Damping structure of electric grinder

Abstract

The utility model relates to the field of electric grinders, in particular to a shock absorption structure of an electric grinder, which comprises a shaft box, a stator and rotor assembly, an output shaft, two groups of bearing assemblies and a counterweight assembly, the stator and rotor assembly is arranged in a casing, the bearing assemblies are arranged on the output shaft, and the tail end of the output shaft is connected with the output end of the stator and rotor assembly. The counterweight assembly is arranged on the output shaft, and the counterweight assembly is independently arranged between the bearing assemblies or independently arranged at the tail end of the output shaft or arranged between the bearing assemblies and at the tail end of the output shaft in a combined mode; through multiple independent schemes (inter-bearing balance weight, tail end balance weight, dynamic balance ring, integrated balance coupling and flexible support) and multiple combination strategies, the vibration of a main machine when the eccentric grinding head is used is reduced, the hand feeling is improved, and the service life of the main machine is prolonged.

Description

TECHNICAL FIELD

[0001] The utility model relates to the field of electric grinder, and relates to an electric grinder damping structure. BACKGROUND

[0002] The damping scheme of the existing electric grinder equipment generally adopts a double-bearing or multi-bearing structure, and the output shaft is rigidly fixed through a shaft box made of high-strength aluminum alloy or other metal materials. This scheme strengthens the rigid connection between the output shaft and the machine body to resist mechanical vibration caused by poor dynamic balance of the grinding head. However, practice shows that when there is a large dynamic imbalance in the grinding head, the vibration of the output shaft will be transmitted to the machine body through the rigid connection structure, causing the whole machine to shake violently. This mechanical vibration not only reduces the processing accuracy, but also accelerates the wear of the transmission components. SUMMARY

[0003] The utility model discloses to solve the problem of the prior art, and provides an electric grinder damping structure for the case where the grinding head has a large imbalance, and the vibration condition when the main machine is not loaded or the grinding head has good symmetry.

[0004] The utility model discloses a kind of electric grinder damping structures, including: shaft box, stator-rotor assembly arranged in the inside of shell, output shaft, bearing assembly and counterweight assembly, the bearing assembly is provided with two groups and is arranged on output shaft, the tail end of the output shaft is connected with the output end of stator-rotor assembly, the counterweight assembly is arranged on output shaft, the counterweight assembly is separately arranged between bearing assembly or separately arranged at the tail end of output shaft or combination is arranged between bearing assembly and the tail end of output shaft.

[0005] Further improvement, the counterweight assembly includes counterweight assembly one and counterweight assembly two, the counterweight assembly one is arranged between bearing assembly, and the counterweight assembly two is arranged at the tail end of output shaft.

[0006] Further improvement, the counterweight assembly one is counterweight block one or counterweight balance ring, the counterweight block one is sleeved on output shaft and located between bearing assembly;The counterweight balance ring is sleeved on output shaft and located between bearing assembly, and the counterweight balance ring includes counterweight block two, the counterweight block two is internally provided with annular cavity one coaxial with output shaft, and the annular cavity one is filled with steel ball or damping oil.

[0007] Further improvement, the counterweight assembly two is a three-jaw coupling one or a balance ring integrated three-jaw coupling, the three-jaw coupling one connects the tail end of the output shaft and the output end of the stator rotor assembly, the balance ring integrated three-jaw coupling connects the tail end of the output shaft and the output end of the stator rotor assembly, the balance ring integrated three-jaw coupling comprises a three-jaw coupling two, the three-jaw coupling two is provided with a counterweight three at the front end, and the counterweight three and the three-jaw coupling two are provided with a coaxial annular cavity two with the output shaft, the annular cavity two is filled with steel balls or damping oil.

[0008] Further improvement, the counterweight block one and the counterweight balance ring are combined and arranged on the output shaft and between the bearing assemblies.

[0009] Further improvement, the three-jaw coupling one and the balance ring integrated three-jaw coupling are combined and arranged between the tail end of the output shaft and the output end of the stator rotor assembly.

[0010] Further improvement, the shaft box is assembled and fixed through a two-piece plastic shaft box, bearing positions on the inner side of the two-piece plastic shaft box and bearing assembly positions are provided with TPE rubber coating, and the bearing assemblies are supported through the TPE rubber coating.

