FI122867B - Assembled crankshaft, especially for medium speed four-stroke diesel engines - Google Patents

Assembled crankshaft, especially for medium speed four-stroke diesel engines Download PDF

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Publication number
FI122867B
FI122867B FI20070152A FI20070152A FI122867B FI 122867 B FI122867 B FI 122867B FI 20070152 A FI20070152 A FI 20070152A FI 20070152 A FI20070152 A FI 20070152A FI 122867 B FI122867 B FI 122867B
Authority
FI
Finland
Prior art keywords
crankshaft
main bearing
members
pins
assembled
Prior art date
Application number
FI20070152A
Other languages
Finnish (fi)
Swedish (sv)
Other versions
FI20070152A (en
FI20070152A0 (en
Inventor
Maximilian Bierl
Niels Lange
Robert Stocker
Original Assignee
Man Diesel Se
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to DE102006009152A priority Critical patent/DE102006009152A1/en
Priority to DE102006009152 priority
Application filed by Man Diesel Se filed Critical Man Diesel Se
Publication of FI20070152A0 publication Critical patent/FI20070152A0/en
Publication of FI20070152A publication Critical patent/FI20070152A/en
Application granted granted Critical
Publication of FI122867B publication Critical patent/FI122867B/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00Shafts; Axles; Cranks; Eccentrics
    • F16C3/04Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06Crankshafts
    • F16C3/10Crankshafts assembled of several parts, e.g. by welding by crimping
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00Engines or pumps
    • F16C2360/22Internal combustion engines

Description

Assembled crankshaft, especially for medium speed 4-stroke diesel engines

The invention relates to an assembled crankshaft 5 according to the preamble of claim 1.

In principle, the crankshaft consists of the knees provided with pivoting pivots on the main bearings, the crankshaft (lifting) pin, the connecting crankshaft flanks with counterweights therein.

In the crankshaft, the oscillating motion is transformed into a rotational motion of 10. The larger crankshafts are loosely preformed, then forged in the correct position with the twisted knees and finished.

The well-known single-piece crankshafts for internal combustion engines are most often made from a single forged piece and require expensive machining. The one-piece design gives the crankshafts the same size as they are needed for medium-speed diesel engines, but with good strength, but only allows for the subsequent repair of damaged parts and the heavy-duty bearings.

Connecting rod bearing pin with very small lifting radius (palm radius) can be implemented in eccentric design type. The center of gravity of the connecting rod bearing 20 is located outside the center of the crankshaft, therefore radially outwardly directed centrifugal forces occur. As a compensation, therefore, counterweights are usually mounted on the crankshaft lifting flanks.

Particularly in large percussion piston engine engines such as those used in ships or power plants, it is common to provide different types of engine with different cylinder numbers. Therefore, a special crankshaft must be forged for each number of cylinders. This requires not only high manufacturing costs but also relatively long lead times as it would be uneconomic

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^ The list keeps all the crankshafts you may ever need in stock.

In medium speed four-stroke diesel engines, the ratio of stroke length s ^ 30 to cylinder bore D is small compared to low speed two stroke engines £ and cylinder pressure Pzyi. generally higher so that the main bearing and palm pins cross sections always overlap, which is why until now LT) 5 has practically no assembled crankshafts in this area.

However, crankshafts have already been proposed in which the individual axle parts, counterweights and crank pins can be separated from the other members and again 2 joined together. These crankshafts must be easy to manufacture from stock and can be assembled without special skill.

Known and already implemented in practice are the concepts of assembled crankshafts in which the crankshaft flank is realized in the form of a plate whose dimension is selected so large that it can simultaneously receive the bearing of the main bearing pins. Connecting rod bearing pins are made in separate parts by shrinking, screwing or otherwise joined to this plate.

According to DE-PS 347 103, the pins inserted into the crankshaft flanks are thus eccentrically placed on the shaft portions such that their center distance 10 is greater than the radius of the palm (= half the stroke of the piston). In addition, the connecting members relative to the crankshaft flanks are smaller than the pin diameters. In order to provide sufficient partitioning strength for the pins between the bores on the crankshaft flanks, either a larger stroke must be selected or the crank and shaft must be made in one piece. In any event, here the lift is so large that there is no overlap of the main bearing and crank pin cross sections in the direction of the crankshaft.

