GB1587484A - Piston for a reciprocating-piston internal-combustion engine - Google Patents
Piston for a reciprocating-piston internal-combustion engine Download PDFInfo
- Publication number
- GB1587484A GB1587484A GB23600/78A GB2360078A GB1587484A GB 1587484 A GB1587484 A GB 1587484A GB 23600/78 A GB23600/78 A GB 23600/78A GB 2360078 A GB2360078 A GB 2360078A GB 1587484 A GB1587484 A GB 1587484A
- Authority
- GB
- United Kingdom
- Prior art keywords
- piston
- studs
- radially
- radially outer
- ring surfaces
- 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.)
- Expired
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 10
- 238000005452 bending Methods 0.000 claims description 7
- 238000010276 construction Methods 0.000 claims description 7
- 230000015572 biosynthetic process Effects 0.000 claims description 4
- 229910001208 Crucible steel Inorganic materials 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 229910001141 Ductile iron Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
- F02F3/22—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/0015—Multi-part pistons
- F02F3/0023—Multi-part pistons the parts being bolted or screwed together
-
- 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
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
- F05C2201/0448—Steel
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Description
(54) PISTON FOR A RECIPROCATING-PISTON INTERNAL
COMBUSTION ENGINE
(71) We, MASCHINENFABRIK AUGSBURG - NURNBERG AKTIEN
GESELLSCHAFT, a German company, of 8900 Augsburg, Stadtbachstrasse 1, Germany (Federal Republic), do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:: This invention relates to a multi-part piston for a reciprocating-piston internal-combustion engine, particularly, although not exclusively, for a large diesel engine, having a piston upper part offording a piston head and a piston skirt part, and a piston lower part, a radially inner ring surface of an annular projection on the underside of the piston head contacting an oppositely facing radially inner ring surface of the piston lower part, the upper and lower parts being connected by means of clamping bolts extending generally parallel to the piston axis and inserted through the radially inner ring surfaces.
A known muiti-part piston of this kind has a clearance, widening radially outwards, between the radially inner ring surfaces on the piston upper part and on the piston lower part, which clearance remains free at ambient temperature so that these ring surfaces abut each other in line contact only on their radially inner edges. As a result of the temperature curving (distortion) of the piston head during operation of the engine, the ring surface of the piston head is deformed against the oppositely facing ring surface of the piston lower part until the two radially inner ring surfaces of the piston upper and lower parts are more or less completely supported in contact over the whole ring surfaces. This arrangement has the disadvantage that a complete support can only be achieved for a certain stress condition and the appertaining temperature curving (distortion).The clearance angle dependent on the stress between the surfaces of the multi-part piston assembly, which clearance exists in all operating conditions except the particular stress condition when the surfaces make complete contact, leads not only to a continuous flow of gas in the clearance under gas pressure with the problems of the local erosion, but also to high thermal and dynamic bending stress amplitudes in the screw-threads of the clamping bolts. The clamping bolts can of course be tightened in such a way that the clearance disappears at ambient temperature, but in this case the screw-threads of the clamping bolts are also required to bend constantly in each operating condition except the particular stress condition when the ring surfaces make complete contact.Also the clamping bolts and their screw-threads have to be dimensioned more strongly, because they have to withstand the stresses required for continual elastic distortion. This demand upon the strength of the clamping bolts limits the use of the known piston construction to average and small pistons.
An object of the invention is to eliminate or to decrease considerably the bending load on the clamping bolts or studs connecting the piston upper part and piston lower part.
