JP2009052481A - Fluid discharge device and extruder - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To surely protect a bearing by preventing contact of fluid with a bearing supporting a rotary shaft of a rotary body in a discharge device such as a gear pump discharging fluid by a rotary body. <P>SOLUTION: Reverse screw shape spiral grooves 22B, 22C, 23B, 23C feeding back rubber which is fluid leaking along rotary shafts 22, 23 to gear 20, 21 side are formed on the rotary shafts 22, 23 of the gear pump 10, and discharge flow paths 40, 41 discharging leaking rubber to an outside are provided between the grooves and bearings 37, 38. Seal members 42, 43 sealing circumferences of the rotary shafts 22, 23 are disposed in a sealed manner between the discharge flow paths 40, 41 and bearings 37, 38, and rubber heading for the bearings 37, 38 is shut off and is prevented from contacting the bearings 37, 38. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a fluid discharge device such as a gear pump (gear pump) that discharges a fluid such as unvulcanized rubber as a rotating body rotates, and an extruder that forms an extrusion-molded product including the fluid discharge device.

  When forming a rubber member, for example, a rubber member constituting a tire, an unvulcanized ribbon rubber is extruded and laminated by spirally winding the outer surface of a rotating support, etc., and forming a predetermined cross-sectional shape To be done. Such unvulcanized rubber has a high viscosity, and it is necessary to use a high-pressure rubber extruder capable of extruding rubber at a high pressure for extrusion molding. Mainly, a fluid discharge device such as a pressurized high-pressure rubber is used. An extruder equipped with a gear pump capable of quantitative discharge is used (see, for example, Patent Document 1).

  By the way, as a gear pump for unvulcanized rubber, a housing (casing) has a pair of gears (meshing gears) that are rotating bodies, a rotating shaft that rotates integrally with each gear, and each rotating shaft. An external gear pump having a pair of bearings and the like that are disposed with a gear interposed therebetween and rotatably support a rotating shaft is widely used. Although such gear pumps are excellent in quantitative discharge performance, etc., the pressurized rubber tends to leak along the rotating shaft through the housing and the gear, rotating shaft, etc. Therefore, it is necessary to prevent the rubber functioning from coming into contact with and entering the bearing such as a bearing. On the other hand, conventionally, various seal members such as a seal ring and an O-ring formed of an elastic body are arranged in a sealing manner around the rotation shaft between the gear of the rotation shaft and each bearing. Therefore, it is common to protect the bearing by suppressing the leakage of rubber toward the bearing.

  However, with such a seal member, it is difficult to completely stop and stop the leakage of rubber along the rotating shaft. In practice, a part of the pressurized rubber leaks beyond the seal member. This is unavoidable, and it is difficult to reliably prevent contact between the rubber and the bearing. For this reason, in this conventional bearing protection method, the leaked rubber comes into contact with the bearing and enters the inside of the bearing, causing the bearing to break or break down, or the wear of the rotating part of the bearing is accelerated due to contact with the rubber. May progress. Further, with the progress of the wear of the bearing, there arises a problem that the accuracy of regulating the rotational position of the gear is lowered, the rotational accuracy of the gear is lowered, and the quantitative transfer accuracy for the rubber is also lowered. On the other hand, in order to deal with each of these problems, when the number of replacements of the bearings and the maintenance of the equipment including the bearing parts is increased, the labor and time required for that increase, etc. The problem of deteriorating arises.

  Therefore, conventionally, in order to cope with the above-described problems, in a fluid discharge device such as a rubber having high viscosity, a configuration for leading (discharging) the leaked rubber to the outside of the device is provided so that the rubber contacts the bearing. A gear pump is also known (see Patent Document 2).

FIG. 3 is a cross-sectional view showing this conventional gear pump, which is a schematic view cut along a plane including the axial direction of both rotary shafts.
As shown in the figure, the gear pump 100 is formed on both sides of the rotary shafts 111 and 112 with the gears 101 and 102 interposed therebetween, and rubber leaked from the gears 101 and 102 toward the bearings 104 and 105 on both sides is gear 101. , 102 reverse threaded spiral grooves 111A, 111B, 112A, 112B for feeding back to the side, and rubber containing chambers 106, 107 provided around the rotating shafts 111, 112 on the bearings 104, 105 side, It has.

