Shaft joint device and torsional natural frequency adjustment method

Abstract

The shaft joint device of one embodiment is a shaft joint device for connecting a first shaft and a second shaft, and includes a first inner ring member attached to the first shaft, a first outer ring member disposed on the outer periphery side of the first inner ring member, a first elastic member connecting the first inner ring member and the first outer ring member, a second inner ring member attached to the second shaft, a second outer ring member disposed on the outer periphery side of the second inner ring member, a second elastic member connecting the second inner ring member and the second outer ring member, and a counterweight attachment plate sandwiched between the first outer ring member and the second outer ring member, which has a counterweight attachment portion capable of attaching and detaching a counterweight member on the outer periphery side of the first outer ring member and the second outer ring member.

Description

Technical Field

[0001] This disclosure relates to a shaft joint device and a method for adjusting the torsional natural vibration frequency of the shaft joint device. Background Technology

[0002] When torque (torsional torque) is applied to a rotating shaft, torsional vibration occurs, resulting in a periodic change in the shaft's torsional angle. Resonance occurs when the angular vibration frequency of the torque variation applied to the rotating shaft approaches the shaft's natural torsional vibration frequency. In the case of an engine crankshaft, resonance is possible when the angular vibration frequency of the torque variation, determined by the engine speed, approaches the crankshaft's natural torsional vibration frequency. Therefore, resonance avoidance design is implemented during the design phase. However, since the resonance frequency is an integer multiple of half the engine speed, the frequency range within which resonance can be avoided becomes very narrow.

[0003] Patent documents 1 and 2 disclose a shaft joint device in which a counterweight is attached to the joint connecting two shafts. The torsional natural vibration frequency of the shaft system is adjusted by increasing or decreasing the number of counterweights, thereby avoiding resonance. These shaft joint devices describe the ability to make adjustments without removing the joint from the shaft system.

[0004] Existing technical documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2012-191842

[0006] Patent Document 2: Japanese Patent Application Publication No. 2015-135181 Summary of the Invention

[0007] The technical problem that the invention aims to solve

[0008] In Patent Documents 1 and 2, no elastic joint is used as the shaft joint, therefore the shaft joint lacks vibration absorption capacity. Consequently, excessive stress may be generated in the shaft system when resonance occurs, potentially causing shaft damage. Furthermore, Patent Document 1 uses a large-diameter and heavy-mass tuning ring, resulting in the need for a large installation space, difficulty in replacing tuning rings with different masses, and the inability to perform fine-tuning of the mass. Additionally, the large inertial force generated by the shaft rotation makes it unsuitable for crankshafts in high-speed engines. Patent Document 2 suffers from the problem of requiring a large-scale device around the shaft joint and space for installing such a device to replace the counterweight.

[0009] This disclosure was made in view of the above-mentioned problems, and its purpose is to provide a shaft joint device that can easily adjust the torsional natural vibration frequency for resonance avoidance when the shaft joint adopts an elastic joint with vibration absorption capability.

[0010] Technical solutions for solving technical problems

[0011] To achieve the above objectives, the first shaft connector device disclosed herein addresses the aforementioned problems and is a shaft connector device for connecting a first shaft and a second shaft, comprising: a first inner ring member mounted on the first shaft; a first outer ring member disposed on the outer periphery of the first inner ring member; a first elastic member connecting the first inner ring member and the first outer ring member; a second inner ring member mounted on the second shaft; a second outer ring member disposed on the outer periphery of the second inner ring member; a second elastic member connecting the second inner ring member and the second outer ring member; and a counterweight mounting plate sandwiched between the first outer ring member and the second outer ring member, having a counterweight mounting portion on the outer periphery of both the first outer ring member and the second outer ring member for detaching and mounting counterweight components.

[0012] To achieve the above objectives, the second shaft connector device disclosed herein is a shaft connector device for connecting a first shaft and a second shaft, comprising: an inner ring member mounted on the first shaft; an outer ring member mounted on the second shaft and disposed on the outer periphery of the inner ring member; an elastic member connecting the inner ring member and the outer ring member; an inner elastic body mounted on the inner periphery of the inner ring member; and a counterweight member detachably supported on the inner elastic body at a location closer to the inner periphery than the inner elastic body.

