WO2016088577A1 - Engrenage hélicoïdal en résine - Google Patents

Engrenage hélicoïdal en résine Download PDF

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Publication number
WO2016088577A1
WO2016088577A1 PCT/JP2015/082680 JP2015082680W WO2016088577A1 WO 2016088577 A1 WO2016088577 A1 WO 2016088577A1 JP 2015082680 W JP2015082680 W JP 2015082680W WO 2016088577 A1 WO2016088577 A1 WO 2016088577A1
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WIPO (PCT)
Prior art keywords
tooth
width direction
reference line
end side
helical gear
Prior art date
Application number
PCT/JP2015/082680
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English (en)
Japanese (ja)
Inventor
憲仕 近江
Original Assignee
株式会社エンプラス
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2015053136A external-priority patent/JP6448423B2/ja
Application filed by 株式会社エンプラス filed Critical 株式会社エンプラス
Priority to CN201580064092.2A priority Critical patent/CN107002852B/zh
Priority to US15/532,773 priority patent/US10584784B2/en
Publication of WO2016088577A1 publication Critical patent/WO2016088577A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling

Definitions

  • the present invention relates to a resin helical gear used for rotation transmission, and more particularly to a resin helical gear whose tooth surface has been modified to reduce rotation transmission errors caused by misalignment of gear shafts. It is.
  • JP-A-8-197332 (particularly paragraphs 0001 to 0006, FIG. 17) JP 2014-89483 A (particularly FIGS. 5 to 6) Japanese Patent Laid-Open No. 10-89442 (particularly FIGS. 1 and 8) JP 2008-275060 A (particularly FIGS. 8 and 11)
  • the present invention provides a resin helical gear with high rotation transmission accuracy that can reduce rotation transmission errors caused by misalignment of gear shafts.
  • the present invention relates to a resin helical gear 1 in which a tooth surface 11 of an involute tooth-shaped tooth 2 is subjected to three-dimensional tooth surface modification.
  • a first processing reference line 12 obliquely connecting a tooth tip side of one end in the tooth width direction of the tooth 2 and a tooth base side of the other end of the tooth 2 in the tooth width direction along the tooth surface 11;
  • a second machining reference line 13 obliquely connecting the tooth tip side of the other end of the tooth 2 in the tooth width direction and the tooth base side of the one end of the tooth 2 in the tooth width direction along the tooth surface 11.
  • the tooth surface 11 is scraped off from the first processing reference line 12 with a smooth first curved surface 15 toward the tooth base on one end side in the tooth width direction of the tooth 2 and from the second processing reference line 13 to the tooth.
  • the three-dimensional tooth surface modification is performed so as to be scraped off by a smooth second curved surface 16 toward the tooth base at the other end in the tooth width direction of the second tooth, whereby the first processing reference line 12 and the first 2
  • the involute tooth profile is left on the tooth tip side of the tooth 2 with respect to the processing reference line 13.
  • the resin helical gear according to the present invention reduces the rotation transmission error caused by the misalignment of the gear shaft and the misalignment of the gear shaft, compared with the conventional resin helical gear subjected to tooth surface modification. Even when there is, rotation transmission accuracy can be improved.
  • FIG.1 (a) is a front view of the resin-made helical gears which concern on this embodiment
  • FIG.1 (b) is FIG.
  • FIG. 1A is a cross-sectional view of a resin helical gear cut along the line A1-A1 in FIG. 1A
  • FIG. 1C is a perspective view of the teeth of the resin helical gear according to the present embodiment viewed obliquely from above. It is a perspective view shown.
  • FIG. 4A is an external perspective view of the teeth of the resin helical gear according to the first comparative example
  • FIG. 4B is an external perspective view of the teeth of the resin helical gear according to the second comparative example.
  • 4 (c) is an external perspective view of the teeth of the resin helical gear according to the third comparative example
  • FIG. 4 (d) is an illustration of the resin helical gear according to the fourth comparative example. It is an external appearance perspective view of a tooth.
  • 2 (a-2), (b-2), and (c-2) are set to the meshing state of the teeth, and the rotation transmission error (meshing primary component of the resin helical gear according to the second comparative example) ) Is measured by a single-tooth meshing test, and the result of measuring the rotation transmission error (meshing primary component) of an unmodified helical gear by a single-tooth meshing test is shown.
  • 2 (a-2), (b-2), and (c-2) are set to the meshing state of the teeth, and the rotational transmission error (meshing primary component) of the resin helical gear according to the third comparative example is set.
  • the drive side is changed from a helical gear made of metal (brass) to a helical gear made of resin (POM (equivalent to M25)), and the gear shaft shown in FIGS. 2 (a-1) and 2 (c-1) is changed.
  • Measurement result of rotation transmission error (meshing primary component) of resin helical gear according to the first embodiment in a state where misalignment occurs and measurement of rotation transmission error (meshing primary component) of unmodified helical gear It is a figure which compares and shows a result. It is an external appearance perspective view of the tooth
  • FIG. 11A is a perspective view showing teeth of a resin helical gear according to the second embodiment of the present invention when viewed obliquely from above, and FIG. 11B is a tooth shape of FIG. 11A.
  • FIG. 11C is a second auxiliary diagram for explaining the tooth shape of FIG. 11A.
  • the meshing state of the teeth is set, and the rotation transmission error of the resin helical gear according to the second embodiment of the present invention is set.
  • the primary component of meshing as a result of measuring the primary component of the tooth meshing test and the rotational transmission error of a helical gear made of resin (unmodified helical gear) that is not subjected to tooth surface modification that is generally used It is a figure which compares and shows the result of having measured the component by the one-tooth surface meshing test.
  • the tooth meshing state shown in FIGS. 2 (a-2), (b-2), and (c-2) is set, and the meshing primary component as the rotation transmission error of the product 2 of the present invention is determined by the one-tooth meshing test.
  • FIG. 14A is a perspective view showing the teeth of a resin helical gear according to Modification 1 of the second embodiment of the present invention when viewed obliquely from above, and FIG. 14B is FIG. 14A.
  • FIG. 14 (c) is a second auxiliary diagram for explaining the tooth shape of FIG. 14 (a).
  • FIG. 15A is a perspective view showing teeth of a resin helical gear according to the third embodiment of the present invention when viewed obliquely from above, and FIG. 15B is a tooth shape of FIG. 15A.
  • 15C is a second auxiliary diagram for explaining the tooth shape of FIG. 15A.
