CN1239195A - Bearing device - Google Patents

Bearing device Download PDF

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Publication number
CN1239195A
CN1239195A CN99108369A CN99108369A CN1239195A CN 1239195 A CN1239195 A CN 1239195A CN 99108369 A CN99108369 A CN 99108369A CN 99108369 A CN99108369 A CN 99108369A CN 1239195 A CN1239195 A CN 1239195A
Authority
CN
China
Prior art keywords
bearing
oilhole
hazardous area
gap
section
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN99108369A
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Chinese (zh)
Inventor
尼尔斯·K·鲍－马森
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN B&W Diesel AS
Original Assignee
MAN B&W Diesel AS
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 MAN B&W Diesel AS filed Critical MAN B&W Diesel AS
Publication of CN1239195A publication Critical patent/CN1239195A/en
Pending legal-status Critical Current

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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
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings
    • 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
    • F01M2001/086—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating gudgeon pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves

Abstract

A crankshaft bearing of large scale diesel engine has a bearing liner (3) making a wedge shape reduced gap (5) with a slide friction surface of a journal (4), the position of the gap varies periodically with load and the angular velocity of the gap is equal to the angular velocity of the outer load. Lubricating oil is supplied to the gap through lubricating oil holes (11, 13, 12) on the bearing liner. There is at least one lubricating oil hole (12) in the region of the danger zone in which the angular velocity of the gap is about half that of the journal (4), the non-groove cross section of the said oil hole is smaller than a cross section of a groove equals to the diameter of the cross section of the hole.

