CN219942551U - Conical double-screw mixer - Google Patents

Abstract

A conical double-screw mixer is used for improving the condition of poor sealing between a revolution bent arm and a rotation stirring shaft. The conical double-screw mixer comprises a revolution bent arm and a rotation stirring shaft; the revolution bent arm comprises a bent arm shell and a rotation transmission assembly in the bent arm shell, the bent arm shell comprises a bent arm ring opening, and the bent arm ring opening surrounds a central hole; the rotation stirring shaft comprises a rotation transmission head section and a spiral stirring section which are axially connected, the rotation transmission head section stretches into the bent arm shell from the central hole and is in transmission connection with the rotation transmission assembly, and the spiral stirring section stretches out of the bent arm shell from the central hole; the spiral stirring section is provided with an oil supporting ring groove, the oil supporting ring groove surrounds and protrudes out of the periphery of the spiral stirring section, a bent arm ring opening stretches into the oil supporting ring groove, an annular interval is arranged between the bent arm ring opening and the oil supporting ring groove, and a sealing ring is arranged in the annular interval; the bent arm ring opening is provided with a material blocking ring plate, and the material blocking ring plate surrounds and protrudes out of the periphery of the bent arm ring opening and covers the annular interval.

Description

Conical double-screw mixer

Technical Field

The utility model relates to stirring equipment, in particular to a conical double-screw mixer.

Background

The conical double-screw equipment has stronger mixing strength and good mixing effect. In the conical cylinder of the conical double-screw mixer, the screw rotates around its own axis (referred to as "rotation") and performs planetary motion (referred to as "revolution") around the central axis of the conical cylinder in the vicinity of the wall surface of the cone. The conical double-screw mixer makes the materials generate compound motion in the conical cylinder by means of revolution and rotation of the screw, so that the materials are uniformly mixed. The direction of the spiral rotation enables the material to move from the bottom of the conical cylinder to the top of the conical cylinder.

The rotation stirring shaft stretches out from the revolution bent arm, and the rotation stirring shaft and the revolution bent arm are not sealed well, so that stirring materials can enter a mechanical structure to be damaged, and foreign matters such as lubricating oil in the mechanical structure can enter the stirring materials to pollute the stirring materials.

Disclosure of Invention

The utility model aims to provide a conical double-screw mixer which is used for improving the condition of poor sealing between a revolution bent arm and a rotation stirring shaft.

According to an embodiment of the present utility model, a conical double-screw mixer includes a revolution bent arm and a rotation stirring shaft; the revolution bent arm comprises a bent arm shell and a rotation transmission assembly in the bent arm shell, wherein the bent arm shell comprises a bent arm ring opening, and the bent arm ring opening surrounds a central hole; the rotation stirring shaft comprises a rotation transmission head section and a spiral stirring section which are axially connected, the rotation transmission head section stretches into the bent arm shell from the central hole and is in transmission connection with the rotation transmission assembly, and the spiral stirring section stretches out of the bent arm shell from the central hole; the spiral stirring section is provided with an oil supporting ring groove, the oil supporting ring groove surrounds and protrudes out of the periphery of the spiral stirring section, the bent arm ring opening stretches into the oil supporting ring groove, an annular interval is formed between the bent arm ring opening and the oil supporting ring groove, and a rotary sealing ring is arranged in the annular interval; the bent arm ring opening is provided with a material blocking ring plate, and the material blocking ring plate surrounds and protrudes out of the periphery of the bent arm ring opening and covers the annular space.

In one or more embodiments, the oil slinger groove includes an annular disk portion and an annular riser; the annular disc part radially protrudes from the periphery of the spiral stirring section and is axially spaced from the axial end face of the bent arm ring opening; the annular vertical plate axially protrudes from the annular disc part, and the annular space is positioned between the annular vertical plate and the outer peripheral surface of the bent arm ring opening.

In one or more embodiments, the striker plate includes an upper end face and a lower end face that are axial; the lower end face faces the annular space and is axially spaced from the oil supporting ring groove; the upper end face is away from the annular space and is inclined downwards from the inner peripheral side to the outer peripheral side.

In one or more embodiments, a bearing housing is disposed within the curved arm housing, the curved arm housing providing a wall of the bearing housing, the bearing housing mounting a bearing that supports the self-rotating drive head segment; the bearing seat comprises an axial wall body perpendicular to the axial direction, the axial wall body and the bearing are provided with axial intervals, an axial adjusting pressing plate is arranged in each axial interval, the axial wall body is provided with an adjusting bolt, the adjusting bolt axially penetrates through the axial wall body and stretches into the axial intervals to tightly prop against the axial adjusting pressing plate, and the axial adjusting pressing plate tightly props against the bearing.

