CN210061590U

CN210061590U - Vibration stirrer

Info

Publication number: CN210061590U
Application number: CN201920425729.1U
Authority: CN
Inventors: 张良奇; 李冠峰; 孔鲜宁
Original assignee: Xuchang Detong Vibratory Mixing Technology Co ltd
Current assignee: Detong Intelligent Technology Co ltd
Priority date: 2019-04-01
Filing date: 2019-04-01
Publication date: 2020-02-14
Anticipated expiration: 2029-04-01

Abstract

The utility model relates to a mixer technical field especially relates to a vibration mixer, including frame, agitator, agitating unit, stirring drive arrangement, vibrating device, vibration drive arrangement, its characterized in that, vibrating device includes transmission shaft, bearing I, bearing frame I, bearing II, bearing frame II, the transmission shaft runs through I setting of bearing frame is through at least two I support of bearing is in the bearing frame I, the one end of transmission shaft with vibration drive arrangement links to each other, the other end with bearing frame II links firmly, bearing frame II passes through II with the spindle nose of (mixing) shaft one end links to each other, the centre of gyration line of transmission shaft with the outer raceway axis skew setting of bearing II, just the centre of gyration line of transmission shaft with there is contained angle α in the axis of rotation of (mixing) shaft.

Description

Vibration stirrer

Technical Field

The utility model belongs to the technical field of the mixer, especially, relate to a vibration mixer.

Background

A blender is a machine that can blend and mix a plurality of raw materials into a specific mixture. The stirring mode can be divided into two categories of forced stirring machines and free-fall stirring machines, wherein the forced stirring machines are popular with customers due to the characteristics of good stirring quality and high stirring efficiency, and are mainstream stirring equipment at home and abroad at present. With the continuous improvement of the requirements of users on stirring quality and the continuous emergence of new materials, particularly materials which are more difficult to stir, higher requirements are put on the technical performance and reliability of the traditional stirring equipment. Taking a cement concrete mixer as an example: the traditional forced mixer belongs to static mixing, and generally has the problems of high energy and raw material consumption, uneven micro-visual mixing of concrete, poor material adaptability and the like. If cement paste in macroscopically uniform concrete after stirring is observed under a microscope, the microcosmically uniform cement paste still has 10-20% of cement particle agglomeration phenomenon, and the stirring quality of the concrete and the durability of a concrete member are influenced.

The vibration stirring technology is recognized at home and abroad as one of the most economical methods for improving the stirring quality and efficiency. From the last 30 s to the present, research results of scholars at home and abroad show that: the vibration stirring can increase the movement speed of particles in the mixture, increase the effective collision times, effectively reduce the agglomeration phenomenon of the cementing material, obviously enhance the interface bonding strength between the aggregate and the cementing material, improve the weakest link in the mixture, improve the strength of the mixture, improve the micro-structure of the mixture and prolong the durability of the mixture member. However, as the vibration stirring technology is developed in a relatively late industrialization way, along with the increase of the types of the mixed materials and the improvement of the stirring quality requirement, the existing vibration stirring machine still has a space for further improving the structure, the vibration effect, the reliability and the like.

Disclosure of Invention

The utility model aims to solve the problem that the structure, the vibration effect and the reliability of the existing vibration stirring machine generally remain to be further promoted, and provide a vibration stirring machine with simpler structure, better vibration effect and higher reliability.

The utility model adopts the technical proposal that:

a vibration stirrer comprises a rack, a stirring cylinder, a stirring device, a stirring driving device, a vibrating device and a vibration driving device, wherein the stirring device comprises a stirring shaft, a stirring arm and stirring blades, the stirring arm is arranged on the stirring shaft, the stirring shaft penetrates through the stirring cylinder, the joint of the stirring shaft and the stirring cylinder is provided with a shaft end seal, one end of the stirring shaft penetrates through a bearing III in a bearing seat III and is connected with the stirring driving device, the other end of the stirring shaft is connected with the vibrating device, the vibrating device is connected with the vibration driving device through belt pulley transmission, the bearing seat III is fixed on the rack or the stirring cylinder, the vibration stirrer is characterized in that the vibrating device comprises a transmission shaft, a bearing I, a bearing seat I, a bearing II and a bearing seat II, the transmission shaft penetrates through the bearing seat I and is supported in the bearing seat I, one end of the transmission shaft is connected with the vibration driving device, the other end of the transmission shaft is fixedly connected with the bearing seat II, the bearing II is connected with a shaft head at one end of the shaft end of the bearing II, a rotation center line of the transmission shaft is connected with an inner raceway of the bearing II, the outer raceway of the bearing II is arranged on the outer raceway of the bearing α, and the center line of the bearing II coincides with the center line of the outer raceway of the bearing III of the bearing III.

Furthermore, the rotation center line of the transmission shaft is superposed with the center line of the inner hole of the bearing seat III.

