemble without distortion of a seal ring for rotation of a mechanical seal device caused by installation. SOLUTION: The seal ring 2 for rotation and a sleeve 52 are provided with fitting holes 4 and 53 penetrating through surfaces fitting to each other. The seal ring 2 for rotation and the sleeve 52 are integrally fixed by fitting with the fitting holes 4 and 53. Further, a drive pin having a fitting means for preventing separation at an end is provided.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to, for example, a stirrer,
The present invention relates to a mechanical seal device used for a grinder, a rotary joint and the like. In particular, the present invention relates to a mechanical seal device with improved fixing of a rotary seal ring.

[0002]

2. Description of the Related Art Regarding the prior art of the present invention, Japanese Patent No. 306
There is a mechanical seal as shown in FIG. 1 of Japanese Patent No. 6367. FIG. 5 shows the mechanical seal 1 disclosed in this publication.
FIG. 50 is a half sectional view of 50.

In FIG. 5, the mechanical seal 150 is shown.
Is a seal case 1 attached to the housing 180 to seal the sealed fluid in the housing 180.
It is arranged between 81 and the rotating shaft 170. In this mechanical seal 150, each of the first mechanical seal 150A and the second mechanical seal 150B is arranged on both sides of one rotary seal ring 151. This rotating seal ring 15
No. 1 is fixed to a sleeve 171 fitted to the rotary shaft 170. The sleeve 171 is divided into two in the axial direction. A step 172 is formed on the surface of the first sleeve 171A having a different outer diameter.
The rotary seal ring 151 is fitted to the small-diameter outer peripheral surface 173 of 72, and the second sleeve 171B is fitted to the small-diameter outer peripheral surface 173 from the other axial direction to form the step 172 and the second sleeve 17.
The rotary seal ring 151 is axially fixed by the end face of 1B.

Between the rotary seal ring 151 and the sleeve 171, O-rings 160A and 160B are arranged on the inner diameter surface and the side surface of the rotary seal ring 151, respectively, to seal between the joint surfaces of these two parts. There is. The first fixing seal ring 152 and the second fixing seal ring 153 are resiliently pressed by the first spring 160A and the second spring 160B seated in the seal case 181 so as to face each other. or,
The first fixing seal ring 152 and the second fixing seal ring 153 are
The third O-ring 16 is provided between the seal case 181 and the seal case 181.
It is sealed by 1A and the fourth O-ring 161B.
Then, the liquid supply port 182 provided in the seal case 181
The liquid A is supplied to the sealed chamber from. The liquid A is applied to the sealing surfaces 151A and 151B on both sides of the rotary seal ring 151.
With respect to the first fixed seal surface 1 of the first fixed sealing ring 152
52A and the second fixed sealing surface 1 of the second fixed sealing ring 153.
53A is closely sealed. Also, the rotary seal ring 1
51 is a drive pin 179 fixed to the sleeve 171
It is structured such that it is locked to and rotates integrally with the rotary shaft 170.

The mechanical seal 15 constructed in this way
0 means that if the rotary seal ring 151 is not accurately fixed by the step portion 172 of the first sleeve 171A and the end surface of the second sleeve 171B, the rotary seal ring 151 will be inclined in the axial direction, and each seal surface 151A. , 151B cannot come into close contact with each other, and the liquid leaks. In particular, since the first and second O-rings 160A and 160B are interposed between the joint surfaces of the rotary seal ring 151, the rotary seal ring 15 as shown in FIG.
1 becomes unstable, and the sealing surfaces 151A, 151
B cannot come into close contact with the first fixed seal surface 152A and the second fixed surface 153A on the same plane. Therefore, the sleeve 17
The outer diameter of 1 is made large, and the joint surface of the step 172 for holding is also made large.

However, when the sleeve 171 has a large diameter, the outer diameter of the mechanical seal 150 also increases, and the mechanical seal 150 as a whole also increases in size. At the same time, each sealing surface 1
Since 51A, 151B, 152A, and 153A also have large diameters, sliding resistance increases. Further, if the joint area of the step portion 172 is increased, the rotary seal ring 51 is made of ceramics or the like. Therefore, the sealing surfaces 151A and 151B are deformed by the crimping with an increased joint area and the flatness is deteriorated. . As a result, it becomes difficult to make a sealed contact, and the sealed fluid leaks.

