CN103038483B - The crosshead of crosshead type diesel engine - Google Patents
The crosshead of crosshead type diesel engine Download PDFInfo
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- CN103038483B CN103038483B CN201180037326.6A CN201180037326A CN103038483B CN 103038483 B CN103038483 B CN 103038483B CN 201180037326 A CN201180037326 A CN 201180037326A CN 103038483 B CN103038483 B CN 103038483B
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- Prior art keywords
- crosshead
- sliding panel
- sliding
- sliding part
- diesel engine
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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
Abstract
The crosshead of a kind of crosshead type diesel engine, the intensity not increasing sliding panel just can make the surface pressing between sliding panel and crosshead decline.The crosshead (2) of crosshead type diesel engine has: the pin (14) being rotatably coupled one end of one end of piston rod and connecting rod；Carry out sliding and reciprocating termination (8) relative to erectting, to free end, the sliding panel arranged from the fixing end being fixed on frame；And the connecting plate (13) of connecting pin (14) and termination (8), in the crosshead (2) of this crosshead type diesel engine, end (8c, 8d) on the vibration-direction of termination (8) is the thinner wall section (8f) that thickness is thinner than central part (8e).
Description
Technical field
The present invention relates to the crosshead of a kind of crosshead type diesel engine.
Background technology
In the past, as the sustainer of Ship Propeling, use crosshead type diesel engine (with reference to patent documentation 1).This crosshead type diesel engine has the crosshead being rotatably coupled in one end of piston rod and one end of connecting rod, and this crosshead is in the enterprising line slip of the sliding panel being fixed on main body side and moves back and forth.When crosshead moves back and forth on sliding panel, power passes to crosshead from piston by piston rod.The power of this transmission component on laterally (direction towards sliding panel) is referred to as side force, and it is the power making sliding panel deform.
In order to suppress the deformation of this sliding panel, in the past, by increasing the thickness of slab of sliding panel or increasing and arrange the flank that the deformation to sliding panel suppressed and increase the intensity of sliding panel.
Patent documentation 1: Japanese Patent Laid-Open 11-336560 publication
Invent problem to be solved
But, if suppressing the deformation of sliding panel and increasing the intensity of sliding panel, then not only resulting in cost increases, and the surface pressing between sliding panel and crosshead rises, it is also possible to cause the unfavorable condition such as rupture of oil film of lubricating oil.
Summary of the invention
The present invention makes in view of this problem, its object is to, it is provided that the crosshead of a kind of crosshead type diesel engine, it is possible to make the surface pressing between sliding panel and crosshead decline with not increasing the intensity of sliding panel.
For solving the means of problem
To achieve these goals, the crosshead of the crosshead type diesel engine of the present invention adopts the following technical scheme that.
That is, the crosshead of the crosshead type diesel engine of the present invention the first technical scheme, has: the pin being rotatably coupled one end of one end of piston rod and connecting rod；Sliding part, this sliding part carries out sliding and moving back and forth relative to sliding panel, and this sliding panel only side is fixed on the main body side of crosshead type diesel engine and erects setting from this side to another side；And connect described pin and the connecting portion of described sliding part, end on the described vibration-direction of described sliding part is the thinner wall section that thickness is thinner than the part except this end, described connecting portion is set as, making to be applied to, from described pin to the power of described sliding part, the position deviateed from the described opposite side side of sliding panel described in the mediad of this sliding part, the arm being positioned at described sliding part side of described connecting portion deviates to the described opposite side side of described sliding panel compared to the central authorities of described sliding part.
The end of the vibration-direction of sliding part is made than end with the thin thickness of outer portion, just make rigidity lower with outer portion than end.Accordingly, because the power (side force) being passed to sliding panel by the end of sliding part can be reduced, therefore the local of surface pressing between sliding part and sliding panel can be suppressed to rise.
Further, owing to connecting portion is set as: the power (side force) from pin to sliding part is applied to the position of opposite side side deviation of the mediad sliding panel from sliding part, therefore the application point of the side force in sliding part just deviates to the opposite side side of sliding panel.Thus, sliding part is just subject to making the end of the opposite side side of sliding part be indexed to sliding panel side, making the end of the side, side of sliding part be indexed to the moment of pin side around application point.Therefore, when side force is applied in crosshead, sliding part just can carry out such displacement: the other side side end of sliding part is indexed to sliding panel side, the end of the side, side of sliding part is indexed to pin side, and the displacement of the end of the side, side of sliding part is more than the displacement of the end of opposite side side.This displacement is the deformation same with sliding panel when applying side force.Its reason is, a side of sliding panel is fixed on main body side and erects setting to another side, therefore when applying side force from crosshead, the displacement ground flexure bigger than a side of another side.Therefore, the crosshead of technique scheme, when being applied with side force, can make sliding part displacement corresponding with the deformation with sliding panel, therefore the surface pressing between sliding part and sliding panel can be made to decline.