[0013] Furthermore, the torsional natural vibration frequency adjustment method disclosed herein is a method for adjusting the torsional natural vibration frequency of a shaft system including a first shaft, a second shaft, the aforementioned first shaft joint device, or the aforementioned second shaft joint device. The method includes: a measurement step, which measures the torsional natural vibration frequency of the shaft system; an evaluation step, which evaluates the resonance state of the shaft system based on the measurement result of the torsional natural vibration frequency; and an adjustment step, which disassembles and assembles the counterweight component according to the evaluation result of the resonance state, thereby adjusting the torsional natural vibration frequency of the shaft system.

[0014] The effects of the invention

[0015] According to the first and second shaft joint devices of this disclosure, when the shaft joint adopts an elastic joint with vibration absorption capability, excessive stress will not be generated even if resonance occurs in the shaft system. Furthermore, the torsional natural vibration frequency for resonance avoidance can be easily adjusted using a compact structure, and the adjustment range of the torsional natural vibration frequency can be expanded. Moreover, according to the torsional natural vibration frequency adjustment method of this disclosure, in addition to the above-mentioned effects, the range of variation of the torsional natural vibration frequency can also be expanded. Attached Figure Description

[0016] Figure 1 This is a front cross-sectional view of a shaft joint device according to one embodiment.

[0017] Figure 2 This is a front view of a counterweight mounting plate in one implementation method.

[0018] Figure 3 This is a front cross-sectional view of a shaft joint device according to one embodiment.

[0019] Figure 4 It is along Figure 3 The view of line AA in the diagram.

[0020] Figure 5A This diagram illustrates the torsional vibration state of a shaft system, including the shaft joint assembly.

[0021] Figure 5B This diagram illustrates the torsional vibration state of a shaft system, including the shaft joint assembly.

[0022] Figure 6 It is a line graph showing the relationship between the natural frequency of torsional vibration and the mass of the counterweight component.

[0023] Figure 7 This is a flowchart illustrating a method for adjusting the torsional natural vibration frequency during the design phase of a shaft system in one implementation.

[0024] Figure 8 This is a flowchart illustrating a method for adjusting the torsional natural vibration frequency during the trial operation phase of a shaft system according to one embodiment. Detailed Implementation

[0025] Hereinafter, several embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, and relative arrangements of the constituent parts described in these embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples.

[0026] For example, expressions such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial" indicate relative or absolute configurations, not only strictly indicating such configurations, but also indicating a state of relative displacement by angle or distance with tolerances or to the extent that the same function can be achieved.

[0027] For example, expressions such as "same," "equal," and "equal in quality" that indicate the state of equality not only strictly represent the state of equality, but also indicate the state of difference in degree or the degree to which the same function can be obtained.

[0028] For example, the expression of shape, such as square or cylindrical, not only refers to square or cylindrical shapes in a strict geometric sense, but also to shapes that include concave or convex parts or chamfered parts within the range that can achieve the same effect.

[0029] On the other hand, expressions such as “setting,” “having,” “possessing,” “including,” or “containing” a constituent element are not exclusive expressions that exclude the existence of other constituent elements.

[0030] Figure 1 This is a cross-sectional view showing a shaft connector device 10 (10A) according to one embodiment. The shaft connector device 10 (10A) is provided for connecting a first shaft 100 and a second shaft 102. The shaft connector device 10 (10A) is composed of a component disposed on the side of the counterweight mounting plate 24 located at the axial center of the first shaft 100 or the second shaft 102, and a component disposed on the side of the counterweight mounting plate 24 located at the axial center of the second shaft 102. A first inner ring component 12 is mounted on the shaft end of the first shaft 100, and a first outer ring component 14 is disposed on the outer periphery of the first inner ring component 12. The first inner ring component 12 and the first outer ring component 14 are connected by a first elastic member 16 disposed between these components.