Furthermore, the transmission shaft is matched with the spigot between the bearing seat II, the inner surface or the outer surface of the spigot can be a non-circular surface, the end part of the transmission shaft is preferably a convex spigot, the end part of the bearing seat II is a concave spigot, and after assembly, the rotation center line of the transmission shaft and the outer raceway axis of the bearing II are arranged in an offset manner; the end part of the transmission shaft can also be a concave spigot, and the end part of the bearing seat II is a convex spigot.

Furthermore, a spigot between the transmission shaft and the bearing seat II is matched and then welded, and preferably, the excircle center line of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, a spigot is matched between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II, and after assembly, the rotation center line of the transmission shaft and the axis of an outer raceway of the bearing II are arranged in an offset manner; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, the transmission shaft is matched with the spigot between the bearing seat II, preferably, the center line of the excircle of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, the inner hole of the concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II, and after assembly, the rotation center line of the transmission shaft and the axis of the outer raceway of the bearing II are arranged in an offset manner; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, the transmission shaft is matched with the spigot between the bearing seat II, preferably, the excircle center line of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, and the inner hole center line of the bearing seat II for mounting the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, the transmission shaft is matched with a spigot between the bearing block II, preferably, an inner hole of a concave spigot of the bearing block II is eccentrically arranged relative to the excircle of the bearing block II, and the center line of the inner hole of the bearing block II for mounting the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, a spigot is matched between the transmission shaft and the bearing seat II, an eccentric sleeve is arranged between the bearing seat II and an outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve type part, preferably, the excircle center line of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, preferably, the eccentric sleeve of a single shaft section is used for installing the inner hole center line of the bearing II to be eccentrically arranged relative to the rotation center line of the transmission shaft, and the inner hole center line of the bearing seat II used for installing the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, a spigot is matched between the transmission shaft and the bearing seat II, an eccentric sleeve is arranged between the bearing seat II and an outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve part, preferably, an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to an outer circle of the bearing seat II, and preferably, the central line of an inner hole of the bearing II, which is used for mounting the bearing II, is eccentrically arranged relative to the rotation central line of the transmission shaft; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Furthermore, the transmission shaft is matched with the bearing seat II through a spigot, preferably, the excircle center line of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, the bearing II is an outer ring eccentric bearing, the outer ring eccentric bearing refers to a bearing with the excircle center line of the outer ring eccentric to the axis of an outer raceway, and the axis of the outer raceway refers to the axial center line of the outer raceway along the transmission shaft; as mentioned above, the spigot fit between the transmission shaft and the bearing seat ii can be reversed, and will not be described herein.

