JP2799133B2 - V type 6 cylinder engine crankshaft - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a V-type six-cylinder engine having four crank journals.

[0002]

2. Description of the Related Art A crankshaft is important for generating power by converting a linear motion caused by a piston of each cylinder into a rotary motion, and simultaneously applying a force to a piston reaching a bottom dead center so that the linear motion can be continued. Has functions.

Although the crankshaft must be made to rotate smoothly without vibration, the center of each crankpin is eccentric with respect to the center of the crank journal. I cannot do it.

In order to solve such a problem, a balancing weight is usually added to the opposite side of the crank pin of the crank arm so that a balance during rotation can be obtained.

[0005] In the case of a small engine, the balancing weight is formed integrally with the crank arm and then corrected in the machining process to obtain a balance. In the case of a large engine, a balancing weight is separately manufactured and attached to the crank arm.

Generally, the balancing weights are arranged in a symmetrical direction in which inertial couple can be canceled.

In this case, there is no particular problem in the arrangement of the balancing weights in the in-line type four-cylinder engine because the crank arm deployment angle is 180 degrees without exception, but the V-type six-cylinder engine is not easy.

The reason is that if balancing weights are attached to all the crank arms, the weight of the shaft becomes excessively heavy, and torsional vibration occurs in a high rotation region of the engine.

In order to solve the problems of the V-type six-cylinder engine, US Pat. No. 4,552,104 and US Pat.
No. 30,512 discloses a device in which five balancing weights are arranged on the crank arm at the front and rear ends of the crankshaft, and one on the crank arm at the center. In these inventions, among the balancing weights, those arranged at the front and rear ends are eccentric with respect to those arranged at the center, thereby reducing the weight of the crankshaft.

As is well known, the force acting on both ends of the shaft in the crankshaft greatly affects the magnitude of the inertial couple.

In view of this, in the above-mentioned method, the dynamic balance with respect to the entire crankshaft is effectively achieved by disposing an inertial couple at the center of the crankshaft with balancing weights at both ends of the shaft. Dynamic balance between adjacent main bearings is achieved by placing a balancing weight on the central crank arm. However, the balancing weight placed on the central crank arm affects only the dynamic balance between adjacent main bearings and cannot contribute to the dynamic balance for the entire crankshaft. Depending on the balancing weight of each pair placed on both ends of the shaft
Therefore, there is a problem that the size of these balancing weights must be increased.

In shaping the crankshaft, the upper and lower molds move in the direction of the center of the weight of the balancing weight, while the balancing weight disposed on the central crank arm has a separation line between the adjacent crank pins. It is quite difficult to shape an appropriately sized shape.

[0013] Viewed in this perspective, the crankshaft disclosed in Japanese Patent Publication 60- 2 No. 27037, the six balancing weights each Kurankua - sequences angle of balancing weights at the same time arranged alongside arm It is shown that the unbalance couple can be eliminated by setting the angle to 60 degrees and making them symmetric to each other.

However, the third and fourth balancing weights disposed on the crank arm adjacent to the center of the crankshaft contribute to the dynamic balance between the adjacent main bearings and also affect the dynamic balance of the entire crankshaft. However, since the second and fifth balancing weights are disposed on the third and seventh crank arms, the moment arm is short and the effect cannot be exhibited as compared with the above-described method. Therefore, the first and sixth balancing weights are eventually increased. There are disadvantages that must be met.

[0015]

SUMMARY OF THE INVENTION It is an object of the present invention to effectively achieve the dynamic balance of the entire crankshaft existing on the crankshaft and the dynamic balance between the internal main bearings with an optimum balancing weight, thereby reducing engine vibration. It is an object of the present invention to provide a crankshaft for a V6 cylinder engine in which the surface pressure acting on each crank journal is reduced to improve the productivity of shaping a desired shape of a crankshaft, particularly a balancing weight.

