TWI375765B - Isolator seal - Google Patents

Description

1375765 IX. Description of the Invention: [Technical Field] The present invention relates to an isolating device and its use in a rotating device, and more particularly to a device for preventing fluid or solids from entering and exiting a cavity, thereby causing a lifespan of the device. These devices are commonly referred to as bearing protectors, bearing seals or bearing isolators. However, the application of such a rotary seal is far beyond the protection of the rotating S and the intermediate bearing. Because of today. . Although bearing insurers will be mentioned hereinafter, it should be understood that the seal of the present invention has a much broader range of applications. [Prior Art] The purpose of the bearing protector is to prevent weeping - to prevent the body, solids and/or debris from invading the shaft: The [...] bearing protector is also used to prevent fluid or solids from escaping to the shaft. Essentially, its use is to prevent premature failure of the bearing. Guarantee = Protection: Generally ί is divided into two types: mechanical seal bearing protection for resistive or meandering bearings " slaughter w〇A see our co-pending more T 〇月案W〇_A-2004005770 It does not reveal a basic contact bearing protector. An eight-way type bearing protector typically includes an assembly that is mounted for rotation about a pumping force and that is fixed upwardly relative to the pumping. For example, the shaft can help the axis of the device. The protector consists of a - stationary component, which is also fixed in the axial direction and is attached or fastened to the stationary part of the device. The rotating assembly typically has a complex outer wheel temple that is positioned adjacent and radially and axially abutting the complex inner rim of the stationary assembly. In theory, these complex corridors provide a path of twists and turns 103554.doc 1375765, thereby preventing the passage of materials or fluids that are not intended by the quintessence. The zigzag draw protector 檑Α当檑Α < χ通通吊 only works during the operation of the device ^ ^ The heart is designed to rely on the rotation of the rotating component and the stationary component = force, thus preventing fluid in these components Between the radial direction, and when the equipment is stationary, the complex zigzag design is in position. In the horizontal application, the liquid level 俜虚一保' liquid-holding radial level is in the protection of the population. In addition, in many industrial applications, when the equipment is stationary, helium and foreign pollutants will be directed to the bearing. The traditional zigzag design does not prevent these contaminants from entering the bearing chamber. This: Another problem in the industrial field of the bearing chamber breathing system. During operation, the lubricating fluid and air from the bearing to the center will expand when heated. In the traditional zigzag seal, this will discharge air through the (four) structure and "call" out of the bearing chamber. Once the equipment is shut down, the bearing chamber will cool and the internal air will contract, drawing the humid air back into the bearing chamber via a tortuous structure. This is called "sucking in". The mechanical seal sleeve protector overcomes the static margin of the tortuous design. However, such mountings can suffer from other problems, such as excessive heat in the high shaft speeds: in the presence or presence of excessive or no lubricant on the surface of the seal. Therefore, the application of mechanical seal bearing protectors is limited. Accordingly, there is a need for a non-contact zigzag type that seals fluid when the device is stationary and/or prevents airborne microparticles from entering the sleeve chamber during breathing in the bearing chamber and/or reduces the volume of airborne tiny particles entering the bearing chamber. Sealed bearing protector. 103554.doc 1375763 ', good shape, regardless of the direction of rotation of the shaft, non-contact zigzag 3L can block the fluid in the seal. This will reduce the possibility or impact of installation errors. In the case where the hinge is improved, the non-contact zigzag seal comprises two impingement devices, one designed to block fluid from escaping the bearing chamber and the other to block fluid from entering the bearing chamber. In addition, ease of installation is important for all bearing protector designs. It is desirable to provide a non-contact zigzag-type seal that is extremely compact in the axial direction so that it can fit into the space pre-occupied by the lip seal and be provided in the form of an integral cartridge unit without the use of a retaining clip. . US-A-5,378'0〇〇 (〇rlowski) discloses a card holder design having a meandering configuration in which the rotor and stator are axially locked together by a solid deformable annular seal or an elastomer. . The elastomer is locked between two relatively rotating rectangular cavities, as shown in Figures 3 and 4 of 〇rl〇wski. The elastic body is subject to frictional resistance - the frictional resistance caused by the stator is small, and the frictional resistance caused by the rotor is large. Therefore, the elastomer in 〇rl〇wski is subject to frictional wear between the two relatively rotating objects. Such frictional wear is exacerbated by the fact that the surfaces 23 and 22b of the rotor 14 are at an acute angle and the three remaining corners of the grooves 21 and 22 in contact with the elastomer (20) are at a 9-degree angle. 〇rl〇wski relies on the relatively un-chamfered surfaces of the four points in contact with the elastomer to maintain axial proximity between the rotor and the stator. All commercially available elastomers have a cross-sectional dimensional tolerance. This is typically +/- 3% of its nominal diameter. Therefore, the value of the frictional resistance specified by Orlowski can vary greatly, given the fact that the elastomer tolerance is known and the grooves 2 1 and 22 will also have an associated width tolerance of 103,554.doc 1375765. During the assembly of the seal onto the apparatus, the impact is axially pulled when the implant is moved into its final operating position. This axial displacement is due in particular to the frictional oncoming resistance from the rotatable elastomer 15 and the shaft 1〇. Since the elastomer 20 is the only element that axially locks the rotor and the stator together, the axial displacement causes the elastomer 2 to withstand shear forces. Therefore, it is highly probable that the frictional resistance between the elastomer and the sides of the grooves 21 and 22 will change during assembly. All of these facts affect and quickly increase the wear on the elastomer 2 and thereby limit the effective sealing life of the elastomer to prevent material from entering and exiting. SUMMARY OF THE INVENTION According to a first aspect of the present invention, an isolating seal is provided, comprising: a stator member for being placed in a stator of a rotating device;

a rotor member disposed on a rotating shaft of the rotating device; the stator member and the rotor member providing respective adjacent surfaces; - a stationary shutoff device including - an elastic annular sealing member that engages two adjacent sides when the rotor is stationary Table 6 In the surface of the rotor and stator of the Xuanzhu, at least one of the surfaces is inclined toward the longitudinal axis. The face, when the rotor is in motion, is disengaged from one or more; and the surfaces are greater than or less than 90. The angle of the slanting one / 徊 甶 towards the longitudinal axis from 5 ° to 1750, more than a smug of people. To 80. Or since 1〇〇. To 120, 103554.doc 1375765 Specific The package is optimally from 30. To 60. Or claim 20. To 15 baht. . In an embodiment of the invention, the tilt can be about 45. . According to a second aspect of the present invention, an isolating seal is provided comprising: - a stator member for being placed in a stator of a rotating device; a rotor member for being placed on a rotating shaft of the rotating device; the stator member and the stator member The rotor members provide respective adjacent surfaces - including - resilient annular sealing members and - stationary blocking means for the auxiliary members - which can be moved - when the rotor member is stationary - the first position - the second position 1 is moved The auxiliary member compresses the elastic annular member to couple the surfaces, and in the second position, the elastic member is reduced, thereby allowing the elastic annular member to be heard while the rotor is in motion Preferably, the elastic sealing member is annular. -= The sealing step comprises a meandering seal formed between the rotor member and the detent member Preferably, the seal member - #includes at least one bi-directional barrier suction device 0. The rotor member and the surface of the forceps member are both - greater than or less than 9 inches. The angle is toward the longitudinal axis. Preferably, the rotor and the sub-junction are formed in the rotor and the relative movement is caused by the relative axial movement to the crucible. The ritual extension member on the cow-on is more preferably 'by two The one or more radially extending members axially constrain the 103554.doc 1375765 rotor and stator member. Preferably, the stator member is provided with at least one inner surface extending from the stator member and an outer surface of the stator member More preferably, the communication hole is adjacent to a radially extending member disposed on the rotor member. Preferably, the inner surface of the stator member and the rotor member and/or in use and the rotation Preferably, in use, the communication aperture is located at the most point of the seal. Preferably, the stator member has a diameter on its outermost surface and its substantially different center: a groove extending inwardly, the diameter extending to a radially outermost point of the innermost surface, from (iv) to a communication hole between the innermost surface of the member and the outermost surface. Preferably, the rotor member And the surface of the stator-rVj ^ 〇+ material Preferably, the elastic annular member is seated in the "V" position == the nominal member is in the radial direction of the suction device when it is at (4). The rotor member is attacked with at least two axial directions. The resistance of the separation =::: turn: two with the stator member "system - a whole miscellaneous pieces. The stator members are mutually - = : = member and or the stator member from the 纟 专 $ special shoulder from the rotor member 苒仵Subsequently extending from one of the members. Preferably, the member member, and the stator member member comprises two axially joined members. The first member of the rotor member member is 103554.doc /y/65 A component can be positioned radially to a second of the rotor component components by mechanical, chemical or other (4) methods to form a permanent or non-permanent connection. The seal of the present invention preferably includes a sub-shell having at least one radially outwardly disposed position for the device chamber; a positional position of the t-position. The position of the clamp TG member is close to An extending groove, the radially extending groove comprising at least one elastomer member for sealing the outer casing to the equipment chamber 1 and preferably also having at least one surface extending outwardly along the #' Dock up the equipment room. Preferably, the rotor includes at least one barrier suction device, the at least one barrier suction device being formed by at least one radially inwardly extending body on the circumference of the rotor. Preferably, the crucible rotor comprises at least two resistive suction means that are offset axially. Preferably, the barrier suction device comprises a continuous and substantially concentric rotor surface, the continuous and substantially concentric rotor surface corresponding to a substantially different center of the stator surface. Preferably, the barrier suction device comprises at least one radially inwardly extending shape on the circumference of the rotor. Preferably, the rotor comprises at least one barrier suction device, the at least one barrier suction device comprising at least one radially inwardly extending body, the at least one radially inwardly extending body being located at the circumference of the rotor Up and close to a substantially radially inner surface of the stator. Preferably, the rotor comprises at least two blocking suction 103554.doc • 12· 1375765 devices that are axially offset. Each barrier suction device includes at least one radially inwardly extending body that is located on the circumference of the rotor and adjacent a substantially radially inclined surface of the stator. Preferably, the stator housing includes at least one inner body, the center of the at least one inner body being offset from the center of the shaft. Preferably, the eccentric inner body of the stator housing is adjacent to at least one of the rotors to block the suction device. w

