WO2001002712A1 - Element coulissant et piston pour moteur thermique - Google Patents
Element coulissant et piston pour moteur thermique Download PDFInfo
- Publication number
- WO2001002712A1 WO2001002712A1 PCT/JP2000/004207 JP0004207W WO0102712A1 WO 2001002712 A1 WO2001002712 A1 WO 2001002712A1 JP 0004207 W JP0004207 W JP 0004207W WO 0102712 A1 WO0102712 A1 WO 0102712A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- sliding
- sliding member
- internal combustion
- combustion engine
- Prior art date
Links
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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
- F16J10/02—Cylinders designed to receive moving pistons or plungers
- F16J10/04—Running faces; Liners
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
-
- 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
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/14—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means
- F16N7/16—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means the oil being carried up by a lifting device
Definitions
- the present invention relates to a sliding member capable of reducing the sliding resistance of the sliding member and effectively preventing generation of abnormal noise by interposing sufficient lubricating oil on the sliding surfaces of the sliding members sliding with each other.
- the present invention also relates to a piston for an internal combustion engine capable of retaining a sufficient lubricating oil on a sliding surface with a sleeve.
- techniques for reducing the sliding resistance of a sliding member include adding a silicon-fluorine compound to the material of the sliding member or performing a coating made of a material such as molybdenum-fluorine resin. I have. However, the former has no remarkable effect on the reduction of sliding resistance, and the latter has a problem that the coating is peeled off or worn.
- a piston for an internal combustion engine (hereinafter simply referred to as a piston)
- a part of the explosion pressure in the combustion chamber is received by a piston ring sliding on the sleeve, and a skirt provided below the piston ring is used as the sleeve.
- the posture of the piston is maintained by contact. Therefore, if the contact between the skirt and the sleeve is not made well, the sliding resistance will increase and fuel consumption will decrease, and in some cases, abnormal noise will be generated due to the contact between the piston and the sleeve. I do.
- Japanese Utility Model Laid-Open No. 52-16464 and Japanese Utility Model Laid-open No. 57-1933941 have a dimple with sandblasting and shot peening on the piston force. However, it is known that this method is not effective in preventing the generation of abnormal noise.
- the present invention is based on the premise that the sliding member will undergo initial wear, and by making the surface properties of the sliding member after initial wear ideal, smooth sliding after initial wear is achieved. It is an object of the present invention to provide a sliding member that can effectively prevent generation of abnormal noise.
- the clearance between the skirt portion of the piston and the sleeve can be reduced, whereby the posture of the piston can be stabilized, and It is an object of the present invention to provide a piston capable of preventing generation of noise and reducing noise and vibration.
- Another object of the present invention is to reduce the sliding resistance at an early stage by causing the initial wear to occur in a short period of time at the beginning of operation. Disclosure of the invention
- the sliding member of the present invention is provided with a convex portion extending in a direction crossing the sliding direction on at least one of the sliding surfaces of the sliding members sliding with each other. It is characterized by providing fine dimples. It is desirable that the direction in which the protrusion extends is orthogonal or substantially orthogonal to the sliding direction.
- the piston for an internal combustion engine of the present invention is characterized in that at least a skirt portion on a side surface of a piston body is provided with a convex portion extending in a circumferential direction, and fine dimples are provided on the surface of the convex portion.
- FIG. 1A shows the surface of the scar portion of the biston without dimples in combigraphic graphics, and shows a convex portion extending in the circumferential direction of the piston body.
- FIG. 1A shows a state after the outer periphery of the piston main body is machined, and the convex portion is formed between concave portions having a substantially arc-shaped cross section.
- the machine Mechanical machining can be performed by relatively moving the biston body in the axial direction while cutting the outer periphery of the biston body using a cutting tool or the like. In this case, the convex portion forms a spiral shape in the axial direction.
- FIGS. 2A and 2B show the cross-sectional shapes of the projections shown in FIGS. 1A and 1B.
- FIG. 2A shows the state after machining
- FIG. 2B shows the state after initial wear.