In one or more embodiments, the adjustment bolt is a fine thread.

In one or more embodiments, the helical stirring section comprises a helical head section and a helical body, the helical head section comprises a solid shaft and is axially connected to the self-rotating drive head section, the helical body comprises a hollow shaft; the solid shaft comprises a plugging section and a collar protruding outwards from the plugging section in a radial direction, the plugging section is plugged into a central hole of the hollow shaft, and the end face of the collar is in butt welding with the end face of the shaft wall of the hollow shaft.

In one or more embodiments, the self-rotating stirring shaft includes a first self-rotating stirring shaft and a second self-rotating stirring shaft, the first self-rotating stirring shaft having a length greater than the second self-rotating stirring shaft, and the stirring helix of the first self-rotating stirring shaft includes an arc outer edge.

In one or more embodiments, the conical double-screw mixer comprises a speed reducer, the speed reducer comprises a revolution input shaft, the bent arm shell comprises a revolution input shell, and the revolution input shell is sleeved on the periphery of the revolution input shaft and is connected with the revolution input shaft in a key way; the revolution input shaft comprises a shaft shoulder, the shaft shoulder and the axial end face of the revolution input shell axially compress an annular base plate, the annular base plate surrounds the periphery of the revolution input shaft, and a sealing ring is arranged between the annular base plate and the radial direction of the revolution input shaft.

In one or more embodiments, the speed reducer further includes a bottom wall, and the revolution input shaft protrudes from the bottom wall of the speed reducer and is connected to the revolution input housing; the rotary sealing ring is arranged between the sealing ring opening and the radial direction of the revolution input shell.

In one or more embodiments, the speed reducer further includes a bottom wall, and the revolution input shaft protrudes from the bottom wall of the speed reducer and is connected to the revolution input housing; a mechanical sealing device is arranged between the bottom wall of the speed reducer and the revolution input shaft.

The embodiment of the utility model has at least the following beneficial effects:

the oil supporting ring groove is used for accommodating the bent arm ring opening, and foreign matters such as lubricating oil and the like leaked from the bent arm ring opening are accommodated by the oil supporting ring groove, so that the foreign matters are prevented from entering the cylinder body to pollute materials. The rotary sealing ring and the baffle plate seal the annular space between the oil supporting ring groove and the bent arm ring opening, so that materials are prevented from entering the bent arm shell from the bent arm ring opening, the mechanical structure in the bent arm shell is damaged, and meanwhile, foreign matters such as lubricating oil in the oil supporting ring groove are prevented from flowing out of the annular space and entering the cylinder body to pollute the materials.

Drawings

The above and other features, properties and advantages of the present utility model will become more apparent from the following description in conjunction with the accompanying drawings and embodiments, in which:

FIG. 1 is an assembled overview of a conical twin screw mixer;

FIG. 2 is a partial schematic view of a conical twin screw mixer at a revolving curved arm;

FIG. 3 is a partial schematic view of a conical twin screw mixer at a crank eye and a trunnion ring groove;

FIG. 4 is a partial schematic view of a conical twin screw mixer at an axially adjustable platen;

FIG. 5 is a partial schematic view of a helical mixing segment of the first rotating mixing shaft at a junction;

FIG. 6 is a partial schematic view of the first rotating stirring shaft at the stirring screw;

FIG. 7 is a partial schematic view of a conical twin screw mixer at a orbital input shaft and an orbital input housing;

FIG. 8 is a partial schematic view of a conical twin screw mixer at an annular backing plate;

FIG. 9 is a partial schematic view of a conical twin screw mixer at an outlet valve;

FIG. 10 is a partial schematic view of a conical twin screw mixer at the top end of a liquid spray pipe;

FIG. 11 is a partial schematic view of the spray tube at the bottom end of the spinning input shaft;

reference numerals:

1-a cylinder;

2-a discharge valve;

3-a flat head top cover;

4-supporting the ear mount;

5-a feed inlet;

6, an overhaul port;

7-reinforcing ribs;

8-a speed reducer;

9-revolution input shaft;

10-autorotation input shaft;

11-revolution bent arms;

12-a first autorotation stirring shaft;

13-a second autorotation stirring shaft;

14-a transmission shaft;

15-a self-rotation transmission head section;

16-a bent arm housing;

17-a self-rotating transmission assembly;

