EP1387059A1 - 10-Zylinder-Verbrennungsmotor - Google Patents
10-Zylinder-Verbrennungsmotor Download PDFInfo
- Publication number
- EP1387059A1 EP1387059A1 EP03014997A EP03014997A EP1387059A1 EP 1387059 A1 EP1387059 A1 EP 1387059A1 EP 03014997 A EP03014997 A EP 03014997A EP 03014997 A EP03014997 A EP 03014997A EP 1387059 A1 EP1387059 A1 EP 1387059A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cylinder
- offset
- order
- internal combustion
- combustion engine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
Definitions
- the invention relates to a 10-cylinder internal combustion engine with two in relation on a crankshaft V-shaped cylinder banks of five in a row arranged cylinders. Furthermore, the invention relates to one for one such a suitable crankshaft engine.
- Such 10-cylinder V engines are generally known in the art however in the area of contemporary passenger cars only little spread, because at higher numbers of cylinders, mainly eight or twelve cylinders can be selected. by virtue of of the space for the engine, which is often very limited in passenger cars nowadays with higher numbers of cylinders almost exclusively V arrangements for Commitment. Because such engines are mainly used in luxury vehicles smooth engine running plays a major role. It will therefore Aimed at cylinder arrangements in which the free forces and moments are first and second order either very small due to the design and preferably to zero or be compensated for by the simplest possible measures can.
- V-12 arrangement with two is particularly favorable Cylinder banks in the form of two in-line six-cylinder arrangements, since this The free forces and moments of the first and second order are due to the design Become zero, which means that additional compensatory measures can in principle be eliminated.
- a V-8 arrangement allows free forces and / or moments depending on the V-inclusion angle not avoid completely. The only exception to this V-8 arrangements with an included angle ⁇ of 90 °, in which the Mass moments of first and second order on the crankshaft can be compensated.
- the object of the invention is a V-10 To create an engine concept that with the least possible effort Balance of mass effects allowed.
- a 10-cylinder internal combustion engine in which for each Cylinder bank on the crankshaft, which has a crank for each cylinder, an uneven division of the offset angle is provided such that for each Cylinder bank the mass effects of second order at least almost completely are balanced, which continues in a normal plane of the crankshaft projected offset angles are the same for both cylinder banks, and at finally the crankings for the two cylinder banks on the crankshaft are arranged so that the negative circumferential portion of the mass moments first Order or the first order mass forces at least almost completely disappears.
- This motor concept enables a basic motor with no mass impact selectable V-angle.
- the mass effects are second order, i. H. the Free forces and moments of the second order already via the respective cylinder bank balanced.
- the resulting first order mass effects of the two Inline five-cylinder banks can be described as positive and negative revolving power and Take up first-order moment vectors.
- Any remaining First-order mass forces, especially positive first-order mass forces Order, or mass moments of the first order can be achieved by simple Measures, for example by counterweights on the cranks or on the Crankshaft are balanced.
- cranks are preferably arranged such that the negative circumference Proportion of the first order mass moments becomes zero, so that at most one First order mass forces would have to be balanced.
- cranks in which the negative circumferential portion of the first order mass forces becomes zero.
- Remaining first-order mass effects can also be targeted Reduction of the mass effect of other engine components, for example the Use the mass effects of the valve train.
- the oscillating masses and / or the stroke on each middle cylinders of the cylinder banks are increased so that the free forces first order are balanced on each cylinder bank.
- the offset angles are for one cylinder bank to the offset angles of the other cylinder bank with respect to the medium offset reflected.
- the arrangement of the cranks is preferred for the second cylinder bank from the arrangement of the cranks for the first cylinder bank arithmetically obtained, in which all the crankings of the second cylinder bank an offset angle to the cranks of the first cylinder bank are rotated and then on the second cylinder bank the angles for the first and fifth as well as swapping the second and fourth crank, i.e. in terms of the middle Cranking can be mirrored.
- the negative circumferences can be offset in a particularly simple manner completely compensate for free mass moments of the first order. However stay receive negative orbiting free mass forces of the first order.
- a disappearance of the negative rotating parts of the free forces of the first order is preferably realized in that the crankings of one cylinder bank each by the same offset angle ⁇ compared to the corresponding one Crank on the other cylinder bank can be arranged twisted.
- ⁇ represents the V-inclusion angle between the cylinder banks.