- the edge formed on the edge of the sliding surface after the initial wear acts like a sneak-back, and there are places where lubricating oil is not supplied to the sliding surface. In this case, the temperature at that location rises, causing abnormal noise.
- FIG. 3A is a diagram showing the surface of the skirt portion of the piston in the present invention in a combigraphic graphic, and shows a convex portion extending in the circumferential direction of the body of the piston, and a convex portion of the convex portion. This shows fine dimples provided on the surface.
- the tip of the convex portion is worn away and becomes substantially trapezoidal as shown in FIG. 3B. At the edge of the sliding contact surface of this trapezoidal portion, an inlet B formed by dimples appears.
- FIGS. 5A and 5B show the surface of the piston body that has just been machined.
- the surface of the piston body that has just been machined has microscopic V-shaped grooves extending in the circumferential direction.
- the lubricating oil is more likely to collect at the bottom of the groove than at the sharp tip due to capillary action, so that an oil film is not easily formed and the sliding resistance is large.
- FIG. 5B shows an example of a dimple in the present invention.
- the dimple D becomes an oil pool and holds the oil ball O. Therefore, even if surface pressure is applied to this surface, the oil film S is formed. It is retained, and the increase of the sliding dam is prevented.
- the lubricating oil is held in each of the fine dimples as described above, and the lubricating oil is easily supplied from the inlet B to the sliding surface by the vertical movement of the piston. Therefore, after the initial wear, the piston has adjusted to the sleeve Thereafter, lubricating oil is supplied to the sliding surface to form an oil film, which lubricates the sliding surface and prevents the generation of oil.
- FIGS. 4A and 4B show the cross-sectional shapes of the projections shown in FIGS. 3A and 3B.
- FIG. 4A shows the state before the initial wear
- FIG. 4B shows the state after the initial wear.
- the protruding parts are processed by dimples, so initial wear occurs rapidly.
- the tip of the protrusion provided along the circumferential direction of the skirt which is the sliding surface with the sleeve, is worn down to a stable surface pressure when it slides. This is because the extra tip of the projection is removed to secure a corresponding area that can withstand the contact pressure during sliding. The removed tip stays in the lubricating oil as wear particles.
- the projection has a substantially trapezoidal shape when viewed in a cross section along the sliding direction.
- the dimples must be of a suitable size to achieve the above-mentioned effects. If the dimples are too small, the ability to retain the lubricating oil will be insufficient, and the size of the inlet will be small, and the effect of drawing the lubricating oil to the sliding surface will be insufficient. On the other hand, when the dimple is too large, the shape of the convex portion is greatly deformed, and the effect of providing the convex portion is lost. Dimples can be formed by shot peening. In this case, the size of the dimple is limited by the dimple size limitation described above. The average depth of the impulse is preferably 0.6 to 1.8 zm.
- FIGS. 6A and 6B show the cross-sectional shapes of the protrusions before initial wear.
- FIG. 6A illustrates an example in which the concave portion has a substantially arc-shaped cross section.
- the convex portion has a substantially arc-shaped cross section (FIG. 6A).
- B) or a structure in which a concave portion and a convex portion are continuous in a wavy shape when viewed in cross section FIG. 6C
- the cross section of the concave and convex portions may be trapezoidal (FIG. 6D) or triangular (FIG. 6E).
- the interval P between the convex portions is preferably 200 to 400 im, and more preferably 250 to 300 m.
- the height H, from the bottom of the concave portion to the tip of the convex portion before the initial wear, is preferably 7 to 15 im, more preferably 8 to 12 m.
- the average particle size of the shot is desirably 20 to 60 m, and the particle size is preferably 20 / m or more.
- Et al is, the air pressure during the shot projection in Shottopi-learning is from 1.5 to 5. It is desirable that 0 k gZ cm 2.
- the dimple can be provided only on the surface of the convex portion, but is preferably provided on the entire surface including the concave portion.
- the grooves and lands of the piston ring are provided with the same protrusions and dimples as above to generate abnormal noise at the groove and the piston ring and at the land and sleeve. Can be prevented from occurring.
