CN103038483A - Cross head for cross head diesel engine - Google Patents
Cross head for cross head diesel engine Download PDFInfo
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- CN103038483A CN103038483A CN2011800373266A CN201180037326A CN103038483A CN 103038483 A CN103038483 A CN 103038483A CN 2011800373266 A CN2011800373266 A CN 2011800373266A CN 201180037326 A CN201180037326 A CN 201180037326A CN 103038483 A CN103038483 A CN 103038483A
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- Prior art keywords
- crosshead
- slide plate
- diesel engine
- slide
- termination
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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
- F16C5/00—Crossheads; Constructions of connecting-rod heads or piston-rod connections rigid with crossheads
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- 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
- F02B75/00—Other engines
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
The purpose of the present invention is to provide a cross head for a cross head diesel engine, the cross head being configured so that the surface pressure between slide plates and the cross head can be reduced without increasing the strength of the slide plates. A cross head (2) for a cross head diesel engine, comprising: a pin (14) for rotatably connecting one end of the piston rod and one end of the connecting rod; shoes (8) reciprocating and sliding on the slide plates raised from the fixed end of the slide plates, which are affixed to a framework, toward the free ends of the slide plates; and connecting plates (13) for connecting the pin (14) and the shoes (8). End sections (8c, 8d) of each of the shoes (8) in the reciprocation direction are thin sections (8f) having a smaller thickness than the center section (8e) of the shoe (8).
Description
Technical field
The present invention relates to a kind of crosshead of crosshead type diesel engine.
Background technique
In the past, the master motor as Ship Propeling is used used crosshead type diesel engine (with reference to patent documentation 1).This crosshead type diesel engine has is connected the crosshead that an end connects rotationally with an end of piston rod with connecting rod, this crosshead is in the enterprising line slip of the slide plate that is fixed in main body side and to-and-fro motion.When crosshead when slide plate moves back and forth, power passes to crosshead from piston by piston rod.The component of the power of this transmission on horizontal (towards the direction of slide plate) is called as lateral force, and it is the power that makes the slide plate distortion.
In order to suppress the distortion of this slide plate, in the past, the thickness of slab by increasing slide plate or increase arranged the intensity that flank that the distortion to slide plate suppressed increases slide plate.
Patent documentation 1: Japanese patent laid-open 11-336560 communique
Invent problem to be solved
But, if suppress the distortion of slide plate and increase the intensity of slide plate, then not only can cause cost to increase, the surface pressure between slide plate and the crosshead rises, and also may cause the unfavorable conditions such as rupture of oil film of lubricant oil.
Summary of the invention
The present invention makes in view of this problem, and its purpose is, a kind of crosshead of crosshead type diesel engine is provided, can not increase slide plate intensity the surface pressure between slide plate and the crosshead is descended.
Be used for solving the means of problem
To achieve these goals, the crosshead of crosshead type diesel engine of the present invention adopts following technological scheme.
That is, the crosshead of the crosshead type diesel engine of the present invention's the first technological scheme has: an end of piston rod is connected the pin that an end connects rotationally with connecting rod; Slide and reciprocating slide part with respect to erectting the slide plate that arranges from a side that is fixed in main body side to another side; And the joint that connects described pin and described slide part, the end on the described vibration-direction of described slide part is the thin thinner wall section of the part of Thickness Ratio except this end.
The end of the vibration-direction of slide part is made than the thin thickness of part beyond the end, just make rigidity lower than part beyond the end.Thus, because can reduce to pass to by the end of slide part the power (lateral force) of slide plate, rise so can suppress the part of surface pressure between slide part and the slide plate.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, described thinner wall section is to have removed the shape of the face of a side opposite with described slide plate.
Because the thinner wall section of the shape that make face with the slide plate opposition side has been removed is so can process easily.In addition, because the slide area ground that does not reduce with respect to slide plate forms thinner wall section, form thinner wall section so can not increase surface pressure ground.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, described thinner wall section is to have removed the shape of the face of described slide plate side.