  In the gear pump 100, rubber leaking in the direction of the bearings 104 and 105 beyond the spiral grooves 111A, 111B, 112A, and 112B along the rotation shafts 111 and 112 is collected by the storage chambers 106 and 107, and discharged into the discharge passage 108. , 109, and through these discharge passages, the rubber is prevented from being discharged to the outside of the housing 103 and coming into contact with the bearings 104, 105.

  However, in this conventional gear pump 100, the effect of suppressing the leakage of rubber into the storage chambers 106 and 107 is not sufficient, and depending on the amount of rubber leaking into the storage chambers 106 and 107, the leaked rubber may become a rotating shaft. The bearings 104 and 105 may be reached along the lines 111 and 112. As a result, the rubber may come into contact with the bearings 104 and 105 and enter the inside thereof, and the bearings 104 and 105 may be damaged or broken, or the same problems as described above may occur. At the same time, the amount of rubber discharged from the storage chambers 106 and 107 to the outside may increase, and the rubber discharge amount and discharge efficiency may decrease.

  Further, in this gear pump 100, lubricating oil, grease, or the like enters the gears 101, 102 along the rotating shafts 111, 112 from the bearings 104, 105 side and comes into contact with the rubber, which may reduce the quality of the rubber. There is also. Similarly, when lubricating oil or grease adheres to the rubber discharged from the storage chambers 106 and 107, the discharged rubber cannot be reused and must be discarded. There is also a problem that increases.

  The above problems may occur not only in the gear pump 100 that discharges rubber but also in other fluid discharge devices that discharge fluid by rotating a rotating body, such as an internal gear pump. It is necessary to prevent the deterioration of fluid quality while ensuring more reliable protection of each bearing.

JP 2004-216826 A JP-A-5-340359

  The present invention has been made in view of the problems of the conventional fluid discharge device that discharges a fluid by rotating such a rotating body, and the object thereof is to contact the bearing that supports the rotating shaft of the rotating body. And preventing the deterioration of the fluid quality as well as protecting the bearing more reliably.

The invention of claim 1 includes a rotating shaft that rotates integrally with the rotating body, and a bearing that rotatably supports the rotating shaft, and discharges fluid by rotating the rotating body. A fluid discharge device provided with a discharge flow path for discharging the fluid leaked along the rotation shaft to the outside between the rotating body and the bearing, wherein the discharge flow path of the rotation shaft and the bearing A sealing member for sealing the periphery of the rotating shaft is disposed between the two.
The invention of claim 2 includes a rotating shaft that rotates integrally with the rotating body, and a bearing that rotatably supports the rotating shaft, discharges fluid by rotating the rotating body, and A fluid discharge device provided with a discharge passage for discharging the fluid leaked along the rotation axis between the rotating body and the bearing, wherein the rotation is provided on a side surface in the axial direction of the rotating body. An annular protrusion provided concentrically with the body, and an annular recess provided on an inner surface opposite to the annular protrusion, which receives the annular protrusion and engages the annular protrusion so as to be movable in the rotation direction of the rotating body. And a groove.
The invention of claim 3 comprises a rotating shaft that rotates integrally with the rotating body, and a bearing that rotatably supports the rotating shaft, discharges fluid by rotating the rotating body, and A fluid discharge device provided with a discharge channel for discharging the fluid leaked along the rotation axis between the rotating body and the bearing, wherein the rotation is provided on a side surface in the axial direction of the rotating body. An annular groove provided concentrically with the body, and an inner surface facing the annular groove, and is accommodated in the annular groove so that the annular groove is movable in the rotation direction of the rotating body. And an annular protrusion to be joined.
According to a fourth aspect of the present invention, in the fluid ejection device according to any one of the first to third aspects, a seal that seals the periphery of the rotating shaft between the rotating body of the rotating shaft and the discharge flow path. A member is arranged.
According to a fifth aspect of the present invention, in the fluid ejection device according to any one of the first to fourth aspects, the fluid is an unvulcanized rubber.
The invention of claim 6 is an extruder for extruding a fluid to form an extruded product, and supplying means for supplying the fluid and discharging the fluid supplied from the supplying means. 5. A fluid discharge device according to any one of claims 5 to 5, and a base provided on a fluid discharge port side of the fluid discharge device for extruding and shaping the fluid.