Further, FIG. 7 is a cross-sectional view of a rotary joint of Conventional Example 2. In FIG. 7, the rotary joint 100 is arranged in a body 101 having an inner peripheral surface, and a rotor 102 rotatably inserted in the inner peripheral surface of the body 101 is provided. Also, body 1
In 01, a large number of fluid supply passages 103 are provided. Further, the rotor 102 is also provided with a number of fluid passages 104. Then, the body 101 and the rotor 102
A plurality of mechanical seals 105 are axially arranged between the fluid supply passages 103, and the fluid supply passages 103 and the fluid passages 104 communicate with each other via the seal chambers 106 formed therebetween.

The respective seal chambers 106 are sealed by respective mechanical seals 105 so as not to flow out. This mechanical seal 105 includes a rotary seal ring 11
The sliding seal surface S between 0 and the stationary seal ring 111 tightly seals. The rotary seal ring 110 is elastically supported by a holding portion 112 fixed to the rotary shaft 102 by a set screw 115 via a spring 113. Further, the fixed sealing ring 111 is pressure-bonded between the divided bodies 101A forming the body 101. For this reason, in the supply of the fluid passage system, the fluid supply passage 103 of the body 101 and the fluid passage 104 of the rotor 102 must be sealed and communicated. Further, since the stationary seal ring 111 is crimped by the divided bodies 101A via the bolts 116, the flatness of the sliding seal surface S of the stationary seal ring 111 is disturbed, and the stationary seal ring 111 is rotated. Due to abrasion and damage due to sliding heat generation of 111, reduction in sealing ability is caused.

Further, the inside of these seal chambers 106 is in a liquid / gas / vacuum state or at a high temperature in the fluid passage 104 according to a program of an apparatus for treating a sealed fluid which operates when used as a rotary joint of a polishing machine. It becomes a state. Therefore, unless the sealing surface of the mechanical seal is cooled or lubricated, the rotary seal ring 110
The fixing seal ring 111 will be worn or damaged. However, with such a structure, cooling of the rotary seal ring 110 and the stationary seal ring 111 becomes difficult in terms of design.

[0010]

In the case of the above-mentioned conventional example 1, when it is attempted to securely fix the fixing seal ring 151, the sleeve 171 has a large diameter, and as a result, the mechanical seal 150 is enlarged. This will increase the sliding resistance of the sealing surface. Further, when the fixing seal ring 151 is pressure-bonded by the sleeve 171 having a large diameter, each sealing surface 151
The flatness of A and 151B is distorted to promote wear, and the sealing ability cannot be exhibited.

Further, in the above-mentioned conventional example 2, the stationary seal ring 1 is used.
Since 11 is fixed to the divided body 101A, the entire diameter increases with the thickness. At the same time, since the stationary seal ring 111 is crimped by each divided body 101A, the flatness of the sliding seal surface S is disturbed, the abrasion of the sliding seal surface S is promoted, and the sealing ability is reduced. Further, since the rotary seal ring 110 pressed by the spring 113 is held on the rotary shaft 102 side, it easily rocks as it rotates. Further, the holding portion 112 fixed to the rotor 102
Is directly fixed to the rotor 102 via the setscrew 115, so that when the setscrew 115 is loosened, the rotary seal ring 110 held by the holding portion 112 swings due to incomplete mounting and a failure. Cause

Further, when a mechanical seal is used for the rotary joint, a holding portion 112 for attaching the rotary seal ring 110 to the rotor 102 is required, so that the rotor 102 becomes longer in the axial direction and the mechanical seal There is a problem that the structure becomes complicated. Further, since the rotary seal ring 110 and the holding portion 112 are complicatedly attached to the rotor 102, vibration and the like may occur when the rotor 102 is rotated at a high speed, which is a problem. or,
Since the rotary seal ring 110 and the holding portion 112 are attached to the rotor 102, the weight increases and a large amount of power energy is consumed.

The present invention has been made in view of the above-mentioned problems, and its technical problem is to prevent the flat surface of the seal surface of the rotary seal ring from being deformed due to the mounting state and to perform the sealing contact. This is to ensure the reliability and prevent wear of the sealing surface due to deformation. Another object of the present invention is to provide an engaging hole in the rotary seal ring to facilitate cooling of the rotary seal ring, prevent thermal deformation of the seal surface, and prevent wear of the seal surface. Furthermore, the material of the rotary seal ring is to be widely applicable from carbon to silicon carbide.

