High-elastic heavy-load coupling for mill

Abstract

The utility model discloses a high-elastic heavy-load coupler for a mill. The high-elastic heavy-load coupler for the mill comprises an inner gear ring, an outer gear ring, an outer gear ring, an inner gear ring, an outer gear ring and an outer gear ring, the inner gear ring is provided with inner teeth, and a tooth groove is formed between every two inner teeth; outer teeth are arranged on the outer gear ring, the outer gear ring is arranged in the inner gear ring in a sleeving mode, and one outer tooth is arranged in one tooth groove; one elastomer group is arranged between one outer tooth and one inner tooth, the elastomer group at least comprises a first hardness elastomer group and a second hardness elastomer group, and the hardness of the first hardness elastomer group is greater than that of the second hardness elastomer group. The elastic body has the buffering performance with the soft hardness and also has the hard torque transmission effect, when equipment is started, the elastic body with the low hardness is firstly stressed and compressed, and the good buffering and damping effect is provided; when the elastic body is compressed to a certain amount, the elastic body with high hardness begins to contact and bear force, and therefore large torque is transmitted.

Description

Technical Field

[0001] The utility model relates to the technical field of couplings, in particular to a high-elasticity and heavy-load coupling for a grinding machine. Background Art

[0002] Couplings can be divided into flexible couplings and rigid couplings based on whether they can compensate for misalignment between the connected shafts. Flexible couplings have compensation capabilities, and depending on whether they have elastic elements, they can be divided into those with elastic elements and those without.

[0003] In flexible couplings with elastic elements, the deformation of the elastic element compensates for misalignment between the connected shafts. Of course, torque also needs to be transmitted through the elastic element, which places high demands on the elastic element. It must be both rigid and flexible, requiring sufficient stiffness to transmit torque while maintaining sufficient flexibility to provide shock absorption.

[0004] This leads to a paradoxical problem. Existing technical solutions generally use non-metallic elastomers as elastic members. However, to ensure that the coupling can transmit sufficiently high torque, the non-metallic elastic members are generally made of high hardness, resulting in limited cushioning and shock absorption (that is, the hardness of the non-metallic elastic members prevents them from providing adequate cushioning). Furthermore, the hubs on both ends of the coupling are relatively fixed, which limits its ability to compensate for axial errors to a very small range.

[0005] Therefore, those skilled in the art provide a high-elasticity and heavy-duty coupling for a grinding mill to solve the problems raised in the above background technology. Utility Model Content

[0006] The purpose of the utility model is to solve the shortcomings in the prior art and to propose a high-elasticity and heavy-load coupling for a grinding mill.

[0007] To achieve the above objectives, the present invention provides the following technical solutions:

[0008] A high-elasticity and heavy-load coupling for a grinding mill, comprising:

[0009] An inner gear ring, wherein the inner gear ring is provided with inner teeth extending toward the center of the inner gear ring, and a tooth groove is formed between every two inner teeth;

[0010] An outer gear ring, wherein the outer gear ring is provided with outer teeth extending away from the center of the outer gear ring, the outer gear ring is sleeved inside the inner gear ring, and one outer tooth is provided in one tooth groove;

[0011] There are multiple elastomer groups, one of which is disposed between one of the outer teeth and one of the inner teeth. The elastomer group includes at least a first hardness elastomer group and a second hardness elastomer group. The hardness of the first hardness elastomer group is greater than that of the second hardness elastomer group.

[0012] When the mill is started with the high-elasticity and heavy-load coupling, the second hardness elastic body group is first subjected to force. After the second hardness elastic body group is squeezed and deformed under the force, the first hardness elastic body group begins to be subjected to force.

[0013] Optionally, each tooth groove is divided into a first volume tooth groove and a second volume tooth groove by the external teeth located in the tooth groove, the first hardness elastomer group is accommodated in the first volume tooth groove, and the second hardness elastomer group is accommodated in the second volume tooth groove.

[0014] Optionally, each of the first hardness elastic body groups includes one first hardness elastic body;

[0015] Each of the second hardness elastomer groups includes a second hardness elastomer.