The thinner wall section of the shape that the face that also can make the slide plate side has been removed.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, described joint is set as, and the power from described pin to described slide part is applied to from the distolateral position of departing from of described opposite side of the described slide plate of mediad of this slide part.
Because joint is set as: the power from pin to slide part (lateral force) is applied to from the distolateral position of departing from of the opposite side of the mediad slide plate of slide part, so the point of action of the lateral force in the slide part just departs to the opposite side of slide plate is distolateral.Thus, slide part just is subject to making the distolateral end of opposite side of slide part be indexed to the slide plate side around the point of action, makes the end of a side side of slide part be indexed to the moment of pin side.Therefore, under lateral force is applied to situation on the crosshead, slide part just can carry out such displacement: the other side side end of slide part is indexed to the slide plate side, the end of one side side of slide part is indexed to the pin side, and the displacement of the end of a side side of slide part is greater than the displacement of the distolateral end of opposite side.This displacement is the same distortion of the slide plate when applying lateral force.Its reason is that a side of slide plate is fixed on main body side and to another side setting setting, so applying from crosshead in the situation of lateral force, another side is than the larger displacement ground deflection of a side.Therefore, the crosshead of technique scheme can make the slide part displacement with corresponding with the distortion of slide plate in the situation that has applied lateral force, so the surface pressure between slide part and the slide plate is descended.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, the arm that is positioned at described slide part side of described joint is than the central authorities of described slide part and to distolateral departing from of described opposite side of described slide plate.
Because the arm of joint is positioned at the slide part side of joint, so can determine to be applied to according to the position of this arm the point of action of the lateral force on the slide part.Technique scheme is that arm is departed to the opposite side of slide plate is distolateral than the central authorities of slide part, thus can make the other side side end of slide part be indexed to the slide plate side, and make the end of a side side of slide part be indexed to the pin side.
In addition, because according to arm and the decisive action point, therefore, preferably the flank etc. that lateral force is passed to slide part be not set except arm, and is only having arm to be connected with slide part.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, the described side side at the arm of the described slide part side of being positioned at of described joint is provided with the notch part that forms to described another side.
Owing to be provided with to the notch part of the distolateral formation of opposite side in a side side of arm, so the point of action that can make lateral force is offset to the opposite side of slide plate than the central authorities of slide part distolateral.In addition, can allow arm with the distortion of notch part as starting point.Thus, can more successfully make the other side side end of slide part be indexed to the slide plate side, and make the end of a side side of slide part be indexed to the pin side.
In addition, as notch part, preferred R shape is with the decline in life-span of avoiding being brought because of repeated load.
In addition, the crosshead type diesel engine of the present invention's the second technological scheme has above-mentioned any described crosshead.
Owing to have above-mentioned any crosshead, so the surface pressure of slide plate is descended, the thickness of slide plate can be done thinly, or do not need excessive reinforcement, so can reduce overall weight, reduce cost.
The effect of invention
Owing to adopt the crosshead of crosshead type diesel engine of the present invention, the surface pressure between slide plate and the crosshead is descended, so can reduce thickening, strengthening of slide plate as far as possible, lightweight and the cost that can obtain crosshead type diesel engine descend.
Description of drawings
Fig. 1 is the roughly sectional arrangement drawing of expression crosshead type diesel engine of the present invention.
The amplification stereogram of the crosshead periphery of Fig. 2 presentation graphs 1.
Fig. 3 is the side view of crosshead.
Fig. 4 is the local amplification plan view of the crosshead of Fig. 3.
Fig. 5 is the figure of the effect of expression crosshead shown in Figure 4, (a) is to represent the termination with respect to the plan view of the position relationship of slide plate, (b) is the plan view of the distortion of expression slide plate and termination.
Fig. 6 is the figure of effect of the end, termination of expression crosshead shown in Figure 3, (a) is the plotted curve with respect to the surface pressure of glide direction of termination, (b) is the shape of expression end, termination and the local enlarged side view of comparative example.