[0011] Compared with the prior art, the electric grinder damping structure has the beneficial effects that:

[0012] Through the inertia counterweight block (flywheel effect), the dynamic balance ring (steel ball or damping oil self-balancing), the flexible TPE rubber coating bearing seat three-stage damping design, the unbalance of the grinding head can be coped with, the electric grinder is suitable for short shaft / long shaft, the main machine vibration is reduced when the eccentric grinding head is used, the hand feeling is improved, the service life of the main machine is improved, meanwhile, the requirement of the shaft box is reduced, so that the opportunity of reducing the cost of the shaft box is increased, and a plurality of independent schemes (counterweight between bearings, tail end counterweight, dynamic balance ring, integrated balance coupling, flexible support) and a plurality of combination strategies are provided, and users can freely select according to cost or performance requirements. BRIEF DESCRIPTION OF DRAWINGS

[0013] Fig. 1 It is a structure schematic view of the combined scheme one in the utility model

[0014] Fig. 2 It is a structure schematic view of the combined scheme two in the utility model

[0015] Fig. 3 It is a structure schematic view of the shaft box outside in the utility model

[0016] Fig. 4 It is a structure schematic view of another position of the shaft box in the utility model

[0017] Fig. 5 It is a structure schematic view of the existing electric grinder damping

[0018] In the figure, 1 - bearing housing, 11 - two half type plastic bearing housing, 12 - TPE rubber coating, 2 - fixed rotor assembly, 3 - output shaft, 4 - bearing assembly, 511 - counterweight block one, 512 - counterweight balance ring, 513 - counterweight block two, 514 - annular cavity one, 521 - three-jaw coupling one, 522 - balance ring integrated three-jaw coupling, 523 - three-jaw coupling two, 524 - counterweight block three, 525 - annular cavity two. DETAILED DESCRIPTION

[0019] In the description of the present application, it should be explained that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, therefore it cannot be understood as a limitation on the present application; unless otherwise explicitly specified and limited, the terms "mounting", "connection" and "connection" should be understood in a broad sense, for example, it can be fixed connection, or it can be detachable connection, etc. For ordinary skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0020] The use principle of the present application is shown in the following embodiments and drawings. Figs. 1-5 The technical scheme of the present application is further described.

[0021] Embodiment 1

[0022] A kind of electric mill damping structure, comprising: bearing housing 1, fixed rotor assembly 2 being arranged in the inside of shell, output shaft 3, bearing assembly 4 and counterweight component, the bearing assembly 4 is provided with two groups and is arranged on output shaft 3, the tail end of the output shaft 3 is connected with the output end of fixed rotor assembly 2, the counterweight component is arranged on output shaft 3, the counterweight component is separately arranged between bearing assembly 4 or separately arranged at the tail end of output shaft 3 or combination is arranged between bearing assembly 4 and the tail end of output shaft 3.The counterweight component includes counterweight component one and counterweight component two, the counterweight component one is arranged between bearing assembly 4, and the counterweight component two is arranged at the tail end of output shaft 3.

[0023] As Figs. 1-5 The use principle of the present application is shown in the following embodiments and drawings.

[0024] The electric mill damping structure is not only suitable for short shaft cases, but also can be used for long shaft electric mills. When the eccentricity of the mill head is large, the inertia of the output shaft is increased, and the balance ring structure is used to dynamically adjust the vibration amplitude of the whole machine. It can be used alone (counterweight assembly one, counterweight assembly two) or in combination (counterweight assembly one + counterweight assembly two) according to the needs. The specific solutions are as follows:

[0025] Solution 1. An inertia counterweight assembly one (counterweight block one 511) is added between the two bearing assemblies 4 of the output shaft 3, the overall mass of the output shaft 3 is increased, the inertia of the output shaft is increased, and during operation, the output shaft rotates at high speed. By increasing the equivalent rotational inertia of the rotating part, the vibration response caused by the eccentricity of the mill head is suppressed.

[0026] Solution 2. A large inertia counterweight assembly two (heavier three-jaw coupling one 521) is added at the tail end of the output shaft 3. At this time, the counterweight assembly two is far away from the center of oscillation of the output shaft 3, which is equivalent to increasing the force arm, and the principle is similar to that of 1.