  • the meshing state of the teeth is set, and the rotation transmission error of the resin helical gear according to the third embodiment of the present invention is set.
  • the primary component of meshing as a result of measuring the primary component of the tooth meshing test and the rotational transmission error of a helical gear made of resin (unmodified helical gear) that is not subjected to tooth surface modification that is generally used It is a figure which compares and shows the result of having measured the component by the one-tooth surface meshing test.
  • FIG. 18 (a) is a perspective view showing the teeth of a resin helical gear according to Modification 1 of the third embodiment of the present invention when viewed obliquely from above
  • FIG. 18 (b) is a perspective view of FIG. 18 (a).
  • FIG. 18C is a second auxiliary diagram for explaining the tooth shape of FIG. 18A.
  • FIG. 19A is a perspective view showing teeth of a resin helical gear according to the fourth embodiment of the present invention when viewed obliquely from above, and FIG. 19B is a tooth shape of FIG. 19A.
  • FIG. 19C is a second auxiliary diagram for explaining the tooth shape of FIG. 19A.
  • FIG. 1 is a view showing a resin helical gear 1 according to the first embodiment of the present invention.
  • FIG. 1A is a front view of the resin helical gear 1 according to the present embodiment.
  • FIG. 1B is a sectional view of the resin helical gear 1 cut along the line A1-A1 in FIG.
  • FIG.1 (c) is a perspective view which shows the tooth
  • a resin helical gear 1 includes a cylindrical boss 4 in which a shaft hole 3 fitted to a shaft is formed, and an outer circumferential surface 4a of the boss 4 radially outward. It has an extending disk-shaped web 5, a cylindrical rim 6 formed on the outer peripheral edge of the web 5, and a plurality of teeth 2 formed on the outer peripheral side of the rim 6. Further, in the resin helical gear 1, the web 5 that connects the outer peripheral surface 4 a of the boss 4 and the inner peripheral surface 6 a of the rim 6 is located at the central portion along the central axis 7 of the boss 4. In addition, the resin helical gear 1 has one side surface 4b (left side surface in FIG.
  • the tooth 2 of the helical helical gear 1 shown in FIG. 1 (c) is formed by three-dimensional modification of the tooth surface 11 of the tooth 2 having an involute tooth profile. That is, in this embodiment, the tooth surface 11 (one tooth surface of both tooth surfaces) used for meshing of the teeth 2 is the tooth tip side on one end side in the tooth width direction of the teeth 2 and the tooth width of the teeth 2.
  • a line that obliquely connects the tooth base side on the other end side in the direction along the tooth surface 11 is defined as a first processing reference line 12, and the tooth tip side on the other end side in the tooth width direction of the tooth 2 and one end in the tooth width direction on the tooth 2
  • a line that obliquely connects the tooth base side along the tooth surface 11 is the second machining reference line 13
  • the first machining reference line 12 is provided along the advancing direction 14 of the meshing contact line. .
  • the tooth surface 11 is scraped off from the first processing reference line 12 with a smooth first curved surface 15 toward the tooth base on one end side in the tooth width direction of the tooth 2, and the tooth of the tooth 2 from the second processing reference line 13.
  • the tooth surface 11 has a tooth surface portion 11a (involute tooth profile) having a shape similar to a triangular shape in which three-dimensional tooth surface modification is not performed on the tooth tip side of the first processing reference line 12 and the second processing reference line 13. Shape tooth surface portion) is left.
  • a modification amount of the tooth surface 11 of the tooth 2 is represented by ⁇ .
  • the ridge line 19a formed by the first curved surface 15 and the second curved surface 16 has the first machining reference line 12 and the second machining reference.
  • the line 13 extends from the intersecting portion 19b to the tooth base side along the tooth height direction.
  • the processing direction of the first curved surface 15 is a direction along a virtual line 29 a extending from the tooth root on one end side in the tooth width direction of the tooth surface 11 so as to be orthogonal to the first processing reference line 12.
  • the processing direction of the second curved surface 16 is a direction along a virtual line 29 b extending from the tooth base on the other end side in the tooth width direction of the tooth surface 11 so as to be orthogonal to the second processing reference line 13.
  • FIG. 2 schematically shows the meshing state of the teeth 20 and 21 when the gear shafts 17 and 18 are misaligned and the meshing state of the teeth 20 and 21 when the gear shafts 17 and 18 are not misaligned.
  • FIG. 2A-1 shows a state where the gear shaft 17 of the helical gear 22 on the driving side is assembled with being shifted by ⁇ with respect to the gear shaft 18 of the helical gear 23 on the driven side.
  • FIG. 2A-2 shows a state in which the teeth 20 of the helical gear 22 on the driving side and the teeth 21 of the helical gear 23 on the driven side in FIG. 2A-1 are engaged.
  • FIG. 2 schematically shows the meshing state of the teeth 20 and 21 when the gear shafts 17 and 18 are misaligned and the meshing state of the teeth 20 and 21 when the gear shafts 17 and 18 are not misaligned.
  • FIG. 2A-1 shows a state where the gear shaft 17 of the helical gear 22 on the driving side is assembled with being shifted by ⁇
  • FIG. 2B-1 shows that the gear shaft 17 of the helical gear 22 on the driving side is assembled without causing a shift in the gear shaft 18 of the helical gear 23 on the driven side (without misalignment). Shows the state.
  • FIG. 2B-2 shows a state in which the teeth 20 of the helical gear 22 on the driving side and the teeth 21 of the helical gear 23 on the driven side in FIG.
  • FIG. 2 (c-1) shows a state in which the gear shaft 17 of the helical gear 22 on the driving side is assembled with a shift of + ⁇ with respect to the gear shaft 18 of the helical gear 23 on the driven side.
  • FIG. 2B-2 shows a state in which the teeth 20 of the helical gear 22 on the driving side and the teeth 21 of the helical gear 23 on the driven side in FIG.
  • FIG. 2 (c-1) shows a state in which the gear shaft 17 of the helical gear 22 on the driving side is assembled with a shift of + ⁇ with respect to the gear shaft 18
  • FIGS. 2 (a-1), 2 (b-1) and 2 (c-1) clarify the difference between them. Therefore, for convenience, the tooth width of the helical gear 22 on the driving side is made smaller than the tooth width of the helical gear 23 on the driven side.
  • FIG. 3 shows the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and the rotation transmission error of the resin helical gear 1 according to this embodiment.