Fig. 7 is that the expression lateral force is with respect to the plotted curve of the variation of the position of crosshead.
Fig. 8 is the local amplification stereogram of the choppy of expression slide plate.
Fig. 9 is the local amplification plan view of the variation of expression crosshead shown in Figure 4.
Figure 10 is the local enlarged side view of variation of the end, termination of expression crosshead shown in Figure 3.
Symbol description:
2 crossheads
3 connecting rods
5 frames
6 slide plates
6a fixed end (side)
6b free end (another side)
8 terminations (slide part)
8a outboard end (end of a side side)
8b inner end (end that opposite side is distolateral)
8c upper end (end)
8d lower end (end)
8e central part (part beyond the end)
The 8f thinner wall section
13 connecting plates (joint)
The 13a arm
14 pins
Embodiment
Below, with reference to accompanying drawing one embodiment of the present invention is described.
Fig. 1 represents the schematic configuration of the crosshead type diesel engine of an embodiment of the present invention.Diesel engine shown in this figure mainly is used as the master motor that Ship Propeling is used, and is the uniflow scavenging mode of two-stroke one work cycle.
This diesel engine has: the support 20 that is positioned at the below; Be located at the frame (main body) 5 on the support 20; And be located at cylinder body 21 on the frame 5.These supports 20, frame 5 and cylinder body 21 utilize a plurality of tension bolts (not shown) that direction up and down extends and the fastened one that is fixed into.
Be provided with cylinder liner 22 at cylinder body 21, be provided with cylinder head 23 in the upper end of this cylinder liner 22.In the space that is formed by cylinder liner 22 and cylinder head 23, be provided with reciprocating piston 1.Be rotatably mounted with the upper end of piston rod 24 in the lower end of piston 1.
On frame 5, be provided with piston rod 24 is connected rotationally the crosshead 2 that connects with connecting rod.That is, the upper end of the lower end of piston rod 24 and connecting rod 3 is connected with crosshead 2.At the both sides of crosshead 2 (among Fig. 1 about), be provided with the pair of sliding plate 6 that direction is up and down extended, and this slide plate 6 is the state that is fixed on frame 5 sides.
As shown in Figure 2, slide plate 6 is fixed on the next door 9 of frame 5.That is, the fixed end 6a as the one side of slide plate is fixed on the next door 9 and towards another side and erects setting.In addition, another side is the free end 6b that is not fixed on the next door 9.
Fig. 3 represents the side view of the crosshead 2 seen from the end face side of pin 14.As shown in the drawing, termination 8 is provided with a pair of in pin 14 both sides.8 sides are provided with arm 13a in the termination of connecting plate 13.This arm 13a as shown in Figure 4, the main part 13b of connection end 8 and connecting plate 13.Come the lateral force of self-marketing 14 to pass to slide plate 6 through this arm 13a.In addition, as shown in the drawing, on termination 8, only be connected with arm 13a, be not provided with the parts that power passed to the termination except arm 13a.
As shown in Figure 4, the central part (central part among this figure on the left and right directions) of the termination 8 of arm 13a on the axial direction of pin 14 and be arranged in the axial direction center side (this figure left side) of pin 14 with departing from.More particularly, the central axial line C1 of arm 13a than the termination 8 central axial line C2 and be offset to the axial direction center side of pin 14 with bias d0.Therefore, the point of action P that passes to the lateral force of termination 8 through arm 13a from pin 14 is located on the central axial line C1 of the arm 13a that departs from from the central axial line C2 of termination 8.Therefore, when lateral force is applied on the point of action P, just produce around the point of action P among Fig. 4 around counterclockwise moment, the inner end 8b of termination 8 is indexed to slide plate 6 sides (below among Fig. 4), and the outboard end 8a of termination 8 is indexed to the axis side (top among Fig. 4) of pin 14.
