CN102537020B - Straight six-cylinder internal combustion engine crank shaft with differential balance blocks - Google Patents
Straight six-cylinder internal combustion engine crank shaft with differential balance blocks Download PDFInfo
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- CN102537020B CN102537020B CN201210043535.8A CN201210043535A CN102537020B CN 102537020 B CN102537020 B CN 102537020B CN 201210043535 A CN201210043535 A CN 201210043535A CN 102537020 B CN102537020 B CN 102537020B
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Abstract
The invention discloses a straight six-cylinder internal combustion engine crank shaft with differential balance blocks. The straight six-cylinder internal combustion engine crank shaft comprises a crank shaft (1), wherein a first cylinder crank (4), a third cylinder crank (5), a fourth cylinder crank (6) and a sixth cylinder crank (7) are sequentially arranged on the crank shaft (1); and a large balance block (2) and a small balance block (3) are arranged on the each of the first cylinder crank (4), the third cylinder crank (5), the fourth cylinder crank (6) and the sixth cylinder crank (7). Since the large balance block (2) and the small balance block (3) are arranged on each of the first cylinder crank (4), the third cylinder crank (5), the fourth cylinder crank (6) and the sixth cylinder crank (7), the balance blocks on different cranks are arranged differentially according to difference of effects for balancing the inner bending moment of the crank shaft by the balance blocks at different positions, and the overall weight of the crank shaft is reduced, the moment generated by the balance blocks is increased, the utilization efficiency of the balance blocks is improved, the self-vibration frequency of an engine shaft system is increased, and the torsional vibration levelness and the strength reliability of the crank shaft are improved.
Description
Technical field
The present invention relates to a kind of I. C. engine crankshaft, relate in particular to a kind of six-in-line I. C. engine crankshaft with differentiation equilibrium block.
Background technique
The torsional oscillation level of I. C. engine crankshaft and strength reliability directly have influence on the performance and used life of motor, and car load stationarity and comfort level, due to the structural feature of bent axle, in crankshaft rotating working procedure, in the situation that meeting outside bent axle balance, on each cross section of bent axle, be still subject to the interior moment of flexure that crank throw centrifugal force causes, under interior Moment, bent axle can produce bending in work engineering, and the deflection of crankshaft on this microcosmic can exert an influence to the force-bearing situation lubricated, bearing support of the load of bent axle, bearing.Control the main method of moment of flexure in bent axle and on bent axle, arrange exactly equilibrium block, traditional six-in-line I. C. engine crankshaft equilibrium block mainly adopts eight equilibrium block arrangements, on the crank of the 1st cylinder, the 3rd cylinder, the 4th cylinder, the 6th cylinder, arrange respectively equilibrium block, and the size of each equilibrium block is basic identical.In but crankshaft counter balance is subject to interior moment of flexure, the distortion of control deflection of crankshaft in reduction bent axle working procedure, also can increase weight and the rotary inertia of bent axle, the cost of bent axle is increased, torsion frequency reduces.
As Chinese patent notification number: CN201125933Y, open day: the utility model patent on October 1st, 2008 discloses a kind of automobile engine crankshaft, comprise main shaft, it is characterized in that: on main shaft, have eight equilibrium blocks, adjacently between equilibrium block, connected by four pitman shafts between two, four pitman shafts are along the upper and lower balance of main shaft, between main shaft and pitman shaft, communicated by oil duct, bent axle adopts the full equilibrium structure of eight equilibrium blocks, adopt different equilibrium block thickness according to different diameter of axle loads simultaneously, under the prerequisite that meets positive machine balance requirement, effectively alleviate the weight of bent axle, between each main shaft and pitman shaft, communicated by oil duct, ensure the lubricated of bent axle and connecting rod.But the counterbalance size of this device is basic identical, and do not have differentiation to arrange, make gross weight larger, the utilization ratio of counterbalance is not high, is unfavorable for improving the torsional oscillation level of bent axle.
Summary of the invention
The object of the invention is basic identical for existing equilibrium block size and do not have differentiation to arrange, make gross weight larger, the defect that the utilization ratio of equilibrium block is not high and deficiency, provide a kind of simple in structure, equilibrium block has been carried out to differentiation layout, increase the moment that equilibrium block produces, a kind of six-in-line I. C. engine crankshaft with differentiation equilibrium block that equilibrium block utilization ratio is higher.
