JP5901981B2 - Rubber stirring device sealing mechanism - Google Patents

Description

The present invention relates to a sealing machine structure for sealing between a housing, the housing and the stirring member of rubber stirring device and a stirring member for stirring the raw rubber charged into the agitation chamber in said housing by rotating .

Is a sealed Organization of conventional rubber agitation equipment, there is known, as described for example in Patent Document 1 below.

JP 2010-162689 A

  This is a seal mechanism that seals between a housing and a rotor of a rubber agitator having a housing and a rotor that agitates raw rubber charged into a chamber in the housing by rotating, The fixed-side seal member that is supported while being allowed to move only in the axial direction and whose seal surface is slidable to the slidable contact surface of the rotary-side seal member fixed to the rotor, and the circumferential direction relative to the fixed-side seal member A pressing force applying mechanism that presses the seal surface of the fixed-side seal member against the sliding contact surface of the rotation-side seal member by applying a pressing force toward the inner side in the axial direction by the yoke pin at two locations separated by a half circumference It is formed in a member at a position away from the yoke pin in the circumferential direction, and feeds a lubricating oil flow to the seal surface by penetrating the fixed-side seal member in the axial direction. Those having a plurality of lubricating oil passage forming an oil film of substantially uniform thickness diffused between the sealing surface and the sliding surface.

  In such a case, as the rotor rotates, the raw rubber whose pressure has increased from the chamber toward the sealing surface and the sliding contact surface is repeatedly guided while flowing. Since the sealing surface is in sliding contact with the sliding contact surface of the rotation-side seal member with a contact pressure higher than the pressure of the raw rubber by the above-described pressing force applying mechanism with an oil film of lubricating oil interposed therebetween, Leakage is prevented.

    Here, in recent years, in response to a request for effective use of resources, while maintaining the sealing performance (leakage prevention performance of raw rubber), the supply amount of lubricating oil supplied to the sealing surface per unit time has been reduced. Although it was considered to reduce the total supply amount, if the supply amount per unit time of the lubricating oil is simply reduced, an oil film breakage occurs in the lubricating oil between the seal surface and the sliding contact surface. The sealing surface and the sliding surface are in direct sliding contact with each other, and the fixed side and rotating side sealing members are rapidly worn, and the temperature rises due to frictional heat and adversely affects the surroundings. In order to deal with such a situation, the present inventor has conducted earnest research, and the contact pressure in the overlapping region on the seal surface that is axially overlapped with the yoke pin is several times higher than the contact pressure in the other region, When the supply amount of lubricating oil per unit time is simply reduced, an oil film breakage occurs only in the polymerization region, and there is an oil film with a thickness that is too large in a region other than the polymerization region. In other words, in the past, since the lubricating oil was supplied to the extent that the oil film does not break in the polymerization region where the contact pressure is high, an oil film having an excessive thickness was formed in other regions other than the polymerization region. I found out.

The present invention has been made based on the above findings, and an object thereof is to provide a sealing Organization rubber agitation equipment which can be easily reduced the supply amount per unit time of the lubricating oil.

These objects, housings and sealing mechanisms for sealing between the housing and the stirring of the rubber stirring device and a stirring member for stirring the raw rubber charged into the agitation chamber in said housing by rotating A seal ring that is supported by the housing while only allowing movement in the axial direction and has a seal surface slidable in contact with the slidable contact surface of the stirrer, and a plurality of positions spaced circumferentially with respect to the seal ring By applying a pressing force toward the inner side in the axial direction, the seal surface of the seal ring is pressed against the sliding contact surface of the stirrer, and is formed on the seal ring and a pressing mechanism that prevents leakage of the stirred raw rubber, A guide passage for guiding a lubricating oil flow to a superposed region overlapping in the axial direction with the pressing force application position on the seal surface, and the guide passage is a portion away from the pressing force application position in the circumferential direction A plurality of through-holes formed in the seal ring and penetrating in the axial direction; a plurality of arc-shaped grooves formed in the seal surface of the seal ring and extending in the circumferential direction from the inner end opening of the through-hole to the overlapping region; and while forming a plurality away cooling jacket for cooling the seal rings by supplying and discharging a cooling fluid into the seal ring in the circumferential direction, respectively bridged by the arc-shaped grooves any of between the two cooling jackets in contact with adjacent This can be achieved by the sealing mechanism of the rubber stirring device.