Further, the transmission shaft with the tang cooperation between II bearing frames, it is preferred II excircle eccentric settings of II concave tang hole relative bearing frame of bearing frame, just bearing II is outer lane eccentric bearing, as before, the transmission shaft with the tang cooperation can be got over each other between II bearing frames, no longer gives details here.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, two ends of the flange are respectively matched with the transmission shaft and the spigot of the bearing seat II, a concave spigot is preferably arranged on one side, close to the transmission shaft, of the flange, a convex spigot is arranged at the end part of the corresponding transmission shaft, and the flange is welded after being matched with the spigot of the transmission shaft; preferably, one side of the flange, which is close to the bearing seat II, is provided with a convex spigot, one end of the corresponding bearing seat II is provided with a concave spigot, and the flange is matched with the spigot of the bearing seat II and then is connected with the spigot of the bearing seat II through a bolt; as mentioned above, the seam allowances on both sides of the flange can be reversed, and are not described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, and preferably, the center line of the excircle of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the flange is eccentrically arranged relative to the outer circle of the flange, and after assembly, the rotation center line of the transmission shaft and the axis of an outer raceway of the bearing II are arranged in an offset manner; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, and preferably, the center line of the excircle of the flange convex spigot is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange and the spigot of the bearing seat II can be reversely matched, and the details are not repeated.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II, and after assembly, the rotation center line of the transmission shaft and the axis of an outer raceway of the bearing II are arranged in an offset manner; as mentioned above, the flange and the spigot of the bearing seat II can be reversely matched, and the details are not repeated.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, and the inner hole of the concave spigot of the flange is eccentrically arranged relative to the excircle of the flange; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the excircle center line of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, and the excircle center line of the convex spigot of the flange is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the engagement of the spigots at the two ends of the flange can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, and the inner hole of the concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II; as mentioned above, the engagement of the spigots at the two ends of the flange can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, and the center line of an inner hole of the bearing seat II for mounting the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, an eccentric sleeve is preferably arranged between the bearing seat II and an outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve part, the excircle center line of the convex spigot of the transmission shaft is preferably eccentrically arranged relative to the rotation center line of the transmission shaft, and the optimized single-shaft section eccentric sleeve is used for installing the inner hole center line of the bearing II to be eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the convex spigot of the transmission shaft is eccentrically arranged relative to the rotation center line of the transmission shaft, and the bearing II is an outer ring eccentric bearing; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of the flange female spigot is eccentrically arranged relative to the outer circle of the flange, and the center line of the outer circle of the flange male spigot is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the engagement of the spigots on the two sides of the flange can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the flange is eccentrically arranged relative to the outer circle of the flange, and an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to the outer circle of the bearing seat II; as mentioned above, the engagement of the spigots on the two sides of the flange can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of the concave spigot of the flange is eccentrically arranged relative to the outer circle of the flange, and the center line of the inner hole of the bearing seat II for mounting the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, an eccentric sleeve is arranged between the bearing seat II and the outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve part, preferably, the inner hole of the concave spigot of the flange is eccentrically arranged relative to the outer circle of the flange, and preferably, the central line of the inner hole of the single-shaft section eccentric sleeve for mounting the bearing II is eccentrically arranged relative to the rotation central line of the transmission shaft; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Further, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the flange is eccentrically arranged relative to the outer circle of the flange, and the bearing II is an outer ring eccentric bearing; as mentioned above, the flange and the drive shaft spigot can be reversed, and will not be described herein.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the convex spigot of the flange is eccentrically arranged relative to the rotation center line of the transmission shaft, and the inner hole of the concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the flange convex spigot is eccentrically arranged relative to the rotation center line of the transmission shaft, and the center line of an inner hole of the bearing seat II for mounting the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Further, a flange is arranged between the transmission shaft and the bearing seat II, an eccentric sleeve is arranged between the bearing seat II and an outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve part, preferably, the excircle center line of the flange male end is eccentrically arranged relative to the rotation center line of the transmission shaft, and preferably, the single-shaft section eccentric sleeve is used for installing the inner hole center line of the bearing II to be eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Further, a flange is arranged between the transmission shaft and the bearing seat II, preferably, the center line of the excircle of the flange convex spigot is eccentrically arranged relative to the rotation center line of the transmission shaft, and the bearing II is an outer ring eccentric bearing; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II, and the center line of the inner hole of the bearing seat II for mounting the bearing II is eccentrically arranged relative to the rotation center line of the transmission shaft; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, an eccentric sleeve is arranged between the bearing seat II and an outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve type part, preferably, an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to an outer circle of the bearing seat II, and preferably, the central line of an inner hole of the bearing II, which is used for mounting the bearing II, is eccentrically arranged relative to the rotation central line of the transmission shaft; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Furthermore, a flange is arranged between the transmission shaft and the bearing seat II, preferably, an inner hole of a concave spigot of the bearing seat II is eccentrically arranged relative to the excircle of the bearing seat II, and the bearing II is an outer ring eccentric bearing; as mentioned above, the flange can be reversely matched with the spigot of the bearing seat II, and the details are not repeated.

Furthermore, the bearing seat II is used for installing an inner hole of the bearing II and is eccentrically arranged relative to the rotation center line of the transmission shaft.

Furthermore, an eccentric sleeve is arranged between the bearing seat II and an outer ring of the bearing II, the eccentric sleeve can be a multi-shaft section sleeve part, and the preferred single-shaft section eccentric sleeve is used for installing the inner hole center line of the bearing II is opposite to the rotation center line of the transmission shaft.

Further, the bearing II is an outer ring eccentric bearing.

Further, bearing frame II with be provided with eccentric cover between II outer lanes of bearing, eccentric cover can be the section sleeve type part of multiaxis, bearing frame II is used for the installation the hole central line of eccentric cover is relative the centre of gyration line eccentric settings of transmission shaft, and preferred uniaxial section eccentric cover is used for the installation the hole central line of bearing II is relative the centre of gyration line eccentric settings of transmission shaft.

Furthermore, the bearing seat II is used for installing an inner hole center line of the bearing II is eccentrically arranged relative to a rotation center line of the transmission shaft, and the bearing II is an outer ring eccentric bearing.

Furthermore, the bearing seat II and an eccentric sleeve is arranged between the bearing II outer rings, the eccentric sleeve can be a multi-shaft section sleeve part, the preferred single-shaft section eccentric sleeve is used for installation, the inner hole center line of the bearing II is opposite to the rotation center line of the transmission shaft, and the bearing II is an outer ring eccentric bearing.

Furthermore, a balance block is arranged on one side, connected with the stirring shaft, of the transmission shaft, the balance block synchronously rotates along with the transmission shaft and is used for carrying out single-side dynamic balance on the transmission shaft, and the specific position and size of the balance block are determined according to actual conditions.

Furthermore, the side of the transmission shaft connected with the stirring shaft and the side of the transmission shaft connected with the vibration transmission device are both provided with balance blocks for performing double-sided dynamic balance on the transmission shaft, the balance blocks synchronously rotate along with the transmission shaft, and the specific position and size of the balance blocks are determined according to actual conditions.