Henceforth, the invention is based on the object of providing a structure for an assembled crankshaft with a lower palm radius compared to low speed, two stroke engines which allows simple, cost-effective manufacture of an arbitrary length for a defined number of strokes is <1 (s <(Dqlz + Drlz); GLZ = main bearing pin, PLZ = connecting rod bearing pin).

25 This occurs in most practical applications with a ratio of piston stroke s well below 2 to piston diameter D. In slow-speed two-stroke diesel engines, most of the cases

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^ axis shafts come into use, in practice s / D ~ 2 or even higher.

According to the invention, this is achieved by the individual organs

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^ 30 for mounting the main bearing, connecting rod bearing pins and palm flanks, according to the kit principle, are connected by frictional or shape frictional (m or frictional and shape frictional) such that suitable contact geometry is provided.

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5 d cross-section of main bearing and crank pins * for individual members.

the cams may overlap in the radial direction of the crankshaft so that the crank radius may be less than or equal to the sum of the combined radii of the main bearing and the crank bearing pin.

3

Of course, the measures of the invention can also be used, with corresponding dimensions, for assembled crankshafts having a radius of palm greater than the sum of the combined radii of the main and connecting rod bearing pins.

5 This gives a high degree of flexibility and a short acquisition time, since the crankshaft blank can be assembled very quickly from individual pieces in stock.

Such assembly of a crankshaft from a plurality of easy-to-handle individual members is generally applicable to all types of percussion piston engines, internal combustion engines, pumps, seals and compressors.

For the procurement of individual organs in the form of semi-finished products, a significantly larger circle of suppliers is concerned. Furthermore, since the manufacturing process of the assembled crankshaft is very different from that of a conventional forged crankshaft, production bottlenecks are avoidable and in any case greatly mitigated.

The introduction of new bearing technologies used in the automobile industry to produce cars, which have not been available in medium-speed diesel engines until now, as these require hardened crank pins. With single-piece crankshaft shafts of this magnitude, the pins are left soft because of the need to keep aftermarket spare for bearing damage. In addition, in the case of inductive hardening of pins, there is a fear of further complexity in manufacturing, which is in any case hitherto regarded as high.

In the following, the invention will be explained in more detail by means of a few exemplary embodiments.

£! In the accompanying drawings, Figs. 1 to 4 show a series of construction principles comprising three different elements 9 in the form of a crankshaft bearing pin, a main bearing pin and a crankshaft lifting flanks; Fig. 5 shows a series of principles of frictional and contoured connection. 30, the crankshaft lifting flange is supported by a plurality of spacers having fitting support surfaces, ß FIG. 6 is a constructional principle in which the main bearing and connecting rod pins are assembled from at least two different insertion members inserted into the lifting flanks; - 8 Assembly Set Principles, wherein the individual crankshaft members comprise substantially the main bearing pin and the single-piece crankshaft knee lifting sides and one connecting rod bearing pin, FIGS. wherein both the main bearing and the crankshaft bearing pin are implemented on both sides by plug connection means.

The crankshaft 8 assembly concept of Figure 1 comprises three different members in the form of a connecting rod bearing pin 1, a main bearing pin 2, and a lifting flange 3.

Both the connecting rod pin 1 and the main bearing pin 2 have circular cylindrical shrink connection members 1a, b; 2 a, b eccentrically mounted to the bearing pins 1, 2 so that the lifting flanks 3 are formed with a circular cylindrical friction mediated shrink joint, whereby the receiving bores 4, 5 shrink joint members 1a, b; For 2a, b, two fully spaced circular cylindrical shrink seams 6, 7 are provided on the lifting flanks.

Another very advantageous variant of the kit design is shown in Fig. 2. Both the connecting rod bearing pin 10 and the main bearing pin 11 20 have shrink fitting members 10a, b on both sides; 11a, b, which are paired in a corresponding fitting bore 12 on the lifting side 13 overlapping such that the respective support surfaces 14, 15 are additionally fitted to the shrink fitting members 10a, b; 11a, b so that the cranking bearing 13 and the main bearing pin 11 are respectively connected to the lifting side 13 by frictional and contouring and respective positioning with respect to the axis of the crankshaft 16 of the complementarily positioned support surfaces 14, 15, at least the angular position of the lifting movement .