[0016] Optionally, each second hardness elastic body includes at least one second elastomer first hardness region and one second elastomer second hardness region, wherein the hardness of the second elastomer first hardness region is less than that of the second elastomer second hardness region; wherein,

[0017] When the second hardness elastic body is subjected to force, the force first acts on the first hardness region of the second elastic body.

[0018] Optionally, each first hardness elastic body includes at least one first hardness region of the first elastic body and one first hardness region of the first elastic body, wherein the hardness of the first hardness region of the first elastic body is less than that of the first hardness region of the first elastic body; wherein,

[0019] When the first hardness elastic body is subjected to force, the force first acts on the first hardness region of the first elastic body.

[0020] Optionally, each of the first hardness elastic bodies includes a first hardness elastic body first side surface, a first hardness elastic body second side surface, a first hardness elastic body third side surface, and a first hardness elastic body fourth side surface, wherein the first hardness elastic body first side surface is arranged opposite to the first hardness elastic body second side surface;

[0021] The third side surface of the first hardness elastic body is arranged opposite to the fourth side surface of the first hardness elastic body;

[0022] The first side surface of the first hardness elastic body contacts the peripheral side wall of the inner gear ring of the inner gear ring;

[0023] The second side surface of the first hardness elastic body contacts the peripheral side wall of the outer gear ring;

[0024] The third side surface of the first hardness elastic body contacts the inner teeth of the inner gear ring or contacts the outer teeth of the outer gear ring; wherein,

[0025] The first hardness elastic body is limited at least by the circumferential side wall of the inner gear ring and the circumferential side wall of the outer gear ring.

[0026] Optionally, each of the second hardness elastic bodies includes a second hardness elastic body first side surface, a second hardness elastic body second side surface, a second hardness elastic body third side surface, and a second hardness elastic body fourth side surface, wherein the second hardness elastic body first side surface is arranged opposite to the second hardness elastic body second side surface;

[0027] The third side surface of the second hardness elastic body is arranged opposite to the fourth side surface of the second hardness elastic body;

[0028] The first side surface of the second hardness elastic body contacts the peripheral side wall of the inner gear ring of the inner gear ring;

[0029] The second side surface of the second hardness elastic body contacts the peripheral side wall of the outer gear ring;

[0030] The third side surface of the second hardness elastic body contacts one of the inner teeth of the inner gear ring or the outer teeth of the outer gear ring;

[0031] The fourth side surface of the second hardness elastic body contacts the inner teeth of the inner gear ring or contacts the outer teeth of the outer gear ring; wherein,

[0032] The first elastic body is limited at least by the circumferential side wall of the inner gear ring, the inner teeth, the circumferential side wall of the outer gear ring and the outer teeth.

[0033] Optionally, a plurality of strip grooves are provided on the outer surface of the first hardness elastomer, each strip groove divides the first hardness elastomer into a plurality of elastic regions, wherein the first hardness region of the first elastomer is located in the elastic region in the middle of the first hardness elastomer.

[0034] Optionally, the shape of the inner tooth is: the thickness gradually increases from one end of the inner tooth to the other end, wherein the end with a thicker thickness is the inner tooth thick end, and the other end is the inner tooth thin end;

[0035] The shape of the external teeth is as follows: the thickness gradually increases from one end to the other end of the external teeth, wherein the end with the thicker thickness is the external tooth thick end, and the other end is the external tooth thin end; wherein,

[0036] In the assembled state, the thick end of the inner teeth is arranged opposite to the thin end of the outer teeth, and the thin end of the inner teeth is arranged opposite to the thick end of the outer teeth.