Preferably, the stator housing comprises at least one radially communicating body, the at least one radially communicating body communicating the innermost surface of the outer casing to the outermost surface of the outer casing β. The radially communicating body or the venting hole is preferably The ground is adjacent to at least one of the barrier suction devices. ’ ’ w~’ Rugged § sub-sub-systems are a single piece. Preferably, wherein - a sleeve 6 7 , a pair of tweezers are radially positioned in the second stator, the two are joined by a mechanical method, a pneumatic method or any other fastening method to be permanent or Non-permanent connection. Preferably, the outer stator on the outer side includes a radial=extension (four)° on the outermost surface thereof. The #extending body is adjacent to the radial position 0 of the two rotor members. Preferably, the rotor is in the shape. Above the body comprises at least one of the present invention extending radially in the radial direction of the present invention adjacent to and in close proximity to the inner surface of the stator. And/or - a stationary embodiment can be: at least one rotating member. The article can be mechanically coupled to the rotating device. J03554.doc 1375765 The seal of the present invention can include a stator housing having at least one axial through hole or slot to accommodate one of the rotating devices Double head

a bolt or a bolt, whereby the outer casing of the mechanical seal can be fastened to the rotating device. Preferably, a first outer casing stator is radially positioned into a second outer casing stator, the outer casing &stator# By one turn? The intermediate ground is axially connected to the second housing stator and is directly connected to the stationary housing of the device. The housing can be axially slid relative to the second housing stator. Preferably, the axial displacement is mechanically limited to maintain a card seat solution. Preferably, a first outer casing stator is radially and axially positioned into a second outer casing stator. The first outer casing stator is indirectly inclined (5) by a rotor, and the second outer casing stator is directly Connect to the stationary housing of the device. The first outer casing stator is slidable obliquely relative to the second outer casing stator. Lightly, the tilt displacement is mechanically limited to protect the solution. Embodiments of the meandering seal of the present invention may be such that at least one rotating structure and/or a stationary member are axially halved for attachment to the apparatus. Preferably, the pair of sub-assemblies are mechanically slid inwardly after being mounted on the apparatus. Preferably, the halved design preferably includes at least one elasticity that is radially halved. The body 'joins it by a permanent method after installation around the pump. The present description also provides a non-contact zigzag-type seal shape protector. 103554.doc xj/5765 Reference will be made herein to an elastomeric sealing member in the form of an elastomer or an O-ring which forms part of the stationary cut-off device or the stationary cut-off device. • It should be understood that any elastomer or solid deformable material is suitable. Although the sealing members are not circular in cross-section, it should be understood that they may have a different shape, including a shape that provides a combination of a flat surface and/or a rounded surface. [Embodiment] The present invention will now be described by way of example only with reference to the accompanying drawings. In general, the rotary seal of the present invention can be used not only for the case where the shaft-rotating member but also the outer casing is a stationary member, but also for the opposite case, in other words, the case where the shaft is stationary and the outer casing is rotated. Furthermore, the invention may be embodied in the form of a rotating structure or in the form of a stationary structure' and in the form of a card and modular seal having metal and non-metallic components. Referring to Figure 1 of the accompanying drawings, the circle shows a bearing protector assembly 1G on the object of the first embodiment of the present invention to the rotating device 11. The apparatus includes a rotating shaft 12 and a stationary housing 13. The stationary housing 13 can typically include a bearing (not shown). ♦ H-protection 11 assembly 10—the zone at the axial end _“X” may partially contain fluid and/or solids and/or foreign debris and/or atmosphere. However, for the sake of “lighter”, it is referred to as “product substance” to describe a single medium or a mixed medium. The region "Y" at the other axial end of the bearing protector assembly 10 may also partially contain fluid and/or solids and/or foreign debris and/or atmosphere. 103554.doc •15-1J75765 to illustrate a single medium or mixture, referred to herein as "atmosphere". The draw protector assembly 10 includes a rotor assembly including a first rotor member 14! 6. The first rotor member 14 is positioned to a second rotor member 15 in the radial direction and the axial direction. The rotor assembly 16 is positioned adjacent to a certain substructure 7 . A transverse section A-A is shown in Figure 2A. A section through the groove 18 is directed to the surface. A transverse section B_B is shown in Figure 2E. A section through the groove 19 to the surface.

This is the outermost diameter of the stator 17. This is the outermost diameter of the stator 17. Referring to Figure 2A, the first rotor member 14 includes at least one radially extending body, i.e., slot 25. The rotor 14 is substantially concentric with the shaft 12 and thus rotates on the shaft centerline 26. The stator 17 includes at least one inner body, i.e., a radial gap between the outermost surface of the stator suction hole 27 #14 and the innermost surface of the stator suction hole 27 provides a suction chamber 28. As seen in Figure 2A, the stator suction aperture 27 is substantially concentric with both the rotor 14 and the shaft 12 and has a centerline 29. The eccentricity value between the rotor 14 and the stator suction hole 27 is shown as the radial distance between the respective center lines 26 and 29 "Z" 〇 due to the presence of the eccentricity 'the rotor 14 and the stator suction hole 27 The pinch gap is not constant along the circumference of the assembly 10. As shown in Fig. 2A, the search gap 3 处 at the 12 o'clock position is significantly smaller than the radial gap 31 shown at the 6 o'clock position. Any fluid entering the suction to 28 will undergo a change in radial clearance as it is carried by the rotor slot 25 in the circumferential direction. This radial clearance: the change 103554.doc -16-1375765 forms the pressure edge of the fluid melon body working in the control gap. This change in fluid pressure causes the fluid to move from the small radial gap position 30 to the large radial gap position 31 in the circumferential direction θ circumferential direction. It can be seen from Figure 2A that the outer groove 18 in the stator 17 is also substantially concentric with the shaft 12. In the end view of the cross-sectional view, the lowest position is referred to as 6 o'clock, and FIG. 2A shows the radial penetration of the concentric groove 18 and the stator suction hole 27. An enlarged view of the shape is shown in Fig. 23. It can be seen from Figure 2B that the punch-through is in the stator

