WO2011025160A2 - Gear coupling using a bevel gear - Google Patents

Abstract

The present invention relates to a gear coupling using a bevel gear, and particularly, to a gear coupling for connecting and transmitting power between a first rotating shaft and a second rotating shaft through gear engagement, the gear coupling comprising: an internal hub having a cylindrical shape with one end coupled to the first rotating shaft, and an internal bevel gear formed at an angle in and along a circumference of the other end thereof; an external hub having a cylindrical shape with one end coupled to the second rotating shaft, and an external bevel gear formed angled outward around a circumference of the other end thereof and meshed with the internal bevel gear to form a backlash; a first pivot holder rotatably coupled inside the internal hub; and a second pivot holder rotatably coupled inside the external hub and coupled via a hinge to the first pivot holder, wherein power can be transmitted even when a shaft angle is formed between the first rotating shaft and the second rotating shaft, and power can be transmitted even with shaft lines which are offset when a pair of the gear couplings is used to form shaft angles, such that power density is superior to that of the prior art, and as locking does not occur, there is no bending moment and no deviation in velocity transfer, such that not only is vibration reduced, but the amount of tooth face slip is also minimal to thus extend the lifespan of gears, and as deposits are discharged from the tooth faces through centrifugal force, they do not become lodged between the teeth.

Description

Gear Coupling Using Bevel Gears

The present invention relates to a gear coupling, and more particularly, to a gear coupling using a bevel gear that can smoothly transmit power while absorbing shaft alignment errors using a spherical involute bevel gear.

The gear coupling is a device for transmitting power by connecting a shaft to a gear of an internal gear and an external gear, and a conventional gear coupling is shown in FIG. 1. 1 is a cross-sectional view showing a conventional gear coupling.

The gear coupling consists of a pinion in the form of an external gear and a sleeve in the form of an internal gear. The pinion 2 is fixed to one rotation shaft 1 and the sleeve 3 is fixed to the other rotation shaft 1. .

The pinion 2 is crowned on the tooth 2a and the teeth are based on involute.

Crowning is processing so that the center of the tooth becomes convex. The purpose of crowning the teeth 2a of the pinion 2 is to allow the pinion 2 to function as a gear coupling even when the position and the axial direction of the drive rotation shaft 1 and the driven rotation shaft 1 are shifted.

In detail, the sleeve 3 is filled with grease or lubricating oil as lubricant, and both ends of the sleeve 3 are coupled with a cover 4 which prevents the lubricant from scattering, and in the center of the sleeve 3 There is a center plate 5 which bisects the sleeve 3. In addition, the shaft nut 6 is fastened so as to prevent the pinion 2 from falling off the rotating shaft, and a shock absorbing material 7 is provided to prevent the shaft nut 6 from colliding with the center plate 5.

Therefore, even if the alignment of the two rotary shafts is misaligned, the external teeth 2a of the pinion 2 are crowned, so that not only smooth driving force can be transmitted but also the internal teeth 3a in the sleeve 3 are moved when both the rotary shafts move in the axial direction. Since the external teeth 2a of the pinion 2 move freely along a groove of the predetermined distance, there is no problem in driving force transmission.

The gear coupling is charged with backlash and crowning to absorb axial error and axial flow of the rotating shaft, and by installing it in duplicate, it absorbs not only axial error and axial flow but also axial parallel error. will be.

2 is a conceptual diagram illustrating three types of axial alignment errors that may occur in a coupling.

Axial angle error (a) means that both axes form a constant angle without forming 180 ° by any factor, and axial flow (b) means that both axes are approaching or moving away by some factor, and parallel error ( c) refers to a phenomenon in which both axes are not positioned in a straight line but are shifted in parallel with each other.

In reality, all three types of errors are combined in three dimensions, so the gear coupling must absorb all the errors and transmit power accurately.

Gear coupling has the advantage of very high power density and no bending moment, while the friction is severe and the wear of the teeth is disadvantageous. In addition, the locking phenomenon may occur under excessive operating conditions, speed transmission error occurs, and the debris is collected in the circumferential direction by centrifugal force, causing frequent problems on the tooth surface.

Another type of flexible coupling is a diaphragm, a laminated disk, a coil spring, a rubber or an elastomer of a resin, etc., which is a shaft joint formed by connecting a flexible elastic medium between two axes to be connected.

Flexible couplings do not require lubrication, are simple in structure, are effective for isolating high frequency rotational vibrations, but have a short fatigue life, especially corrosion or damage to joints. In addition, additional vibration such as resonance may occur, and the power density is low, so that the effective diameter is larger than the gear coupling and there is a problem that a bending moment occurs.