  ADVANTAGE OF THE INVENTION According to this invention, it can prevent that a fluid contacts the bearing which supports the rotating shaft of the rotary body with which a fluid discharge apparatus is provided, can protect a bearing more reliably, and suppress generation | occurrence | production of the quality deterioration of a fluid. Can do.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
The fluid discharge device of the present embodiment is similar to the above-described conventional device, for example, a rotating body housed in a housing (casing) such as various gear pumps, a rotating shaft that rotates integrally with the rotating body, and a rotating shaft Is a device that includes a bearing or the like that rotatably supports the bearing and rotates the rotating body to discharge the fluid supplied to the inside of the housing.

  In the present embodiment, an external gear pump (hereinafter referred to as a gear pump) that discharges a pressurized fluid in a fixed amount (constant volume) is used as the fluid discharge device. A case where a certain unvulcanized rubber (hereinafter simply referred to as rubber) is discharged at a predetermined pressure will be described as an example. In the following, this gear pump is applied to the above-described high-pressure rubber extruder, that is, high-pressure rubber is extruded by an extruder equipped with this gear pump, and is an extruded product, for example, a rubber member constituting a tire. An example of forming a ribbon-like rubber used for forming will be described.

FIG. 1 is a main part side view schematically showing a schematic configuration of an extruder according to the present embodiment, and a part of the internal configuration is seen through and indicated by a broken line.
As shown in the figure, the extruder 1 includes a substantially cylindrical cylinder 3 (only the tip is shown in the figure) provided in the extruder body 2 and a gear pump 10 attached to the tip.

  The extruder main body 2 is a rubber supply means for supplying rubber to the gear pump 10. Here, the raw material rubber supplied from a hopper (not shown) rotates while being heated in the inside 3 </ b> A of the cylinder 3 (see FIG. The rubber is continuously fed into the gear pump 10 (arrow F in the figure).

  The gear pump 10 includes a pair of gears (meshing gears) 20 and 21 that are rotating bodies that rotate in opposite directions (arrows K1 and K2 in the figure), and a housing portion (high pressure chamber) formed inside the gears 20 and 21. And a housing 30 accommodated in the housing 11. Here, the gears 20 and 21 are spur gears formed in substantially the same shape, and are arranged in the accommodating portion 11 so as to mesh with each other, and are rotatably accommodated and supported while maintaining the state. On the other hand, the housing 30 has a rubber introduction port 12 communicating with the inside 3A of the cylinder 3 and a rubber discharge port (extrusion port) 13 opened on the other end surface with the housing portion 11 interposed therebetween. 11 is formed in communication.

  The gear pump 10 rotates the gears 20 and 21 in a direction opposite to each other at a predetermined speed, and both the gears rotating the rubber supplied to the rubber introduction port 12 from the tip of the extruder body 2 (arrow F in the figure). It takes in between each tooth space part (interdental part) of 20 and 21, and the wall surface of the accommodating part 11, and carries out rotational transfer (conveyance) by predetermined amount toward the rubber discharge port 13 side. The gear pump 10 discharges the transferred rubber from the tooth groove portion on the rubber discharge port 13 side, discharges the rubber from the rubber discharge port 13 by a predetermined amount, and continuously discharges the fixed amount toward the outside of the apparatus (arrow H in the figure). The extruder 1 extrudes the rubber discharged under pressure in this way from an opening (rubber extruding portion) of a base (not shown) provided at the tip of the gear pump 10 on the rubber discharge port 13 side. A rubber member having a cross-sectional shape (here, ribbon-like rubber) is continuously formed.

Next, the structure of the gear pump 10 of this embodiment will be described in more detail.
FIG. 2 is a partial cross-sectional view of the gear pump 10 as seen from the direction of the arrows X-X in FIG. 1, and schematically shows the schematic configuration thereof.
As illustrated, the gear pump 10 includes rotating shafts 22 and 23 that rotate integrally with the gears 20 and 21 described above, and supports the rotating shafts 22 and 23 in a housing 30 so as to be rotatable.

  The rotating shafts 22 and 23 extend from both side surfaces of the gears 20 and 21 in the housing portion 11 to the outside of the housing portion 11 concentrically with the gears 20 and 21, respectively, and have a substantially cylindrical shape having steps. The smaller diameter portions 22 </ b> A and 23 </ b> A are formed on the outer side (end portion side) in the axial direction than the larger diameter portions on the gears 20 and 21 side. In addition, the rotary shafts 22 and 23 have one (downward in the figure) rotary shaft 23 as a drive shaft and the other (upward in the figure) rotary shaft 22 as a driven shaft. When the rotary shaft 23 is rotationally driven by a known driving means including a transmission mechanism that transmits force, the other gear 20 and the rotary shaft 22 that mesh with the rotary shaft 23 are connected to the housing 30 via the gear 21 (see FIG. 1). Rotate synchronously within.