- the sliding member of the present invention is not limited to the piston as described above, but can be applied to any members that slide with each other.
- the present invention can be applied to reciprocating sliding parts and rotary sliding parts such as piston pins, sliding metals for internal combustion engines, camshaft holders, and the like.
- a solid lubricant such as molybdenum disulfide or a fluororesin can be provided on the surface of the sliding member in advance by surface treatment such as coating, impregnation or diffusion, or after performing shot peening.
- FIG. 1A is an enlarged perspective view of a surface of a piston having no dimple, showing a state before initial wear
- FIG. 1B is a view showing a state after initial wear.
- FIG. 2A is a view showing a cross section of the surface of the biston having no dimple, showing a state before the initial wear
- FIG. 2B is a view showing a state after the initial wear
- FIG. 3A is an enlarged perspective view of the surface of the piston of the present invention, showing a state before initial wear
- FIG. 3B is a view showing a state after initial wear.
- FIG. 4A is a view showing a cross section of the surface of the biston of the present invention, showing a state before the initial wear
- FIG. 4B is a view showing a state after the initial wear.
- FIG. 5A is a diagram schematically showing a cross section of a conventional piston
- FIG. 5B is a diagram schematically showing a cross section of a biston of the present invention
- FIG. 5C is a dimple holding an oil ball. It is a figure showing a state.
- FIG. 6A and 6B are cross-sectional views showing a convex portion of a piston before initial wear
- FIG. 6A is a diagram showing a concave portion having a substantially circular arc cross-section
- FIG. 6B is a diagram showing FIG.
- FIG. 4 is a view showing a projection having a substantially arc-shaped cross section in reverse.
- FIGS. 6C to 6E are cross-sectional views showing the convex portion before the initial wear of the piston
- FIG. 6C is a diagram showing that the concave portion and the convex portion are continuous in a cross-sectional view
- FIG. 6D is a diagram showing a cross section of a concave portion and a convex portion having a trapezoidal shape
- FIG. 6E is a diagram showing a convex portion and a concave portion having a triangular shape.
- FIG. 7 is a diagram showing a relationship between a projection pressure and an average dimple depth in the example.
- FIG. 8 is a diagram showing a relationship between a running-in operation time and a reduction index in the example.
- FIG. 9 is a diagram showing the relationship between the average dimple depth and the sliding resistance reduction rate in the example.
- FIG. 10 is a diagram showing the relationship between the projection pressure and the sliding resistance reduction rate in the example.
- FIG. 11 is a diagram showing the relationship between the pressing load of the sample and the coefficient of friction in the example. It is. BEST MODE FOR CARRYING OUT THE INVENTION
- Pistons of general shape and size were made.
- a protrusion (streak) with a cross-sectional shape as shown in Fig. 6A is formed on the outer circumference of the piston, and the interval between the protrusions is about 250 m, and the height of the protrusions is about 10 m. did.
- the piston was attached to the center of the turntable, and glass beads having an average particle size of 40 m were projected on the side of the piston by compressed air while rotating the turntable. Then, a plurality of samples were prepared by changing the projection pressure from 1.5 kg Z cm 2 to 5.0 kg Z cm 2 .
- the surface roughness Ra of each sample was measured, and the value of Ra was taken as the average depth.
- Figure 7 shows the results. As can be seen from FIG. 7, the depth of the dimple increases as the projection pressure of shot beaning increases.
- Fig. 8 shows the reduction index at the start of operation as 1 and the reduction index with time. In FIG. 8, a reduction index of 0.9 indicates that the sliding resistance was reduced by 10%.
- a piston having the cross-sectional shape shown in FIG. 6A without shot peening was used as a comparative example, and the same running-in operation was performed. The results are also shown in FIG.
- the reduction index decreases instantaneously from 1 to 0.94, and thereafter gradually decreases.