[0031] On the other hand, on the second shaft 102 side, a second inner ring member 18 is installed at the shaft end of the second shaft 102, and a second outer ring member 20 is disposed on the outer periphery of the second inner ring member 18. The second inner ring member 18 and the second outer ring member 20 are connected by a second elastic member 22 disposed between these members. A counterweight mounting plate 24 is clamped between the first outer ring member 14 and the second outer ring member 20 by these members. The counterweight mounting plate 24 has a counterweight mounting portion 26 on the outer periphery of the first outer ring member 14 and the second outer ring member 20. The counterweight mounting portion 26 is configured to allow for the detachment and mounting of the counterweight member 28.

[0032] When the torsional natural vibration frequency of the first shaft 100 or the second shaft 102 is close to the torsional natural vibration frequency of the shaft joint device 10 (10A) alone, and resonance may occur, the torsional natural vibration frequency of the shaft joint device 10 (10A) can be changed by adjusting the mass and number of the counterweight components 28 installed on the counterweight mounting part 26, thereby suppressing the occurrence of resonance.

[0033] According to the above embodiment, the first shaft 100 side and the second shaft 102 side are connected via the first elastic member 16 and the second elastic member 22, and the counterweight mounting plate 24 is also connected to the first shaft 100 side and the second shaft 102 side via the first elastic member 16 and the second elastic member 22. Therefore, the vibration generated in the shaft system is absorbed by the first elastic member 16 and the second elastic member 22, and the vibration of the shaft system is attenuated and transmitted to the counterweight mounting plate 24. Therefore, even if resonance occurs in the shaft system, excessive stress will not be generated, thus suppressing damage to the shaft system. Furthermore, the counterweight mounting portion 26 formed on the counterweight mounting plate 24 is located on the outer periphery of the two outer ring members 14 and 20, so the counterweight member 28 can be easily disassembled and assembled without disassembling the shaft joint device 10 (10A), thereby facilitating the adjustment of the torsional natural vibration frequency. Moreover, the counterweight member 28 is positioned radially away from the axis of rotation of the shaft system, so even if the mass of the counterweight member 28 is small, a large torque can be generated. This allows for an expansion of the adjustment range of the torsional natural vibration frequency of the shaft joint device 10 (10A).

[0034] The first inner ring component 12, the first outer ring component 14, the second inner ring component 18, and the second outer ring component 20 are made of rigid materials such as metal. The first elastic component 16 and the second elastic component 22 are made of elastic materials such as rubber (e.g., natural rubber with self-dampening properties).

[0035] In one embodiment, the first shaft 100 is a crankshaft of an internal combustion engine (not shown), and the second shaft 102 is a rotating shaft mounted on a generator (not shown). In this case, the first shaft 100 is the drive shaft, and the second shaft 102 is the driven shaft. The rotation of the crankshaft of the first shaft 100 is transmitted to the rotating shaft of the second shaft 102 via the shaft joint device 10 (10A), thereby activating the generator.

[0036] In one implementation, such as Figure 1 As shown, the first inner ring component 12 includes a main body 12a and a bottom 12b. The main body 12a has a flange 12a1 extending radially at one axial end of the cylindrical portion, and the bottom 12b is fixed to the flange 12a1. The first shaft 100 is connected to the bottom 12b. The second inner ring component 18 also has the same shape, including a main body 18a and a bottom 18b. The main body 18a has a flange 18a1 extending radially at one axial end of the cylindrical portion, and the bottom 18b is fixed to the flange 18a1. The second shaft 102 is connected to the bottom 18b.

