CN104989526A - Cross head for cross head diesel engine - Google Patents
Cross head for cross head diesel engine Download PDFInfo
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- CN104989526A CN104989526A CN201510426913.4A CN201510426913A CN104989526A CN 104989526 A CN104989526 A CN 104989526A CN 201510426913 A CN201510426913 A CN 201510426913A CN 104989526 A CN104989526 A CN 104989526A
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- Prior art keywords
- crosshead
- slide plate
- diesel engine
- termination
- slide
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Classifications
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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
The application is the divisional application of following patent application:
Application number: 201180037326.6
The applying date: on November 02nd, 2011
Denomination of invention: the crosshead of crosshead type diesel engine
Technical field
The present invention relates to a kind of crosshead of crosshead type diesel engine.
Background technique
In the past, as the master motor of Ship Propeling, use crosshead type diesel engine (with reference to patent documentation 1).This crosshead type diesel engine has the crosshead be connected rotationally with one end of connecting rod one end of piston rod, and this crosshead is in the enterprising line slip of the slide plate being fixed on main body side and to-and-fro motion.When crosshead moves back and forth on slide plate, power passes to crosshead from piston by piston rod.The component of power on horizontal (direction towards slide plate) of this transmission is called as lateral force, and it is the power that slide plate is out of shape.
In order to suppress the distortion of this slide plate, in the past, by increasing the thickness of slab of slide plate or increasing and arrange the intensity that the flank suppressed the distortion of slide plate increases slide plate.
Patent documentation 1: Japanese Patent Laid-Open 11-336560 publication
Invent problem to be solved
But, if suppress the distortion of slide plate and increase the intensity of slide plate, then cost not only can be caused to increase, the surface pressure rising between slide plate and crosshead, also may cause the unfavorable conditions such as the rupture of oil film of lubricant oil.
Summary of the invention
The present invention makes in view of this problem, its object is to, provides a kind of crosshead of crosshead type diesel engine, make the surface pressure between slide plate and crosshead decline with can not increasing the intensity of slide plate.
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 first technological scheme, has: the pin be connected rotationally with one end of connecting rod one end of piston rod; Carry out sliding and reciprocating slide part relative to erectting to another side the slide plate arranged from the side being fixed on main body side; And connect the joint of described pin and described slide part, end on the described vibration-direction of described slide part is the thinner wall section that the part of Thickness Ratio except this end is thin, on the axial direction of described pin, relative to the thickness of described slide part, the thinner thickness of arm.
The thickness thinner than part beyond end is made in the end of the vibration-direction of slide part, just makes rigidity lower than part beyond end.Thus, because the end of slide part can be reduced by and pass to the power (lateral force) of slide plate, therefore the local of surface pressure between slide part and slide plate can be suppressed to rise.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, described thinner wall section is the shape in the face eliminating the side contrary with described slide plate.
Owing to making the thinner wall section of the shape be removed with the face of slide plate opposition side, therefore can easily process.In addition, due to do not reduce relative to slide plate slide area form thinner wall section, therefore form thinner wall section while surface pressure can not be increased.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, described thinner wall section is the shape in the face eliminating described slide plate side.
The thinner wall section of the shape that the face also can making 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 makes to be applied to the position of departing from from the described opposite side side of slide plate described in the mediad of this slide part from described pin to the power of described slide part.
Because joint is set as: the power (lateral force) from pin to slide part is applied to the position of departing from from the opposite side side of the mediad slide plate of slide part, therefore the point of action of lateral force in slide part just departs to the opposite side side of slide plate.Thus, slide part is just subject to making the end of the opposite side side of slide part be indexed to slide plate side, making the end of the side, side of slide part be indexed to the moment of pin side around point of action.Therefore, when lateral force is applied in crosshead, slide part just can carry out such displacement: the other side side end of slide part is indexed to slide plate side, the end of the side, side of slide part is indexed to pin side, and the displacement of the end of the side, side of slide part is greater than the displacement of the end of opposite side side.This displacement is the distortion same with slide plate when applying lateral force.Its reason is, a side of slide plate is fixed on main body side and erects to another side and arranges, therefore when applying lateral force from crosshead, another side bends than the larger displacement of a side.Therefore, the crosshead of technique scheme, when being applied with lateral force, can making slide part conjugate with corresponding with the distortion of slide plate, therefore the surface pressure between slide part and slide plate can be made to decline.
In addition, in the crosshead of the crosshead type diesel engine of technique scheme, the arm being positioned at described slide part side of described joint compared to the central authorities of described slide part, depart from by the described opposite side side to described slide plate.