  • FIG. 3B is a diagram showing the results of the one-tooth engagement test (second engagement test) in the tooth engagement state of FIG. 2B-2.
  • FIG. 3C is a diagram showing a result of the one-tooth engagement test (third engagement test) in the tooth engagement state of FIG. 2C-2.
  • the resin helical gear 1 according to the present embodiment is indicated as the product 1 of the present invention.
  • the horizontal axis represents the load torque (Nm)
  • the vertical axis represents the meshing primary component (sec) of the rotation transmission error.
  • the meshing primary component as a rotation transmission error is abbreviated as a rotation transmission error as appropriate.
  • the single-tooth contact test was performed using a single-tooth contact tester (MEATA-4) manufactured by Ogasawara Precision Laboratories.
  • the gear specifications of the driving side helical gear 22 and the driven side helical gear 23 used in this one-tooth engagement test are: number of teeth (Z) 36, module (m) 0.7, pressure angle ( ⁇ ) 20 °, torsion angle ( ⁇ ) 20 °, tooth width 7 mm, parallel teeth.
  • the alignment error ( ⁇ shown in FIGS. 2A and 2C) of the gear shafts 17 and 18 is 0 in consideration of the condition in which the resin helical gear 1 according to this embodiment is used. .5 °.
  • the one-tooth engagement test was performed by applying a load torque of 0.05 Nm to 0.3 Nm in consideration of the conditions under which the resin helical gear 1 according to this embodiment is used.
  • a helical gear made of metal (brass) was used as the drive-side helical gear 22 having a standard tooth profile (involute tooth profile).
  • the driven helical gear 23 is a non-modified helical gear (not shown) made of resin (POM (equivalent to M25)), which is a criterion for determining whether the rotation transmission error is good or not, and the resin (
  • the helical gear 1 made of POM (equivalent to M25) or any of the helical gears 24 to 27 made of resin (POM (equivalent to M25)) according to first to fourth comparative examples described later is used.
  • the single tooth surface meshing tester cannot give an alignment error between the gear shafts 17 and 18 (the drive side tilts the gear shaft 17 of the helical gear 22 with respect to the gear shaft 18 of the helical gear 23 on the driven side).
  • the driving side at 0 ° is replaced with a helical gear to constitute the meshing state shown in FIG. 2 (c-2).
  • the single-tooth surface meshing tester ensures that the backlash is secured to the theoretical inter-axis distance when the gear shaft 17 of the helical gear 22 on the driving side and the gear shaft 18 of the helical gear 23 on the driven side are tested. For this reason, the distance is 0.25 mm.
  • the modification amount ⁇ of the tooth surface 11 is set to 20 ⁇ m.
  • POM (M25) indicates grade M25 of trade name “Duracon” (registered trademark) manufactured by Polyplastics Co., Ltd.
  • the product 1 of the present invention has a rotation transmission error smaller than that of an unmodified helical gear or an unmodified non-modified helical gear. It has become.
  • the product 1 of the present invention has a rotation transmission error smaller than that of an unmodified helical gear or a numerical value similar to that of an unmodified helical gear. It has become.
  • the product 1 of the present invention shows the numerical value that the rotation transmission error is closer to the unmodified helical gear, and the rotation transmission error is a very small numerical value and the fluctuation range is small. .
  • the rotation transmission error has decreased significantly compared with the unmodified helical gear.
  • the product 1 of the present invention can always reduce the rotation transmission error as compared with the non-modified helical gear that is always used, regardless of the direction of misalignment.
  • FIG. 4 is a view showing the teeth 30 to 33 of the resin helical gears 24 to 27 according to the first to fourth comparative examples.
  • FIG. 4A is an external perspective view of the teeth 30 of the resin helical gear 24 according to the first comparative example in which the tooth surface 34 is crowned.
  • FIG. 4B is an external perspective view of the tooth 31 of the resin helical gear 25 according to the second comparative example in which a part of the tooth surface 34 is subjected to bias-in tooth surface modification.
  • FIG. 4C is an external perspective view of the teeth 32 of the resin helical gear 26 according to the third comparative example in which the entire tooth surface 34 is subjected to bias-in tooth surface modification.
  • FIG. 4D is an external perspective view of the teeth 33 of the resin helical gear 27 according to the fourth comparative example in which the tooth surface 34 is subjected to bias-out tooth surface modification.
  • FIG. 5 sets the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and transmits the rotation of the resin helical gear 24 according to the first comparative example. It is a figure which compares and shows the result of having measured the error by the single-tooth surface meshing test, and the result of having measured the rotation transmission error of the unmodified helical gear by the single-tooth surface meshing test.
  • Fig.5 (a) is a figure which shows the result of a 1st meshing test.
  • FIG. 5B is a diagram showing the results of the second meshing test.
  • FIG. 5C is a diagram showing the results of the third meshing test.
  • the resin helical gear 24 according to the first comparative example is indicated as the first comparative example.
  • the rotation transmission error is larger than that of the unmodified helical gear in the range where the load torque exceeds 0.2 (Nm). It has become.
  • the second meshing test shown in FIG. 5B in the first comparative example, when the load torque becomes 0.1 (Nm) or more, the rotation transmission error is larger than that of the unmodified helical gear. It is getting bigger.
  • the third meshing test shown in FIG. 5C in the first comparative example, the rotation transmission error is significantly reduced as compared with the unmodified helical gear.
  • FIG. 6 sets the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and transmits the rotation of the resin helical gear 25 according to the second comparative example. It is a figure which compares and shows the result of having measured the error by the single-tooth surface meshing test, and the result of having measured the rotation transmission error of the unmodified helical gear by the single-tooth surface meshing test.
  • Fig.6 (a) is a figure which shows the result of a 1st meshing test.
  • FIG.6 (b) is a figure which shows the result of a 2nd meshing test.
  • FIG. 6C shows the result of the third meshing test.
  • the resin helical gear 25 according to the second comparative example is indicated as the second comparative example.
  • the rotation transmission error is larger than that of the unmodified helical gear.
  • the rotation transmission error is almost the same as that of the unmodified helical gear.
  • the rotation transmission error is significantly reduced compared to the unmodified helical gear.
  • FIG. 7 sets the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and transmits the rotation of the resin helical gear 26 according to the third comparative example. It is a figure which compares and shows the result of having measured the error by the single-tooth surface meshing test, and the result of having measured the rotation transmission error of the unmodified helical gear by the single-tooth surface meshing test.
  • Fig.7 (a) is a figure which shows the result of a 1st meshing test.