In addition, by making point of action P depart from the central authorities of termination 8, thereby, make between outboard end (end of a side side of the slide part) 8a of the termination 8 of the fixed end 6a side that is positioned at slide plate 6 and the point of action P apart from become large apart from d2 than between inner end (end that the opposite side of slide part the is distolateral) 8b of the termination 8 of the free end 6b side that is positioned at slide plate 6 and the point of action P of d1.Thus, rely on lateral force to put in the situation of point of action P in power, the displacement of outboard end 8a becomes than the displacement large (with reference to Fig. 5 described later (b)) of inner end 8b.
On the other hand, as shown in Figure 3, the central part 8e on the above-below direction that the upper end portion 8c on the vibration-direction (above-below direction among this figure) of termination 8 and underpart 8d are provided with Thickness Ratio termination 8 is thin thinner wall section 8f also.This thinner wall section 8f forms the taper that is connected with the outer contour 13b of arm 13a when crosshead 2 is seen in the side as shown in Figure 3.That is, thinner wall section 8f forms by removing into taper with the face of slide plate 6 opposition sides.Fig. 6 (b) is the figure that the end of termination 8 is amplified expression, and is as shown in the drawing, and the 8g necklace ground, tapering of the outer contour 13b of arm 13a and thinner wall section 8f forms.This shape is preferably along from the stress line of arm 13a lateral force of 8 towards the termination and form.In addition, dot the shape of comparative example among this figure.This comparison shape is normally used shape, and the end thickness of its termination 8 is made with central part and is equal to, and, the outer contour 13b ' of arm 13a ' for the width that is equal to termination 8 before termination 8 is connected.That is, the shape of comparative example is that the end of termination 8 has than present embodiment large rigid shape also.
The distortion of the caused slide plate 6 of lateral force then, is described with Fig. 7 and Fig. 8.
Fig. 7 represents lateral force with respect to the variation of the position of crosshead 2, and in the figure, transverse axis represents to be applied to by crosshead 2 size of the lateral force on the slide plate, and the longitudinal axis represents the vibration-direction position of crosshead 2.As shown in the drawing, express maximum value at position Z1 and position Z2 lateral force.Here it is, and position Z1 represents that lateral force increases because of the outburst in the combustion space in the cylinder, and position Z2 represents that piston rod 24 (with reference to Fig. 1) becomes large from the vertical inclination and towards the component on the direction (lateral) of slide plate 6.So, the size of lateral force changes according to the vibration-direction position of crosshead 2.
The choppy of two kinds of slide plates 6 when Fig. 8 represents to be subject to lateral force.
Choppy A is that the free end 6b of slide plate 6 is subject to lateral force and produces the figure of deflection deformation take fixed end 6a as fulcrum.
Choppy B is termination 8 local pushing slide plates 6, the slide plate 6 local figures that produce depressed deformation.
Below, corresponding choppy A and choppy B illustrate the action effect of present embodiment respectively.
Choppy A:
The crosshead 2 corresponding choppy A of present embodiment, its departing from effectively of point of action P shown in Figure 4 plays a role.
That is, shown in Fig. 5 (a), when lateral force in the figure from right-hand when being applied to left, the free end 6b of slide plate 6 just is indexed to left (choppy A) like that shown in double dot dash line.
On the other hand because the crosshead 2 of present embodiment makes arm 13a be offset to free end 6b side, so point of action P from the termination 8 the central axial line C2 free end 6b side that misplaces.Thus, be applied on the termination 8 around clockwise moment, shown in Fig. 5 (b), can make the outboard end 8a of termination 8 be indexed to significantly pin 14 sides (right side among the figure).Because the distortion of this termination 8 is distortion same with the choppy A of slide plate 6, make termination 8 distortion so imitate the distortion of slide plate 6, the surface pressure between slide plate 6 and the termination 8 is descended.