Arm due to joint is positioned at the slide part side of joint, therefore can determine the point of action of the lateral force be applied on slide part according to the position of this arm.Technique scheme makes arm compared to the central authorities of slide part and the opposite side side to slide plate is departed from, therefore the other side side end of slide part can be made to be indexed to slide plate side, and make the end of the side, side of slide part be indexed to pin side.
In addition, due to the decisive action point according to arm, therefore, preferably the flank etc. lateral force being 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, in the side, described side being positioned at the arm of described slide part side of described joint, the notch part formed to another side described is provided with.
Owing to being provided with the notch part formed to opposite side side in the side, side of arm, therefore the point of action of lateral force can be made compared to the central authorities of slide part to be offset to the opposite side side of slide plate.In addition, arm can be allowed using notch part as the distortion of starting point.Thus, the other side side end of slide part more successfully can be made to be indexed to slide plate side, and make the end of the side, side of slide part be indexed to pin side.
In addition, as notch part, preferred R shape is to avoid the decline in the life-span brought because of repeated load.
In addition, the crosshead type diesel engine of the present invention second technological scheme, has above-mentioned crosshead described in any one.
Owing to having any one crosshead above-mentioned, therefore the surface pressure of slide plate can be made to decline, can the thickness of slide plate be done thin, or not need excessive reinforcement, therefore can overall weight be reduced, reduce costs.
The effect of invention
Owing to adopting the crosshead of crosshead type diesel engine of the present invention, the surface pressure between slide plate and crosshead can be made to decline, therefore can reduce the thickening of slide plate as far as possible, strengthen, lightweight and the cost that can obtain crosshead type diesel engine decline.
Accompanying drawing explanation
Fig. 1 is the roughly sectional arrangement drawing representing crosshead type diesel engine of the present invention.
Fig. 2 represents the amplification stereogram of the crosshead periphery of Fig. 1.
Fig. 3 is the side view of crosshead.
Fig. 4 is the close-up top view of the crosshead of Fig. 3.
Fig. 5 is the figure of the effect representing the crosshead shown in Fig. 4, and (a) represents the plan view of termination relative to the position relationship of slide plate, and (b) is the plan view of the distortion representing slide plate and termination.
Fig. 6 is the figure of the effect of the tip end representing the crosshead shown in Fig. 3, and (a) is the plotted curve of the surface pressure relative to glide direction of termination, and (b) represents the shape of tip end and the Partial enlarged side view of comparative example.
Fig. 7 represents the plotted curve of lateral force relative to the change of the position of crosshead.
Fig. 8 is the enlarged partial isometric view of the choppy representing slide plate.
Fig. 9 is the close-up top view of the variation representing the crosshead shown in Fig. 4.
Figure 10 is the Partial enlarged side view of the variation of the tip end representing the crosshead shown in Fig. 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 side, side)
8b inner end (end of opposite side side)
8c upper end (end)
8d lower end (end)
8e central part (beyond end part)
8f thinner wall section
13 connecting plates (joint)
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 is mainly used as the master motor of Ship Propeling, is the uniflow scavenging mode of two-stroke one work cycle.
This diesel engine has: the support 20 being positioned at below; Be located at the frame (main body) 5 on support 20; And the cylinder body 21 be located in frame 5.These supports 20, frame 5 and cylinder body 21 utilize multiple tension bolts (not shown) of vertically extending and to be fastenedly integrally fixed.
Cylinder body 21 is provided with cylinder liner 22, is provided with cylinder head 23 in the upper end of this cylinder liner 22.Reciprocating piston 1 is provided with in the space formed by cylinder liner 22 and cylinder head 23.The upper end of piston rod 24 is rotatably mounted with in the lower end of piston 1.
Crankcase made by support 20, is provided with bent axle 4.The lower end of connecting rod 3 is connected with rotationally in the upper end of bent axle 4.
In frame 5, be provided with the crosshead 2 piston rod 24 and connecting rod 3 are connected rotationally.That is, the lower end of piston rod 24 and the upper end of connecting rod 3 are connected with crosshead 2.In the both sides (left and right in Fig. 1) of crosshead 2, be provided with the pair of sliding plate 6 vertically extended, and this slide plate 6 is in the state being fixed on frame 5 side.
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 one side of slide plate to be fixed on next door 9 and to erect setting towards another side.In addition, another side is the free end 6b be not fixed on next door 9.