- a similar effect can be achieved by varying individual offset angles ⁇ one or both of the cylinder banks with respect to mass effects second Achieve order to achieve corresponding second-order mass effects from others Compensate engine components. It is particularly possible for one operating state to be selected, for example a defined speed, this other mass effects completely in the first order and in the second Compensate order at least partially.
- cranks of a cylinder bank are the angular difference amounts to the mean crank same size.
- the cranks are preferably chosen so that on both The angle differences to the mean offset for the first and the cylinder banks fifth crank and continue for the second and fourth crank respectively are equal in amount to each other, but differ according to their sign differ.
- the first-mentioned offset angle arrangement proves particularly in Connection with an only phase-shifted, not mirrored Arrangement of the offset angle for the two cylinder banks as favorable, since this the crankings for a cylinder bank are relatively even on the circumference of the crankshaft are distributed, thus the distances between the crankings of a cylinder bank little to each other of an integer multiple of 72 degrees, d. H. one complete uniform distribution, deviate.
- crankshaft favors Furthermore, the solution of the above object is achieved by the in the claims defined crankshaft favors.
- the preferred exemplary embodiments explained in more detail below relate each to a person not shown in the figures, but to a person skilled in the art principally known 10-cylinder internal combustion engine. Its cylinders are in two Cylinder banks arranged in a V-shape next to each other, the cylinder banks Depending on the example, include a V-angle ⁇ of 36 °, 72 °, 90 °, 144 ° or 108 °. Of the angular sizes given here as an example, however, can easily be in one wide range.
- Pistons arranged in the cylinders are each via a crank mechanism with a Crankshaft connected.
- This crankshaft has a crank for each cylinder, on which the respective crank drive engages.
- the exemplary embodiments are based on the consideration for each cylinder bank to provide an uneven pitch of the crank angle ⁇ on the crankshaft is chosen such that the mass effects alone for each cylinder bank second order, that is, the free mass forces and mass moments of the second Order are almost or preferably completely balanced. For this are the in a normal plane of the crankshaft projected offset angle ⁇ - without viewing the order of the crankings - the same for both cylinder banks.
- the offset angle ⁇ for both cylinder banks are always based on the first physical offset Axial direction of the crankshaft.
- all of the exemplary embodiments have in common the cranks for the two Arrange cylinder banks on the crankshaft in such a way that the negative rotating one Share of the resulting first order mass forces and / or the mass moments first order at least almost completely disappears.
- the negative circumferential portion of the first order mass moments becomes two cylinder banks by mirroring the offset angle with respect to the middle or third offset for a cylinder bank and / or by a Phase shift by an offset angle ⁇ of the cranks between the Cylinder banks made zero or at least on a negligibly small one Value reduced.
- a negative circumferential first order mass moment of 160 Nm and a positive circumferential first order mass moment of 515 Nm can be achieved, but there are second order moments in the order of 540 Nm negative circumferential direction and 1420 Nm in positive circumferential direction at an ignition distance of 72 °.
- the circumferential second order moments in both directions can be reduced to around 100 Nm at ignition intervals of 54 ° and 90 °, but the positive first order moment is 4943 Nm.
- a longitudinal reflection of the offset angle ⁇ is provided.
- the arrangement of the cranks for the second cylinder bank can thus be obtained from the arrangement of the cranks for the first cylinder bank by first rotating all the cranks by an offset angle ⁇ and then swapping the angles for the first and fifth as well as the second and fourth cranks , ie be reflected in relation to the middle, third offset.
- Table 1 shows, free forces are retained in the first two exemplary embodiments.
- the first exemplary embodiment performs somewhat better because of the more even distribution of the crankings around the crankshaft.
- Cranking arrangements in which the cranking angles ⁇ j of the second cylinder bank are obtained from the cranking angles ⁇ i of the first cylinder bank solely by a phase shift by the specified displacement angle ⁇ j are more favorable in this regard.
- Table 1 shows, arrangements with a more even distribution of the cranking, i.e. those in which the cranking angles are only slightly spaced apart from one another by an integral multiple of 72 °, tend to be more favorable (see exemplary embodiments 3, 4 and 5) than more irregular arrangements according to working examples 6 and 7.
- Example 9 is based on Example 1, but has twice the V-inclusion angle ⁇ . Examples 10 and 11 were compared to Examples 1 and 9 Variation of the oscillating masses made to the remaining, negative to eliminate all-round free forces.
- Corresponding designs can be used for V-angles ⁇ of 216 ° and 288 ° form. They correspond to Examples 1, 9, 10 and 11, each with an exchange of the cylinder banks and allow 4/9 or 5/10 crank pins with ⁇ of about 0 °.