  In the present invention, since the lubricating oil flow is guided to the overlapping region in the axial direction overlapping the pressing force application position on the sealing surface through the guide passage formed in the seal ring, the lubricating oil per unit time of the lubricating oil Even if the supply amount is reduced, a certain amount of lubricating oil is first supplied to the polymerization region, and as a result, the contact pressure in the polymerization region is several times higher than the other regions as described above. However, the oil film breakage of the lubricating oil in the polymerization region is effectively prevented. In addition, since the contact pressure is much lower than that in the polymerization region for the other regions between the polymerization regions, the lubricating oil supplied to the polymerization region is diffused between the seal surface and the sliding contact surface to have a substantially uniform thickness. By forming the oil film, it is effectively lubricated and the oil film is not cut. As a result, the supply amount of lubricating oil per unit time to the sealing surface can be easily reduced.

Also, with the induction passage can be easily and inexpensively formed, the site of the seal ring between the cooling jacket cooling with cooling jacket is not performed, and cooled by Jun Namerayu of Ru flow induction passage, said An increase in the temperature of the seal ring between the cooling jackets can be effectively suppressed.

1 is a schematic front sectional view showing Embodiment 1 of the present invention. It is a front view of the press mechanism vicinity. FIG. 3 is a cross-sectional view taken along the arrow I-I in FIG. 2. It is sectional drawing similar to FIG. 3 in the seal mechanism vicinity. It is a partially expanded side view of a rotating ring. It is a rear view of a seal ring. It is a front view of an end ring. It is the II-II arrow sectional drawing of the rotor in FIG. It is III-III arrow sectional drawing of FIG.

Embodiment 1 of the present invention will be described below with reference to the drawings.
1-4, 11 is a rubber stirring device for stirring raw rubber, here a Banbury mixer, a kneading device for stirring and kneading raw rubber such as kneader and chemicals (Banbury mixer in this embodiment). This rubber kneading device 11 is a pair of parallel rotors 12 rotating in opposite directions supported by axially opposite ends on a frame (not shown), and a housing 13 fixed to the frame and housing the axially central part of these rotors 12. have. The housing 13 includes a housing main body 18 and an end ring 55 which is detachably attached to the housing main body 18, and the housing main body 18 is a casing 14 which is hollow and has both axial ends open, A pair of side plates 15 that respectively close both axial ends of the casing 14; and an end plate 17 that is fixed to the side plates 15 and has loose fitting holes 16 in which the rotor 12 is loosely fitted. ing.

  On the other hand, each rotor 12 has a rotor shaft 20 that is coaxial with the loose fitting hole 16 and passes through the loose fitting hole 16, and an axial direction of the rotor shaft 20 in a kneading chamber 21 as a stirring chamber provided in the housing 13 A wing 22 is formed on the outer periphery of the central portion and protrudes while drawing a spiral. When the rotor 12 is rotated in the reverse direction by a drive source (not shown), the raw rubber charged into the kneading chamber 21 in the housing 13 is irregularly deformed and gradually drawn while being drawn between the rotor shafts 20 by the blades 22. Agitation, here kneading.

  An inlet 23 for feeding raw rubber is formed in the upper central portion of the housing 13, and a floating weight 24 for pushing the raw rubber put into the kneading chamber 21 downward is inserted into the inlet 23 so as to be movable up and down. Has been. On the other hand, the lower central portion of the housing 13 is formed with a discharge port 25 for discharging the raw rubber in a desired kneaded state to the outside. The discharge port 25 is supported by the housing 13 so as to be swingable. However, when the raw rubber is in a desired kneading state, the drop door 26 is opened by swinging downward, and the raw rubber is discharged to the outside (downward). In the present invention, as a stirring device, for example, a screw-type heating machine that heats raw rubber (only improving plasticity) may be used. In this case, the pair of screws corresponds to the stirring body.