Description

Bearing means
The present invention relates to a kind of size and Orientation that bears by the round bearing device of the outer load of cycle variation and especially a kind of crankshaft bearing of large-scale diesel engine, it has the bearing shell of the affiliated axle journal of a suit, bearing shell sliding friction surface and axle journal sliding friction surface define one and are the gap that wedge shape narrows down to supporting region always, interstitial site is with the load period variation, angle of clearance speed approximates external load angular velocity, gives the gap supplying lubricating oil by the oilhole of bearing shell side.
In the bearing structure that the load direction vector remains unchanged, that is to say that in the changeless bearing structure in gap, lubricant oil is passed to the gap in large quantities from rotating journal, thereby maintain the lubricating film that one deck can carry.But under the situation of crankshaft bearing, rule of thumb, the situation of the oily prompt drop in the gap that in certain outer regions, occurred flowing through to zero.Outside journal angle speed approximates during the twice of load angle speed, such situation has just appearred.In this case, lack subsequently fresh oil supply.As a result, axle journal goes out to remain more close bearing shell under the oil condition in side pressure.Because it can not be a fresh oil and can only be the old oil that remains, so therefore oil be heated strongly.The result is that oil viscosity is little, and this has impelled again oil is extruded from the side.Here, the phenomenon that the bearing material local superheating may occur and wear and tear fast.
For overcoming this defective, the past is provided with in adventurous side face district and axially passes oil cavity whole bearing width and that link to each other with the lubricant oil supply line.These oil ducts have guaranteed the fresh oil supply, but they have interrupted the bearing shell sliding friction surface on whole width and have therefore caused bearing surface to dwindle greatly.Need bigger bearing width so that the fluid pressure that acceptable pressure can be accepted occurs here.But this causes the huger structure of volume ratio, and people need compact structure usually.This needs are particularly useful for modern large-scale diesel engine.
Based on this, the objective of the invention is to utilize simple measures with low cost to improve the bearing means of the above-mentioned type, thereby not only can obtain compact structure, and can obtain permanent working life.
According to the present invention, above-mentioned purpose is so to realize, promptly be provided with at least one oilhole in angle of clearance speed approximates half hazardous area of journal angle speed, the non-flute profile aperture cross section of oilhole equals the cross section of the groove of the clean diameter of aperture cross section less than its width.
Utilize such measure to eliminate the problems referred to above.Can give this hazardous area supply abundant new oil in the oilhole in hazardous area by attaching troops to a unit.Keep away in stage of above-mentioned oilhole at the axle journal of motion and to have imported a large amount of new oils, thereby flush out old hot lubricant oil reliably and obtained the lubricating film that one deck can carry.Be arranged on each oilhole in the hazardous area affect axle journal near the time fluid pressure that produces.Because the aperture cross section of above-mentioned oilhole is smaller and sliding friction surface is not interrupted as yet fully, so this influence is smaller.Formed fluid pressure here remains in the tolerance interval.Measure of the present invention can obtain oil pressure and lubricated aspect all gratifying compromise proposal.
The favourable design of above-mentioned measure and suitably improvement have been provided in the dependent claims.Being arranged on each oilhole in the hazardous area, to be designed to the less hole of diameter simply be suitable.This has not only obtained simple workability, and causes especially little sliding friction surface loss.
Another adequate measure is, is provided with many grease channels that are arranged in the hazardous area in, can be arranged in the recessed road of fuel feeding in the back of bearing district to these oilhole supplying lubricating oils by at least one.Can advantageously distribute these oilholes so that obtain to infeed the well distributed of fresh oil.In addition, for further improving the distribution of lubricant oil, be provided with the little oil duct that leaves the endoporus limit.But can save this measure usually.What can imagine equally is for improving bearing shell stability, to be equipped with an independently recessed road of fuel feeding for each oilhole.
In the crankshaft bearing of large-scale diesel engine, the oilhole that is arranged in the hazardous area suitably is arranged in the angular region away from 30 °～60 ° of bearing shell Lower Half ends forward on axle journal turns to.Realized thus described oilhole be positioned at one its be arranged in angular region after the zone that the highest bearing pressure estimate to occur, this advantageously causes the fluid pressure of formation to remain an acceptable value.
Another favourable measure is to be provided with one at least at the lubricating oil bath near the bearing shell next door in the hazardous area.Because journal motion, so produced pumping action when opening in the gap, this causes and sucks fresh oil and help lubricant oil supply in this hazardous area from above-mentioned lubricating oil bath.
The oilhole that setting is arranged in before and after the hazardous area is suitable, and these oilholes have the aperture cross section bigger than the aperture cross section that is arranged in the oilhole in the hazardous area.The oilhole of arranging before and after the adjacent area in hazardous area is also benefited from, thus attach troops to a unit in the oilhole in hazardous area can be limited to a narrow angular region.
Other of above-mentioned measure suitably improves and favourable design proposal has provided in other dependent claims and can obtain them in conjunction with the accompanying drawings from follow-up embodiment describes.
In the following drawings:
Fig. 1 shows the crankshaft bearing of large-scale diesel engine;
Fig. 2 shows the duty cycle curve of the axle journal of crankshaft bearing shown in Figure 1;
Fig. 3 schematically shows the bearing shell Lower Half of crankshaft bearing shown in Figure 1.
Large-scale diesel engine is well-known as the basic structure and the mode of action of the two-stroke large-scale diesel engine that is used for marine propeller, therefore, does not here need its detailed description.The bent axle of this motor have many that be in alignment with each other and be bearing in respectively a Fig. 1 based on the axle journal in the main bearing of type.Main bearing shown in Figure 1 is made of two-part combined bearing housing, and it has one and frame all-in-one-piece lower casing 1 and a removable upper casing 2.These two bearing housinges partly are furnished with the recess in a hole of complementary one-tenth, affiliated half one that bearing shell 3 is housed in described recess, and the axle journal 4 that matches separately then passes bearing shell.Be the axle journal 4 of packing into, last half bearing shell 3 of pulling down upper casing 2 and matching.
