WO2008050379A1 - Engrenage et module d'entraînement d'engrenage - Google Patents

Engrenage et module d'entraînement d'engrenage Download PDF

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Publication number
WO2008050379A1
WO2008050379A1 PCT/JP2006/321012 JP2006321012W WO2008050379A1 WO 2008050379 A1 WO2008050379 A1 WO 2008050379A1 JP 2006321012 W JP2006321012 W JP 2006321012W WO 2008050379 A1 WO2008050379 A1 WO 2008050379A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
range
nitrogen
tooth
oil film
Prior art date
Application number
PCT/JP2006/321012
Other languages
English (en)
Japanese (ja)
Inventor
Masanori Satou
Yoshiyasu Nakano
Katsufumi Abe
Original Assignee
Ntn Corporation
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
Application filed by Ntn Corporation filed Critical Ntn Corporation
Priority to JP2008540810A priority Critical patent/JPWO2008050379A1/ja
Priority to PCT/JP2006/321012 priority patent/WO2008050379A1/fr
Publication of WO2008050379A1 publication Critical patent/WO2008050379A1/fr

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Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0463—Grease lubrication; Drop-feed lubrication
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/54—Surface roughness

Definitions

  • the present invention relates to a gear and a gear driving device, and can be applied to, for example, a gear and a gear driving device used in a power transmission unit or a gear pump of an automobile transmission.
  • Patent Document 1 discloses a gear in which countless dents are randomly provided on the tooth surface.
  • the average area of these micro-indentations is 35 to 150 111 2
  • the ratio of the micro-indentations to the surface is 10 to 40%
  • the average surface roughness with micro-indentations is RmaxO. 6 to 2.5 ⁇ m.
  • the parameter Sk of the surface roughness of the tooth surface with a small dent is set so that Sk ⁇ —1.6. This improves the ability to form an oil film on the surface and sufficiently forms an oil film between the tooth surfaces of the gear, thereby preventing damage caused by poor lubrication such as peeling from the surface of the gear and improving durability. ing.
  • Patent Document 1 Japanese Utility Model Publication No. 4 56254
  • An object of the present invention is to sufficiently form an oil film between the tooth surfaces of a gear rotating at high speed, to prevent occurrence of pitching, abrasion and scoring, and to improve durability by preventing temperature rise and wear. It is an object of the present invention to provide a gear and a gear driving device using such a gear.
  • the gear of the present invention has an infinite number of minute concave recesses on the tooth surface, and the area ratio of the recesses on the surface provided with the recesses is 35 to 75%. It is in the range of.
  • the oil film forming ability is improved by setting the area ratio of the indentation in the surface provided with the indentation in the tooth surface within the range of 35 to 75%. Therefore, long life can be obtained even under the condition of extremely thin oil film thickness under dilute lubrication.
  • Rqni is within the range of 0.13 ⁇ m ⁇ Rqni ⁇ 0.5 ⁇ m.
  • the parameter Rqni is the square root of the roughness center line force, the square root of the height deviation up to the roughness curve, integrated over the measured length interval, and averaged over that interval, also known as the root mean square roughness.
  • Rqni is obtained by numerical calculation of the cross-sectional curve and roughness curve force recorded on an enlarged scale, and is measured by moving the stylus of the roughness meter in the width and circumferential directions.
  • a nitrogen-enriched layer can be formed on the surface of the gear.
  • the nitrogen-enriched layer is a layer having an increased nitrogen content formed on the tooth surface, and can be formed by a process such as carbonitriding, nitriding, or nitriding.
  • the fatigue life can be greatly improved by forming the nitrogen-enriched layer and making the austenite grain size finer as the grain size number of the austenite grains in the nitrogen-enriched layer exceeds 10. Austenai When the grain size number is 10 or less, the fatigue life is not greatly improved. Therefore, the range is over 10 and usually 11 or more. The finer the austenite grain size, the better, but usually it is difficult to obtain a grain size number exceeding 13.
  • austenite grains appear when heated to a temperature above the transformation point during heat treatment, and when transformed, they transform to a different structure, but after transformation, traces of austenite grain boundaries remain, and the traces remain. It refers to a crystal grain based on