  2 to 6, reference numeral 30 denotes a plurality of sealing mechanisms installed between the housing 13, specifically the end ring 55, and a stirrer 46 (rotor shaft 20), which will be described later, and seals between them. The seal mechanism 30 prevents leakage of chemicals, rubber, and the like from the kneading chamber 21 to the outside, and entry of dust, foreign matter, and the like from the outside into the kneading chamber 21. Here, the seal mechanism 30 has a substantially cylindrical seal ring 31 inserted into the loose fitting hole 16 via an end ring 55, and the rotor shaft 20 is loosely fitted in each seal ring 31. Yes.

  Each seal ring 31 is divided into a plurality of pieces in the circumferential direction, here divided into two divided pieces 31a having the same length in the circumferential direction, and these divided pieces 31a are a plurality of fastening bodies extending perpendicularly to the dividing surface, Here, the bolts 32 are detachably connected. In addition, circumferential grooves 33 that open in the outer periphery and extend in the circumferential direction shorter in the circumferential direction than the divided pieces 31a are formed on the outer side in the axial direction, which is the large diameter of each divided piece 31a. Is closed by a cover plate 34 fixed to the outer periphery of the split piece 31a. As a result, a plurality (two) of cooling jackets 35 extending in the circumferential direction and spaced apart in the circumferential direction are formed in each seal ring 31. As described above, the seal ring 31 is composed of the plurality of divided pieces 31a arranged in the circumferential direction. However, since the cooling jacket 35 is formed on each of the divided pieces 31a, the same number as the divided pieces 31a exists. Will do.

  Here, a supply pipe 37 is connected to one circumferential end of one cooling jacket 35, and a discharge pipe 38 is connected to the other circumferential end of the other cooling jacket 35. The other circumferential end and the other cooling jacket 35 are connected to each other by a connecting pipe 39. When a cooling fluid such as cooling water or cooling oil is supplied from the cooling source to the one cooling jacket 35 through the supply pipe 37, the cooling fluid is contained in one cooling jacket 35, the connecting pipe 39, and the other cooling jacket 35. Then, the exhaust gas is discharged to a discharge source (not shown) such as a tank through the discharge pipe 38 to cool the seal ring 31 around the cooling jacket 35. Thus, a plurality of cooling jackets 35 are formed in each seal ring 31 apart from each other in the circumferential direction by supplying and discharging the cooling fluid therein.

  42 is a substantially cylindrical collar loosely fitted in the inner end of the seal ring 31 close to the kneading chamber 21, and these collars 42 can rotate integrally with the rotor shaft 20 in the direction of the arrow. In addition, on the outer periphery of the inner end portion in the axial direction of these collars 42, a frustoconical inclined surface 42a that is inclined inward in the radial direction toward the inner side in the axial direction is formed. A ring-shaped rotary ring 43 that surrounds the collar 42 from the outer side in the radial direction and has the same diameter as the inner end of the seal ring 31 in the axial direction is provided outside the inner side in the axial direction of the collars 42. An inclined surface 43a having a frustoconical shape having the same gradient as the inclined surface 42a is formed on the inner periphery of the inner end portion 43 in the axial direction. The inner end of the collar 42 in the axial direction is inserted into the rotating ring 43 with the inclined surface 42a and the inclined surface 43a in surface contact. Further, both the inner end portions in the axial direction of the collar 42 and the rotating ring 43 are inserted into circumferential grooves 44 formed in both end surfaces in the axial direction of the blades 22 of the rotor 12 and extending in the circumferential direction.

  47 is a screw ring that is fitted on the rotor shaft 20 outside the collar 42 in the axial direction and rotates integrally with the rotor shaft 20, and a plurality of pressing screws 48 extending in the axial direction are screwed to these screw rings 47. Match. Then, when these pressing screws 48 are screwed in and the collar 42 is moved inward in the axial direction, the rotating ring 43 is pressed against the bottom wall (inner axial side surface) of the circumferential groove 44 by the wedge action of the inclined surfaces 42a, 43a, Accordingly, the rotating ring 43 is detachably attached so as to be able to rotate integrally with the rotor 12. In addition, a sliding contact layer 50 made of a wear-resistant metal such as a Ni—Cr—B—Si alloy (typically Colmonoy) is provided at the axially outer end of the rotating ring 43 adjacent to the seal ring 31. On the other hand, a sliding contact layer 51 made of a similar wear-resistant metal is also provided on the inner end in the axial direction of the seal ring 31 close to the rotating ring 43.