Another object of the present invention is to facilitate the attachment of the rotary seal ring to the rotary shaft and reduce the size of the rotary seal ring. Then, the outer diameter of the rotary seal ring is reduced to reduce the size of the mechanical seal as a whole. Another object is to make the sleeve a thin cylindrical shape without steps so that the inner diameter of the seal case or the mechanical seal of the body can be reduced. Further, along with the reduction in the diameter of the stationary seal ring, the sealing device is also reduced in diameter to reduce the sliding resistance due to the sliding area to prevent wear and reduce the consumption of power energy due to the sliding resistance. .

[0015]

The present invention has been made to solve the above-mentioned technical problem, and the technical means is configured as follows. A mechanical seal device of the present invention according to claim 1 is a mechanical seal device for sealing between a rotary shaft and a seal housing, wherein a sleeve fitted to the rotary shaft and a side face fitted to the sleeve are provided. A rotary sealing ring having a sealing surface,
A stationary seal ring elastically held by the seal housing and having a relative seal surface in close contact with the seal surface of the rotary seal ring, wherein the rotary seal ring and the sleeve are fitted to each other. Has engaging holes that penetrate each other on the mating surface,
In addition to having a pin portion that fits into the engagement hole, the pin portion has a drive pin that is held by locking means that prevents the pin portion from coming off the engagement hole.

In the mechanical seal device of the present invention according to claim 1, the rotary seal ring can be easily attached to the rotary shaft by the drive pin through the engaging hole.
In addition, since the seal surface does not receive external pressure due to the attachment, the flatness can be maintained and the seal surface can be brought into close contact with the relative seal surface to exert the sealing ability. Further, since the rotary seal ring is held only by the drive pin, the rotary seal ring can be formed to have an arbitrary size both in the radial direction and the axial direction, and the mechanical seal can be downsized. Further, since the rotary seal ring is provided with through holes such as engagement holes, a cooling effect of the rotary seal ring is produced, and thermal deformation can be prevented.
And, the fitting interval between the engaging hole and the pin portion is a tight fit,
Since it is possible to make a loose fit and fit with the same size and optionally fit as necessary, it is possible to make a corresponding contact surface so as to be in close contact with the relative seal surface 11.

According to a second aspect of the mechanical seal device of the present invention, the engaging means has a head portion thicker than the pin portion at one end, and the head portion prevents the head portion from coming off between the rotary shaft and the sleeve. It is held.

In the mechanical seal device according to the second aspect of the present invention, the head portion of the drive pin is formed larger than the pin portion so as to serve as locking means for preventing slippage between the rotary seal ring and the rotary shaft. Therefore, if the drive pin is fitted into the engagement hole and the sleeve is inserted into the rotary shaft before inserting the sleeve into the rotary shaft, the head of the drive pin is retained between the rotary shaft and the sleeve so as not to come off. . Then, the rotary seal ring is held by the drive pin so as to rotate integrally with the rotary shaft, and moreover, the seal surface can be closely joined with the relative seal surface of the stationary seal ring in the same plane. In addition, if the sleeve is pulled out from the rotary shaft, the drive pin is easily separated from the rotary seal ring, so that the rotary seal ring can be replaced with a new rotary seal ring. If the drive pin is made smaller, the rotary seal ring can also be made smaller, so that the rotary seal ring can be made compact and the mechanical seal can be made compact.

According to a third aspect of the mechanical seal device of the present invention, the retaining means is retained between the rotating shaft and the retaining ring fitted to the outer periphery of the rotating seal ring to prevent the retaining shaft from coming off. It is a thing.

In the mechanical seal device according to the third aspect of the present invention, since the rotary seal ring can be reinforced by the retaining ring fitted to the outer periphery of the rotary seal ring, the rotary seal ring is liable to be cracked, but the wear resistance is high. Also, it becomes possible to use a material having heat resistance. Then, if the drive pin is fitted into the engagement hole, the drive pin has one end retained by the retaining shaft between the rotating shaft and the retaining ring, so that the drive pin rotates the rotary seal ring together with the rotating shaft. To be retained. Since the drive pin is a cylindrical pin, the rotation sealing ring can be downsized by reducing the diameter. Moreover, the mounting of the rotary seal ring is extremely simple because the drive pin is inserted into the engagement hole and the sleeve is inserted into the rotary shaft to complete the assembly of the rotary seal ring.