The external diameter of definite relatively axle journal 4 and the internal diameter of bearing shell 3 are to obtain required glade plane space.This gap cause thus axle journal 4 relatively bearing shell 3 move radially.Under the load effect, axle journal 4 here moves, thereby has produced adjacent with a supporting region and tapered gap that dwindles 5, end.This gap is in fact smaller, represents to amplify to show this gap for clear in Fig. 1.
In this class motor, the load of being passed to bearing housing by axle journal 4 changes by the cycle according to well-known mode and exactly is that its size and Orientation changed by the cycle.Curve 6 among Fig. 2 shows the situation that load changed by the cycle.The curve 7 of Fig. 2 has shown the periodicity situation of movement of the axle journal 4 that is caused by direction and the big or small load that changes by the cycle.The mobile relevant therewith situation of change in 5 positions, gap that shown of load vector of representing with arrow 8 in Fig. 1 and axle journal 4, move with the angular velocity that approximates load vector 8 angular velocity this gap position.For actual considering a problem, above-mentioned value can be considered to be equal.
Sliding friction surface with oil lubrication bearing shell 3 and axle journal 4.For this reason, bearing housing 1,2 is furnished with the groove that links to each other with oil feed line 9 shown in Figure 1 with bearing shell 3, has been equipped with the oilhole 11 that feeds the space between bearing shell 3 and the axle journal 4 for described groove.Therewith correspondingly, bearing shell Lower Half 3a shown in Figure 3 is furnished with the groove 10 that is made of reverse groove and infeed lubricant oil, and radial hole 11,12 leaves described groove, can lubricant oil be introduced space between axle journal 4 and the bearing shell 3 by these holes.
In two engage side end regions of half bearing shell 3a, be respectively equipped with a hole 11.The hole 11 adjacent with seam inwardly feeds one respectively in the circumferential slot cut 13 of inner opening, and it has constituted an oilhole with bigger aperture cross section.Its degree of depth is extended along with thereby the groove 13 that reduces to obtain wedge-shaped cross-section away from seam continuously can be on Fig. 3 is unshowned continues grooving shape in half bearing shell 3.
Supply with the lubricant oil of groove 13 and pass to gap 5 by rotating journal 4.Flow velocity in the gap of flowing through is under the situation of U, when the angular velocity and the load angle speed in gap 5 is decided to be when identical as described above, obtains following relation: U=(ω b+ ω j)/2-ω l
Wherein, ω bBe meant the angular velocity of bearing shell 3; ω jBe meant the angular velocity of axle journal 4; ω lBe meant the angular velocity of load vector 8.
See from the outside, promptly with system of coordinates that fixedly bearing shell 3 matches in, ω b=0.When the angular velocity of axle journal 4 was the twice of load angle speed, wherein said load angle speed equaled the angular velocity in gap 5, U=0 as described above.
From the gap 5, that is to say that in the system of coordinates in this gap above-mentioned relation is suitable for too.Here, ω l=0, ω b=-ω jTherefore, flow velocity U is also near zero.
This condition is present in the hazardous area of representing with Z in Fig. 2.Under the situation of not taking suitable ancillary method, as shown in Figure 2, the very approaching phenomenon of sliding friction surface that axle journal 4 and bearing shell 3 may occur, this be because do not supply fresh oil and be heated and thereby the less old oil that remains of ratio of viscosities extruded by side direction, and make the relatively thin cause of lubricant film.
For avoiding such phenomenon in the Z of hazardous area, occurring and avoid wearing and tearing and high temperature occurring, in the Z of hazardous area, infeed fresh oil.For forming corresponding grease channel, be provided with above-mentioned hole 12.They are relatively on axle journal turns in the angular region of the end of half forward bearing shell 3a (is left end at this) between 30 °～60 °.This angular region belongs to hazardous area Z and it and is positioned at and estimates to occur the back in the zone of high bearing pressure in this class crankshaft bearing.Below will describe the effect in hole 12 in detail.
At an axle journal that does not belong to hazardous area Z in 4 stages cycle of motion, that is to say when axle journal 4 time away from bearing shell 3 districts that comprise hole 12, by a large amount of fresh oils of hole 12 inputs, thereby rinsed out the old oil that is heated, subsequently axle journal 4 near the time, just when axle journal enters 7 sections of curves that belong to hazardous area Z, can form the lubricating film that can carry completely.
Dwindled the pressure-bearing surface of half bearing shell 3a slightly owing to porose 12, this must cause fluid pressure to raise.But the relative bearing width with the aperture cross section of the diameter in hole 12 is smaller, thereby the loss of consequent pressure-bearing surface is little, and this at least pressure-bearing surface loss is significantly smaller than the pressure-bearing surface loss in axially passing the same sipes of whole bearing width.The fluid pressure that forms here remains in the tolerance interval.Therewith relatively, also can advantageously will comprise that the back in the zone of maximum load appears in the area arrangements in hole 12 in expectation.
In the embodiment shown, be provided with two holes 12 in the angular region between above-mentioned 30 °～60 °.Obviously, more or less hole 12 can be set.For obtaining lubricant oil distribution as well as possible in the bearing district under whole, here stagger on circumferential and axial relatively in these two holes 12.Distribute for improving lubricant oil, the little oil duct that leaves hole 12 inner edge acies can also be set.But in most of the cases, this is unnecessary and does not also draw in the embodiment shown.
The hole 12 here oil supply 10 by a back side communicates with each other and links to each other with adjacent joint side opening 11.Groove 10 requires to have a bigger cross section here.If therefore undermine the stability of half bearing shell 3a, be equipped with a narrow oil supply then obviously can for each hole 12,11.
Axle journal 4 can be brought into play certain pumping action because of its radial motion.Being provided with one here, in the Z of hazardous area is suitable near bearing shell 3 and lubricating oil bath 14 that dot in Fig. 1 in the axial direction.Axle journal 4 sucks extra fresh oil in the example shown in the time of can opening in the gap in the Z of hazardous area 5 thus when move in the upper right.
Be arranged in attach troops to a unit in the hazardous area Z's and the oilhole that constitutes by hole 12 before and after and guaranteed proper lubrication outside the Z of hazardous area by the oilhole that hole 11 and affiliated separately hole 12 constitute.Here, because the relative movement between axle journal 4 and the gap 5, so can provide lubricant oil to the gap reliably.The edge section of hazardous area Z is benefited thus, thereby with holes 12 angular region can be narrow.