So, adopt present embodiment owing to can allow slide plate 6 to carry out the distortion of choppy A and surface pressure is descended, so do not need to increase slide plate 6 thickness of slab, increase the strengthening measure of this class of stiffening element of other flank etc.Therefore, as shown in Figure 2, the structure that can adopt the flank of the distortion of the free end 6b that will suppress slide plate 6 to be cancelled.Thus, can obtain lightweight and the cost decline of crosshead type diesel engine.In addition, will strengthen being welded on operation on slide plate 6 and next door 9 (with reference to Fig. 2) with flank owing to can omit, so can significantly reduce manufacturing time limit and manufacture cost.
Choppy B:
The crosshead 2 corresponding choppy B of present embodiment, its thinner wall section 8f shown in Figure 3 plays a role effectively.
That is, shown in Fig. 6 (b), because 8 end 8c, 8d are provided with thinner wall section 8f in the termination, so the rigidity of this thinner wall section 8f is lower than the central part 8e of termination 8.Thus, can reduce to be delivered to by end 8c, the 8d of termination 8 lateral force of slide plate 6.Therefore, can avoid the part of the surface pressure at place, 8 ends, termination to increase.For example, as the comparative example that dots shown in, thickness and the central part of the end of termination 8 are being made one regularly in the same manner, 8 the end through the termination and the lateral force transmitted represents maximum value shown in the dotted line of Fig. 6 (a).Relatively, in the present embodiment, shown in the solid line of Fig. 6 (a) like that, owing to the rigidity that makes end 8c, 8d descends than central part 8e, so can make the surface pressure of end 8c, the 8d of termination 8 roughly certain in the same manner with central part 8e.
So, adopt present embodiment, owing to can allow slide plate 6 to carry out the distortion of choppy B and the surface pressure of end, termination 8c, 8d is descended, thus do not need to increase slide plate 6 thickness of slab, increase the strengthening measure of this class of stiffening element of other flank etc.Therefore, as shown in Figure 2, the structure that can adopt the flank of the distortion of the free end 6b that will suppress slide plate 6 to be cancelled.So lightweight and the cost that can obtain crosshead type diesel engine descend.In addition, will strengthen being welded on operation on slide plate 6 and next door 9 (with reference to Fig. 2) with flank owing to can omit, so can significantly reduce manufacturing time limit and manufacture cost.
In addition, because the thinner wall section 8f of the shape of the face with slide plate 6 opposition sides made after being removed, so can easily process.In addition, because the slide area ground that does not reduce with respect to slide plate 6 forms thinner wall section 8f, form thinner wall section 8f so can not make surface pressure increase ground.
Below, modified embodiment of the present embodiment is described.
Can replace the departing from method of point of action P shown in Figure 4 and adopt the method that departs from shown in Figure 9.That is, arm 30 shown in Figure 9, at its base end part 30a, the central axial line of arm 30 is consistent with the central axial line C2 of termination 8, but than base end part 30a and 8 sides are formed with notch part 31 in the termination.This notch part 31 is located at the fixed end 6a side (being the outboard end 8a side of termination 8, upside in the figure) of slide plate 6, and forms towards the free end 6b of slide plate 6 side (being the inner end 8b of termination 8, downside in the figure).By notch part 31 is set like this, thereby can make point of action P be offset to the inner end 8b side of termination 8, can allow the distortion of notch part 31.
In addition, because notch part 31 makes the R shape, so concentrate the life-span that to avoid by repeatedly load brings to descend by relaxing stress.
In addition, the central axis of the base end part 30a of arm 30 shown in Figure 9 is made consistent with the central axial line C2 of termination 8, but the center axis deviation that also can make base end part 30a to the termination 8 inner end 8b side.
In addition, thinner wall section 8f shown in Figure 3 although the face of the arm 13a side of its termination 8 is made taper (with reference to Figure 10 (a)), also can replace, and shown in Figure 10 (b), does the face of the arm 13a side of termination 8 orthogonal.In addition, shown in Figure 10 (c), also the face of the arm 13a side of termination 8 can be made the R shape.