[0021]

BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of a mechanical seal device according to the present invention will be described below with reference to FIGS. 1 to 4. FIG. 1 is a half sectional view of a mechanical seal device 1 according to a first embodiment of the present invention. 2 is a sectional view of a mechanical seal device 1 according to a second embodiment of the present invention. FIG. 3 is a half sectional view of a mechanical seal device 1 according to a third embodiment of the present invention. FIG. 4 is a mechanical seal device 1 according to a fourth embodiment of the present invention.
FIG.

FIG. 1 shows a mechanical seal device 1 showing a first embodiment. In FIG. 1, reference numeral 1 is a mechanical seal device. The mechanical seal device 1 is used as a shaft sealing device for a water absorption pump or a circulation pump of a boiler or an agitator. FIG. 1 is composed of a first mechanical seal 1A and a second mechanical seal 1B as a shaft sealing device of the pump A. The mechanical seal device 1 is provided between the rotary shaft 50 and the housing 60 of the device to seal the working fluid in the device H.

A sleeve 52 is fitted on the rotary shaft 50 via a key 51 so as to rotate integrally. First O-rings 58 are mounted in annular grooves 57 provided in parallel while the sleeve 52 and the rotary shaft 50 are fitted.
A first engagement hole 53 is formed between the two first O-rings 58. A counterbore hole 53A is provided on the inner diameter side of the sleeve 52 of the first engagement hole 53. This engagement hole 53
Are provided in the circumferential direction of the sleeve 52 according to the rotational force of the rotary seal ring 2. Further, on both sides of the first engagement hole 53 of the sleeve 52, there are two annular grooves 54 for attaching an O-ring.
One is provided. Also in this annular groove 54, the second O-ring 5
5 is installed. These O-rings 55 and 58 are
The fluid flowing from the first engagement hole 53 and the inside H of the device is sealed.

The rotary seal ring 2 is fitted on the outer peripheral surface of the sleeve 52 via a second O-ring 55. The rotary sealing ring 2 is formed in a cylindrical shape and has a first sealing surface 3 on both side surfaces.
A and the second sealing surface 3B are provided. The rotary seal ring 2 is provided with a second ring at a position corresponding to the first engagement hole 53 of the sleeve 52.
Engagement holes 4 are provided. The corresponding engagement holes 53, 4 are formed to have the same diameter. Further, as the material of the rotary seal ring 2, carbon, silicon carbide, ceramics, super hard alloy, or the like is used. A reinforcing ring 5 is fitted on the outer peripheral surface of the rotary seal ring 2. The reinforcing ring 5 is used to reinforce a material having a poor ductility such as a ceramic material for the rotary seal ring 2. As the material of the reinforcing ring 5, iron, steel, stainless steel or the like is used.

The sleeve 52 and the rotary seal ring 2 are
They are integrally connected by a drive pin 6. The drive pins 6 are arranged in three equal parts in the circumferential direction of the rotary seal ring 2. When the rotating seal ring 2 has a large diameter 4, 6, ...
The number is equally distributed, but in the case of a small diameter, 2 or 1 is sufficient. The head portion 6A of the drive pin 6 has a large diameter, and the pin portion 6B has a diameter smaller than that of the head portion 6A. This head portion 6A is a counterbore hole 53 of the sleeve 52.
It is embedded in A and engaged. And drive pin 6
The head portion 6A is configured as a locking means that is locked by the rotary seal ring 2 and the sleeve 52 so as not to come out even when the rotary seal ring 2 rotates. The pin portion 6B of the drive pin 6 is fitted into the second engagement hole 4 of the rotary seal ring 2 or in a loose fit. In the case of a clearance fit, it is advisable to set the distance in the range of 0.001 to 0.8 mm.
The drive pin 6 is made of heat-treated steel. In addition, stainless steel, hard alloy, etc. are used after heat treatment.

A first mechanical seal 1A is arranged on one side of the rotary seal ring 2. The first mechanical seal 1A includes a first stationary seal ring 10A and a first seal surface 3A on one side of the rotary seal ring 2. The first stationary sealing ring 10A, which is an annular body, is provided with a first relative sealing surface 11A that is in close contact with the first sealing surface 3A. The sliding surface of the first stationary seal ring 10A is axially movably fitted to the outer peripheral fitting surface of the holding portion 61 of the housing 60. Further, a step portion for the O-ring is formed on the sliding surface of the first stationary seal ring 10A, and this step portion and the housing 6
An O-ring 12 is provided between the step of the fitting surface of 0 and the step of the fitting surface of the holding portion 61 by the O-ring 12. It is sealed.

