KR101301222B1 - Isolator seal - Google Patents

Abstract

The present invention relates to an insulator seal, which includes a stator member positioned on a stator of a rotating apparatus, a rotor member located on a rotating shaft of the rotating apparatus, and the stator member and the rotor member have an adjacent surface. And a static interruption device having an elastic annular sealing member that connects both adjacent surfaces when the rotor is stopped and separates one or more stator adjacent surfaces and the rotor adjacent surface when the rotor is moved, with at least one An insulator seal inclined with respect to the longitudinal inlet at an angle of at least 90 degrees or less, a stator member located on the stator of the rotating device, and a rotor member located on the rotating shaft of the rotating device, The stator member and the rotor member have an adjacent surface, and the auxiliary member presses the annular member of elasticity when the rotor member is stopped. An auxiliary position movable between the first position to be engaged with the contact surfaces and a second position where the elastic annular member is reduced in pressure as the rotor moves so that the elastic annular member separates the surface of the one or more rotors from the surface of the stator An insulator sealing portion having a static interruption device including a member and an annular sealing member of elasticity.

Description

Insulator Seal {ISOLATOR SEAL}

TECHNICAL FIELD The present invention relates to use in insulator seals and rotating devices, and more particularly, to a device for preventing a fluid or a solid from entering or exiting an empty space, thereby reducing the life of the device. This device is often referred to as bearing protector, bearing seal, or bearing insulator. However, the use of the rotary seal goes beyond the protection of the bearing in the rotating device. Thus, while referring to the bearing protector below, it should be appreciated that the seal of the present invention is used in a wider range.

The purpose of the bearing protector is to prevent fluids, solids and debris from entering the bearing chamber. At the same time, bearing protectors are mounted to prevent the outflow of fluids or solids from the bearing chamber. Essentially, the purpose is to prevent the bearings from breaking prematurely.

Bearing protectors generally fall into two categories: repeller or labyrinth bearing protectors and mechanically sealed bearing protectors. A mechanically sealed bearing protector filed together is shown in International Publication No. 2004/005770, which generally shows a contact bearing protector.

Maze bearing protectors typically include components axially fixed to the rotating device and mounted to be rotated about an axis. For example, the shaft consists of a pump or other part of a rotating device. The protection device has a static member fixed axially and attached or mounted to the stop of the device.

The rotating member is typically located adjacent and has a complex outer profile that is very close radially and axially to the complex inner profile of the stop. In theory, these complex profiles together provide a tortuous passageway that prevents the passage of unwanted materials or fluids.

Labyrinth bearing protectors generally operate only while the device is in operation. This is because the structure relies on the reverse rotation of the rotating member and the fixing member to create centrifugal force, which prevents the fluid from spreading radially between the members.

When the device is stationary, the complex maze structure cannot maintain a fluid level at a radial level higher than the inlet position of the protective device in horizontal application.

In addition, in many industries, water spray, steam, and external contaminants are directed to bearing protection when the device is stationary. Conventional maze structures do not prevent such contaminants from entering the bearing chamber.

In addition, the aeration of the bearing chamber is another problem in the industry. During operation, the viscous fluid and air in the bearing chamber warm and expand. In a conventional maze-shaped seal, this expansion draws air through the maze and out of the bearing chamber. When the device stops, the bearing chamber cools down and the internal air contracts, picking up moist air through the maze array and sending it to the bearing chamber. This is called "breathing".

Mechanical sealed bearing protectors can overcome the fixed limitations of the maze structure. However, this device may also cause other problems such as excessive heat generation when high shaft speeds are applied or when lubrication is minimal or lacking in sealing surfaces. Therefore, the use of mechanical sealed bearing protection is limited.

When the device is stationary while the chamber is "breeding" and the amount of air molecules entering the bearing chamber can be reduced or blocked, a non-contact maze-type sealed bearing protection device capable of sealing the fluid is required.

It would be desirable if the non-contact maze-shaped seal could block the fluid regardless of the direction of shaft rotation. This reduces the likelihood and effectiveness of installation errors.

It is more desirable if the non-contact maze seal is integrated with two repulsion devices, one designed to prevent fluid from leaving the bearing chamber and the other designed to prevent fluid from entering the bearing chamber.

In addition, ease of installation is important in all bearing protector designs. It is preferable that the non-contact maze-shaped seal is compressed in the axial direction so that the lip seal is inserted into the space occupied in advance and supplied to the integrated cartridge without the installation clip.

U.S. Patent No. 5378000 (Orowski) shows a maze-shaped cartridge structure in which the rotor and stator are locked together in an axial direction by a rigid and deformable annular seal or elastomer. The elastomer is locked between two rotating rectangular cavities, as shown in Figures 3 and 4 of the Orowski publication. The elastomer is subjected to frictional resistance, which is less affected by the stator and more affected by the rotor. Therefore, Orowski's elastomer is damaged from friction between two counter rotating bodies. This wear worsens as follows.

The acute angle between the surface 23 and the surface 22b of the rotor 14 and the 90 degree angles of the three corner portions of the groove portion 21 and the groove portion 22 are in contact with the elastomer 20. Orowski relies on each of these relatively angled surfaces of the four points in contact with the elastomer to maintain the axial proximity between the rotor and the stator. All commercially available elastomers have cross-sectional size tolerances. This is generally a tolerance of +/- 3% of the nominal diameter. Therefore, the magnitude of the frictional resistance defined by Orowski is very variable as long as this elastomer tolerance, so that the grooves 21 and 22 also have manufacturing width tolerances.

During assembly of the seal to the device, the device is pulled axially, pushed and moved to the last travel position. The axial movement is in particular due to the frictional forces generated from the rotating elastomer 15 and the shaft 10. This axial movement puts the elastomer 20 under shear stress because the only element that axially locks the rotor and stator together is the elastomer. Therefore, the frictional resistance between the elastomer and the groove 21 and the groove 22 is likely to change during assembly.

All of these facts quickly increase and affect the wear of the elastomer 20 and limit the useful sealing life of the elastomer to the entry and exit of the material.

According to a first aspect of the invention, an insulator seal is provided, which comprises a stator member located on the stator of the rotating device, and a rotor member located on the rotating shaft of the rotating device, wherein the stator member and the rotor member A static blocker having an adjacent surface and having an elastic annular sealing member that connects two adjacent surfaces when the rotor stops and separates one or more rotor adjacent and stator adjacent surfaces as the rotor moves With the device, at least one of said surfaces is inclined with respect to the longitudinal axis above 90 degrees or below.

Preferably, the inclination of the at least one surface with respect to the longitudinal direction is between 5 degrees and 175 degrees, more preferably between 10 degrees and 80 degrees, or between 100 degrees and 120 degrees, most preferably 30 degrees Between 60 degrees or between 120 and 150 degrees. In certain embodiments of the present invention the slope is approximately 45 degrees.

According to a second aspect of the invention, an insulator seal is provided, comprising: a stator member positioned at a stator of a rotating device; A rotor member positioned on a rotating shaft of the rotating apparatus, the stator member and the rotor member having an adjacent surface, and the auxiliary member presses the elastic annular sealing member when the rotor member is stopped, thereby adjoining the adjacent surface. Auxiliary member movable between the first position to be engaged with the wheel and the second position at which the elastic annular member is reduced in pressure as the rotor moves so that the elastic annular member separates the surface of the at least one rotor from the surface of the stator. And a static blocking device having an elastic annular sealing member.

Preferably, the elastic sealing member is in the shape of a donut.

Preferably, the seal includes a labyrinth seal formed between the rotor member and the stator member.