The innermost region and the outermost region of the t-sub 17 form a communication hole 35. The automatically generated communication hole 35 has the advantage that the hole will always appear at the maximum radial gap position 31, and the machine used, manufactured Technology or Operator Unrelated This will provide advantages to the supply company. Figure 2C corresponds to Figure 2B and shows an alternative embodiment in which the stator suction aperture 27 includes an additional radially extending inner region 36. The radially extending region opens into a natural communication hole 37, and the length of the hole 37 is more strictly controlled and less changed in the case where the associated hole 27 and the groove 18 are naturally associated with each other. . Figure 2D corresponds to Figure 2B and shows another alternative embodiment in which the communication apertures 38 are provided by a milling slot or drilled hole through the stator 17. Figure 2E corresponds to Figure 1 and illustrates yet another embodiment which shows a barrier suction structure adjacent the side of the product material. As seen in Figure 2E and Figure 1, the second rotor 15 includes at least one radially extending body, i.e., slot 45. The rotor 15 is substantially concentric with the shaft 12 and rotates on the shaft centerline 46. The stator 17 includes at least one inner body, i.e., a stator suction hole 47. The radial gap between the outermost surface of the rotor 15 and the innermost surface of the stator suction hole 47 is 103554.doc -17 - 1375765 is the suction chamber 48. The stator suction holes 47 are substantially concentric with both the rotor 15 and the shaft 12 and have a center line 49. The eccentricity between the rotor 15 and the stator suction holes 47 is shown in the figure as the radial distance between the respective centerlines 46 and 49"w". Due to the eccentricity, the L-direction gap between the rotor 15 and the stator suction hole 47 is not constant along the circumference of the assembly 1 。. As shown in Figure π, the radial gap 50 at the 12 o'clock position is significantly less than the radial gap 5 1 at the 6 o'clock position. Similarly, any fluid entering the suction chamber 48 is circumferentially oriented by the rotor slot 45. When transported, they will experience changes in radial clearance. This change in radial clearance creates a change in the pressure of the fluid operating in the radial gap. This change in fluid pressure causes the fluid to move from the small radial gap position 5 至 to the large radial gap position 5 1 in the circumferential direction. A rotor slot or recess 45 that extends radially on the outer surface of the rotor and that is discontinuous in the circumferential direction is not essential to promote fluid motion. The effect of the two opposing and oppositely aligned opposing rotating surfaces is generally sufficient to block and/or draw fluid. Equivalently, two substantially concentrically aligned opposing rotating surfaces - one of the preferred rotors - comprising a radially extending and circumferentially discontinuous rotor slot or depression - are sufficient to block and/or Aspirate fluid. As can be seen from Figures 2E and 1, the outer slot 19 in the stator 17 is substantially concentric with the shaft. At the radially lowest position on the end view of the cross-section, referred to as 6 o'clock, Figure 2E shows the radial communication of the concentric groove 19 with the stator suction hole 47 = 55. This is further illustrated in Figure 2F, which is a plan view of Figure 3E in Figure c = I03554.doc 1375765. The feedthrough forms a communication hole 55 between the innermost region and the outermost region of the stator 17. This combination of the outer concentric groove 19 and the eccentric stator suction hole 47 forms a natural communication hole 55 at the maximum radial clearance position 5?. _ Obviously the position of the communication hole 5 5 can be at any circumferential position with respect to the varying radial gap between the rotor and the stator. For example, in some applications, the communication hole may be more suitable to be at a position near the minimum radial gap position between the rotor and the stator', thus corresponding to the highest fluid pressure difference position, whereby φ utilizes a relatively high fluid Pressure pushes the fluid out of the communication hole. An experienced reader will note that one or two suction systems can be used. Preferably, since each of the sides of the assembly 1 is blocked from entering and exiting the material, a double barrier suction system is provided, wherein one of the barriers is on the atmospheric side and the other is on the product side. The large radial gaps 3 1 and $ 1 can be made only by changing the oblique machining orientation between the atmospheric material end of the stator 17 and the eccentric suction hole on the product material end, thereby positioning the communication holes 37 and 55 (if needed) to form an angle relationship with each other. • The number and/or size of the suction slots 25 and 45 and/or their respective angular orientations can be varied to suit the sealed application. Preferably, the barrier suction designs on both sides of the present invention should be substantially balanced and equal to each other so as not to facilitate entry and/or discharge in any particular manner. Referring to Figure 3, the bearing protector is a cartridge unit that can be provided without any positioning means. Preferably, the rotor assembly 6A includes two axially joined rotor members 14 and 15. Preferably, the first rotor 14 is radially positioned in the second rotor 15 at the radial position 61. 6 The rotors 14 and 15 are both axially compressed 103554.doc -19·1375765 Preferably, the rotor comprises at least Two barrier suction devices are offset in the axial direction. Each barrier suction device includes at least one body that is circumferentially of the rotor and extends radially inwardly. As shown in FIG. 3, the two rotors 14 and/or 15 include at least one serpentine body 72 and 73 extending radially inward and circumferentially on the outermost radial surfaces of the rotor peaks 14 and 15. . The castellations 72 and 73 may have a square shape as shown or have any shape including a curved surface and a flat surface. For example, the cross section of the shape may be trapezoidal, v-shaped or semi-circular. As another example, it may have a thread having a left-handed or right-handed pitch. The radial rotor surface and the ridges 72 and 73 extend radially adjacent (typically 0.005 〃 to 0.010") adjacent innermost stator surfaces 74 and 75, respectively. Obviously, the radial proximity is not limited to 0 005 〃, Rather, it may be greater or less than this value. The innermost radial surfaces 74 and 75 of the stator 17 adjacent the outermost radial surface of the rotor assembly 60 may equally have a serpentine body as described above. Any combination of rotor or stator jaws is used to limit and/or prevent axial fluid movement. The bearing protector 10 includes a static shutoff device that includes an elastomer 81 that is located 80 in the radial direction. Radially facing the inside of the elastomer 81. The shape of the 卩疋v" shape is composed of two oppositely rotating/surfaces, i.e., consisting of the stator surface 82 and the rotor surface 83. Elastomer 81 is radially located on the "v" shape, the radial position of which is slightly larger than the nominal radial direction of the elastomer 81 when it is in its free state. In practice t, the arrangement means the elastomer 81 In a way that stretches in the radial direction 103554.doc •21 - 1375765 works. Since the elastomer 81 is stretched outwardly, the arrangement creates a corresponding inward radial force acting around the circumference of the elastomer 81, thereby driving it into the composite" The v"formed surfaces 82 and 83. This creates a static seal between the rotor assembly 60 and the stator 17 on the surfaces 82 and 83. This arrangement will be further detailed below with reference to Figures 6A and 6B. It can be seen that the 'rotor assembly 60 includes the first rotor 14 and the second rotor 15 ^ the second rotor 15 projects radially outwardly from the outermost surface of the elastomer 81. The rotor 15 includes radially inward surfaces 90 and 91 » The surface 91 is inclined in the radial direction and the axial direction. A gap 92 exists between the inclined surface 91 and the outer surface of the elastic body 81. The gap 92 enables the elastic body 81 to be protected from the outward direction in the case where the speed of the shaft 12 is low. Frictional resistance When the device is activated and the shaft 12 is rotated, the elastomer 81 is subjected to a centrifugal force acting in a radially outward manner. The centrifugal forces enable the elastomer 8 to be lifted from the inclined stator surface 82 and moved to the rotor tilt. On surface 91. This is shown in Figure 6B. The inclined surface 91 on the rotor transforms the substantially radial motion of the elastomer 81 into a radial and axial movement to urge it toward the rotor lumen 94. When the device shaft 12 stops rotating, it acts on the elastomer 81. The centrifugal force in the outward direction also stops. At this time, the inherent elasticity of the elastomer 81 forms a radially inward direction of force, thereby driving the elastomer 81 back into its v-shaped A holding surfaces 82 and 83 of the respective stator 17 and rotor 14. As shown in Fig. 6A, the elastomer 81 in the v-shaped support surfaces 82 and 83 provides a radial cut-off device and forms a static seal to prevent fluid or solid from the side of the atmosphere to the source 103554.doc • 22· 1375765 On the side of the material, or from the side of the product to the side of the atmosphere. The radial gap 92 can be any size. For example, it can range from zero to 2.000" or 50 mm and above. Preferably, the radial clearance is about 0.010". In addition, in some applications, it may be considered necessary to cause the inclined surface 91 to compress the elastomer 8 radially inwardly, so that the "radial gap" at this time provides frictional resistance between the rotor surfaces 91 and 83. Interference fit. The above arrangement does not have any limitations of US 5,378, 〇〇〇 (〇ri〇wski). It is explained as follows: - The v-shaped support structure of the present invention ensures that the elastomer 81 does not contact sharp surfaces or blade-like surfaces that may cut into the elastomer 81 during startup and shutdown of the device. - The v-shaped support structure of the present invention ensures that any elastomer 81 manufacturing tolerances do not affect the design at all. In the static state, regardless of the cross-sectional dimension of the elastomer 8, the frictional resistance of the elastomer 81 to the surfaces 82 and 83 is constant. The difference in cross-sectional dimensions of all the elastomers 81 is from the rotor gap 92 and/or the rotor cavity 94. accommodate. - The v-shaped support structure of the present invention can accommodate any slight axial displacement of the respective rotor 6 and stator 17 components that may occur during installation of the present invention onto the shaft. In the event that the corresponding axial nominal gap between the rotor 6〇 and the stator 17 changes, the dome-shaped support structure will open or close in the axial direction accordingly, since it comprises two separate surfaces. This effect on the elastomer Μ is a slight change in the nominal radial sealing position of the elastomer 81. The elastomer 81 will be seated at a radial position slightly above the nominal position if the axial gap is closed, or at a slightly lower than if the axial clearance is increased by 103554.doc -23 · 1375765 The radial position of the nominal position. This design ensures that the elastomer 81 is not subjected to any stress and/or shear forces that are not desired due to axial movement. Figure 4 is an isometric exploded view of four of the six components of the bearing protector of Figure 1. During assembly of the invention, the rotor 14 is pushed through the dice 17 until it is positioned in the axial direction. The elastic body 8 is stretched radially outward and placed in the support region formed by the rotor 14 and the stator 7 assembly. Figure 4Β shows this. When the rotor 15 is axially supplied to the sub-assembly (10), the radially inclined surface 101 is radially positioned on the elastic body 81. Continued axial movement of the rotor 丨5 causes the inclined surface 1〇1 to compress radially but does not damage the solid-deformable elastomer 81. Therefore, the inclined surface is very desirable. Fig. 5 corresponds to Fig. 3, which shows a partial longitudinal cross-sectional view of a bearing protector 1〇3 which does not include an additional solid deformable member or elastomer 1〇4. The elastomer is mounted in a radial cavity 105 obtained between two opposing rotating surfaces, stators 1 and 6 and between turns. The magazine Λ1Ι/Ι, 弹 生 104 104 helps to limit the volumetric flow of airborne tiny particles through the invention. Further advantages are obtained by the embodiment of the present invention being compatible with the embodiment shown in Fig. 1. Therefore, the addition of the elastomer 104 does not require changes to the components of the first embodiment. Figure 7 shows another embodiment of the invention. A partial longitudinal section view of J. The bearing protection 109 has a rotor assembly 110 comprising at least one suction-preventing device 111, the barrier suction device U1 comprising a body extending from the radial direction of the nozzle 112, at least one of the radial extensions The shape and shape of the mouth 112 has a radial root 113 inclined to the outermost circumference of the assembly m. The radially extending 103554.doc • 24· 1375765 extended body 112 is adjacent to one of the stators 11 5 and is substantially radially inclined to the inner surface 114. When the rotor assembly 110 is rotated with the pump 116, the 彳f: the extended body 112, in particular in the radially inclined root 丨 13, radially moving the atmospheric material toward the inner inclined surface 114 of the stator 115. The centrifugal force generated by the rotation of the rotor assembly 11 turns also causes the atmospheric matter to radially Move outside. Once the atmospheric material is connected to the inclined surface Π4 of the stator 115, when the substance is detached from the bearing protector 109, its radial velocity is converted into an axial displacement. As shown in Figure 7, the rotor assembly 11A includes at least two barrier suction devices 111 and 117 that are axially offset. Each of the barrier suction means is formed by at least one radially inwardly extending shape, the at least one radially inwardly extending body being located on the circumference of the rotor, substantially radially inclined from one of the stators U5 surface. Although FIG. 7 shows the inclined root portion ι 3 of the radially inwardly extending body 112, the root portion 113 may be any combination of inclined surfaces, parallel surfaces, or curved surfaces, including but not limited to both longitudinal and end views. The shape is convex, concave and parallel, or any combination thereof. Referring to Figure 8, the stator assembly 12A includes two axially coupled stator members 121 and 122 that are radially positioned and axially butted. The stator assembly 120 is composed of two members that are axially captured (four) and a monolith. The forceps member 121 includes a radially inwardly extending body 124 on its outermost radial surface adjacent the radial abutment of the two stators 122 and 121. The radially extending body 124 acts as a trough to ensure that the stator assembly 12〇 is not radially in the radial position between the two stators 122 and I03554.doc -25· =1 Excessive interference with the device housing 125. The stator member 12A includes a recess 126 extending radially inwardly from its outermost surface, the recess 126 carrying a solid deformable elastomer member 127 that is the device housing 125 The innermost surface provides a circumferential seal. The stator member 122 has a radially outwardly extending body 128 that axially positions the stator assembly 12A to the end face of the device housing 125. The detents 122 and 121 are at 129 They are joined by mechanical means such as radial interference fit or threads. However, chemical means such as an adhesive and/or a permanent means such as welding are also a further example of a suitable fixing method. The rotor 123 includes a body U0 extending radially outward from its innermost surface, the body 130 carrying A solid deformable elastomeric member 131 that provides a circumferential seal to the outermost surface of the device shaft 132. The rotor 123 has at least one barrier suction body 133, and the barrier suction body 133 includes at least one radially extending body, i.e., a groove 134 on the outermost circumference of the rotor ι 23, a groove 134, and a rotor 123 in the cavity of the stator 122. Operation. The cavity is preferably eccentric as described above with reference to Figure 2A. Further, the stator 122 includes at least one venting opening 135 as described above with reference to Figure 2B. The rotor 12 3 includes at least two axially offset barrier suction devices 丨 3 3 and 103554.doc -26 - 1375765 13 and the female barrier suction device is formed by at least one radially inwardly extending shape. The shape extending inwardly along the control is located on the circumference of the rotor and sin against the eccentric suction cavity on the inner surfaces of the dice 121 and 122. The rotor 123 includes a cutoff structure 137 that includes an elastomer 138 ρ that operates in a v-shaped support region 139 that includes an inclined stator radial surface 140 and an inclined rotor radial surface 141.