Accrdmg~~ö the present invention there is provided a multi-part piston for a reciprocating-piston internal-combustion engine having a piston upper part affording a piston head and a piston skirt part, and a piston lower part, a radially inner ring surface of an annular projection on the underside of the piston head contacting an oppositely facing radially inner ring surface of the piston lower part, the oppositely facing inner ring surfaces, in the unstressed condition of the piston parts, forming between them an annular clearance widening radially outwards, the piston upper and lower parts being connected by means of radially inner clamping bolts or studs extending generally parallel to the piston axis and inserted through the inner ring surfaces, there being provided in the radially outer region of the piston on the piston upper part and the piston lower part respectively, two oppositely facing radially outer ring surfaces disposed parallel to each other and which in the unstressed condition of the piston parts are spaced in the axial direction at a distance from each other, and radially outer clamping bolts or studs disposed in the radially outer region of the piston, the axial spacing between the oppositely facing radially outer ring surfaces in the unstressed condition of the piston parts being predetermined so that after the bolts or studs are tightened, the radially inner and the outer ring surfaces are fully in contact with each other.
As a result of the construction of the piston in accordance with the invention, with prestressing of the clamping bolts or studs at ambient conditions, the optimum stressing condition of the individual piston components can be achieved under the total stress conditions which prevail in operation of the engine, the optimum stressing condition placing a lower demand on the clamping bolts or studs at a safe level.
Preferably, in the unstressed condition of the piston parts, the radially inner ring surface on
the annular projection on the underside of the piston head is perpendicular to the piston axis, and the radially inner ring surface of the piston lower part is bevelled away from the piston head in the radially outward direction. Also,
in the unstressed condition of the piston parts, the oppositely facing radially outer ring sur
faces respectively on the piston upper part and
on the piston lower part lie in planes perpen
dicular to the piston axis.
Advantageously, the radially outer ring surface on the piston upper part is formed in the end region of the piston skirt part remote from the piston head, whereby on the one hand a greater spacing of the fixing points is achieved with the piston lower part for the thermal and mechanical stressing influences and on the other hand the elasticity of a large region of the piston upper part is utilised for compensating the stressing forces.
In a further advantageous feature the radially outer clamping bolts or studs extend
through the radially outer ring surfaces, whereby the furthest lever point as regards the radially inner ring surfaces can be reached with the aim of achieving the lowest possible centripetal forces.
Preferably, the axis of each screw-threaded bore in the annular projection of the piston head is inclined to the axial direction at a predetermined angle away from the piston axis in the direction away from the piston head, this predetermined angle approximately corresponding to the angle of the radially outwardly widening annular clearance between the radially inner ring surfaces before the radially outer clamping bolts or studs are tightened. By this means, the solitary static bending strain which is otherwise placed on the screw-threads of the clamping bolts or studs during construction can also be eliminated.
The invention may be caried into practice in a number of ways but one specific embodiment will now be described, by way of example only, with reference to the accompanying drawing which shows a multi-part piston in accordance with the invention, in axial section.
The piston shown in the drawing is for a large two-stroke diesel, and basically comprises a piston upper part 1 and a piston lower part 2. The piston upper part 1 is made of steel or cast steel and has a piston head 3 and a piston skirt part 4. Grooves 5 are provided in the cylindrical outer surface of the piston skirt part 4 to take the piston rings 6. An annular projection 7 with a ring surface 8 is formed on the underside of the piston head 3 and the piston upper part 1 is supported on the piston lower part 2 on a ring surface 9 thereof which generally corresponds to the ring surface 8 of the projection 7.The ring surface 8 of the
piston upper part 1 lies generally perpendicular to the piston axis, in the unstressed condition
of the piston upper part 1, whereas the ring
surface 9 of the piston lower part 2 is bevelled slightly away from the piston head 3 in the radially outward direction so that between the ring surfaces 8 and 9 there is a clearance which widens radially outwardly at an angle rp.
The piston lower part 2, which is made of cast steel or spheroidal graphite iron, surrounds a supporting part 10 of the piston lower part 2, to whose underside a connecting rod 11 is fixed. In the radially outer region of the supporting part 10, a radially outer ring surface 12 is constructed, opposite which there is a corresponding radially outer ring surface 13 in the lower region of the piston skirt part 4 the radially outer ring surfaces being spaced in the axial direction at a distance a. Both the inner ring surfaces 8, 9 and the outer ring surfaces 12, 13 have clamping bolts or studs 14, 15 inserted in them, which are preferably constructed as necked-down bolts or studs.