Figure 3 illustrates a modification of the embodiment of Figure 2, and therefore

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^ use the same reference numerals. In addition, mass lifting members 18 are also provided on the lifting sides 13.

Another highly advantageous variant is shown in Figure 4. With shrink connection members | 10 a, b; 11a, b are in each case a semi-cylindrical structure and, when assembled with two complementary support surfaces 14, 15, form a substantially circular cylindrical geometry such that the connecting rod bearing 10 and the main bearing pin 11 are each connected in a circular bore 12 to the lifting side 13 by friction and contour.

5

For example, the crankshaft 8, 16 of an 18-valve internal combustion engine would require 37 single parts (shaft end on clutch side, shaft end on opposite side of clutch, 18 flanks 3, 13, eight main bearing pins 2, 11 and nine crankshaft bearings 11) to implement the above principle.

According to the embodiment of Fig. 5, the friction and form-fitting joint on the lifting side 13 is supported by one or more spacers 19, 20 on the supporting surfaces of the fitting.

According to Figure 5, the main bearing 21 and connecting rod bearing pins 22 are formed by at least two different single members for insertion into the lifting side 23 which move the centers of the pins 21, 22 parallel to one another and further screw the individual members on the lifting side 23.

According to another preferred embodiment of the invention, Fig. 7 shows that the individual elements of the crankshaft 30 may comprise substantially the main bearing pin 31 and the single-piece crankshaft knee 32 on two lifting faces 33 and the crankshaft bearing pin 34, the main bearing pin 31 being interconnected by a circular cylindrical bore 35 or with that recess on the lifting side 33 frictionally to the crankshaft knee 32.

Figure 8 illustrates, in another preferred embodiment, that the individual elements of the crankshaft 40 substantially comprise a crankshaft knee 41, available as both a main bearing pin and a crankshaft bearing pin, and a shrink ring 42 for frictionally interconnecting two crankshaft knees 41 in each case.

Figure 9 shows another preferred modification of the invention. Both the main bearing 50 and the connecting rod bearing pin 51 are provided with lifting flank members 50a, 51a, b on both sides. These parts have bearing surfaces 52, 53,

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so that the main bearing 50 and the crankshaft bearing pin 51 can each be assembled into complementary formed support surfaces 52, 53 and in each case can be connected by a pair of stretching screws 54 to 50a, 51b. In addition, the mass balance compensating members 55 can be screwed into the pairs of part pieces £ 50a, 51b.

Figures 10 and 11 show two other embodiments of Figure 9

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5 variants which can be seen without further explanation by simply the o figures.

A further exemplary embodiment is shown in Fig. 12. Both the main bearing 60 and the crank bearing pin 61 are provided on both sides by the plug connection members 60a, 61a, b so that each of the two complementarily acting plug connection members 60a, 61a is inserted into each other. in connection with forming one lifting flank and each lifting flank, a balancing weight 62 can be screwed in. The plug connection is further secured by means of stretching screws 65.

5 In addition, the described crankshaft construction of a plurality of kit components makes it easier to use crankshaft hardened pins for high-speed diesel engines, and thus to use modern types of plain bearing which, thus far, have not been mentioned in this type of engine. use. In addition, the described crankshaft structure, assembled from a plurality of kit components, makes it easier to eliminate problems with crankshaft parts that have been identified as defective during the manufacturing or testing process by using another prefabricated component. In addition, the described construction of crankshafts assembled from a plurality of assembly parts makes it easier to repair crankshafts in the event of engine damage in the event of bearing clipping or the like, where possible only by replacing the damaged part.

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Claims (8)