The rotor 123 also has at least one radially extending chevron 142 that abuts radially on the radially inner surface of the stator 122 and/or 121. Referring to Fig. 9A, the seal of the present invention may include a stator housing 15a having a body 151 extending radially outward. The stator 151 includes at least one radial through hole or slot 152 for receiving a stud or bolt 1 514 in one of the rotating devices 153, thereby enabling the stator 丨 5 本 of the present invention to be mechanically effective Fasten to the rotating equipment】53.

As shown in FIG. 9A, the stator housing 155 also includes an external environment connection 156 for injecting or filling a primary fluid or secondary fluid into the seal 158 and pumping it into the process chamber. Inside. Referring to Figure 10, the seal of the present invention can include two stator housings 160 and 161 that slide axially. One of the stator housings 16 is radially inside the second stator housing 161, and at least one of the stators includes an axially slidable elastomeric member. 162 'The axially sliding elastomeric member 162 is in the two housings 160 A circumferential seal is applied between 161 and 161. Preferably, it is effective by a radially extending body 163 and/or: limiting axial movement between the two stator housings. Preferably, the two tweezers casings 160 and 161 are rotatably connected by mechanical means such as a driving pin or a driving sleeve, such as a driving pin or a driving sleeve, which makes the two The stator is axially movable but limits the commutation movement. The outer stator housing 161 includes a radially extending body 166 that houses an elastomeric member 167. The elastomeric member 167 provides a circumferential seal between the stator housing 161 and the device housing 168. The rotor 169 includes an elastomer 17 〇 which seals the rotor 169 circumferentially to the device shaft 71. Other elements of the invention shown in Figure 10 have been previously described with reference to other embodiments. Preferably, the axially sliding elastic member 162 has a radial compression amount smaller than that of the outer stator elastic body 167 and the shaft elastic body 17, and thus the frictional resistance is smaller than that of the outer stator elastic body 167 and the shaft elastic body 17A. This smaller frictional resistance thereby promotes axial movement at the elastomeric crucible 62 rather than at other locations within the seal. Thus, the embodiment shown in FIG. 1A provides an apparatus shaft 171 and device