Preferably the seal comprises at least one two-way repulsive pumping device.

Preferably the surfaces of the rotor member and the stator member are inclined at least 90 degrees or less with respect to the longitudinal axis.

Preferably the rotor member and the stator member are axially separated but constrained relative to relative axial movement by at least one radially extending member formed in one of the rotor member and the stator member.

In particular, the rotor and stator member are axially constrained by at least two radially extending members.

Preferably, the stator member has at least one connecting hole extending between the inner surface of the stator member and the outer surface of the stator member. More preferably, the connecting hole is adjacent to the radially extending member provided in the rotor member. Preferably the inner surface of the stator member is eccentric with respect to the rotor member and eccentric with respect to the rotating shaft during use.

Preferably the connecting holes are located at the lowest radial in the seal during use.

Preferably, the stator member has an outermost surface and a groove portion extending radially inward at a generally innermost surface of the eccentric, and the radially extending groove portion is a radially outermost portion of the innermost surface. Extending to a point to form a connection hole connecting the innermost and outermost portions of the stator member.

Preferably, the surface of the rotor member and the stator member together form a "v" shape. In particular, the resilient annular member is held in the " v " shaped portion in a free state at a radial position that is larger than the nominal radial position of the resilient annular sealing member.

In particular, the rotor member has at least two reaction pumps separated in the axial direction.

In addition, the rotor member and the stator member are each integrally formed.

In particular, the rotor member and the stator member are axially constrained with respect to each other by at least one radially extending shoulder portion, the shoulder portion extending from the rotor member, the stator member or a combination of the members.

In one preferred embodiment, the rotor member has two axially connected members and the stator member is integral. The first rotor member part is located radially to the second rotor member part, the two of which are connected by mechanical, chemical or other fastening means to create a permanent or temporary attachment.

Preferably the seal of the invention comprises a stator housing having at least one radially outwardly positioned positioning element positioned in the device chamber. The positioning element is located adjacent to the radially extending groove and has at least one elastomeric member sealing the housing to the device chamber. The housing also has at least one radially extending outer surface axially in contact with the device chamber.

The rotor also includes at least one rebound pumping device having at least one radially inwardly extending feature located around the rotor.

Preferably, the rotor comprises at least two reaction pumps that move axially.

The repulsive pumping device has a continuous and generally concentric rotor surface that generally corresponds to a stator surface of different center.

The repulsive pumping device also has at least one radially inwardly extending shape located around the rotor.

The rotor includes at least one rebound pumping device having at least one radially inwardly extending feature located at the periphery of the rotor, the feature being adjacent to the radially oblique inner surface of the stator.

The rotor also includes at least two reaction pumps that move in the axial direction. Each repulsive pumping device has at least one radially inwardly extending feature located near the rotor adjacent the stator inner surface that is generally radially inclined.

Preferably, the stator housing comprises at least one internal shape, which has a central part out of the central part of the shaft. An eccentric inner shape of the stator housing is adjacent to at least one repulsive pumping device of the rotor.

The stator housing includes at least one radially connecting portion that connects the innermost surface of the housing to the outermost surface of the housing. The radially connected feature or outlet hole is adjacent to at least one reaction pump.

The stator housing includes two axially connected members and the rotor is integral.

One stator is located radially to the second stator, the two being connected by mechanical, chemical or other fastening means to form a permanent or temporary attachment.

The radially outer stator is integrated in the radially extending shape at the outermost surface. The radially extending portion is adjacent to the radial position of the two rotor members.

The rotor comprises at least one radially extending shape on the outer surface, which is located very close to the inside of the stator.

In an embodiment of the labyrinth seal according to the invention, at least one rotary member and one stop member can be mechanically attached to the rotary device.

The seal of the present invention includes a stator housing having at least one axial hole or slot for receiving studs or bolts in the rotary device, such that the housing of the mechanical seal can be secured to the rotary device.

Preferably, the first housing stator is located radially to the second housing stator, the first housing stator is axially indirectly connected to the shaft via the rotor, and the second housing stator is fixed to the device. It is directly connected to the housing. The first housing stator is axially slid relative to the second housing stator. In particular, the axial movement is mechanically limited, thus continuing the cartridge method.

In particular, the first housing stator is positioned radially and axially to the second housing stator, the housing stator is indirectly connected to the shaft indirectly via the rotor, and the second housing stator is connected to the stationary housing of the device. Are connected directly. The first housing stator is to be connected at an angle to the second housing stator. In particular, the oblique movement is mechanically limited, thus continuing the cartridge method.

In an embodiment of the labyrinth seal according to the invention, at least one rotor member and one stator member are divided axially for attachment to the device. The divided elements are mechanically fixed together radially after being installed in the device. The pre-dividing structure also has at least one radially divided elastomer, which is installed near the shaft and then joined by permanent means.

The present invention provides a bearing protector in the form of a non-contact labyrinth type seal.

Reference is made here to elastic sealing members in the form of O-rings or elastomers forming a static barrier. All elastomers or rigid deformable materials are suitable. The sealing member shown in the figure may have a circular cross section, but they may have other shapes, including having a flat surface or a composite of a circular surface.

The accompanying drawings are as follows.

1 is a longitudinal cross-sectional view of one embodiment of a maze-shaped sealed bearing protector of the present invention mounted to a shaft.

FIG. 2A is a cross-sectional view of the pumping rebounder corresponding to FIG. 1 and along line A-A. FIG.

FIG. 2B corresponds to FIG. 2A and is an enlarged view of the drainage hole.

Fig. 2C corresponds to Fig. 2A and shows another structure of the drainage hole.

Figure 2d is another structure of the drainage hole.

FIG. 2E corresponds to FIG. 1 and is a sectional view of the pumping rebounder according to line B-B.

FIG. 2F corresponds to FIG. 2E and is a plan view along line C-C.

3 is an enlarged view of the longitudinal section corresponding to FIG.

4a corresponds to FIG. 1 and is an exploded view.

4B corresponds to FIG. 1 and is a partial cross-sectional view.

5 is an enlarged view of the longitudinal section corresponding to FIG.

FIG. 6A is an enlarged partial sectional view corresponding to FIG. 1 showing the blocking elastomer in a stationary state. FIG.

FIG. 6B is an enlarged partial sectional view corresponding to FIG. 6A, showing the blocking elastomer in a moving state. FIG.

7 is a longitudinal cross-sectional view of another embodiment of the present invention.

8 is a longitudinal cross-sectional view of another embodiment of the present invention.

9A is a longitudinal cross-sectional view of another embodiment of the present invention.

FIG. 9B is a longitudinal cross-sectional view of the embodiment shown in FIG. 9A, showing the peripheral connection of the stator. FIG.

Figure 10 is a longitudinal cross section of another embodiment of the present invention.

11A is a longitudinal cross-sectional view of another embodiment of the present invention.

11B is a longitudinal cross-sectional view of another embodiment of the present invention.

12A is an exploded perspective view of another embodiment of the present invention, which is a maze-shaped seal separated in the longitudinal direction.

Fig. 12B is an enlarged view of the axially separated end of the embodiment shown in Fig. 12A.

FIG. 12C shows a longitudinal partial cross-sectional view of the embodiment shown in FIG. 12 and includes a circular locking ring.

FIG. 12D shows a longitudinal partial section of the separated elastomer of the embodiment shown in FIG. 12A.

12E is a longitudinal partial cross-sectional view of another embodiment of the present invention, showing the screw of the present invention.

12F is a partial cross-sectional view of another embodiment of the present invention, showing the screw used in the present invention in a situation where it is not secured in an axially separated assembly.