    7
  1. An assembled crankshaft for medium-speed four-stroke diesel engines consisting of single members for removably interconnecting a plurality of main bearing, crankshaft pins and crankshaft flanges, characterized in that the individual members are assembled by means of a kits that by selecting suitable contact geometries for individual members, the main bearing and crankshaft pivots may overlap in the radial direction of the crankshaft so that the radius of the palm may be less than or equal to the sum of the combined radii of the main bearing and crankshaft pins; the main bearing pin (2) having on both sides circular cylindrical shrink fitting members (1a, b; 2a, b) disposed centrally on the bearing pins such that the crankshaft flanks (3) the expected circular cylindrical, friction mediated shrink fitting, wherein the receiving bores (4,5) have shrink fitting members (1a, b; 2 a, b) on the lifting flanks (3) can be implemented as two fully separated circular cylindrical shrink seams (6, 7).
  2. 2. Assembled crankshaft for medium-speed four-stroke diesel engines consisting of single members for detachably connecting a plurality of main bearing, crankshaft pins and crankshaft flanges, characterized in that the individual members are assembled by means of a kit or by friction or form that by selecting suitable contact geometries for the individual members, the cross-sections of the main bearing and crankshaft pins may overlap in the radial direction of the crankshaft so that the palm radius may be less than or equal to the sum of the combined radii of the main bearing and crankshaft also that the main bearing pins (11) have on both sides shrink coupling members (10a, b; 11a, b) which are paired in a corresponding fitting bore (12) on the crankshaft flank (13) In such a way, that the response to the wellbeing of 30 g of the support surfaces (14, 15) are arranged in a complementary kutistusliitoselimiin (10a, b; 11 a, b) so that the crankshaft flange (13), respectively, the crankshaft (10) and the C 1/2 main bearing pin (11) are connected to the crankshaft (16) of the support surfaces (14, 15) formed by frictional and contouring ) with respect to the axis, through the respective direction, at least the angular position of the lifting movement can be varied. 8
  3. The assembled crankshaft according to claim 2, characterized in that, for frictional and contoured engagement, the crankshaft flank (13) is supported by one or more spacers (19, 20) on matching support surfaces.
  4. An assembled crankshaft according to claim 2, characterized in that the shrink connection members (10a, b; 11a, b) each have a semi-cylindrical shape and, when assembled with two corresponding support surfaces (14, 15), form a substantially circular cylindrical geometry and so on. in each case, the crankshaft (10) and the main bearing pin (11) are joined together in a circular-cylindrical bore on the crankshaft flank (13) by friction and form spacing-10.
  5. 5. Assembled crankshaft for medium-speed four-stroke diesel engines consisting of single members for detachably connecting a plurality of main bearing, crankshaft pins and crankshaft flanges, characterized in that the individual members are frictionally or frictionally and interlocked that, by selecting suitable contact geometries for the individual members, the cross-sections of the main bearing and crankshaft pins may overlap in the radial direction of the crankshaft so that the palm radius may be less than or equal to the sum of the combined radii of the main bearing and crankshaft and the crankshaft pins (22) are composed of at least two different single members inserted into the crankshaft flanks (23) which move the center of the pins (21, 22) in a parallel direction. and screwing the individual members on the side (23) of the crankshaft.
  6. 6. Assembled crankshaft for medium-speed four-stroke diesel engines consisting of single members for detachably connecting a plurality of main bearing, crankshaft pins and crankshaft flanges, characterized in that the individual members are connected by frictional or frictional means and in a shape-mediated manner such that, by selecting suitable contact geometries for the individual members, the cross-sections of the main bearing and crankshaft pins may overlap in the radial direction of the crankshaft so that the radius of the palm may be less than or equal to LO 5 main bearings. the sum of the combined radii, whereby the individual elements of the crankshaft (3) substantially comprise the main bearing pin (31) 3535 and the single-piece crankshaft knee (32) on two crankshaft flanks (33) and one crankshaft pin (34), wherein the main bearing pin (31) can be connected via a circular cylindrical bore (35) or a circular cylindrical cup-shaped recess in the crankshaft flank (33) to the crankshaft knee (32).
  7. 7. Assembled crankshaft for medium-speed four-stroke diesel engines 5 consisting of single members for detachably connecting a plurality of main bearing, crankshaft pins and crankshaft flanges, characterized in that the individual members are fused or frictionally disposed, by selecting suitable contact geometries for individual members, the cross-sections of the main bearing 10 and the crankshaft pins may overlap in the radial direction of the crankshaft so that the radius of the palm may be less than or equal to the sum of the combined radii of the main bearing and crankshaft. (51) a crank shaft side member (50a, 51a, b) is provided on both sides, these members having 15 bearing surfaces (52, 53) such that the main bearing (50) and the crankshaft each the pin (51) can each be assembled into complementarily fitted support surfaces (52, 53) and each pair of part pieces can be joined by stretching screws (54).
  8. 8. Assembled crankshaft for medium-speed four-stroke diesel engines consisting of single members for detachably connecting a plurality of main bearing, crankshaft pins and crankshaft flanges, characterized in that the individual members are fused or frictionally disengaged, by selecting suitable contact geometries for the individual members, the cross-sections of the main bearing and crankshaft pins may overlap in the radial direction of the crankshaft so that the radius of the palm may be less than or equal to the sum of the combined radii of the main bearing and crankshaft. the crankshaft pin (61) is formed by both half (M a) plug-in connecting members (60a, 61a, b), such that in each case two complementary-acting plug-in members (60a, 61 (a) are inserted into each other during the formation of each of the 30 crankshaft flanks; the balancing weight (62) can be screwed into the side of the shaft. CM LO δ o o CM 10
FI20070152A 2006-02-24 2007-02-22 Assembled crankshaft, especially for medium speed four-stroke diesel engines FI122867B (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE102006009152A DE102006009152A1 (en) 2006-02-24 2006-02-24 Built up crankshaft for four stroke diesel internal combustion engine has friction or form locked components with defined relative dimensions
DE102006009152 2006-02-24