Slide plate 6 is just fixed on next door 9 by fixed end 6a, is not provided with the stiffening elements such as the flank preventing slide plate 6 to be out of shape.
Crosshead 2 has: the pin 14 be connected rotationally in the lower end of piston rod 24 and the upper end of connecting rod 3; Carry out sliding and reciprocating termination (slide part) 8 relative to slide plate 6; And the connecting plate of connecting pin 14 and termination 8 (joint) 13.
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 in pin 14 both sides.Arm 13a is provided with in the side, termination 8 of connecting plate 13.This arm 13a as shown in Figure 4, the main part 13b of connection end 8 and connecting plate 13.The lateral force carrying out self-marketing 14 passes to slide plate 6 through this arm 13a.In addition, as shown in the drawing, termination 8 is only connected with arm 13a, is not provided with parts power being passed to termination except arm 13a.
As shown in Figure 4, arm 13a compared to the termination 8 on the axial direction of pin 14 central part (central part in this figure on left and right directions) and be arranged in the axial direction center side (this figure left side) of pin 14 with departing from.More particularly, arm 13a central axial line C1 compared to 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 passing to the lateral force of termination 8 through arm 13a from pin 14 is located in the central axial line C1 of the arm 13a departed from from the central axial line C2 of termination 8.Therefore, when lateral force is applied on point of action P, just produce around point of action P in Fig. 4 around counterclockwise moment, the inner end 8b of termination 8 is indexed to slide plate 6 side (in Fig. 4 below), and the outboard end 8a of termination 8 is indexed to the axis side (in Fig. 4 top) of pin 14.
In addition, by the central authorities making point of action P depart from termination 8, thus, make the outboard end of the termination 8 of the fixed end 6a side being positioned at slide plate 6 (end of the side, side of slide part) the distance d1 between 8a and point of action P become inner end (end of the opposite side side of slide part) the distance d2 between 8b and point of action P of the termination 8 than the free end 6b side being positioned at slide plate 6 large.Thus, when power relies on lateral force to put on point of action P, the displacement of outboard end 8a becomes the displacement large (with reference to Fig. 5 (b) described later) than inner end 8b.
On the other hand, as shown in Figure 3, the upper end portion 8c on the vibration-direction (in this figure above-below direction) of termination 8 and underpart 8d is provided with the thinner wall section 8f that central part 8e on the above-below direction of Thickness Ratio termination 8 is also thin.This thinner wall section 8f is formed as the taper be connected with the outer contour 13b of arm 13a when crosshead 2 is seen in side as shown in Figure 3.That is, thinner wall section 8f is by being formed removing into taper with the face of slide plate 6 opposition side.The figure represented is amplified in the end of termination 8 by Fig. 6 (b), and as shown in the drawing, the outer contour 13b of arm 13a and the 8g necklace ground, tapering of thinner wall section 8f are formed.This shape is preferably formed along from arm 13a towards the stress line of the lateral force of termination 8.In addition, the shape of comparative example represented by dashed line in this figure.This compares shape is normally used shape, and the end thickness of its termination 8 is made and is equal to central part, and the outer contour 13b ' of arm 13a ' is the width be equal to termination 8 before being connected with termination 8.That is, the shape of comparative example is that the end of termination 8 has compared to the also large rigid shape of present embodiment.
Then, the distortion of the slide plate 6 caused by lateral force is described with Fig. 7 and Fig. 8.
Fig. 7 represents the change of lateral force relative to the position of crosshead 2, and in the figure, transverse axis represents the size being applied to the lateral force on slide plate by crosshead 2, and the longitudinal axis represents the vibration-direction position of crosshead 2.As shown in the drawing, maximum value is indicated at position Z1 and position Z2 lateral force.Here it is, position Z1 represents that lateral force increases because of the outburst in the combustion space in cylinder, and position Z2 represents that piston rod 24 (with reference to Fig. 1) tilts from vertical and becomes large towards towards the component the direction (lateral) of slide plate 6.So, the size of lateral force changes according to the vibration-direction position of crosshead 2.
Fig. 8 represents the choppy of two kinds of slide plates 6 when being subject to lateral force.
Choppy A is that the free end 6b of slide plate 6 is subject to lateral force and with fixed end 6a for fulcrum produces the figure of deflection deformation.
The figure that choppy B is local, termination 8 pushing slide plate 6, slide plate 6 local produces depressed deformation.
Below, corresponding choppy A and choppy B illustrates the action effect of present embodiment respectively.