FIG. 12G is a partial cross-sectional view of the embodiment shown in FIG. 12F of the present invention, showing the screw of the present invention in a fixed position in an axially separated assembly.

Figure 13 shows another embodiment of the present invention in the form of a bearing seal fitted to the outerboard end of the cartridge seal.

Figure 14 shows another embodiment of the present invention in the form of a bearing seal fixed to a rotating shaft.

Figure 15 shows another embodiment of the present invention in the form of an axial compression labyrinth seal comprising one repellent pumping device towards the atmosphere.

Figure 16 shows another embodiment of the present invention in the form of an axial compression maze seal which includes a repulsion pumping device and a shutoff sealing device towards the atmosphere.

Figure 17 shows another embodiment of the present invention in the form of an axial compression labyrinth seal comprising a barrier seal.

FIG. 18 is a longitudinal cross-sectional view of another embodiment of the present invention in the form of a maze-shaped sealed bearing protector mounted on a shaft in a twentieth embodiment of the present invention.

19 is an enlarged partial sectional view corresponding to FIG.

Fig. 20A is an enlarged partial sectional view of another embodiment of the present invention, showing the seal in the stationary state.

FIG. 20B is an enlarged partial sectional view corresponding to FIG. 20A and showing the seal in a moving state. FIG.

Figure 21A shows an enlarged partial cross section of another embodiment of the present invention.

Figure 21B shows an enlarged partial cross section of another embodiment of the present invention.

Figure 21C shows an enlarged partial cross section of another embodiment of the present invention.

Figure 21D shows an enlarged partial cross section of another embodiment of the present invention.

Figure 21E shows an enlarged partial cross section of another embodiment of the present invention.

Figure 21f shows an enlarged partial cross section of another embodiment of the present invention.

Figure 21G shows an enlarged partial cross section of another embodiment of the present invention.

Fig. 22 is a cross-sectional view of yet another embodiment of the present invention, showing the structure of two parts constrained axially by a radially extending circlip.

FIG. 23 corresponds to FIG. 22 and shows an enlarged partial cross section of this embodiment.

Figure 24 shows an enlarged partial cross section of another embodiment of the present invention.

Figure 25 shows an enlarged partial sectional view of yet another embodiment of the present invention, showing ease of separation from the device.

Embodiments of the present invention will be described with reference to the accompanying drawings.

The rotary seal according to the invention is used not only when the shaft is a rotating member and the housing is a stationary member, but also vice versa, ie when the shaft is a stationary member and the housing is a rotating member.

In addition, the present invention can be implemented in both rotating and stationary structures, and is used in element sealing and cartridges with metallic elements as well as nonmetallic elements.

1 is shown a first embodiment of the present invention, in which a bearing protector assembly 10 is fitted to a part of a rotating device 11. The device comprises a rotating shaft 12 and a fixed housing 13. The fixed housing 13 typically includes a bearing but is not shown.

The area "X" at one axial end of the bearing protector assembly 10 partially includes fluid, solids, debris, or air. However, to be precise, it is referred to herein as a "product substance" to describe one medium or a mixed medium.

Another axial end region " Y " of the bearing protector assembly 10 includes, in part, fluid or solid or debris and air. However, to describe a medium or a mixed medium, it is called an "atmospheric substance."

The bearing protector assembly 10 includes a rotor assembly 16 having a first rotor member 14 and is positioned axially and radially in a second rotor member 15. The rotor assembly 16 is located adjacent to the stator member 17.

The back section A-A is shown in Fig. 2A. This is the cross section of the groove 18 at the outermost radial surface of the stator 17.

The back section B-B is shown in Fig. 2E. This is the cross section of the groove 19 at the outermost radial surface of the stator 17.

2A, the first rotor member 14 comprises at least one radially extending feature, i. E. A slot 25. As shown in FIG. The rotor 14 is generally located concentrically on the shaft 12 and rotates on the shaft centerline 26. The stator 17 includes at least one internal shape, ie the stator pumping hole 27. The radial clearance between the outermost surface of the rotor 14 and the innermost surface of the stator pumping hole 27 provides a pumping chamber 28.

From FIG. 2A, the stator pumping hole 27 is generally eccentric with respect to the rotor 14 and the shaft 12 and has a centerline 29. The eccentric size between the rotor 14 and the stator pumping hole 27 is shown as the radial distance "Z" between the respective centerlines 26 and 29.

As a result of the eccentricity, the radial clearance between the rotor 14 and the stator pumping hole 27 is not constant around the assembly 10. As shown in Fig. 2A, the radial clearance 30 at the 12 o'clock position is smaller than the radial clearance 31 shown at the 6 o'clock position.

The fluid entering the pumping chamber 28 changes in radial clearance when transported circumferentially by the rotor slot 25. This change in radial clearance creates a change in the pressure of the fluid acting in the radial clearance. This change in fluid pressure causes the fluid to move circumferentially from the small radial clearance position 30 to the large radial clearance position 31.

2A, the outer groove 18 of the stator 17 is centered with the shaft 12. In the radially lowest position, referred to as the six o'clock position in cross section, FIG. 2A shows the radial exit of the concentric groove 18 with stator pumping holes 27. An enlarged view of the shape portion is shown in Fig. 2B. In FIG. 2B, the outlet makes a connection hole 35 between the innermost region of the stator 17 and the outermost region of the stator 17. The advantage of this automatically created connection hole 35 is that the hole is always created in the largest radial clearance position 31 independent of the device, production technology and the operator. This benefits the supplier.

FIG. 2C shows another embodiment corresponding to FIG. 2B with a stator pumping hole 27 comprising an additional radially extending inner region 36. This radially extending area creates an automatic connection hole 37, and the length of the hole 37 is more closely controlled with little change given by the natural manufacturing tolerances of the hole 27 and the groove 18. .

FIG. 2D corresponds to FIG. 2B and shows another embodiment in which the connecting hole 38 is provided by a drill hole or a processing hole extending through the stator 17. FIG.

FIG. 2E corresponds to FIG. 1 and shows an embodiment showing a repulsive pumping structure adjacent to the product material side.

2E and 1, the second rotor 15 carries at least one elongated shape portion, i.e. a hole 45. As shown in FIG. The rotor 15 is centered with the shaft 12 and rotates at the shaft center line 46. The stator 17 includes at least one internal shape, ie the stator pumping hole 47. The radial clearance between the outermost surface of the rotor 15 and the innermost surface of the stator pumping hole 47 is a pumping chamber 48.

The stator pumping hole 47 is generally eccentric with respect to the rotor 15 and the shaft 12 and has a centerline 49. The eccentric size between the rotor 15 and the stator pumping hole 47 is represented by the radial distance "W" between the respective centerlines 46 and 49.

As a result of this eccentricity, the radial clearance between the rotor 15 and the stator pumping hole 47 is not constant around the assembly 10. As shown in FIG. 2E, the radial clearance 50 at the 12 o'clock position is generally smaller than the radial clearance 51 at the 6 o'clock position.

Again, the fluid entering the pumping chamber 48 tends to change in radial clearance when transported by the stator aperture 45. This change in the radial clearance creates a change in the fluid operating in the radial clearance. This change in fluid pressure causes circumferential fluid movement from the small radial clearance position 50 to the large radial clearance position 51.

Rotor holes or serrated 45 extending radially and discontinuous at the outer surface of the rotor are unnecessary to improve fluid movement. Operation of two reverse rotating surfaces, not centered, is often sufficient to pump the fluid.

Equally, the two reverse rotating surfaces of the concentrically aligned rotor, including radially extending and discontinuous rotor holes or serrations, are sufficient to pump the fluid.