- the initial decrease of the reduction index is slower than that of the example of the present invention, and thereafter, the reduction index maintains a higher level than the example of the present invention. Comparing the reduction indexes at the end of the running-in operation, it was confirmed that the present invention example had a lower reduction index by 2.2% than the comparative example. D. Sliding test
- the side surface of the sample of the above example was pressed against a plate material simulating a sleeve, and the sample was reciprocated with a stroke of 50 mm. At that time, lubricating oil was dropped on the surface of the plate and the pressing load was increased stepwise. The frictional resistance at that time was measured in real time, and the frictional resistance was integrated over time to determine the average frictional resistance per unit time.
- the same sliding test was performed on the sample of the comparative example used in the above-mentioned running-in operation. When the average friction resistance of the comparative example was set to 1, the average friction resistance of the example was calculated, and the sliding resistance reduction rate (%) with respect to the comparative example was calculated.
- Fig. 9 shows the relationship between the average dimple depth and the sliding resistance reduction rate. From FIG. 9, it can be seen that the sliding resistance reduction rate is high when the average dimple depth is 0.6 to 1.8.
- FIG. 9 the relationship shown in FIG. 9 is redrawn into the relationship between the shot peening projection pressure and the sliding resistance reduction rate, and is shown in FIG. In Fig. 10, plots were made for projection pressures of 2.5 to 4.5 kcm 2 , but the curves applied to these plots were extended and enclosed with dashed lines. As a result, it is estimated that the sliding resistance reduction rate is high when the projection pressure is 1.5 to 5.0 kg O cm Z cm 2 .
- the convex portion extending in the circumferential direction is provided, and fine dimples are provided on the surface of the convex portion, the dimple holds the lubricating oil, Lubricating oil is easily drawn out from the inlet formed by the dimples in the running-in operation, so that abnormal noise can be prevented and the sliding resistance after the running-in operation can be reduced.
- the clearance between the skirt and the sleeve of the piston can be reduced, the posture of the piston can be stabilized, and the noise and vibration can be reduced by preventing the piston from hitting. Can be.
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/763,612 US6523456B1 (en) | 1999-07-05 | 2000-06-27 | Sliding members and piston for internal combustion engine |
EP00940850A EP1111225B1 (en) | 1999-07-05 | 2000-06-27 | Sliding member and piston for internal combustion engine |
NZ509735A NZ509735A (en) | 1999-07-05 | 2000-06-27 | Sliding member and piston for internal combustion engine |
CA002341723A CA2341723C (en) | 1999-07-05 | 2000-06-27 | Sliding member and piston for internal combustion engine |
BR0007005-0A BR0007005A (pt) | 1999-07-05 | 2000-06-27 | Elementos corrediços e pistão para motores de combustão interna |
DE60032720T DE60032720T2 (de) | 1999-07-05 | 2000-06-27 | Gleitelement und kolben für brennkraftmaschine |