  • FIG. 7B is a diagram showing the results of the second meshing test.
  • FIG.7 (c) is a figure which shows the result of a 3rd meshing test.
  • the resin helical gear 26 according to the third comparative example is indicated as the third comparative example.
  • the rotation transmission error is larger than that of the unmodified helical gear.
  • the rotation transmission error has decreased significantly compared with the unmodified helical gear.
  • the rotation transmission error is significantly reduced as compared with the unmodified helical gear.
  • FIG. 8 sets the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and transmits the rotation of the resin helical gear 27 according to the fourth comparative example. It is a figure which compares and shows the result of having measured the error by the single-tooth surface meshing test, and the result of having measured the rotation transmission error of the unmodified helical gear by the single-tooth surface meshing test.
  • Fig.8 (a) is a figure which shows the result of a 1st meshing test.
  • FIG. 8B is a diagram showing the results of the second meshing test.
  • FIG. 8C is a diagram showing the results of the third meshing test.
  • the resin helical gear 27 according to the fourth comparative example is indicated as a fourth comparative example.
  • the rotation transmission error is smaller than that of the unmodified helical gear.
  • the rotation transmission error is larger than that of the unmodified helical gear.
  • the rotation transmission error is significantly worse (larger) than that of the unmodified helical gear.
  • Table 1 shown below summarizes the results of the one-tooth engagement test (first to third engagement test) of the product to be measured (the product 1 of the present invention, the first to fourth comparative examples).
  • a circle indicates a case where the rotation transmission error of the product to be measured is equal to or smaller than the rotation transmission error of the unmodified helical gear (good case).
  • x indicates a case where the rotation transmission error of the measurement target product is larger (bad) than the rotation transmission error of the unmodified helical gear.
  • the rotation transmission error of the product 1 of the present invention is better than the rotation transmission error of the helical gear in all the results of the first to third meshing tests (indicated by a circle). Is in the state shown).
  • the rotation transmission error of the first to fourth comparative examples is that at least one of the results of the first to third meshing tests is more than the rotation transmission error of an unmodified helical gear. It is getting worse (in a state indicated by a cross).
  • the product 1 of the present invention was able to reduce the rotation transmission error more than the generally used unmodified helical gear and the first to fourth comparative examples, regardless of the misalignment direction. .
  • the resin helical gear 1 according to the present embodiment includes an unmodified helical gear and a conventional helical gear (first to fourth) that has undergone conventional tooth surface modification. Comparative Example) Compared with 24-27, the rotation transmission error caused by misalignment of the gear shafts 17 and 18 can be reduced, and the rotation transmission accuracy can be improved even when the gear shafts 17 and 18 are misaligned. .
  • FIG. 9 shows that the drive side gear is a resin (POM (equivalent to M25)) helical gear instead of a metal (brass) helical gear having a standard tooth profile
  • FIG. 2 (a-1) and FIG. Measurement result of rotation transmission error of resin helical gear 1 according to the first embodiment and rotation transmission error of unmodified helical gear in the state where the misalignment of the gear shaft shown in 2 (c-1) occurs It is a figure which contrasts and shows the measurement result.
  • FIG. 9A shows the measurement result of the rotation transmission error of the resin helical gear 1 according to the first embodiment in the state where the misalignment of the gear shaft shown in FIG.
  • FIG. 9A shows the measurement result of the rotation transmission error of the resin helical gear 1 according to the first embodiment in the state where the misalignment of the gear shaft shown in FIG.
  • FIG. 9A shows the measurement result of the rotation transmission error of the resin helical gear 1 according to the first embodiment in the state where the misalignment
  • FIG. 6 is a diagram showing a comparison of the measurement result of the rotation transmission error of the helical gear with no modification.
  • FIG. 9B shows the measurement result of the rotation transmission error of the resin helical gear 1 according to the first embodiment in a state where the misalignment of the gear shaft shown in FIG.
  • FIG. 6 is a diagram showing a comparison of the measurement result of the rotation transmission error of the helical gear with no modification.
  • the gear shaft shown in FIG. 2 (a-1) and FIG. 2 (c-1) is misaligned.
  • the drive side gear having the standard tooth profile is a resin (POM (equivalent to M25)) helical gear
  • the rotation transmission error is the same as or smaller than that of the helical gear without modification. That is, when the resin helical gear 1 according to the first embodiment is used in a state where the gear shaft is misaligned, the driving side helical gear is made of resin (POM (equivalent to M25)). Even if it is a gear, rotation transmission accuracy can be improved.
  • the resin helical gear 1 according to the first embodiment is adapted to perform three-dimensional tooth surface modification on one tooth surface of both tooth surfaces, but is not limited to this, and both tooth surfaces are provided. Three-dimensional tooth surface modification may be performed to reduce rotational transmission errors in both the forward and reverse directions when the gear shaft is misaligned.
  • the intersection 19b of the first machining reference line 12 and the second machining reference line 13 of the tooth surface 11 is closer to the tooth root than the position shown in FIG. You may set the 1st process reference line 12 and the 2nd process reference line 13 so that it may be located in. With this configuration, in the resin helical gear 1, the length of the first processing reference line 12 positioned along the traveling direction 14 of the meshing contact line is increased. Further, in the resin helical gear 1 according to the first embodiment, the intersecting portion 19b of the first machining reference line 12 and the second machining reference line 13 of the tooth surface 11 has a tooth shape more than the position shown in FIG.
  • the modification amount of the tooth surface 11 is equal to ⁇ on the first curved surface 15 side and the second curved surface 16 side.
  • the modification amount ⁇ 1 of the tooth surface 11 on the first curved surface 15 side is set to be larger than the modification amount ⁇ 2 of the tooth surface 11 on the second curved surface 16 side (see FIG. 10A), or the second
  • the modification amount ⁇ 2 of the tooth surface 11 on the curved surface 16 side may be made larger than the modification amount ⁇ 1 of the tooth surface 11 on the first curved surface 15 side (see FIG. 10B) to reduce the rotation transmission error.
  • FIG. 11A is a perspective view showing the teeth 2 of the resin helical gear 1 according to the second embodiment of the present invention when viewed obliquely from above.
  • FIG.11 (b) is a 1st auxiliary
  • FIG.11 (c) is a 2nd auxiliary
  • the tooth 2 of the resin helical gear 1 is formed by performing three-dimensional tooth surface modification on the tooth surface 11 of the tooth 2 having an involute tooth shape. That is, in this embodiment, the tooth surface 11 (one tooth surface of both tooth surfaces) used for the engagement of the teeth 2 is the tooth tip side in the center of the tooth width direction of the tooth 2 and the tooth width direction of the tooth 2.
