JP2006316951A - Power transmission of compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent the fretting wear at a connecting part of each rotor while securing the smooth setting of the first rotor with the second rotor in a power transmission of a compressor having the first and the second rotor that notifies the rotational power each other and inserts the second rotor into the hole which is formed in the first rotor and engaged mutually. <P>SOLUTION: In the constitution having a plurality of inner teeth 13 on the inner peripheral face of the hole 12 formed in a hub 3 which composes the first rotor and engages the hub 3 with a shaft 10 each other by forming a plurality of outer teeth 14 to gear with the inner teeth 13 the outer peripheral face of the shaft 10 which composes the second rotor, a gap is formed between the inner teeth 13 and the outer teeth 14 on the position where the inner teeth 13 and the outer teeth 14 are starting to fit by moving the hub 3 and the shaft 10 relatively toward the shaft of the hole 12 and the tooth surface of the inner teeth 13 and that of the outer teeth 14 are pressure welded on the other part than the fitting start part. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention is used in a compressor and is connected to each other to transmit rotational power, for example, a driving side rotating body that rotates by receiving rotational power from a driving source such as an engine, and the driving side rotating body It is related with the power transmission device of the compressor provided with the shaft inserted in the inside of the hole formed in this, and a rotational power is transmitted from a drive side rotary body.

  For example, in an in-vehicle compressor that uses an engine as a power source, the driving side rotating body that rotates by receiving rotational power from the power source, and the driving side inserted into a hole formed in the driving side rotating body A power transmission device including a shaft to which rotation of the rotating body is transmitted is provided. Generally, a plurality of internal teeth are formed on the inner peripheral surface of the hole of the driving side rotating body, and the outer peripheral surface of the shaft is formed. An involute spline fitting structure in which a plurality of external teeth meshing with the internal teeth is formed is employed.

  In such a fitting structure, the driving-side rotating body and the shaft are relatively moved in the axial direction so that the inner teeth and the outer teeth are fitted together. A predetermined clearance is set between and.

  For this reason, when excessive torque fluctuations are input from the power source, the presence of this clearance causes minute vibrations on the drive-side rotating body and shaft, resulting in fretting wear on the contact surfaces between the inner teeth and the outer teeth. When this occurs and this state proceeds, the spline fitting function is lost and power cannot be transmitted.

For this reason, in the prior art, as shown in Patent Document 1 described below, the first press-fit portion in which the wave front surface of any of the plurality of external teeth and the tooth bottom surface of the internal teeth are brought into contact with each other and plastically deformed with each other. And the structure etc. which provide the 2nd press-fit part which contact | abutted the tooth surface of external teeth other than the external tooth in which a 1st press-fit part is formed, and the tooth surface of an internal tooth, and mutually plastically deformed are considered.
JP 11-108070 A

  However, since the drive side rotor and the shaft are relatively moved in the axial direction as described above to fit the inner teeth and the outer teeth, in the conventional configuration in which the contact surface between the inner teeth and the outer teeth is plastically deformed, The shaft cannot be smoothly inserted into the hole of the driving-side rotating body, resulting in inconvenience such as troublesome assembly work.

  Therefore, in the present invention, the first and second rotating bodies that transmit the rotational power to each other are provided, and the second rotating body is inserted into a hole formed in the first rotating body and connected to each other. In the power transmission device of the compressor, the main problem is to prevent fretting wear at the connecting portions of the respective rotating bodies while ensuring smooth assembly of the first rotating body and the second rotating body. It is said.

  In order to achieve the above object, a power transmission device for a compressor according to the present invention includes first and second rotating bodies through which rotational power is transmitted to each other, and a hole formed in the first rotating body. The second rotating body is inserted into the inner surface, a plurality of inner teeth are formed on the inner peripheral surface of the hole, and a plurality of outer teeth are formed on the outer peripheral surface of the second rotating body. Thus, in the configuration in which the first and second rotating bodies are connected to each other, the first rotating body and the second rotating body are relatively moved in the axial direction of the hole to thereby form the internal teeth. A gap is formed between the inner teeth and the outer teeth at the portion where the outer teeth start to fit in the axial direction, and the tooth surfaces of the inner teeth and the outer portions at portions other than the portion where the fitting begins. The tooth surface of the tooth is brought into pressure contact (Claim 1).

  Therefore, the first rotating body and the second rotating body are moved relative to each other in the axial direction of the hole so that the inner teeth of the first rotating body and the outer teeth of the second rotating body start to be fitted at the inner part. Since a gap is formed between the teeth and the outer teeth, the second rotating body can be smoothly inserted into the hole of the first rotating body, and the inner teeth and the outer teeth are fitted. Because the tooth surface of the internal tooth and the tooth surface of the external tooth are pressed against each other in the part other than the start part, no clearance is formed between the internal tooth and the external tooth. It is possible to eliminate the minute vibration of each rotating body.