- the increase in the oscillating masses on the bends 3 and 8 can be replaced by an increase in the stroke of 9% on the associated cylinders 3 and 8 compared to Examples 10 and 11.
- This is expediently combined with a corresponding shortening of the connecting rods, so that the top dead center (compression) remains at almost the same height.
- This changes the offset angle ⁇ i only slightly, as example 12 shows.
- the ignition sequence corresponds to example 11. The advantage of this is the avoidance of ballast.
- examples 1 and 3 and 8 to 11 with the most uniform firing intervals are the most favorable, as can be seen in Table 3 with the firing sequences likewise given there.
- these examples are advantageous because the crankshaft angle deviates only slightly from 72 ° with regard to the second engine order.
- All of the exemplary embodiments are characterized by extensive compensation the mass action in the first and second order. Any remaining Residual forces and / or residual moments can be reduced by simple measures, for example, counterweights on the crankshaft and / or the crank drives very much just balance.
Abstract
Description
- erste Kröpfung: 0,00°
- zweite Kröpfung: 70,12°
- dritte Kröpfung: 283,72°
- vierte Kröpfung: 137,33°
- fünfte Kröpfung: 207,45°.
- erste Kröpfung: 0,00°
- zweite Kröpfung: 109,88°
- dritte Kröpfung: 256,28°
- vierte Kröpfung: 42,67°
- fünfte Kröpfung: 152,55°.
- Figur 1a
- eine schematische Darstellung einer Kurbelwelle mit für die Zylinderbänke gespiegelten Kröpfungen nach einem ersten Ausführungsbeispiel der Erfindung,
- Figur 1b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 1a,
- Figur 2a
- eine schematische Darstellung einer Kurbelwelle mit gespiegelten Kröpfungen nach einem zweiten Ausführungsbeispiel der Erfindung,
- Figur 2b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 2a,
- Figur 3a
- eine schematische Darstellung einer Kurbelwelle mit für die Zylinderbänke phasenverschobenen Kröpfungen nach einem dritten Ausführungsbeispiel der Erfindung,
- Figur 3b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 3a,
- Figur 4a
- eine schematische Darstellung einer Kurbelwelle mit phasenverschobenen Kröpfungen nach einem vierten Ausführungsbeispiel der Erfindung,
- Figur 4b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 4a,
- Figur 5a
- eine schematische Darstellung einer Kurbelwelle mit phasenverschobenen Kröpfungen nach einem fünften Ausführungsbeispiel der Erfindung,
- Figur 5b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 5a,
- Figur 6a
- eine schematische Darstellung einer Kurbelwelle mit phasenverschobenen Kröpfungen nach einem sechsten Ausführungsbeispiel der Erfindung,
- Figur 6b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 6a,
- Figur 7a
- eine schematische Darstellung einer Kurbelwelle mit phasenverschobenen Kröpfungen nach einem siebten Ausführungsbeispiel der Erfindung,
- Figur 7b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 7a.
- Figur 8a
- eine schematische Darstellung einer Kurbelwelle mit für die Zylinderbänke phasenverschobenen Kröpfungen nach einem achten Ausführungsbeispiel der Erfindung,
- Figur 8b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 8a,
- Figur 9a
- eine schematische Darstellung einer Kurbelwelle mit gespiegelten Kröpfungen nach einem neunten Ausführungsbeispiel der Erfindung,
- Figur 9b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 9a,
- Figur 10a
- eine schematische Darstellung einer Kurbelwelle mit erhöhter oszillierender Masse an den mittleren Zylindern der Zylinderbänke nach einem zehnten Ausführungsbeispiel der Erfindung,
- Figur 10b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 10a,
- Figur 11a
- eine schematische Darstellung einer Kurbelwelle mit erhöhter oszillierender Masse an den mittleren Zylindern der Zylinderbänke nach einem elften Ausführungsbeispiel der Erfindung,
- Figur 11b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 11a,
- Figur 12a
- eine schematische Darstellung einer Kurbelwelle mit erhöhtem Hub an den mittleren Zylindern der Zylinderbänke nach einem zwölften Ausführungsbeispiel der Erfindung, und in
- Figur 10b
- den Kurbelstern erster Ordnung zu der Kurbelwelle aus Figur 12a.