In addition, shown in Figure 10 (d), also can form the taper that leaves slide plate 6 by the face with slide plate 6 sides of 8 ends, termination, thinner wall section 8f is set.
In addition, the shape of slide plate 6 sides of the thinner wall section 8f shown in Figure 10 (d), it also can make up with Figure 10 (a) to (c) that the face (face of arm 13a side) of the opposition side of slide plate 6 is processed.
Claims (7)
1. the crosshead of a crosshead type diesel engine has:
One end of piston rod is connected the pin that an end connects rotationally with connecting rod;
Slide and reciprocating slide part with respect to erectting the slide plate that arranges from a side that is fixed in main body side to another side; And
The joint that connects described pin and described slide part, the crosshead of this crosshead type diesel engine be characterised in that,
End on the described vibration-direction of described slide part is the thin thinner wall section of the part of Thickness Ratio except this end.
2. the crosshead of crosshead type diesel engine as claimed in claim 1 is characterized in that, described thinner wall section is to have removed the shape of the face of a side opposite with described slide plate.
3. the crosshead of crosshead type diesel engine as claimed in claim 1 or 2 is characterized in that, described thinner wall section is to have removed the shape of the face of described slide plate side.
4. such as the crosshead of each described crosshead type diesel engine in the claims 1 to 3, it is characterized in that, described joint is set as, and the power from described pin to described slide part is applied to from the distolateral position of departing from of described opposite side of the described slide plate of mediad of this slide part.
5. the crosshead of crosshead type diesel engine as claimed in claim 4 is characterized in that, the arm that is positioned at described slide part side of described joint is than the central authorities of described slide part and to distolateral departing from of described opposite side of described slide plate.
6. such as the crosshead of claim 4 or 5 described crosshead type diesel engines, it is characterized in that, in a described side side of the arm of the described slide part side of being positioned at of described joint, be provided with the notch part that forms to described another side.
7. a crosshead type diesel engine is characterized in that, has each described crosshead in the claim 1 to 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510426913.4A CN104989526B (en) | 2010-11-08 | 2011-11-02 | Crosshead of crosshead diesel engine and crosshead diesel engine |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-249806 | 2010-11-08 | ||
| JP2010249806A JP5665488B2 (en) | 2010-11-08 | 2010-11-08 | Crosshead of crosshead type diesel engine |
| PCT/JP2011/075357 WO2012063717A1 (en) | 2010-11-08 | 2011-11-02 | Cross head for cross head diesel engine |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510426913.4A Division CN104989526B (en) | 2010-11-08 | 2011-11-02 | Crosshead of crosshead diesel engine and crosshead diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103038483A true CN103038483A (en) | 2013-04-10 |
| CN103038483B CN103038483B (en) | 2016-07-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180037326.6A Active CN103038483B (en) | 2010-11-08 | 2011-11-02 | The crosshead of crosshead type diesel engine |
| CN201510426913.4A Active CN104989526B (en) | 2010-11-08 | 2011-11-02 | Crosshead of crosshead diesel engine and crosshead diesel engine |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510426913.4A Active CN104989526B (en) | 2010-11-08 | 2011-11-02 | Crosshead of crosshead diesel engine and crosshead diesel engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5665488B2 (en) |