Further, owing to the arm of connecting portion is positioned at the sliding part side of connecting portion, therefore the application point of the side force being applied on sliding part can be determined according to the position of this arm.Technique scheme is to make arm deviate to the opposite side side of sliding panel compared to the central authorities of sliding part, therefore the other side side end of sliding part can be made to be indexed to sliding panel side, and makes the end of the side, side of sliding part be indexed to pin side.
Further, since according to arm decisive action point, it is therefore preferable that be not provided with passing to side force the flank etc. of sliding part except arm, and only have arm be connected with sliding part.
Additionally, the crosshead of the crosshead type diesel engine of the present invention the second technical scheme, have: the pin that one end of one end of piston rod and connecting rod is rotatably coupled；Sliding part, this sliding part carries out sliding and moving back and forth relative to sliding panel, and this sliding panel only side is fixed on the main body side of crosshead type diesel engine and erects setting from this side to another side；And connect described pin and the connecting portion of described sliding part, end on the described vibration-direction of described sliding part is the thinner wall section that thickness is thinner than the part except this end, described connecting portion is set as, make to be applied to, from described pin to the power of described sliding part, the position deviateed from the described opposite side side of sliding panel described in the mediad of this sliding part, in the side, described side of close described sliding panel of the arm being positioned at described sliding part side of described connecting portion, it is provided with to the notch part formed near the described opposite side side of described sliding panel.
Owing to being provided with the notch part formed to opposite side side in the side, side of arm, therefore the application point of side force can be made compared to the central authorities of sliding part to be offset to the opposite side side of sliding panel.It addition, arm can be allowed as the deformation of starting point using notch part.Thus, can more successfully make the other side side end of sliding part be indexed to sliding panel side, and make the end of the side, side of sliding part be indexed to pin side.
It addition, as notch part, it is preferable that R shape is to avoid the decline in life-span brought because of repeated load.
It addition, the crosshead type diesel engine of the present invention the second technical scheme, there is the crosshead described in any of the above-described kind.
Owing to having the crosshead of any of the above-described kind, therefore the surface pressing of sliding panel can be made to decline, can the thickness of sliding panel be done thin, or reinforcement that need not be excessive, therefore overall weight can be reduced, reduce cost.
The effect of invention
Owing to adopting the crosshead of crosshead type diesel engine of the present invention, the surface pressing between sliding panel and crosshead can be made to decline, therefore the thickening of sliding panel can be reduced as far as possible, strengthen, lightweight and the cost decline of crosshead type diesel engine can be obtained.
Accompanying drawing explanation
Fig. 1 indicates that the substantially profilograph of the 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 indicates that the figure of the effect of the crosshead shown in Fig. 4, and (a) indicates that the termination top view relative to the position relationship of sliding panel, and (b) indicates that the top view of the deformation of sliding panel and termination.
Fig. 6 indicates that the figure of the effect of the tip end of the crosshead shown in Fig. 3, and (a) is the curve chart of the surface pressing relative to glide direction of termination, and (b) indicates that the shape of tip end and the Partial enlarged side view of comparative example.
Fig. 7 indicates that the side force curve chart relative to the change of the position of crosshead.
Fig. 8 indicates that the enlarged partial isometric view of the choppy of sliding panel.
Fig. 9 indicates that the close-up top view of the variation of the crosshead shown in Fig. 4.
Figure 10 indicates that the Partial enlarged side view of the variation of the tip end of the crosshead shown in Fig. 3.
Symbol description:
2 crossheads
3 connecting rods
5 frames
6 sliding panels
The fixing end (side) of 6a
6b free end (another side)
8 terminations (sliding part)
8a outboard end (end of side, side)
8b medial end (end of opposite side side)
8c upper end (end)
8d lower end (end)
8e central part (end is with outer portion)
8f thinner wall section
13 connecting plates (connecting portion)
13a arm
14 pins
Detailed description of the invention
Below, it is explained with reference to one embodiment of the present invention.
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 principally serves as the sustainer of Ship Propeling, is the uniflow scavenging mode of two-stroke one cycle of operation.
This diesel engine has: the support 20 being positioned below；It is located at the frame (main body) 5 on support 20；And it is located at the cylinder body 21 in frame 5.These supports 20, frame 5 and cylinder body 21 utilize the multiple tension bolts (not shown) vertically extended and fastened are integrally fixed.