  A power transmission device for a compressor according to the present invention includes first and second rotating bodies that transmit rotational power to each other, and the second rotation is formed in a hole formed in the first rotating body. Inserting a body, forming a plurality of internal teeth on the inner peripheral surface of the hole, forming a plurality of external teeth meshing with the inner teeth on the outer peripheral surface of the second rotating body, and the first In the configuration in which the first and second rotating bodies are connected to each other by fastening the rotating body and the second rotating body in the axial direction with a center bolt, a slit is provided on the rotating shaft, The diameter of the base end of the center bolt is larger than that of the front end, and the portion of the second rotating body inserted into the hole by the base end of the center bolt screwed into the second rotating body May be enlarged in the radial direction (claim 2).

  In such a configuration, if the second rotating body is inserted into the hole formed in the first rotating body and then fastened with the center bolt, the shaft diameter is enlarged by the base end of the center bolt. Since the outer surface of the second rotating body can be brought into pressure contact with the inner surface of the hole of the first rotating body, it is ensured that the second rotating body is smoothly inserted into the hole of the first rotating body. It is possible to eliminate the clearance between the inner teeth and the outer teeth, and it is possible to eliminate the minute vibrations of the respective rotating bodies due to the presence of the clearance.

  A power transmission device for a compressor according to the present invention includes first and second rotating bodies that transmit rotational power to each other, and the second rotation is formed in a hole formed in the first rotating body. In the configuration in which the first and second rotating bodies are connected to each other by inserting a body and fastening the first rotating body and the second rotating body in the axial direction with a center bolt, The hole has a polygonal cross section, the cross section of the second rotating body is a polygonal shape that matches the cross sectional shape of the hole, a slit is provided in the second rotating body, and the base end of the center bolt The diameter of the second rotating body is made larger than the tip end portion, and the portion of the second rotating body inserted into the hole is expanded in the radial direction by the base end portion of the center bolt screwed to the rotating shaft. (Claim 3).

  In such a configuration, since the hole formed in the first rotating body and the cross section of the second rotating body have corresponding polygonal shapes, and the second rotating body is provided with a slit, the first If the second rotating body is inserted into the hole formed in the rotating body and fastened with the center bolt, the diameter of the second rotating body is enlarged at the base end of the center bolt, and the first rotating body Since the outer surface of the second rotating body can be pressed against the inner surface of the hole, the second rotating body can be smoothly inserted into the hole of the first rotating body, It is possible to eliminate the clearance with the outer surface of the second rotating body, and it is possible to eliminate the minute vibration of each rotating body due to the presence of the clearance.

  In the above-described configuration, the portion of the second rotating body disposed inside the hole may be formed in a tapered shape that gradually increases in diameter from the insertion side into the hole.

  A power transmission device for a compressor according to the present invention includes first and second rotating bodies that transmit rotational power to each other, and the second rotation is formed in a hole formed in the first rotating body. In the configuration in which a body is inserted and the first and second rotating bodies are connected to each other, a square spline comprising a plurality of convex portions and concave portions is formed on the inner peripheral surface of the hole, and the second You may make it form the square-shaped spline axis | shaft which consists of a convex part and concave part which fit with the said square-shaped spline in the outer peripheral part inserted in the said hole of a rotary body (Claim 5).

  In such a configuration, since the shape is simpler than that of the involute spline, dimensional management is easy, and the second rotating body can be easily inserted into the hole of the first rotating body. For this reason, it becomes possible to eliminate the clearance between the inner surface of the hole and the outer surface of the second rotating body while ensuring smooth insertion of the second rotating body into the hole of the first rotating body. It is possible to eliminate the minute vibrations of the respective rotating bodies due to the presence of the.

  A power transmission device for a compressor according to the present invention includes first and second rotating bodies that transmit rotational power to each other, and the second rotation is formed in a hole formed in the first rotating body. The first and second teeth are inserted by forming a plurality of internal teeth on the inner peripheral surface of the hole and forming a plurality of external teeth meshing with the inner teeth on the outer peripheral surface of the second rotating body. In the configuration in which the two rotating bodies are connected to each other, at least one of the inner teeth and the outer teeth may be formed with a predetermined lead angle with respect to the axial center of the hole (claim). Item 6).