  The rotor 12, collar 42, screw ring 47, pressing screw 48, and rotating ring 43 described above as a whole rotate in the reverse direction to knead (stir) the raw rubber charged in the kneading chamber 21 in the housing 13. A stirring body 46 is formed. In the present invention, the agitator may be configured by integrally forming the rotating ring with the rotor. In this case, the collar 42, the screw ring 47, and the pressing screw 48 described above are unnecessary. The seal surface 53 formed at the inner end in the axial direction of the seal ring 31 (sliding contact layer 51) is at the outer end in the axial direction of the rotating ring 43 (sliding contact layer 50) constituting a part of the stirrer 46. The formed slidable contact surface 54 is slidably contacted by being rotated relative to the slidable contact surface 54, which will be described later, thereby preventing the stirred raw rubber from leaking from the kneading chamber 21 to the outside. 55 is a substantially cylindrical end ring. The end ring 55 is inserted into the loose fitting hole 16 of the end plate 17 from the outside in the axial direction, and then an end constituting a part of the housing 13 by a plurality of bolts 56. The plate 17 is detachably attached.

  Further, the end ring 55 surrounds the inner end portion in the axial direction of the seal ring 31 and the outer portion in the axial direction of the rotary ring 43 from the radially outer side, and the end ring 55 is interposed between the end ring 55 and the seal ring 31. On the other hand, a gap 59 is formed between the end ring 55 and the rotating ring 43. Further, a gap 60 is also formed between the inner end face in the axial direction of the end ring 55 and the outer end face in the axial direction of the blade 22 of the rotor 12, and these gaps 60 communicate with the gap 59. As a result, when raw rubber kneading proceeds and the plasticity of the raw rubber decreases, the raw rubber is intermittently pushed by the blades 22 of the rotor 12 and passes through the gaps 60 and 59 one after another, and the sealing surface 53, the slidable contact surface 54 may reach the slidable contact portion. At this time, if the contact pressure between the seal ring 31 and the rotating ring 43 (the contact pressure between the sliding contact layers 51 and 50) is higher than the pressure of the raw rubber, the raw rubber cannot push the seal ring 31 back outward in the axial direction. . In this case, the seal surface 53 and the slidable contact surface 54 maintain surface contact via an oil film of lubricating oil, and the raw rubber does not leak to the outside.

  Here, as shown in FIG. 7, the end ring 55 is divided into a plurality of pieces in the circumferential direction. Here, the end ring 55 is divided into two ring pieces 55a having the same length in the circumferential direction. When the ring piece 55a is attached to the end plate 17 by 56, both end faces in the circumferential direction of the ring pieces 55a are in surface contact to form one cylindrical body. In the present invention, the end ring 55 may be divided into three or more in the circumferential direction. If the end ring 55 can be divided into a plurality of parts in the circumferential direction in this way, raw rubber is clogged in a spiral groove, which will be described later, or it does not flow, or the rotating ring 43 and the end ring 55 are in direct contact with each other and are damaged. In such a case, since the end ring 55 can be easily removed prior to the rotating ring 43, the rotating ring 43 can be easily replaced.

  Reference numeral 65 denotes a plurality of oil passages formed in the end plate 17, and a supply pipe 66 (see FIG. 2) connected to the axial outer ends of these oil passages 65 is connected to a process oil supply source (not shown). On the other hand, the inner end of the oil passage 65 in the axial direction communicates with the gap 60. When process oil made of mineral oil or the like is supplied from the supply source to the kneading chamber 21 through the supply pipe 66 and the oil passage 65, the process oil softens the raw rubber during kneading and improves its fluidity. 67 is a fluid cylinder installed corresponding to each seal mechanism 30 and extending parallel to the rotor 12. The tip (inner end in the axial direction) of the piston rod 68 of each fluid cylinder 67 is coaxial with the piston rod 68 and is at the tip. (Axial inner end portion) is inserted into a base end portion (axial outer end portion) of the receiving rod 70 fitted in a fitting hole 69 formed in the side plate 15. A spring 71 is interposed between the flange portion provided at the axially outer end portion of the receiving rod 70 and the bottom surface of the fitting hole 69.