For achieving the above object, technical solution of the present invention is: a kind of six-in-line I. C. engine crankshaft with differentiation equilibrium block, comprise bent axle, on bent axle, be disposed with the first cylinder crank, the 3rd cylinder crank, the 4th cylinder crank and the 6th cylinder crank, described the first cylinder crank, the 3rd cylinder crank, on the 4th cylinder crank and the 6th cylinder crank, be respectively arranged with a large equilibrium block and a little equilibrium block, on the outboard end of the first cylinder crank, be fixed with large equilibrium block, the other end of the first cylinder crank is fixed with little equilibrium block, one side of the end of the 3rd cylinder crank and close the first cylinder crank is fixed with little equilibrium block, the other end of the 3rd cylinder crank is fixed with large equilibrium block, one side of the end of the 4th cylinder crank and close the 3rd cylinder crank is fixed with large equilibrium block, the opposite side of the 4th cylinder crank is fixed with little equilibrium block, one side of the end of the 6th cylinder crank and close the 4th cylinder crank is fixed with little equilibrium block, the opposite side of the 6th cylinder crank is fixed with large equilibrium block.
The large equilibrium block width of described large equilibrium block is 3:2-2:1 with the ratio of the little equilibrium block width of little equilibrium block.
The invention has the beneficial effects as follows:
1. the present invention is respectively arranged with a large equilibrium block and a little equilibrium block on the first cylinder crank, the 3rd cylinder crank, the 4th cylinder crank and the 6th cylinder crank, according to the difference of moment of flexure effect in equilibrium block balance crankshaft on diverse location, equilibrium block on different cranks is carried out to differentiation layout.
2. the present invention is simple in structure, has alleviated the overall weight of bent axle, has increased the moment that equilibrium block produces, and is conducive to improve the utilization ratio of equilibrium block, has improved the natural frequency of vibration of engine shaft system, has improved torsional oscillation level and the strength reliability of bent axle.
Brief description of the drawings
Fig. 1 is the structural representation of invention.
Fig. 2 is the structural representation of the large equilibrium block 2 of the present invention.
Fig. 3 is the structural representation of the little equilibrium block 3 of the present invention.
In figure: bent axle 1, large equilibrium block 2, little equilibrium block 3, the first cylinder crank 4, the three cylinder crank 5, the four cylinder crank 6, the six cylinder cranks 7, large equilibrium block width L1, little equilibrium block width L2.
Embodiment
Below in conjunction with brief description of the drawings and embodiment, the present invention is described in further detail.
Referring to Fig. 1 to Fig. 3, a kind of six-in-line I. C. engine crankshaft with differentiation equilibrium block of the present invention, comprise bent axle 1, on bent axle 1, be disposed with the first cylinder crank 4, the 3rd cylinder crank 5, the 4th cylinder crank 6 and the 6th cylinder crank 7, described the first cylinder crank 4, the 3rd cylinder crank 5, on the 4th cylinder crank 6 and the 6th cylinder crank 7, be respectively arranged with a large equilibrium block 2 and a little equilibrium block 3, on the outboard end of the first cylinder crank 4, be fixed with large equilibrium block 2, the other end of the first cylinder crank 4 is fixed with little equilibrium block 3, one side of the end of the 3rd cylinder crank 5 and close the first cylinder crank 4 is fixed with little equilibrium block 3, the other end of the 3rd cylinder crank 5 is fixed with large equilibrium block 2, one side of the end of the 4th cylinder crank 6 and close the 3rd cylinder crank 5 is fixed with large equilibrium block 2, the opposite side of the 4th cylinder crank 6 is fixed with little equilibrium block 3, one side of the end of the 6th cylinder crank 7 and close the 4th cylinder crank 6 is fixed with little equilibrium block 3, the opposite side of the 6th cylinder crank 7 is fixed with large equilibrium block 2.
The large equilibrium block width L1 of described large equilibrium block 2 is 3:2-2:1 with the ratio of the little equilibrium block width L2 of little equilibrium block 3.