  In such a configuration, when the first rotating body and the second rotating body are relatively moved in the axial direction of the hole and the inner teeth and the outer teeth are engaged with each other, the relative movement is further performed in the axial direction of the hole. Since at least one of the inner tooth and the outer tooth is formed with a predetermined lead angle with respect to the axial center of the hole, the tooth surface of the inner tooth and the tooth surface of the outer tooth are gradually brought into pressure contact with each other. It becomes. For this reason, it becomes possible to eliminate the clearance between the inner surface of the hole and the outer surface of the second rotating body while ensuring smooth insertion of the second rotating body into the hole of the first rotating body. It is possible to eliminate the minute vibrations of the respective rotating bodies due to the presence of the.

  A power transmission device for a compressor according to the present invention includes first and second rotating bodies that transmit rotational power to each other, and the second rotation is formed in a hole formed in the first rotating body. The first and second teeth are inserted by forming a plurality of internal teeth on the inner peripheral surface of the hole and forming a plurality of external teeth meshing with the inner teeth on the outer peripheral surface of the second rotating body. In the configuration in which the two rotating bodies are connected to each other, the first rotating body and the second rotating body are relatively moved in the axial direction of the hole so that the inner teeth and the outer teeth are fitted. At least one of the inner teeth and the outer teeth is cut out at a portion where the inner teeth and the outer teeth begin to be pressed, and the inner teeth, at least one tooth tip surface and the other tooth bottom surface of the inner teeth are pressed against the portions other than the portion where the fitting starts. (Claim 7).

  In such a configuration, the first rotating body and the second rotating body are relatively moved in the axial direction of the hole so that the inner teeth of the first rotating body and the outer teeth of the second rotating body are fitted. Since at least one of the internal teeth and the external teeth is notched at the beginning of the opening and a gap is formed between the internal teeth and the external teeth, the second rotary body can be smoothly inserted into the hole of the first rotary body. It is possible to insert the inner teeth and the outer teeth, and at least one tooth tip surface of the inner teeth and the outer teeth and the other tooth bottom surface are pressed against each other at a portion other than the portion where the inner teeth and the outer teeth start to be fitted. Clearance is no longer formed between the outer teeth and the outer teeth, and it is possible to eliminate minute vibrations of the respective rotating bodies due to the presence of the clearance.

  As described above, according to the present invention, in the power transmission device in which the second rotating body is inserted into the hole formed in the first rotating body to transmit the rotational power to each other. A smooth assembly between the first rotating body and the second rotating body can be ensured to facilitate the assembling work, and fretting wear at the connecting portions of the respective rotating bodies can be prevented. It becomes possible.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS The best embodiment of the present invention will be described below with reference to the accompanying drawings.

  In FIG. 1, a power transmission device for a clutchless compressor is shown as an example of a power transmission device for a compressor. The power transmission device 1 includes a pulley 2, a hub 3, a damper inner ring 4, a damper outer ring 5, and a damper rubber 6.

  The pulley 2 is rotatably fitted to a boss portion 7a projecting from a housing 7 of the compressor via a radial bearing 8, and a groove (V groove) for attaching a drive belt (V belt) (not shown) to the outer peripheral surface. ) 9 is formed, and is rotated about the shaft 10 as a rotation center by a driving force from a power source such as an engine connected via a driving belt.

  The front end portion of the shaft 10 protrudes from the housing 7, and the hub 3 is fixed to the front end portion by a center bolt 11 in the axial direction. More specifically, the hub 3 is formed in a cylindrical shape with a hole 12 formed in the center thereof, and a plurality of internal teeth 13 are formed on the inner peripheral surface of the hole 12, and the shaft 10 A plurality of external teeth 14 that mesh with the internal teeth 13 are formed on the outer peripheral surface of the tip, and the internal teeth 13 and the external teeth 14 are engaged with each other via a stopper 15 that is engaged in the hole of the hub 3. Thus, the hub 3 is fixed to the front end portion of the shaft 10 in the axial direction by screwing the center bolt 11 into a female screw 16 formed at the front end portion of the shaft 10. The hub 3 constitutes a first rotating body, and the shaft 10 constitutes a second rotating body.

  A hub inner ring 4 is integrally formed on the outer surface of the hub 3. The damper inner ring 4 includes a flange portion 4a extending outward in the radial direction and a cylindrical portion 4b formed integrally with the flange portion 4a and extending to the front side.

A damper outer ring 5 is held on the cylindrical portion 4 b of the damper inner ring 4 via a damper rubber 6. The damper outer ring 5 is formed to have a larger diameter than the cylindrical portion 4b of the damper inner ring 4, and is formed integrally with the cylindrical portion 5b and the cylindrical portion 5b for holding the damper rubber 6 between the cylindrical portion 4b. And a flange portion 5a extending outward in the direction.
The flange portion 5 a of the damper outer ring 5 is fixed to the pulley 2 by a joining means such as a bolt 16.