A housing 6 is provided on the first stationary seal ring 10A.
There is provided a recess 13 that locks with the fixed stop pin 63 of 0, and the recess 13 and the lock pin 63 are locked and held so that the first stationary seal ring 10A does not rotate. Further, the first stationary seal ring 10A includes the coil spring 14
Is pressed so that the first relative sealing surface 11A is in pressure contact. This coil spring 14 is used as the first stationary seal ring 1.
A plurality of them are provided at equal intervals along the circumferential direction of 0A. First
The stationary sealing ring 10A is made of carbon, silicon carbide, ceramic, super steel alloy, or the like. Then, preferably, the first relative sealing surface 11A projects so that the sliding contact area becomes small.

A second mechanical seal 1B is provided on the second seal surface 3B side of the rotary seal ring 2. This second mechanical seal 1B is also the second stationary seal ring 10B.
And the other second sealing surface 3B of the rotary seal ring 2. Second stationary seal ring 10B forming an annular body
Is formed in a shape substantially similar to that of the first stationary seal ring 10A. The sliding surface of the second stationary sealing ring 10B is movably held by the fitting surface of the second holding portion 65 of the housing 60, and the first stationary sealing ring 10A is also provided.
It is pressed by the coil spring 14 similarly to. Other configurations are almost the same as those of the first stationary seal ring 10A. Since the first stationary seal ring 10A and the second stationary seal ring 10B have substantially the same structure, the component structure is easy and the assembly is easy, so that the mechanical seal device 1 is inexpensive. You can

The mechanical seal device 1 thus constructed is arranged in the fluid chamber 62 of the housing 60 and seals the sealed fluid in the apparatus H. At the same time, the mechanical seal device 1 is cooled, and fluid inflow / outflow passages are provided so as to communicate with the fluid chamber 62 of the housing 60 in order to assist the sealing ability of the sealing surfaces to be joined. Specifically, the first inflow passage 70 is provided on the first mechanical seal 1A side of the housing 60, and the fluid that has flowed into the first inflow passage 70 cools the first mechanical seal 1A while rotating. It flows out from an outflow passage 75 provided outside the sealing ring 2. Similarly, housing 6
No. 0 second mechanical seal 1B side also has a second inflow passage 71
The fluid flowing in from the second inflow passage 71 flows out through the outflow passage 75 while cooling the second mechanical seal 1B in the same manner.

Further, by interposing a fluid in the fluid chamber 62 of the housing 60, it becomes possible to effectively seal the sealed fluid in the equipment H. In particular, if the pressure in the fluid chamber is set to be slightly higher than the pressure of the sealed fluid, this pressure can cooperate with the mechanical seal device 1 to effectively seal the sealed fluid. Further, even when the mechanical seal device 1 is used in a boiler pump or the like and the fluid to be sealed is at high temperature, the mechanical seal device 1 is cooled by flowing fresh water into the fluid chamber 62, and the mechanical seal is generated by the fluid in the fluid chamber. In cooperation with the device 1, it is possible to effectively seal the fluid to be sealed.

FIG. 2 shows a mechanical seal device 1 according to a second embodiment of the present invention. FIG. 1 is a sectional view showing the mechanical seal device 1 attached to one location of a rotary joint, but a plurality of mechanical seal devices 1 (not shown) are arranged in parallel to the rotary shaft 50 in the axial direction. .

Although not shown in FIG. 2, a polishing liquid supply device, a pure water supply device, and a vacuum device are arranged as fluid supply devices for supplying fluid to the rotary joint B. The first pipe communicates with the inflow passage 41 of the rotary joint B so that the fluid can be supplied from these polishing liquid supply device, pure water supply device, and vacuum device. Then, the fluid supplied from these devices flows into the inflow passage 41 of the rotary joint B and reaches the first fluid passage 59 of the rotary shaft 50, and the first fluid passage 59.
Is supplied to a polishing device (not shown). Further, from the pure water supply device, the rotary joint B is connected through the second pipe.
Of the second mechanical seal 1B, the sliding seal surfaces 3B and 11B of the second mechanical seal 1B are cooled by the pure water flowing from the pure water supply device. Further, the first mechanical seal 1A is similarly cooled by the pure water supplied from the first supply passage 42A.