  • a first machining reference line 40 that obliquely connects the tooth base side at one end side along the tooth surface 11 (see FIG.
  • the tooth surface 11 is scraped off from the first processing reference line 40 toward the tooth tip on one end side in the tooth width direction of the tooth 2 with a smooth first curved surface 45 (see FIG. 11B), and the second processing reference.
  • a smooth second curved surface 46 is scraped from the line 41 toward the tooth base on the other end side in the tooth width direction of the tooth 2 (see FIG. 11B), and the tooth width direction and the like of the tooth 2 from the third processing reference line 42. It is scraped off by a smooth third curved surface 47 toward the tooth tip on the end side (see FIG. 11C), and smoothly smoothed from the fourth processing reference line 43 toward the tooth base on one end side in the tooth width direction of the tooth 2.
  • Three-dimensional tooth surface modification is performed (see FIG.
  • the tooth 2 has a diamond-shaped tooth surface portion 11a (involute tooth profile shape) that is not subjected to three-dimensional tooth surface modification at the center portion of the tooth surface 11 surrounded by the first to fourth processing reference lines 40 to 43. (Tooth surface part) is left.
  • FIG. 12 sets the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and the rotation transmission error of the resin helical gear 1 according to the present embodiment.
  • FIG. 12B is a diagram showing a result of the one-tooth engagement test (second engagement test) in the tooth engagement state of FIG. 2B-2.
  • FIG. 12C is a diagram showing the results of the one-tooth engagement test (third engagement test) in the tooth engagement state of FIG. 2C-2.
  • the resin helical gear 1 according to the present embodiment is indicated as the product 2 of the present invention.
  • the horizontal axis represents the load torque (Nm)
  • the vertical axis represents the meshing primary component (sec) of the rotation transmission error.
  • the meshing primary component as a rotation transmission error is abbreviated as a rotation transmission error as appropriate.
  • the modification amount ⁇ of the tooth surface 11 in the product 2 of the present invention is the four positions of the tooth surface 11 (the tooth tip on one end side in the tooth width direction, the tooth root on one end side in the tooth width direction, and the tooth tip on the other end side in the tooth width direction). And the tooth base on the other end side in the tooth width direction) are the same numerical value (20 ⁇ m).
  • the single tooth meshing test is performed under the same conditions as the resin helical gear 1 according to the first embodiment except that the applied load torque is in the range of 0.1 Nm to 0.3 Nm. It was. That is, the resin helical gear 1 according to the present embodiment is used under conditions where a larger load torque (0.1 Nm to 0.3 Nm) acts than the resin helical gear 1 according to the first embodiment. Therefore, a one-tooth engagement test was performed within the range of the load torque acting at the time of use.
  • the product 2 of the present invention has a numerical value of the rotation transmission error smaller than that of the unmodified helical gear.
  • the product 2 of the present invention has a rotation transmission error smaller than that of an unmodified helical gear or a numerical value similar to that of an unmodified helical gear. It has become.
  • the rotation transmission error has decreased significantly compared with the unmodified helical gear.
  • the difference between the rotation transmission error of the product 2 of the present invention and the rotation transmission error of the unmodified helical gear increases as the load torque increases.
  • the product 2 of the present invention can always reduce the rotation transmission error as compared with the non-modified helical gear that is always used, regardless of the direction of misalignment.
  • Table 2 shown below shows the results of the one-tooth engagement test (first to third engagement test) of the product to be measured (present product 2, first to fourth comparative examples) with a load torque of 0.1 Nm to 0 .3 Nm range (see FIG. 12, FIG. 5 to FIG. 8).
  • a circle indicates a case where the rotation transmission error of the product to be measured is equal to or smaller than the rotation transmission error of the unmodified helical gear (good case).
  • x indicates a case where the rotation transmission error of the measurement target product is larger (bad) than the rotation transmission error of the unmodified helical gear.
  • FIG. 13 shows the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and the meshing primary component as a rotation transmission error of the product 2 of the present invention is set to one tooth. It is a figure which compares and shows the result measured by the surface meshing test, and the result measured by the one-tooth meshing test about the meshing primary component as a rotation transmission error of the product 1 of the present invention.
  • FIG. 13 (a) is a diagram showing the results of a one-tooth engagement test (first engagement test) in the tooth engagement state of FIG. 2 (a-2).
  • FIG. 13B is a diagram showing a result of the one-tooth engagement test (second engagement test) in the tooth engagement state of FIG. 2B-2.
  • FIG. 13 (c) is a diagram showing the results of a one-tooth engagement test (third engagement test) in the tooth engagement state of FIG. 2 (c-2).
  • the horizontal axis represents the load torque (Nm)
  • the vertical axis represents the meshing primary component (sec) of the rotation transmission error.
  • the meshing primary component as a rotation transmission error is abbreviated as a rotation transmission error as appropriate.
  • the product 2 of the present invention is a numerical value with a rotation transmission error smaller than that of the product 1 of the present invention within a load torque range of 0.1 Nm to 0.3 Nm. It has become.
  • the product 2 of the present invention has a rotation transmission error larger than that of the product 1 of the present invention within the load torque range of 0.1 Nm to 0.3 Nm. It is a small number.
  • the product 2 of the present invention has a rotation transmission error larger than that of the product 1 of the present invention within a load torque range of 0.15 Nm to 0.3 Nm. It has decreased significantly.
  • the difference between the rotation transmission error of the product 2 of the present invention and the rotation transmission error of the product 1 of the present invention increases as the load torque increases within the load torque range of 0.15 Nm to 0.3 Nm.
  • the product 2 of the present invention can reduce the rotation transmission error compared to the product 1 of the present invention at least in the range of the load torque of 0.15 Nm to 0.3 Nm regardless of the misalignment direction. .
  • FIG.14 (a) is a perspective view which shows the tooth
  • FIG. 14B is a first auxiliary diagram for explaining the shape of the tooth 2 in FIG.
  • FIG.14 (c) is a 2nd auxiliary
  • the tooth 2 of the resin helical gear 1 is formed by three-dimensionally modifying the tooth surface 11 of the tooth 2 of the involute tooth shape 2. That is, in this modification, the tooth surface 11 (one tooth surface of both tooth surfaces) used for meshing of the tooth 2 is the tooth tip side on one end side in the tooth width direction of the tooth 2 and the tooth width of the tooth 2.