A structure that accommodates axial longitudinal displacement between the outer casings 168. This axial displacement is caused to occur at the elastomer 162 where the frictional resistance is smaller rather than at the shaft elastomer. This ensures that the respective running clearance between the rotor 169 and the inner stator 160 is substantially maintained without sacrificing. Any amount of movement between the axial device shaft 171 and the device housing 168 can be accommodated. Referring to Figure 11A, the seal of the present invention includes two housings 180 and 181 that slide obliquely. The dragon φ _ plus - 7 M * - the middle rafter casing 180 is radially inside the first stator casing 181 and includes a body 182 extending in the radial direction. The shape 182 abuts the obliquely sliding elastic body 183 in the axial direction. The outer stator housing (8) 103554.doc -28- includes a longitudinally extending body 184 that axially abuts the opposite axial sides of the oblique sliding elastomer 183. The oblique sliding elastomer performs a circumferential seal between the two outer casings i80 and 181. The axial movement between the two stator housings 180 and 181 is effectively limited by a radially extending body 184. 3 Two dice call 18 〇 and 181 by, for example, a drive pin or a drive sleeve 185. A suitable mechanical means is effective to rotate the connection, which enables the two stators 180 and 181 to move diagonally but limit rotational movement. The outer stator housing 181 includes a radially extending body 186 that houses an elastomer member 187. The elastomeric member 187 provides a circumferential seal between the stator housing 181 and the device peripheral 188. Alternatively, the diagonal movement can be performed by two mating spherical surfaces 32 〇 or in place of a mechanical member, as shown in Fig. 11B. Other elements of the invention shown in Figure 11 have been previously described with reference to other embodiments. Thus, the embodiment shown in Figures 11A and 11B provides a structure that accommodates an oblique displacement between the device axes i89 and s and the housing 18 8 . This oblique displacement is caused to occur at the pivotal position of the two stators 18A and 181, at the elastomer 183 or the ball joint 320, rather than at other locations. This ensures that the device application in which the oblique displacement between the shaft 189 and the device housing 188 is 'substantially maintained without sacrificing the respective running clearance between the rotor 19〇 and the inner stator 180/32i. Referring to Fig. 12A, the seal 200 is substantially halved across its longitudinal axis to facilitate installation of a conventional seal that cannot be removed in a conventional manner. 103554.doc • 29-1375765.

The seal comprises at least two halved rotor assembly halves 201 and 202 that are substantially mated in the longitudinal direction and at least two halved stators I 203 and 204 that are substantially mated in the longitudinal direction. The shape of the seal, particularly the cut-off and barrier suction device, has been described above. Here, the specific pair of fractals of this embodiment will be described with further reference to Figs. 12A, 12B, 12c, 12D, uE, 12F and 12G. It can be seen from Figure 12A that the two halves of the stator are joined together by suitable fastening means, for example by one or more cap screws 2〇5. The cap screws 205 are used in the gap holes in the halved stator half 2 〇 3 and are sprinkled in the corresponding threaded holes 2 〇 7 of the second bisector stator 2 〇 4 . The method of fastening the cap screw 205 is by way of example only. In another example, the two halved stator halves each include a clearance hole such that the bolt passes through both and is secured by the use of a nut on the bolt. As can be seen from Fig. 12B, the two halves of the stator are half-added (4) with a suitable seal 210' to seal the two halves together: the radial end between the two halves on. The sealing device 210 can be a sealant applied as it is mounted to the device, or a sealed jaw member as shown. The gasket-type member may cover the entire radial end of the stator 204 or, as shown in Figure 12B, define its shape. It can be seen from Figure 12B that the 'seal 210 is located in the overlap 211 of the at least two radial ends of the stator halves 203 or 204. The sealing jaw 210 provides a seal extending in the warp direction between the stator-to-equipment housing 2 body 212 and the stator-to-rotor elastomer 213. Preferably, the sealing jaws 21〇 are butted to each of the elastomers 212 and 103554.doc -30 · 1375765 213 〇 from Figure 12, it can be seen that the two halves of the rotor assembly 2〇ι and 202 are properly fastened. The devices are attached together, for example by one or more cap screws 215. The cap screw 215 is used in the one of the split rotor half 216 t and is engaged in the counter split thread 2 17 of the second split rotor 2〇2.

Alternatively, both of the two halve rotors may include a clearance hole that allows a bolt to pass through both and is secured by the use of a nut on the bolt. As can be seen from Figure 12B, the two halve rotor halves 2 and 1 〇 2 have a suitable sealing means 220, and the sealing means 22G is positioned between the two halves before the two halves are fastened together. To the end. Also, the sealing means may be a sealant applied to the device or a sealed jaw member as shown. The sealing jaw member 22() can cover the rotor plus the entire radial end or, as shown in Figure 12B, define its shape.

As can be seen from Figure 12B, the gasket 22 is located at least the translated end of the rotor half 201 or 202.沟槽t's groove 221 towel. The seal bore 22() provides a radial extension between the rotor to the device shaft = body 222 and the rotor to stator elastomer 2ι 3 in the seal. Preferably, the gasket 220 is butted to each of the elastomer 222 blades 213. The two halves of the rotor or stator may be lapped together to flatten it to form an integral sealing surface. This eliminates the need to use a sealing jaw in the door of the halve. Then, the additional design required to make the joint between the two metal parts is greater than the design of 103554.doc !375765 required to use the solid deformable material. Further, by mounting the unit on the rotating member of the apparatus (4), the respective bearing protector assemblies can be glued together by a suitable adhesive and/or sealant. The two halves of the stator and the rotor may also be mechanically held together by suitable means such as coupling screw clamps, circlips, buckles and/or connecting straps. Referring to Figure 12C, the seal of the present invention Yet another embodiment includes a strap type 23() and 231 fastening means for both the stator 232 and the rotor 233 to bias the two respective halves together. It is necessary to use halved elastomeric members 212, 213 and 222 before mounting the invention on the device. The elastomers 212, 213, and 222 can be diametrically divided by, for example, a knife and after they are wound on the shaft, 'the ends of the elastomers mm and 222 are fastened by a suitable adhesive to form a continuous ring. . Since the ends of the elastomer are susceptible to radial offset, which may affect sealing performance, the split elastomer includes a shunt position between its ends, as shown in Figure 12d. As seen in Figure 12D, the end portion of the halved elastomer 235 includes a radially inwardly projecting member 236 and the other end of the halved elastomer 235 includes a corresponding locating hole 237. During assembly around the device shaft, the extended elastomeric end 236 is positioned and secured within the elastomeric end having the aperture 237 by proper adhesion. This design provides a precise radial position between the ends of the elastomer 235 and is therefore easy to install. In some applications, it can be difficult to connect the two #对对分组103554.doc -32· 1375765 pieces together using a screw, and when the seal is installed in the area where the seal is difficult to handle, Preferably, the screws are embedded in the halved components. As described above, a method of fastening the two radial halves uses screws in the optical positioning holes 2 16 and the threaded positioning holes 217. These locating holes in the absence of the ·, , meat, rotor and stator can be threaded. In this case, a special screw is used as shown in Fig. 12A.

It can be seen from Figure 12 that the capped screw 239 has a finite axial length and has a radially inwardly extending groove 300 which is between the screw and the threaded portion 302. extend. From (4) it can be seen that 'the cap screw 239 is screwed into the threaded locating hole in one of the axially halved rotor members 3〇3' until the thread on the cap screw 239 passes through the axis of the corresponding thread 3〇5 in the rotor 303. Until the end. The groove extending radially inward of the cap screw 239 has an outer surface that is radially smaller than the inner surface of the thread 3〇5 of the rotor 303. At this time, the cap screw 305 is axially locked between the shoulders 301 and 3〇6 in the axially halved rotor 3, and cannot be moved during the installation of the halving sealing device. Figure 12G shows the corresponding threads 3〇7 corresponding to the rotor half and the cap screws 239 in the tightened position clamp the two radial split rotor halves 3〇3 and 3〇8 together. The same method of fastening by a capped screw can also be used for the fastener. Referring to Fig. 3', the cartridge type mechanical seal 241 is mounted on the shaft 242 and fastened to the outer casing 243 of a rotating device. The cartridge type mechanical seal 241 prevents the process material 244 from leaking out of the process chamber 245. 103554.doc • 33- 1375765 Figure 13 shows a seal 240 on the non-process material side of the 6-seat mechanical seal 241 of the Kamen Temple. The mechanical seal 241 contains a barrier fluid 246 in the barrier chamber 247. The medial mechanical obscurity of the maple leaves prevents the barrier fluid 246 from entering the process chamber 245 at the closure surface 248. The seal 24 is resistant to the barrier/gut body to the cartridge mechanical seal 241 to the atmospheric side 249. The stator 25 of the seal 240 is a separate and replaceable holder of the mechanical seal cover (5). Obviously, the stator can be an integral part if desired.