A chamber for receiving coolant is surrounded by the piston upper part 1 and the piston lower part 2, and in use coolant is supplied through inlet and outlet ducts in the connecting rod 11. In addition, a further piston skirt part 16 is fixed to the underside of the supporting part 10 to provide cylindrical support for the piston.
The piston upper part 1 and the piston lower part 2 are connected by the radially.
inner and radially outer clamping bolts or studs 14, 15 respectively inserted in the radially inner and the radially outer ring surfaces 8, 9, 12, 13, the bolts or studs being shown in the untightened condition in the drawing.
In the first stage of assembly the outer clamping bolts or studs 15 are tightened until the clearance a closes and the radially outer ring surfaces 12, 13 are completely supported in contact against each other. The distance a is predetermined so that after the radially outer ring surfaces 12, 13 have been brought into contact, the piston upper part 1 is deformed elastically until the radially inner ring surfaces 8, 9 are completely supported in contact over the entire ring surfaces and the clearance angle cp, which was provided to compensate for the distortion (curving) of the piston upper part 1 appearing at operational temperature, is thus already closed at ambient temperature. Subsequently, the radially inner clamping bolts or studs 14 are tightened.
As a result, the formation of an angle of the screwed-in part of the screw-threads of the clarnping bolts or studs 15 at an angle f to the piston axis takes place only once during construction, so that the main part of the thermally-conditioned bending of the bolts or studs also takes place statically only once and no longer each time the engine runs up to the predetermined stress condition at which, in the known piston construction, the bolts become unstressed.Even this formation of bending stress in the radially inner clamping bolts or studs 14 could be avoided by making the screw-threaded bore in the annular projection 7 of the piston head 3 arranged at and angle y' from the parallel to the piston axis away from the piston axis in the downward direction, this angle (p' approximately corresponding to the angle f between the ring surfaces 8 and 9 before the clamping bolts or studs 15 are tightened.
WHAT WE CLAIM IS:
1. A multi-part piston for a reciprocatingpiston internal combustion engine, having a piston upper part affording a piston head and a piston skirt part, and a piston lower part, a radially inner ring surface of an annular projection on the underside of the piston head contacting an oppositely facing radially inner ring surface of the piston lower part, the oppositely facing inner ring surfaces, in the unstressed condition of the piston parts, forming between them an annular clearance widening radially outwards, the piston upper and lower parts being connected by means of radially inner clamping bolts or studs extending generally parallel to the piston axis and inserted through the inner ring surfaces, there being provided in the radially outer region of the piston on the piston upper part and the piston lower part respectively, two oppositely facing radially outer ring surfaces disposed parallel to each other and which in the unstressed condition of the piston parts are spaced in the axial direction at a distance from each other, and radially outer clamping bolts or studs disposed in the radially outer region of the piston, the axial spacing between the oppositely facing radially outer ring surfaces in the unstressed condition of the piston parts being predetermined so that after the bolts or studs are tightened, the radially inner and the outer ring surfaces are fully in contact with each other.
2. A multi-part piston as claimed in claim 1, in which, in the unstressed condition of the piston parts, the radially inner ring surface on the annular projection on the underside of the piston head is perpendicular to the piston axis, and the radially inner ring surface of the piston lower part is bevelled away from the piston head in the radially outward direction.
3. A multi-part piston as claimed in claim 1 or claim 2, in which, in the unstressed condition of the piston parts, the oppositely facing radially outer ring surfaces respectively on the piston upper part and on the piston lower part iie in planes perpendicularly to the piston axis.
4. A multi-part piston as claimed in any one of claims 1 to 3, in which the radially outer ring surface on the piston upper part is formed in the end region of the piston skirt part remote from the piston head.