  The housing 30 includes a case outer peripheral portion 31 disposed so as to cover the entire gears 20, 21 from the outer peripheral side, and a pair of case side portions 32, 33 disposed opposite to both side surfaces of the gears 20, 21. And a pair of side plates 34 and 35 disposed on both outer sides of the case side surfaces 32 and 33 so as to be spaced apart from each other.

  In the housing 30, the housing portion 11 is formed in the center portion of the outer peripheral portion 31 of the case so that the gears 20 and 21 are housed and the inner surface is in sliding contact (sliding) with each tooth outer surface, and the openings on both side surfaces are closed. As described above, a pair of substantially plate-like case side surface portions 32 and 33 are disposed and attached to each of the inner edge portions of the case outer peripheral portion 31. The housing 30 divides the housing portion 11 (see FIG. 1) for housing the gears 20 and 21 by the case outer peripheral portion 31 and the case side surface portions 32 and 33, and the gears 20 and 21 are disposed inside thereof. A case that is housed away from the outside is formed, and the rubber introduction port 12 and the rubber discharge port 13 are formed at predetermined positions substantially opposite to each other with the housing portion 11 of the case outer peripheral portion 31 interposed therebetween.

  In addition, here, the inner surfaces (inner side surfaces of the housing portion 11) of the case side surfaces 32 and 33 facing the gears 20 and 21 are formed in a shape corresponding to the side surfaces of the gears 20 and 21, and they can slide on each other. It is made to contact. In addition, each case side surface portion 32, 33 is formed with a shaft hole (through hole) having a diameter corresponding to the diameter through which each of the rotation shafts 22, 23 is rotatably passed. Each of the rotary shafts 22, 23 accommodates a portion in which spiral grooves 22B, 22C, 23B, 23C, which will be described later, are formed in the shaft hole, and passes through each shaft hole to a pair of outer sides. It arrange | positions so that it may extend to the side plates 34 and 35. FIG.

  The side plates 34 and 35 have a substantially rectangular plate shape, and are each attached with a plurality of spacers (collars) 36 having a predetermined thickness between the side surfaces of the case outer peripheral portion 31 and the side surfaces of the case outer peripheral portion 31 and the case. Opposite to the outer surfaces of the side portions 32 and 33, they are arranged substantially in parallel with a predetermined distance therebetween. In the present embodiment, these spacers 36 (see FIG. 1) are formed in a cylindrical shape (here, substantially cylindrical), and each of the four side plates 34 and 35 is approximately diagonally relatively close to the corners. Screws and bolts are inserted into the inner diameter portion of the spacer 36 from the through holes of the side plates 34 and 35 formed at the same position and screwed into the screw holes formed in the outer peripheral portion 31 of the case. , 35 are fixed to the outer peripheral portion 31 of the case. Accordingly, the space between the side plates 34 and 35 of the housing 30 and the case outer peripheral portion 31 and the case side surface portions 32 and 33 is a space (gap) where all portions other than the spacer 36 are open to the outside. Yes.

  In this gear pump 10, voids are formed in the housing 30 along the inner surfaces of the side plates 34 and 35 in this way, and the outer peripheral surfaces of the rotary shafts 22 and 23 passing through the same portion are externally extended over the entire circumferential direction. The voids connecting the outer peripheral surfaces of the rotary shafts 22 and 23 and the outside of the housing 30 are used as discharge passages 40 and 41 for discharging leakage rubber to be described later. Further, the small diameter portions 22A and 23A on the outer side (end side) of the rotary shafts 22 and 23 are inserted into shaft holes formed in the side plates 34 and 35 with respect to the left and right discharge flow paths 40 and 41, respectively. The bearings 37 and 38 such as ball bearings, roller bearings, or needle bearings attached to the inner surface of the shaft hole support both end portions of the rotary shafts 22 and 23 so that their axial directions are parallel to each other. is doing.

  In addition to the above, when the gear pump 10 rotates the gears 20, 21 and the rotation shafts 22, 23 to discharge rubber or the like, the above-described pressurized rubber leaks from the housing portion 11, and the rotation shaft 22, , Bearing protection means for preventing leakage along the shaft 23 and contact with the bearings 37 and 38. In the present embodiment, the bearing protection means is constituted by a plurality of types of means provided between the gears 20 and 21 of the rotary shafts 22 and 23 and the bearings 37 and 38, and the protection function of the bearings 37 and 38 is provided. It is strengthening.