[0027] Solution 3. An inertia counterweight assembly one (counterweight balance ring 512) is added between the two bearing assemblies of the output shaft 3. The counterweight balance ring 512 has an annular cavity one 514 between the output shaft 3. Appropriate size and number of steel balls are added. The steel balls rotate together under the drive of the output shaft. When encountering a mill head with large eccentricity, the steel balls will dynamically adjust the position, or fill with damping oil, utilize the centrifugal migration characteristics of non-Newtonian fluid / discrete particles to compensate for high-order vibration components in real time, so as to achieve dynamic balance with the unbalanced mill head, thereby achieving the damping effect.

[0028] Solution 4. A large inertia counterweight assembly two (three-jaw coupling two 523) is added at the tail end of the output shaft 3. The three-jaw coupling 523 integrated with a counterweight block three 524 is integrated inside the output shaft 3. The counterweight block three 524 has an annular cavity two 525 between the output shaft 3. At this time, the counterweight is far away from the center of oscillation of the output shaft, which is equivalent to increasing the force arm, and the principle is similar to that of 1.

[0029] As a further preferred embodiment, the counterweight assembly one is a counterweight block one 511 or a counterweight balance ring 512, the counterweight block one 511 is sleeved on the output shaft 3 and located between the bearing assemblies 4; the counterweight balance ring 512 is sleeved on the output shaft 3 and located between the bearing assemblies 4, the counterweight balance ring 512 includes a counterweight block two 513, the counterweight block two 513 has an annular cavity one 514 coaxial with the output shaft 3 inside, and the annular cavity one 514 is filled with steel balls or damping oil.

[0030] The advantage of using the counterweight block one 511 structure in solution 1 alone is that when the coupling structure cannot be changed, a counterweight block can be added between the two bearing assemblies, which is suitable for first-order vibration suppression, and the structure is simple and the cost is low.

[0031] The advantage of using the counterweight balance ring 512 structure in scheme 3 alone is that it can dynamically self-balance, has strong adaptability, and can cope with the case of excessive eccentricity of the grinding head, but the structure is relatively complex and the cost is slightly higher.

[0032] As a further preferred embodiment, the counterweight assembly two is a three-jaw coupling one 521 or a balance ring integrated three-jaw coupling 522, the three-jaw coupling one 521 connects the tail end of the output shaft 3 and the output end of the stator-rotor assembly 2; the balance ring integrated three-jaw coupling 522 connects the tail end of the output shaft 3 and the output end of the stator-rotor assembly 2, the balance ring integrated three-jaw coupling 522 includes a three-jaw coupling two 523, the front end of the three-jaw coupling two 523 is provided with a counterweight three 524, and the counterweight three 524 and the three-jaw coupling two 523 are provided with an annular cavity two 525 coaxial with the output shaft 3, the annular cavity two 525 is filled with steel balls or damping oil.

[0033] The advantage of using the heavier three-jaw coupling one 521 in scheme 2 alone is that the three-jaw coupling one 521 is rigidly connected with the tail end of the output shaft 3 and the output end of the stator-rotor assembly 2, the coupling is farther away from the output end, the effect is better under the condition of increasing the same mass, and the force arm effect is significant.

[0034] The advantage of using the heavier three-jaw coupling one 521 in scheme 4 alone is that the coupling is farther away from the output end, the force arm is longer, the effect is better under the condition of increasing the same mass, and the force arm x dynamic compensation double action is further improved by cooperating with the counterweight three 524 and the steel balls or damping oil filled in the inner annular cavity two, but the structure is relatively complex and the cost is slightly higher.

[0035] As a further preferred embodiment, the counterweight one 511 and the counterweight balance ring 512 are combined and arranged on the output shaft 3 between the bearing assemblies 4. Scheme 1 and scheme 3 are combined to use, a part is a single counterweight one 511, and a part is a counterweight balance ring 512, which is suitable for medium eccentric working conditions, and wide frequency damping is realized by inertia foundation + dynamic compensation, and the cost is lower than that of a pure dynamic scheme.