In this rotary joint B, a fluid chamber 62 is provided on the inner peripheral surface of the housing 60. The inner peripheral surface of the housing 60 is fitted to the rotary shaft 50 which is arranged so as to be rotatable and whose relative movement in the axial direction is blocked and provided with the outer peripheral surface 56. A pair of mechanical seals 1A and 1B in the axial direction (vertical direction) are arranged in a fluid chamber 62 between the inner peripheral surface of the housing 60 and the outer peripheral surface 56 of the rotary shaft 50 to form the mechanical seal device 1.

A first fluid passage 59 is formed in the rotary shaft 50 so as to have an L-shaped cross section in the axial and radial directions. A sleeve 52 is fitted and fixed to the rotary shaft 50. Two annular grooves are formed on the inner peripheral surface of the sleeve 52, and O-rings are provided on both sides of the annular groove to seal the fluid flowing through the annular groove. The rotary seal ring 2 is fitted on the outer peripheral surface of the sleeve 52. The rotary seal ring 2 is provided with a first seal surface 3A and a second seal surface 3B on both side surfaces. Further, a second fluid passage 7 and a second engagement hole 4 are provided in a penetrating state in the radial direction of the rotary seal ring 2. The rotary seal ring 2 is attached to the sleeve 52.
O-rings are attached to both sides of the second fluid passage 7 and the second engagement hole 4 in the axial direction while they are fitted to each other so that the fluids from the second fluid passage 7 and the first engagement hole 53 are sealed by the rotary seal ring. 2 and sleeve 5
Seals from leaking between two mating parts. The material of the rotary seal ring 2 is the same as that of the rotary seal ring 2 shown in FIG.

The rotary seal ring 2 is integrally connected to the sleeve 52 by a drive pin 6. The head 6A of the drive pin 6 is held between the rotary shaft 50 and the bottom surface of the annular groove of the sleeve 52 to prevent the drive pin 6 from coming out. The pin portion 6B of the drive pin 6 is fitted in the first engaging hole 53 of the sleeve 52 and the second engaging hole 4 of the rotary seal ring 2 in a penetrating state. Then, the rotary seal ring 2 rotates integrally with the rotary shaft 50. The drive pin 6 has a structure similar to that shown in FIG. A plurality of drive pins 6 are provided in the circumferential direction according to the diameter of the rotary seal ring 2 to strongly hold the rotary seal ring 2 in the circumferential direction. At the same time, the rotary seal ring 2 is fitted and held in the second engagement hole 4 so as not to be deformed. or,
The drive pin 6 is heat-treated to improve its strength. For this reason, the drive pin 6 can be formed to have a small diameter, and the rotary seal ring 2 is also formed to have a small axial width to be small in size.

A first stationary seal ring 10A having a first relative seal surface 11A in close contact with the first seal surface 3A is arranged on the first seal surface 3A side of the rotary seal ring 2. or,
The second stationary seal ring 10 is provided with a second relative seal surface 11B that is in close contact with the second seal surface 3B on the second seal surface 3B side.
B is arranged. The first stationary seal ring 10A and the second stationary seal ring 10B are formed on the tapered surface 16 whose outer peripheral surface is in pressure contact with the O-ring, and the inner peripheral surface 17 thereof.
A gap K is formed with respect to the sleeve 52. Cold water is allowed to flow into the gap K to cool the sliding surface of the second seal surface 3B. Since the first stationary seal ring 10A and the second stationary seal ring 10B are formed in substantially the same shape, they can be arranged symmetrically. Therefore, the stationary seal ring 10 can be easily processed and the number of parts can be reduced. Furthermore, the assembly is easy. Since the whole is compact, the rotary joint B can also be made small.
As a result, the overall cost can be reduced.

The first stationary seal ring 10A and the second stationary seal ring 10B are provided with a tapered surface 16 on their outer peripheral surfaces, and the housing 60 facing the tapered surface 16 is formed.
Also, a tapered surface 18 is formed. This taper surface 1
The space between 6 and 18 is configured to be narrowed toward the center of the first stationary seal ring 10A and the second stationary seal ring 10B, and the first O-ring 15A serves to reduce the gap between the first stationary seal ring 10A and the first stationary seal ring 10A. The first relative seal surface 11A is elastically pressed against the first seal surface 3A. Further, the second O-ring 15B elastically presses the second relative sealing surface 11B of the second stationary sealing ring 10B against the second sealing surface 3B. And
Each O-ring 15 allows the stationary seal ring 10 and the housing 6
While sealing between the taper surfaces 16 and 18 with 0, each stationary seal ring 10 is elastically pressed in a direction opposite to each other. For this reason, a coil spring for pressing the stationary seal ring 10 is not required, so that the number of parts can be reduced. Further, it becomes possible to seal the fluid containing the slurry without any problem.