  Specifically, in this gear pump 10, as a bearing protection means, a spiral groove 22B formed on the outer peripheral surface of the rotary shafts 22, 23 between the gears 20, 21 of the rotary shafts 22, 23 and the bearings 37, 38, 22C, 23B, and 23C and the above-described discharge flow paths 40 and 41 provided between them and the bearings 37 and 38 are sequentially arranged, respectively. Further, seal members 42 and 43 are arranged on the side surfaces (inner side surfaces) of the side plates 34 and 35 on the discharge flow paths 40 and 41 side, and annular projections (projections) 20A and 21A are formed on both side surfaces of the gears 20 and 21. These constitute the bearing protection means.

  The spiral grooves 22B, 22C, 23B, and 23C are grooves having a concave cross section for feeding rubber leaked from the accommodating portion 11 along the rotary shafts 22 and 23 back to the gears 20 and 21, respectively. , 23 on the outer peripheral surfaces on both sides of the gears 20 and 21, in a spiral manner with a predetermined pitch and inclination angle from the vicinity of the side surfaces of the gears 20 and 21 toward the outer side in the axial direction, or in parallel. A plurality of lines are formed. Further, the spiral grooves 22B, 22C, 23B, and 23C are located in the above-described shaft holes of the case side surface portions 32 and 33, and extend over the entire outer peripheral surface facing the inner surface of the shaft hole. When the shaft rotates in a predetermined direction, it is formed in a reverse screw shape with respect to the rotation direction of each of the rotating shafts 22 and 23 so that a force in the direction opposite to the leakage direction acts on the leakage rubber in the shaft hole. . Accordingly, the spiral grooves 22B, 22C, 23B, and 23C of the rotary shafts 22 and 23 have spiral shapes opposite to each other across the gears 20 and 21, and the gears 20, 21 are rotated along with the rotation of the rotary shafts 22, 23. Pressure is applied to the rubber leaking in the direction of the bearings 37 and 38 on both sides from the gears 20 and 21 in the direction of the gears 20 and 21 (inward in the axial direction), and the pressure is sent back to the gears 20 and 21. , 21 has a function of pushing back into the operation (rotation) region (accommodating portion 11).

  On the other hand, the rubber leaked to the outside of the case side surfaces 32 and 33 without being fed back by the spiral grooves 22B, 22C, 23B and 23C of the rotary shafts 22 and 23, the gears 20 and 21 and the bearing 37, 38 are collected by being peeled off from the outer peripheral surfaces of the rotary shafts 22 and 23 by the discharge channels 40 and 41 provided between the rotary shafts 38 and 41. The discharge passages 40 and 41 are leakage rubber discharge passages for discharging (leading out) leaked rubber to the outside of the apparatus. The rubber leaking into the discharge passages 40 and 41 along the rotary shafts 22 and 23 is Then, it falls in the discharge passages 40 and 41, is discharged to the outside of the housing 30, and is prevented from reaching the bearings 37 and 38.

  Here, in this embodiment, in order to further improve the protection function of the bearings 37 and 38, the rotation shafts are respectively disposed between the discharge passages 40 and 41 of the rotation shafts 22 and 23 and the bearings 37 and 38, respectively. The above-described seal members 42 and 43 that seal the periphery of the portions 22 and 23 are arranged to protect the bearings 37 and 38 more reliably.

  The seal members 42 and 43 are sealed against the outer peripheral surfaces of the rotary shafts 22 and 23, such as a seal ring or O-ring formed of an elastic body such as a synthetic resin, or a metal seal ring using metal elasticity. It is a well-known sealing means that can be arranged in a shape, and is sandwiched between the fixing members 44 and 45 and the side plates 34 and 35 and is in close contact with the side surfaces of the side plates 34 and 35. The fixing members 44 and 45 are substantially plate-like members and are detachably attached to the side plates 34 and 35 by fastening means such as screws. The fixing members 44 and 45 are formed with substantially annular recesses (stepped portions) of a size capable of accommodating the sealing members 42 and 43 around the shaft holes through which the rotary shafts 22 and 23 pass. The seal members 42 and 43 are accommodated inside and disposed around the rotary shafts 22 and 23. In this state, the seal members 42 and 43 are in close contact with the opposing surfaces of the fixing members 44 and 45, and are axially inside (here, the rotation shafts) of the portions supported by the bearings 37 and 38 of the rotation shafts 22 and 23. The rotary shafts 22 and 23 are in contact with the outer peripheral surface in a rotatable state, such as slidably contacting (sliding contact) with the respective outer peripheral surfaces of the stepped portions 22 and 23 described above. . Thereby, the sealing members 42 and 43 seal and seal the periphery of the contact portion of the rotary shafts 22 and 23.