  Therefore, when the rotational power from the power source is transmitted to the pulley 2 through the drive belt, it is transmitted to the shaft 10 through the damper outer ring 5, the damper rubber 6, the damper inner ring 4, and the hub 3. It has become.

  By the way, the fitting state of the hub 3 and the shaft 10 is such that the internal teeth 13 and the external teeth 14 are axially moved by relatively moving the hub 3 and the shaft 10 in the axial direction of the hole 12 formed in the hub 3. However, in the portion where the inner teeth 13 and the outer teeth 14 start to be fitted, a gap is formed between the inner teeth 13 and the outer teeth 14 and the portions other than the portions where the fitting begins. In this part, the tooth surface of the inner tooth 13 and the tooth surface of the outer tooth 14 are pressed against each other (first configuration example).

  More specifically, for example, in the initial part where the inner teeth 13 and the outer teeth 14 begin to fit in the axial direction, as shown in FIG. As shown in FIG. 2 (b), the tooth gap width W1 of the internal tooth 13 is set to be larger than the tooth thickness W2 of the tooth 14 and the part other than the part where the internal tooth 13 and the external tooth 14 begin to fit. It is formed in two different splines (two-stage splines) formed somewhat smaller than the tooth thickness W2 of the external teeth.

  Therefore, in the process of relatively moving the hub 3 and the shaft 10 in the axial direction of the hole 12 and fitting the inner teeth 13 and the outer teeth 14, at the initial stage when the inner teeth 13 and the outer teeth 14 start to be fitted. Since a gap is formed between the inner teeth 13 and the outer teeth 14, the shaft 10 is easily inserted into the hole 12 of the hub 3 (the outer teeth 14 are easily inserted into the inner teeth 13 in the axial direction). When the hub 3 and the shaft 10 are further moved relative to each other in the axial direction of the hole 12, the tooth surfaces of the inner teeth 13 and the tooth surfaces of the outer teeth 14 are pressed against each other to be deformed and fitted with no clearance. .

  Therefore, it is possible to eliminate the minute vibrations of the hub 3 and the shaft 4 due to the presence of the clearance while ensuring the smooth assembly of the hub 3 and the shaft 10, and the internal teeth 13 and the shaft 4 of the hub 3 can be eliminated. It becomes possible to prevent the fretting wear of the external teeth 14.

3 and 4 show another configuration example of the fitting structure between the hub 3 and the shaft 10 (second configuration example). In this example, a plurality of inner teeth 13 are formed on the inner peripheral surface of the hole 12, and a plurality of outer teeth 14 that mesh with the inner teeth 13 are formed on the outer peripheral surface of the shaft 10. A slit 20 is formed at the distal end portion inserted into the center bolt 11, the diameter (R1) of the base end portion 11a of the center bolt 11 is formed larger than the diameter (R2) of the distal end portion (R1> R2), and the center bolt 11 Is screwed onto the shaft 10 so that the distal end portion of the shaft 10 is expanded in the radial direction by the proximal end portion 11a of the center bolt 11.
Since other configurations are the same as the configurations in FIG. 3, the same portions are denoted by the same reference numerals, and description thereof is omitted.

  Accordingly, in such a configuration, the inner teeth 13 and the outer teeth 13 are so fitted that the shaft 10 is loosely fitted in the holes 12 of the hub 3 (so that a clearance is formed between the inner teeth 13 and the outer teeth 14). The teeth 14 are formed in advance, and the hub 3 and the shaft 10 are moved relative to each other in the axial direction of the hole 12 so that the inner teeth 13 and the outer teeth 14 are fitted together (state shown in FIG. 4A). After that, if the hub 3 is fixed to the shaft 10 with the center bolt 11, when the center bolt 11 is tightened to the back, the distal end portion of the shaft 10 is pushed outward in the radial direction by the base end portion 11a. As shown in FIG. 4B, the teeth 14 are displaced radially outward, and are pressed against the inner teeth 13 formed on the inner peripheral surface of the hole 12, so that the hub 3 and the shaft 10 are in clearance. Will be fitted together.

  For this reason, it becomes possible to eliminate minute vibrations of the hub 3 and the shaft 10 due to the presence of the clearance while ensuring a smooth assembly of the hub 3 and the shaft 10, and the internal teeth 13 of the hub 3 and the shaft 10. It becomes possible to prevent the fretting wear of the external teeth 14.