Ausf.-beispiel (Figur Nr.)i V-Winkel γ | Kröpfungsnummer i für erste Zylinderbank (Kröpfungswinkel ϕi)/ Kröpfungsnummer j für zweite Zylinderbank (Versetzungswinkel δj) | Freie Kräfte erster Ordnung [N] Umlaufrichtung | Freie Momente erster Ordnung [Nm]Umlaufric htung | |||||||
1/6 | 2/7 | 3/8 | 4/9 | 5/10 | pos. | neg. | pos. | neg. | ||
1/72° | Kröpfungswinkel ϕi | 0,00 | 70,12 | 283,72 | 137,33 | 207,45 | 599 | 1937 | 4713 | 0 |
Versetzungswinkel δj | 351,45 | 211,21 | 144,00 | 76,79 | 296,55 | |||||
2/72° | Kröpfungswinkel ϕi | 0,00 | 109,88 | 256,28 | 42,67 | 152,55 | 3569 | 11548 | 2625 | 0 |
Versetzungswinkel δj | 296,55 | 76,79 | 144,00 | 211,21 | 351,45 | |||||
3/108° | Kröpfungswinkel ϕi | 0,00 | 70,12 | 283,72 | 137,33 | 207,45 | 1843 | 7 | 4718 | 0 |
Versetzungswinkel δj | 36,00 | 36,00 | 36,00 | 36,00 | 36,00 | |||||
4/72° | Kröpfungswinkel ϕi | 0,00 | 70,12 | 283,72 | 137,33 | 207,45 | 1843 | 7 | 4707 | 0 |
Versetzungswinkel δj | 324,00 | 324,00 | 324,00 | 324,00 | 324,00 | |||||
5/90° | Kröpfungswinkel ϕi | 0,00 | 70,12 | 283,72 | 137,33 | 207,45 | 1937 | 0 | 4955 | 17 |
Versetzungswinkel δj | 0,00 | 0,00 | 0,00 | 0,00 | 0,00 | |||||
6/108° | Kröpfungswinkel ϕi | 0,00 | 109,88 | 256,28 | 42,67 | 152,55 | 10983 | 0 | 2655 | 100 |
Versetzungswinkel δj | 36,00 | 36,00 | 36,00 | 36,00 | 36,00 | |||||
7/72° | Kröpfungswinkel ϕi | 0,00 | 109,88 | 256,28 | 42,67 | 152,55 | 10983 | 0 | 2591 | 100 |
Versetzungswinkel δj | 324,00 | 324,00 | 324,00 | 324,00 | 324,00 |
Ausf.-beispiel (Figur Nr.)/ V-Winkel γ | Kröpfungsnummer i für erste Zylinderbank (Kröpfungswinkel ϕi)/ Kröpfungsnummer j für zweite Zylinderbank (Versetzungswinkel δj) | Freie Kräfte erster Ordnung [N] Umlaufrichtung | Freie Momente erster Ordnung [Nm] Umlaufrichtung | |||||||
1/6 | 2/7 | 3/8 | 4/9 | 5/10 | pos. | neg. | pos. | neg. | ||
8/36° | Kröpfungswinkel ϕi | 0,00 | 70,12 | 283,72 | 137,33 | 207,45 | 1139 | 3 | 2899 | 9 |
Versetzungswinkel δj | 252 | 252 | 252 | 252 | 252 | |||||
9/144° | Kröpfungswinkel ϕi | 0,00 | 70,12 | 283,72 | 137,33 | 207,45 | 1567 | 1937 | 2912 | 0 |
Versetzungswinke δj | 135,45 | 355,21 | 288,00 | 220,79 | 80,55 | |||||
10/72° | Kröpfungswinkel ϕi | 0,00 | 68,33 | 284,17 | 140,01 | 208,34 | 3 | 9 | 4766 | 0 |
Versetzungswinkel δj | 352,34 | 215,68 | 144,00 | 72,32 | 295,66 | |||||
11/144° | Kröpfungswinkel ϕi | 0,00 | 68,33 | 284,17 | 140,01 | 208,34 | 3 | 1 | 2946 | 0 |
Versetzungswinkel δj | 136,34 | 359,68 | 288,00 | 216,32 | 79,66 | |||||