  Further, in this gear pump 10, annular protrusions 20 </ b> A and 21 </ b> A that continuously extend along the circumferential direction are provided on both side surfaces in the axial direction of the gears 20 and 21 so as to protrude from the side surfaces. Each of the annular protrusions 20A and 21A is rotated into a protrusion (wall shape) having a predetermined cross-sectional shape (here, a substantially rectangular shape) such as a substantially rectangular shape or a triangular shape, and the tooth bottom position of the gears 20 and 21. They are formed concentrically with the outer peripheral surfaces of the shafts 22 and 23 (here, substantially at intermediate positions).

  On the other hand, the inner surface of the housing 30 that faces each of the annular protrusions 20A and 21A, that is, the side surface facing the housing portion 11, and the inner side surfaces of the case side surfaces 32 and 33 correspond to the annular protrusions 20A and 21A. Shaped annular grooves M are formed at opposing positions. Each of the annular grooves M accommodates the corresponding annular protrusions 20A and 21A, and the annular protrusions 20A and 21A are engaged with each other so as to be movable (slidable) in the rotational direction of the gears 20 and 21. The engaging portion is formed in a position, shape and size, and is formed in a concave shape having a substantially rectangular cross section corresponding to the annular protrusions 20A and 21A, and can accommodate the entire annular protrusions 20A and 21A.

  As described above, the annular protrusions 20A and 21A provided on the side surfaces of the gears 20 and 21 can move (turn) in the rotation direction of the gears 20 and 21 in the annular grooves M provided to face each other. In addition to being accommodated, the gears 20 and 21 are maintained in an engaged state so that at least a part of the gears 20 and 21 is slid. Thereby, the gear pump 10 suppresses the rubber in the accommodating portion 11 from passing through between the side surfaces of the gears 20 and 21 and the case side surfaces 32 and 33 and leaking to the rotating shafts 22 and 23, and thereby each spiral groove. The amount of rubber leaking to 22B, 22C, 23B, 23C and the discharge passages 40, 41 is reduced.

  In the gear pump 10 of the present embodiment described above, the rubber leaked along the rotary shafts 22 and 23 beyond the spiral grooves 22B, 22C, 23B, and 23C is discharged from the discharge passages 40 and 41 to the outside of the apparatus. It is possible to prevent the rubber from leaking and contacting the bearings 37 and 38 along the rotary shafts 22 and 23. Further, since the seal members 42 and 43 are arranged between the discharge flow paths 40 and 41 and the bearings 37 and 38 to seal the periphery of the rotary shafts 22 and 23, the discharge flow paths 40 and 41 side of the bearings 37 and 38 are provided. The rubber can be blocked from moving in the direction of the bearings 37 and 38 from the discharge flow paths 40 and 41.

  As a result, it is possible to surely prevent the rubber from reaching and contacting the bearings 37 and 38 and effectively prevent the rubber from entering the bearings 37 and 38, thereby protecting the bearings 37 and 38 more reliably. 38, it is possible to prevent breakage or failure due to contact with the rubber described above, or progression of wear. Along with this, a reduction in the bearing function of the bearings 37 and 38, such as the precision of regulating the rotational positions of the gears 20 and 21 by the bearings 37 and 38, is suppressed, and the rotational accuracy of the gears 20 and 21 and the quantitative determination with respect to the rubber. It is also possible to maintain the transfer accuracy at a sufficient height over a long period of time. In addition, the number of replacements of the bearings 37 and 38, the number of maintenance of the apparatus including the bearings 37 and 38, labor and time for the same, and the operation rate and productivity of the apparatus can be improved.