[0037] exist Figure 1In the exemplary embodiment shown, bolts 21a are screwed into threaded holes formed axially in the cylindrical body of a first outer ring member 14 and a second outer ring member 20, which are bottomless cylindrical shapes. Nuts 21b are fastened to a counterweight mounting plate 24 opposite to the threaded holes, with the bolts 21a engaging with the nuts 21b, thereby supporting the counterweight mounting plate 24 on the bolts 21a. The counterweight mounting plate 24 side end faces of the main body portion 12a of the first inner ring member 12 and the main body portion 18a of the second inner ring member 18 are closer to the counterweight mounting plate 24 side than the counterweight mounting plate 24 side end faces of the first outer ring member 14 and the second outer ring member 20. When the main body portion 12a or the main body portion 18a contacts the counterweight mounting plate 24, the vibration absorption capacity of the first elastic member 16 or the second elastic member 22 is reduced. Therefore, by adjusting the amount of protrusion of the bolt 21a protruding from the nut 21b toward the counterweight mounting plate 24, a gap can be formed between the main body 12a or the main body 18a and the counterweight mounting plate 24.

[0038] In one implementation, such as Figure 2 As shown, the counterweight mounting plate 24 is composed of a circular plate-like body, for example, made of a rigid material.

[0039] In one implementation, such as Figure 2 As shown, the counterweight mounting portion 26 formed on the counterweight mounting plate 24 has a plurality of through holes 30 formed circumferentially at intervals on the outer periphery of the first outer ring member 14 and the second outer ring member 20. According to this embodiment, by selecting the through hole 30 for mounting the counterweight member 28 among the plurality of through holes 30, the torsional natural vibration frequency of the shaft joint device 10 (10A) can be adjusted, and by adjusting the mass and number of the counterweight members 28 mounted in the plurality of through holes 30, the torsional natural vibration frequency can be finely adjusted.

[0040] The counterweight component 28 is made of, for example, a small-diameter circular plate made of metal, and is fixed to the counterweight mounting part 26 by means of mounting means such as bolts 34 inserted into the through hole 30. The counterweight component 28 is appropriately mounted on one or both sides of the plate-shaped counterweight mounting plate 24. In this way, by adjusting the shape, mass and number of each counterweight component 28 mounted on the counterweight mounting part 26, the torsional natural vibration frequency of the shaft joint device 10 (10A) can be finely adjusted, and the degree of freedom of adjustment can be increased.

[0041] The mounting method of the counterweight component 28 is not limited to bolts. For example, a pin or the like can be inserted into the through hole 30 to fix the counterweight component 28. Alternatively, a fitting part for fitting the counterweight component 28 can be formed in the counterweight mounting part 26, and the counterweight component 28 can be fitted into the fitting part.

[0042] In one embodiment, through holes 30 are formed at equal intervals in the circumferential direction of the counterweight mounting plate 24. Furthermore, counterweight members 28 are installed in the through holes 30, which are symmetrically positioned relative to the center point of the counterweight mounting plate 24 through which the rotation axis CA passes. This suppresses vibrations caused by uneven mass distribution of the counterweight members 28 relative to the center point.

[0043] In one implementation, such as Figure 2 As shown, the counterweight mounting plate 24 has a through hole 32 formed at its radial center. This reduces the mass of the counterweight mounting plate itself. In one embodiment, the counterweight mounting plate 24 is divided into multiple parts in the circumferential direction. This facilitates the installation of the counterweight mounting plate 24. Figure 2 In the exemplary embodiment shown, the counterweight mounting plate 24 is divided into two in the circumferential direction.

[0044] Figure 3 This is a cross-sectional view of a shaft joint device 10 (10B) according to another embodiment for connecting the first shaft 100 and the second shaft 102. Figure 4 It is along Figure 3 The image shows a view along line AA. In this shaft connector assembly 10 (10B), an inner ring member 40 is mounted on a first shaft 100, and an outer ring member 42 is mounted on a second shaft 102. The outer ring member 42 is disposed on the outer periphery of the inner ring member 40, and the inner ring member 40 and the outer ring member 42 are connected by an elastic member 44 disposed between them. Furthermore, an inner elastic body 46 is mounted on the inner periphery of the inner ring member 40, and a counterweight member 48 is mounted on the inner periphery of the inner elastic body 46. The counterweight member 48 is supported on the inner elastic body 46 in a detachable manner.