Cylinder body 21 is provided with cylinder jacket 22, is provided with cylinder head 23 in the upper end of this cylinder jacket 22.Reciprocating piston 1 it is provided with in the space formed by cylinder jacket 22 and cylinder head 23.The upper end of piston rod 24 it 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 it is rotatably coupled in the upper end of bent axle 4.
In frame 5, it is provided with the crosshead 2 piston rod 24 and connecting rod 3 being rotatably coupled.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, it is provided with the pair of sliding plate 6 vertically extended, and this sliding panel 6 is in the state being fixed on frame 5 side.
As in figure 2 it is shown, sliding panel 6 is fixed on the next door 9 of frame 5.That is, the fixing end 6a as one side of sliding panel is fixed on next door 9 and erects setting towards another side.It addition, another side is the free end 6b not being fixed on next door 9.
The strengthening parts such as sliding panel 6 is simply fixed on next door 9 by fixing end 6a, the flank being not provided with preventing sliding panel 6 from deforming.
Crosshead 2 has: the pin 14 being rotatably coupled the upper end of the lower end of piston rod 24 and connecting rod 3；Carry out sliding and reciprocating termination (sliding part) 8 relative to sliding panel 6；And the connecting plate of connecting pin 14 and termination 8 (connecting portion) 13.
Fig. 3 represents the side view of the crosshead 2 seen the end face side from pin 14.As shown in the drawing, termination 8 is provided with a pair in pin 14 both sides.It is provided with arm 13a 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 side force carrying out self-marketing 14 passes to sliding panel 6 through this arm 13a.It addition, as shown in the drawing, termination 8 is only connected to arm 13a, is not provided with the parts transmitting the force to termination except arm 13a.
As shown in Figure 4, arm 13a is arranged in the axis direction center side (this figure left side) of pin 14 compared to the central part (in this figure the central part on left and right directions) of the termination 8 on the axis direction of pin 14 with deviateing.More specifically, the central axial line C1 of arm 13a is offset to the axis direction center side of pin 14 compared to the central axial line C2 of termination 8 with bias d0.Therefore, pass to the application point P of the side force of termination 8 through arm 13a from pin 14 to be located in from the central axial line C1 of the central axial line C2 of the termination 8 arm 13a deviateed.Therefore, when side force is applied on application point P, just producing in Fig. 4 around moment counterclockwise around application point P, the medial end 8b of termination 8 is indexed to sliding panel 6 side (in Fig. 4 lower section), and the outboard end 8a of termination 8 is indexed to the axis side (in Fig. 4 top) of pin 14.
Additionally, by making application point P deviate the central authorities of termination 8, thus, make the outboard end (end of the side, side of sliding part) being positioned at the termination 8 of the fixing end 6a side of sliding panel 6 distance d1 between 8a and application point P become bigger than the medial end of the termination 8 of the free end 6b side being positioned at sliding panel 6 (end of the opposite side side of sliding part) distance d2 between 8b and application point P.Thus, when power relies on side force to put on application point P, the displacement of outboard end 8a becomes the displacement than medial end 8b big (with reference to Fig. 5 (b) described later).
On the other hand, as it is shown on figure 3, upper end 8c on the vibration-direction (in this figure above-below direction) of termination 8 and bottom 8d is provided with thickness than also thin for the central part 8e thinner wall section 8f on the above-below direction of termination 8.This thinner wall section 8f be formed as when crosshead 2 is seen in side as shown in Figure 3 with the outer contour 13b of the arm 13a taper being connected.That is, thinner wall section 8f is by being formed removing into taper with the face of sliding panel 6 opposition side.Fig. 6 (b) is the figure that the end of termination 8 gives enlarged representation, and as shown in the drawing, the 8g necklace ground, tapering of the outer contour 13b and thinner wall section 8f of arm 13a is formed.This is preferably shaped to be formed along from arm 13a towards the line of tension of the side force of termination 8.It addition, the shape of comparative example is 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 being 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 the rigid shape also big compared to present embodiment.
Then, the deformation of sliding panel 6 caused by side force is described with Fig. 7 and Fig. 8.
Fig. 7 represents the side force change relative to the position of crosshead 2, and in the figure, transverse axis represents the size of the side force being applied on sliding panel by crosshead 2, and the longitudinal axis represents the vibration-direction position of crosshead 2.As shown in the drawing, maximum is represented at position Z1 and position Z2 side force.Here it is, position Z1 represents that side 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 big towards towards the component the direction (lateral) of sliding panel 6.So, the size of side force changes according to the vibration-direction position of crosshead 2.