| KR (1) | KR101492746B1 (en) |
| CN (2) | CN103038483B (en) |
| WO (1) | WO2012063717A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104196870A (en) * | 2014-07-24 | 2014-12-10 | 江苏科技大学 | Crosshead component of large diesel engine |
| CN113187620A (en) * | 2020-01-10 | 2021-07-30 | 日本发动机股份有限公司 | Framework |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016160958A (en) * | 2015-02-26 | 2016-09-05 | 三菱重工業株式会社 | Guide of cross head bearing and cross head type diesel engine |
| CN114135459B (en) * | 2021-12-08 | 2024-01-12 | 西南石油大学 | Ultra-long stroke reciprocating pump with connecting rod pulled |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5888011U (en) * | 1981-12-10 | 1983-06-15 | 大同メタル工業株式会社 | Guide shoe bearing for large engines |
| JPS5929812A (en) * | 1982-08-10 | 1984-02-17 | Mitsubishi Heavy Ind Ltd | Crosshead of reciprocating machine |
| JPS60167812U (en) * | 1984-04-17 | 1985-11-07 | 三菱重工業株式会社 | crosshead bearing |
| CN86101282A (en) * | 1985-04-01 | 1987-01-14 | 劳舍兄弟有限公司 | The column of supporting crosshead guide bar slide rail |
| US5031512A (en) * | 1989-04-21 | 1991-07-16 | Nuovopigone - Industrie Meccaniche E Fonderia S.P.A. | Crosshead for reciprocating piston machines, in particular for reciprocating compressors |
| JPH11336560A (en) * | 1998-05-28 | 1999-12-07 | Mitsubishi Heavy Ind Ltd | Cross head of diesel engine |
| JP2002147431A (en) * | 2000-09-25 | 2002-05-22 | Waertsilae Schweiz Ag | Crosshead sliding shoe |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1419457A (en) * | 1921-06-01 | 1922-06-13 | Miles D Joyner | Crosshead |
| JPS60167812A (en) * | 1984-02-04 | 1985-08-31 | Hiroshi Mizuno | Drive device of vibration conveyor |
| JPH02107737U (en) * | 1989-02-14 | 1990-08-28 | ||
| JP2001317533A (en) * | 2000-05-10 | 2001-11-16 | Mitsubishi Heavy Ind Ltd | Diesel engine |
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2010
- 2010-11-08 JP JP2010249806A patent/JP5665488B2/en active Active
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2011
- 2011-11-02 WO PCT/JP2011/075357 patent/WO2012063717A1/en active Application Filing
- 2011-11-02 KR KR1020137002313A patent/KR101492746B1/en active IP Right Grant
- 2011-11-02 CN CN201180037326.6A patent/CN103038483B/en active Active
- 2011-11-02 CN CN201510426913.4A patent/CN104989526B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5888011U (en) * | 1981-12-10 | 1983-06-15 | 大同メタル工業株式会社 | Guide shoe bearing for large engines |
| JPS5929812A (en) * | 1982-08-10 | 1984-02-17 | Mitsubishi Heavy Ind Ltd | Crosshead of reciprocating machine |
| JPS60167812U (en) * | 1984-04-17 | 1985-11-07 | 三菱重工業株式会社 | crosshead bearing |
| CN86101282A (en) * | 1985-04-01 | 1987-01-14 | 劳舍兄弟有限公司 | The column of supporting crosshead guide bar slide rail |
| US5031512A (en) * | 1989-04-21 | 1991-07-16 | Nuovopigone - Industrie Meccaniche E Fonderia S.P.A. | Crosshead for reciprocating piston machines, in particular for reciprocating compressors |
| JPH11336560A (en) * | 1998-05-28 | 1999-12-07 | Mitsubishi Heavy Ind Ltd | Cross head of diesel engine |
| JP2002147431A (en) * | 2000-09-25 | 2002-05-22 | Waertsilae Schweiz Ag | Crosshead sliding shoe |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104196870A (en) * | 2014-07-24 | 2014-12-10 | 江苏科技大学 | Crosshead component of large diesel engine |
| CN113187620A (en) * | 2020-01-10 | 2021-07-30 | 日本发动机股份有限公司 | Framework |
| CN113187620B (en) * | 2020-01-10 | 2023-01-31 | 日本发动机股份有限公司 | Framework |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2012102630A (en) | 2012-05-31 |
| CN103038483B (en) | 2016-07-13 |
| KR20130044311A (en) | 2013-05-02 |
| KR101492746B1 (en) | 2015-02-11 |
| WO2012063717A1 (en) | 2012-05-18 |
| JP5665488B2 (en) | 2015-02-04 |
| CN104989526B (en) | 2020-07-28 |
| CN104989526A (en) | 2015-10-21 |
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