[0016]

According to the present invention, there is provided a computer system having the above object.
For the first aspect of the present invention,FirstCrank pin,No.
Second crankpin,Third crankpin,The fourth clan
Kupin,Fifth and sixth crankpins
WhenThe firstCrank journal,Second crank jar
Naru,Third crank journal and fourth crank journal
JournalWhenAnd the firstCrank arm,Second Qu
Rank arm,Third crank arm,Fourth crank
arm,Fifth crank arm,6th crank lure
M,A seventh crank arm, an eighth crank arm, and
Ninth crank armCrankshaft withSo
hand,FirstCrank journalAnd the second crank jar
With nullBetweenFirstcrankpinWhenSecond crankpin
WhenIs provided,SecondCrank journalAnd the third class
Link journalBetweenThirdWith the crankpinFourth Qu
Rank pins andIs provided,Third classLink journalWhen
With the fourth crank journalBetweenFifthCrank pin
WhenWith the sixth crankpinIs provided,FirstCrank
With the journalFirstBetween the crankpinFirstClan
KuahHomeBut,FirstWith the crankpinSecondCrank pin
BetweenSecondThe crank armSecondCrank pin
WhenSecondBetween the crank journalThirdcrank
ArmSecondWith crank journalThirdcrank
Between the pinthe fourthThe crank armThirdClan
With Kupinthe fourthBetween the crankpinFifthCranka
Teamthe fourthWith the crankpinThirdCrank journal
BetweenSixthThe crank armThirdcrank
Journal andFifthBetween the crankpinSeventhKula
Link armFifthWith the crankpinSixthCrankpi
BetweenEighthThe crank armSixthCrankpi
Andthe fourthBetween the crank journalNinthClan
Of the V-type six-cylinder engine
In the crankshaft,FirstOn the crank arm
And the center of its weight isClan
JournalWith respect to the axis centerFirstCrank pin
Located on the opposite side ofFirstBalancing weight
And;SecondGiven to the crank arm,
Center is aboveFirstOn the same side as the balancing weight
One saidFirstAgainst balancing weightsThe firstK
From ranked journalthe fourthHead to the crank journal
Look at,CounterclockwiseOnly a predetermined angleAt the angularly displaced position
The second placedA balancing weight;the fourth
Crank arm andSixthAttached to each crank arm
And the center of its weight isFirstBalancing wa
From the center of the weight of the siteThe firstFrom the crank journal
the fourthLook towards the crank journal,Clockwise
90 degree angular displacementVirtual lineArranged symmetrically up and down
ThirdBalancing weightAnd the fourth balancing
EightAnd;EighthCrank armGranted toReAnd said
Before the virtual lineRecordSecond balunShiNg weight and
Vertical symmetryMakeFifth placed in positionBaLansingC
With Eight; The ninthGranted to the crank armSaid
The first balancen centered on a virtual lineGwaitWhen
Vertically symmetricSixth rose placed in positionNsingu
A V-type six-cylinder, comprising:
Provide an engine crankshaft. Andfirst
From the first crank journal to the fourth crank journal
Look towards, that is,Forward of the crankshaftFrom
When you see it (see Figure 6),First and sixthBalancing
EightFirst and sixthBalancing weights,
No.Second, third, fourth and fifthBalancing way
IsSecond, third, fourth and fifthBalancing
As a whole, in balance with each other
Equilibrate.

According to a second aspect of the present invention, another balancing weight is arranged between the third and fourth balancing weights.

[Action]

The arrangement of the balancing weights cancels out the inertial couple of the crankshaft and the unbalanced couple due to the balancing weights.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings. FIG. 1 is a side view of a crankshaft according to the present invention, and reference numerals 1 to 6 in the drawings denote first to sixth crankpins to which connecting rods are connected.

The first to sixth crank pins 1 to 6
In the case of a type 6 cylinder, the first to fourth crank journals 1
Each set is divided and arranged between 1 to 14.

The first to sixth crankpins 1 to 6 are adjacent to each other, and the first to sixth crankpins 1 to 6 and the first to fourth crank journals 11 to 1 are adjacent to each other.
The first to ninth crank arms 21 to 29 are interposed between adjacent ones of the crank arms 4.

The flywheel (not shown) has a flange 3 formed adjacent to the fourth crank journal 14.
Attach to 0.

In the crankshaft according to this embodiment, first and second balancing weights 31 and 32 are provided to the first and second crank arms 21 and 22 at the front end in the first to ninth crank arms 21 to 29, respectively. The third and fourth intermediate crank arms 24 and 26
And fourth balancing weights 33, 34, respectively, and the eighth and ninth crank arms 28, 2 at the rear end.
Fifth and sixth balance weights 35 and 36 are also provided to the ninth.

FIG. 2 is a sectional view of each part of the crankshaft of FIG.
The first balancing weight 31 given to 1 is shown in FIG.
As shown in (a), the center of the weight is located below the center C of the axis of the crankshaft, and the second crank arm 2
The second balancing weight 32 given to FIG.
Its weight center lower so as in (b), however, and is located at a position displaced about 30 ° angle in a counterclockwise direction with respect to the first balancing weight 31.