[0037] The utility model has the following beneficial effects:

[0038] The high-elasticity and heavy-load coupling for a grinding mill proposed by the utility model is designed through the elastomer, so that the first hardness elastomer group and the second hardness elastomer group cooperate to achieve both a softer hardness cushioning property and a harder torque transmission function. When the equipment is started, the elastomer with lower hardness is first subjected to force and compressed, providing a good buffering and shock-absorbing effect; when compressed to a certain amount, the elastomer with higher hardness begins to contact and bear force, thereby transmitting a larger torque. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Figure 1 This is a schematic cross-sectional view of a high-elasticity and heavy-load coupling for a grinding mill in the first embodiment of the present application;

[0040] Figure 2 This is a schematic cross-sectional view of an inner gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0041] Figure 3 This is a schematic structural diagram of an inner gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0042] Figure 4 This is a structural schematic diagram of an outer gear ring of a high-elasticity and heavy-load coupling for a grinding mill in the first embodiment of the present application;

[0043] Figure 5 This is a schematic cross-sectional view of the outer gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0044] Figure 6 This is a schematic structural diagram of an elastic body in a high-elasticity and heavy-load coupling for a grinding mill according to a second embodiment of the present application;

[0045] Figure 7 This is a schematic structural diagram of an elastic body in a high-elasticity and heavy-load coupling for a grinding mill according to the third embodiment of the present application;

[0046] Figure 8 This is a structural schematic diagram of a high-elasticity and heavy-load coupling for a grinding mill according to the third embodiment of the present application.

[0047] Legend:

[0048] 1. Inner gear ring; 11. Inner teeth; 2. Outer gear ring; 21. Outer teeth; 3. Elastomer; 31. First hardness portion; 32. Second hardness portion; 12. Peripheral side wall of inner gear ring; 22. Peripheral side wall of outer gear ring; 4. First volume tooth groove; 5. Second volume tooth groove; 111. Thick end of inner teeth; 112. Thin end of inner teeth; 211. Thick end of outer teeth; 212. Thin end of outer teeth; 6. End cover; 7. Strip groove; 311. First hardness area of ​​first elastomer; 312. First hardness area of ​​first elastomer; 313. First side surface of first hardness elastomer; 316. Fourth side surface of first hardness elastomer. DETAILED DESCRIPTION

[0049] The following, in conjunction with the accompanying drawings, provides a clear and complete description of the technical solutions in the embodiments of the present invention. It should be noted that the described embodiments are only some of the embodiments of the present invention, and are not intended to be exhaustive. Based on the embodiments of the present invention, all other embodiments derived by persons of ordinary skill in the art without inventive effort are within the scope of protection of the present invention. It should be noted that the terms used herein are intended solely to describe specific embodiments and are not intended to limit the exemplary embodiments of the present invention. For ease of description, the dimensions of the various parts shown in the drawings are not drawn to scale. Technologies, methods, and devices known to persons of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, such technologies, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely illustrative and not limiting. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following figures. Therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0050] like Figures 1 to 5 The high elastic heavy load coupling for mill shown in the figure comprises an inner gear ring 1, an outer gear ring 2 and an elastic body group 3, wherein:

[0051] The inner gear ring 1 is provided with inner teeth 11 extending toward the center of the inner gear ring 1, and a tooth groove is formed between every two inner teeth;

[0052] The outer gear ring 2 is provided with outer teeth 21 extending away from the center of the outer gear ring. The outer gear ring 2 is sleeved inside the inner gear ring, and one outer tooth is provided in one tooth groove.

[0053] There are multiple elastomer groups 3, one of which is disposed between one of the outer teeth 21 and one of the inner teeth 11. The elastomer group 3 includes at least a first hardness elastomer group and a second hardness elastomer group. The hardness of the first hardness elastomer group is greater than that of the second hardness elastomer group.

[0054] When the high-elasticity and heavy-load coupling for the grinding mill is started, the second hardness elastic body group is first subjected to force. After the second hardness elastic body group is squeezed and deformed to a preset threshold value, the first hardness elastic body group begins to be subjected to force.

[0055] It is understandable that the preset threshold value can be set by changing the hardness and shape of the second hardness elastic body group as needed.

[0056] In this embodiment, the interior of the outer gear ring is used to connect with the shaft of an external device.