[0045] The torsional natural vibration frequency of the shaft joint device 10 (10B) can be adjusted by changing the mass and number of the counterweights 48 mounted on the inner circumference of the inner elastic body 46. Therefore, when the torsional natural vibration frequency of the first shaft 100 or the second shaft 102 is close to the torsional natural vibration frequency of the shaft joint device 10 (10B) and resonance may occur, the torsional natural vibration frequency of the shaft joint device 10 (10B) can be changed by adjusting the mass of the counterweights 48 mounted on the inner elastic body 46, thereby suppressing the occurrence of resonance.

[0046] In the shaft joint device 10 (10B), the first shaft 100 side and the second shaft 102 side are connected via an elastic member 44, and the counterweight member 48 is also connected to the inner ring member 40 via an inner elastic body 46. Therefore, vibrations generated in the shaft system are absorbed by the elastic member 44 and the inner elastic body 46, and the vibrations of the shaft system are attenuated and transmitted to the counterweight member 48. Therefore, even if resonance occurs in the shaft system, excessive stress will not be generated, thus suppressing damage to the shaft system. Furthermore, by changing the support stiffness of the inner elastic body 46, the adjustment range of the torsional natural vibration frequency can be expanded. In this case, for example, by changing the inner elastic body 46 to an elastic body made of a different material such as hardness or Young's modulus, the support stiffness can be changed. Moreover, the counterweight member 48 is disposed on the inner circumference of the inner elastic body 46, thus allowing for compactness, and no installation space is required on the outer circumference of the shaft joint device 10 (10B).

[0047] In one implementation, such as Figure 3 As shown, the inner elastic body 46 is composed of an annular member mounted on the inner circumferential surface of the inner ring member 40. Because the inner elastic body 46 is composed of an annular member, mounting to the inner circumferential surface of the inner ring member 40 is easy, and the installation space is reduced. Furthermore, the counterweight member 48 is composed of multiple counterweight members arranged along the circumferential direction of the inner elastic body 46 on the inner circumferential side of the annular member. In this example, mounting of multiple counterweight members is easy. Therefore, the mass and number of each of the multiple counterweight members can be easily adjusted.

[0048] And, as Figure 4 As shown, the counterweight component 48 is composed of multiple rod-shaped bodies, each rod having an arcuate surface along the inner circumferential surface of the inner elastic body 46, which is composed of an annular component. This allows the multiple rod-shaped bodies to be compactly housed inside the inner elastic body 46. Various methods can be used to install the counterweight component 48 onto the inner elastic body 46. For example, it can be fixed with adhesive, or it can be installed using pins or the like.

[0049] In one implementation, such as Figure 3 As shown, the inner ring component 40 includes a large-diameter portion 40a and a small-diameter portion 40b. The large-diameter portion 40a has a flange portion 40a1 extending radially inward at one axial end, and the small-diameter portion 40b has a flange portion 40b1 extending radially outward at one axial end. The flange portions 40a1 and 40b1 are joined by means such as bolts (not shown). The other axial end of the small-diameter portion 40b is connected to the first shaft 100. The outer ring component 42 is joined to the connector plate 50 by means such as bolts (not shown), and the central portion of the opposite side of the connector plate 50 is joined to the second shaft 102.

[0050] exist Figure 3 as well as Figure 4 In the exemplary embodiment shown, an outer ring member 42 with a bottomless cylindrical shape has a bolt 52 screwed into a threaded hole 54 formed along the axial direction. When the large diameter portion 40a of the inner ring member 40 and the counterweight member 48 contact the joint plate 50, the vibration absorption capacity of the elastic member 44 and the inner elastic body 46 is reduced. Therefore, by adjusting the protrusion of the bolt 52 protruding from the outer ring member 42 toward the joint plate 50, a gap can be formed between the large diameter portion 40a and the counterweight member 48 and the joint plate 50.