5. A multi-part piston as claimed in any one of the preceding claims, in which the radially outer clamping bolts or studs extend through the radially outer ring surfaces.
6. A multi-part piston as claimed in any one of the preceding claims, in which the axis of each screw-threaded bore in the annular projection of the piston head is inclined to the axial direction at a predetermined angle away from the piston axis in the direction away from the piston head, this predetermined angle approximately corresponding to the angle ol the radially outwardly widening annular dear ance between the radially inner ring surfaces before the radially outer clamping bolts or studs are tightened.
7. A multi-part piston for a reciprocatingpiston internal-combustion engine substantially as specifically described herein with reference to the accompanying drawing.
8. A reciprocating-piston internal-combustion engine having a piston as claimed in any one of the preceding claims.
**WARNING** end of DESC field may overlap start of CLMS **.
Claims (8)
1. A multi-part piston for a reciprocatingpiston internal combustion engine, having a piston upper part affording a piston head and a piston skirt part, and a piston lower part, a radially inner ring surface of an annular projection on the underside of the piston head contacting an oppositely facing radially inner ring surface of the piston lower part, the oppositely facing inner ring surfaces, in the unstressed condition of the piston parts, forming between them an annular clearance widening radially outwards, the piston upper and lower parts being connected by means of radially inner clamping bolts or studs extending generally parallel to the piston axis and inserted through the inner ring surfaces, there being provided in the radially outer region of the piston on the piston upper part and the piston lower part respectively, two oppositely facing radially outer ring surfaces disposed parallel to each other and which in the unstressed condition of the piston parts are spaced in the axial direction at a distance from each other, and radially outer clamping bolts or studs disposed in the radially outer region of the piston, the axial spacing between the oppositely facing radially outer ring surfaces in the unstressed condition of the piston parts being predetermined so that after the bolts or studs are tightened, the radially inner and the outer ring surfaces are fully in contact with each other.
2. A multi-part piston as claimed in claim 1, in which, in the unstressed condition of the piston parts, the radially inner ring surface on the annular projection on the underside of the piston head is perpendicular to the piston axis, and the radially inner ring surface of the piston lower part is bevelled away from the piston head in the radially outward direction.
3. A multi-part piston as claimed in claim 1 or claim 2, in which, in the unstressed condition of the piston parts, the oppositely facing radially outer ring surfaces respectively on the piston upper part and on the piston lower part iie in planes perpendicularly to the piston axis.
4. A multi-part piston as claimed in any one of claims 1 to 3, in which the radially outer ring surface on the piston upper part is formed in the end region of the piston skirt part remote from the piston head.
5. A multi-part piston as claimed in any one of the preceding claims, in which the radially outer clamping bolts or studs extend through the radially outer ring surfaces.
6. A multi-part piston as claimed in any one of the preceding claims, in which the axis of each screw-threaded bore in the annular projection of the piston head is inclined to the axial direction at a predetermined angle away from the piston axis in the direction away from the piston head, this predetermined angle approximately corresponding to the angle ol the radially outwardly widening annular dear ance between the radially inner ring surfaces before the radially outer clamping bolts or studs are tightened.
7. A multi-part piston for a reciprocatingpiston internal-combustion engine substantially as specifically described herein with reference to the accompanying drawing.