Further, a flexible coupling is arranged between the stirring shaft and the stirring driving device, an included angle α is formed between the rotation central line of the transmission shaft and the rotation central line of the stirring shaft, the allowable compensation angle of the flexible coupling is required to be not smaller than the included angle α, otherwise, the flexible coupling is blocked or fails, and two ends of the stirring shaft are respectively supported by a bearing II and a bearing III, so that the included angle α between the rotation central line of the stirring shaft and the rotation central line of the transmission shaft can be compensated by the allowed inclination angles of the inner ring and the outer ring of the bearing II and the bearing III, and otherwise, the bearing II and the bearing III are blocked or fails.

Further, agitating unit is two sets ofly, stirring drive arrangement power supply is motor I, motor I links to each other with the speed reducer, realizes two sets of agitating unit synchronous antiport through the synchronous ware, because the centre of gyration line of transmission shaft with there is contained angle α in the axis of gyration of (mixing) shaft, requires the clearance of synchronizer meshing can compensate the centre of gyration line of transmission shaft with contained angle α between the axis of gyration of (mixing) shaft causes the oblique displacement of synchronizer meshing department, otherwise the synchronizer is held out die or the trouble.

The beneficial effects of the utility model reside in that:

1. the utility model provides a vibration stirrer, which has simple structure and stable and reliable work;

2. according to different proportioning attributes of materials, a specific eccentric design and a vibration transmission device design can be adopted, so that the stirrer obtains proper amplitude and frequency and has strong adaptability;

3. in the working process, the amplitude and the frequency are not influenced by loads, the vibration performance is stable, and the consistency of the mixed material is good;

4. the transmission shaft is matched with the bearing seat II through a spigot, so that the structure is simple, the positioning connection is convenient, and the manufacturing cost is low;

5. a flange is arranged between the transmission shaft and the bearing seat II and matched by adopting a spigot, so that the positioning and the connection are convenient, the implementation of an eccentric scheme is more flexible and various, and the disassembly, the assembly and the maintenance are convenient;

6. an included angle α exists between the rotation center line of the transmission shaft and the rotation axis of the stirring shaft, and the rotation center line of the transmission shaft is superposed with the center line of the inner hole of the bearing seat III, so that the shaft end seal, the bearing II, the bearing III and the flexible coupling are stressed uniformly, and the reliability of the equipment is high.

7. And a dynamic balance design is adopted, so that the working is stable, and the equipment reliability is high.

Drawings

FIG. 1 is a schematic view of a single stirring device of the embodiment 1 of the vibration stirrer

FIG. 2 is a schematic structural view of a vibration device of a single stirring device according to embodiment 1 of the present invention

FIG. 3 is a schematic view of a structure of a vibration agitator of the present invention, showing two stirring devices in accordance with embodiment 1

FIG. 4 is a schematic structural view of a vibration device of a vibration agitator of embodiment 1 with two stirring devices

Fig. 5-52 are schematic diagrams of different vibrating devices in embodiments 2-49 of the vibration agitator of the present invention.

In the figure: 1. a frame; 2. a mixing tank; 3. a stirring device; 301. a stirring shaft; 302. a stirring arm; 303. a stirring blade; 4. a stirring drive device; 401. a motor I; 402. a speed reducer; 403. a synchronizer; 5. a vibrating device; 501. a drive shaft; 502. a positioning sleeve; 503. a bearing I; 504. a bearing seat I; 505. a bearing II; 506. a bearing seat II; 507. an eccentric sleeve; 6. a vibration driving device; 601. a motor II; 602. a driving pulley; 603. a belt; 604. a driven pulley; 7. a bearing seat III; 701. a bearing III; 8. a flexible coupling; 9. a counterbalance; 10. a flange; 11. and sealing the shaft end.

Detailed Description

The invention is further described with reference to the following figures and specific examples.

Example 1

A vibration stirrer comprises a frame 1, a stirring cylinder 2, a stirring device 3, a stirring driving device 4, a vibrating device 5 and a vibrating driving device 6 are arranged on the frame 1, the stirring device 3 comprises a stirring shaft 301, a plurality of stirring arms 302 are welded on the stirring shaft 301, stirring blades 303 are fixed on the stirring arms 302 through high-strength bolts, so that disassembly, assembly and adjustment are facilitated, the stirring shaft 301 penetrates through the stirring cylinder 2, a shaft end seal 11 is arranged at the joint of the stirring shaft 301 and the stirring cylinder 2, one end of the shaft end seal passes through a bearing III 701 in a bearing pedestal III 7, the shaft end seal passes through a flexible shaft coupling 8 and is connected with the stirring driving device 4, the stirring driving device 4 comprises a motor I401 and a speed reducer 402, the bearing pedestal III 7 is arranged on the side wall of the stirring cylinder 2 or the frame 1, a lubricating oil channel, a bearing end cover and a dustproof cover are arranged on the bearing pedestal III, a shaft head 505 is arranged on the bearing head 505, the other end of the bearing 301, the bearing 301 extends into the vibrating device 301, the vibrating device, the bearing 505 is connected with an inner ring 505 of the bearing pedestal II through the bearing pedestal III, the bearing pedestal II, the bearing pedestal III, the bearing 505, the bearing pedestal II is arranged on the bearing pedestal III, the bearing pedestal II, the bearing pedestal III, the bearing 505, the bearing pedestal II is arranged on the bearing pedestal II, the bearing pedestal III, the bearing pedestal II, the bearing pedestal III is arranged on the bearing, the bearing pedestal III, the bearing 505, the bearing 505, the bearing pedestal II is arranged on the bearing, the bearing 505, the bearing pedestal II, the bearing is arranged on the bearing, the bearing pedestal II, the bearing pedestal III, the bearing pedestal II, the bearing pedestal II is arranged on the bearing pedestal II, the bearing pedestal III, the bearing pedestal II is arranged on the bearing, the bearing pedestal III, the bearing pedestal II, the bearing pedestal II is arranged on the bearing pedestal II, the bearing pedestal III is arranged on the bearing pedestal III, the bearing pedestal II, the bearing pedestal III, the bearing pedestal III, the bearing pedestal II is arranged on the bearing pedestal III is arranged on the bearing pedestal II, the bearing pedestal III, the bearing pedestal III bearing, the bearing pedestal III, the bearing