JP2001507922A JP3897238B2 (ja) | 1999-07-05 | 2000-06-27 | 摺動部材および内燃機関用ピストン |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19106699 | 1999-07-05 | ||
JP11/191066 | 1999-07-05 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001002712A1 true WO2001002712A1 (fr) | 2001-01-11 |
Family
ID=16268318
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2000/004207 WO2001002712A1 (fr) | 1999-07-05 | 2000-06-27 | Element coulissant et piston pour moteur thermique |
Country Status (13)
Country | Link |
---|---|
US (1) | US6523456B1 (ja) |
EP (1) | EP1111225B1 (ja) |
JP (1) | JP3897238B2 (ja) |
CN (1) | CN1175178C (ja) |
BR (1) | BR0007005A (ja) |
CA (1) | CA2341723C (ja) |
DE (1) | DE60032720T2 (ja) |
ID (1) | ID28721A (ja) |
MY (1) | MY123377A (ja) |
NZ (1) | NZ509735A (ja) |
TW (1) | TW444101B (ja) |
WO (1) | WO2001002712A1 (ja) |
ZA (1) | ZA200101258B (ja) |
Cited By (3)
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WO2006077682A1 (ja) * | 2005-01-18 | 2006-07-27 | Nsk Ltd. | 転動装置 |
US7287459B2 (en) | 2004-12-02 | 2007-10-30 | Honda Motor Co., Ltd. | Piston for internal combustion engine |
WO2010115010A2 (en) * | 2009-04-01 | 2010-10-07 | Purdue Research Foundation | Positive displacement machine piston with wavy surface form |
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JP3555844B2 (ja) | 1999-04-09 | 2004-08-18 | 三宅 正二郎 | 摺動部材およびその製造方法 |
GB2367522B (en) * | 2000-10-07 | 2004-04-28 | Federal Mogul Bradford Ltd | Engine piston and manufacture thereof |
US6739238B2 (en) * | 2000-11-20 | 2004-05-25 | Nissan Motor Co., Ltd. | Sliding structure for a reciprocating internal combustion engine and a reciprocating internal combustion engine using the sliding structure |
JP2003184883A (ja) | 2001-12-20 | 2003-07-03 | Nissan Motor Co Ltd | 軸受摺動部材 |
JP3555891B2 (ja) * | 2002-02-22 | 2004-08-18 | 新日本石油株式会社 | 低摩擦摺動材料及びこれに用いる潤滑油組成物 |
US6969198B2 (en) * | 2002-11-06 | 2005-11-29 | Nissan Motor Co., Ltd. | Low-friction sliding mechanism |
JP3891433B2 (ja) * | 2003-04-15 | 2007-03-14 | 日産自動車株式会社 | 燃料噴射弁 |
EP1479946B1 (en) * | 2003-05-23 | 2012-12-19 | Nissan Motor Co., Ltd. | Piston for internal combustion engine |
JP2005008851A (ja) * | 2003-05-29 | 2005-01-13 | Nissan Motor Co Ltd | 硬質炭素薄膜付き機械加工工具用切削油及び硬質炭素薄膜付き機械加工工具 |
JP4863152B2 (ja) * | 2003-07-31 | 2012-01-25 | 日産自動車株式会社 | 歯車 |
WO2005014761A2 (ja) * | 2003-08-06 | 2005-02-17 | Nissan Motor Co., Ltd. | 低摩擦摺動機構、低摩擦剤組成物及び摩擦低減方法 |
JP4973971B2 (ja) * | 2003-08-08 | 2012-07-11 | 日産自動車株式会社 | 摺動部材 |
JP4117553B2 (ja) * | 2003-08-13 | 2008-07-16 | 日産自動車株式会社 | チェーン駆動装置 |
US7771821B2 (en) * | 2003-08-21 | 2010-08-10 | Nissan Motor Co., Ltd. | Low-friction sliding member and low-friction sliding mechanism using same |
EP1508611B1 (en) | 2003-08-22 | 2019-04-17 | Nissan Motor Co., Ltd. | Transmission comprising low-friction sliding members and transmission oil therefor |
DE10340990A1 (de) * | 2003-09-05 | 2005-04-28 | Ks Kolbenschmidt Gmbh | Feinbearbeitete Oberfläche der Bolzenlöcher eines Kolbens |
US20070134468A1 (en) * | 2004-07-14 | 2007-06-14 | Buehler Jane E | Enhanced friction reducing surface and method of making the same |
US7687112B2 (en) * | 2004-07-14 | 2010-03-30 | Kinetitec Corporation | Surface for reduced friction and wear and method of making the same |