  72 is a plurality of yokes (the same number as the sealing mechanism 30) extending in the radial direction, and the radially outer end of each yoke 72 is connected to the cylinder case of the fluid cylinder 67, while the radially inner portion of the yoke 72 is As shown in FIG. 2, it is bifurcated and curved in an arc. A plurality of (two) yoke pins 73 extending in the axial direction, which are 180 degrees apart from each other in the circumferential direction, are fixed to the radially inner end of the yoke 72, and the axial inner ends of these yoke pins 73 are connected to the seal ring 31. Are respectively inserted into pin holes 74 formed in the outer end surface in the axial direction. Further, the portion of the yoke 72 divided into two forks, that is, the axially outer end portion of the support pin 75 extending in the axial direction fixed to the side plate 15 is inserted in a state of spherical contact with the central portion in the radial direction of the yoke 72, As a result, the yoke 72 can swing around the support pin 75.

  As described above, the radially outer end portion of the yoke 72 is connected to the side plate 15 via the fluid cylinder 67, the receiving rod 70, and the spring 71, and the radially central portion thereof is similarly connected to the side via the support pin 75. Further, two yoke pins 73 that are connected to the plate 15 and provided 180 degrees apart at the radially inner end of the yoke 72 are inserted into the pin holes 74 of the seal ring 31, respectively. 31 is supported by the housing 13 while being prevented from rotating around the axis, while only being allowed to move in the axial direction.

  When the fluid cylinder 67 is activated and the piston rod 68 protrudes, the yoke 72 swings around the support pin 75 so that the radially inner end moves inward in the axial direction. A predetermined pressing force is applied, and the contact pressure between the sliding contact layer 50 and the sliding contact layer 51 is maintained at a value higher than the pressure of the raw rubber that has entered the gap 59. The fluid cylinder 67, the receiving rod 70, the spring 71, the yoke 72, the yoke pin 73, and the support pin 75 described above apply a pressing force toward the inner side in the axial direction to the seal ring 31 as a whole. 53 is pressed against the sliding contact surface 54 of the stirrer 46 (rotating ring 43) to constitute a pressing mechanism 76 that prevents leakage of the raw rubber kneaded (stirred) from the kneading chamber 21 to the outside. In the present invention, as the above-described pressing mechanism, a compression spring, a screw mechanism for adjusting the compression amount of the compression spring, a cylinder, or the like may be used.

  78 is formed on the seal ring 31 at a position where a pressing force is applied from the pressing mechanism 76 to the seal ring 31, that is, at a position away from the arrangement position of the yoke pin 73 in the circumferential direction. A plurality of through holes penetrating through the outer periphery of the through holes 78 are connected to a lubricating oil supply source (not shown) via supply pipes 79. Further, the inner ends in the axial direction of these through holes 78 are open to the seal surface 53 of the seal ring 31 (sliding contact layer 51). As a result, the seal surface 53 of the seal ring 31 through the through hole 78, that is, the seal Lubricating oil made of mineral oil is supplied from the supply source between the surface 53 and the sliding contact surface 54, and an oil film of the lubricating oil is formed between the sealing surface 53 and the sliding contact surface 54.

  Here, a spiral groove 82 is formed on the inner side in the axial direction from the slidable contact surface 54, that is, on the stirring body 46 on the kneading chamber 21 side, specifically on the outer peripheral surface of the rotating ring 43. If the spiral groove 82 is formed on the outer peripheral surface of the stirring body 46 (rotating ring 43) axially inside the sliding contact surface 54 in this way, the raw rubber whose pressure has been increased by being pushed by the blade 22 as described above is transferred to the housing 13. When the seal surface 53 and the slidable contact surface 54 flow toward the slidable contact portion slidably contacting each other while passing through the gaps 60 and 59 one after another from the inner kneading chamber 21, the spiral groove 82 provided in the middle of this flow The resistance based on the pressure loss due to the rapid expansion of the cross-sectional area of the flow path is given to the raw rubber, and the pressure of the raw rubber decreases.

  As a result, although the pressure of the raw rubber is not changed on the kneading chamber 21 side from the spiral groove 82, the pressure of the raw rubber is reduced by the resistance on the seal surface 53 and the sliding contact surface 54 side from the spiral groove 82. Even if the pressing force applied from the mechanism 76 to the seal ring 31 is reduced, the sealing performance by the seal ring 31 and the rotating ring 43 can be sufficiently maintained. As described above, when the pressing force applied from the pressing mechanism 76 to the seal ring 31 is reduced, the contact pressure between the seal surface 53 and the sliding contact surface 54 is reduced. The supply amount per unit time of the supplied lubricating oil can be easily reduced without any problem.