Next, the third balancing weight 33 applied to the fourth crank arm and the sixth crank arm 26
The fourth balancing weight 34 given to each of FIGS.
As shown in (c) and (d), the first balancing weight 31
Is located at a position which is displaced approximately 90 degrees clockwise from the center of the weight, and is therefore vertically located on the left side in the orthogonal direction in the figure. The centers of these weights are vertically symmetrical with respect to each other.

The fifth crank arm 28 has a fifth
The balancing weight 35 is the second weight as shown in FIG.
It is vertically symmetrical with respect to the balancing weight 32. The sixth balancing weight 36 provided to the ninth crank arm 29 is vertically symmetric with respect to the first balancing weight 31 as shown in FIG.

As with the second balancing weight 32,
The fifth balancing weight 35 is at a position displaced about 30 degrees clockwise with respect to the sixth balancing weight 36.
Is located .

The first balancing weight 31 and the sixth balancing weight 36, the second balancing weight 32 and the fifth balancing weight 35, and the third balancing weight 33 and the fourth balancing weight 34.
Have mutually equivalent or equivalent mass first moments.

As shown in FIG. 2, first and second balancing weights 31 and 32 disposed at both ends of the crankshaft and fifth and sixth balancing weights 35 and 3 are provided.
6 is vertically symmetrical, and the third and fourth balancing weights 33 and 34 arranged in the middle are positioned with respect to the center line of the weight of the first and second balancing weights 31 and 32 arranged at both ends. Are located vertically on the left side in the orthogonal direction.

Each balancing weight 31 in FIG.
The arrangement relationship of to 36 can be shown as in FIG.

Looking through this, the first and sixth balancing weights 31 and 36 and the second and fifth balancing weights 32 and 35, and the intermediate third and fourth balancing weights 33 and 34 are mutually connected to the shaft of the crankshaft. It can be seen that they are arranged completely symmetrically with respect to the center C.

Considering the rotation of the crankshaft, if the crankshaft is rotated by 90 degrees in the state shown in FIG. 1, the configuration shown in FIG. 3 is obtained. In this case, the arrangement of the balancing weights changes as shown in FIG.

That is, the first and sixth balancing weights 31, 36 and the second and fifth balancing weights 32,
35, and the third and fourth balancing weights 33, 3
4 are completely point symmetric with respect to the center C of the axis of the crankshaft.

Therefore, in the crankshaft according to the present invention, it can be seen that the arrangement of the balancing weights is completely symmetric when viewed from the center of the shaft.

FIG. 6 shows the arrangement of the first to sixth balancing weights 31 to 36 based on the center C of the shaft in the above-described embodiment.

In the drawing, the first and sixth balancing weights 3
Reference numerals 1 and 36 are point-symmetric with respect to the center C of the axis. Second
Balancing weight 32 is α with respect to a straight line connecting the first center C of the first crank pin 1 around a shaft while positioned on the opposite direction of the second crank pin 2, i.e., about -30 degrees (first 4th crank from crank journal 11
Clockwise when looking toward the journal 14.
(+) And counterclockwise minus (-)
You. ) Located in the a to an imaginary line, the fifth balance weights 35 to line 5, connecting the center C of the center of the axis of the sixth crank pin 6 while positioned on the opposite direction of the sixth crank pin 5 and 6 Te α, that is, the virtual to such an about +30 degrees
It is located on the line and is vertically symmetric. The third balancing weights 33, the third to a line connecting the first and sixth balancing weights 31 and 36, on the opposite side of the fourth crank pin 3 and 4, and, beta (approximately +60 degrees) to a to a virtual
It is located on the line . 4th balancing weight 34
Connects the first and sixth balancing weights 31, 36.
Opposite the third and fourth crankpins 3 and 4 with respect to the line
And on an imaginary line forming β (about -60 degrees)
I have.

In the state shown in FIG. 5, there is no unbalanced couple with respect to the center C of the shaft.

In other words, the unbalance couple against the rotating weight and the reciprocating weight cancel each other at the center C of the shaft, and the unbalance couple against the balancing weight also cancels each other.

However, if the unbalanced couple in the arrangement state shown in FIG. 4 is described with reference to FIG. 7, the unbalanced couple due to the reciprocating weight and the rotating weight occurs in the directions shown by arrows A _{1 to} A _6. The arrow B shows the unbalanced couple caused by the crank arm.
_1, in the direction indicated by B _2, and Fuheiko couple of forces generated by the balancing weights generated in the direction indicated by the arrow D ₁ to D _6.