  • a first processing reference line 50 that obliquely connects the tooth base side on the other end side in the direction along the tooth surface 11 (see FIG.
  • the tooth surface 11 is scraped from the first processing reference line 50 toward the tooth tip on the other end side in the tooth width direction of the tooth 2 with a smooth first curved surface 52, and from the first processing reference line 50 to the tooth 2. It is scraped off by a smooth second curved surface 53 toward the tooth base on one end side in the tooth width direction (see FIG. 14B), and from the second processing reference line 51 toward the tooth tip on one end side in the tooth width direction of the tooth 2. It is scraped off by the smooth third curved surface 54 and is also scraped off by the smooth fourth curved surface 55 from the second processing reference line 51 toward the tooth base on the other end side in the tooth width direction of the tooth 2 (FIG. 14 (c).
  • the tooth surface 11 of the resin helical gear 1 according to this modification as described above is a three-dimensional shape of the tooth surface 11 of the resin helical gear 1 according to the second embodiment shown in FIG.
  • the shape is such that the diamond-shaped tooth surface portion 11a (the tooth surface portion of the involute tooth profile shape) that is not subjected to the target tooth surface modification is eliminated.
  • the resin helical gear 1 according to this modification can obtain the same effects as those of the resin helical gear 1 according to the second embodiment.
  • the resin helical gear 1 according to the second embodiment is adapted to perform three-dimensional tooth surface modification on one tooth surface of both tooth surfaces, but is not limited thereto, and both tooth surfaces are provided. Three-dimensional tooth surface modification may be performed to reduce rotational transmission errors in both the forward and reverse directions when the gear shaft is misaligned.
  • the modification amount ⁇ of the tooth surface 11 is set at four locations (tooth tip on one end side in the tooth width direction, tooth on one end side in the tooth width direction).
  • Original, tooth tip on the other end side in the tooth width direction and tooth root on the other end side in the tooth width direction) is 20 ⁇ m, but this numerical value is not limited, and the modification amount ⁇ at each of the four positions is different.
  • a numerical value may be used, and the numerical value of the modification ⁇ can be set to an optimum value according to the use conditions.
  • FIG. 15A is a perspective view showing the teeth 2 of the resin helical gear 1 according to the third embodiment of the present invention when viewed obliquely from above.
  • FIG. 15B is a first auxiliary diagram for explaining the shape of the tooth 2 in FIG.
  • FIG. 15C is a second auxiliary diagram for explaining the shape of the tooth 2 in FIG.
  • the tooth 2 of the resin helical gear 1 is formed by performing three-dimensional tooth surface modification on the tooth surface 11 of the tooth 2 having an involute tooth shape. That is, in this embodiment, the tooth surface 11 (one tooth surface of both tooth surfaces) used for meshing of the teeth 2 is the tooth tip side of the tooth width direction one end side of the teeth 2 and the tooth width direction of the teeth. A first processing reference line 57 that diagonally connects the tooth base side of the other end side along the tooth surface 11 (see FIG.
  • the tooth tip side of the tooth width direction other end side of the tooth 2 and the tooth A second machining reference line 58 that obliquely connects the root side at one end in the tooth width direction along the tooth surface 11 is set (see FIG. 15C), and the first to second machining reference lines 57 to 58 is the standard for tooth surface modification.
  • the meshing contact line 44 obliquely moves the tooth surface 11 from the tooth tip side on one end side in the tooth width direction of the tooth 2 toward the tooth root side on the other end side in the tooth width direction of the tooth 2. It progresses across.
  • the tooth surface 11 is scraped off with a smooth first curved surface 60 from the first processing reference line 57 toward the tooth base on one end side in the tooth width direction of the tooth 2 (see FIG. 15B), and the second processing reference.
  • a smooth second curved surface 61 is scraped from the line 58 toward the tooth tip on one end side in the tooth width direction of the tooth 2, and toward the tooth base on the other end side in the tooth width direction of the tooth 2 from the second processing reference line 58.
  • Three-dimensional tooth surface modification is performed (see FIG. 15A) so as to be scraped off by the smooth third curved surface 62 (see FIG. 15C).
  • the tooth 2 has a portion on the tooth tip side of the second machining reference line 58 from the intersection 63 of the first machining reference line 57 and the second machining reference line 58 as a line on the tooth surface 11 of the involute tooth profile shape,
  • the first to third curved surfaces 60 to 62 constitute a tooth surface.
  • FIG. 16 shows the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and the rotation transmission error of the resin helical gear 1 according to this embodiment.
  • FIG. 16B is a diagram showing the result of the one-tooth engagement test (second engagement test) in the tooth engagement state of FIG. 2B-2.
  • FIG. 16C is a diagram showing the results of the one-tooth engagement test (third engagement test) in the tooth engagement state of FIG. 2C-2.
  • the resin helical gear 1 according to this embodiment is indicated as product 3 of the present invention.
  • the horizontal axis represents the load torque (Nm)
  • the vertical axis represents the meshing primary component (sec) of the rotation transmission error.
  • the meshing primary component as a rotation transmission error is abbreviated as a rotation transmission error as appropriate.
  • the tooth surface modification amount ⁇ in the product 3 of the present invention is three locations on the tooth surface (tooth tip on one end side in the tooth width direction, tooth root on one end side in the tooth width direction, and tooth root on the other end side in the tooth width direction). And the same numerical value (20 ⁇ m).
  • the single tooth meshing test is performed under the same conditions as the resin helical gear 1 according to the first embodiment except that the applied load torque is in the range of 0.1 Nm to 0.3 Nm. It was. That is, the resin helical gear 1 according to the present embodiment is used under conditions where a larger load torque (0.1 Nm to 0.3 Nm) acts than the resin helical gear 1 according to the first embodiment. Therefore, a one-tooth engagement test was performed within the range of the load torque acting at the time of use.
  • the product 3 of the present invention has a smaller numerical value of the rotation transmission error than the unmodified helical gear.
  • the product 3 of the present invention has a rotation transmission error smaller than that of an unmodified helical gear or a numerical value similar to that of an unmodified helical gear. It has become.
  • the product 3 of the present invention has an extremely small numerical value for rotation transmission error as compared with the result of the first meshing test.
  • the rotation transmission error is reducing significantly compared with an unmodified helical gear.
  • the difference between the rotation transmission error of the product 3 of the present invention and the rotation transmission error of the unmodified helical gear increases as the load torque increases.