[0057] The high-elasticity and heavy-load coupling for a grinding mill proposed in the utility model is designed so that the elastomer has both a softer cushioning property and a harder torque transmission function. When the equipment is started, the elastomer with lower hardness is first subjected to force and compressed, providing a good buffering and shock-absorbing effect; when compressed to a certain amount, the elastomer with higher hardness begins to contact and bear force, thereby transmitting a larger torque.

[0058] See also Figure 1 In this embodiment, each tooth groove is divided into a first volume tooth groove and a second volume tooth groove by an external tooth 21 located in the tooth groove. The first hardness elastomer group is accommodated in the first volume tooth groove 4, and the second hardness elastomer group is accommodated in the second volume tooth groove 5.

[0059] See also Figure 1 In this embodiment, the inner gear ring 1 further includes an inner gear ring peripheral side wall 12, and the inner teeth are formed by protruding from the inner gear ring peripheral side wall 12 toward the center of the inner gear ring;

[0060] The outer gear ring 2 further includes an outer gear ring peripheral side wall 22 , and the outer teeth are formed by protruding from the outer gear ring peripheral side wall 22 toward the outside of the outer gear ring.

[0061] See also Figure 1 In this embodiment, each first hardness elastic body group includes a first hardness elastic body 31;

[0062] Each second hardness elastic body group includes a second hardness elastic body 32; wherein,

[0063] The volume of the second hardness elastic body 32 is larger than that of the first hardness elastic body 31 .

[0064] In this way, it can be ensured that during the movement of the inner teeth and the outer teeth, the force is first transmitted to the first hardness elastic body 32 .

[0065] See also Figure 1 In this embodiment, the volume of at least one of the first-volume tooth grooves 4 is configured to accommodate at least one second-hardness elastic member 32. That is, in this embodiment, the volume of the first-volume tooth groove 4 is larger than the first-hardness elastic member 32 accommodated therein. In this case, when the outer gear ring rotates clockwise, the second-hardness elastic member 32 is squeezed first. While the inner gear ring has not yet rotated, the outer gear ring rotates, eliminating the gap within the first-volume tooth groove 4 (i.e., the compression of the second-hardness elastic member 32 is substantially equal to the gap within the first-volume tooth groove 4). At this point, the first-hardness elastic member within the first-volume tooth groove 4 begins to be subjected to force, thereby transmitting greater torque.

[0066] In other words, whether to design a gap, the size of the designed gap and the position of the gap can all be set according to your own needs.

[0067] In this embodiment, each second hardness elastic body 32 includes at least one second elastic body first hardness region and one second elastic body second hardness region, wherein the hardness of the second elastic body first hardness region is less than that of the second elastic body second hardness region; wherein,

[0068] When the second hardness elastic body is subjected to force, the force first acts on the first hardness region of the second elastic body.

[0069] In this way, the second hardness elastic body can also be given a certain cushioning change by different hardness. In this embodiment, the hardness of both the first hardness region of the second elastic body and the second hardness region of the second elastic body is less than that of the first hardness elastic body.

[0070] In this embodiment, each first hardness elastic body 31 includes at least a first elastic body first hardness region 311 and a first elastic body second hardness region 312, wherein the hardness of the first elastic body first hardness region 311 is less than that of the first elastic body second hardness region 312; wherein,

[0071] When the first hardness elastic body is subjected to force, the force first acts on the first hardness region of the first elastic body.

[0072] In this way, for the first hardness elastomer, a certain cushioning change can also be given by different hardness.

[0073] See also Figure 6 as well as Figure 7In this embodiment, each first hardness elastic body 31 includes a first hardness elastic body first side surface 313, a first hardness elastic body second side surface, a first hardness elastic body third side surface and a first hardness elastic body fourth side surface 316, wherein the first hardness elastic body first side surface 313 is arranged opposite to the first hardness elastic body second side surface;

[0074] The third side surface of the first hardness elastic body is disposed opposite to the fourth side surface 316 of the first hardness elastic body;

[0075] The first side surface 313 of the first hardness elastic body contacts the inner gear peripheral side wall 12 of the inner gear ring 1;

[0076] The second side surface of the first hardness elastic body contacts the outer gear ring circumferential side wall 22 of the outer gear ring 2;

[0077] The third side surface of the first hardness elastic body contacts the inner teeth 11 of the inner gear ring 1 or contacts the outer teeth 21 of the outer gear ring 2; wherein,

[0078] The first hardness elastic body is limited at least by the inner gear ring peripheral side wall 12 and the outer gear ring peripheral side wall 22 .