  Thus, the sealing effect of the seal members 42 and 43 further enhances the protection effect of the bearings 37 and 38, and at the same time, lubricating oil, grease, and the like move from the bearings 37 and 38 along the rotary shafts 22 and 23. Even in such a case, they can be blocked to prevent entry into the discharge channels 40 and 41 and further transmission. As a result, the contact between the lubricating oil or grease and the rubber can be avoided, and the deterioration of the rubber quality can be suppressed. In addition, since it is possible to avoid contact with and adhesion of lubricating oil or grease to the rubber leaked into the discharge passages 40 and 41, the rubber discharged from the rubber can be reused, and the rubber is wasted by disposal. The amount of can also be reduced.

  Further, in this gear pump 10, the rubber in the accommodating portion 11 is difficult to leak out due to the annular protrusions 20A and 21A provided on the side surfaces of the gears 20 and 21 and the annular groove M engaged therewith. Even when the pressure of the rubber is relatively high, the rubber can be prevented from leaking to the rotating shafts 22 and 23 side. Therefore, the amount of rubber leaking to the discharge passages 40 and 41 can be further reduced, and the contact between the rubber and the bearings 37 and 38 can be more reliably prevented, and the protection effect of the bearings 37 and 38 can be further increased. Can be increased. At the same time, since the amount of rubber discharged to the outside through the discharge channels 40 and 41 decreases, there is also an opportunity for the above-mentioned lubricating oil and the rubber to come into contact with the rubber while suppressing a decrease in the discharge amount and discharge efficiency of the rubber. It is also possible to suppress the occurrence of deterioration in rubber quality.

  Here, in addition to the seal members 42 and 43 of the present embodiment, a second seal member that seals the periphery of the similar rotary shafts 22 and 23 is used as the gears 20 and 21 of the rotary shafts 22 and 23 and the discharge flow path 40. , 41 may be further arranged. That is, the outer periphery of the rotating shafts 22 and 23 is obtained by, for example, sandwiching the seal member between the side surfaces of the case side surfaces 32 and 33 on the side of the discharge channels 40 and 41 with the fixing members similar to the fixing members 44 and 45 described above. It may be arranged so as to be sealed with respect to the surface, and the space between each of the spiral grooves 22B, 22C, 23B, 23C and the discharge flow paths 40, 41 may be sealed.

  By doing so, the rubber leakage outlet side from the spiral grooves 22B, 22C, 23B, and 23C of the rotary shafts 22 and 23 can be sealed, so that the rubber is prevented from leaking into the discharge passages 40 and 41. Can be effectively suppressed, and the effect of suppressing leakage of rubber can be further improved. Therefore, the amount of rubber leaking into the discharge passages 40 and 41 can be reduced, and the leaked rubber can be reliably prevented from reaching the bearings 37 and 38 along the rotary shafts 22 and 23, thereby protecting the bearings 37 and 38. Can be further increased. In addition, even when lubricating oil, grease, or the like moves from the bearings 37 and 38 side along the rotary shafts 22 and 23 due to the sealing action of the sealing member, they are cut off to interrupt the gears 20 and 21 side. Therefore, the contact between the lubricating oil, grease, etc. and the rubber can be avoided, and the deterioration of the quality of the rubber can be more reliably suppressed.

  Further, in the present embodiment, the annular protrusions 20A and 21A are provided on the side surfaces of the gears 20 and 21, and the annular concave groove M is provided on the inner surface of the housing 30. The effect is obtained. That is, an annular concave groove concentric with each of both side surfaces in the axial direction of the gears 20 and 21 is provided, and an annular surface is formed on the inner surface of the housing 30 (inner side surface of the accommodating portion 11) facing each annular concave groove. An annular protrusion having a shape corresponding to the concave groove may be provided. In this case, the annular groove and the annular protrusion are formed in a cross-sectional shape corresponding to each other, for example, a rectangular shape such as a rectangular cross-section, etc. The annular grooves are accommodated in the annular protrusions so as to engage with the annular protrusions so as to be movable in the rotational direction of the gears 20 and 21.

  Further, in this gear pump 10, the discharge flow paths 40 and 41 are formed by the plurality of spacers 36, but the discharge flow paths 40 and 41 are, for example, a passage communicating from the rotary shafts 22 and 23 to the outside of the housing 30 or a lead-out conduit. Any other shape or form may be used as long as it extends from the outer peripheral surfaces of the rotary shafts 22 and 23 and opens toward the outside of the housing 30 so that the rubber flows and can be discharged out of the apparatus. . However, like this gear pump 10, the discharge passages 40 and 41 are formed in a hollow shape in which all parts other than the spacers 36 are opened to the outside, and the outer peripheral surfaces of the rotary shafts 22 and 23 of the parts are formed. When exposed to the outside as a whole, the rubber can be discharged reliably and smoothly regardless of the direction in which the gear pump 10 is arranged, etc., so that the discharge flow paths 40 and 41 are formed as such. It is more desirable to do.