18-long curved arms;

19-short bent arms;

20-stirring the spiral;

21-arm bending ring opening;

22-a central hole;

23-a spiral stirring section;

24-oil supporting ring grooves;

25-a first annular space;

26-a first sealing ring;

27-a striker plate;

28-a second sealing ring;

29-a first bearing seat;

30-a first bearing;

31-a third sealing ring;

32-a fourth sealing ring;

33-a fifth seal ring;

34-an annular disk portion;

35-annular vertical plates;

36-a first axial separation;

37-upper end face;

38-lower end face;

39-second axial spacing;

40-a second bearing block;

41-a second bearing;

42-axial wall;

43-third axial spacing;

44-axial adjustment press plate;

45-a first disc portion;

46-handle;

47-sixth sealing ring;

48-adjusting bolts;

49-helical head section;

50-a helical body;

51-plug-in section;

52-solid shaft;

53-hollow shaft;

54-collar;

55-butt welding;

56-arc outer edges;

57-revolution input housing;

58-shaft shoulders;

59-an annular shim plate;

60-seventh seal ring;

61-fourth axial spacing;

62-mechanical sealing means;

63-a sealed housing;

64-sealing ring openings;

65-sealing the top wall;

66-eighth seal ring;

67-hexagonal head bolt with holes;

68-a ninth sealing ring;

69-collar;

70-moving plate;

71-a gasket;

72-distance sleeve;

73-tenth sealing ring;

74-handle;

75-spraying liquid pipe;

76-rotating the spray head;

77-spraying liquid elbow;

78-a rotary joint;

79-spraying liquid gland;

80-an oil-impregnated bearing;

81-eleventh sealing ring;

82-sealing seat

83-twelfth seal ring;

84-main motor;

85-still tablet.

Detailed Description

Reference now will be made in detail to embodiments of the utility model, one or more examples of which are illustrated in the drawings. Each example is provided by way of explanation, not limitation, of the utility model. Indeed, it will be apparent to those skilled in the art that various modifications and variations can be made in the present utility model without departing from the scope or spirit of the utility model. For instance, features illustrated or described as part of one embodiment, can be used with another embodiment to yield a still further embodiment. Accordingly, it is intended that the present utility model cover the modifications and variations of this utility model provided they come within the scope of the appended claims and their equivalents.

It is noted that these and other figures are merely examples, which are not drawn to scale and should not be construed as limiting the scope of the utility model as it is actually claimed.

The terms "first," "second," and the like may be used interchangeably to distinguish one feature from another and are not intended to mean that the various features must be located in the positions shown in the various embodiments.

As shown in fig. 1, the conical twin screw mixer comprises an inverted conical barrel 1. The bottom of the cylinder body 1 can be provided with a discharge valve 2, and the discharge valve 2 is opened and closed to control the discharge of the equipment. The top of the cylinder 1 can be provided with a flat head top cover 3 which is welded with the cylinder 1 into a whole. The flat head top cover 3 is of an integral structure with radian, which is welded completely, and has the advantages of good strength, high utilization rate, no dead angle, no oil leakage, less residual materials, convenient cleaning and capability of meeting the hole opening requirements under different working conditions. Four supporting lugs 4 which are uniformly distributed can be welded on the periphery of the cylinder body 1 and the flat head top cover 3, and the supporting lugs 4 are connected with the cylinder body 1 and the flat head top cover 3, so that the strength of the cylinder body 1 and the flat head top cover 3 can be enhanced, and the conical double-screw mixer can be fixed. The top cover 3 of the flat head is provided with a feed inlet 5 and an overhaul port 6. The flat head top cover 3 can be welded with the reinforcing rib 7 at the center, and the speed reducer 8 can be connected with the reinforcing rib 7 through a flange, so that the strength of the whole transmission is ensured during load operation.

As shown in fig. 2, the speed reducer 8 may include a revolution input shaft 9 and a rotation input shaft 10. The revolution input shaft 9 drives the bent arm housing 16 of the revolution bent arm 11, and thereby drives the revolution bent arm 11 to revolve, thereby driving the first rotation stirring shaft 12 and the second rotation stirring shaft 13 mounted on the revolution bent arm 11 to revolve. The rotation input shaft 10 may drive the first rotation stirring shaft 12 and the second rotation stirring shaft 13 to rotate through the rotation transmission assembly 17 installed in the bent arm housing 16, specifically, the rotation input shaft 10 may be connected with a bevel gear in a key manner, and may drive the rotation transmission head section 15 through the bevel gear meshing and the transmission shaft 14 in the revolution bent arm 11, and the rotation transmission head section 15 is a shaft section of the first rotation stirring shaft 12 and the second rotation stirring shaft 13, thereby the first rotation stirring shaft 12 and the second rotation stirring shaft 13 are driven to rotate. The first rotation stirring shaft 12 and the second rotation stirring shaft 13 also comprise a spiral stirring section 23, stirring spirals 20 are distributed on the spiral stirring section 23, and the rotation transmission head section 15 and the spiral stirring section 23 are axially and fixedly connected.