2E and 1, the outer groove 19 in the stator 17 is generally centered with the shaft 12. In the radially lowest position, referred to as the six o'clock position in cross section, FIG. 2E shows the radial connection outlet 55 of the concentric groove 19 with the stator pumping hole 47. This is shown in more detail in FIG. 2F and is a plan view along section C-C in FIG. 2E. This outlet makes a connection hole 55 between the innermost and outermost region of the stator 17. The combination of the outer concentric groove 19 and the eccentric stator pumping hole 47 makes an automatic connection hole 55 in the large radial clearance position 51.

Obviously, the position of the connection hole 55 can be in any position relative to changing the radial clearance between the rotor and the stator. For example, in some applications, the connecting hole is adapted to a position adjacent to the position of the smallest radial clearance between the stator and the rotor, which corresponds to the position of the highest fluid pressure differential, so that fluid is drawn out of the connecting hole. Use relatively high fluid pressure to come out.

The skilled person will appreciate that one or two pumping systems can be used. Preferably, the dual rebound pumping system has a repeller on the air side and a repeller on the product side so that the inflow and outflow of material is repelled from both sides of the assembly 10.

The large radial clearances 31 and 51 and the connection holes 37 and 55, if necessary, provide for the machined angular displacement between the eccentric pumping holes at the air end and the product end of the stator 17. It can be positioned in any angular relationship to each other by simply changing.

The number and size of the pumping holes 25 and 45 and the respective angular orientations can be changed to suit the purpose of sealing.

Preferably, the repulsive pumping structures on both sides of the present invention should be approximately balanced and identical to each other so that inflow and outflow are not improved in any particular method.

3, the bearing protector is a cartridge unit and is provided without any setting device. Preferably the rotor assembly 60 has two axially coupled rotor members 14, 15. That is, the first rotor 14 is located radially in the second rotor 15 at the radial position 61. The two rotors 14, 15 are compressed axially until the axial face 62 of the rotor 15 abuts the axial shoulder 63 of the rotor 14. That is, the radial position 61 is a mechanical interference fit to hold the two rotors together. Optionally, these parts can be chemically bonded with a suitable adhesive, or permanently bonded by welding or a combination thereof, thereby forming a fixed attachment.

Preferably, the radially innermost rotor 14 carries a contour 64 extending radially from the innermost surface. This feature 64 is adjacent to the radial position 61 of the two rotor members 14, 15. This contour 64 ensures that the bearing protector 10 slides on the shaft 12 without radial interference with the shaft 12, which is the radial direction between the two rotors 14, 15. It is by the interference fitting part 61.

The ends of each rotor 14, 15 are greater longitudinally outward than the innermost radial portion of the stator 17. The stator 17 is integrated.

As shown in FIG. 3, the rotor 14 carries a cavity 65 extending radially from the innermost surface. Cavity 65 includes an elastic seal 66 that seals rotor assembly 60 to shaft 12. Elastomer 66 transmits rotational drive from shaft 12 to rotor assembly 14.

The bearing protector 10 preferably comprises a stator housing 17, which has at least one radially outward device chamber position 67. The positioning portion 67 is located adjacent to the radially extending groove 68 and includes at least one elastomeric member 69 for sealing the stator 17 to the inner region of the device chamber 13. do. The stator 17 has an outer surface 70 extending in at least one radial direction, which is in axial contact with the apparatus chamber 71.

Preferably, the rotors 14 and 15 comprise at least one repulsive pumping device as mentioned above.

Preferably, the rotor comprises at least two reaction pumps axially moved. Each reaction pump has at least one radially inwardly extending shape located around the rotor.

As shown in Fig. 3, the two rotors 14, 15 carry at least one radially inner and outer circumferential castellation portion 72, 73, which is one of the rotors 14,15. Located on the outermost radial surface. The uneven portions 72 and 73 have a rectangular shape as shown, or any shape having a curved or straight surface. For example, such a shape may be trapezoidal, V-shaped, or semi-circular in cross section. As another example, it may have threads with a left thread pitch or a right thread pitch.

The radial rotor surface and the concave-convex portions 72 and 73 move in a radial direction about 0.005 " to 0.010 " to the adjacent innermost stator surfaces 74 and 75. Clearly, the radial adjacency is not limited to 0.005 "and may be larger or smaller than this value.

The innermost radial surfaces 74, 75 of the stator 17 are adjacent to the outermost radial surface of the rotor assembly 60 and may have the above-mentioned concave-convex shape. In fact, uneven coupling of the stator or rotor can be used to limit or prevent axial fluid movement.

The bearing protector 10 carries a static interrupter assembly 80 having an elastomer 81 positioned radially in a “v” shaped portion located radially inwardly of the elastomer 81. do. This " v " portion is composed of two reverse rotating surfaces, i.e., the stator surface 82 and the rotor surface 83. As shown in FIG.

The elastomer 81 is held in the "v" shape at a radial position that is somewhat larger than the nominal radial position of the elastomer 81 when in the free state. In practice, this arrangement means that the elastomer 81 acts as a radially extending means. As the elastomer 81 extends outwardly, this structure produces an inner radial force acting around the elastomer 81 to be applied to the "v" shaped portion surfaces 82 and 83. This creates a fixed seal between the rotor assembly 60 of the surfaces 82 and 83 and the stator 17. This structure will be described in more detail with respect to FIGS. 6A and 6B.

6A, the rotor assembly 60 includes a first rotor 14 and a second rotor 15. The second rotor 15 extends radially outward beyond the outer surface of the elastomer 81, the second rotor 15 carrying radially inner surfaces 90, 91. This surface 91 is inclined radially and axially.

A gap 92 exists between the inclined surface 91 and the outer surface of the elastomer 81. The gap 92 frees the elastomer 81 from external frictional resistance during the speed of the slow shaft 12.

As the shaft 12 rotates as the device starts up, the elastomer 81 is subjected to centrifugal force, which acts radially outward. Centrifugal force causes the elastomer 81 to rise from the inclined stator surface 82 and to move to the inclined surface 91 of the rotor. This is shown in Figure 6b.

The inclined surface 91 on the rotor then generally translates the radial movement of the elastomer 81 into radial and axial movement and pushes it towards the rotor space 94.

As the shaft 12 of the device stops, the outward centrifugal force acting on the elastomer 81 also stops. The natural elasticity of the elastomer 81 then forms an inward radial force, and the elastomer 81 is formed in the v-shape of each stator 17 and the rotor 14 as shown in FIG. 6A. Return to seating surfaces 82 and 83.

Elastomers 81 on the v-shaped seating surfaces 82 and 83 provide a radial barrier and are stationary to prevent the passage of fluids or solids from the atmosphere to the product or from the product to the atmosphere. Form a seal.

Radial clearance 92 may be any size. For example, it can be from 0 to 2.000 "or 50mm, or more. The radial clearance is approximately 0.010", and in some applications, the inclined surface 91 needs to compress the elastomer 81 radially inward. , "Radial clearance" is an interference fit that provides frictional resistance between the rotor surfaces 91 and 83.

The above-mentioned structure does not have any limitation of US Pat. No. 5,378,00 (Orowski). These are described below.

The v-shaped seating configuration of the present invention ensures that the elastomer 81 is not sharp or in contact with the tip of the knife, the sharp surface being able to rupture the elastomer 81 while the device is in operation or stationary. .

The v-shaped seating configuration of the present invention ensures that the production tolerances of all elastomers 81 do not affect the design. In the stationary condition, the frictional resistance to the surfaces 82 and 83 of the elastomer 81 is somewhat constant regardless of the cross-sectional size of the elastomer 81. The cross-sectional size change of all the elastomers 81 is accommodated by the rotor clearance 92 or the rotor space 94.