  • the nitrogen content in the nitrogen-enriched layer is preferably in the range of 0.1% to 0.7%. On the other hand, if the nitrogen content is less than 0.1%, the effect cannot be obtained, and the fatigue life is reduced particularly under the condition of contamination. If the nitrogen content is more than 0.7%, voids called voids will be formed, or the retained austenite will increase so much that the hardness will not be achieved, resulting in a short life.
  • the nitrogen content is the value at the surface layer of 50 m of the tooth surface, and can be measured by, for example, EPMA (wavelength dispersive X-ray microanalyzer).
  • the tooth surface becomes a minute rough surface and an oil film can be easily formed. Since the indentation becomes an oil reservoir, the oil film on the sliding surface can be formed reliably. As a result, the temperature rise can be reduced and the metal contact between the tooth surfaces of the meshing gears can be relaxed. Pitting, abrasion, and scoring can be achieved even in the high-speed rotation region. Can be prevented. Therefore, even if the oil film thickness is extremely thin under low viscosity and dilute lubrication, a long life of the gear and the gear driving device can be obtained. Furthermore, by improving the fatigue life of the surface layer of the toothed wheel, it is possible to obtain excellent cracking resistance and aging resistance.
  • Fig. 1 shows an example of a transmission used in an automobile.
  • An input shaft 2, a drive pion 3, and an output shaft 4 are arranged in series in a case 1, and a counter parallel to the output shaft 4 is provided.
  • Shaft 5 and reverse shaft 6 are arranged
  • a gear 7 group is attached to the drive pion 3 and each shaft 2, 4 and 5, and the input shaft 2 can be fitted by changing the meshing of each gear 7 group by the operation from the outside of the case 1. Change to the output shaft 4 or reverse and take it out!
  • the transmission includes a gear driving device having a driving gear driven by a driving force and a driven gear driven by meshing with the driving gear.
  • FIG. 2 shows a gear 7 constituting a part of the gear driving device.
  • the tooth surface 7a of this gear is a minute rough surface in which countless independent minute depressions are randomly formed.
  • This fine rough surface has an indentation area ratio of 35 to 75%.
  • the surface roughness parameter Rymax in the axial direction of the surface provided with the indentation is within the range of 1.3 ⁇ m ⁇ Rymax ⁇ 3.O / zm.
  • the surface roughness parameter Rqni in the axial direction of this surface is It is within the range of 0.13 ⁇ m ⁇ Rqni ⁇ 0.5 m.
  • a desired finished surface can be obtained by special barrel polishing, but is not limited thereto, and for example, a shot or the like may be used. .
  • the surface layer of the tooth surface 7a of the gear wheel 7 is formed with a nitrogen-enriched layer by a treatment such as carbonitriding, nitriding, or nitriding, and the grain size number of the austenite crystal grains in the nitrogen-enriched layer is 10 It is set to a range exceeding the number, for example, number 12.
  • the nitrogen content in the surface layer 50 m of the tooth surface 4a is set in the range of 0.1 to 0.7%.
  • FIG. 3 is a view showing the microstructure of the tooth surface of the gear, particularly austenite grains.
  • Fig. 3 (A) shows a gear having an austenite grain size of JIS standard grain number 12 (invention example), and
  • Fig. 3 (B) shows a gear having a grain size number 10 (comparative example).
  • FIGS. 4 (A) and 4 (B) show the austenite grain sizes illustrated in FIGS. 3 (A) and 3 (B).
  • the average particle size in Fig. 3 (A) was 5.6 m as a result of measurement by the intercept method.
  • the gear of the gear drive device of the present invention is provided with an infinite number of minute concave recesses, so that the tooth surface becomes a minute rough surface and an oil film is easily formed.
  • this dent becomes an oil reservoir, an oil film can be reliably formed on the sliding surface. Because of this, itching The metal contact between the tooth surfaces 7a of the mating gear 7 can be alleviated, and the temperature rise can be reduced, and the occurrence of pitching, abrasion and scoring can be prevented even in the high-speed rotation region, and the life can be extended. Can do.
  • by setting the area ratio of the depressions on the surface with the depressions within the range of 35 to 75%, it becomes possible to prevent oil film breakage even under lean lubrication, and even under extremely thin oil film conditions. Long life can be obtained.
  • This gear has a nitrogen-enriched layer on the surface layer, and the austenite grain size number in this nitrogen-enriched layer exceeds 10, so the austenite grain size becomes finer and the fatigue life is greatly improved. can do.