When the conical double-screw mixer works, the autorotation stirring shafts 12 and 13 revolve along the conical wall of the cylinder body 1, so that materials do circular motion along the conical wall, the autorotation stirring shafts 12 and 13 rotate to enable the materials to spirally rise along the stirring screw 20 from the conical bottom of the cylinder body 1, and the revolution and autorotation compound motion of the autorotation stirring shafts 12 and 13 enable a part of the materials to be sucked into the cylindrical surface of the spiral stirring section 23 and simultaneously enable the materials at the conical wall of the cylinder body 1 to flow to the center of the cone of the cylinder body 1 under the action of autorotation centrifugal force of the spiral stirring section 23. The superposition circulation of several movements of the material in the cylinder 1 forms a complex vortex movement, and convection, shearing and diffusion are generated, so that the components of the material in the cylinder 1 are mixed in a convection way.

With continued reference to fig. 1, the orbital bending arm 11 may include a long bending arm 18 and a short bending arm 19, the long bending arm 18 having a length greater than the short bending arm 19, the long bending arm 18 mounting the first rotation stirring shaft 12, the short bending arm 19 mounting the second rotation stirring shaft 13, the first rotation stirring shaft 12 having a length greater than the second rotation stirring shaft 13. The long bent arm 18 and the short bent arm 19 enable revolution tracks of the first rotation stirring shaft 12 and the second rotation stirring shaft 13 to be staggered, the diameter of the stirring spiral 20 of the first rotation stirring shaft 12 is smaller than that of the stirring spiral 20 of the second rotation stirring shaft 13, materials are stirred fully, and the materials are mixed uniformly.

As shown in fig. 3, the curved arm housing 16 includes a curved arm collar 21, and the curved arm collar 21 encloses a central bore 22. The rotation transmission head 15 extends from the central hole 22 into the bent arm casing 16, is in driving connection with the rotation transmission assembly 17, and the spiral stirring section 23 extends from the central hole 22 out of the bent arm casing 16. The spiral stirring section 23 is provided with an oil supporting ring groove 24, the oil supporting ring groove 24 surrounds and protrudes from the outer periphery of the spiral stirring section 23, and an annular groove space having an opening is formed in the outer periphery of the spiral stirring section 23. The bent arm ring opening 21 extends into the oil supporting ring groove 24, enters the annular groove part space from the opening and is accommodated by the annular groove part space. The bent arm ring port 21 and the oil supporting ring groove 24 are provided with radial gaps to form a first annular space 25, a first sealing ring 26 is arranged in the first annular space 25 to seal the first annular space 25, and the first sealing ring 26 is a rotary sealing ring. The arm band 21 is provided with a striker plate 27, and the striker plate 27 surrounds and protrudes at the outer periphery of the arm band 21, covering the first annular space 25 to seal the first annular space 25.

The oil supporting ring groove 24 accommodates the bent arm ring opening 21, and foreign matters such as lubricating oil leaked from the bent arm ring opening 21 are accommodated by the oil supporting ring groove 24, so that the foreign matters are prevented from entering the cylinder body 1 to pollute materials. The first annular space 25 between the oil supporting ring groove 24 and the bent arm ring opening 21 is sealed by the first sealing ring 26 and the material blocking ring plate 27, so that materials are prevented from entering the bent arm shell 16 from the bent arm ring opening 21, the mechanical structure in the bent arm shell 16 is prevented from being damaged, and meanwhile, foreign matters such as lubricating oil in the oil supporting ring groove 24 are prevented from flowing out of the first annular space 25 and entering the cylinder body 1 to pollute the materials.