JP4358801B2 (ja) * | 2005-08-08 | 2009-11-04 | 大同メタル工業株式会社 | 内燃機関用すべり軸受 |
US20080248214A1 (en) * | 2007-04-09 | 2008-10-09 | Xueyuan Nie | Method of forming an oxide coating with dimples on its surface |
JP5916732B2 (ja) * | 2010-09-20 | 2016-05-11 | シージーン アイエヌシー | 単一標識固定化プローブ及びエキソ核酸切断活性を利用した固相におけるターゲット核酸配列検出 |
CN104169599B (zh) * | 2012-03-27 | 2015-08-26 | 千住金属工业株式会社 | 滑动构件 |
CN104755199B (zh) * | 2012-10-25 | 2017-09-26 | 千住金属工业株式会社 | 滑动构件以及滑动构件的制造方法 |
JP5713074B2 (ja) * | 2013-09-27 | 2015-05-07 | 千住金属工業株式会社 | 摺動部材 |
EP3184462A1 (en) * | 2015-12-23 | 2017-06-28 | Sulzer Mixpac AG | Cartridge with reduced friction |
JP6890611B2 (ja) * | 2016-11-18 | 2021-06-18 | イーグル工業株式会社 | 摺動部材 |
CN114320653B (zh) * | 2022-03-03 | 2022-06-10 | 潍柴动力股份有限公司 | 活塞、活塞加工方法及用于活塞的喷射工装 |
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2000
- 2000-06-22 MY MYPI20002815 patent/MY123377A/en unknown
- 2000-06-27 CA CA002341723A patent/CA2341723C/en not_active Expired - Fee Related
- 2000-06-27 JP JP2001507922A patent/JP3897238B2/ja not_active Expired - Fee Related
- 2000-06-27 NZ NZ509735A patent/NZ509735A/en unknown
- 2000-06-27 ID IDW20010761A patent/ID28721A/id unknown
- 2000-06-27 DE DE60032720T patent/DE60032720T2/de not_active Expired - Lifetime
- 2000-06-27 WO PCT/JP2000/004207 patent/WO2001002712A1/ja active IP Right Grant
- 2000-06-27 BR BR0007005-0A patent/BR0007005A/pt not_active Application Discontinuation
- 2000-06-27 US US09/763,612 patent/US6523456B1/en not_active Expired - Lifetime
- 2000-06-27 EP EP00940850A patent/EP1111225B1/en not_active Expired - Lifetime
- 2000-06-27 CN CNB008012768A patent/CN1175178C/zh not_active Expired - Fee Related
- 2000-07-03 TW TW089113137A patent/TW444101B/zh not_active IP Right Cessation
-
2001
- 2001-02-14 ZA ZA200101258A patent/ZA200101258B/en unknown
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Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7287459B2 (en) | 2004-12-02 | 2007-10-30 | Honda Motor Co., Ltd. | Piston for internal combustion engine |
WO2006077682A1 (ja) * | 2005-01-18 | 2006-07-27 | Nsk Ltd. | 転動装置 |
JPWO2006077682A1 (ja) * | 2005-01-18 | 2008-06-19 | 日本精工株式会社 | 転動装置 |
US7811002B2 (en) | 2005-01-18 | 2010-10-12 | Nsk, Ltd. | Rolling device |
JP4665905B2 (ja) * | 2005-01-18 | 2011-04-06 | 日本精工株式会社 | 転動装置の製造方法 |
WO2010115010A2 (en) * | 2009-04-01 | 2010-10-07 | Purdue Research Foundation | Positive displacement machine piston with wavy surface form |
WO2010115010A3 (en) * | 2009-04-01 | 2011-01-13 | Purdue Research Foundation | Positive displacement machine piston with wavy surface form |
KR101350110B1 (ko) | 2009-04-01 | 2014-01-09 | 퍼듀 리서치 파운데이션 | 파형 표면 형태를 갖는 포지티브 디스플레이스먼트 기계 피스톤 |
Also Published As
Publication number | Publication date |
---|---|
ID28721A (id) | 2001-06-28 |
CA2341723A1 (en) | 2001-01-11 |
US6523456B1 (en) | 2003-02-25 |
DE60032720D1 (de) | 2007-02-15 |
EP1111225A4 (en) | 2006-01-18 |
BR0007005A (pt) | 2001-06-19 |
TW444101B (en) | 2001-07-01 |
ZA200101258B (en) | 2002-07-18 |
MY123377A (en) | 2006-05-31 |
CN1316035A (zh) | 2001-10-03 |
EP1111225A1 (en) | 2001-06-27 |
NZ509735A (en) | 2003-12-19 |
EP1111225B1 (en) | 2007-01-03 |
JP3897238B2 (ja) | 2007-03-22 |
CN1175178C (zh) | 2004-11-10 |
CA2341723C (en) | 2006-02-07 |
DE60032720T2 (de) | 2007-04-26 |
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