FIG. 5 shows another configuration example of the fitting structure between the hub 3 and the shaft 10 (third configuration example). In this example, the hole 12 has a polygonal cross section, and the shaft 10 has a polygonal shape that matches the cross sectional shape of the hole 12 (in FIG. 5A, a quadrangular shape, in FIG. 5B). And a center bolt 11 as shown in FIG. 3, the diameter (R1) of the base end portion 11a is compared with the diameter (R2) of the tip end portion 11b. The center bolt 11 is screwed into the shaft 10 so that the portion of the shaft 10 inserted into the hole 12 at the base end portion 11a of the center bolt 11 is expanded in the radial direction. I have to.
Since other configurations are the same as those in FIG. 3, the same reference numerals are given to the same portions and the description thereof is omitted.

  Even in such a configuration, the cross-sectional shape of the shaft 10 is formed somewhat smaller than the cross-sectional shape of the hole 12, and the hub 3 and the shaft 10 are moved relative to each other in the axial direction of the hole 12 to be fitted (see FIG. 5 (a), (b) upper stage), and then, if the hub 3 is fixed to the shaft 10 with the center bolt 11, the shaft by the base end 11a of the center bolt 11 when the center bolt 11 is tightened to the back. The outer end surface of the shaft 10 is displaced radially outward and pressed against the inner surface of the hole 12 of the hub 3 facing each other, and the hub 3 and the shaft 10 are fitted with no clearance. (The lower part of FIGS. 5A and 5B).

  For this reason, it becomes possible to eliminate minute vibrations of the hub 3 and the shaft 10 due to the presence of the clearance while ensuring a smooth assembly of the hub 3 and the shaft 10, and the internal teeth 13 of the hub 3 and the shaft 10 can be removed. It becomes possible to prevent the fretting wear of the external teeth 14. Particularly in such a configuration, since the cross-sectional shapes of the hole 12 and the shaft 10 are formed in a polygonal shape, dimensional management becomes easy.

In the configuration shown in FIG. 5, as shown in FIG. 6, the outer peripheral surface of the distal end portion of the shaft 10 (the outer peripheral surface of the portion inserted into the hole 12 of the shaft 10) is gradually increased in the radial direction A taper surface 21 that enlarges the size of the shaft 12 is formed, and together with or instead of this, an inner peripheral surface of the hole 12 is formed on a taper surface 22 that gradually decreases in the radial direction from the insertion end of the shaft 10. The clearance between the inner surface of the hole 12 and the outer surface of the shaft 10 may be gradually reduced as the shaft 3 and the shaft 10 are relatively moved in the axial direction of the hole 12.
By adopting such a configuration, the clearance between the hub 3 and the shaft can be more effectively reduced.

  7 and 8 show another configuration example of the fitting structure between the hub 3 and the shaft 10 (fourth configuration example). In this example, a rectangular spline 30 composed of a plurality of convex portions and concave portions (uneven portions 32) is formed on the inner peripheral surface of the hole 12 of the hub 3, and the square shape is inserted into the portion of the shaft 10 to be inserted into the hole 12. A square spline shaft 31 composed of a convex portion and a concave portion (concave portion 33) fitted with the spline is formed, and the hub 3 and the shaft 10 are moved relative to each other in the axial direction of the hole 12 so that the concave portion 32 ( As shown in FIG. 9A, the square spline 30) and the uneven portion 33 (square spline shaft 31) of the shaft 10 begin to fit in the axial direction. A gap is formed between the uneven portion 32 and the uneven portion 33 formed on the shaft 10, and a tooth surface of the internal tooth 32 at a portion other than the portion where the fitting starts, as shown in FIG. And press contact allowances 34 are formed on the tooth surfaces of the external teeth 33. .

  Therefore, in such a configuration, the uneven portion 32 formed on the hub 3 and the uneven portion formed on the shaft 10 in the process of fitting the hub 3 and the shaft 10 relative to each other in the axial direction of the hole 12. In the initial stage when the engagement with 33 is started, a gap is formed between the concavo-convex portion 32 and the concavo-convex portion 33, so that the shaft 10 is easily inserted into the hole 12 of the hub 3 ( When the hub 3 and the shaft 10 are moved relative to each other in the axial direction of the hole 12, the pressure contact allowance 34 of the concave and convex portions 32 and 33 is pressed against each other. They are mutually deformed and fitted with no clearance.

  For this reason, it is possible to eliminate the minute vibrations of the hub 3 and the shaft 4 due to the presence of the clearance while ensuring the smooth assembly of the hub 3 and the shaft 10, and the uneven portion 32 of the hub 3 and the shaft 4. It becomes possible to prevent fretting wear of the uneven portion 33. In particular, in this example, since a polygonal spline is adopted, it is easier to manage the dimensions of the connecting portion between the hub 3 and the shaft 10 than an involute spline.