Fig. 8 represents the choppy of two kinds of sliding panels 6 when being subject to side force.
The free end 6b that choppy A is sliding panel 6 is subject to side force and produces the figure of deflection deformation with fixing end 6a for fulcrum.
Choppy B is the figure that local, termination 8 pushes sliding panel 6, sliding panel 6 local generation depressed deformation.
Below, corresponding choppy A and choppy B illustrates the action effect of present embodiment respectively.
Choppy A:
The corresponding choppy A of the crosshead 2 of present embodiment, the deviation of the application point P shown in its Fig. 4 effectively acts as effect.
That is, as shown in Fig. 5 (a), when side force is applied to left from right in the figure, the free end 6b of sliding panel 6 is as being indexed to left (choppy A) shown in double dot dash line.
On the other hand, owing to the crosshead 2 of present embodiment makes arm 13a be offset to free end 6b side, therefore application point P misplaces free end 6b side from the central axial line C2 of termination 8.Thus, moment clockwise is 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.Due to the deformation that the deformation of this termination 8 is same with the choppy A of sliding panel 6, therefore imitate the deformation of sliding panel 6 and make termination 8 deform, the surface pressing between sliding panel 6 and termination 8 can be made to decline.
So, adopt present embodiment, owing to sliding panel 6 can be allowed to carry out the deformation of choppy A and make surface pressing decline, therefore the thickness of slab of sliding panel 6 need not be increased, increase the strengthening measure of this class of strengthening part of other flank etc..Therefore, as in figure 2 it is shown, the structure that the flank of deformation of the free end 6b by suppressing sliding panel 6 is cancelled can be adopted.Thus, lightweight and the cost that can obtain crosshead type diesel engine decline.Additionally, due to the operation being welded on by reinforcement flank on sliding panel 6 and next door 9 (with reference to Fig. 2) can be omitted, therefore manufacture time limit and manufacturing cost can be greatly reduced.
Choppy B:
The corresponding choppy B of the crosshead 2 of present embodiment, the thinner wall section 8f shown in its Fig. 3 effectively acts as effect.
That is, as shown in Fig. 6 (b), owing to being provided with thinner wall section 8f at end 8c, 8d of termination 8, therefore the rigidity of this thinner wall section 8f is lower than the central part 8e of termination 8.Thus, the side force being delivered to sliding panel 6 by end 8c, 8d of termination 8 can be reduced.Accordingly, it is capable to avoid the local of the surface pressing of end, termination 8 to increase.Such as, as shown in the comparative example that is represented by dashed line, making a timing by identical with central part for the thickness of the end of termination 8, shown in the dotted line of the side force such as Fig. 6 (a) transmitted through the end of termination 8, represents maximum.Relatively, in the present embodiment, shown in solid such as Fig. 6 (a), owing to making the rigidity of end 8c, 8d decline compared to central part 8e, therefore can the surface pressing of end 8c, 8d of termination 8 be made substantially certain identically with central part 8e.
So, adopt present embodiment, owing to sliding panel 6 can be allowed to carry out the deformation of choppy B and make the surface pressing of tip end 8c, 8d decline, therefore the thickness of slab of sliding panel 6 need not be increased, increase the strengthening measure of this class of strengthening part of other flank etc..Therefore, as in figure 2 it is shown, the structure that the flank of deformation of the free end 6b by suppressing sliding panel 6 is cancelled can be adopted.Then, lightweight and the cost that can obtain crosshead type diesel engine decline.Additionally, due to the operation being welded on by reinforcement flank on sliding panel 6 and next door 9 (with reference to Fig. 2) can be omitted, therefore manufacture time limit and manufacturing cost can be greatly reduced.
Further, since make the thinner wall section 8f of the shape after the face with sliding panel 6 opposition side is removed, therefore can easily be processed.Additionally, due to do not reduce relative to sliding panel 6 slide area form thinner wall section 8f, therefore surface pressing can not be made to form thinner wall section 8f with increasing.
Below, modified embodiment of the present embodiment is described.
The deviation method of the application point P shown in Fig. 4 can be replaced to adopt the deviation 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 fixing end 6a side (i.e. the outboard end 8a side of termination 8, upside in the figure) of sliding panel 6, and is formed towards the free end 6b side (i.e. the medial end 8b of termination 8, downside in the figure) of sliding panel 6.By so arranging notch part 31, it is thus possible to make application point P be offset to the medial end 8b side of termination 8, the deformation of notch part 31 can be allowed.
Additionally, due to notch part 31 makes R shape, therefore concentrate it can be avoided that the life-span brought by load repeatedly declines by relaxing stress.