[0079] In this embodiment, each second hardness elastic body 32 includes a second hardness elastic body first side surface, a second hardness elastic body second side surface, a second hardness elastic body third side surface, and a second hardness elastic body fourth side surface, wherein the second hardness elastic body first side surface is arranged opposite to the second hardness elastic body second side surface;

[0080] The third side surface of the second hardness elastic body is arranged opposite to the fourth side surface of the second hardness elastic body;

[0081] The first side surface of the second hardness elastic body contacts the inner gear ring circumferential side wall 12 of the inner gear ring 1;

[0082] The second side surface of the second hardness elastic body contacts the outer gear ring circumferential side wall 22 of the outer gear ring 2;

[0083] The third side surface of the second hardness elastic body contacts one of the inner teeth 11 of the inner gear ring 1 or the outer teeth 21 of the outer gear ring 2;

[0084] The fourth side surface of the second hardness elastic body contacts the inner teeth 11 of the inner gear ring 1 or contacts the outer teeth 21 of the outer gear ring 2; wherein,

[0085] The first elastic body is limited at least by the inner gear ring peripheral side wall 12 , the inner teeth 11 , the outer gear ring peripheral side wall 22 and the outer teeth 21 .

[0086] See also Figure 7In this embodiment, a plurality of strip grooves 7 are provided on the outer surface of the first hardness elastomer 31, and each strip groove 7 divides the first hardness elastomer 31 into a plurality of elastic regions, wherein the first hardness region of the first elastomer is located in the elastic region in the middle of the first hardness elastomer 31.

[0087] See also Figure 3 as well as Figure 4 In this embodiment, the shape of the inner tooth 11 is as follows: the thickness gradually increases from one end of the inner tooth 11 to the other end, wherein the end with a thicker thickness is an inner tooth thick end 111, and the other end is an inner tooth thin end 112;

[0088] The shape of the outer teeth 21 is as follows: the thickness gradually increases from one end to the other end of the outer teeth 21, wherein the thicker end is the outer tooth thick end 211, and the other end is the outer tooth thin end 212;

[0089] In the assembled state, the inner tooth thick end 111 is disposed opposite to the outer tooth thin end 212 , and the inner tooth thin end 112 is disposed opposite to the outer tooth thick end 211 .

[0090] See also Figure 8 In this embodiment, the high-elasticity and heavy-load coupling for the grinding mill further includes an end cover 6 , which is arranged on one side of the outer gear ring 2 .

[0091] The present application also provides a design method for a high-elasticity and heavy-load coupling for a mill, the design method for a high-elasticity and heavy-load coupling for a mill comprising:

[0092] Step 1: Obtain the target function;

[0093] Step 2: Obtain parameter information of the high-elasticity and heavy-load coupling for the grinding mill;

[0094] Step 3: Create a finite element model of the high-elasticity and heavy-load coupling for the mill according to the parameter information of the high-elasticity and heavy-load coupling for the mill;

[0095] Step 4: Solve the finite element model of the high-elasticity and heavy-load coupling for the mill using ABAQUS software, and output the hardness information of the first hardness elastic body group and the hardness information of the second hardness elastic body group;

[0096] Step 5: According to the Bayesian optimization method, iterate a new parameter combination and repeat steps 3 and 4 until the number of iterations reaches a preset value;

[0097] Step 6: Obtain the optimal hardness information of the first hardness elastomer group and the optimal hardness information of the second hardness elastomer group based on the objective function and the hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group calculated each time.

[0098] The design method for a highly elastic, heavy-duty mill coupling in this application requires only input of the coupling's parameter information, along with the permitted geometric parameter ranges and material property ranges for fabrication. Within these parameters, parameters that meet performance requirements are automatically iterated. This reduces the experimental testing and iteration required to design a highly elastic, heavy-duty mill coupling for different application scenarios. This makes the optimization design method in this application more efficient.