[0036] As a further preferred embodiment, the three-jaw coupling one 521 and the balance ring integrated three-jaw coupling 522 are combined and arranged between the tail end of the output shaft 3 and the output end of the stator-rotor assembly 2. Scheme 2 and scheme 4 are combined to use, a part is a single three-jaw coupling one 521, and a part is a balance ring integrated three-jaw coupling 522, which is suitable for large eccentric working conditions, and the system resonance frequency is further reduced by using the multiple force arm advantage and stacking dynamic compensation.

[0037] As a further preferred embodiment, the shaft box 1 is assembled and fixed by a two-piece plastic shaft box 11, the bearing position inside the two-piece plastic shaft box 11 and the bearing assembly position are provided with TPE rubber coating 12, and the bearing assembly 4 is supported by the TPE rubber coating 12.

[0038] By improving the anti-vibration ability of the output shaft, the rigidity and material requirements of the shaft box are reduced, so that plastic materials are used to reduce costs. The shaft box 1 is assembled and fixed by a two-piece plastic shaft box 11, which mainly supports the bearing on the output shaft. The bearing position and the bearing assembly position are provided with TPE rubber coating 12 to realize soft contact between the output shaft and the shaft box, and soft contact between the shaft box and the machine body, thereby constructing a three-stage vibration isolation system (rigid connection → elastic damping → plastic buffer), blocking the transmission path of vibration to the machine body, further weakening the transmission of vibration to the machine body, and achieving the purpose of improving the use of hand feeling and improving the service life of the machine body.

[0039] The preferred embodiments of the present application are described in detail above. It should be understood that those skilled in the art can make many modifications and changes without creative labor according to the concept of the present application. Therefore, any technical solution obtained by logical analysis, reasoning or limited experiment on the basis of the existing technology according to the concept of the present application shall be within the protection scope determined by the claims.

Claims

1. A vibration damping structure for an electric grinder, characterized in that, include: The machine includes a shaft box, a stator and rotor assembly housed inside the housing, an output shaft, a bearing assembly, and a counterweight assembly. Two sets of bearing assemblies are provided and are located on the output shaft. The tail end of the output shaft is connected to the output end of the stator and rotor assembly. The counterweight assembly is located on the output shaft. The counterweight assembly can be located individually between the bearing assemblies, individually at the tail end of the output shaft, or in combination between the bearing assemblies and at the tail end of the output shaft.

2. The electric mill vibration damping structure according to claim 1, characterized in that, The counterweight assembly includes a first counterweight assembly and a second counterweight assembly. The first counterweight assembly is disposed between the bearing assemblies, and the second counterweight assembly is disposed at the tail end of the output shaft.

3. The electric mill vibration damping structure according to claim 2, characterized in that, The first counterweight component is a counterweight block or a counterweight balance ring. The counterweight block is fitted onto the output shaft and located between the bearing assemblies. The counterweight balance ring is fitted onto the output shaft and located between the bearing assemblies. The counterweight balance ring includes a second counterweight block. The second counterweight block has an annular cavity coaxial with the output shaft. The annular cavity is filled with steel balls or damping oil.

4. The electric mill vibration damping structure according to claim 2, characterized in that, The second counterweight component is a three-jaw coupling or a balance ring integrated three-jaw coupling. The first three-jaw coupling connects the tail end of the output shaft to the output end of the stator and rotor assembly. The balance ring integrated three-jaw coupling connects the tail end of the output shaft to the output end of the stator and rotor assembly. The balance ring integrated three-jaw coupling includes a second three-jaw coupling. The front end of the second three-jaw coupling is provided with a third counterweight. An annular cavity second, coaxial with the output shaft, is provided between the third counterweight and the second three-jaw coupling. The annular cavity second is filled with steel balls or damping oil.

5. The electric mill vibration damping structure according to claim 3, characterized in that, The counterweight block and the counterweight balance ring are combined and disposed on the output shaft and located between the bearing assemblies.

6. The electric mill vibration damping structure according to claim 4, characterized in that, The three-jaw coupling, integrated with the balance ring, is located between the tail end of the output shaft and the output end of the stator and rotor assembly.

7. The electric mill vibration damping structure according to claim 1, characterized in that, The axle box is assembled and fixed by two halves of plastic axle box. The bearing positions and bearing assembly positions inside the two halves of plastic axle box are covered with TPE rubber, which supports the bearing assembly.

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