  • the product 3 of the present invention can always reduce the rotation transmission error as compared with the non-modified helical gear that is always used, regardless of the direction of misalignment.
  • Table 3 shows the results of the one-tooth engagement test (first to third engagement test) of the product to be measured (the product 3 of the present invention, the first to fourth comparative examples) with a load torque of 0.1 Nm to 0 .3 Nm (see FIGS. 16, 5 to 8).
  • a circle indicates a case where the rotation transmission error of the product to be measured is equal to or smaller than the rotation transmission error of the unmodified helical gear (good case).
  • x indicates a case where the rotation transmission error of the measurement target product is larger (bad) than the rotation transmission error of the unmodified helical gear.
  • FIG. 17 sets the meshing state of the teeth shown in FIGS. 2 (a-2), (b-2), and (c-2), and the meshing primary component as a rotation transmission error of the product 3 of the present invention is set to one tooth. It is a figure which compares and shows the result measured by the surface meshing test, and the result measured by the one-tooth meshing test about the meshing primary component as a rotation transmission error of the product 1 of the present invention.
  • FIG. 17 (a) is a diagram showing the results of the one-tooth engagement test (first engagement test) in the tooth engagement state of FIG. 2 (a-2).
  • FIG. 17B is a diagram showing the result of the one-tooth engagement test (second engagement test) in the tooth engagement state of FIG. 2B-2.
  • FIG. 17 (c) is a diagram showing the results of a one-tooth engagement test (third engagement test) in the tooth engagement state of FIG. 2 (c-2).
  • the horizontal axis represents the load torque (Nm)
  • the vertical axis represents the meshing primary component (sec) of the rotation transmission error.
  • the meshing primary component as a rotation transmission error is abbreviated as a rotation transmission error as appropriate.
  • the product 3 of the present invention is a numerical value in which the rotation transmission error is smaller than that of the product 1 of the present invention when the load torque is in the range of 0.1 Nm to 0.3 Nm. It has become. Further, according to the result of the second meshing test shown in FIG. 17 (b), the product 3 of the present invention has a rotation transmission error larger than that of the product 1 of the present invention within the load torque range of 0.15 Nm to 0.3 Nm. It is a small number. Further, according to the result of the third meshing test shown in FIG.
  • the product 3 of the present invention has a rotation transmission error larger than that of the product 1 of the present invention within the load torque range of 0.15 Nm to 0.3 Nm. It has decreased significantly.
  • the difference between the rotation transmission error of the product 3 of the present invention and the rotation transmission error of the product 1 of the present invention increases as the load torque increases in the range of the load torque of 0.15 Nm to 0.3 Nm.
  • the product 3 of the present invention can reduce the rotation transmission error less than that of the product 1 of the present invention regardless of the misalignment direction at least within the range of the load torque of 0.15 Nm to 0.3 Nm. .
  • FIG. 18 (a) is a perspective view showing the teeth 2 of the resin helical gear 1 according to Modification 1 of the third embodiment of the present invention when viewed obliquely from above.
  • FIG. 18B is a first auxiliary diagram for explaining the shape of the tooth 2 in FIG.
  • FIG.18 (c) is a 2nd auxiliary
  • the tooth 2 of the resin helical gear 1 is formed by three-dimensionally modifying the tooth surface 11 of the tooth 2 of the involute tooth shape 2. That is, in this modification, the tooth surface 11 (one tooth surface of both tooth surfaces) used for meshing of the tooth 2 is the tooth tip side on one end side in the tooth width direction of the tooth 2 and the tooth width direction of the tooth.
  • a first processing reference line 64 that obliquely connects the tooth base side of the other end side along the tooth surface 11 (see FIG.
  • a second processing reference line 65 that obliquely connects the tooth base side at one end side in the tooth width direction along the tooth surface 11 (see FIG. 18C), and these first to second processing reference lines 64 are set.
  • the standard for tooth surface modification is ⁇ 65.
  • the tooth surface 11 is scraped off from the first processing reference line 64 with a smooth first curved surface 66 toward the tooth base on one end side in the tooth width direction of the tooth 2, and the tooth width of the tooth from the first processing reference line 64. It is scraped off by a smooth second curved surface 67 toward the tooth tip on the other end side in the direction (see FIG. 18B), and is directed from the second processing reference line 65 toward the tooth base on the other end side in the tooth width direction of the tooth 2. Three-dimensional tooth surface modification is performed (see FIG. 18A) so as to be scraped off by the smooth third curved surface 68 (see FIG. 18C).
  • the tooth surface 11 remains as a line on the tooth surface 11 of the involute tooth shape from the intersection 70 of the first processing reference line 64 and the second processing reference line 65 to the tooth tip side of the first processing reference line 64.
  • the first to third curved surfaces 66 to 68 constitute tooth surfaces.
  • the tooth tip on the other end side in the tooth width direction is modified by ⁇ by three-dimensional tooth surface modification, while one end in the tooth width direction.
  • the side tooth tip is not modified by three-dimensional tooth surface modification (see FIG. 18A).
  • the tooth surface 11 of the helical helical gear 1 according to the third embodiment shown in FIG. 15 (a) has a tooth tip on one end side in the tooth width direction modified by ⁇ by three-dimensional tooth surface modification.
  • the tooth tip on the other end side in the tooth width direction is not modified by three-dimensional tooth surface modification.
  • the tooth surface 11 of the resin helical gear 1 according to this modification is common in that only one side of the tooth tips on both ends in the width direction is modified.
  • the resin helical gear 1 according to this modification can obtain the same effect as the resin helical gear 1 according to the third embodiment.
  • the resin helical gear 1 according to the third embodiment is adapted to perform three-dimensional tooth surface modification on one tooth surface of both tooth surfaces, but is not limited to this, and both tooth surfaces are provided. Three-dimensional tooth surface modification may be performed to reduce rotational transmission errors in both the forward and reverse directions when the gear shaft is misaligned.
  • the amount of modification ⁇ of the tooth surface 11 is set at three locations (tooth tip on one end side in the tooth width direction, tooth on one end side in the tooth width direction).
  • the numerical value is not limited to this, and the modification amount ⁇ at each of the three positions may be a different numerical value. Can be set to an optimum value according to the use conditions.
  • FIG. 19A is a perspective view showing the teeth 2 of the resin helical gear 1 according to the fourth embodiment of the present invention when viewed obliquely from above.