10 and 11 show another configuration example of the fitting structure between the hub 3 and the shaft 10 (fifth configuration example). In this example, the spline formed on the inner peripheral surface of the hole of the hub 3 is constituted by an involute spline made of parallel teeth, and the tip portion inserted into the hole 12 of the shaft 10 is predetermined with respect to the axis of the hole 12. An involute spline shaft is formed with a lead angle α (the external teeth 14 formed on the shaft 10 are formed with a predetermined lead angle α with respect to the axis of the hole 12), and a hub 3 between the inner teeth 13 and the outer teeth 14 in the initial portion where the inner teeth 13 formed on the inner peripheral surface of the third hole 12 and the outer teeth 14 formed on the outer peripheral surface of the shaft 10 start to fit. Is formed.
Other configurations are the same as those in the configuration example shown in FIG. 1, and therefore, the same portions are denoted by the same reference numerals and description thereof is omitted.

  In such a configuration, in the process in which the hub 3 and the shaft 10 are relatively moved in the axial direction of the hole 12 to be engaged, the internal teeth 13 and the external teeth 14 are initially engaged with each other at the initial stage. Since a gap is formed between the outer teeth 14 and the outer teeth 14, the outer teeth 14 of the shaft 10 can be easily fitted into the inner teeth 13 of the hub 3, and the hub 3 and the shaft 10 are further connected in the axial direction of the hole 12. When the relative movement is made, the external teeth 14 are formed with a predetermined lead angle α. Therefore, at one end side in the axial direction as the amount of insertion of the shaft 10 increases, as shown in FIG. One tooth surface of the inner tooth 13 is in pressure contact with the outer tooth 14, and the other tooth surface of the inner tooth 13 is in pressure contact with the outer tooth 14 on the other end side in the axial direction, as shown in FIG. And the parts that are pressed against each other are deformed and fitted with no clearance. It becomes a.

  For this reason, it becomes possible to eliminate minute vibrations of the hub 3 and the shaft 10 due to the presence of the clearance while ensuring a smooth assembly of the hub 3 and the shaft 10, and the internal teeth 13 of the hub 3 and the shaft 10. It becomes possible to prevent the fretting wear of the external teeth 14.

  12 and 13 show another configuration example of the fitting structure between the hub 3 and the shaft 10. In this example, a plurality of internal teeth 13 are formed on the inner peripheral surface of the hole 12 of the hub 3, and a plurality of external teeth 14 that mesh with the inner teeth 13 are formed on the outer peripheral surface of the shaft 10. 1, but the hub 3 and the shaft 10 are moved relative to each other in the axial direction of the hole 12 to start fitting the inner teeth 13 and the outer teeth 14. At least one of the inner teeth 13 and the outer teeth 14 is pressed into contact with the other tooth bottom surface at a portion other than the portion where the fitting starts.

  More specifically, in the configuration shown in FIG. 12, the outer teeth 14 are notched to the bottom surfaces of the inner teeth 13 by cutting out the tooth tip portions of the insertion end portions 41 of the outer teeth 14 formed on the outer peripheral surface of the shaft 10. The tooth tip of the external tooth 14 is made larger than the tooth base of the internal tooth 13 at a portion other than the insertion end, and the wave front surface 14 a of the external tooth 14 is pressed against the tooth bottom surface 13 b of the internal tooth 13. They are designed to be mutually deformed.

  In such a configuration, when the hub 3 and the shaft 10 are relatively moved in the axial direction of the hole 12 and the inner teeth 13 and the outer teeth 14 are fitted, the shaft 10 is initially in the beginning of fitting. Since the tip surface of the external tooth 14 does not contact the bottom surface of the internal tooth 13 of the hub 3, the external tooth 14 of the shaft 10 can be easily fitted into the internal tooth 13 of the hub 3. When the hole 12 is relatively moved in the axial direction, the tooth tip surface 14a of the outer tooth 14 and the tooth bottom surface 13b of the inner tooth 13 are deformed and pressed against each other, and are fitted with no clearance.

  For this reason, it becomes possible to eliminate minute vibrations of the hub 3 and the shaft 10 due to the presence of the clearance while ensuring a smooth assembly of the hub 3 and the shaft 10, and the internal teeth 13 of the hub 3 and the shaft 10. It becomes possible to prevent the fretting wear of the external teeth 14.

  Further, as shown in FIG. 13, the tooth tip portion of the insertion end portion 42 into which the shaft of the internal tooth 13 formed on the inner peripheral surface of the hole 12 is inserted is notched, and the tooth tip surface 13 a of the internal tooth 13 is formed. The tooth bottom surface 14 b of the outer teeth 14 is made not to contact the tooth bottom surface 14 b of the outer teeth 14. You may make it deform | transform mutually by press-contacting to the tooth base 14b.