[0099] In this embodiment, the parameter information of the high-elasticity and heavy-load coupling for the grinding mill includes:

[0100] Parameter information of the inner gear ring (such as stiffness, size), number information and parameter information (such as stiffness, size) of the inner teeth, parameter information of the outer gear ring (such as stiffness, size), number information and parameter information (such as stiffness, size) of the outer teeth, and the initial length of the elastic part.

[0101] In this embodiment, the objective function is as follows:

[0102] in,

[0103] σ max is the maximum torque of the high elastic heavy load coupling for mill in the finite element calculation results, a σ is the weight corresponding to the maximum torque of the high elastic heavy load coupling, y i,Target is the i-th target performance, y i is the i-th performance calculated by the current simulation, a i is the weight of the i-th objective performance.

[0104] In this embodiment, creating a finite element model of a high-elasticity and heavy-load coupling for a mill according to parameter information of the high-elasticity and heavy-load coupling for a mill includes:

[0105] Establish inner gear ring unit, outer gear ring unit, and elastic body unit; among them, the outer gear ring unit and the inner gear ring unit are beam unit models;

[0106] Assign material parameters to the inner gear ring unit, outer gear ring unit, and elastic body unit respectively;

[0107] The various units are assembled together and interaction relationships are set to form a finite element model of the high-elasticity and heavy-load coupling for the mill.

[0108] In this embodiment, defining the objective function according to the target performance includes:

[0109] A target property of a given elastic body, such as the stiffness of the elastic body;

[0110] Define the minimization objective function based on the target performance.

[0111]

[0112] Among them, y i,Target is the i-th target performance, y i is the i-th performance calculated by the current simulation, a i is the weight of the i-th objective performance.

[0113] In this embodiment, the interaction relationship of the present application includes the displacement coupling and limiting relationship between the elastic body and the outer gear ring and the inner gear ring.

[0114] Finally, it should be noted that the above is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art can still modify the technical solutions described in the aforementioned embodiments or make equivalent replacements for some of the technical features therein. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A high elasticity and heavy load coupling for a grinding mill, characterized in that: The high elasticity and heavy load coupling for the grinding mill comprises: An inner gear ring (1), wherein the inner gear ring (1) is provided with inner teeth (11) extending toward the center of the inner gear ring (1), and a tooth groove is formed between every two inner teeth; An outer gear ring (2), wherein the outer gear ring (2) is provided with outer teeth (21) extending in a direction away from the center of the outer gear ring, the outer gear ring (2) is sleeved inside the inner gear ring, and one of the outer teeth is provided in one tooth groove; An elastomer group (3), wherein the number of the elastomer groups (3) is plural, and one elastomer group (3) is arranged between one of the outer teeth (21) and one of the inner teeth (11), and the elastomer group (3) comprises at least a first hardness elastomer group and a second hardness elastomer group, wherein the hardness of the first hardness elastomer group is greater than the hardness of the second hardness elastomer group; wherein, When the grinding mill is started with the high-elasticity and heavy-load coupling, the second hardness elastic body group is first subjected to force. After the second hardness elastic body group is squeezed and deformed under the force, the first hardness elastic body group begins to be subjected to force.

2. The high elasticity and heavy load coupling for grinding mill according to claim 1, characterized in that: Each tooth groove is divided into a first volume tooth groove and a second volume tooth groove by the external teeth (21) located in the tooth groove. The first hardness elastomer group is accommodated in the first volume tooth groove, and the second hardness elastomer group is accommodated in the second volume tooth groove.

3. The high elasticity and heavy load coupling for grinding mill according to claim 2, characterized in that: Each of the first hardness elastic body groups includes a first hardness elastic body (31); Each of the second hardness elastic body groups includes a second hardness elastic body (32).