The mechanical seal device 1 constructed as described above seals the liquid supplied from the inflow passage 41 and containing the abrasive and the like, and the intermittent gas and vacuum state. The second sealing hole 2 of the rotary seal ring 2 fits into the pin portion 6B of the drive pin 6 fixed to the sleeve 52 that rotates integrally with the rotary shaft 50.
It is possible to maintain the free state without receiving any external pressure. In addition, since the force from the drive pin 6 is received only in the circumferential direction even during the rotation, the rotating sealing ring 2 is not distorted. And the rotary seal ring 2 is
The first stationary seal ring 10A and the second stationary seal ring 10B are pressed against each other from both sides with substantially the same force. Therefore, the first relative seal surface 11A can come into close contact with the first seal surface 3A and the first relative seal surface 11B can come into close contact with the second seal surface 3B of the rotary seal ring 2.

Further, since the rotary seal ring 2 is fixed only by the drive pin 6, the rotary seal ring 2 can be made compact both in the axial direction and in the radial direction. Furthermore, since the stationary seal ring 10 can be made smaller in size than the rotary seal ring 2, it can be made compact in relation to the combination thereof. Moreover, the stationary seal ring 10
Since it can be configured symmetrically, it requires only one part, and the number of parts is reduced, resulting in mass production.

FIG. 3 shows a mechanical seal device 1 according to a third embodiment of the present invention. The mechanical seal device 1 of FIG. 3 has almost the same configuration as the mechanical seal device 1 of FIG. The difference is that the drive pin 6 has no head portion 6A and is formed only on the pin portion 6B. Then, the drive pin 6 is fitted into the engagement holes 4 and 53, held between the rotary shaft 50 and the reinforcing ring 5 fitted to the outer peripheral surface of the rotary seal ring 2, and is pulled out from the rotary seal ring 2. It was designed so that it would not exist. Since the reinforcing ring 5 reinforces the rotary seal ring 2 from the outer peripheral side, any material such as ceramic, carbon, or any material that is excellent as a sliding material can be used.

FIG. 4 shows a mechanical seal device 1 showing a fourth embodiment of the present invention. The structure of the mechanical seal device 1 of FIG. 4 is almost the same as that of FIG. 2 is different from the mechanical seal device 1 shown in FIG. 2 in that the drive pin 6 is formed on a cylindrical head portion 6A, and the pin portion 6B has a rubber tube integrally joined to the outer peripheral surface of the pin. The head portion 6A is fitted in the first engagement hole 53 of the sleeve 52, and the pin portion 6B is fitted in the second engagement hole 4 of the rotary seal ring 2. Since the head portion 6A of the drive pin 6 is formed larger than the diameter of the second engagement hole 4, the drive pin 6 does not come out of the rotary seal ring 2. Since the rotary seal ring 2 is held by the pin portion 6B provided with the rubber tube, it is possible to hold the seal surfaces 3A and 3B so as to be slightly elastically deformable with respect to the relative seal surfaces 11A and 11B. Become.

[0042]

The mechanical seal device according to the present invention has the following excellent effects.

According to the mechanical seal device of the invention of claim 1, the rotary seal ring can be easily attached to the rotary shaft by the drive pin through the engaging hole.
Moreover, since the rotary seal ring is fitted and held in the drive pin by the engagement hole, the seal surface does not receive external pressure due to the mounting state, so the flatness of the seal surface is maintained and the seal surface is in close contact with the relative seal surface. It exerts the effect of preventing uneven wear while exhibiting the sealing ability. Further, since the rotary seal ring is held only by the drive pin, the rotary seal ring can be formed in an arbitrary size both in the radial direction and the axial direction, and the mechanical seal can be downsized as a whole. Further, since the rotating seal ring is provided with through holes such as engaging holes, fluid is present in the engaging holes to cool the rotating seal ring to prevent thermal deformation of the sealing surface of the rotating seal ring. Has the effect of preventing.