Choppy A:
The corresponding choppy A of crosshead 2 of present embodiment, the departing from of point of action P shown in its Fig. 4 plays a role effectively.
That is, as shown in Fig. 5 (a), when lateral force is applied to left from right in the figure, the free end 6b of slide plate 6 is as being indexed to left (choppy A) like that shown in double dot dash line.
On the other hand, the crosshead 2 due to present embodiment makes arm 13a be offset to free end 6b side, therefore point of action P to misplace free end 6b side from the central axial line C2 of termination 8.Thus, moment is clockwise applied on termination 8, as shown in Fig. 5 (b), the outboard end 8a of termination 8 can be made to be indexed to pin 14 side (in figure right side) significantly.Distortion due to this termination 8 is the distortion same with the choppy A of slide plate 6, therefore imitates the distortion of slide plate 6 and termination 8 is out of shape, and the surface pressure between slide plate 6 and termination 8 can be made to decline.
So, adopt present embodiment, due to slide plate 6 can be allowed to carry out the distortion of choppy A and make surface pressure decline, therefore do not need the thickness of slab of increase slide plate 6, increase the strengthening measure of this class of stiffening element of other flank etc.Therefore, as shown in Figure 2, the structure that the flank of the distortion of the free end 6b by suppressing slide plate 6 is cancelled can be adopted.Thus, lightweight and the cost that can obtain crosshead type diesel engine decline.In addition, due to the operation be welded on by reinforcement flank on slide plate 6 and next door 9 (with reference to Fig. 2) can be omitted, therefore significantly can reduce and manufacture time limit and manufacture cost.
Choppy B:
The corresponding choppy B of crosshead 2 of present embodiment, the thinner wall section 8f shown in its Fig. 3 plays a role effectively.
That is, as shown in Fig. 6 (b), because end 8c, 8d in termination 8 are provided with thinner wall section 8f, therefore the rigidity of this thinner wall section 8f is lower than the central part 8e of termination 8.Thus, end 8c, 8d of termination 8 can be reduced by and be delivered to the lateral force of slide plate 6.Therefore, the local of the surface pressure of end, termination 8 can be avoided to increase.Such as, as shown in comparative example represented by dashed line, the thickness in the end by termination 8 makes a timing identically with central part, through termination 8 end and the lateral force transmitted represents maximum value as Suo Shi the dotted line of Fig. 6 (a).Relatively, in the present embodiment, as as shown in the solid line of Fig. 6 (a), owing to making the rigidity of end 8c, 8d decline compared to central part 8e, therefore can the surface pressure of end 8c, 8d of termination 8 be made roughly certain identically with central part 8e.
So, adopt present embodiment, due to slide plate 6 can be allowed to carry out the distortion of choppy B and make the surface pressure of tip end 8c, 8d decline, therefore do not need to increase the thickness of slab of slide plate 6, increase the strengthening measure of this class of stiffening element of other flank etc.Therefore, as shown in Figure 2, the structure that the flank of the distortion of the free end 6b by suppressing slide plate 6 is cancelled can be adopted.So lightweight and the cost that can obtain crosshead type diesel engine decline.In addition, due to the operation be welded on by reinforcement flank on slide plate 6 and next door 9 (with reference to Fig. 2) can be omitted, therefore significantly can reduce and manufacture time limit and manufacture cost.
In addition, owing to making the thinner wall section 8f of the shape after being removed with the face of slide plate 6 opposition side, therefore can easily process.In addition, due to do not reduce relative to slide plate 6 slide area form thinner wall section 8f, therefore surface pressure can not be made to form thinner wall section 8f with increasing.
Below, modified embodiment of the present embodiment is described.
The departing from method of point of action P shown in Fig. 4 can be replaced and adopt departing from method shown in Fig. 9.That is, the arm 30 shown in Fig. 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 is formed with notch part 31 compared to base end part 30a in side, termination 8.This notch part 31 is located at the fixed end 6a side (i.e. the outboard end 8a side of termination 8, upside in the figure) of slide plate 6, and towards slide plate 6 free end 6b side (i.e. the inner end 8b of termination 8, downside in the figure) and formed.By arranging notch part 31 like this, thus point of action P can be made to be offset to the inner end 8b side of termination 8, the distortion of notch part 31 can be allowed.
In addition, because notch part 31 makes R shape, therefore the life-span can avoiding being brought by load is repeatedly concentrated to decline by relaxing stress.