[0051] Figure 5A as well as Figure 5B This is an explanatory diagram showing the torsional vibration state of the shaft system including the first shaft 100, the second shaft 102, and the counterweight mounting plate 24. Figure 5A This indicates the case where the direction of torsional vibration of the first shaft 100 and the direction of the inertial force applied based on the load of the counterweight component 28 are in the same direction. Figure 5B This indicates the case where the direction of the torsional vibration of the first shaft 100 and the direction of the inertial force applied by the counterweight component 28 are opposite.

[0052] When the torsional natural vibration frequency of the shaft joint device 10 is made close to the torsional natural vibration frequency of the first shaft 100 through the adjustment means of the above-described embodiment, such as Figure 6 As shown, the torsional natural frequencies of the two are the coupled torsional natural frequencies, i.e. Figure 6 The in-phase and out-of-phase natural vibration frequencies are shown. The natural vibration frequencies of the two vibration modes depend only on the proximity of the torsional natural vibration frequency of the shaft without the counterweight mounting plate 24 to the torsional natural vibration frequency determined solely by the elastic members 16, 22 and the counterweight mounting plate 24, and the mass of the counterweight member 28. Therefore, by adjusting the mass of the counterweight member 28, the torsional natural vibration frequency of the shaft joint device 10 can be adjusted to a vibration frequency that avoids resonance with the torsional natural vibration frequency of the first shaft 100.

[0053] For example, when the first shaft 100 is the crankshaft of an internal combustion engine, the frequency of torque variation generated by the internal combustion engine is generally an integer multiple of the rotational speed and half of it. When the torsional natural vibration frequency of the crankshaft system is close to its torque variation frequency, resonance can be avoided by utilizing the aforementioned dependence for appropriate tuning.

[0054] Figure 7 This is a process diagram of a method for adjusting the torsional natural vibration frequency according to one embodiment. This method suppresses resonance in a shaft system including a first shaft 100, a second shaft 102, and the aforementioned shaft joint devices 10 (10A, 10B) by adjusting the individual torsional natural vibration frequency of each shaft joint device 10.

[0055] like Figure 7 As shown, in the design phase of the shaft joint device 10 (10A, 10B), an analytical model of the shaft system is first created based on the design drawings (step S10). The torsional natural vibration frequency of the shaft joint device 10 is calculated based on the created analytical model (step S12). Next, the masses of the counterweight components 28 and 48 of the shaft joint device 10 (10A, 10B), and the support rigidity of the counterweight mounting plate 24 of the shaft joint device 10 (10A) or the inner ring component 40 of the shaft joint device 10 (10B) are set as parameters, and the change in the torsional natural vibration frequency is analyzed based on the calculated torsional natural vibration frequency (step S14). Based on the analysis results in step S14, the specifications of the counterweight component 28 and the counterweight mounting plate 24 are determined in the shaft joint device 10 (10A), and the specifications of the support rigidity of the counterweight component 48 and the inner ring component 40 are determined in the shaft joint device 10 (10B) (step S16). Then, the shaft joint device 10 (10A, 10B) is assembled with the first shaft 100 as the drive shaft and the second shaft 102 as the driven shaft according to the specifications determined in step S16, and a trial run is performed.

[0056] During the trial operation phase, such as Figure 8 As shown, the torsional natural vibration frequency of the shaft system assembled with shaft joint assemblies 10 (10A, 10B), first shaft 100, and second shaft 102 is measured (measurement step S20). In evaluation step S22, the resonance state of the shaft system is evaluated based on the measurement results. That is, the torsional natural vibration frequency is estimated based on the data obtained during trial operation and with reference to the analytical results obtained during design. In the following adjustment step S24, the necessary change in the torsional natural vibration frequency to avoid resonance is determined based on the torsional natural vibration frequency estimated in evaluation step S22. Furthermore, the mass and number of counterweight components 28 and 48 are adjusted in a manner that corresponds to the determined necessary change. Moreover, in shaft joint assembly 10 (10A), the support rigidity of the counterweight mounting plate 24 is adjusted, and in shaft joint assembly 10 (10B), the support rigidity of the inner elastic body 46 is adjusted. As a result, the resonance phenomenon of the shaft system can be accurately avoided.