The v-shaped seating configuration of the invention accommodates the slight axial movement of the respective rotor 60 and stator 17 components, which takes place during the mounting of the invention to the shaft. If each axial nominal gap between the rotor 60 and the stator 17 changes, the v-shaped seating shape will open or close in the axial direction because it has two independent faces. This effect with the elastomer 81 causes the radial sealing position of the elastomer 81 to change slightly. The elastomer 81 may be seated in a radial position slightly higher than the nominal when the axial clearance is closed, or in a position slightly lower than the nominal if the axial clearance is increased. This structure ensures that the elastomer 81 is not subjected to undesirable stresses or shear stresses as a result of the axial movement.

4A is an exploded perspective view of four of the six components of the bearing protection device of FIG. During assembly of the present invention, the rotor 14 is pushed through the stator 17 until it is positioned axially. The elastomer 81 extends radially outward and is located in the v-shaped seating area, which is made by the subcomponent 100 of the rotor 14 and the stator 17. 4b shows this. When the rotor 15 is provided axially to the subassembly 100, the radially inclined surface 101 is radially located on the elastomer 81. Continued axial movement of the rotor 15 causes the inclined surface 101 to radially press the rigid and deformable elastomer 81 without damage. Therefore, the inclined surface 101 is very desirable.

5 corresponding to FIG. 3 shows a partial longitudinal cross-section of a bearing protector 103 involving an additional solid deformable member or elastomer 104. The elastomer 104 is mounted in the radial cavity 105 obtained between the stator 106 and the rotor 107, which are two reverse rotating surfaces. The elastomer 104 helps to limit the volumetric flow rate of air molecules passing through the present invention. Moreover, compared to the embodiment of FIG. 1, a supply advantage is obtained and the addition of the elastomer 104 eliminates the need to change the parts of the first embodiment.

Figure 7 shows a partial longitudinal cross section of another embodiment of the present invention. The bearing protector 109 includes a rotor assembly 110 comprising at least one rebound pumping device 111 having at least one radial extension 112 with an inclined radial route 113. And the repulsive pumping device is located on the outermost surface of the rotor assembly 110. The radially extending portion 112 is adjacent to the radially inclined inner surface 114 of the stator 115.

When the rotor assembly 110 is rotated by the shaft 116, the radially extending portion 112, in particular the radially inclined root 113, is a surface in which the atmospheric material is inclined into the stator 115. Move toward (114). The atmospheric material is moved radially outward by the centrifugal force generated by the rotation of the rotor assembly 110. When the atmospheric material is connected to the inclined surface 114 of the stator 115, its radial speed is converted to axial movement as the material moves away from the bearing protector 109.

As shown in FIG. 7, the rotor assembly 110 comprises at least two reaction pumps 111 and 117, which are moved axially. Each repulsive pumping device has at least one radially inwardly extending feature located around the rotor adjacent to the radially inclined inner surface of the stator 115.

7 shows a sloped route 113 of the feature 112 extending radially inward, the profile of the route 113 can be a combination of inclined, parallel or curved surfaces, which is a longitudinal cross section and an end face. In parallel, concave, convex, or a combination thereof.

8, the stator assembly 120 has two axially connected stator members 121, 122, which are located radially and abut in axial direction. The stator assembly 120 has two radially extending members, which support the rotor 123 axially, preferably integrally.

The stator member 121 is adjacent to the radial attachment portions of the two stators 122 and 121 and carries a shape 124 extending radially inward from the outermost radial surface. The radially extending portion 124 acts as an undercut such that the stator assembly 120 is not severely radially interfered with the device housing 125 when the stator assembly 120 is in a radial position between the two stators 122 and 121.

The stator member 121 includes a recess 126 extending radially inward from its outermost surface, which includes a rigid, variable elastic member 127 that seals the innermost surface of the device housing 125.

The stator member 122 has a radially outwardly extending feature 128, which axially positions the stator assembly 120 at the end surface of the device housing 125.

Stators 122 and 121 are connected at 129 by mechanical means such as radial interference fittings or threads. However, chemical means such as adhesives or permanent means such as welding are another example of a suitable fastening method.

The rotor 123 includes a shape 130 extending radially outward from the innermost surface and has a rigid, variable elastic member 131 that provides a peripheral seal against the outermost surface of the device shaft 132. have.

The rotor 123 has at least one radially pumping portion 133 having at least one radially extending portion, ie a hole 134 at the outermost periphery of the rotor 123.

The hole 134 and the rotor 123 operate in the cavity of the stator 122. Preferably this cavity is eccentric as mentioned above in connection with Figure 2A.

The stator 122 also carries at least one outlet hole 135 as mentioned above in connection with FIG. 2B.

The rotor 123 includes at least two reaction pumps 133 and 136 moved in the axial direction. Each repulsive pumping device has at least one radially inwardly extending shape located around the rotor adjacent to the eccentric pumping cavity on the inner surfaces of the stators 121, 122.

The rotor 123 is a block type comprising an elastomer 138 operating in a v-shaped seating area 139 having an inclined stator radial surface 140 and an inclined rotor radial surface 141. An array 137.

The rotor 123 has at least one radially extending convex portion 142, which is proximate and radially adjacent to the inner radial surfaces of the stators 122, 121.

9A, the seal of the present invention includes a stator housing 150 having a shape 151 extending radially outward. In the shape 151, the stator 150 comprises at least one axial hole or slot 152 for receiving the studs or bolts 154 in the components of the rotating device 153, the stator of the present invention 150 is mechanically rigidly mounted to the rotary device 153.

As shown in FIG. 9B, the stator housing 155 has a peripheral connection 156 for injecting or ejecting the first fluid or the second fluid into the seal 158 to enter the processing space 159. .

In connection with Figure 10, the seal of the present invention includes two axially sliding stator housings 160,161. One stator housing 160 is radially inward of the second stator housing 161, and at least one stator carries an elastomeric member 162 that slides in an axial direction, which is between two housings 160, 161. Seal around.

Preferably, the axial movement between the two stator housings is reliably limited by the radially extending features 163 and 164. In particular, the two stator housings 160,161 are reliably rotatably connected by suitable mechanical means, such as drive pins or drive lugs 165, which allow the two stators to move axially without rotating.

The outer stator housing 161 carries a radially extending feature 166, which houses the elastomeric member 167. The elastomeric member 167 seals the periphery between the stator housing 161 and the device housing 168.

The rotor 169 includes an elastomer 170, which seals the rotor 169 in a circumferential direction with respect to the device shaft 171.

Another element of the invention shown in FIG. 10 has already been described in connection with another embodiment.

The axially sliding elastomeric member 162 preferably has a smaller radial compression and frictional resistance than the outer stator elastomer 167 and the shaft elastomer 170. This small frictional resistance causes axial movement to occur in this elastomer 162 than at other locations in the seal.

Therefore, the embodiment of FIG. 10 provides a structure that can accommodate axial movement between the device shaft 171 and the device housing 168. This axial movement causes the frictional resistance elastomer 162 to occur at a smaller position than in the shaft elastomer 170. This maintains the respective operating clearance between the rotor 169 and the internal stator 160 and is intact. The amount of movement between the axial device shaft 171 and the device housing 168 can be adjusted.