Referring to Fig. 14', a meandering seal 26 is effectively fastened to a rotating shaft 261 by one or more set screws 262 mounted in the axially extending rotor 263. Referring to Fig. 15 #The compact zigzag seal 27 包含 contains a barrier suction device 27i on the atmosphere side. Referring to Figure 16, an axially-compact zigzag seal 28 includes a barrier suction device 281 on the atmospheric side and includes a shut-off seal 282 ° • Referring to Figure 17, an axially compact zigzag seal 290 A cut-off sealing device 291 is included. Referring to Fig. 18, a meandering seal bearing protector 35 is mounted on a shaft 351. Rotor assembly 352 and stator 353 are generally constructed in a manner similar to that described with reference to the drawings. The reader will note that the stator-to-rotor annular elastomer 354 is radially locked by the rotor inner surface 355 and the rotor outer surface 356. However, the 354 can be moved axially to engage the stator in a sealed manner. Adjacent to the elastomer 354 is a rotatable axially biased elastomer 357. The shaft I03554.doc • 34· 1375765 is preferably radially larger than the elastomer 355 but has the same cross-sectional area. The axially biased elastomer 357 is axially locked between the 'axial surface 358 of the rotor 352 and the axial surface of the elastomer 354. Preferably, the elastic body 357 is slightly compressed in the axial direction to exert an axial force on the elastic body 354 to urge the stator 353 to be engaged in a sealed manner. As shown more clearly in Figure 19, the axially biased elastomer 357 can be circumferentially stretched in the rotor groove. The radial groove 359 in the rotor 352 is preferably greater than the outermost surface of the elastomer 357 by 0.010 turns in the radial direction Φ. Preferably, the adjacent surface 361 is inclined in the radial direction as shown. However, the surface may be perpendicular to the axis 351 相应 . Accordingly, when the device shaft 351 and the seal 350 are stationary, there is a seal of the stator 353 to the rotor 352. When the device shaft 351 and the seal 35 are in motion, the elastic body 357 is subjected to the centrifugal force of the rotating assembly, thereby causing the elastic body 357 to be stretched circumferentially. This circumferential stretching removes the axial biasing force from the elastomer 354, causing the elastomer 354 to float in the axial direction in the radially constrained groove 362. The frictional resistance between the elastomer 354 and the stator 353 is sufficient to cause the elastomer 354 to move axially into the space pre-occupied by the elastomer 357' thereby creating an axial gap between the rotor assembly 352 and the stator 353. Referring to Fig. 20A', the seal 360 is shown in a rest position, and the rotatable elastomer 354 sprays the stator.353 at a surface 362 in a sealed manner. In the dynamic position shown in Fig. 20, the rotatable elastomer 354 is axially offset from the stator 3 53 - a radial gap 3 63 is shown. The axial rotor surface 358 is inclined in the axial direction, as shown at 364, such that the axial clearance near the innermost surface of the elastomer 357 "Ν" is less axially close to 103554.doc • 35 - Elastomer 3 5 The axial clearance of the outermost surface of 7 is 〃μ,. When the device is at rest, the innermost surface of the elastomer 357 is generally radially proportional to its nominal radial dimension Α() plus it is referred to herein as preloading.

The combination of the initial duty preload and the slanted inclined surface 358 on the elastomer 357 causes the -axial force to be applied to the elastomer 354. When the elastomer 357 is stretched along the circumference, the inclined surface 358 effectively promotes the formation of an axial gap. The above structure has significant technical advantages. First, the implementation of an axial seal between the rotor and the stator is a more reliable solution than radial seal engagement. First, the material properties of the respective elastomers 354 and 357 can be technically selected, especially for density, to suit the use of such elastomers. For example, the elastomer 354 is preferably (d) a hard elastomer that is often between 7 〇 and 9 〇 氏 (sh〇re) hardness to make it more resistant to relative rotational friction and wear.

3 5 7 is preferably more elastic and can be stretched circumferentially and typically has a Shore hardness of 4 〇 7 。. Not only can you choose different densities of the same material, but you can also choose different materials. By way of example, the elastomer 354 can be made of a pTFE material and the elastomer 357 can be made of a material such as fluorinated rubber supplied by Dupont Dow elastomers. As another example, the material of elastomer 354 can be selected to include self-lubricating properties such that it is adapted to interface with relatively sliding and/or rotating surfaces. Referring to Figure 2, an alternative construction provides a significant advantage: the elastomer 370 can have a cross-sectional area that is less than the solid annular shape of the elastomer 371. Therefore, in applications where the shaft 103554.doc • 36· 1375765 #- is slower, the elastomer 370 is more likely to stretch along the circumference. Referring to Figure 21B, an alternative design provides significant advantages: the elastomer 375 has a cross-sectional area that is greater than the solid annular shape of the elastomer 376. Thus, elastomer 375 can provide a greater degree of axial compression than elastomer 376. Referring to Figure 21C, another alternative design provides the distinct advantage that the elastomer 38 is in the shape of a hollow ring. Therefore, in applications where the shaft speed is slower, the elastomer 380 is more likely to stretch along the circumference.

The shaft or wedge biasing members 357, 370, 375 and/or 380 can be spring-like members 21E, shaped members. In fact, as exemplified in Figures 21 〇 2IF and 21G, which are described herein, any form of annular shape may be utilized. Figure 21D shows a spring-like member 385 as the axially biasing member adjacent the sealing member 386. The spring-like member 385 is a closed-loop annulus, which is elongatable circumferentially when subjected to an internal radial force greater than the internal stress of the spring.

The figure shows a wedge member 39A that can be fully or partially radially or not split at one or more of its circumferential points, and the member member provides one or more axial biases for the sealing member 392. Inclined surface

Figure 21F shows a wedge member 394, biased. a spring-like member 393 that energizes a wedge member 394 and provides an axial view for the sealing member 395. Figure 21G shows a lip that provides a substantially cut-off seal between the relatively rotating members 397 and 398. The ring 396 ° I-shaped ring 396 can be energized by any suitable member (including spring-like members as shown). 103554.doc • 37- 1375765 Referring to Figure 22, there is shown a seal 400 comprising a rotor 4〇1 and a stator 4〇2. The rotor 401 is axially constrained by the radially extending shoulders 4〇3 of the stator and the elastic retaining ring 4〇4. The rotor 401 is sealed by the elastomer 4〇6 and rotatably coupled to the device shaft 405, which is sealed by the elastomer 4〇8 and rotatably coupled to the device housing 407. On the surface of the rotor 4〇1 of the surface us, 414 exposed inwardly in the near-arc 402, the rotor 4〇丄 includes one or more radially extending domes 410 and/or 411 and / or 412. As shown at locations 416 and 417 at the lower cross-section of the cross-sectional view, the stator surfaces 413 and/or 414 are not concentric with the rotor surface and/or 411. The varying radial clearance between the outwardly facing surface of the rotor and the inwardly facing surface of the stator promotes fluid movement. . It should be understood that the seal 4 does not necessarily require a radially discontinuous spiral or suction groove on the outer surface of the rotor and/or on the river to promote flow. Referring to Fig. 23' as shown in the figure, the figure shows a cut-off body comprising a solid circle 42 〇 excited by an axial circle in more detail. The one-piece construction provides an axially extending cavity 422 comprising a second surface 423 and at least one inwardly facing surface 424, but preferably two inwardly facing surfaces 424 and 425. The cover cap seal 450 includes a housing 451 that extends in the radial direction to replace the bearing chamber (in the figure of the face, the one that rotates the early single object). This has particular commercial advantages for "business": from the entire application 03554.doc -38. 1375765 is particularly advantageous in suitable applications. Such applications may include the use of an oil mist system to fully slide a bearing in a rotating device. An open vane barrier suction design comprising a tilted stator facilitates oil circulation. The embodiment of Figure 8 is a design variant opposite the embodiment of Figure 1, wherein the stator includes two axially and radially joined components. The rotor system is monolithic. Figure 9 is a modified version of the embodiment, wherein the stator housing is modified to be effectively fastened to the equipment housing. The determined position is generally very practical for installation 'and the device The mechanical seal or the stuffed main seal chamber in one of the rotating devices may be replaced. The stator housing may also include an external environment connection to inject or fill a primary fluid or secondary fluid into the present invention, and then pump the fluid into the process. In the same cavity, this design can be used to recirculate bearing lubrication fluid from the bearing chamber to a cooler in a closed loop system and then back to the bearing chamber. Figure 1 is an embodiment that accommodates any amount of axial movement if installed in a sliding housing. This is advantageous in applications where the shaft is excessively moved due to physical and/or thermal expansion factors. Embodiments enable the present invention to be used in a mount or pedestal structure in which a spherical bearing and in which the shaft is angularly aligned with respect to the housing. Some types of rotating equipment have a large shaft diameter. For this type of equipment, Lower and replacement of faulty bearing protectors can take hours, days or weeks. In such applications, it is especially preferred if the bearing protector can be installed in place without the need to remove the rotating equipment. The dichotomy invention shown in Figures 12A to 12D is the main advantage. It is very simple to install on a rotating equipment and takes less time than a non-divisible design. In addition, the bearing protection pass 103554.doc •40-1375765 Often low-performance applications, the process pressure and temperature are virtually zero. This makes it very suitable and feasible to fasten two sets of components, including elastomers, with a sealant or adhesive. Supplemental mechanical mounting is quite effective. The embodiment shown in Figure 14 can be used in applications where the rotational drive integrity is a problem. The embodiments of the invention shown in Figures 15, 5 and 17 all show compactness in the axial direction.