Publications (3)

Publication Number Publication Date
FI20070152A0 FI20070152A0 (en) 2007-02-22
FI20070152A FI20070152A (en) 2007-08-25
FI122867B true FI122867B (en) 2012-08-15

Family

ID=37832197

Family Applications (1)

Application Number Title Priority Date Filing Date
FI20070152A FI122867B (en) 2006-02-24 2007-02-22 Assembled crankshaft, especially for medium speed four-stroke diesel engines

Country Status (5)

Country Link
JP (1) JP5280636B2 (en)
KR (1) KR101249086B1 (en)
CN (1) CN101025185B (en)
DE (1) DE102006009152A1 (en)
FI (1) FI122867B (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107091271A (en) * 2016-02-17 2017-08-25 福特环球技术公司 Bent axle

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AT507015B1 (en) * 2009-06-25 2010-12-15 Avl List Gmbh Internal combustion engine with several cylinders in row
DE102009046745A1 (en) 2009-11-17 2011-05-19 Man Diesel & Turbo Se Crankshaft for internal combustion engine, particularly for marine diesel engine, comprises shaft extension for mounting crankshaft in crankcase, where counterweight is mounted on respective jack lift
CN101865268B (en) * 2010-05-21 2012-09-26 北京中清能发动机技术有限公司 Crank-round slider mechanism, crank shaft thereof and equipment using same
DE102010052426A1 (en) * 2010-11-24 2012-06-06 Spx Flow Technology Norderstedt Gmbh Pump gear crank
RU2456484C1 (en) * 2010-12-07 2012-07-20 Евгений Николаевич Захаров Composite crankshaft (versions)
DE102012111124B3 (en) * 2012-11-19 2013-12-05 Thyssenkrupp Presta Teccenter Ag Built crankshaft and method of making a built crankshaft
CN103016509B (en) * 2012-12-25 2015-08-05 刘刚 A kind of reciprocating-piston engine vuilt-up crankshaft
CN103591122A (en) * 2013-11-26 2014-02-19 常州纺织服装职业技术学院 Eccentric shaft assembly used for net trimmer
DE102014103594A1 (en) 2014-03-17 2015-09-17 Thyssenkrupp Ag Built crankshaft and crank with a built crankshaft
RU2570616C1 (en) * 2014-10-29 2015-12-10 Евгений Николаевич Захаров Composite crankshaft
RU2619413C1 (en) * 2016-02-24 2017-05-15 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Пензенский государственный университет" (ФГБОУ ВПО "Пензенский государственный университет") Assembling-disassembling ice crankshaft
CN111219407A (en) * 2020-03-31 2020-06-02 山东理工职业学院 New energy automobile power assembly and processing and preparing method thereof

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CN107091271A (en) * 2016-02-17 2017-08-25 福特环球技术公司 Bent axle

Also Published As

Publication number Publication date
JP5280636B2 (en) 2013-09-04
DE102006009152A1 (en) 2007-09-06
FI20070152A (en) 2007-08-25
KR101249086B1 (en) 2013-03-29
FI122867B1 (en)
CN101025185B (en) 2012-12-05
FI20070152D0 (en)
FI20070152A0 (en) 2007-02-22
JP2007225110A (en) 2007-09-06
CN101025185A (en) 2007-08-29
KR20070088348A (en) 2007-08-29

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