With continued reference to fig. 3, a second seal ring 28 may be disposed between the curved arm collar 21 and the radial direction of the rotary drive head segment 15, the second seal ring 28 being a rotary seal ring. The bent arm collar 21 can be fixed on a first bearing seat 29 by bolts, a first bearing 30 is arranged in the first bearing seat 29, and the first bearing 30 supports the rotation transmission head section 15. A third sealing ring 31 can be arranged between the first bearing seat 29 and the radial direction of the rotation transmission head section 15 for sealing, and the third sealing ring 31 is a rotary sealing ring. The first bearing seat 29 may be bolted to the curved arm housing 16. A fourth sealing ring 32 may be provided axially between the curved arm housing 16 and the first bearing support 29.

With continued reference to fig. 3, the trunnion ring groove 24 may include an annular disk portion 34 and an annular riser 35. The annular disc part 34 protrudes radially from the outer periphery of the spiral stirring section 23, covers the axial end part of the bent arm ring opening 21 to catch the foreign matters leaked from the bent arm ring opening 21, and has a first axial interval 36 with the axial end surface of the bent arm ring opening 21, so that the bent arm ring opening 21 is prevented from being bumped and ground when the oil supporting ring groove 24 rotates along with the rotation stirring shafts 12 and 13. The annular vertical plate 35 protrudes from the annular disc part 34 along the axial direction, covers the outer peripheral surface of the bent arm ring opening 21 to hold foreign matters, and forms a first annular space 25 between the annular vertical plate 35 and the radial direction of the outer peripheral surface of the bent arm ring opening 21, so that the bent arm ring opening 21 is prevented from being bumped and ground when the oil supporting ring groove 24 rotates along with the rotation stirring shafts 12 and 13.

With continued reference to fig. 3, the oil supporting ring groove 24 may be disposed between the axial directions of the rotation transmission head section 15 and the spiral stirring section 23, and divide the rotation stirring shafts 12, 13 into two sections of the rotation transmission head section 15 and the spiral stirring section 23 in the axial directions, and the rotation transmission head section 15, the oil supporting ring groove 24 and the spiral stirring section 23 are fixed by bolts. A fifth sealing ring 33 can be arranged between the oil supporting ring groove 24 and the axial direction of the rotation transmission head section 15 for sealing.

With continued reference to fig. 3, the striker plate 27 may include an axial upper end surface 37 and a lower end surface 38. The lower end face 38 faces the first annular space 25 and has a second axial space 39 with the annular vertical plate 35 of the oil ring groove 24, so as to avoid rubbing the annular vertical plate 35 of the oil ring groove 24 which rotates. The upper end surface 37 faces away from the first annular space 25 and is inclined downward from the inner peripheral side to the outer peripheral side, so that the material falling on the upper end surface 37 rolls off and is not easily accumulated at the upper end surface 37.

As shown in fig. 4, a second bearing 40 may be disposed within the curved arm housing 16. The wall of the second bearing housing 40 may be provided by the crimping arm housing 16, integral with the crimping arm housing 16. A second bearing 41 is mounted in the second bearing housing 40, and the second bearing 41 supports the rotation transmission head section 15. The second bearing housing 40 may include an axial wall 42, the axial wall 42 being substantially perpendicular to the axial direction. A third axial space 43 may be provided between the axial wall 42 and the second bearing 41, and an axial adjustment pressure plate 44 may be provided in the third axial space 43. The axial adjustment platen 44 may include a first disk portion 45 and a shank portion 46 protruding from the center of the first disk portion 45. The shank 46 may extend through the axial wall 42 from the third axial space 43 and may be smoothly connected to an outer surface of the axial wall 42, and a sixth seal ring 47 may be disposed between the shank 46 and a radial direction of the axial wall 42 to seal the first disk 45 against the second bearing 41 to prevent the second bearing 41 from loosening and swinging the rotation stirring shafts 12, 13. The axial wall body 42 is provided with an adjusting bolt 48, the adjusting bolt 48 penetrates through the axial wall body 42 along the axial direction and stretches into the second axial interval 43, the head of the adjusting bolt 48 abuts against the first disc portion 45 of the axial adjusting pressing plate 45, the first disc portion 45 abuts against the second bearing 41 further by screwing the adjusting bolt 48, and the second bearing 41 is prevented from loosening to swing the autorotation stirring shafts 12 and 13.

With continued reference to fig. 4, the adjusting bolt 48 may be a fine thread, and the rotation of the adjusting bolt 48 is finer, so that the tightening force applied to the first disc portion 45 is more precisely controllable, and the second bearing 41 is prevented from being too loose or too tight by the first disc portion 45.

With continued reference to fig. 4, the adjustment bolts 48 are smoothly connected to the outer surface of the axial wall 42 to avoid material residue, and the smooth connection can be achieved by cutting out the adjustment bolts 48 protruding from the outer surface of the axial wall 42 and then welding and grinding.