With reference to Figure 11A, the seal of the present invention includes two obliquely sliding stator housings 180,181. One stator housing 180 is radially inside the second stator housing 181 and includes a radially extending shape 182. The shape portion 182 is in contact with the elastomer 183 sliding in an axial direction. The outer stator housing 181 also includes a radially extending feature 184 that abuts against the axially opposite side of the elastomeric slide 183 at an angle. The obliquely sliding elastomer seals between the two housings 180, 181.

The axial movement between the two stator housings 180, 181 is certainly limited by the radially extending features 184.

The stator housings 180, 181 are reliably rotated by suitable mechanical means such as drive pins or drive lugs 185 to allow angular movement of the two stators 180, 181 but limit rotational movement.

Outer stator housing 181 carries radially extending features 186 and houses an elastomeric member 187. The elastomeric member 187 provides a seal between the stator housing 181 and the device housing 188.

In addition, as shown in FIG. 11B, the angular motion can be controlled by two matching spherical surfaces 320 or other mechanical means.

Another element of the invention shown in FIG. 11 has already been described in connection with another embodiment.

Therefore, the embodiment of FIGS. 11A and 11B provides a structure capable of adjusting the angular movement between the device shaft 189 and the device housing 188. This angular movement is at the pivot position between the two stators 180,181, or at the elastomer 183 or spherical joint 320, rather than at other positions. This maintains the operating clearance between the rotor 190 and the internal stators 180, 321 in the device that receives the angular movement between the shaft 189 and the device housing 188, but is not damaged.

12A, the seal 200 is mainly divided across the longitudinal axis for ease of installation of the device, and cannot be separated by conventional methods for installing a conventional seal.

The seal has split rotor assembly halves 201, 202 that are at least longitudinally and generally aligned, and also have separate stator halves 203,204 that are generally aligned at least two longitudinally. In particular, the features of the seal blocking device and the repulsive pumping device have already been mentioned.

Specific division shapes of this embodiment will be described with reference to Figs. 12A, 12B, 12C, 12D, 12E, 12F, and 12G.

In FIG. 12A, two divided halves of the stator are connected together by a suitable fastener such as one or more cap screws 205. The cap screw operates in the free hole 206 of one of the divided stator halves 203 and is connected to the screw hole 207 of the second split stator 204.

The fixing method of the cap screw 205 is merely an example. In another embodiment, the two divided stator halves carry clearance holes, allowing the bolts to pass through both sides and secured by using nuts on the bolts.

In Fig. 12B, the two divided stator halves 203 and 204 have a suitable sealing device 210 positioned at the radial end between the two before being mounted together. The sealing device 210 may be a sealant supplied when installed in the device, or may be a gasket type member as shown. The gasket type member may cover the entire radial end of the stator 204 or may be shaped as shown in FIG. 12B.

In FIG. 12B, the gasket 210 seats in the channel 211 at at least two radial ends of the stator half 203 or stator half 204. Gasket 210 provides a seal that extends radially between the stator for device housing elastomer 212 and the stator for rotor elastomer 213. Preferably, the gasket 210 is in contact with each of the elastomers 212 and 213.

12A, the two divided halves of the rotor assembly 201, 202 are connected together by suitable fasteners, such as one or more cap screws 215. As shown in FIG. The cap screw 215 operates in the clearance hole 216 of one of the divided rotor halves 201 and is connected to the screw hole 217 of the second divided rotor 202.

In addition, the two divided stator halves may carry radial holes that allow the bolts to pass through them and are secured using nuts to the bolts.

12b, the two divided rotor halves 201 and 202 have a suitable sealing device 220 positioned at the radial end between the two before being secured together. In addition, the sealing device 220 may be a gasket type as shown, or a sealant used when installing the device. The gasket type member 220 may cover the entire radial end of the rotor 202 or may be shaped as shown in FIG. 12B.

12B, the gasket 220 is mounted to the channel 221 at least two radial ends of the rotor half 201 or rotor half 202. Gasket 220 provides a seal that extends radially between the rotor for device shaft elastomer 222 and the rotor for stator elastomer 213. In particular, the gasket 220 is in contact with each of the elastomers 222 and 213.

The two divided halves of the rotor and the stator can overlap one another to form a flat, integral sealing surface. This eliminates the need for a gasket between the halves. However, there is more technology needed to make a sealable connection between two metal parts than when a rigid deformable material is used.

In addition, two halves of each bearing protector part can be attached together with a suitable adhesive or sealant during installation of the unit to the rotating part of the device.

In addition, the two halves of the stator and the rotor are mechanically fixed and supported together by suitable means such as jubilee clips, circlips, split rings, tie wraps and the like.

12C, another embodiment of the seal according to the present invention includes a strap-type fastener 230, 231 that secures the stator 232 and the rotor 233, so that each of the two divided halves Secure together. This requires divided elastomeric members 212, 213, 222 before installing the invention on the device. Elastomers 212, 213, 222 may be radially divided, for example using a knife or the like, and after being wrapped around the shaft, the ends of the elastomers 212, 213, 222 are secured with a suitable binder to create a continuous circular ring.

Since the ends of the elastomer can be radially deviated and easily fixed together, the divided elastomer includes a clear position between both ends as shown in FIG. 12D.

12D, one end of the divided elastomer 235 includes a member 236 extending radially inward, and the other end of the divided elastomer 235 includes a corresponding position hole 237. As shown in FIG. During assembly around the device shaft, the extended elastomer end 236 is positioned and secured to the elastomer with holes 237 with a suitable adhesive. This structure ensures a sharp radial position between the two ends of the elastomer 235, and is therefore preferred to facilitate installation.

In some applications it is difficult to use together two axially separated parts that are screwed together, and it is desirable if the screws can be retained in the divided parts while making the seal difficult in the access area.

As mentioned above, one method of securing two radial halves together is to use threaded positioning holes 216 and 217 in the gap. However, at both half of the rotor and the stator, the positioning hole may be threaded. In this case, special screws are used as shown in Fig. 12E.

12E, the cap screw 239 has a recess 300 extending radially inward over a limited axial length, which extends between the head 301 and the thread 302 of the screw.

In FIG. 12F, the cap screw 239 is one axial split rotor until the screw 304 in the cap screw 239 removes the axial end of the corresponding screw 305 of the rotor 203. It is screwed into the screw position hole of the member 303. The recess 300 extending radially inwardly of the cap screw 239 has an outer surface, which is radially smaller than the inner surface of the screw 305 of the rotor 303. The cap screw 239 is held axially between the shoulder portions 301, 306 of the axially divided rotor 303 and cannot be moved during installation of the divided sealing device.

12G shows the corresponding screw 307 in the corresponding rotor half 308 and the cap screw 239 in a fixed position, with both radially divided rotor halves 303 and 308 together. Tighten

Similarly, cap screw fixing is used to fix the stator.

In connection with Figure 13, a cartridge type mechanical seal 241 is mounted to the shaft 242 and secured to the housing 243 of the rotating device. The cartridge type mechanical seal 241 prevents the treatment material 244 from leaking out of the processing chamber 245.

13 shows the seal 240 on the untreated material side of the cartridge mechanical seal 241. The mechanical seal 241 includes a blocking fluid 246 in the blocking chamber 247. The blocking fluid 246 prevents the escape from the process chamber 245 by the mechanical sealing surface 248 therein. The seal 240 prevents the blocking fluid from escaping to the air side 249 of the cartridge type mechanical seal 241.

Stator 250 of seal 240 is a separate replaceable part of cartridge mechanical seal 251. Obviously, the stator can be integral if desired.

14, the labyrinth seal 260 is firmly secured to the rotating shaft 261 by one or more set screws 262 mounted to an axially extending rotor 263. As shown in FIG.

Referring to Fig. 15, the axial compression labyrinth seal 270 includes one rebound pumping device 271 on the air side.