12/72° | Kröpfungswinkel ϕi | 0,00 | 67,01 | 284,43 | 141,84 | 208,85 | 0 | 1 | 4803 | 0 |
Versetzungswinkel δj | 352,85 | 218,83 | 144,00 | 69,17 | 295,15 |
Nr. | V-Winkel | Kröpfungsnummer/Zündabstand in ° | ||||||||||
1. | 72° | Zündfolge | 1 | 6 | 5 | 9 | 2 | 8 | 3 | 7 | 4 | 10 |
Zündabstände | 80.6 | 72.0 | 65.3 | 72.0 | 74.4 | 72.0 | 74.4 | 72.0 | 65.3 | 72.0 | ||
2. | 72° | Zündfolge | 1 | 3 | 5 | 4 | 2 | 9 | 7 | 6 | 8 | 10 |
Zündabstände | 76.3 | 76.3 | 70.1 | 67.2 | 40.6 | 67.2 | 70.1 | 76.3 | 76.3 | 99.6 | ||
3. | 108° | Zündfolge | 1 | 6 | 5 | 10 | 2 | 7 | 3 | 8 | 4 | 9 |
Zündabstände | 71.8 | 80.8 | 71.8 | 65.5 | 71.8 | 74.6 | 71.8 | 74.6 | 71.8 | 65.5 | ||
4. | 72° | Zündfolge | 1 | 6 | 5 | 10 | 2 | 7 | 3 | 8 | 4 | 9 |
Zündabstände | 107.8 | 44.8 | 107.8 | 29.5 | 107.8 | 38.6 | 107.8 | 38.6 | 107.8 | 29.5 | ||
5. | 90° | Zündfolge | 1 | 6 | 5 | 10 | 2 | 7 | 3 | 8 | 4 | 9 |
Zündabstände | 90.0 | 62.6 | 90.0 | 47.3 | 90.0 | 56.4 | 90.0 | 56.4 | 90.0 | 47.3 | ||
6. | 108° | Zündfolge | 1 | 6 | 8 | 10 | 4 | 9 | 3 | 5 | 2 | 7 |
Zündabstände | 72.0 | 103.7 | 103.7 | 37.9 | 72.0 | 74.4 | 103.7 | 42.7 | 72.0 | 37.9 | ||
7. | 72° | Zündfolge | 1 | 6 | 5 | 10 | 7 | 9 | 3 | 8 | 2 | 4 |
Zündabstände | 108.0 | 99.4 | 108.0 | 42.7 | 67.2 | 38.4 | 108.0 | 38.4 | 67.2 | 42.7 | ||
8. | 36° | Zündfolge | 1 | 7 | 5 | 8 | 2 | 9 | 3 | 6 | 4 | 10 |
Zündabstände | 73.8 | 78.8 | 67.6 | 69.7 | 76.7 | 69.7 | 67.6 | 78.8 | 73.8 | 63.5 | ||
9. | 144° | Zündfolge | 1 | 7 | 5 | 10 | 2 | 6 | 3 | 9 | 4 | 8 |
Zündabstände | 78.7 | 73.9 | 63.4 | 73.9 | 78.7 | 67.7 | 69.6 | 76.8 | 69.6 | 67.7 | ||
10. | 144° | Zündfolge | 1 | 7 | 5 | 10 | 2 | 6 | 3 | z9 | 4 | 8 |
Zündabstände | 76.0 | 75.7 | 64.3 | 75.7 | 76.0 | 68.2 | 71.8 | 72.3 | 71.8 | 68.2 | ||
11. | 72° | Zündfolge | 1 | 6 | 5 | 9 | 2 | 8 | 3 | 7 | 4 | 10 |
Zündabstände | 79.7 | 72.0 | 68.0 | 72.0 | 72.2 | 72.0 | 72.2 | 72.0 | 68.0 | 72.0 | ||
12. | 72° | Zündfolge | 1 | 6 | 5 | 9 | 2 | 8 | 3 | 7 | 4 | 10 |
Zündabstände | 79.2 | 72.0 | 69.8 | 72.0 | 70.6 | 72.0 | 70.6 | 72.0 | 69.8 | 72.0 |
Claims (16)
daß die in eine Normalebene der Kurbelwelle projizierten Kröpfungswinkel ϕ für beide Zylinderbänke gleich sind, und
daß die Kröpfungen für die beiden Zylinderbänke an der Kurbelwelle derart angeordnet sind, daß der negativ umlaufende Anteil der Massenkräfte erster Ordnung und/oder der Massenmomente erster Ordnung wenigstens nahezu vollständig verschwindet.