  The gear pump 10 and the extruder 1 (see FIG. 1) according to the present embodiment can be applied to the production of various rubber members. For example, passenger car tires (PSR) and small truck tires composed of rubber members. (LTR), truck and bus tires (TBR), construction vehicle tires (ORR), aircraft tires (APR), and the like. The gear pump 10 and the extruder 1 are preferably used for discharging (extruding) unvulcanized rubber having a high viscosity and a relatively high pressure. It can also be used for the discharge of fluid and extrusion molding. In addition, in the gear pump 10, the seal members 42 and 43, the annular protrusions 20 </ b> A and 21 </ b> A, and the annular concave groove M are provided together. However, only one of them may be provided. , 38 can be improved, and the above-described effects can be sufficiently obtained.

It is a principal part side view which shows typically schematic structure of the extruder of this embodiment. It is a partial cross section figure of the gear pump seen from the XX line arrow direction of FIG. It is sectional drawing which shows the conventional gear pump.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Extruder, 2 ... Extruder main body, 3 ... Cylinder, 3A ... Inside, 10 ... Gear pump, 11 ... Storage part, 12 ... Rubber inlet, 13. ..Rubber discharge port, 20 ... gear, 20A ... annular protrusion, 21 ... gear, 21A ... annular protrusion, 22 ... rotary shaft, 22A ... small diameter part, 22B ... Spiral groove, 22C ... spiral groove, 23 ... rotating shaft, 23A ... small diameter part, 23B ... spiral groove, 23C ... spiral groove, 30 ... housing, 31 ... outer periphery of the case Part, 32... Case side part, 33 .. case side part, 34 .. side plate, 35 .. side plate, 36 .. spacer, 37 .. bearing, 38. ..Drain channel, 41 ... Drain channel, 42 ... Seal member, 43 ... Seal member, 44 ... Fixing member 45 ... fixing member, M ... annular groove.

Claims (6)

A rotating shaft that rotates integrally with the rotating body; and a bearing that rotatably supports the rotating shaft; and discharging the fluid by rotating the rotating body; and the rotating body and the bearing of the rotating shaft A fluid discharge device provided with a discharge flow path for discharging the fluid leaked along the rotation axis to the outside,
A fluid discharge device, wherein a seal member for sealing the periphery of the rotary shaft is disposed between the discharge flow path of the rotary shaft and the bearing. A rotating shaft that rotates integrally with the rotating body; and a bearing that rotatably supports the rotating shaft; and discharging the fluid by rotating the rotating body; and the rotating body and the bearing of the rotating shaft A fluid discharge device provided with a discharge flow path for discharging the fluid leaked along the rotation axis to the outside,
An annular protrusion provided concentrically with the rotating body on the side surface in the axial direction of the rotating body, and an inner surface facing the annular protrusion. The annular protrusion is accommodated and the annular protrusion is disposed on the rotating body. A fluid discharge device comprising: an annular groove that is movably engaged in a rotational direction. A rotating shaft that rotates integrally with the rotating body; and a bearing that rotatably supports the rotating shaft; and discharging the fluid by rotating the rotating body; and the rotating body and the bearing of the rotating shaft A fluid discharge device provided with a discharge flow path for discharging the fluid leaked along the rotation axis to the outside,
An annular groove provided concentrically with the rotating body on the side surface in the axial direction of the rotating body, and an inner surface facing the annular groove, the annular groove being accommodated in the annular groove. A fluid discharge device comprising: an annular protrusion that is movably engaged in a rotating direction of the rotating body. In the fluid ejection device according to any one of claims 1 to 3,
A fluid discharge device, wherein a sealing member for sealing the periphery of the rotating shaft is disposed between the rotating body of the rotating shaft and the discharge channel. In the fluid ejection device according to any one of claims 1 to 4,
A fluid discharge apparatus, wherein the fluid is unvulcanized rubber. An extruder for extruding a fluid to form an extruded product,
6. A supply means for supplying the fluid; the fluid discharge apparatus according to claim 1 for discharging the fluid supplied from the supply means; and a fluid discharge port side of the fluid discharge apparatus. And a die for extruding and molding the fluid.

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