  Here, since the spiral groove 82 spirally extends outward in the axial direction as it goes forward in the rotational direction (arrow direction) of the stirrer 46 (rotating ring 43), the sealing surface 53, the sliding surface as described above. The raw rubber that flows toward the sliding contact portion between the contact surfaces 54 and whose pressure is reduced by the spiral groove 82 is pushed back from the rear side wall in the rotational direction of the spiral groove 82 that rotates together with the stirrer 46 (rotating ring 43). Applied and pushed back toward the kneading chamber 21. In this way, a part of the plasticized raw rubber reciprocates between the sliding surface between the sealing surface 53 and the sliding surface 54 and the kneading chamber 21 while flowing in the gaps 59 and 60. The number of the spiral grooves 82 is 2 or 3 (3 in this case), and the spiral groove 82 is formed on the outer periphery of the rotating ring 43 by one turn. As a result, when the rotating ring 43 makes one rotation with the rotor 12, the raw rubber is pushed back to the kneading chamber 21 side by the amount corresponding to the lead of the spiral groove 82, that is, three pitches. When the number of spiral grooves 82 is 2 or 3, the raw rubber can be effectively pushed back toward the kneading chamber 21 while preventing the rubber kneading device 11 from becoming large.

Moreover, although the cross-sectional shape of the spiral groove 82 is rectangular as shown in FIGS. 4 and 5 in this embodiment, it may be triangular, U-shaped, or the like. The cross-sectional area of the spiral groove 82 is preferably in the range of 2.0 to 6.0 mm ² . The reason is that if the cross-sectional area is less than 2.0 mm ² , it is difficult to cause a sufficient pressure drop depending on the type of raw rubber, while if it exceeds 6.0 mm ² , the axial length of the rotating ring 43 is long. This is because the rubber kneading device 11 may become large. 84 is a plurality of inclined grooves formed on the outer end surface in the axial direction of the blade 22 on the radially outer side from the circumferential groove 44, here, the number of inclined grooves is the same as the number of the spiral grooves 82, and these inclined grooves 84 are circumferential. Are formed at an equal angle to each other (see FIG. 8). These inclined grooves 84 are inclined to the rear side in the rotational direction with respect to the radial direction, and as a result, the raw rubber that has entered the gap 60 is formed in the inclined grooves 84 when the rotor 12 rotates in the arrow direction. The rear side wall in the rotational direction is pushed and pushed back radially outward (toward the kneading chamber 21).

  In this way, since the raw rubber is pushed back radially outward (toward the kneading chamber 21) from the gap 60 by the inclined groove 84, the raw rubber whose pressure has been reduced becomes stronger in the kneading chamber 21 by the rotation of the rotor 12 in the arrow direction. It is pushed back and the raw rubber can be effectively removed from the spiral groove 82. In addition, as described above, the plurality of inclined grooves 84 are formed on the outer end surface in the axial direction of the blade 22 so that the raw rubber is pushed back toward the kneading chamber 21, so that the fluidity of the raw rubber is improved. The amount of process oil supplied through 65 can be reduced. In this embodiment, the radially inner ends of the inclined grooves 84 communicate with the axially inner ends of the corresponding spiral grooves 82. As a result, the raw rubber is smoothly smoothed by the spiral grooves 82 and the inclined grooves 84. It is pushed back into the kneading chamber 21.

  86 is a through hole formed in the housing 13, here in each end ring 55, with a radially inner end communicating with the gap 59. The through hole 86 of the housing 13 has a spiral groove 82, a seal surface 53, a sliding surface. A pressure sensor 87 for detecting the pressure in the gap 59 located between the housing 13 (end ring 55) and the stirrer 46 (rotating ring 43) is installed between the sliding surfaces of the contact surfaces 54. These pressure sensors 87 detect the pressure in the gap 59 and output the detection result to a control unit (not shown). If such a pressure sensor 87 is provided, when the sealing performance between the seal ring 31 and the rotating ring 43 is reduced and the raw rubber is about to leak to the outside, a sign of the leakage can be detected. Can be easily detected in advance.