The present invention has been made to solve the disadvantages while utilizing the advantages of the gear coupling as described above is an object of the present invention by using a spherical involute bevel gear bevel gear that can overcome the axial error, axial flow and parallel error It is to provide a gear coupling using.

The present invention for achieving the above object in the gear coupling for transmitting power by connecting the first rotary shaft and the second rotary shaft by the meshing of the gear, made of a cylindrical shape, one side is coupled to the first rotation shaft, the other side An internal hub having an internal bevel gear inclined inward along a circumference; And an external hub having a cylindrical shape, one side of which is coupled to the second rotating shaft, and the external bevel gear is inclined outward along the other circumference to form an internal bevel gear and backlash. It is characterized in that the power can be transmitted even in a state in which the second rotating shaft forms the shaft angle.

Here, a first pivot holder rotatably coupled by a first thrust bearing inside the internal hub and a second pivotally rotatably coupled by a second thrust bearing inside the external hub and hinged to the first pivot holder. It is characterized in that the pivot holder is further provided.

In addition, a lubricant is filled in the internal hub and the external hub, and one side of each of the first thrust bearing and the second thrust bearing is combined with a first packing disc and a second packing disc to seal the lubricant, and the internal hub and The outer circumferential surface of the external hub is characterized in that the case for sealing the lubricant is coupled.

In addition, a cylindrical spline spacer having a spline groove in the circumferential direction is further interposed between the circumferential hub having a spline formed at one outer circumference and the second rotary shaft to guide the axial flow of the first and second rotary shafts. It is characterized by.

Preferably, the pitch cone angle formed by the internal hub and the external hub is characterized in that 70 ° ~ 80 °.

Meanwhile, the pair of gear couplings using the bevel gears are disposed to face each other, and a pair of spline spacers having a cylindrical shape having spline grooves formed on an inner circumferential surface and into which the first and second splines are respectively inserted. By connecting the bevel gear coupling, it is characterized in that the first rotation shaft and the second rotation shaft to form an axial angle while transmitting power even when the axis line is shifted.

The effect of the present invention by the configuration as described above is due to the excellent surface pressure strength, the power density is superior to the conventional general gear coupling and there is no locking phenomenon does not occur because of the locking phenomenon.

In addition, since the amount of sliding of the tooth surface is reduced, the wear life is reduced, and the gear life is long, and when the residue of lubricant is hit by the centrifugal force during rotation, it escapes to the outside.

In addition, the allowable axial error is proportional to the amount of backlash, but even if the backlash is given a typical amount of backlash of 0.05m, as shown in one embodiment, a considerable performance is obtained (at least 0.05m). If the maximum amount of backlash is identified, there is a significant increase in the allowable axial error.

And since there is no speed transmission error, no additional vibration occurs.

1 is a cross-sectional view showing the structure of a conventional general gear coupling.

2 is a conceptual diagram illustrating three types of axis alignment errors that may occur in a coupling.

Figure 3 is an internal cut perspective view showing the internal structure of the gear coupling using a bevel gear according to an embodiment of the present invention.

4 is a perspective view of the internal hub and the first pivot holder of the present invention shown in FIG.

Figure 5 is a perspective view showing the bite state of the internal bevel gear and the external bevel gear according to the axial error. (a) shows no axial error, and (b) shows axial error.

6 is a conceptual diagram showing a state in which the axial angle error is overcome by the present invention.

Figure 7 is an internal cutaway perspective view showing the internal structure of the gear coupling using a bevel gear according to another embodiment of the present invention

8 is a conceptual diagram illustrating that the axial angle error and parallel error is overcome according to another embodiment of the present invention.

<< Explanation of main parts of drawing >>

110: internal hub 112: internal bevel gear

120: external hub 122: external bevel gear

124: spline 130: the first pivot holder

132: first thrust bearing 140: second pivot holder

142: second thrust bearing 150: first packing disc

160: second packing disk 170: case

180: spline spacer 182: spline groove

p: pin h: hole

θ: pitch cone angle

210: first internal hub 212: first internal bevel gear

220: first external hub 222: first external bevel gear

230: first pivot holder 240: second pivot holder

310: second internal hub 312: second internal bevel gear

320: second external hub 322: second external bevel gear

330: third pivot holder 340: fourth pivot holder

400: spline spacer 410: spline groove

Hereinafter, with reference to the accompanying drawings will be described in detail a preferred embodiment of the present invention. The following description and the accompanying drawings are presented for the overall understanding of the present invention, and thus the technical scope of the present invention is not limited thereto. And a detailed description of known configurations and functions that may unnecessarily obscure the subject matter of the present invention will be omitted.