  In such a configuration, when the hub 3 and the shaft 10 are relatively moved in the axial direction of the hole 12 so that the inner teeth 13 and the outer teeth 14 are fitted, the hub 3 is initially in the beginning of fitting. Since the tooth tip surface 13a of the inner teeth 13 does not contact the tooth bottom surface 14b of the outer teeth 14 of the shaft 3, the outer teeth 14 of the shaft 10 can be easily fitted into the inner teeth 13 of the hub 3, and the hub 3 and the shaft 10 Are moved relative to each other in the axial direction of the hole 12, the tooth tip surface 13a of the inner tooth 13 and the tooth bottom surface 14b of the outer tooth 14 are deformed and pressed against each other, and are fitted with no clearance.

  For this reason, it is possible to eliminate the minute vibrations of the hub 3 and the shaft 10 due to the presence of the clearance while ensuring a smooth assembly of the hub 3 and the shaft 10, and the inner surface 13 of the hub 3 and the outside of the shaft 10 can be eliminated. It is possible to prevent fretting wear of the teeth 14.

  In the above, fretting wear at the connecting portion between the hub 3 and the shaft 10 is ensured while ensuring a smooth assembly between the hub 3 as the first rotating body and the shaft 10 as the second rotating body. Although various configuration examples to prevent are shown, the present invention is not limited to the configuration examples shown here, and the above-described configurations may be used in appropriate combination. In the above description, the configuration in which the rotational power is transmitted from the hub 3 serving as the first rotating body to the shaft 10 serving as the second rotating body is shown, but the direction in which the power is transmitted is particularly limited. is not.

FIG. 1 is a cross-sectional view showing a first structural example of a power transmission device for a compressor according to the present invention. FIG. 1 (a) is a cross-sectional view showing the whole power transmission device, and FIG. FIG. 1C is a cross-sectional view in which the hub 3 and the shaft 10 are cut in parallel to the axis of the hole 12. 2 is a cross-sectional view showing a fitting state of the power transmission device shown in FIG. 1, and FIG. 2 (a) is a diagram showing a fitting state cut along line IIa-IIa in FIG. 1 (c). (B) is a figure which shows the fitting state cut | disconnected by the IIb-IIb line | wire of FIG.1 (c). FIG. 3 is a cross-sectional view showing a second configuration example of the power transmission device of the compressor according to the present invention, FIG. 2 (a) is a cross-sectional view showing the whole power transmission device, and FIG. 2 (b) is a center bolt. FIG. 2C is a view of the tip of the shaft as seen from the axial direction. 4 is a cross-sectional view showing a fitting state of the power transmission device shown in FIG. 3, FIG. 4 (a) is a view showing a state before the center bolt is screwed, and FIG. 4 (b) is a view showing the center bolt. It is a figure which shows the state after screwing. FIG. 5 is a cross-sectional view showing a third configuration example of the power transmission device for a compressor according to the present invention, and FIG. 5 (a) shows an example in which the cross section of each of the hole of the hub and the shaft is made square, FIG. 5B is a diagram showing an example in which the cross section of each of the hole of the hub and the shaft is pentagonal. FIG. 6 is a cross-sectional view showing a modification of the power transmission device shown in FIG. FIG. 7 is a cross-sectional view showing a fourth configuration example of the power transmission device for the compressor according to the present invention. FIG. 8 is a cross-sectional view showing a configuration example of the shaft 10 (FIG. 8A) and the hub 3 (FIG. 8B) used in the power transmission device shown in FIG. FIG. 9 is a cross-sectional view showing a fitting state of the power transmission device shown in FIGS. 7 and 8, and FIG. 9 (a) is a cross section at a portion where the hub and the shaft are relatively moved in the axial direction to start fitting. FIG. 9B is a diagram showing a cross section at a portion other than the portion where the hub and the shaft are relatively moved in the axial direction and the fitting is started. FIG. 10 is a cross-sectional view showing a fifth configuration example of the power transmission device of the compressor according to the present invention, FIG. 10 (a) is a cross-sectional view showing the whole power transmission device, and FIG. 10 (b) is a shaft. FIG. FIG. 11 is a cross-sectional view showing a fitting state of the power transmission device shown in FIG. 10, and FIG. 11 (a) is at one end side in the axial direction when the hub and the shaft are relatively moved in the axial direction. FIG. 11B shows a cross section at the other end side in the axial direction when the hub and the shaft are relatively moved in the axial direction and fitted. 12 is a cross-sectional view showing a sixth configuration example of the power transmission device for a compressor according to the present invention, and FIG. 12 (a) is a cross-sectional view showing the relationship between the internal teeth and the external teeth. (B) is a sectional side view showing a process in which a hub and a shaft are relatively moved in the axial direction and fitted. 13 is a cross-sectional view showing a modification of the power transmission device shown in FIG. 12, FIG. 13 (a) is a cross-sectional view showing the relationship between internal teeth and external teeth, and FIG. 13 (b) is a hub. It is a sectional side view which shows the process in which a shaft and a shaft are relatively moved and fitted in an axial direction.