  • the nitrogen content in the nitrogen-enriched layer is less than 0.1%, the fatigue life under the contamination condition decreases, and conversely if more than 0.7%, voids called voids are formed.
  • the amount of retained austenite increases too much and the hardness is not obtained, resulting in a short life. For this reason, it is possible to extend the life of the gear by setting the nitrogen content within the range of 0.1% to 0.7%.
  • the gear of the present invention can obtain a long life even under the condition that the oil film thickness is extremely thin under low viscosity and lean lubrication, and the gear drive of the present invention using such a gear is used.
  • the device can have a long life. Furthermore, by improving the fatigue life of the surface layer, it is possible to obtain excellent crack strength and aging resistance.
  • the gear of the present invention is excellent in pitching resistance, abrasion resistance, and scoring resistance, and is therefore optimal as a gear 7 for an automobile transmission as shown in FIG.
  • two to three sets of planetary gear mechanisms are normally used for automatic transmissions (AT) for automobiles, and the reduction ratio varies by fastening the sun gear, carrier, and ring gear of these planetary gear mechanisms with a clutch. It has become. Therefore, it is preferable to apply the surface texture of the present invention to the sun gear, planetary pinion, ring gear and the like in such a planetary gear mechanism.
  • gear of the present invention can of course be used for various gear drive devices other than the automobile transmission.
  • the life of the gear was evaluated.
  • the tooth surface of the gear makes rolling contact and sliding contact with the tooth surface of the other side, and the contact is in a form according to the contact state between the race of the rolling bearing and the raceway. Therefore, it is considered that the life evaluation of gears can be evaluated by the life test evaluation of rolling bearings.
  • the present inventors conducted a life test of the rolling bearing under the conditions described below. When measuring the surface properties represented by these parameters for components such as rolling elements and rolling rings of rolling bearings, even one measured value can be relied on as a representative value. It is good to decide.
  • the measurement methods and conditions of the parameters Ryni, Rymax, Sk, and Rqni measured in this example are as follows.
  • the parameter Ryni is the average value of the maximum height for each reference length, that is, the reference length is extracted from the roughness curve in the direction of the average line, and the distance between the peak line and the valley bottom line of this extracted part. Is a value measured in the direction of the vertical magnification of the roughness curve (ISO 428 7: 1997).
  • the norm Sk indicates the degree of distortion (skewness) of the roughness curve (ISO 428 7: 1997), and is a standard statistic to know the asymmetry of the uneven distribution. In a symmetric distribution such as a Gaussian distribution, the Sk value is close to 0. When the convex and concave portions are deleted, the Sk value is negative, and in the opposite case, the Sk value is positive.
  • Measurement speed 0.30mm / s Measurement location: Roller center
  • Measuring device Surface roughness measuring instrument Surfcom 1400A (Tokyo Seimitsu Co., Ltd.)
  • the roller surface is enlarged, and the image power can be quantitatively measured by a commercially available image analysis system.
  • a surface texture inspection method and a surface texture inspection apparatus are used, stable and accurate measurement can be performed. In this method, light is irradiated onto an inspection surface having a curvature, the inspection surface is photographed with a camera, the brightness of the image of the inspection surface photographed with this camera is measured, and the bright portion of the measured brightness is measured.
  • a surface texture inspection method that inspects the surface texture of the surface to be inspected using a light-dark pattern formed with the contrast of the dark area.
  • the brightness distribution of the image to be measured is obtained by irradiating light in the direction of the optical axis of the camera.
  • shading luminance distribution
  • light is irradiated in the direction of the optical axis of the camera, and the brightness distribution of the measured image is the origin of the portion of the inspection surface corresponding to the position where this brightness distribution shows the peak value, and the symmetry axis of curvature. Approximate the one-dimensional luminance distribution along each orthogonal coordinate axis with an approximate function, and remove the luminance distribution of the image using these approximate functions.