With continued reference to fig. 1, the helical mixing section 23 of the first self-rotating mixing shaft 12 may include a helical head section 49 and a helical body 50. With further reference to fig. 5, the screw head section 49 may include a solid shaft 52 and be axially coupled to the rotation transmission head section 15, and the screw body 50 may include a hollow shaft 53 and be axially coupled to the screw head section 49. The screw head section 49 is connected with the screw main body 50 and the rotation transmission head section 15, and a solid shaft 52 is adopted, so that the rigidity and the strength are good. The spiral main body 50 rotates and stirs, and the hollow shaft 53 is adopted, so that the weight is reduced and the torque transmission capability is high.

With continued reference to fig. 5, solid shaft 52 may include a socket section 51, where socket section 51 is inserted into the central bore of hollow shaft 53 and is tightly connected, solid shaft 52 may further include a collar 54 projecting radially outwardly from socket section 51, where the end surface of collar 54 may butt-weld the end surface of the shaft wall of hollow shaft 53 to form a butt-weld 55, reducing stress concentrations at the junction of helical head section 49 and helical body 50, increasing the strength of helical stirring section 23 at the head junction, and preventing breakage of helical stirring section 23 at the head junction. The plug-in section 51 enables the solid shaft 52 and the hollow shaft 53 to be aligned during welding, and the concentricity of the spiral stirring section 23 is good. The butt weld 55 has better penetration capability and strength than filler welds, fillet welds.

As shown in fig. 6, the stirring screw 20 of the first rotation stirring shaft 12 may include an arc outer edge 56, and the arc surface softens the right angle of the outer edge, so as to reduce the extrusion force and friction force applied to the outer edge of the stirring screw 20 when stirring materials, reduce the stress of the longer first rotation stirring shaft 12, and prolong the service life of the longer first rotation stirring shaft 12.

With continued reference to fig. 2, the long and short curved arms 18, 19 may be one piece, welded from castings, without bolted connections, with better strength, lower failure rates, and convenient maintenance and cleaning than are formed from multiple separate component bolted connections. And all finishing processes of the long bent arm 18 and the short bent arm 19 are finished at one time, so that the transmission precision of the autorotation transmission assembly 17 arranged in the long bent arm 18 and the short bent arm 19 is ensured, the problem of oil leakage during heavy load is solved, and less residual materials are cleaned more conveniently. A sealing ring is arranged between the long bent arm 18 and the short bent arm 19.

With continued reference to fig. 2, the speed reducer 8 may be a single-motor two-stage speed reducer, with the main motor 84 driving two-stage speed reducer, one of which drives the revolution input shaft 9 and the other of which drives the rotation input shaft 10. The flexure arm housing 16 may include a revolving input housing 57, and the revolving input housing 57 may be flange-connected with the long and short flexure arms 18, 19. With further reference to fig. 7, the revolution input shaft 9 protrudes from the bottom wall of the speed reducer 8, and the revolution input housing 57 is sleeved on the outer periphery of the revolution input shaft 9 and is in key connection with the revolution input shaft 9, and the revolution input shaft 9 transmits torque to the revolution input housing 57, thereby driving the revolution bent arm 11 to revolve.

With further reference to fig. 8, the revolution input shaft 9 may include a shoulder 58, a fourth axial space 61 may be provided between the shoulder 58 and an axial end face of the revolution input housing 57, an annular shim plate 59 may be disposed in the fourth axial space 61, and the annular shim plate 59 may be axially compressed by the shoulder 58 and the axial end face of the revolution input housing 57. The annular packing 59 surrounds the outer circumference of the revolution input shaft 9, and a seventh seal ring 60 may be provided between the annular packing 59 and the radial direction of the revolution input shaft 9. The annular gasket 59 and the seventh seal 60 prevent oil leakage and air leakage at negative or positive pressure of the apparatus.

With continued reference to fig. 7, a mechanical sealing device 62 may be disposed between the bottom wall of the speed reducer 8 and the revolution input shaft 9, so as to seal the circumferential gap between the revolution input shaft 9 and the speed reducer 8, and prevent the oil dirt of the speed reducer 8 from flowing out of the contaminated material from the circumferential gap around the revolution input shaft 9. The mechanical seal 62 is a fluid leakage prevention means constituted by at least one pair of end surfaces perpendicular to the rotation axis held in engagement and relatively sliding with the cooperation of the fluid pressure and the elastic force (or magnetic force) of the compensating mechanism and the auxiliary seal.