When the flexible shaft coupling stirring device works, an included angle of 0.5 degrees is formed between the axis of the stirring shaft 301 and the axis of the transmission shaft 501, and in order to ensure that the flexible shaft coupling 8 works normally and reduce the bad vibration transmitted to the stirring driving device 4, the allowable compensation amount of the flexible shaft coupling 8 is set to be 1 degree. Bearing I503 is lubricated in advance through the lubricated oil duct, bearing II 505 and bearing III 701, I401 of starter motor realizes that (mixing) shaft 301 rotates, II 601 of starter motor, drive transmission shaft 501 and rotate at a high speed, and then drive II 506 of bearing frame of hole eccentric settings and rotate at a high speed, II 505 of rethread bearing will be periodic high frequency low amplitude vibration transmission to the end of (mixing) shaft 301 one end, thereby drive the vibration of whole agitating unit, stirring vane vibrates while stirring, thereby exert the vibration effect to the mixture in the agitator tank, destroy gelled material and conglomerate, promote the liquefaction, increase or improve gaseous part, purify the aggregate surface, increase interface bonding strength between each material, make concrete microstructure more tend to closely knit, mechanical properties and durability improve by a wide margin. Meanwhile, the balance block 9 is arranged on the end face of the bearing seat II 506, so that the undesirable vibration transmitted to the rack and a transmission system is effectively reduced, the utilization rate of vibration energy is improved, and the effective vibration effect is enhanced.

When the stirring devices 3 and the vibrating devices 5 are respectively two groups, the power source of the stirring driving device 4 is a motor, the motor I401 is connected with the speed reducer 402, the synchronizer 403 realizes synchronous reverse rotation of the two groups of stirring devices 4, and the output shaft of the speed reducer 402 is connected with the stirring shaft 301 through the flexible coupling 8. And the balance weight 9 is arranged on the end surface of the bearing seat II 506 and the end surface of the driven pulley 604, and is used for carrying out double-sided dynamic balance on the transmission shaft, so that the undesirable vibration transmitted to the rack and the transmission system is effectively reduced.

Example 2

The difference from example 1 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, the eccentric sleeve 507 can be a multi-shaft section sleeve type part, and the optimized single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 and is arranged eccentrically relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviation mode.

Example 3

The difference from example 1 is that: the bearing II 505 is an outer ring eccentric bearing, the outer ring eccentric bearing refers to a bearing with an outer ring outer circle center line eccentric to an outer raceway axis, and the outer raceway axis refers to a center line of an outer raceway along the axial direction of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 4

The difference from example 1 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the bearing seat II 506 is used for installing the inner hole of the bearing II 505 to be eccentric relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating mode.

Example 5

The difference from example 1 is that: the bearing II 505 is an outer ring eccentric bearing, and the bearing seat II 506 is used for installing the inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 6

The difference from example 1 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the bearing II 505 is an outer ring eccentric bearing, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating manner.

Example 7

The difference from example 1 is that: and a spigot between the transmission shaft 501 and the bearing seat II 506 is matched and then welded, and an inner hole for mounting the bearing II 505 is processed and manufactured to be eccentric relative to the rotation center line of the transmission shaft 501 through the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 8

The difference from example 7 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, and as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviation mode.

Example 9

The difference from example 7 is that: the bearing II 505 is an outer ring eccentric bearing, so that the rotating center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 10

The difference from example 7 is that: the rabbets between the transmission shaft 501 and the bearing seat II 506 can be mutually reversed, and the excircle center line of the convex rabbets of the transmission shaft 501 is preferably arranged eccentrically relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 11

The difference from example 7 is that: as mentioned above, the inner hole of the female spigot of the bearing seat II 506 is preferably eccentrically arranged relative to the outer circle of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 12

The difference from example 7 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the bearing seat II 506 is used for installing the inner hole of the bearing II 505 to be eccentric relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating mode.