  • FIG.19 (b) is a 1st auxiliary
  • FIG.19 (c) is a 2nd auxiliary
  • the tooth 2 of the resin helical gear 1 is formed by performing three-dimensional tooth surface modification on the tooth surface 11 of the tooth 2 having an involute tooth profile. That is, in this embodiment, the tooth surface 11 (one tooth surface of both tooth surfaces) used for meshing of the teeth 2 is the tooth tip side on one end side in the tooth width direction of the teeth 2 and the tooth width of the teeth 2.
  • a first processing reference line 71 obliquely connecting the tooth base side in the center in the direction along the tooth surface 11 (see FIG.
  • FIG. 19B the tooth tip side on the other end side in the tooth width direction of the tooth 2 and the tooth 2
  • the meshing contact line 44 obliquely moves the tooth surface 11 from the tooth tip side on one end side in the tooth width direction of the tooth 2 toward the root side on the other end side in the tooth width direction of the tooth 2. It progresses across.
  • the tooth surface 11 is scraped off with a smooth first curved surface 73 from the first processing reference line 71 toward the tooth base on one end side in the tooth width direction of the tooth 2 (see FIG. 19B).
  • Three-dimensional tooth surface modification is performed so that the second curved surface 74 is scraped away from the line 72 toward the tooth base on the other end side in the tooth width direction of the tooth 2 (see FIG. 19C). (See FIG. 19 (a)).
  • the tooth 2 of the resin helical gear 1 according to the present embodiment has a tooth surface in which a substantially triangular portion on the tooth tip side from the first machining reference line 71 and the second machining reference line 72 is an involute tooth profile.
  • the area of the tooth surface portion 11a of the involute tooth profile remaining as the portion 11a is larger than the area of the tooth surface portion 11a of the involute tooth profile shape of the tooth surface 11 of the resin helical gear 1 according to the first embodiment. It has become.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Thermal Sciences (AREA)
  • Gears, Cams (AREA)

Abstract

L'invention vise à procurer un engrenage hélicoïdal en résine qui a une bonne précision de transmission de rotation et qui peut réduire des erreurs de transmission de rotation provoquées par le mauvais alignement d'un arbre d'engrenage. À cet effet, selon l'invention, les éléments suivants sont établis : une première ligne de référence d'usinage (12), qui relie en diagonale le côté pointe de dent d'une dent (2) sur un côté d'extrémité dans la direction de la largeur de la dent au côté racine de dent de la dent (2) sur l'autre côté d'extrémité dans la direction de la largeur de la dent le long d'une surface de dent (11) ; et une seconde ligne de référence d'usinage (13), qui relie en diagonale le côté pointe de dent de la dent (2) sur l'autre côté d'extrémité dans la direction de la largeur de la dent au côté racine de dent de la dent (2) sur le premier côté d'extrémité dans la direction de la largeur de la dent le long de la surface de dent (11), Une modification de la surface de dent en trois dimensions est ensuite réalisée, de telle sorte que la surface de dent (11) est rasée en une première surface incurvée lisse (15) à partir de la première ligne de référence d'usinage (12) vers la racine de la dent sur le premier côté d'extrémité de la dent (2) dans la direction de la largeur de la dent et rasée en une seconde surface incurvée lisse (16) à partir de la seconde ligne de référence d'usinage (13) vers la racine de la dent sur l'autre côté d'extrémité de la dent (2) dans la direction de la largeur de la dent. En résultat, une forme de dent à développante demeure davantage vers le côté pointe de dent de la dent (2) que la première ligne de référence d'usinage (12) et la seconde ligne de référence d'usinage (13).
PCT/JP2015/082680 2014-12-05 2015-11-20 Engrenage hélicoïdal en résine WO2016088577A1 (fr)

Priority Applications (2)

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CN201580064092.2A CN107002852B (zh) 2014-12-05 2015-11-20 树脂制斜齿轮
US15/532,773 US10584784B2 (en) 2014-12-05 2015-11-20 Resin helical gear

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JP2014-246604 2014-12-05
JP2014246604 2014-12-05
JP2015-053136 2015-03-17
JP2015053136A JP6448423B2 (ja) 2014-12-05 2015-03-17 樹脂製はすば歯車

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019115181A1 (fr) * 2017-12-15 2019-06-20 Zf Friedrichshafen Ag Denture optimisée en termes de bruit

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DE2445104A1 (de) * 1974-03-07 1975-09-18 Maag Zahnraeder & Maschinen Ag Stirnrad mit von den evolventenflaechen abweichenden flanken
JPH1089442A (ja) * 1996-09-18 1998-04-07 Kawasaki Heavy Ind Ltd ３次元歯面修整はすば／やまば歯車
JP2006177415A (ja) * 2004-12-21 2006-07-06 Toyota Motor Corp 歯車の歯面形状の設計方法および歯車
JP2007120743A (ja) * 2005-09-28 2007-05-17 Enplas Corp 歯車及び歯車装置
EP1832370A1 (fr) * 2006-03-09 2007-09-12 Winergy AG Procédé de fabrication d'engrenages à développante de roues dentées
JP2008240793A (ja) * 2007-03-26 2008-10-09 Enplas Corp 樹脂製歯車
JP2008275060A (ja) * 2007-04-27 2008-11-13 Sumitomo Metal Ind Ltd 鉄道車両用歯車装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2445104A1 (de) * 1974-03-07 1975-09-18 Maag Zahnraeder & Maschinen Ag Stirnrad mit von den evolventenflaechen abweichenden flanken
JPH1089442A (ja) * 1996-09-18 1998-04-07 Kawasaki Heavy Ind Ltd ３次元歯面修整はすば／やまば歯車
JP2006177415A (ja) * 2004-12-21 2006-07-06 Toyota Motor Corp 歯車の歯面形状の設計方法および歯車
JP2007120743A (ja) * 2005-09-28 2007-05-17 Enplas Corp 歯車及び歯車装置
EP1832370A1 (fr) * 2006-03-09 2007-09-12 Winergy AG Procédé de fabrication d'engrenages à développante de roues dentées
JP2008240793A (ja) * 2007-03-26 2008-10-09 Enplas Corp 樹脂製歯車
JP2008275060A (ja) * 2007-04-27 2008-11-13 Sumitomo Metal Ind Ltd 鉄道車両用歯車装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019115181A1 (fr) * 2017-12-15 2019-06-20 Zf Friedrichshafen Ag Denture optimisée en termes de bruit

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