Claims (11)

1. crankshaft bearing that bears round bearing device and the especially large-scale diesel engine of the outer load that size and Orientation changes by the cycle, it has the bearing shell (3) of an affiliated axle journal of a suit (4), the sliding friction surface of bearing shell sliding friction surface and axle journal (4) define one always wedgewise narrow down to the gap (5) of supporting region, the position in described gap changes by the cycle with load, the angular velocity of its intermediate gap (5) approximates outer load angle speed, can be by the oilhole (11,13 of bearing shell side; 12) give described gap supplying lubricating oil, it is characterized in that, in the angular velocity of gap (5) approximates half hazardous area (Z) of axle journal (4) angular velocity, be provided with at least one oilhole (12), the non-flute profile aperture cross section of described oilhole equals the cross section of groove of the clean diameter of aperture cross section less than its width.
2. bearing means as claimed in claim 1 is characterized in that, each oilhole (12) that is arranged on hazardous area (Z) is designed to the less hole of diameter.
3. bearing means as claimed in claim 2 is characterized in that, is provided with the little oil duct that leaves the endoporus limit.
4. the described bearing means of one of claim as described above, it is characterized in that, be provided with many oilholes (12) that are arranged in the hazardous area (Z), can give these oilhole supplying lubricating oils by at least one recessed road of fuel feeding (10) that is arranged in bearing shell (3) zone, the back side.
5. bearing means as claimed in claim 4 is characterized in that, has been equipped with an independently recessed road of fuel feeding for each oilhole (12).
6. the described bearing means of one of claim as described above is characterized in that, each oilhole (12) of (Z) of attaching troops to a unit in the hazardous area is arranged in one and is connected in the angular region of back, the highest bearing pressure district.
7. the described bearing means of one of claim as described above, it is characterized in that, in the crankshaft bearing of a large-scale diesel engine, attach troops to a unit in each oilhole (12) of hazardous area (Z) be arranged on one away from 30 °～60 ° in forward bearing shell Lower Half (3a) end of turning to of axle journal (4) angular region in.
8. the described bearing means of one of claim as described above is characterized in that, is provided with a lubricating oil bath (14) of contiguous bearing shell (3) in the axial direction at least in hazardous area (Z).
9. the described bearing means of one of claim as described above, it is characterized in that, be provided with and be arranged in the oilhole (11 of attaching troops to a unit before or after the oilhole (12) of hazardous area (Z), 13), they have a big aperture cross section of aperture cross section that matches well the oilhole (12) that belongs to hazardous area (Z).
10. bearing means as claimed in claim 9 is characterized in that, is arranged on the outer oilhole (11,13) in hazardous area (Z) and has a slot cut that constitutes the aperture cross section respectively.
11. as claim 9 or 10 described bearing meanss, it is characterized in that, in the crankshaft bearing of a large-scale diesel engine, be arranged on the outer oilhole (11,13) in hazardous area (Z) and be arranged in the engage side petiolarea of bearing shell Lower Half (3a).
CN99108369A 1998-06-13 1999-06-11 Bearing device Pending CN1239195A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19826460.7 1998-06-13
DE19826460A DE19826460C2 (en) 1998-06-13 1998-06-13 bearing arrangement