Example 13

The difference from example 7 is that: the bearing II 505 is an outer ring eccentric bearing, and the bearing seat II 506 is used for installing the inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 14

The difference from example 7 is that: the bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and the optimized excircle center line of the convex spigot of the transmission shaft 501 is eccentric relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 15

The difference from example 7 is that: the bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and the preferred concave spigot inner hole of the bearing seat II 506 is eccentric relative to the excircle of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 16

The difference from example 7 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the bearing II 505 is an outer ring eccentric bearing, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating manner.

Example 17

The difference from example 7 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the preferred outer circle center line of the convex spigot of the transmission shaft 501 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 18

The difference from example 7 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as described above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the preferred concave spigot inner hole of the bearing seat II 506 is eccentrically arranged relative to the outer circle of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 19

The difference from example 7 is that: the bearing II 505 is an outer ring eccentric bearing, and the preferable excircle center line of the convex spigot of the transmission shaft 501 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 20

The difference from example 7 is that: the bearing II 505 is an outer ring eccentric bearing, and an inner hole of a concave spigot of the bearing seat II 506 is preferably eccentrically arranged relative to the outer circle of the bearing seat II 506, so that the rotating center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 21

The difference from example 7 is that: the center line of the excircle of the convex spigot of the transmission shaft 501 is preferably arranged eccentrically relative to the center line of rotation of the transmission shaft 501, and the inner hole of the concave spigot of the bearing seat II 506 is arranged eccentrically relative to the excircle of the bearing seat II 506, so that the center line of rotation of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

Example 22

The difference from example 1 is that: a flange 10 is arranged between the transmission shaft 501 and the bearing seat II 506, two ends of the flange 10 are respectively matched with the stop mouths of the transmission shaft 501 and the bearing seat II 506, one side, close to the transmission shaft 501, of the preferred flange 10 is in concave stop mouth matching and then welded, and one side, close to the bearing seat II 506, of the flange 5 is in convex stop mouth matching and then bolted connection. The bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in a machining mode, and therefore the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 23

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, and as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviation mode.

Example 24

The difference from example 22 is that: the bearing II 505 is an outer ring eccentric bearing, so that the rotating center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 25

The difference from example 22 is that: the preferable excircle center line of the convex spigot of the transmission shaft 501 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 26

The difference from example 22 is that: the inner hole of the concave spigot of the preferred flange 10, which is close to one side of the transmission shaft 501, is eccentrically arranged relative to the outer circle of the flange 10, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 27

The difference from example 22 is that: the center line of the excircle of the convex spigot of the preferred flange 10, which is close to one side of the bearing seat II 506, is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

Example 28

The difference from example 22 is that: preferably, the female spigot inner hole on one side of the bearing seat II 506 is eccentrically arranged relative to the excircle of the bearing seat II 506, so that the rotating center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 29

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the bearing seat II 506 is used for installing the inner hole of the bearing II 505 to be eccentric relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating mode.

Example 30

The difference from example 22 is that: the bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and the bearing II 505 is an outer ring eccentric bearing, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 31

The difference from example 22 is that: the bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and the optimized excircle center line of the convex spigot of the transmission shaft 501 is eccentric relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 32

The difference from example 22 is that: the bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and the preferred concave spigot inner hole of the flange 10 close to one side of the transmission shaft 501 is eccentric relative to the outer circle of the flange 10, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 33

The difference from example 22 is that: the bearing seat II 506 is used for installing the inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and the excircle of the convex spigot at one side of the flange 10 close to the bearing seat II 506 is eccentric relative to the excircle of the flange 10, so that the rotation center line of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

Example 34

The difference from example 22 is that: the bearing seat II 506 is used for installing an inner hole of the bearing II 505 and is eccentric relative to the rotation center line of the transmission shaft 501 in machining and manufacturing, and preferably, the inner hole of the female spigot at one side of the bearing seat II 506 is eccentrically arranged relative to the excircle of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 35

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the bearing II 505 is an outer ring eccentric bearing, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating manner.

Example 36

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the preferred outer circle center line of the convex spigot of the transmission shaft 501 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 37

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the preferred female spigot inner hole of the flange 10 close to one side of the transmission shaft 501 is eccentrically arranged relative to the outer circle of the flange 10, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in a deviating manner.