It 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 also can make the center axis deviation medial end 8b side to termination 8 of base end part 30a.
It 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, but also can replace, as shown in Figure 10 (b), by rectangular for the face of the arm 13a side of termination 8.It addition, as shown in Figure 10 (c), it is possible to R shape is made in the face of the arm 13a side of termination 8.
It addition, as shown in Figure 10 (d), it is possible to by the face of sliding panel 6 side of end, termination 8 is formed as leaving the taper of sliding panel 6, thinner wall section 8f is set.
Additionally, the shape of sliding panel 6 side of the thinner wall section 8f shown in Figure 10 (d), it can also be combined with Figure 10 (a) to (c) that the face (face of arm 13a side) of the opposition side to sliding panel 6 is processed.
Claims (3)
1. a crosshead for crosshead type diesel engine, has:
The pin that one end of one end of piston rod and connecting rod is rotatably coupled；
Sliding part, this sliding part carries out sliding and moving back and forth relative to sliding panel, and this sliding panel only side is fixed on the main body side of crosshead type diesel engine and erects setting from this side to another side；And
Connecting described pin and the connecting portion of described sliding part, the crosshead of this crosshead type diesel engine is characterised by,
End on the described vibration-direction of described sliding part is the thinner wall section that thickness is thinner than the part except this end,
Described connecting portion is set as, and makes to be applied to, from described pin to the power of described sliding part, the position deviateed from the described opposite side side of sliding panel described in the mediad of this sliding part,
The arm being positioned at described sliding part side of described connecting portion deviates to the described opposite side side of described sliding panel compared to the central authorities of described sliding part.
2. a crosshead for crosshead type diesel engine, has:
The pin that one end of one end of piston rod and connecting rod is rotatably coupled；
Sliding part, this sliding part carries out sliding and moving back and forth relative to sliding panel, and this sliding panel only side is fixed on the main body side of crosshead type diesel engine and erects setting from this side to another side；And
Connecting described pin and the connecting portion of described sliding part, the crosshead of this crosshead type diesel engine is characterised by,
End on the described vibration-direction of described sliding part is the thinner wall section that thickness is thinner than the part except this end,
Described connecting portion is set as, and makes to be applied to, from described pin to the power of described sliding part, the position deviateed from the described opposite side side of sliding panel described in the mediad of this sliding part,
In the side, described side of close described sliding panel of the arm being positioned at described sliding part side of described connecting portion, it is provided with to the notch part formed near the described opposite side side of described sliding panel.
3. a crosshead type diesel engine, it is characterised in that there is the crosshead described in claim 1 or 2.
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 CN103038483A (en) | 2013-04-10 |
| CN103038483B true CN103038483B (en) | 2016-07-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510426913.4A Active CN104989526B (en) | 2010-11-08 | 2011-11-02 | Crosshead of crosshead diesel engine and crosshead diesel engine |
| CN201180037326.6A Active CN103038483B (en) | 2010-11-08 | 2011-11-02 | The crosshead of crosshead type 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 |
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| Country | Link |
|---|---|
| JP (1) | JP5665488B2 (en) |
| KR (1) | KR101492746B1 (en) |
| CN (2) | CN104989526B (en) |
| WO (1) | WO2012063717A1 (en) |
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| 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 |
| JP7403321B2 (en) * | 2020-01-10 | 2023-12-22 | 株式会社ジャパンエンジンコーポレーション | frame |
| 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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| JPS5929812A (en) * | 1982-08-10 | 1984-02-17 | Mitsubishi Heavy Ind Ltd | Crosshead of reciprocating machine |
| JPS60167812A (en) * | 1984-02-04 | 1985-08-31 | Hiroshi Mizuno | Drive device of vibration conveyor |
| JPS60167812U (en) * | 1984-04-17 | 1985-11-07 | 三菱重工業株式会社 | crosshead bearing |
| JPH02107737U (en) * | 1989-02-14 | 1990-08-28 | ||
| JPH11336560A (en) * | 1998-05-28 | 1999-12-07 | Mitsubishi Heavy Ind Ltd | Cross head of diesel engine |
| 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 CN201510426913.4A patent/CN104989526B/en active Active
- 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
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|---|---|---|---|---|
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012063717A1 (en) | 2012-05-18 |
| CN103038483A (en) | 2013-04-10 |
| CN104989526B (en) | 2020-07-28 |
| JP2012102630A (en) | 2012-05-31 |
| CN104989526A (en) | 2015-10-21 |
| JP5665488B2 (en) | 2015-02-04 |
| KR101492746B1 (en) | 2015-02-11 |
| KR20130044311A (en) | 2013-05-02 |
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