In addition, the central axis of the base end part 30a of the arm 30 shown in Fig. 9 is made consistent with the central axial line C2 of termination 8, but the center axis deviation of base end part 30a also can be made to the inner end 8b side of termination 8.
In addition, the thinner wall section 8f shown in Fig. 3, although taper (with reference to Figure 10 (a)) is made in the face of the arm 13a side of its termination 8, also can replace, as shown in Figure 10 (b), do orthogonal by the face of the arm 13a side of termination 8.In addition, as shown in Figure 10 (c), also R shape can be made in the face of the arm 13a side of termination 8.
In addition, as shown in Figure 10 (d), the face also by slide plate 6 side by end, termination 8 is formed as the taper leaving slide plate 6, arranges thinner wall section 8f.
In addition, the shape of slide plate 6 side of the thinner wall section 8f shown in Figure 10 (d), its Figure 10 (a) to (c) that also can process with the face of the opposition side to slide plate 6 (face of arm 13a side) combines.
Claims (5)
1. a crosshead for crosshead type diesel engine, has:
By the pin that one end of piston rod is connected rotationally with one end of connecting rod;
Carry out sliding and reciprocating slide part relative to erectting to another side the slide plate arranged from the side being fixed on main body side; And
Connect the joint of described pin and described slide part, the feature of the crosshead of this crosshead type diesel engine is,
End on the described vibration-direction of described slide part is the thinner wall section that the part of Thickness Ratio except this end is thin,
On the axial direction of described pin, relative to the thickness of described slide part, the thinner thickness of arm.
2. the crosshead of crosshead type diesel engine as claimed in claim 1, it is characterized in that, described thinner wall section is the shape in the face eliminating the side contrary with described slide plate.
3. the crosshead of crosshead type diesel engine as claimed in claim 1, it is characterized in that, described thinner wall section is the shape in the face eliminating described slide plate side.
4. the crosshead of crosshead type diesel engine as claimed in claim 1, it is characterized in that, described joint is set as, and makes to be applied to the position of departing from from the described opposite side side of slide plate described in the mediad of this slide part from described pin to the power of described slide part.
5. a crosshead type diesel engine, is characterized in that, has the crosshead according to any one of Claims 1-4.
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 |
| CN201180037326.6A CN103038483B (en) | 2010-11-08 | 2011-11-02 | The crosshead of crosshead type diesel engine |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180037326.6A Division CN103038483B (en) | 2010-11-08 | 2011-11-02 | The crosshead of crosshead type diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104989526A true CN104989526A (en) | 2015-10-21 |
| CN104989526B CN104989526B (en) | 2020-07-28 |
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ID=46050865
Family Applications (2)
| 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 |
Family Applications Before (1)
| 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 |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5665488B2 (en) |
| KR (1) | KR101492746B1 (en) |
| CN (2) | CN103038483B (en) |
| WO (1) | WO2012063717A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113187620A (en) * | 2020-01-10 | 2021-07-30 | 日本发动机股份有限公司 | Framework |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104196870B (en) * | 2014-07-24 | 2016-10-12 | 江苏科技大学 | A kind of large-scale diesel engine crosshead assembly |
| 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 |
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| 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 |
| 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 |
| KR100797129B1 (en) * | 2000-09-25 | 2008-01-22 | 베르트질레 슈바이츠 악티엔게젤샤프트 | Cross-head sliding shoe |
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2010
- 2010-11-08 JP JP2010249806A patent/JP5665488B2/en active Active
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2011
- 2011-11-02 CN CN201180037326.6A patent/CN103038483B/en active Active
- 2011-11-02 CN CN201510426913.4A patent/CN104989526B/en active Active
- 2011-11-02 KR KR1020137002313A patent/KR101492746B1/en active IP Right Grant
- 2011-11-02 WO PCT/JP2011/075357 patent/WO2012063717A1/en active Application Filing
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| 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 |
| EP0393770A1 (en) * | 1989-04-21 | 1990-10-24 | NUOVOPIGNONE 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 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113187620A (en) * | 2020-01-10 | 2021-07-30 | 日本发动机股份有限公司 | Framework |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101492746B1 (en) | 2015-02-11 |
| CN103038483B (en) | 2016-07-13 |
| WO2012063717A1 (en) | 2012-05-18 |
| JP2012102630A (en) | 2012-05-31 |
| KR20130044311A (en) | 2013-05-02 |
| CN103038483A (en) | 2013-04-10 |
| JP5665488B2 (en) | 2015-02-04 |
| CN104989526B (en) | 2020-07-28 |
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