Example 38

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as described above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 and is eccentrically arranged relative to the rotary center line of the transmission shaft 501, and the preferred flange 10 is eccentrically arranged relative to the outer ring of the flange 10 at the side close to the bearing seat II 506, so that the rotary center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 39

The difference from example 22 is that: an eccentric sleeve 507 is arranged between the bearing seat II 506 and the outer ring of the bearing II 505, as mentioned above, the preferred single-shaft section eccentric sleeve 507 is used for installing the inner hole center line of the bearing II 505 to be eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the preferred female spigot inner hole at one side of the bearing seat II 506 is eccentrically arranged relative to the outer ring of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 40

The difference from example 22 is that: the bearing II 505 is an outer ring eccentric bearing, and the preferable excircle center line of the convex spigot of the transmission shaft 501 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

EXAMPLE 41

The difference from example 22 is that: the bearing II 505 is an outer ring eccentric bearing, and the inner hole of the concave spigot at one side of the preferred flange 10, which is close to the transmission shaft 501, is eccentrically arranged relative to the outer circle of the flange 10, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 42

The difference from example 22 is that: the bearing II 505 is an outer ring eccentric bearing, and the center line of the excircle of the convex spigot of the preferred flange 10, which is close to one side of the bearing seat II 506, is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

Example 43

The difference from example 22 is that: bearing II 505 is an outer ring eccentric bearing, and preferably, a female spigot inner hole on one side of a bearing seat II 506 is eccentrically arranged relative to the outer circle of the bearing seat II 506, so that the rotating center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 44

The difference from example 22 is that: the center line of the excircle of the convex spigot of the preferable transmission shaft 501 is eccentrically arranged relative to the center line of rotation of the transmission shaft 501, and the inner hole of the concave spigot of one side of the flange 10, which is close to the transmission shaft 501, is eccentrically arranged relative to the excircle of the flange 10, so that the center line of rotation of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

Example 45

The difference from example 22 is that: the optimized excircle center line of the convex spigot of the transmission shaft 501 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the optimized excircle center line of the convex spigot of the flange 10 close to one side of the bearing seat II 506 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset manner.

Example 46

The difference from example 22 is that: the center line of the excircle of the convex spigot of the transmission shaft 501 is preferably arranged eccentrically relative to the center line of rotation of the transmission shaft 501, and the inner hole of the concave spigot on one side of the bearing seat II 506 is preferably arranged eccentrically relative to the excircle of the bearing seat II 506, so that the center line of rotation of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

Example 47

The difference from example 22 is that: the inner hole of the concave spigot, close to one side of the transmission shaft 501, of the preferred flange 10 is eccentrically arranged relative to the outer circle of the flange 10, and the center line of the outer circle of the convex spigot, close to one side of the bearing seat II 506, of the preferred flange 10 is eccentrically arranged relative to the rotation center line of the transmission shaft 501, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset mode.

Example 48

The difference from example 22 is that: the inner hole of the concave spigot, which is close to one side of the transmission shaft 501, of the preferred flange 10 is eccentrically arranged relative to the outer circle of the flange 10, and the inner hole of the concave spigot, which is close to one side of the bearing seat II 506, of the preferred bearing seat II 506 is eccentrically arranged relative to the outer circle of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the outer raceway axis of the bearing II 505 are arranged in an offset.

Example 49

The difference from example 22 is that: the center line of the excircle of the convex spigot of the preferred flange 10, which is close to one side of the bearing seat II 506, is eccentrically arranged relative to the rotation center line of the transmission shaft 501, and the inner hole of the concave spigot of one side of the bearing seat II 506 is eccentrically arranged relative to the excircle of the bearing seat II 506, so that the rotation center line of the transmission shaft 501 and the axis of the outer raceway of the bearing II 505 are arranged in an offset manner.

In any two kinds of eccentric combination schemes of above all embodiments, finally all need to realize the centre of gyration line of transmission shaft 501 and the outer raceway axis skew setting of bearing II 505, and total offset is the vector sum of eccentric volume separately, can see out by above concrete implementation mode, the utility model provides a pair of vibration mixer has that eccentric mode is nimble various, and overall structure is simple, the vibration effect is effectual, the characteristics of high reliability.

The stirring device shown in the drawings of all the embodiments of the utility model is only a schematic structural diagram, is suitable for both a continuous stirrer and an intermittent stirrer.

The above description is only for the preferred embodiment of the present invention, and any three or more eccentric combination schemes are not further described, but the present invention is not limited thereto, and any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention should be included within the protection scope of the present invention.

Claims

1. A vibration stirrer comprises a rack, a stirring cylinder, a stirring device, a stirring driving device, a vibrating device and a vibration driving device, wherein the stirring device comprises a stirring shaft, a stirring arm and stirring blades, the stirring arm is arranged on the stirring shaft, the stirring shaft penetrates through the stirring cylinder, the joint of the stirring shaft and the stirring cylinder is provided with a shaft end seal, one end of the stirring shaft penetrates through a bearing III in a bearing seat III and is connected with the stirring driving device, the other end of the stirring shaft is connected with the vibrating device, the vibrating device is connected with the vibration driving device through belt pulley transmission, the bearing seat III is fixed on the rack or the stirring cylinder, the vibration stirrer is characterized in that the vibrating device comprises a transmission shaft, a bearing I, a bearing seat I, a bearing II and a bearing seat II, the transmission shaft penetrates through the bearing seat I and is supported in the bearing seat I through at least two bearings I, one end of the transmission shaft is connected with the vibration driving device, the other end of the transmission shaft is fixedly connected with the bearing seat II, the bearing seat II is connected with a shaft head at one end of the bearing II through the bearing II, a rotation center line of the bearing II is arranged with an outer raceway of the bearing, and the rotation center line of the bearing II is superposed with the rotation center line α of the rotation axis of the stirring.