The present invention has a basic configuration of the internal hub 110, the external hub 120, the first pivot holder 130, the second pivot holder 140, the internal hub 110 and the external hub 120 is a spherical inball Rotate (Spherical involute) bevel gears to form a rotation, and the internal pivot 110 and the external hub 120 inside the first pivot holder 130 and the second pivot holder 140 are hinged to each other and internally installed The hub 110 and the external hub 120 are rotated while maintaining a state in which they are engaged with each other so that the rotational force can be transmitted at a transmission ratio of 1: 1.

Spherical involute bevel gears are a form of known bevel gears in which the complete spherical involute surface of the bevel gear corresponds to the surface of the trajectory on which one edge of the plane is drawn as the unstretched film wound around the side of the foundation cone.

The kinematic characteristics of the spherical involute bevel gears can be found in Korean Society of Precision Engineering Vol. 12, No. 5 (1995.5), "Kinematics and Shape Modeling of Involute Bevel Gear Pairs" (Park No-Gil), Korean Society of Precision Engineering, Vol. 17, No. 2 (2000.2) "Experimental Study on Spherical Involute Bevel Gears" (Dong-Hyun Jung, Hyung-Woo Lee, Park No-Gil).

<Example 1>

First, the internal hub 110 will be described with reference to FIGS. 3 and 2. Figure 3 is an internal cutaway perspective view showing the internal structure of the gear coupling using a bevel gear according to an embodiment of the present invention, Figure 4 is a perspective view showing the internal hub and the first pivot holder of the present invention shown in FIG. .

The internal hub 110 is formed in a generally cylindrical shape, one side is connected to the first rotating shaft, and the other side is an internal bevel gear 112 having a sawtooth shape along the circumference as shown in FIG.

The internal bevel gear 112 is formed to be inclined at a predetermined angle inwardly, and the teeth are involute teeth and do not require crowning in the dental direction as in the conventional gear coupling.

Next, the external hub 120 will also be described with reference to FIG. 3.

The external hub 120 also has a generally cylindrical shape so as to correspond to the internal hub 110, one side is connected to the second rotating shaft, and the other external bevel gear 122 having a sawtooth shape is formed along the circumference.

The external bevel gear 122 is formed to be inclined at an angle to the outside and the tooth is an involute tooth and the tooth surface does not require a separate crowning process.

The external bevel gear 122 meshes with the internal bevel gear 112, and forms a backlash so that the external bevel gear 122 is engaged with the internal bevel gear 112. A pitch cone angle θ formed by the external hub 120 and the internal hub 110 is achieved. It is preferable that the teeth are joined to form about 70 ° to 80 °.

Backlash refers to a gap between the gear teeth that are originally engaged to facilitate gear rotation. In the present invention, such a backlash is imposed in a certain amount to sufficiently absorb the axial error of both shafts.

Here, the number of teeth of the internal bevel gear 112 and the external bevel gear 122 is the same.

5 is a perspective view illustrating a bite state of an internal bevel gear and an external bevel gear according to an axial error. (a) is when there is no axial error, and (b) is when there is an axial error.

As shown, when there is no axial error, the internal bevel gear 112 and the external bevel gear 122 are in contact with all gears simultaneously on the pitch circle.

However, in the state of axial error, the internal / external bevel gears maintain the gear contact toward the pitch line and the teeth of the gears are separated from each other. That is, while the internal bevel gear 112 and the external bevel gear 122 are in close contact with each other in A, it is possible to see a state separated from each other in the B position. However, the bite of the mutual gears is good and the rotational force transmission proceeds smoothly.

Tooth contact of the existing gear coupling is a point contact due to the crowning process and there is a weakness caused by excessive sliding between the tooth surface, whereas the present invention is because there is no separate crowning process, the line contact and the sliding between the tooth surface is very small. The life due to wear is considerably longer. This also results in an increase in the amount of torque that can be transmitted. That is, higher power density can be obtained than before.

In addition, the spherical involute tooth has a merit that a 1: 1 speed ratio can be maintained even if the shaft angle is changed. Therefore, a transmission error does not occur even when the shaft angle is generated, so that a quiet operation can be performed without additional vibration.