Therefore, arrows (A ₁ , A ₆ ), (A ₂ ,
A ₅ ), (A ₃ , A ₄ ), (B ₁ , B ₂ ), the couple generated with respect to the center C of the axis are arrows (D ₁ , D ₆ ),
A balance is established by a couple generated at (D ₂ , D ₅ ) and (D ₃ , D ₄ ).

8 to 14 show another embodiment of the crankshaft according to the present invention.

First to sixth crank pins 51 to 56
Are arranged in a group between the first through fourth crank journals 61-64. Adjacent ones of the first to sixth crankpins 1 to 6 and between adjacent ones of the first to sixth crankpins 51 to 56 and the first to fourth crank journals 61 to 64 First to ninth crank arms 71 to 79 are interposed.

A flywheel (not shown) is mounted on a flange 90 formed adjacent to the fourth crank journal 64.

In the crankshaft according to the present embodiment, the first and second crank arms 71 to 72 at the front end of the first to ninth crank arms 71 to 79 respectively have the first and second crank arms 71 to 72.
And second balancing weights 81 and 82 are provided,
Also, intermediate fourth, fifth and sixth crank arms 74 and 7
3rd, 4th, 5th balancing weights 8 at 5, 76
3, 84 and 85 are respectively provided, and the eighth and ninth crank arms 78 and 79 at the rear end are also provided with sixth and seventh balancing weights 86 and 87, respectively.

FIG. 9 is a sectional view of each part of the crankshaft shown in FIG. 8, and the first balancing weight 81 provided to the first crank arm 71 has the center of its weight as shown in FIG. As shown in FIG. 9 (b), the second balancing weight 82, which is located below the center C of the axis of the crankshaft and is given to the second crank arm 72, has its center of weight located below and It is located at a position displaced about 30 ° angle in a counterclockwise direction with respect to the first balancing weight 81.

Next, the third balancing weight 83 given to the fourth crank arm 74 and the fourth and fifth balancing weights 84 and 85 given to the fifth crank arm 75 and the sixth crank arm 76 are respectively FIG.
As shown in (c), (b) and (e), the first balancing weight 81 is located at a position which is displaced approximately 90 degrees clockwise from the center of the weight of the first balancing weight 81, and is therefore located vertically on the left in the orthogonal direction in the figure. I have. In addition, the third balancing weight 83
And the center of the weight of the fifth balancing weight 85 are vertically symmetrical to each other.

On the other hand, the center of the weight of the fourth balancing weight 84 is the third and fifth balancing weights 83 and 8.
5 is located in the middle.

The sixth crank arm 78 has a sixth
The balancing weight 86 is the second weight as shown in FIG.
It is vertically symmetric with respect to the balancing weight 82. The seventh balancing weight 87 provided to the ninth crank arm 79 is vertically symmetric with respect to the first balancing weight 81 as shown in FIG.

The second balancing weight 82 and the sixth balancing weights similar 86-position to a position displaced about 30 ° angle in a clockwise direction with respect to the seventh balancing weights 37
Is placed .

The first balancing weight 81 and the seventh balancing weight 87, the second balancing weight 82, the sixth balancing weight 86, the third balancing weight 83, and the fifth balancing weight 85 are equal to or substantially equal to each other. And the fourth balancing weight 84 has a second primary moment of
The balancing weights 82, 83, 85, and 86 have a mass first moment that balances with each other.

As shown in FIG. 9, the first and second balancing weights 81 and 82 disposed at both ends of the crankshaft are vertically symmetrical, and the third and second balancing weights 81 and 82 are disposed in the middle.
The fourth and fifth balancing weights 83, 84, 85 are first and second balancing weights 81, disposed at both ends.
With respect to the center line of the weight of the 82s, they are located vertically on the left side in the orthogonal direction.

Each balancing weight 81 in FIG.
11 can be shown as shown in FIG.

Looking through this, the first and seventh balancing weights 81 and 87 and the second and sixth balancing weights 82 and 86, and the intermediate third and fifth balancing weights 83 and 85 are mutually connected to the shaft of the crankshaft. It can be seen that they are arranged completely symmetrically with respect to the center C.

Taking the rotation of the crankshaft into consideration, turning 90 degrees in the state shown in FIG. 8 results in FIG. 10, and the arrangement of the balancing weights in this case changes as shown in FIG.