Publications (1)

Publication Number Publication Date
CN1239195A true CN1239195A (en) 1999-12-22

Family

ID=7870840

Family Applications (1)

Application Number Title Priority Date Filing Date
CN99108369A Pending CN1239195A (en) 1998-06-13 1999-06-11 Bearing device

Country Status (4)

Country Link
JP (1) JP2000027850A (en)
KR (1) KR20000006156A (en)
CN (1) CN1239195A (en)
DE (1) DE19826460C2 (en)

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CN102734310A (en) * 2011-04-04 2012-10-17 环保汽车国际公司 Pushrod connection to a journal
CN103775500A (en) * 2014-01-21 2014-05-07 芜湖美达机电实业有限公司 Thick-wall bearing bush
CN105980719A (en) * 2014-02-14 2016-09-28 大丰工业株式会社 Plain bearing and lubricant supply mechanism equipped with same
CN105980720A (en) * 2014-02-14 2016-09-28 大丰工业株式会社 Plain bearing
CN106979217A (en) * 2017-05-12 2017-07-25 广西玉柴机器股份有限公司 A kind of crankshaft installed structure of opposed engine
CN107002751A (en) * 2015-11-24 2017-08-01 大丰工业股份有限公司 Halfbody bearing
CN107690541A (en) * 2015-06-05 2018-02-13 阿凯提兹动力公司 Minimize the oil leakage for waving the bearing of journals from two-stroke-cycle engine
CN109707814A (en) * 2019-01-25 2019-05-03 深圳市锐健电子有限公司 A kind of novel ball screw device
CN110139991A (en) * 2016-12-09 2019-08-16 大丰工业株式会社 Half-and-half bearing
CN110872962A (en) * 2018-08-29 2020-03-10 三菱自动车工业株式会社 Lubricating device for internal combustion engine

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US9133932B2 (en) 2011-04-04 2015-09-15 Ecomotors, Inc. Pushrod connection to a journal
CN102734310B (en) * 2011-04-04 2016-12-14 艾克莫特公司 Connect the push rod joint of axle journal
CN102734310A (en) * 2011-04-04 2012-10-17 环保汽车国际公司 Pushrod connection to a journal
CN103775500A (en) * 2014-01-21 2014-05-07 芜湖美达机电实业有限公司 Thick-wall bearing bush
CN103775500B (en) * 2014-01-21 2016-03-09 芜湖美达机电实业有限公司 A kind of thick walled half bearing
CN105980720B (en) * 2014-02-14 2018-06-05 大丰工业株式会社 Sliding bearing
CN105980719A (en) * 2014-02-14 2016-09-28 大丰工业株式会社 Plain bearing and lubricant supply mechanism equipped with same
CN105980720A (en) * 2014-02-14 2016-09-28 大丰工业株式会社 Plain bearing
CN107690541B (en) * 2015-06-05 2019-12-24 阿凯提兹动力公司 Minimizing oil leakage from rocking journal bearings of two-stroke cycle engines
CN107690541A (en) * 2015-06-05 2018-02-13 阿凯提兹动力公司 Minimize the oil leakage for waving the bearing of journals from two-stroke-cycle engine
CN107002751A (en) * 2015-11-24 2017-08-01 大丰工业股份有限公司 Halfbody bearing
CN110139991A (en) * 2016-12-09 2019-08-16 大丰工业株式会社 Half-and-half bearing
CN110139991B (en) * 2016-12-09 2021-05-18 大丰工业株式会社 Half bearing
CN106979217A (en) * 2017-05-12 2017-07-25 广西玉柴机器股份有限公司 A kind of crankshaft installed structure of opposed engine
CN110872962A (en) * 2018-08-29 2020-03-10 三菱自动车工业株式会社 Lubricating device for internal combustion engine
CN109707814A (en) * 2019-01-25 2019-05-03 深圳市锐健电子有限公司 A kind of novel ball screw device

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DE19826460A1 (en) 1999-12-23
KR20000006156A (en) 2000-01-25
DE19826460C2 (en) 2002-01-17
JP2000027850A (en) 2000-01-25

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