Explanation of symbols

3 Hub (first rotating body)
10 Shaft (second rotating body)
DESCRIPTION OF SYMBOLS 11 Center bolt 11a Base end part 12 Hole 13 Internal tooth 14 External tooth 20 Slot 21, 22 Tapered surface 30 Square type spline 31 Square type spline shaft 32, 33 Uneven part

Claims (7)

A first rotating body and a second rotating body for transmitting rotational power to each other; the second rotating body is inserted into a hole formed in the first rotating body; and the inner peripheral surface of the hole Compression that forms a plurality of internal teeth and connects the first and second rotary bodies to each other by forming a plurality of external teeth that mesh with the internal teeth on the outer peripheral surface of the second rotary body. In the power transmission device of the machine,
The inner teeth and the outer teeth at a portion where the first and second rotating bodies are relatively moved in the axial direction of the hole and the inner teeth and the outer teeth start to be fitted in the axial direction. A power transmission device for a compressor, wherein a gap is formed between the inner tooth and the tooth surface of the outer tooth at a portion other than the portion where the fitting starts. . A first rotating body and a second rotating body for transmitting rotational power to each other; the second rotating body is inserted into a hole formed in the first rotating body; and the inner peripheral surface of the hole A plurality of internal teeth are formed and a plurality of external teeth meshing with the internal teeth are formed on an outer peripheral surface of the second rotating body, and the first rotating body and the second rotating body are centered. In the power transmission device for the compressor, the first and second rotating bodies are connected to each other by fastening in the axial direction with bolts.
A slit is provided on the rotating shaft, a diameter of a base end portion of the center bolt is formed larger than that of a front end portion, and the hole is formed by the base end portion of the center bolt screwed into the second rotating body. A power transmission device for a compressor, wherein a portion of the inserted second rotating body is expanded in a radial direction. A first rotating body and a second rotating body through which rotational power is transmitted to each other; the second rotating body is inserted into a hole formed in the first rotating body; and In the power transmission device for a compressor, which connects the first and second rotating bodies to each other by fastening the second rotating body in the axial direction with a center bolt.
The hole has a polygonal cross section, the second rotating body has a polygonal shape matching the hole cross sectional shape, the second rotating body is provided with a slit, and the base end of the center bolt The diameter of the part is formed larger than the tip part, and the part of the second rotating body inserted into the hole is expanded in the radial direction by the base end part of the center bolt screwed to the rotating shaft. A power transmission device for a compressor. 4. The compressor according to claim 2, wherein a portion of the second rotating body disposed inside the hole is formed in a tapered shape that gradually increases in diameter from the insertion side into the hole. Power transmission device. First and second rotating bodies that transmit rotational power to each other are provided, and the first and second rotating bodies are inserted into holes formed in the first rotating body. In the power transmission device of the compressor that connects the rotating bodies to each other,
A square spline composed of a plurality of convex portions and concave portions is formed on the inner peripheral surface of the hole, and a convex portion and a raised portion that are fitted to the square spline at an outer peripheral portion to be inserted into the hole of the second rotating body. A power transmission device characterized in that a square spline shaft is formed. A first rotating body and a second rotating body for transmitting rotational power to each other; the second rotating body is inserted into a hole formed in the first rotating body; and the inner peripheral surface of the hole Compression that forms a plurality of internal teeth and connects the first and second rotary bodies to each other by forming a plurality of external teeth that mesh with the internal teeth on the outer peripheral surface of the second rotary body. In the power transmission device of the machine,
A power transmission device, wherein at least one of the inner teeth and the outer teeth is formed with a predetermined lead angle with respect to the axial center of the hole. A first rotating body and a second rotating body for transmitting rotational power to each other; the second rotating body is inserted into a hole formed in the first rotating body; and the inner peripheral surface of the hole Compression that forms a plurality of internal teeth and connects the first and second rotary bodies to each other by forming a plurality of external teeth that mesh with the internal teeth on the outer peripheral surface of the second rotary body. In the power transmission device of the machine,
At least one of the internal teeth and the external teeth at a portion where the internal teeth and the external teeth begin to be engaged by relatively moving the first rotary body and the second rotary body in the axial direction of the hole. The power transmission device is characterized in that at least one tooth tip surface of the inner teeth and the outer teeth and the other tooth bottom surface are pressed in a portion other than the portion where the fitting starts.

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