  In addition, in the pressing force applying position where the pressing force is applied to the seal ring 31 from the pressing mechanism 76, that is, in the overlapping region 90 on the seal surface 53 that overlaps the arrangement position of the yoke pin 73 in the axial direction, the pressing mechanism 76 Under the influence of the pressing force, the contact pressure between the seal surface 53 and the sliding contact surface 54 is several times higher than the contact pressure in other regions other than the polymerization region 90, and as a result, the lubricating oil supplied from the through hole 78 is reduced. When the supply amount per unit time is small, the oil film of the lubricating oil is cut only in the polymerization region 90, although an oil film having an excessive thickness is formed in the other region. In order to cope with such a situation, in this embodiment, as shown in FIGS. 2, 4, 6, and 9, in addition to the through holes 78 described above, at least the through holes 78 are formed on the seal surfaces 53 of the seal rings 31. A plurality of arc-shaped grooves 91 extending in the circumferential direction from the axially inner end opening to the overlapping region 90 and covered by the sliding contact surface 54 of the rotating ring 43 are formed.

In this way, by forming the guide passage 92 including the through-hole 78 and the arc-shaped groove 91 in the seal ring 31 so as to guide the lubricant flow to the polymerization region 90 on the seal surface 53, the lubricant per unit time of the lubricant is obtained. Even if the supply amount is reduced, a certain amount of lubricating oil is first supplied to the polymerization region 90, and as a result, the contact pressure of the polymerization region 90 is smaller than the other regions as described above. Even if it is twice as high, it is possible to effectively prevent the oil film from running out of the lubricating oil in the polymerization region 90. Further, since the contact pressure is much lower than that in the polymerization region 90 for the other regions between the polymerization regions 90, the lubricating oil supplied to the polymerization region 90 diffuses between the seal surface 53 and the sliding contact surface 54 and is substantially By forming an oil film having a uniform thickness, the oil film is effectively lubricated and the oil film is not cut. As a result, the supply amount of the lubricating oil per unit time to the seal surface 53 can be easily reduced .

Here, each arcuate groove 91 extends from the inner end opening in the axial direction of the through-hole 78 to at least the polymerization region 90 in the forward direction of the stirring body 46 in the rotation direction (arrow direction in FIG. 6). In this way, a part of the lubricating oil that has flowed out from the inner end opening of the through hole 78 to the sealing surface 53 is dragged in the rotational direction by the sliding contact surface 54, so that the flow is accelerated and smoothly guided to the polymerization region 90. be able to. Also, each has the cooling jacket 35 as described above formed with a plurality away seal ring 31 in the circumferential direction, in this embodiment, by the arcuate grooves 91 also either between adjacent contact two cooling jackets 35 In other words, both ends in the circumferential direction of each arcuate groove 91 overlap with the circumferential end of the adjacent cooling jacket 35 on the side close to the arcuate groove 91. As described above, if any of the two adjacent cooling jackets 35 is bridged by the arc-shaped grooves 91, the portion of the seal ring 31 between the cooling jackets 35 that is not cooled by the cooling jacket 35 is obtained. Cooling is performed by the lubricating oil flowing through the arc-shaped groove 91, and the temperature rise of the seal ring 31 between the cooling jackets 35 can be effectively suppressed.

  Here, the radial groove width L of each arcuate groove 91 described above is preferably in the range of 1/16 to 3/16 times the radial width M of the seal surface 53. The reason is that if the groove width L is less than 1/16 times the width M, depending on the type of the lubricating oil, it may not be possible to guide the required amount of lubricating oil flow to the polymerization region 90. If it exceeds 16 times, the contact area between the seal surface 53 and the sliding contact surface 54 may decrease and the oil film of the lubricating oil may be cut off. However, within the above range, the sealing surface 53 and the sliding contact surface 54 This is because the necessary amount of lubricating oil flow can be surely guided to the polymerization region 90 while ensuring an appropriate contact area with. In addition, the cross-sectional shape of the arc-shaped groove 91 described above is rectangular as shown in FIG. 9 in this embodiment, but may be triangular, U-shaped, or the like.