That is, the first and seventh balancing weights 81 and 87 and the second and sixth balancing weights 82,
86, and third and fifth balancing weights 83, 8
5 are completely point symmetric with respect to the center C of the axis of the crankshaft.

Therefore, it can be seen that the arrangement of the balancing weights in the crankshaft according to the present embodiment is completely symmetric when viewed from the center of the shaft.

FIG. 13 shows the arrangement of the first to seventh balancing weights 81 to 87 based on the center C of the shaft in the above-described embodiment.

In the drawing, the first and seventh balancing weights 81 and 87 are point-symmetric with respect to the center C of the axis. The second balancing weight 82 is located in the opposite direction to the first and second crankpins 51 and 52 while the first
Α with respect to a straight line connecting the center C of the center of the axis of emission Kupyn 51, i.e., about -30 degrees (first crank journal 6
When viewed from 1 to 4th crank journal 64
Clockwise plus (+) and counterclockwise
It is assumed to be negative (-). ) Located in the a to an imaginary line, the sixth
The balancing weight 86 is the fifth and sixth crankpin 5
The sixth crank pin 5 while being positioned in the opposite direction
Α with respect to a straight line connecting the center C of the 6 central and the shaft, i.e., located to the virtual line such about +30 degrees, and it has a symmetrical vertically. Third balancing weight 83, the first 及
Beauty seventh balancing weights 81,87 third with respect to the line connecting the on the opposite side of the fourth crank pin 53, and is positioned to an imaginary line that the beta (approximately +60 degrees).
The fifth balancing weight 85 includes the first and seventh balancing weights.
The third and fourth lines are connected to the line connecting the sing weights 81 and 87.
On the opposite side of the crank pins 53 and 54, and β (about -6
(0 degree).

In the state of FIG. 12, there is no unbalanced couple force with respect to the center C of the axis.

In other words, the unbalanced couple due to the rotating weight and the reciprocating weight are mutually offset at the center C of the shaft, and the unbalanced couple due to the balancing weight is also offset to each other.

However, if the unbalanced couple in the arrangement state shown in FIG. 11 is described with reference to FIG. 14, the unbalanced couple due to the reciprocating weight and the rotating weight occurs in the directions shown by arrows A _{1 to} A _6. The arrow B shows the unbalanced couple force caused by the crank arm.
_1, in the direction indicated by B _2, and Fuheiko couple of forces generated by the balancing weights generated in the direction indicated by the arrow D ₁ to D _6.

Therefore, arrows (A ₁ , A ₆ ), (A ₂ ,
A ₅ ), (A ₃ , A ₄ ), (B ₁ , B ₂ ), the couple generated with respect to the center C of the axis are arrows (D ₁ , D ₆ ),
A balance is established by a couple generated at (D ₂ , D ₅ ) and (D ₃ , D ₄ ).

[0063]

As described above, according to the present invention, the inertial couple generated in the crankshaft can be effectively eliminated.
Dynamic balancing between the entire crankshaft and the internal main bearings is achieved in a V6 engine with more optimal balancing weights than conventional crankshaft balancing.

[Brief description of the drawings]

FIG. 1 is a side view of an embodiment of a crankshaft according to a first aspect of the present invention.

FIGS. 2A and 2B are cross-sectional views of various parts of the crankshaft of FIG. 1, wherein FIG. 2A is a cross-sectional view taken along line II of FIG. 1, FIG. 2B is a cross-sectional view taken along line II-II of FIG. III-II in FIG.
FIG. 1D is a sectional view taken along line IV-IV of FIG.
(E) is a sectional view taken along line VV in FIG. 1, (f) is a sectional view taken along line VI-VI in FIG. 1,

FIG. 3 is a plan view of FIG. 1;

FIG. 4 is a schematic diagram schematically showing an arrangement of balancing weights in FIG. 1;

FIG. 5 is a schematic diagram simply showing an arrangement of balancing weights in FIG. 3;

FIG. 6 is a schematic diagram illustrating an arrangement of balancing weights around the crankshaft in the crankshaft of FIG. 1;

FIG. 7 is a schematic diagram showing the magnitude of the centrifugal force of each of the balancing weights shown in FIG. 4;

FIG. 8 is a side view of an embodiment of the crankshaft according to the second aspect of the present invention.