[0057] The contents described in the above embodiments can be understood, for example, as follows.

[0058] 1) One embodiment of the shaft connector device is a shaft connector device (10 (10A)) for connecting a first shaft (100) and a second shaft (102), comprising: a first inner ring member (12) mounted on the first shaft; a first outer ring member (14) disposed on the outer periphery of the first inner ring member; a first elastic member (16) connecting the first inner ring member and the first outer ring member; a second inner ring member (18) mounted on the second shaft; a second outer ring member (20) disposed on the outer periphery of the second inner ring member; a second elastic member (22) connecting the second inner ring member and the second outer ring member; a counterweight mounting plate (24) sandwiched between the first outer ring member and the second outer ring member, having a counterweight mounting portion (26) on the outer periphery of the first outer ring member and the second outer ring member for detaching and mounting a counterweight member (28).

[0059] With this structure, the first and second shaft sides are connected via a first and a second elastic member, and the counterweight mounting plate is also connected to the first and second shaft sides via the first and second elastic members. Therefore, vibrations generated in the shaft system are absorbed by the first and second elastic members, and the vibrations are attenuated and transmitted to the counterweight mounting plate. Thus, even if resonance occurs in the shaft system, excessive stress will not be generated, thereby suppressing damage to the shaft system. Furthermore, the counterweight mounting portion of the counterweight mounting plate is located on the outer periphery of the outer ring member, allowing for easy assembly and disassembly of the counterweight member without disassembling the shaft joint device, thereby facilitating adjustment of the torsional natural vibration frequency. Moreover, the counterweight member is positioned radially away from the axis of rotation of the shaft system, so even with a small mass, a large torque can be generated. This expands the adjustment range of the torsional natural vibration frequency of the shaft joint device.

[0060] 2) Another embodiment of the shaft joint device is based on the shaft joint device (10 (10A)) described in 1), wherein the counterweight mounting part includes a plurality of through holes (30) formed circumferentially at intervals on the outer periphery of the first outer ring component and the second outer ring component.

[0061] Based on this structure, the torsional natural vibration frequency of the shaft joint device can be adjusted by assembling and disassembling the counterweight components relative to the aforementioned multiple through holes, and the torsional natural vibration frequency can be finely adjusted by adjusting the mass and number of the counterweight components installed in the multiple through holes.

[0062] 3) In order to achieve the above objective, another embodiment of the shaft joint device is a shaft joint device (10 (10B)) for connecting a first shaft (100) and a second shaft (102), comprising: an inner ring member (40) mounted on the first shaft; an outer ring member (42) mounted on the second shaft and disposed on the outer periphery of the inner ring member; an elastic member (44) connecting the inner ring member and the outer ring member; an inner elastic body (46) mounted on the inner periphery of the inner ring member; and a counterweight member (48) detachably supported on the inner elastic body at a position closer to the inner periphery than the inner elastic body.

[0063] With this structure, the first and second shaft sides are connected via the aforementioned elastic member, and the counterweight member is also connected to the inner ring member via the aforementioned inner elastic body. Therefore, vibrations generated in the shaft system are absorbed by the elastic member and the inner elastic member, and the vibrations of the shaft system are attenuated and transmitted to the counterweight member. Thus, even if resonance occurs in the shaft system, excessive stress will not be generated, thereby suppressing damage to the shaft system. Furthermore, by changing the support stiffness of the inner elastic body, the adjustment range of the torsional natural vibration frequency can be expanded. Moreover, since the counterweight member is located on the inner circumference of the inner elastic body, it can be compacted, eliminating the need for installation space on the outer circumference of the shaft joint device.

[0064] 4) Another embodiment of the shaft connector device is based on the shaft connector device (10 (10B)) described in 3), wherein the inner elastic body (46) is composed of an annular component mounted on the inner circumferential surface of the inner ring component (40).