  • the luminance of the measured image corresponding to each coordinate position is corrected, and the surface properties of the inspection surface are inspected with this corrected luminance pattern, thereby reducing shading.
  • Surface texture can be inspected with no light / dark pattern.
  • a single measured value can be relied on as a representative value. It is good to measure two places that face each other in the diameter direction.
  • the measurement conditions are as follows, for example.
  • Fig. 5 shows an example of a test rolling bearing.
  • This rolling bearing 10 is a needle roller bearing in which a needle roller 12 is incorporated in an outer ring 13 as a rolling element. It has come to support.
  • the following describes the results of a life test conducted on a variety of needle roller bearings with different surface finishes on the needle roller surface.
  • Dr 33 mm
  • inner diameter dr 25 mm
  • needle roller 12 diameter D 4 mm
  • length L 25.8 mm.
  • This is a bearing with a cage 15 using needle rollers. Five types of needle bearings with different surface roughness finishes were produced as test bearings.
  • bearing A (comparative example) with super-finish after grinding
  • bearing B (comparative example) with numerous indentations of small concave shapes randomly formed
  • bearing C (example)
  • bearing D (example)
  • bearing E (Example).
  • the test apparatus used is a radial load tester 16 as schematically shown in FIG. 7, in which test bearings 10 are mounted on both sides of the rotating shaft 17, and a test is performed by applying rotation and load.
  • the finish of the inner race (partner shaft) used in the test is RaO. 10 to 0.16 / z m of polished finish.
  • the water race (outer ring) is also common.
  • the test conditions are as follows.
  • Fig. 8 shows a list of characteristic values of the surface finish of each test bearing and the oil film parameter ⁇ .
  • the life ratio of each test bearing to the bearing A with no depression is 1.6 times for bearing B, 2.0 times for bearing C, 3.8 times for bearing D, and 4 for bearing E. It was 0 times.
  • Example 2 Next, a gear pitching test was performed using a spur gear fatigue tester shown in FIG. 9, and the pitching strength was evaluated.
  • the drive-side gear 31 (29 teeth) and the driven-side gear 32 (30 teeth) are attached to one side of each rotary shaft 33, 34, and the drive-side shaft 33 is not shown in the figure. It is driven by.
  • torque is loaded by a load lever 35 and a weight 36 attached to the shaft 33 on the drive side.
  • Two types of drive side gears 31 were prepared depending on whether or not the surface treatment according to the present invention was performed. The details of the test conditions are as follows.
  • Testing machine Spur gear fatigue testing machine
  • Drive-side gear Outer diameter 79 mm, Inner diameter 35 mm, Tooth width 8.2 mm, SCr420 (Carburizing), 29 teeth
  • Tonolek 186N'm (19kgf'm)
  • Lubricating oil temperature 80 ° C
  • Lubricating oil ATF oil
  • FIG. 10 (a) shows the result (comparative example) when surface treatment is applied to both the drive side and driven side gears
  • Fig. 10 (b) shows the drive side gear
  • FIG. 10 (c) shows the results (Example) when the tooth surface is treated so that the surface properties according to the present invention are satisfied.
  • FIG. 10 (c) shows the teeth of the drive side gear and the driven side gear.
  • the results (Examples) in the case of using the surface treated so as to satisfy the surface properties according to the present invention are shown on the surface. From these, it can be confirmed that the pitching life is improved more than 2 times in the case of Fig. 10 (b) and more than 3 times in the case of Fig. 10 (c) compared to the case of Fig. 10 (a). .
  • the nitrogen content and the foreign material life are in a substantially proportional relationship.
  • the comparative product 3 with a nitrogen content of 0.72 should have an upper limit of 0.7 for the nitrogen content in light of the extremely reduced lifespan of contamination.
  • the lower limit of the nitrogen content should be 0.1.
  • the austenite grain size is preferably a value exceeding 10.
  • FIG. 1 Partial cross-sectional view of an automobile transmission
  • FIG. 3 is a diagram showing the microstructure of gears, particularly austenite grains, where (A) is a gear according to an example of the present invention, and (B) is a conventional gear.
  • FIG. 4 (A) shows the austenite grain boundary illustrated in FIG. 3 (A), and (B) shows the austenite grain boundary illustrated in FIG. 3 (B).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)
  • General Details Of Gearings (AREA)