2. A vibratory mixer as set forth in claim 1 wherein: the rotation center line of the transmission shaft is superposed with the center line of the inner hole of the bearing seat III.

3. A vibratory mixer as set forth in claim 1 wherein: the transmission shaft with the spigot cooperation between II bearing frames, just the transmission shaft tip is protruding spigot, II tip of bearing frame are concave spigot.

4. A vibratory mixer as set forth in claim 3 wherein: and the excircle of the convex spigot of the transmission shaft is eccentrically arranged.

5. A vibratory mixer as set forth in claim 3 wherein: and an inner hole of the concave spigot of the bearing seat II is eccentrically arranged.

6. A vibratory mixer as set forth in claim 3 wherein: the excircle of the convex spigot of the transmission shaft is eccentrically arranged, and the inner hole of the concave spigot of the bearing seat is eccentrically arranged.

7. A vibratory mixer as claimed in claim 4 or 5, wherein: and the bearing seat II is used for installing an inner hole of the bearing II in an eccentric mode.

8. A vibratory mixer as claimed in claim 4 or 5, wherein: and an eccentric sleeve is arranged between the bearing seat II and the outer ring of the bearing II.

9. A vibratory mixer as claimed in claim 4 or 5, wherein: and the bearing II is an outer ring eccentric bearing.

10. A vibratory mixer as set forth in claim 1 wherein: the transmission shaft with be provided with the flange between the bearing frame II, the flange both ends respectively with the transmission shaft with II tang cooperations of bearing frame, just the flange is close to transmission shaft one side is concave tang, the flange is close to II one side of bearing frame are protruding tang.

11. A vibratory mixer as set forth in claim 10 wherein: and the excircle of the convex spigot of the transmission shaft is eccentrically arranged.

12. A vibratory mixer as set forth in claim 10 wherein: and an inner hole of the flange female spigot is eccentrically arranged.

13. A vibratory mixer as set forth in claim 10 wherein: and the excircle of the flange male spigot is eccentrically arranged.

14. A vibratory mixer as set forth in claim 10 wherein: and an inner hole of the concave spigot of the bearing seat II is eccentrically arranged.

15. A vibratory mixer as set forth in claim 10 wherein: the transmission shaft male spigot excircle is eccentric, just the flange female spigot hole is eccentric.

16. A vibratory mixer as set forth in claim 10 wherein: the flange male spigot excircle is eccentric, just the II female spigot hole eccentric settings of bearing frame.

17. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and the bearing seat II is used for installing an inner hole of the bearing II in an eccentric mode.

18. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and an eccentric sleeve is arranged between the bearing seat II and the outer ring of the bearing II.

19. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and the bearing II is an outer ring eccentric bearing.

20. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and an eccentric sleeve is arranged between the bearing seat II and the outer ring of the bearing II, and the bearing seat II is used for installing the inner hole of the eccentric sleeve in an eccentric manner.

21. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and the bearing seat II is used for installing the inner hole of the bearing II in an eccentric mode, and the bearing II is an outer ring eccentric bearing.

22. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and an eccentric sleeve is arranged between the bearing seat II and the outer ring of the bearing II, and the bearing II is an outer ring eccentric bearing.

23. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and a balance block is arranged on one side of the transmission shaft connected with the stirring shaft.

24. A vibratory mixer as set forth in claim 1 or claim 3 or claim 10 wherein: and balance blocks are arranged on one side of the transmission shaft connected with the stirring shaft and one side of the transmission shaft connected with the vibration driving device.

25. A vibratory mixer as set forth in claim 11 or 12 wherein: and the excircle of the flange male spigot is eccentrically arranged.

26. A vibratory mixer as set forth in claim 11 or 12 wherein: and an inner hole of the concave spigot of the bearing seat II is eccentrically arranged.

27. A vibratory mixer as set forth in claim 11 or 12 or 13 or 14 wherein: and the bearing seat II is used for installing an inner hole of the bearing II in an eccentric mode.

28. A vibratory mixer as set forth in claim 11 or 12 or 13 or 14 wherein: and an eccentric sleeve is arranged between the bearing seat II and the outer ring of the bearing II.

29. A vibratory mixer as set forth in claim 11 or 12 or 13 or 14 wherein: and the bearing II is an outer ring eccentric bearing.

30. A vibration agitator as claimed in claim 1, wherein a flexible coupling is provided between the agitator shaft and the agitator drive means, and the allowable compensation angle of said flexible coupling is not less than angle α.

31. A vibratory mixer as set forth in claim 1 wherein: agitating unit is two sets of, stirring drive arrangement power supply is motor I, motor I links to each other with the speed reducer, realizes two sets of agitating unit synchronous antiport through the synchronous ware.