Next, the operation of the first embodiment will be described.
When raw rubber is introduced into the housing 13 of the rubber kneading device 11 through the insertion port 23, the pair of rotors 12 are rotated in the reverse direction by the driving source, whereby the charged raw rubber is fed by the blades 22 of the rotor 12. It is irregularly deformed while being drawn between the rotor shafts 20 and gradually stirred, here kneaded. At this time, the lubricating oil is supplied from the supply source to the sealing surface 53 (between the sealing surface 53 and the sliding contact surface 54) through the through-hole 78, and the lubricating oil film is formed between the sealing surface 53 and the sliding contact surface 54. And the rotation of the rotor 12 is made smooth. When the raw rubber is kneaded and the plasticity decreases, the raw rubber is intermittently pushed by the blades 22 of the rotor 12 to flow through the gaps 60 and 59, and the seal surface 53 and the sliding contact surface 54 It may reach the sliding contact part.

  At this time, the fluid cylinder 67 of the pressing mechanism 76 is activated, so that the yoke 72 swings around the support pin 75 so that the radially inner end moves inward in the axial direction. A pressing force toward the inner side in the axial direction is applied to the ring 31, and the seal surface 53 of the seal ring 31 comes into sliding contact while being pressed against the sliding contact surface 54 of the agitator 46 (rotating ring 43). Here, if the contact pressure between the seal ring 31 and the rotating ring 43 is maintained at a value higher than the pressure of the raw rubber that has entered the gap 59, leakage of the stirred (kneaded) raw rubber to the outside is prevented. Can be blocked.

  At this time, as described above, the seal ring 31 is formed with the guide passage 92 that guides the lubricating oil flow to the overlap region 90 on the seal surface 53, so that the overlap region 90 is several times higher in contact pressure than the other regions. A certain amount of lubricating oil is initially supplied by induction through the induction passage 92. As a result, even when the supply amount of the lubricating oil per unit time is reduced, it is possible to effectively prevent the lubricating oil film from being cut off in the polymerization region 90, whereby the lubricating oil per unit time with respect to the seal surface 53 can be prevented. The supply amount of can be easily reduced. Note that, with respect to the other regions between the polymerization regions 90, the contact pressure is considerably lower than that of the polymerization region 90, so the lubricating oil supplied to the polymerization region 90 diffuses between the seal surface 53 and the sliding contact surface 54 and is substantially By forming an oil film having a uniform thickness, the oil film is effectively lubricated and the oil film is not cut.

  The present invention can be applied to the industrial field of sealing between a housing and a stirrer of a rubber stirrer provided with a housing and a stirrer that stirs the raw rubber in the housing.

11… Rubber stirring device 13… Housing
21… Stirrer chamber 30… Seal mechanism
31… Seal ring 35… Cooling jacket
46… Stirrer 53… Seal surface
54 ... Sliding contact surface 76 ... Pressing mechanism
78 ... Through hole 90 ... Polymerization region
91 ... Arc-shaped groove 92 ... Guide passage L ... Groove width M ... Width

Claims (1)

A seal mechanism that seals between a housing and a stirrer of a rubber stirrer that includes a housing and a stirrer that stirs the raw rubber introduced into the stirrer chamber in the housing by rotation, A seal ring that is supported while only allowing movement in the axial direction and whose seal surface can be slidably contacted with the slidable contact surface of the stirrer, and a pressing force directed inward in the axial direction at a plurality of positions that are circumferentially separated from the seal ring Is applied to the sliding contact surface of the stirrer to prevent leakage of the stirred raw rubber, and the pressing force is formed on the seal ring. A guide passage that guides the lubricant flow to the application region and the overlapping region in the axial direction, and the guide passage is formed in a seal ring at a portion that is circumferentially separated from the pressing force application position. A plurality of through-holes penetrating in the axial direction, and a plurality of arc-shaped grooves formed on the seal surface of the seal ring and extending in the circumferential direction from the inner end opening of the through-hole to the overlapping region, and the seal ring while several forms apart a cooling jacket for cooling the circumferential direction the sealing ring by supplying and discharging a cooling fluid within, either between neighboring contacts two cooling jacket was set to bridge respectively by said arc-shaped grooves A rubber stirring device sealing mechanism characterized by the above.

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