According to another aspect of the mechanical seal device of the present invention, the head portion of the drive pin is formed larger than the pin portion, and the drive pin is configured as a retaining means for preventing slipping between the rotary seal ring and the rotary shaft. Therefore, if the drive pin is fitted into the engaging hole and the sleeve is inserted into the rotary shaft before inserting the sleeve into the rotary shaft, the head of the drive pin is retained by the retainer between the rotary shaft and the sleeve. It Therefore, there is an effect that the assembly of the rotary seal ring is extremely simple. The rotary sealing ring is held by the drive pin through the engagement hole so as to rotate integrally with the rotary shaft, and the sealing surface is in close contact with the relative sealing surface of the stationary sealing ring on the same plane. It has the effect of being held in a state. In addition, if the sleeve is pulled out from the rotary shaft, the drive pin is easily separated from the rotary seal ring, so that the rotary seal ring can be replaced with a new rotary seal ring. Since the rotation seal ring can be made smaller by making the drive pin smaller, the rotation seal ring can be made smaller and the mechanical seal can be made smaller.

According to the mechanical seal device of the third aspect of the present invention, since the rotary seal ring can be reinforced by the reinforcing ring fitted to the outer periphery of the rotary seal ring, it is easily cracked by ceramics or the like, but is resistant. It is possible to use a material having wear resistance and heat resistance. And
When the drive pin is fitted into the engagement hole, the drive pin is retained at one end between the rotary shaft and the reinforcing ring so that the drive pin rotates the rotary seal ring together with the rotary shaft. Has the effect of being retained by. Since the drive pin is a cylindrical pin, the rotation sealing ring can be downsized by reducing the diameter. In addition, when mounting the rotary seal ring, the drive pin is inserted into the engagement hole and the sleeve is inserted into the rotary shaft, so that the assembly of the rotary seal ring is completed.

[Brief description of drawings]

FIG. 1 is a half sectional view of a mechanical seal device according to a first embodiment of the present invention.

FIG. 2 is a sectional view of a mechanical seal device according to a second embodiment of the invention.

FIG. 3 is a half sectional view of a mechanical seal device according to a third embodiment of the present invention.

FIG. 4 is a sectional view of a mechanical seal device according to a fourth embodiment of the present invention.

FIG. 5 is a half cross-sectional view of a conventional mechanical seal device.

6 is a half sectional view of the rotary seal ring of FIG.

FIG. 7 is a cross-sectional view of another conventional rotary joint.

[Explanation of symbols]

1 Mechanical seal device 1A 1st mechanical seal 1B 2nd mechanical seal 2 rotation seal ring 3 Sealing surface 3A 1st sealing surface 3B Second sealing surface 4 Second engagement hole 5 Reinforcement ring 6 drive pins 6A head 6B pin part 7 Second fluid passage 10 Stationary sealed ring 11 Relative sealing surface 11A 1st relative sealing surface 11B Second relative sealing surface 12 O-ring 13 recess 14 coil spring 15A 1st O-ring 15B 2nd O-ring 16 Tapered surface 17 Inner surface 18 Tapered surface 41 Inflow passage 42A First supply passage 42B Second supply passage 50 rotation axis 51 key 52 Sleeve 53 First engagement hole 53A counterbore 54 annular groove 55 O-ring 56 outer peripheral surface 57 annular groove 58 O-ring 59 First fluid passage 60 housing 61 First holding unit 62 Fluid chamber 63 stop pin 70 First inflow passage 71 Second inflow passage 75 Outflow passage H inside equipment

Claims (3)

[Claims] 1. A mechanical seal device for sealing between a rotary shaft and a seal housing, comprising: a sleeve fitted to the rotary shaft; and a rotary seal ring fitted to the sleeve and having a sealing surface on a side surface. And a stationary seal ring elastically held in the seal housing with a relative seal surface that is in close contact with the seal surface of the rotary seal ring, wherein the rotary seal ring and the sleeve are It has engaging holes penetrating each other on the surfaces to be fitted with each other, has a pin portion that fits into both of the engaging holes, and has a drive pin held by locking means for preventing coming out from the engaging holes. Mechanical seal device characterized by 2. The locking means has a head portion thicker than a pin portion at one end, and the head portion is retained by a retaining member between the rotary shaft and the sleeve. 1
Mechanical seal device described in. 3. The both ends of the drive pin are retained by the locking means by a reinforcing ring fitted to the outer periphery of the rotary sealing ring and the rotary shaft so as to prevent the drive pin from coming off. Mechanical seal device described in.