9 is a cross-sectional view of each part of the crankshaft of FIG. 8, (a) is a cross-sectional view taken along line XI-XI of FIG. 8, (b)
8 is a cross-sectional view taken along line XII-XII in FIG. 8, and FIG.
FIG. 8D is a cross-sectional view taken along the line II-XIII, and FIG.
FIG. 8 (e) is a sectional view taken along line XV-XV of FIG. 8,
(F) is a sectional view taken along the line XVI-XVI of FIG. 8, and (g) is a sectional view of FIG.
XVII-XVII line sectional view of

FIG. 10 is a plan view of FIG. 8;

FIG. 11 is a schematic diagram schematically showing an arrangement of balancing weights in FIG. 8;

FIG. 12 is a schematic diagram simply showing an arrangement of balancing weights in FIG. 10;

FIG. 13 is a schematic diagram illustrating an arrangement of balancing weights around the crankshaft in the crankshaft of FIG. 8;

FIG. 14 is a schematic diagram showing the magnitude of centrifugal force and the like of each of the balancing weights shown in FIG. 11;

[Explanation of symbols]

1-6 first through sixth crank pins 11-14 first through fourth crank journals 2 1-29 first to ninth crank arm 31 to 36. The first to sixth balancing weights 51 to 56 first to sixth crank pin 61-64 first through fourth crank jar Anal 7 1-79 first to ninth crank arm 81 to 87 first to seventh balancing weights C crankshaft center α crankshaft center C and the two balancing weights (31 when 32, 35 and 36,81 weigh angle β crankshaft center C and the two balancing weights when the two straight lines connecting the center viewed from the axial direction of the crank shaft structure of the 82, 86 and 87) (33 and 31; 34 and 36 ; 83 and 81; 84
Angle when the secondary straight line connecting the weight center of the 87) is viewed from the axial direction of the crankshaft which constitutes

Claims (11)