Abstract

L'invention concerne un engrenage et un module d'entraînement d'engrenage. Selon l'invention, la formation d'un film d'huile entre les surfaces des dents des engrenages tournant à vitesse élevée est satisfaisante, ce qui permet d'empêcher l'apparition de tangage, d'abrasion et de grippure ainsi que de prévenir toute augmentation de température et usure, et donc d'améliorer la durabilité. Cette invention a pour objet à un engrenage possédant une surface de dents pourvue d'un nombre très important de dépressions présentées dans une configuration aléatoire, concave et minuscule, le rapport de surface desdites dépressions dans la surface à dépressions étant compris entre 35 to 75%. Par conséquent, la surface à dents acquiert une meilleure aptitude à la formation de film d'huile, de manière que la durée de vie prolongée peut être assurée même dans des conditions où l'épaisseur du film d'huile est extrêmement mince lors d'une lubrification fine/à faible viscosité.
PCT/JP2006/321012 2006-10-23 2006-10-23 Engrenage et module d'entraînement d'engrenage WO2008050379A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2008540810A JPWO2008050379A1 (ja) 2006-10-23 2006-10-23 歯車および歯車駆動装置
PCT/JP2006/321012 WO2008050379A1 (fr) 2006-10-23 2006-10-23 Engrenage et module d'entraînement d'engrenage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2006/321012 WO2008050379A1 (fr) 2006-10-23 2006-10-23 Engrenage et module d'entraînement d'engrenage

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WO2008050379A1 true WO2008050379A1 (fr) 2008-05-02

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113108047A (zh) * 2021-04-21 2021-07-13 湖南工程学院 一种自动变速器齿轮副油膜厚度估算控制系统及方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0130008B2 (fr) * 1984-07-14 1989-06-15 Ntn Toyo Bearing Co Ltd
JPH0456254U (fr) * 1990-09-21 1992-05-14
JPH07242994A (ja) * 1994-03-09 1995-09-19 Daido Steel Co Ltd 歯面強度の優れた歯車用鋼，歯車および歯車の製造方法
JPH11230312A (ja) * 1998-02-13 1999-08-27 Nippon Steel Corp 高接触疲労寿命歯車及びその製造方法
JP2002031212A (ja) * 2000-07-17 2002-01-31 Koyo Seiko Co Ltd 転がり摺動部品
WO2005036003A1 (fr) * 2003-10-10 2005-04-21 Ntn Corporation Palier de roulement

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003065422A (ja) * 2001-08-29 2003-03-05 Koyo Seiko Co Ltd 歯車、減速歯車機構及び電動式パワーステアリング装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0130008B2 (fr) * 1984-07-14 1989-06-15 Ntn Toyo Bearing Co Ltd
JPH0456254U (fr) * 1990-09-21 1992-05-14
JPH07242994A (ja) * 1994-03-09 1995-09-19 Daido Steel Co Ltd 歯面強度の優れた歯車用鋼，歯車および歯車の製造方法
JPH11230312A (ja) * 1998-02-13 1999-08-27 Nippon Steel Corp 高接触疲労寿命歯車及びその製造方法
JP2002031212A (ja) * 2000-07-17 2002-01-31 Koyo Seiko Co Ltd 転がり摺動部品
WO2005036003A1 (fr) * 2003-10-10 2005-04-21 Ntn Corporation Palier de roulement

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113108047A (zh) * 2021-04-21 2021-07-13 湖南工程学院 一种自动变速器齿轮副油膜厚度估算控制系统及方法

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