In connection with Fig. 16, the axial compression maze seal 280 includes one repulsive pumping device 281 and a shutoff sealing device 282 toward the atmospheric material.

Referring to Fig. 17, the axial compression labyrinth seal 290 includes a shutoff sealing device 291.

Referring to Fig. 18, a maze-shaped sealed bearing protector 350 is mounted to the shaft 351. Rotor assembly 352 and stator 353 are formed in a similar manner as described in connection with FIG. 1 as a whole.

Those skilled in the art will appreciate that the stator for the rotor donut-shaped elastomer 354 is radially retained by the inner rotor surface 355 and the outer rotor surface 356, while the rotor donut elastomer 354 is in the axial direction. It is movable and can be sealedly connected to the stator.

The axially biased auxiliary member, ie another elastomer 357, is adjacent to the elastomer 354. The axially biased elastomer preferably has a similar cross sectional area, but is larger in radial direction than the elastomer 354. The axially biased elastomer 357 is held axially between the axial surface 358 of the rotor 352 and the axial surface of the elastomer 354. Preferably, the elastomer 357 is slightly compressed in the axial direction and is sealedly connected to the stator 353 by applying an axial force to the elastomer 354.

The axially biased elastomer 357 extends circumferentially in the rotor recess 359, as is more clearly shown in FIG. The radial recess 359 in the rotor 352 is preferably 0.010 "larger radially than the outermost surface of the elastomer 357. The adjacent surface 361 is inclined radially as shown. However, the surface may be perpendicular to the shaft 351.

Thus, the stator 353 to the rotor 352 are sealed when the device shaft 351 and the seal 350 are stationary. As the device shaft 351 and seal 350 move, the elastomer 357 is subjected to centrifugal force of the rotating assembly causing the elastomer 357 to extend circumferentially. The circumferentially extending action removes the axial eccentric force from the elastomer 354 that allows the elastomer 354 to axially float in the radially formed recess 362. The frictional resistance between the elastomer 354 and the stator 353 is sufficient to axially move the elastomer 354 to the space occupied by the auxiliary member elastomer 357, so that the rotor assembly 352 and the stator ( 353) form an axial gap between them.

With reference to FIG. 20A, the seal 360 is shown in a fixed position, and the rotating elastomer 354 sealably connects the stator 353 at the surface 362. In the moving position shown in Fig. 20B, the rotating elastomer 354 is moved axially from the stator 353 showing the axial gap 363.

The axial rotor surface 358 is inclined axially, as shown at 364, and the axial clearance "N" adjacent to the innermost surface of the elastomer 357 is at the outermost surface of the elastomer 357. It is smaller in the axial direction than the adjacent axial clearance "M".

When the device is stopped, the innermost surface of the elastomer 357 is 0.005 " to 0.010 " radially larger than its nominal radial size in the free state, commonly referred to as the radial preload.

The combination of the initial radial preload on the elastomer 357 and the axially biased surface 358 causes the axial force to act on the elastomer 354. The elastomer 357 extends in the circumferential direction, such that the inclined surface 358 causes an axial gap to be formed.

The above-mentioned structure has important technical advantages.

Firstly, the axial seal connection between the rotor and the stator is a more reliable solution for the radial seal connection.

Secondly, material properties such as the density of each of the elastomers 354 and 357 are technically selected for the purpose of such elastomers. For example, elastomer 354 is typically a rigid elastomer having a 70 to 90 Shore hardness, so that the resistance to reverse rotational wear is greater. It is desirable for the elastomer 357 to be more elastic and extend well in the circumferential direction, typically having a Shore hardness of 40-70.

Not only different densities of the same material may be selected, but different materials may also be selected. For example, elastomer 354 can be made of PTEF material, while elastomer 357 is made of a material such as viton provided by Dupont Dow elastomer. As another example, the material of the elastomer 354 is selected to include self-lubricating properties, ideally in contact with the reverse slide surface or the reverse rotation surface.

With regard to Figure 21A, another structure provides an important advantage: the elastomer 370 may be a hard donut with a smaller cross-sectional area than the elastomer 371. Therefore, the elastomer 370 can extend around in slower shaft speed applications.

With regard to FIG. 21B, another structure provides an important advantage: the elastomer 375 is a solid donut with a larger cross-sectional area than the elastomer 376. The elastomer 375 therefore provides a greater degree of axial compression on the elastomer 376.

With regard to FIG. 21C, another structure provides an important advantage: The elastomer 380 is hollow donut shaped. The elastomer 380 therefore extends around in slower shaft speed applications.

The axially inclined members 357, 370, 375, 380 can be spring-like members or wedge-shaped members. In fact, the annular shape can be used as illustrated in Figs. 21D, 21E, 21F, and 21G.

Figure 21d shows a spring-like member 385, such as an axially biased member, adjacent to the sealing member 386. The spring-like member 385 is a closed loop garter spring, which is less than the spring internal tension. It is circumferentially expandable when subjected to greater inner radial forces.

21E shows wedge-shaped member 390 and may or may not be divided radially in whole or in part at one or more peripheral points. The wedge-shaped member 390 has one or more inclined surfaces 391 and inclines in the axial direction to the sealing member 392.

Fig. 21F shows a spring-like member 393 for activating the wedge-shaped member 394, which provides the sealing member 395 with an axial tilt.

Fig. 21G shows a donut shape, such as a lip with a major shutoff seal between the reverse rotating parts 397 and 398. Donut shaped member 396 such as a lip is axially moved by any suitable means including member 399 such as the illustrated spring.

22i shows a seal 400 having a rotor 401 and a stator 402. The rotor 401 is axially constrained by a radially extending shoulder 403 and a circlip 404 of the stator.

The rotor 401 is sealed and rotatably connected to the device shaft 405 by an elastomer 406, which stator is sealed and rotatably connected to the device housing 407 by an elastomer 408.

The rotor 401 is at least one uneven portion 410, 411, 412 extending radially on a surface exposed to the outside of the rotor 401 abutting the surfaces 413, 414 with the surfaces of the stator 402 exposed inside. ).

The stator surfaces 413 and 414 are not centered with respect to the rotor surfaces 410 and 411, as shown at the lower portion of the cross section at locations 416 and 417. The varying radial clearance of the surface with different centers between the rotor outer surface and the stator inner surface activates fluid movement.

The seal 400 does not necessarily require pumping holes in the rotor outer surfaces 410 and 411 or bends that are not radially constant to activate fluid movement.

With reference to Fig. 23, the blocking portion is shown and it is shown in great detail with the hard donut member 420 being axially maneuvered by the hard donut member 421. The unitary rotor 401 structure has an axially extending cavity 422 and includes at least one outwardly contacting surface 423 and at least one inwardly contacting surface 424, but preferably Has two inwardly contacting surfaces 424 and 425.

In connection with Figure 24, the seal 450 includes a housing 451, which extends radially to replace the bearing chamber cover cap (shown as a separate component in the previous figures). This provides commercial benefits to the producers of the rotary device, removing one part from the overall assembly.

The housing 451 includes an axial bore 452 and axially secures the housing 451 to the bearing chamber 454, corresponding to the screw holes 453 in the bearing chamber 454 of the rotating device. Be sure to

Figure 24 shows how the rotating assembly 460 is separated from the housing 451, which is held together with the bearing chamber 454 of the components of the rotating device. This structure facilitates replacement and repair of the reverse rotation wear member 461.

A summary of the various embodiments of the invention is as set forth above and will be presented further.