A variant of a non-contact bearing protector. These embodiments are of the utmost importance when the present invention is used to replace oil seals or lip seals that are generally axially as wide as the radial direction.

The mounting advantages of the embodiment shown in Figures 12E through 12G result from the installation of seals and components in areas that are difficult to access. Components such as screws are often * lost from position and are often lost. This embodiment solves this problem by merely showing by way of example how the cap (four) lock is placed in each of the semi-contact methods of the non-contact seal, so that when the fan is half inverted, the cap screw does not The embodiments of the present invention shown in Figures 18 through 21 provide a variety of annular additional arrangements for circumferentially stretched members and rotor to stator sealing members which are particularly advantageous for slower shaft speed applications. .

The embodiment shown in Figures 22 and 23 shows a single-part rotor design that includes - along (four) and radially extending slots as a single overall embodiment. The commercial advantage over the two-piece rotor design is that it is part (4) It is also shown in Figures 24 and 25 that the embodiment of the present invention shows a bearing-protecting housing, 103554.doc • 4] · 1375765 is used as a cover for the bearing housing. Gentleman & sucking melon board. This is commercially advantageous for manufacturers of rotating equipment because it reduces the entire Shishi to one component. This embodiment has a radially extending outer casing that also provides a means for axial clamping and/or fastening to the bearing chamber of the rotating equipment. The invention as exemplified above has been used to seal, protect and isolate bearing chambers, fans, pumps, mixers, fans, rotary valves, electric motors and all rotating equipment that requires material entry and/or protection. object. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a half longitudinal cross-sectional view of an embodiment of a meandering seal bearing protector of the present invention mounted on a shaft; FIG. 2A corresponds to FIG. Turn over a .α 颂 Α Α Α Α Α Α Α Α Α ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; Figure 2D shows a further design of the venting hole; Figure 2A corresponds to Figure 1, the pel gg, the item is a section through the suction blocker on the line BB; Figure 2F corresponds to Figure 2E, which shows Figure 3 corresponds to Figure 1 'shown-enlarged partial longitudinal cross-sectional view; Figure 4A corresponds to Figure 丨, which shows an isometric projection exploded view; Figure 4B corresponds to Figure 1, which shows. . ',,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,, , its Hungarian,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,,诜 w ^ 〇 P ® m shows that the elastomer is in its dynamic state; Figure 7 shows a partial longitudinal J cross-sectional view of another embodiment of the present invention; Figure 8 shows a partial longitudinal view of another embodiment of the present invention. Figure 9A FIG. 9B shows a partial longitudinal view of the embodiment shown in FIG. 9A, and the basin Φ embodies an external environment connection in the stator; FIG. 10 shows another embodiment of the present invention. 11A is a partial longitudinal cross-sectional view of another embodiment of the present invention; FIG. 11B is a partial longitudinal cross-sectional view of another embodiment of the present invention; FIG. 12A shows another embodiment of the present invention. Etc. 'moon shirt figure, this embodiment is a longitudinally halved zigzag seal; Fig. 2B shows a 4-corner projection view on the axially opposite end of the embodiment shown in Fig. 12A; circle 12C shows a circle Fastening the strip of the embodiment shown in Figure 12A Figure 12D shows a cross-sectional circle of the halved elastomer of the embodiment shown in Figure 12A; Figure 12E shows a partial longitudinal cross-section of the screw of the present invention in another embodiment of the present invention; A partial cross-sectional end view of a portion of an embodiment showing a screw for use in an unsecured position in an axially halved assembly of the present invention; μ 103554.doc • 43· Figure 4F shows the invention of Figure 12F The face of the embodiment is Cheng Guoguo +4· The partial section of the file I, the eight shows that the axis is in the axial part of the sub-assembly; the mouth of the ancestral straight is a mounting to a card seat. FIG. 14 shows a bearing seal in the outer side of the seal of another embodiment of the present invention. FIG. 14 shows a bearing seal of another embodiment of the present invention. Form 1 shows another embodiment of the present invention

A / m 〆 , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , : a form of a tortuous seal in the upward direction of the barrier suction device and comprising a cut-off seal; comprising a cut-off seal. Figure 17 shows an axially compact zigzag of the further embodiment of the invention. Figure 18 shows a longitudinal cross-sectional view of another embodiment of the present invention in the form of a meandering seal bearing protector mounted on a shaft, which is a twenty embodiment of the present invention; Figure 19 corresponds to a circle] 8, which shows an enlarged partial cross-sectional view; FIG. 20A shows an enlarged partial cross-sectional view of another embodiment of the present invention, showing the seal in a stationary state; FIG. 20A corresponds to FIG. 20A, which shows one eight < Sectional view showing the seal in a dynamic state; Figure 21A shows an enlarged partial cross-sectional view of another embodiment of the present invention; 103554.doc -44 - 1375765 Figure 21B shows an enlarged local soil of another embodiment of the present invention 21C shows an enlarged view of another embodiment of the present invention:: FIG. 21D shows an enlarged cross-sectional view of another embodiment of the present invention. FIG. 21A shows an enlarged view of another embodiment of the present invention. FIG. 21 is a partial cross-sectional view showing another embodiment of the present invention. FIG. 21 is a partial cross-sectional view showing another embodiment of the present invention, and FIG. 22 is a cross-sectional view showing another embodiment of the present invention. The two-part design showing the axially constrained by the radially extending circlips corresponds to Fig. 22, which shows a partial section of the embodiment of the present invention: J5Ί · circle, Fig. 24 shows An enlarged partial cross-sectional view of another embodiment of the present invention; and Figure 25 shows an enlarged partial cross-sectional view of another embodiment of the present invention which is not easily detachable from the apparatus. [Main component symbol description] 10 Bearing protector assembly 11 Rotating device 12 Rotating shaft 13 Static housing 14 First rotor member 15 Second rotor member 16 Rotor assembly 17 Stator 18 Slot 19 Slot 103554.doc · 45 1375765 25 Slot 26 shaft centerline 27 stator suction hole 28 suction chamber 29 center line 30 radial gap 31 radial gap 35 communication hole 37 communication hole 38 communication hole 45 slot 46 shaft center line 47 stator suction hole 48 suction chamber 49 Centerline 50 Small Radial Gap Location 51 Large Radial Gap Location 55 Via Hole 60 Rotor Assembly 61 Radial Position 62 Axial Surface 63 Axial Shoulder 64 Release Shape 65 Cavity 103554.doc -46· 1375765 ψ 66 Elastic Body seal 67 equipment chamber positioning body 68 radially extending groove 69 elastomer member 70 radially extending outward facing surface 71 equipment chamber 72 堞 shaped body 73 堞 shaped body 74 innermost stator surface 75 innermost stator surface 80 static cutoff Device assembly 81 elastomer 82 stator surface 83 rotor surface 90 radially inward surface 91 radially inward surface 92 94 rotor cavity 100 rotor 14 and stator 17 subassembly 101 radial inclined surface 103 bearing protector 104 elastomer 105 radial cavity 106 stator - 47, 103554.doc 1375765 107 rotor 109 bearing protector 110 rotor assembly 111 Blocking suction device 112 Radially extending body 113 Radial root 114 Inner surface 115 Stator 116 Shaft 117 Blocking suction device 120 Stator assembly 121 Stator member 122 Stator member 123 Rotor 124 extending radially inward 125 Device housing 126 Groove 127 solid deformable elastomeric member 128 radially outwardly extending body 130 radially outwardly extending body 131 solid deformable elastomeric member 132 device shaft 133 blocking suction body 134 slot 103554.doc -48 1375765 135 bleed hole 136 barrier suction device 137 cut-off structure 138 elastomer 139 v-shaped support region 140 stator radial surface 141 rotor radial surface 142 堞-shaped body 150 stator housing 151 radially outwardly extending shape 152 radial passage Hole or slot 153 rotating device 154 stud or bolt 155 stator housing 156 outside 157 connection 157 primary fluid or secondary fluid 158 seal 159 process cavity 160 stator housing 161 stator housing 162 elastomeric member 163 radially extending body 164 radially extending shape 165 drive pin or drive sleeve 103554.doc 49, 1375765