With continued reference to fig. 7, a seal housing 63 may be provided between the bottom wall of the speed reducer 8 and the revolution input housing 57. The seal housing 63 includes a seal ring port 64 and a seal top wall 65 that are connected to each other. The seal top wall 65 may be bolted to the bottom wall of the speed reducer 8, against the bottom wall of the speed reducer 8 to seal. The seal ring port 64 surrounds the outer periphery of the revolution input housing 57, and an eighth seal ring 66 is provided between the seal ring port 64 and the radial direction of the revolution input housing 57 to seal the gap between the seal ring port 64 and the revolution input housing 57, the eighth seal ring 66 being a rotary seal ring. The seal housing 63 prevents the oil dirt in the speed reducer 8 from flowing out of the contaminated material from the circumferential gaps around the revolution input shaft 9. The eighth seal 66 may be secured by a collar 69. The revolution input housing 57 may be hard-chrome plated on an outer circumferential surface in contact with the eighth seal ring 66 to reduce a friction coefficient, reduce friction with an inner circumferential surface of the eighth seal ring 66, ensure a service life of the eighth seal ring 66, and prevent the eighth seal ring 66 from being damaged after long-time operation, thereby causing leakage. The seal ring port 64 and the seal top wall 65 may be connected by a recessed wall which may be formed by joining separate walls via a perforated hex head bolt 67, and the separate walls are sealed at the junction by a ninth seal ring 68.

As shown in fig. 9, the discharge valve 2 and the cylinder 1 can be connected through a flange. The discharge valve 2 can be a manual dislocation valve, and the handle 74 rotates the moving plate 70 to generate a relative gap between the moving plate 70 and the static plate 85 so as to enable materials to pass through, so that the operation is simple and convenient, and the time and the labor are saved. The discharging valve 2 can be of a flat plate structure and is close to the first autorotation stirring shaft 12, so that residual materials are reduced. Distance sleeves 72 can be arranged between the static piece 85 and the gasket 71 of the discharge valve 2, and the left, right, up and down positions between the moving piece 70 and the static piece 85 can be accurately positioned, so that the moving piece 70 and the static piece 85 are matched more tightly. And a tenth sealing ring 73 is provided to seal the gap between the flange and the moving plate 70 to prevent leakage of the material.

With continued reference to fig. 1 and 2, the rotation input shaft 10 may be hollow and the spray tube 75 may pass through the rotation input shaft 10. The spray tube 75 may be screwed at the top end with a swivel 78 for easy connection to the piping of the liquid supply system. The spray pipe 75 can be provided with a spray elbow 77 at the tail end, the spray elbow 77 is provided with a rotary spray head 76, and the rotary spray head 76 can rotationally spray atomized liquid into the cylinder 1 to participate in mixing, so that the conical double-screw mixer can perform mixing operation on particles, powder and liquid materials, and the mixer is wider in application and wider in mixing field.

With continued reference to fig. 2, the rotary sprayer 76 may be replaced with a cleaning sprayer, which may be gas or liquid to clean the residual material on the revolving curved arm 11 of the apparatus, and may be rotated under the force when the pressure reaches a certain level, so that the cleaning area is larger.

As shown in fig. 10, a spray gland 79 may be bolted to the top wall of the speed reducer 8. The top end of the spray tube 75 penetrates out of the spray gland 79, the spray tube 75 and the spray gland 79 can be provided with an eleventh sealing ring 81 and an oil-containing bearing 80 above the eleventh sealing ring 81 between the spray tube and the spray gland in the radial direction, so that oil stains are prevented from leaking, and the spray tube 75 is prevented from swinging to damage the eleventh sealing ring 81. The eleventh seal ring 81 is a rotary seal ring.

As shown in fig. 11, a sealing seat 82 may be disposed at the bottom end of the rotation input shaft 10, the liquid spraying pipe 75 penetrates out from the sealing seat 82, and a twelfth sealing ring 83 is disposed between the sealing seat 82 and the radial direction of the liquid spraying pipe 75 to seal, so as to prevent oil stains in the revolution bent arm 11 from overflowing upwards out of the speed reducer 8 from the gap between the liquid spraying pipe 75 and the rotation input shaft 10. The twelfth seal 83 is a rotary seal.

Although the utility model has been described in terms of embodiments, it is not intended to be limited thereto, and variations and modifications may be made by those skilled in the art without departing from the spirit and scope of the utility model.