(57) [Claims] 1. A first crank pin (1), second class
Crank pin ( 2 ) , third crank pin ( 3 ) , fourth crank pin
Rank pin ( 4 ) , fifth crank pin ( 5 ) and sixth pin
Crank pin ( 6 ) and the first crank journal
( 11 ) , the second crank journal ( 12 ) , the third crank journal
Crank journal ( 13 ) and fourth crank jar
Null ( 14 ) and the first crank arm ( 2
1 ) , the second crank arm ( 22 ) , the third crank
Arm ( 23 ) , fourth crank arm ( 24 ) , fifth
Crank arm ( 25 ) , sixth crank arm ( 2)
6 ) , the seventh crank arm ( 27 ) , the eighth crank
Arm (28) and the ninth a crank shaft with a crank arm (29), the first crank journal (11) a second Kurankuji
The first crank pin between the journal (12) and (1)
A second crank pin ( 2 ) , a second crank journal ( 12 ) and a third crank pin ;
The third crank pin between the journal (13) and (3)
A fourth crank pin ( 4 ) is provided, and a third crank journal ( 13 ) and a fourth crank pin ( 4 ) are provided.
Fifth crank pin between the journal (14) and (5)
A sixth crank pin (6) and is provided between the first crank journal (11) and the first crank pin (1) a first crank arm (21) is a first crank pin ( 1 ) and the second crankpin ( 2 )
Second crank arm (22) is the second crank pin (2) a second crank journal between the
(12) a third crank arm (23) between the, between the second crank journal (12) and the third crank pin (3) is a fourth crank arm (24), Third crank pin ( 3 ) and fourth crank pin ( 4 )
A fifth crank arm ( 25 ) between the fourth crank pin ( 4 ) and a third crank journal.
Between the (13) the sixth crank arm (26) is between the third crank journal (13) and the fifth crank pin (5) is the seventh crank arm (27), Fifth crankpin ( 5 ) and sixth crankpin ( 6 )
Between the eighth crank arm ( 28 ) , the sixth crank pin ( 6 ) and the fourth crank journal.
Between the (14) Ninth crank arm (29) is, At a crankshaft for a V-type 6-cylinder engine respectively provided, are applied to the first crank arm (21), its weight A first balancing weight ( 31 ) whose center is located on the opposite side of the center of the crank journal axis of the crankshaft to the first crankpin ( 1 ) ; and the second crank arm ( 22 ). And the center of the weight is on the same side as the first balancing weight ( 31 ) and the first balancing weight ( 3)
1 ) , from the first crank journal ( 11 )
Look toward the fourth crank journal (14), the counterclockwise direction are arranged in only the angular position displaced a predetermined angle
A second balancing weight ( 32 ), which is provided to each of the fourth crank arm ( 24 ) and the sixth crank arm ( 26 ) , and whose center of weight is the weight of the first balancing weight ( 31 ) . from the center of, as viewed toward the first crank journal (11) to the fourth click <br/> rank journal (14), arranged symmetrically above and below for the imaginary line which is displaced 90 degrees angle clockwise did
The third balancing weight ( 33 ) and the fourth balancing weight
Sing weight and (34); is assigned to the eighth crank arm (28), the temporary
Wherein about a virtual line second balancing weight (3
2) and the fifth balancing <br/> ring weights disposed in a position forming a vertical symmetry (35); issued to the ninth crank arm (29), the temporary
Wherein about a virtual line first balancing weight (3
6. A crankshaft for a V-type six-cylinder engine, comprising: ( 1 ) a sixth balancing weight ( 36 ) arranged in a vertically symmetrical position . 2. The center of the weight of the second balancing weight ( 32 ) with respect to the first balancing weight ( 31 ) moves from the first crank journal ( 11 ) to the fourth crank journal. (14) to look toward a second balancing <br/> Guueito disposed at a position displaced 30 degrees angle in the counterclockwise direction (32); fifth respect sixth balancing weight (36) Bas <br/> weight center of Lansing weight (35) is, when viewed toward the first click <br/> rank journal (11) to the fourth crank journal (14), 30 in the clockwise direction Fifth balancing weight ( 3
5); weight center of the third bus <br/> Lansing weight relative to the first balancing weight (31) (33), first from the first click <br/> rank journal (11) look toward fourth crank journal (14), a third balancing weights disposed in a position displaced 60 degrees angle clockwise (3
3) a; weight center of the fourth Bas <br/> Lansing weight relative to the first balancing weight (31) (34), first from the first click <br/> rank journal (11) look toward fourth crank journal (14), a fourth balancing weights disposed in a position displaced 120 degrees angle clockwise (3
4); and wherein the configuring comprises claim 1, wherein the V-type 6
Crankshaft for cylinder engine. 3. A first balancing weight ( 31 )
V according to claim 1 wherein the sixth balancing weight (3 6), wherein the mass first moment is the same
Type 6 cylinder engine crankshaft. 4. A second balancing weight ( 32 )
The V according to claim 1, characterized in that the fifth balancing weight ( 35 ) has the same first moment of mass.
Type 6 cylinder engine crankshaft. 5. A third balancing weight ( 33 )
V according to claim 1, wherein the fourth balancing weight (3 4), wherein the mass first moment is the same
Type 6 cylinder engine crankshaft. 6.FirstCrank pin(51),Second Qu
Rank pin (52),Third crankpin (53),No.
Four crankpins (54),Fifth crankpin (5
5) And the sixth crankpin (56)WhenThe firstClan
Journal(61),Second crank journal (6
2),Third crank journal (63) And the fourth quarter