166 Radially extending body 167 Elastomeric member 168 Equipment housing 169 Rotor 171 Equipment shaft 180 Stator housing 181 Stator housing 182 Radially extending body 183 Sliding elastic body 184 Radially extending body 185 Drive pin or drive Cap 186 Radially extending body 187 Elastomeric member 188 Equipment housing 189 Equipment shaft 190 Rotor 200 Sealing 201 Bisecting rotor assembly half 202 Halving rotor assembly half 203 halving stator half 204 halving stator half 205 Cap screw 206 clearance hole 207 threaded hole 103554.doc -50· 1375765 210 sealing device 211 groove 212 equipment housing elastomer 213 rotor elastomer 215 cap screw 216 clearance hole 217 threaded hole 220 sealing device 221 groove 222 equipment shaft elasticity Body 230 Stator Elastomer 231 Band Type Fastening Device 232 Band Type Fastening Device 235 Splitting Elastomer 236 Radially Inwardly Projecting Member 237 Positioning Hole 239 Cap Screw 240 Seal 241 Cartridge Mechanical Seal 242 Shaft 243 Rotating device housing 244 Process material 245 Process chamber 246 Barrier fluid 10 3554.doc •51 1375765 247 Barrier chamber 248 Inside mechanical seal surface 249 Atmospheric side 250 Stator 251 Dock mechanical seal 260 Zigzag seal 261 Rotary Han 262 Set screw 263 Rotor 270 Axial compact zigzag seal 271 Barrier suction device 280 axially compact zigzag seal 281 barrier suction device 282 cutoff seal 290 axially compact zigzag seal 291 cutoff seal 300 groove 301 screw head 302 threaded portion 303 axial pair Sub-rotor member 304 Thread 305 Thread 306 Shoulder 307 Thread 103554.doc • 52- 1375765 308 Split rotor half 320 Fit spherical 321 Inner stator 350 Zigzag seal bearing protection 351 Shaft 352 Rotor assembly 353 Stator 354 Stator to rotor ring Elastomer 355 rotor inner surface 356 rotor outer surface 357 axially offset elastomer 358 axial rotor surface 359 radial groove 360 seal 361 surface 362 groove 363 radial gap 370 elastomer 371 elastomer 375 elastomer 376 elastic Body 380 axial biasing member 385 spring-like member 3 86 Sealing member 103554.doc • 53 · 1375765 390 Wedge member 391 Inclined surface 392 Sealing member 393 Spring-like member 394 Wedge member 395 Sealing member 396 Lip ring 397 Relatively rotating member 398 Relatively rotating member 399 Spring-like member 400 Sealed 401 rotor 402 stator 403 shoulder 404 circlip 405 device shaft 406 elastomer 407 equipment housing 408 elastomer 410 堞 body 411 堞 body 412 堞 body 413 inwardly exposed surface 414 inwardly exposed surface 103554.doc • 54 · 1375765

416 417 420 421 422 423 424 425 450 451 452 453 454 460 461 Position position Solid ring Solid ring cavity facing outward surface facing inner surface facing surface Sealing housing Axial hole Threading 匕 Bearing chamber Rotatable assembly relative Rotating wear member

103554.doc -55-

Claims (1)

1375765 .. Patent Application No. 094124729\3曰Chinese Patent Application Renewal (June 101 < X. Patent Application Range: 1. An isolation seal comprising: a stator for insertion into a rotating device a stator member (353); a rotor member (352) for being placed on a rotating shaft of the rotating device; the stator member and the rotor member providing respective adjacent surfaces (82, 355/256); and a a resilient annular sealing member (354) and a stationary wearing device of an auxiliary member (357) movable between a first # position and a second position when the rotor member is stationary, in the first position The upper auxiliary member compresses the resilient annular member to engage the surfaces, and in the second position, the compression of the resilient member is reduced, thereby disengaging the resilient annular member when the rotor is in motion 2. The one or more of the rotor and the stator surface. 2. The insulating seal of claim 1, wherein the elastic sealing member is annular. 3. The insulating seal of claim 1 or 2, further comprising a The A labyrinth seal between the rotor member and the stator member. The isolation seal of claim 1 or 2 further comprising at least one two-way barrier suction device. 5. The barrier seal of claim 1 or 2, wherein at least one of the surfaces is greater than or less than 9 inches. The angle is inclined towards the longitudinal axis. 6. The insulation seal of claim 1 or 2, wherein the slope of the at least one surface of the surfaces toward the longitudinal axis is between five. With 175. between. 103554-1010611.doc 1375765 The slope of at least one of the surfaces of the isolating seals of claim 2 or 2 toward the longitudinal axis is between 1 〇. With 8 baht. Or 1〇〇. Between 120°. 8, 8 as requested! Or an isolation seal of 2, wherein the slope of the at least one surface of the surfaces toward the longitudinal axis is from 3 turns. To 6 〇. Or since 12 〇. Between 150°. 9. The barrier seal of claim 2, wherein the at least one surface of the surfaces has an inclination of about 45 toward the longitudinal axis. . 10. The barrier of claim 1 wherein the surfaces of the rotor member and the stator member are - greater than or less than 90. The angle is inclined toward the longitudinal axis. 11. 12. 13. 14. The isolation seal of claim _ wherein the rotor and stator members are axially spaced but extend radially by at least one of the rotor and stator members The member is constrained to perform relative axial movement. The isolating seal of claim 11, wherein the rotor member and the stator member are axially constrained by two or more radially extending members. The isolation seal of claim 1 or 2, wherein the stator member is provided with at least one communication hole. The (four) hole extends between an inner surface of the stator member and an outer surface of the stator member. The isolation (four) of claim 13 is such that the communication hole # is disposed with a radially extending member on the rotor member. 15. The isolating seal of claim 13 and the rotor member and/or the use of 16. The seal seal of claim 13 wherein the inner surface of the stator member is concentric with the axis of rotation. 'Where in use' the connection of the hole 103554-1010611.doc 1375765 is located at the lowest radial point on the seal. 17. 17. The isolating seal of claim 1 or 2, wherein the stator member is on its outermost surface And a radially inwardly extending groove is formed on the innermost surface of a different center, the radially extending groove extending to a radially outermost point of the innermost surface to form a maximum connection to the stator member a communication hole between the inner surface and the outermost surface. 18. The barrier seal of claim (4) which causes the surfaces to form a "V" shape. 19. The isolator of claim 18, wherein the resilient annular member is seated within the "V" shape - at a radial position - the radial position is greater than a nominal diameter of the resilient annular member when in its free state To the location. 2) If the gap of the request 1 or 2 is private, h is away from the seal 'where the rotor member is provided with >, and the two axially separated resistive suction means. 21. A type of card seat type seal, which is packaged with + corrective - as defined in claims 1 to 20 - 隔离 defined as an isolation seal. Item 22·—Type of bearing protector, ^ ^ Package 3—Isolation seal of any one of the requirements of items 1 to 20, Item 103554-101061 id〇 (1375765 . * XI, Fig.: 094124729 Patent Application $ Chinese Graphic Replacement (1〇1年〇6月Y 1375765 Figure 2a 103554-fig-10106.pdf 1375765 103554-fig-10106.pdf 1375765 C I Section B-B Figure 2e / -- f 1 XXX XX 乂 \ 1 _! 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