daß die in eine Normalebene der Kurbelwelle projizierten Kröpfungswinkel ϕ für beide Zylinderbänke gleich sind, und
daß die Kröpfungen für die beiden Zylinderbänke an der Kurbelwelle derart angeordnet sind, daß der negativ umlaufende Anteil der Massenkräfte erster Ordnung und/oder der Massenmomente erster Ordnung wenigstens nahezu vollständig verschwindet.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10235575 | 2002-08-03 | ||
DE2002135575 DE10235575A1 (de) | 2002-08-03 | 2002-08-03 | 10-Zylinder-Verbrennungsmotor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1387059A1 true EP1387059A1 (de) | 2004-02-04 |
EP1387059B1 EP1387059B1 (de) | 2007-10-31 |
Family
ID=30010583
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20030014997 Expired - Lifetime EP1387059B1 (de) | 2002-08-03 | 2003-07-02 | 10-Zylinder-Verbrennungsmotor |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1387059B1 (de) |
DE (2) | DE10235575A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103696933A (zh) * | 2013-12-19 | 2014-04-02 | 宝鸡市博磊化工机械有限公司 | 煤化工用高低压一体式十列对称平衡大型往复压缩机 |
CN109611442A (zh) * | 2019-02-15 | 2019-04-12 | 广西玉柴机器股份有限公司 | V型10缸柴油机曲轴 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1552667A (en) * | 1924-11-05 | 1925-09-08 | Chris G Barr | Crank shaft |
US3039447A (en) * | 1957-10-02 | 1962-06-19 | Daimler Benz Ag | Multi-cylinder internal combustion engine |
US5000141A (en) * | 1988-08-04 | 1991-03-19 | Isuzu Motors Limited | Crankshaft assembly |
EP0501096A2 (de) * | 1991-02-26 | 1992-09-02 | AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH.Prof.Dr.Dr.h.c. Hans List | Kurbelwelle |
DE10218922A1 (de) * | 2002-04-27 | 2002-11-07 | Christian Puchas | Kurbelwelle für einen V10-Motor mit 100 DEG - 120 DEG V-Winkel |
EP1333192A2 (de) * | 2002-01-30 | 2003-08-06 | Mitsubishi Heavy Industries, Ltd. | Verfahren zur Bestimmung eines Winkels der Kurbelanordnung eines Multizylinderverbrennungsmotor und zugehöriger Multizylinderverbrennungsmotor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1096112B (de) * | 1957-10-02 | 1960-12-29 | Daimler Benz Ag | Als V-Motor ausgebildeter 10-Zylinder-Motor mit 5fach gekroepfter Kurbelwelle |
FR2273186B1 (de) * | 1974-05-31 | 1977-09-30 | Semt |
-
2002
- 2002-08-03 DE DE2002135575 patent/DE10235575A1/de not_active Withdrawn
-
2003
- 2003-07-02 DE DE50308482T patent/DE50308482D1/de not_active Expired - Lifetime
- 2003-07-02 EP EP20030014997 patent/EP1387059B1/de not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1552667A (en) * | 1924-11-05 | 1925-09-08 | Chris G Barr | Crank shaft |
US3039447A (en) * | 1957-10-02 | 1962-06-19 | Daimler Benz Ag | Multi-cylinder internal combustion engine |
US5000141A (en) * | 1988-08-04 | 1991-03-19 | Isuzu Motors Limited | Crankshaft assembly |
EP0501096A2 (de) * | 1991-02-26 | 1992-09-02 | AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH.Prof.Dr.Dr.h.c. Hans List | Kurbelwelle |
EP1333192A2 (de) * | 2002-01-30 | 2003-08-06 | Mitsubishi Heavy Industries, Ltd. | Verfahren zur Bestimmung eines Winkels der Kurbelanordnung eines Multizylinderverbrennungsmotor und zugehöriger Multizylinderverbrennungsmotor |
DE10218922A1 (de) * | 2002-04-27 | 2002-11-07 | Christian Puchas | Kurbelwelle für einen V10-Motor mit 100 DEG - 120 DEG V-Winkel |
Non-Patent Citations (1)
Title |
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O.R.LANG: "TRIEBWERKE SCHNELLLAUFENDER VERBRENNUNGSMOTOREN", 1966, SPRINGER-VERLAG, BERLIN/HEIDELBERG/NEW YORK, XP002256750 * |
Cited By (3)
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CN103696933B (zh) * | 2013-12-19 | 2015-10-21 | 宝鸡市博磊化工机械有限公司 | 煤化工用高低压一体式十列对称平衡大型往复压缩机 |
CN109611442A (zh) * | 2019-02-15 | 2019-04-12 | 广西玉柴机器股份有限公司 | V型10缸柴油机曲轴 |
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