Claims (10)

1. A conical twin screw mixer, comprising:

the revolution bent arm comprises a bent arm shell and a rotation transmission assembly in the bent arm shell, wherein the bent arm shell comprises a bent arm ring opening, and the bent arm ring opening surrounds a central hole; and

the rotation stirring shaft comprises a rotation transmission head section and a spiral stirring section which are axially connected, the rotation transmission head section extends into the bent arm shell from the central hole and is in transmission connection with the rotation transmission assembly, and the spiral stirring section extends out of the bent arm shell from the central hole;

wherein,,

the spiral stirring section is provided with an oil supporting ring groove, the oil supporting ring groove surrounds and protrudes out of the periphery of the spiral stirring section, the bent arm ring opening stretches into the oil supporting ring groove, an annular interval is formed between the bent arm ring opening and the oil supporting ring groove, and a rotary sealing ring is arranged in the annular interval;

the bent arm ring opening is provided with a material blocking ring plate, and the material blocking ring plate surrounds and protrudes out of the periphery of the bent arm ring opening and covers the annular space.

2. The conical twin screw mixer of claim 1, wherein:

the oil supporting ring groove comprises an annular disc part and an annular vertical plate;

the annular disc part radially protrudes from the periphery of the spiral stirring section and is axially spaced from the axial end face of the bent arm ring opening;

the annular vertical plate axially protrudes from the annular disc part, and the annular space is positioned between the annular vertical plate and the outer peripheral surface of the bent arm ring opening.

3. The conical twin screw mixer of claim 1, wherein:

the material blocking ring plate comprises an upper end face and a lower end face in the axial direction;

the lower end face faces the annular space and is axially spaced from the oil supporting ring groove;

the upper end face is away from the annular space and is inclined downwards from the inner peripheral side to the outer peripheral side.

4. The conical twin screw mixer of claim 1, wherein:

a bearing seat is arranged in the bent arm shell, the bent arm shell provides a wall body of the bearing seat, the bearing seat is provided with a bearing, and the bearing supports the autorotation transmission head section;

the bearing seat comprises an axial wall body perpendicular to the axial direction, the axial wall body and the bearing are provided with axial intervals, an axial adjusting pressing plate is arranged in each axial interval, the axial wall body is provided with an adjusting bolt, the adjusting bolt axially penetrates through the axial wall body and stretches into the axial intervals to tightly prop against the axial adjusting pressing plate, and the axial adjusting pressing plate tightly props against the bearing.

5. The conical twin screw mixer of claim 4, wherein:

the adjusting bolt is a fine thread.

6. The conical twin screw mixer of claim 1, wherein:

the spiral stirring section comprises a spiral head section and a spiral main body, wherein the spiral head section comprises a solid shaft and is axially connected with the autorotation transmission head section, and the spiral main body comprises a hollow shaft;

the solid shaft comprises a plugging section and a collar protruding outwards from the plugging section in a radial direction, the plugging section is plugged into a central hole of the hollow shaft, and the end face of the collar is in butt welding with the end face of the shaft wall of the hollow shaft.

7. The conical twin screw mixer of claim 1, wherein:

the self-rotation stirring shaft comprises a first self-rotation stirring shaft and a second self-rotation stirring shaft, the length of the first self-rotation stirring shaft is greater than that of the second self-rotation stirring shaft, and the stirring spiral of the first self-rotation stirring shaft comprises an arc outer edge.

8. The conical twin screw mixer of claim 1, wherein:

the conical double-screw mixer comprises a speed reducer, wherein the speed reducer comprises a revolution input shaft, the bent arm shell comprises a revolution input shell, and the revolution input shell is sleeved on the periphery of the revolution input shaft and is connected with the revolution input shaft in a key way;

the revolution input shaft comprises a shaft shoulder, the shaft shoulder and the axial end face of the revolution input shell axially compress an annular base plate, the annular base plate surrounds the periphery of the revolution input shaft, and a sealing ring is arranged between the annular base plate and the radial direction of the revolution input shaft.

9. The conical twin screw mixer of claim 8, wherein:

the speed reducer further comprises a bottom wall, and the revolution input shaft protrudes from the bottom wall of the speed reducer and is connected with the revolution input shell;

the rotary sealing ring is arranged between the sealing ring opening and the radial direction of the revolution input shell.

10. The conical twin screw mixer of claim 8, wherein:

the speed reducer further comprises a bottom wall, and the revolution input shaft protrudes from the bottom wall of the speed reducer and is connected with the revolution input shell;

a mechanical sealing device is arranged between the bottom wall of the speed reducer and the revolution input shaft.