Rank Journal (64)WhenAnd the firstcrank
arm(71),Second crank arm (72),Third
The crank arm (73),Fourth crank arm (7
4),Fifth crank arm (75),Sixth crank
arm(76),The seventh crank arm (77),Eighth
The crank arm (78) And ninth crank arm
(79)Crankshaft withAnd,First Crank journal(61) And the second crank
Journal (62)WhenBetweenFirstCrank pin(51)
WhenThe second crankpin (52)WhenIs provided,Second Crank journal(62) And the third crank
Journal (63)WhenBetweenThirdCrank pin(53)
WhenThe fourth crankpin (54)WhenIs provided,Third Crank journal(63) And the fourth crank
Journal (64)WhenBetweenFifthCrank pin(55)
WhenThe sixth crankpin (56)WhenIs provided,First Crank journal(61)WhenFirstCrankpi
N(51)BetweenFirstCrank arm(71)
But,First Crank pin(51)WhenSecondCrank pin(5
2)BetweenSecondCrank arm(72)But,Second Crank pin(52)WhenSecondCrank journal
Le(62)BetweenThirdCrank arm(73)
But,Second Crank journal(62)WhenThirdCrankpi
N(53)Betweenthe fourthCrank arm(74)
But,Third Crank pin(53)Whenthe fourthCrank pin(5
4)BetweenFifthCrank arm(75)But,the fourth Crank pin(54)WhenThirdCrank journal
Le(63)BetweenSixthCrank arm(76)
But,Third Crank journal(63)WhenFifthCrankpi
N(55)BetweenSeventhCrank arm(77)
But,Fifth Crank pin(55)WhenSixthCrank pin(5
6)BetweenEighthCrank arm(78)But,Sixth Crank pin(56)Whenthe fourthCrank journal
Le(64)BetweenNinthCrank arm(79)
However, the crankshaft of the V-6 engine provided
At the footFirstCrank arm(71)Is given to
The center of the crankshaft isCrank journalAxial
Said to the centerFirstCrank pin(51)Opposite to
Located on the side ofFirstBalancing weight(81)
And;SecondCrank arm(72)Is given to
The center of the saidFirstBalancing weight(81)When
On the same side and saidFirstBalancing weight(8
1)AgainstThe firstCrank journal(61)From
the fourthCrank journal(64)Look towards,Anti
ClockwiseOnly a predetermined angleAt the angularly displaced positionThe arranged number
Second balancingweight(82)And;the fourthCrank arm(74)as well asSixthcrank
arm(76)To the center of its weight
But,SaidFirstBalancing weight(81)Of the weight
From the centerThe firstCrank journal(61)FromFourth
ofCrank journal(64)Look towardshand,Clock
Vertically symmetrical with respect to the virtual line displaced 90 degrees
didThirdBalancing weight(83)as well asFifth ba
Lansing weight (85)And;FifthCrank arm(75)Is given to
The center of the,SaidFirstBalancing weight(81)
From the center of weightThe firstCrank journal(61)
Fromthe fourthCrank journal(64)Look towards
hand,90 degree angular displacement clockwiseVirtual linePlaced aboveNo.
FourBalancing weight(84)And;EighthCrank arm(78)Granted toSaid provisional
Focusing on thought linesSaidSecondBalancing weight(8
2)WhenVertically symmetricSixth placed in positionBalance
Ng weight(86)And;NinthCrank arm(79)Granted toSaid provisional
Focusing on thought linesSaidFirstBalancing weight(8
1) andVertically symmetricSeventh placed in positionBalance
Ng weight(87)And characterized by comprising
The crankshaft of a V-type 6-cylinder engine. 7. The center of the weight of the second balancing weight ( 82 ) with respect to the first balancing weight ( 81 ) moves from the first crank journal ( 61 ) to the fourth crank journal. look toward (64), a second balancing <br/> Guueito disposed at a position displaced 30 degrees angle in the counterclockwise direction (82); the relative seventh balancing weights (8 7) weight center of the sixth Bas <br/> Lansing weight (8 6), as viewed toward the first click <br/> rank journal (61) to the fourth crank journal (64), clockwise The sixth balancing weight ( 8
6); weight center of the third bus <br/> Lansing weight relative to the first balancing weight (81) (83) is, first from the first click <br/> rank journal (61) look toward fourth crank journal (64), a third balancing weights disposed in a position displaced 60 degrees angle in the clockwise direction (8
3) a; weight center of the fourth Bas <br/> Lansing weight relative to the first balancing weight (81) (84), first from the first click <br/> rank journal (61) look toward fourth crank journal (64), fifth balancing way bets placed at a position displaced 120 degrees angle in the clockwise direction (8
5); weight center of the fourth Bas <br/> Lansing weight relative to the first balancing weight (81) (84), first from the first click <br/> rank journal (61) fourth look toward the crank journal (64), a fourth balancing weights arranged on a virtual line that is displaced 90 degrees angle in the clockwise direction (8
4); and wherein the configuring comprises claims 6 V type according 6
Crankshaft for cylinder engine. 8. A first balancing weight ( 81 ) .
7. The V according to claim 6, wherein the first moment of mass is the same as the seventh balancing weight ( 87 ).
Type 6 cylinder engine crankshaft. 9. A second balancing weight ( 82 ) and
Sixth V of claim 6, wherein balancing the weight (86), wherein the mass first moment is the same
Type 6 cylinder engine crankshaft. 10. A third balancing weight ( 83 ).
The crankshaft of a V-type six-cylinder engine according to claim 6, wherein the first balancing moment and the fifth balancing weight ( 85 ) have the same mass first moment. 11. A fourth balancing weight ( 84 ).
Is the second balancing weight ( 82 ) and the third rose
Nothing Weight ( 83 ) , Fifth Balancing Way
A crankshaft for a V-type six-cylinder engine according to claim 6, characterized in that the crankshaft has a mass first moment which is such that it is in equilibrium with the third balancing weight ( 85 ) and the sixth balancing weight ( 86 ) .