In addition, in the present invention, the backlash serves as a passage for discharging the sludge or debris included in the lubricant even though it is a means for overcoming the axial error. In the case of the existing gear coupling, the residue (lubrication) during lubrication gathers at the teeth of the sleeve teeth and the teeth of the pinion by the centrifugal force, causing the gear contact to be caught in the tooth contact portion. As the teeth are radially directed, the debris is discharged to the outside through the backlash, so that the teeth are removed from the tooth surface. So the tooth surface is always clean, which greatly improves the fitting and scoping strength.

On the other hand, the present invention can increase the limit of acceptable axial error without great limitation.

The allowable axial error of the existing gear coupling is determined by the tooth width and the amount of crowns in the dental direction. Therefore, in order to increase the allowable axial error, the width of the tooth should be reduced and the crown amount should be larger. Therefore, the existing gear coupling has a limit in the range of the maximum shaft angle error.

In the case of the present invention, the allowable axial error is determined by the amount of backlash. The relation between the backlash amount B and the allowable axial error ΔΣ is as follows.

Where Z is the number of gear teeth,

Is the basic cone angle of the gear and m is the gear module.

The amount of backlash is generally given about 0.05 times of the module in order to facilitate the assembly of the gear in consideration of the assembly error. This size is an empirical amount enough to prevent the problem of collision between the back side of teeth when reverse torque occurs while making assembly smooth. Therefore, it is reasonable to view the backlash amount at the level of 0.05m which can prevent the tooth collision due to the reverse torque. Substituting the usual amount of backlash into equation (1)

Since the preferred embodiment (Z = 21,

= 60 °), the allowable axis angle error ΔΣ is up to 0.6 °.

Since the size is almost the same as the allowable axial error (0.5 ° ~ 1.0 °) of the conventional gear coupling, it is considered that the allowable axial error of the conventional coupling can be sufficiently absorbed without a separate backlash amount. Therefore, even if a normal amount of backlash (0.05m) is imposed, not only the assembly is performed smoothly but also the allowable shaft angle error is possible up to 0.6 °.

It depends on how much the limit backlash that the collision due to reverse torque is larger than 0.05m, but the present invention can give the maximum backlash up to the limit backlash amount, it is self-evident that the allowable amount of the axial error increases Do. Therefore, it is obvious that the present invention is much more free to increase the allowable shaft angle error compared to the conventional gear coupling. Therefore, the amount of backlash can be increased in the range in which the bending strength that does not collide with the teeth is allowed.

For reference, the portion where the internal hub 110 and the external hub 120 are engaged is sealed by a case to be described later, and the portion of the external hub 120 is formed to have a relatively small diameter as shown in the external hub. The outer surface from the bevel gear 112 to the external bevel gear 122 forms a curved surface.

Next, the first pivot holder 130 and the second pivot holder 140 will be described together with reference to FIGS. 3 and 4.

As shown in the drawing, the first and second pivot holders are rotatably coupled and hinged to each other in the internal and external hubs, respectively.

Since the structures are the same as each other, the first pivot holder 130 will be mainly described. As shown, one side of the cylindrical shape is inserted into and coupled to the internal hub 110, and is rotatable and supported in the axial direction (thrust). It is coupled to the internal hub 110 by a first thrust bearing 132 to be supported). Thrust bearings are bearings that support the action of the load in the axial direction, and ball, collar, and footstep bearings may be used.

The other side of the first pivot holder 130 is disposed to face the center of the external hub 120, and a hole h at which the pin p can be inserted is formed at an end thereof.

Similarly, the second pivot holder 140 is also inserted into the external hub 120 and is coupled by the second thrust bearing 142, and a hole h is formed at the other end of the first pivot holder 130. It is arranged in communication with the hole (h) and is hinged to each other by being fixed by the pin (p).

In this structure, the first and second pivot holders 140 are coupled to face each other as the internal and external hubs 120 face each other to maintain the internal and external hubs 120 engaged. At the same time, it supports the reaction force (thrust) generated in the axial direction during torque transmission.

The first and second pivot holders 140 are hinged to each other when an axial angle occurs in the internal and external hubs 120 so that the first and second thrust bearings can actively absorb and simultaneously absorb the first and second thrust bearings. Rotationally coupled by 142 does not interfere with the rotational forces of both axes.

Preferably, a lubricant is filled in the inner space formed by the internal hub 110 and the external hub 120. The lubricant lubricates the engagement of the internal bevel gear 112 and the external bevel gear 122 and the hinge coupling of the first and second pivot holders 140 and the action of the first and second thrust bearings 142.