[0065] With this structure, the inner elastic body is composed of a ring-shaped component, making it easy to install onto the inner circumferential surface of the inner ring component and reducing the installation space required. Furthermore, the counterweight component consists of multiple counterweight components arranged along the circumference of the inner elastic body, which is a ring-shaped component, facilitating the installation of these multiple counterweight components. Therefore, it is easy to adjust the mass and number of each of the multiple counterweight components.

[0066] 5) Another method for adjusting the torsional natural vibration frequency is a method for adjusting the torsional natural vibration frequency of a shaft system including a first shaft (100), a second shaft (102) and the aforementioned shaft joint device (10 (10A, 10B)). The method includes: a measurement step (S20) for measuring the torsional natural vibration frequency of the shaft system; an evaluation step (S22) for evaluating the resonance state of the shaft system based on the measurement result of the torsional natural vibration frequency; and an adjustment step (S24) for adjusting the torsional natural vibration frequency of the shaft system by disassembling and assembling the counterweight components (28, 48) according to the evaluation result of the resonance state.

[0067] Based on this structure, the resonance state is evaluated based on the measurement results of the torsional natural vibration frequency of the shaft system, and the torsional natural vibration frequency of the shaft system is adjusted based on the evaluation results, thus reliably avoiding the resonance phenomenon of the shaft system.

[0068] Explanation of reference numerals in the attached figures

[0069] 10 (10A, 10B) Shaft joint device;

[0070] 12. First inner ring component;

[0071] 12a Main body;

[0072] 12a1 Flange portion;

[0073] 12b Bottom;

[0074] 14. First outer ring component;

[0075] 16. First elastic component;

[0076] 18. Second inner ring component;

[0077] 18a Main body;

[0078] 18a1 Flange portion;

[0079] 18b Bottom;

[0080] 20. Second outer ring component;

[0081] 21b Nut;

[0082] 22. Second elastic component;

[0083] 24. Counterweight mounting plate;

[0084] 26. Counterweight installation unit;

[0085] 28, 48 counterweight components;

[0086] 30 and 32 through holes;

[0087] Bolts 21a, 34, and 52;

[0088] 40 Inner ring component;

[0089] 40a Large diameter part;

[0090] 40a1 Flange portion;

[0091] 40b Small diameter section;

[0092] 40b1 Flange portion;

[0093] 42. Outer ring component;

[0094] 44. Elastic components;

[0095] 46. ​​Inner elastomer;

[0096] 50 connector plate;

[0097] 54. Threaded hole;

[0098] 100 First axis;

[0099] 102 Second Axis;

[0100] CA rotation axis.

Claims

1. A shaft connector device for connecting a first shaft and a second shaft, comprising: A first inner ring component is mounted on the first shaft; The first outer ring component is disposed on the outer periphery of the first inner ring component; A first elastic member connects the first inner ring member to the first outer ring member; The second inner ring component is mounted on the second shaft; The second outer ring component is disposed on the outer periphery of the second inner ring component; The second elastic member connects the second inner ring member to the second outer ring member; The counterweight mounting plate is formed in an annular shape when viewed from the axial direction of the first and second shafts, and extends radially outward from the center of the axial direction. It is sandwiched between the first outer ring component and the second outer ring component, and has a counterweight mounting part that allows for the assembly and disassembly of the counterweight components at a position radially outward compared to the position where the first and second outer ring components are fastened.

2. The shaft joint device according to claim 1, wherein, The counterweight mounting part includes a plurality of through holes formed circumferentially at intervals on the outer periphery of the first outer ring component and the second outer ring component.

3. A method for adjusting the torsional natural vibration frequency, comprising adjusting the torsional natural vibration frequency of a shaft system including a first shaft, a second shaft, and the shaft joint device as described in claim 1 or 2, comprising: The measurement procedure involves determining the torsional natural vibration frequency of the shaft system. The evaluation step evaluates the resonance state of the shaft system based on the measurement results of the torsional natural vibration frequency; The adjustment process involves disassembling and assembling the counterweight components based on the evaluation results of the resonance state, thereby adjusting the torsional natural vibration frequency of the shaft system.

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