4. The high elasticity and heavy load coupling for grinding mill according to claim 3, characterized in that: Each second hardness elastic body (32) comprises at least one second elastic body first hardness region and one second elastic body second hardness region, wherein the hardness of the second elastic body first hardness region is less than that of the second elastic body second hardness region; wherein, When the second hardness elastic body is subjected to force, the force first acts on the first hardness region of the second elastic body.

5. The high elasticity and heavy load coupling for grinding mill according to claim 3, characterized in that: Each first hardness elastic body (31) comprises at least a first elastic body first hardness region (311) and a first elastic body second hardness region (312), wherein the hardness of the first elastic body first hardness region (311) is less than that of the first elastic body second hardness region (312); wherein, When the first hardness elastic body is subjected to force, the force first acts on the first hardness region of the first elastic body.

6. The high elasticity and heavy load coupling for a grinding mill according to any one of claims 1 to 5, characterized in that: Each of the first hardness elastic bodies (31) comprises a first hardness elastic body first side surface (313), a first hardness elastic body second side surface, a first hardness elastic body third side surface, and a first hardness elastic body fourth side surface (316), wherein the first hardness elastic body first side surface (313) is arranged opposite to the first hardness elastic body second side surface; The third side surface of the first hardness elastic body is arranged opposite to the fourth side surface (316) of the first hardness elastic body; The first side surface (313) of the first hardness elastic body contacts the inner gear ring peripheral side wall (12) of the inner gear ring (1); The second side surface of the first hardness elastic body contacts the outer gear ring peripheral side wall (22) of the outer gear ring (2); The third side surface of the first hardness elastic body contacts the inner teeth (11) of the inner gear ring (1) or contacts the outer teeth (21) of the outer gear ring (2); wherein, The first hardness elastic body is limited at least by the inner gear ring peripheral side wall (12) and the outer gear ring peripheral side wall (22).

7. The high elasticity and heavy load coupling for a grinding mill according to any one of claims 1 to 5, characterized in that: Each of the second hardness elastic bodies (32) comprises a second hardness elastic body first side surface, a second hardness elastic body second side surface, a second hardness elastic body third side surface, and a second hardness elastic body fourth side surface, wherein the second hardness elastic body first side surface is arranged opposite to the second hardness elastic body second side surface; The third side surface of the second hardness elastic body is arranged opposite to the fourth side surface of the second hardness elastic body; The first side surface of the second hardness elastic body contacts the inner gear ring peripheral side wall (12) of the inner gear ring (1); The second side surface of the second hardness elastic body contacts the outer gear ring peripheral side wall (22) of the outer gear ring (2); The third side surface of the second hardness elastic body contacts one of the inner teeth (11) of the inner gear ring (1) or the outer teeth (21) of the outer gear ring (2); The fourth side surface of the second hardness elastic body contacts the other of the inner teeth (11) of the inner gear ring (1) or the outer teeth (21) of the outer gear ring (2); wherein, The first elastic body is limited at least by the inner gear ring peripheral side wall (12), the inner teeth (11), the outer gear ring peripheral side wall (22), and the outer teeth (21).

8. The high elasticity and heavy load coupling for a grinding mill according to claim 6, characterized in that: A plurality of strip grooves (7) are provided on the outer surface of the first hardness elastomer (31), and each strip groove (7) divides the first hardness elastomer (31) into a plurality of elastic regions, wherein the first hardness region of the first elastomer is located in the elastic region in the middle of the first hardness elastomer (31).

9. The high elasticity and heavy load coupling for grinding mill according to claim 1, characterized in that: The shape of the inner tooth (11) is as follows: the thickness gradually increases from one end of the inner tooth (11) to the other end, wherein the end with a thicker thickness is the inner tooth thick end (111), and the other end is the inner tooth thin end (112); The shape of the outer tooth (21) is as follows: the thickness gradually increases from one end of the outer tooth (21) to the other end, wherein the end with a thicker thickness is the outer tooth thick end (211), and the other end is the outer tooth thin end (212); wherein, In the assembled state, the inner tooth thick end (111) and the outer tooth thin end (212) are arranged opposite to each other, and the inner tooth thin end (112) and the outer tooth thick end (211) are arranged opposite to each other.

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