In order to seal the lubricant, the first thrust bearing 132 and the second thrust bearing 142 are respectively connected to the first packing disc 150 and the second packing disc 160 having a disc shape, and the internal hub Cylindrical case 170 is coupled to the outer circumferential surface of the portion where the 110 and the external hub 120 are engaged to seal the lubricant discharged through the backlash formed by the internal bevel gear 112 and the external bevel gear 122. do. Of course, the first and second packing discs 160 and the case 170 should be sealed by using an o-ring or the like.

The case 170 is coupled to the outer circumferential surface of the portion where the internal hub 110 and the external hub 120 is meshed with a slight distance, and it is preferable to form a curved surface as mentioned above, which is both shaft angle When the case 170 is curved, a portion where the internal hub 110 and the external hub 120 engage with each other is formed as a curved surface, such as a joint or a universal joint in the case 170. Be able to act.

6 is a conceptual diagram illustrating a state in which an axial error is overcome by the present invention.

It is to be noted that the actual axial error occurs as a three-dimensional behavior or a two-dimensional behavior for understanding. The dotted line shows the state before the axial error occurs and the solid line shows the state where the axial error occurs.

Since the backlash is formed between the internal hub 110 and the external hub 120, the opposite side of the internal bevel gear 112 and the external bevel gear 122 is in close contact with one side of the internal bevel gear 112 and the external bevel gear 122. 6 is spaced apart from each other, and the first pivot holder 130 and the second pivot holder 140 are also bent at a predetermined angle with respect to the pin p so that both rotation shafts form an axial angle.

In the present invention, the spline spacer 180 may be further interposed between the external hub 120 and the second rotary shaft.

The spline spacer 180 is capable of guiding and absorbing the axial flow of the shaft. The spline spacer 180 has a cylindrical shape and a spline groove 182 is formed along the axial direction on an inner circumferential surface thereof.

Splines 124 having a shape in which a plurality of keys are formed are formed at one outer circumference of the external hub 120 so as to correspond to the spline grooves 182.

Therefore, the second rotation shaft is fixed or spline-coupled to one side of the spline spacer 180 and at the same time the spline 124 of the external hub 120 is inserted into the other side of the spline spacer 180 to be fixed in the axial direction. By slidably moving in the axial direction while sliding the distance, the error is absorbed when the first and second rotation shafts flow in the axial direction.

Hereinafter, another embodiment of the present invention will be described.

<Example 2>

This is a double gear coupling using a bevel gear in which a pair of bevel gear gear couplings described in Embodiment 1 is coupled by a connecting member such as the spline spacer. 7 is an internal cutaway perspective view showing the internal structure of the gear coupling using a bevel gear according to another embodiment of the present invention.

The present invention is a gear coupling using one bevel gear consisting of a first internal hub 210, a first external hub 220, a first pivot holder 230, a second pivot holder 240, and Gear coupling using another bevel gear consisting of a second internal hub 310, a second external hub 320, a third pivot holder 330, a fourth pivot holder 340 to the spline spacer 400 The first rotary shaft and the second rotary shaft which are coupled to face each other to be connected to each other are connected to each other to form a shaft angle, and at the same time, the power can be smoothly transmitted even when the axis is shifted. That is, the axial error and parallel error are overcome simultaneously.

The first internal hub 210, the first external hub 220, the second internal hub 310, and the second external hub 320 are the internal hub 110 and the external contact described above in the first embodiment. Since the hub 120 and its configuration are substantially the same, detailed description thereof will be omitted.

In addition, the first pivot holder 130, the second pivot holder 240, the third pivot holder 330, and the fourth pivot holder 340 also have the first pivot holder 130 and the second pivot. The holder 140 and its configuration are large and similar.

In addition, the spline spacer 400 also has a cylindrical shape with a spline groove 410 formed on an inner circumferential surface thereof, and thus has the same configuration as described above.

However, since two bevel gears are used as described above, parallel errors that cannot be absorbed in the previous embodiment can be absorbed. In other words, if the spherical involute bevel gear of the present invention is used in duplicate, the rotational force can be smoothly transmitted while overcoming all three axial errors, axial flows, and parallel errors.

8 is a conceptual diagram illustrating that the axial angle error and parallel error is overcome according to another embodiment of the present invention.

It is to be noted that the actual axial and parallel errors are depicted as two-dimensional behavior for the sake of three-dimensional behavior or understanding. The dotted line indicates the state before the axial error and the parallel error occurs, and the solid line indicates the state where the axial error and the parallel error have occurred.