On bent axle 1, be disposed with the first cylinder crank 4, the 3rd cylinder crank 5, the 4th cylinder crank 6 and the 6th cylinder crank 7, according to the mechanism of moment of flexure in crankshaft counter balance balance crankshaft, the efficiency difference of moment of flexure in equilibrium block balance crankshaft on diverse location is respectively arranged with a large equilibrium block 2 and a little equilibrium block 3 on the first cylinder crank 4, the 3rd cylinder crank 5, the 4th cylinder crank 6 and the 6th cylinder crank 7.Wherein, on two cranks of the first cylinder crank 4 and the 3rd cylinder crank 5 apart from each others, be provided with large equilibrium block 2, on two nearer cranks, be provided with little equilibrium block 3.The large equilibrium block width L1 of large equilibrium block 2 is 3:2-2:1 with the ratio of the little equilibrium block width L2 of little equilibrium block 3.According to the difference of moment of flexure effect in equilibrium block balance crankshaft on diverse location, equilibrium block on different cranks is carried out to differentiation layout.
Between the first cylinder crank 4 and the 3rd cylinder crank 5, it is the second cylinder, on the corresponding bent axle 1 of the second cylinder, equilibrium block is not set, between the 4th cylinder crank 6 and the 6th cylinder crank 7, it is the 5th cylinder, on the corresponding bent axle 1 of the 5th cylinder, equilibrium block is not set yet, can adopts this arrangement for the bent axle of six-in-line internal-combustion engine.
On the outboard end of the first cylinder crank 4, be fixed with large equilibrium block 2, the other end of the first cylinder crank 4 is fixed with little equilibrium block 3, one side of the end of the 3rd cylinder crank 5 and close the first cylinder crank 4 is fixed with little equilibrium block 3, the other end of the 3rd cylinder crank 5 is fixed with large equilibrium block 2, one side of the end of the 4th cylinder crank 6 and close the 3rd cylinder crank 5 is fixed with large equilibrium block 2, the opposite side of the 4th cylinder crank 6 is fixed with little equilibrium block 3, one side of the end of the 6th cylinder crank 7 and close the 4th cylinder crank 6 is fixed with little equilibrium block 3, the opposite side of the 6th cylinder crank 7 is fixed with large equilibrium block 2.So just the effective mass of more equilibrium blocks is arranged on the crank of apart from each other, increase the moment that equilibrium block produces, be conducive to improve the utilization ratio of equilibrium block, improved the natural frequency of vibration of engine shaft system, improved torsional oscillation level and the strength reliability of bent axle 1.
Claims (2)
1. the six-in-line I. C. engine crankshaft with differentiation equilibrium block, comprise bent axle (1), on bent axle (1), be disposed with the first cylinder crank (4), the 3rd cylinder crank (5), the 4th cylinder crank (6) and the 6th cylinder crank (7), it is characterized in that: described the first cylinder crank (4), the 3rd cylinder crank (5), on the 4th cylinder crank (6) and the 6th cylinder crank (7), be respectively arranged with a large equilibrium block (2) and a little equilibrium block (3), on the outboard end of described the first cylinder crank (4), be fixed with large equilibrium block (2), the other end of the first cylinder crank (4) is fixed with little equilibrium block (3), one side of the end of the 3rd cylinder crank (5) and close the first cylinder crank (4) is fixed with little equilibrium block (3), the other end of the 3rd cylinder crank (5) is fixed with large equilibrium block (2), one side of the end of the 4th cylinder crank (6) and close the 3rd cylinder crank (5) is fixed with large equilibrium block (2), the opposite side of the 4th cylinder crank (6) is fixed with little equilibrium block (3), one side of the end of the 6th cylinder crank (7) and close the 4th cylinder crank (6) is fixed with little equilibrium block (3), the opposite side of the 6th cylinder crank (7) is fixed with large equilibrium block (2).