The embodiment of Fig. 1 is a cartridge non-contact labyrinth type seal, having a labyrinth, and one or more radial concave-convex features forming a two-way repulsive pumping device and shut-off device toward the product and atmospheric material. This structure is particularly advantageous for preventing fluids and solids from entering and exiting the bearing cavity.

The embodiment of FIG. 2 is particularly advantageous for the user because the pumping system is not only very efficient with the use of a rotor operating in an eccentric pumping chamber, but also because the device is bidirectional in rotation. This means that the same non-contact bearing protector of the present invention can be used to seal both ends of a typical industrial bearing chamber, and the shaft rotates clockwise (as viewed from one side of the chamber) or counterclockwise.

4A and 6 are particularly advantageous for the user as a blocking device which prevents moisture from entering the bearing chamber when the device is static and the shaft does not rotate. The advantage of the v-shaped seating area minimizes the deterioration of the elastomer in device startup and shut-off and helps to keep the device longer.

The embodiment of Figure 5 is particularly advantageous in applications where there is an additional protective device necessary to minimize the volume flow of air molecules through the device of the present invention.

The embodiment of Figure 7 is particularly advantageous in applications where the movement or circulation of the product is appropriate. The application involves the use of an oil-spray system to lubricate the bearings of the rotor parts. The open wing rebound pumping structure entails a biased stator to help facilitate lubrication circulation.

The embodiment of Figure 8 is of a different design than the embodiment of Figure 1 in which the stator has two axially and radially coupled parts and the rotor is integral.

The embodiment of Figure 9 is the application of Figure 1, wherein the stator housing is securely fixed to the device housing. This secure position is often very practical to install, and the device can replace a mechanical seal or a major seal packaged in a rotator part. The stator housing entails a peripheral connection to the present invention for injecting or ejecting the first fluid or the second fluid, which is then pumped into the process chamber. Equally, the structure can be used for bearing lubricating fluid which is recirculated from the bearing chamber to, for example, a cooler and then returned to the bearing chamber in a closed loop system.

10 can accommodate axial movement, if mounted in a sliding housing. This is desirable where the shaft movement is excessive due to physical or thermal expansion conditions.

The embodiment of Figure 11 is used for bearing block arrays or columns using spherical bearings when the angular array of housings on the shaft changes.

Some types of rotating devices have large shaft diameters. The device spends a lot of time dismantling and replacing a failed bearing protector. In such applications, it is particularly desirable if the bearing protector can be installed without dismantling the rotating device. In such an application, the divided invention of the embodiment of Fig. 12D through 12A is greatly beneficial. Installation to the rotating device is very simple and takes less time than a non-separable structure. In addition, bearing protectors are actually for low efficiency with zero processing pressure and temperature. This makes it simple to fix two sets of parts comprising elastomers with suitable and practical sealants or adhesives.

The embodiment of Figure 13 is effective for mechanical installation.

The embodiment of Figure 14 can be used for applications where rotational drive integrity is a concern.

15, 16 and 17 of the present invention show a modification of the axial compression non-contact bearing protection device. This embodiment is essential where the present invention replaces oil and lip seals, often axially widening, such as widening radially.

Since it is difficult to access the area, it is very difficult to install the seals and components, and the installation advantages of the embodiment arise from Figs. 12E to 12G. Often parts such as screws fall out of position and are lost. In the present invention, the cap screw shown in each half of the non-contact sealing device is shown as an example method. The cap screw even prevents the half from falling out when it is upside down.

18 to 21 of the present invention provide a wide variety of donut shapes for the periphery extending member and the rotor stator sealing member, which is particularly advantageous for slow shaft speeds.

22 and 23 show a rotor structure with grooves extending axially and radially with one integral member. This embodiment has commercial advantages over a two part rotor structure with fewer parts.

24 and 25 of the present invention show a bearing protector housing acting as a cover plate for the bearing housing. This is beneficial for rotating device manufacturers, which reduces one part in the overall assembly. This embodiment has a radially extending housing and provides a method for securing axial clamping and a rotating bearing bearing chamber.

As indicated above, the present invention is used in all parts of seals, protectors, insulated bearing chambers, fans, pumps, mixers, blower rotary valves, electric motors and rotating devices required for the inflow and outflow of protective materials.

Claims (22)

A stator 353 positioned in the stator assembly of the rotating device; A rotor 352 positioned on a rotating shaft of the rotating device; And And a static blocking device having an elastic annular sealing member 354 and an auxiliary member 357, and forming a seal between the stator 353 and the rotor 352. The stator 353 and the rotor 352 have adjacent surfaces 355 and 356, respectively, and the elastic annular sealing member 354 and the auxiliary member 357 have the rotor 352 stopped. A first position in which the auxiliary member 357 compresses the elastic annular sealing member 354 to engage the adjacent surfaces 355 and 356, and an elastic annular shape when the rotor 352 moves. The compression of the sealing member 354 is reduced such that the insulator seal is movable between the second position where the elastic annular sealing member 354 separates one or more rotors 352 and the surfaces 355, 356 of the stator 353. . The insulator seal of claim 1, wherein the inclination of the longitudinal axis of at least one of the surfaces is between 5 degrees and 175 degrees. The insulator seal of claim 1, wherein the inclination of the longitudinal axis of at least one of the surfaces is between 10 degrees and 80 degrees or 100 degrees and 120 degrees. The insulator seal of claim 1, wherein the inclination of the longitudinal axis of at least one of the surfaces is between 30 degrees and 60 degrees or 120 degrees and 150 degrees. The insulator seal of claim 1, wherein the inclination of the at least one longitudinal axis of the surfaces is 45 degrees. The insulator seal of claim 1, wherein the inclination of the at least one longitudinal axis of the surfaces is at an angle other than 90 degrees. The insulator sealing portion according to claim 1, wherein the elastic annular sealing member has a donut shape. The insulator seal according to claim 1, wherein a labyrinth seal is further provided between the rotor and the stator. 2. The insulator seal as claimed in claim 1, further comprising at least one two-way repulsive pumping device. 2. The insulator seal as claimed in claim 1, wherein the surfaces of the rotor and stator are inclined at an angle other than 90 degrees with respect to the longitudinal axis. The insulator of claim 1, wherein the rotor and the stator are separated in the axial direction, but the relative axial movement is constrained by at least one radially extending member formed on one of the rotor and the stator. Seals. 12. The insulator seal as claimed in claim 11, wherein the rotor and the stator are axially constrained by two or more radially extending members. 2. The insulator seal as claimed in claim 1, wherein the stator includes at least one connecting hole extending from an inner surface of the stator to an outer surface of the stator. The insulator sealing part according to claim 13, wherein the connecting hole is adjacent to a radially extending member provided in the rotor. The insulator seal according to claim 13, wherein the inner surface of the stator is eccentric to the rotor or to the rotating shaft in use. 14. The insulator seal of claim 13, wherein said connecting hole is located at the lowest radial point in the seal during use. 2. The stator of claim 1, wherein the stator has a radially inwardly extending groove and an eccentric innermost surface on its outermost surface, wherein the radially extending groove extends to the radially outermost point of the innermost surface. And a connection hole for connecting the outermost surface and the innermost surface of the stator. The insulator seal of claim 1, wherein the surfaces form a “v” shaped portion together. 19. The apparatus of claim 18, wherein the elastic annular sealing member is seated in the " v " portion at a radial position larger than the radial position of the elastic annular sealing member in the free state. Insulator Seal. 2. The insulator seal as claimed in claim 1, wherein the rotor includes at least two repulsive pumping devices separated in the axial direction. A cartridge seal with an insulator seal according to claim 1. Bearing protection device with insulator seal according to claim 1.

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