Also, if the lower part of the part where the first internal bevel gear 212 and the first external bevel gear 222 are engaged by the backlash is in close contact with each other, the upper parts are spaced apart from each other and the first pivot holder (p) 230 and the second pivot holder 240 are also bent at a predetermined angle, and at the same time, when the upper portions of the parts where the first internal bevel gear 312 and the second external bevel gear 322 are in close contact with each other are spaced apart from each other, As the third pivot holder 330 and the fourth pivot holder 340 are bent at the same angle around the pin p, both rotation shafts form an axial angle and smoothly transmit power even when the axis is out of alignment. It can be.

For reference, in the present invention, a three-dimensional area where the axis alignment heat error (axial error, parallel error, and axial flow) can be completely absorbed can be obtained. The allowable axial error when using one gear coupling (ΔΣ ₀ ) And the allowable axial flow rate (ΔZ ₀ ). 9 shows the distance a = 70 mm between the first axis of pivot pivot (p position in FIG. 8) and the center of the first axis of rotation for a slightly exaggerated allowable axis alignment error ΔΣ ₀ = 10 ° and the allowable axis flow of ΔZ ₀ = 21 mm. Relative displacement of the center of the first axis of rotation relative to the standard distance L _S = 140 mm

Indicates the range of. The axial angle error ΔΣ _t and the parallel error ΔE between the first rotational axis and the second rotational axis with respect to the axial alignment error occurring in this area are calculated as follows.

Axial error

,

Parallel error

here,

: Relative displacement of the center of the first axis of rotation with respect to the displacement of the center of the second axis of rotation,

= Direction vector of the first axis of rotation,

= Direction vector of the second axis of rotation,

Is the shortest normal vector between the first and second axes of rotation.

In addition, the plurality of points shown in FIG. 9 are locations simulating a meaningful region of the center of the first rotating shaft capable of completely absorbing the axis alignment heat error.

The present invention can be used for gear coupling, and more specifically, it can be used for gear coupling using bevel gears that can smoothly transmit power while absorbing shaft alignment errors using spherical involute bevel gears.

Claims (6)

1. In the gear coupling which transmits power by connecting the 1st rotation shaft and the 2nd rotation shaft by meshing of gears,

   An internal hub 110 having a cylindrical shape, one side of which is coupled to the first rotating shaft, and the internal bevel gear 112 inclined inward along the other circumference; And

   An external hub 120 having a cylindrical shape, one side of which is coupled to the second rotating shaft, and the external bevel gear 122 is inclined outward along the other circumference to form an internal bevel gear 112 and backlash. Consisting of,

   Gear coupling using a bevel gear, characterized in that the first rotation shaft and the second rotation shaft can transmit power even in the form of the shaft angle.
2. The method of claim 1,

   The first pivot holder 130 is rotatably coupled by the first thrust bearing inside the internal hub 110 and the first pivot is rotatably coupled by the second thrust bearing inside the external hub 120. Gear coupling using a bevel gear, characterized in that the second pivot holder 140 which is hinged to the holder 130 is further provided.
3. The method of claim 1,

   Lubricant is filled in the internal hub 110 and the external hub 120,

   One side of each of the first thrust bearing 132 and the second thrust bearing 142 is coupled to the first packing disc 150 and the second packing disc 160 to seal the lubricant,

   Gear coupling using a bevel gear, characterized in that the case 170 for sealing the lubricant is coupled to the outer circumferential surface of the internal hub 110 and the external hub 120.
4. The method of claim 1,

   Between the external hub 120 and the second rotary shaft formed with the spline 124 on one side circumference, a cylindrical spline spacer 180 having a spline groove 182 formed on the inner circumferential surface is further interposed.

   Gear coupling using a bevel gear, characterized in that can guide the axial flow of the first rotary shaft and the second rotary shaft.
5. The method according to any one of claims 1 to 4,

   Gear coupling using the bevel gear, characterized in that the pitch cone angle formed by the internal hub 110 and the external hub 120 is 70 ° ~ 80 °.
6. A pair of gear couplings using the bevel gear of any one of claims 1 to 3 are disposed to face each other, the spline groove 410 is formed on the inner circumferential surface and the first spline 224 and the second side By connecting the pair of bevel gear coupling to the spline spacer 400 is inserted two splines 324, respectively,

   A gear coupling using a bevel gear, characterized in that the first rotating shaft and the second rotating shaft form an axial angle, and thus power can be transmitted even when the axis line is shifted.

Images