2. a kind of six-in-line I. C. engine crankshaft with differentiation equilibrium block according to claim 1, is characterized in that: the large equilibrium block width (L1) of described large equilibrium block (2) is 3:2-2:1 with the ratio of the little equilibrium block width (L2) of little equilibrium block (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210043535.8A CN102537020B (en) | 2012-02-24 | 2012-02-24 | Straight six-cylinder internal combustion engine crank shaft with differential balance blocks |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210043535.8A CN102537020B (en) | 2012-02-24 | 2012-02-24 | Straight six-cylinder internal combustion engine crank shaft with differential balance blocks |
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| Publication Number | Publication Date |
|---|---|
| CN102537020A CN102537020A (en) | 2012-07-04 |
| CN102537020B true CN102537020B (en) | 2014-06-25 |
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| CN201210043535.8A Active CN102537020B (en) | 2012-02-24 | 2012-02-24 | Straight six-cylinder internal combustion engine crank shaft with differential balance blocks |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9482307B2 (en) | 2014-11-26 | 2016-11-01 | Caterpillar Inc. | Multi-cylinder engine crankshaft torsional vibration absorber and balancer and process thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6688272B2 (en) * | 2002-05-29 | 2004-02-10 | Ford Global Technologies, Llc | Crankshaft assembly for enabling engine cylinder deactivation |
| EP1750023A1 (en) * | 2005-08-01 | 2007-02-07 | Kabushiki Kaisha Toyota Jidoshokki | Crankshaft for V-type six-cylinder engine |
| EP1881212B1 (en) * | 2006-07-17 | 2009-01-07 | Peugeot Citroën Automobiles S.A. | Crankshaft with balance weight mounted on flanges for absorbing vibration transmitted to the cylinder block of an internal combustion engine |
| CN201636193U (en) * | 2009-12-15 | 2010-11-17 | 奇瑞汽车股份有限公司 | Forging crankshaft of in-line six cylinder engine |
| CN202468677U (en) * | 2012-02-24 | 2012-10-03 | 东风汽车有限公司 | In-line six-cylinder internal combustion engine crankshaft with differential balance blocks |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100535023B1 (en) * | 2002-10-31 | 2005-12-07 | 현대자동차주식회사 | crankshaft having damper |
| JP2010209969A (en) * | 2009-03-09 | 2010-09-24 | Toyota Motor Corp | Crankshaft |
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2012
- 2012-02-24 CN CN201210043535.8A patent/CN102537020B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6688272B2 (en) * | 2002-05-29 | 2004-02-10 | Ford Global Technologies, Llc | Crankshaft assembly for enabling engine cylinder deactivation |
| EP1750023A1 (en) * | 2005-08-01 | 2007-02-07 | Kabushiki Kaisha Toyota Jidoshokki | Crankshaft for V-type six-cylinder engine |
| EP1881212B1 (en) * | 2006-07-17 | 2009-01-07 | Peugeot Citroën Automobiles S.A. | Crankshaft with balance weight mounted on flanges for absorbing vibration transmitted to the cylinder block of an internal combustion engine |
| CN201636193U (en) * | 2009-12-15 | 2010-11-17 | 奇瑞汽车股份有限公司 | Forging crankshaft of in-line six cylinder engine |
| CN202468677U (en) * | 2012-02-24 | 2012-10-03 | 东风汽车有限公司 | In-line six-cylinder internal combustion engine crankshaft with differential balance blocks |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9482307B2 (en) | 2014-11-26 | 2016-11-01 | Caterpillar Inc. | Multi-cylinder engine crankshaft torsional vibration absorber and balancer and process thereof |
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| CN102537020A (en) | 2012-07-04 |
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Owner name: DONGFENG CAR CO. Free format text: FORMER OWNER: DONGFENG AUTOMOBILE CO., LTD. Effective date: 20130814 |
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Effective date of registration: 20130814 Address after: 430056 Wuhan economic and Technological Development Zone, Hubei Province, Dongfeng Road, No. 1, No. Applicant after: Dongfeng Motor Corporation Address before: 430056 Dongfeng Road, Wuhan Economic Development Zone, Hanyang District, Hubei, China, No. 10, No. Applicant before: DONGFENG MOTER Co.,Ltd. |
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Address after: 430056 No. 1 Dongfeng Avenue, Wuhan economic and Technological Development Zone, Hubei, Wuhan Patentee after: DONGFENG MOTOR Corp. Address before: 430056 No. 1 Dongfeng Avenue, Wuhan economic and Technological Development Zone, Hubei, Wuhan Patentee before: Dongfeng Motor Corporation |
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