8. A reciprocating-piston internal-combustion engine having a piston as claimed in any one of the preceding claims.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19772730071 DE2730071A1 (en) | 1977-07-02 | 1977-07-02 | MULTI-PIECE PISTON FOR COMBUSTION MACHINERY |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB1587484A true GB1587484A (en) | 1981-04-01 |
Family
ID=6013077
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB23600/78A Expired GB1587484A (en) | 1977-07-02 | 1978-05-26 | Piston for a reciprocating-piston internal-combustion engine |
Country Status (10)
| Country | Link |
|---|---|
| JP (1) | JPS5413810A (en) |
| BR (1) | BR7803794A (en) |
| DD (1) | DD136872A1 (en) |
| DE (1) | DE2730071A1 (en) |
| DK (1) | DK293178A (en) |
| ES (1) | ES470881A1 (en) |
| FR (1) | FR2396172A1 (en) |
| GB (1) | GB1587484A (en) |
| IT (1) | IT1105329B (en) |
| NL (1) | NL7805990A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2384541A (en) * | 2002-01-25 | 2003-07-30 | Federal Mogul Bradford Ltd | Piston with gap between crown and body portion to allow for heat expansion |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2821176C2 (en) * | 1978-05-13 | 1982-12-09 | Mahle Gmbh, 7000 Stuttgart | Piston with base plate for internal combustion engine |
| JPS55130798A (en) * | 1979-11-17 | 1980-10-09 | Yoshio Midorikawa | Autographing pen |
| FR2483521A1 (en) * | 1980-05-30 | 1981-12-04 | Semt | PISTON OF ALTERNATIVE PISTON MACHINE, ESPECIALLY OF INTERNAL COMBUSTION ENGINE |
| JPS623537U (en) * | 1985-06-20 | 1987-01-10 | ||
| FI102559B1 (en) * | 1995-03-09 | 1998-12-31 | Waertsilae Nsd Oy Ab | Internal combustion engine piston unit |
| DK172217B1 (en) * | 1995-08-11 | 1998-01-05 | Dampskibsselskabet Af 1912 | Piston for diesel engines |
| DE19603589A1 (en) * | 1996-02-01 | 1997-08-07 | Kolbenschmidt Ag | Pendulum shaft piston |
| DE19855134A1 (en) * | 1998-11-30 | 2000-05-31 | Mahle Gmbh | Composite piston has thrust pieces with spherical contact faces located approx. on the level of the hub zenith |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR474969A (en) * | 1913-10-27 | 1915-03-29 | Jakob Kraus | Electrostatic sorter for the preparation of flammable or explosive materials |
| DE1269414B (en) * | 1966-06-15 | 1968-05-30 | Mahle Kg | Internal combustion engine piston with base plate |
| US3465651A (en) * | 1968-02-13 | 1969-09-09 | Alco Products Inc | Composite pistons |
| DE2230722C3 (en) * | 1972-06-23 | 1981-12-24 | Mahle Gmbh, 7000 Stuttgart | Internal combustion engine pistons, in particular for diesel engines, with a lower part and an upper part detachably connected to this |
| DE2307347A1 (en) * | 1973-02-15 | 1974-08-22 | Maschf Augsburg Nuernberg Ag | MULTI-PIECE PLUNGER FOR FOUR-STROKE COMBUSTION MACHINES, IN PARTICULAR LARGE DIESEL ENGINES |
| US4083292A (en) * | 1976-06-16 | 1978-04-11 | Caterpillar Tractor Co. | Piston with high top ring location |
-
1977
- 1977-07-02 DE DE19772730071 patent/DE2730071A1/en not_active Withdrawn
-
1978
- 1978-05-26 GB GB23600/78A patent/GB1587484A/en not_active Expired
- 1978-06-01 NL NL7805990A patent/NL7805990A/en not_active Application Discontinuation
- 1978-06-06 IT IT49735/78A patent/IT1105329B/en active
- 1978-06-08 DD DD78205884A patent/DD136872A1/en unknown
- 1978-06-14 BR BR7803794A patent/BR7803794A/en unknown
- 1978-06-16 ES ES470881A patent/ES470881A1/en not_active Expired
- 1978-06-23 JP JP7635278A patent/JPS5413810A/en active Pending
- 1978-06-28 FR FR7819268A patent/FR2396172A1/en not_active Withdrawn
- 1978-06-29 DK DK293178A patent/DK293178A/en unknown
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2384541A (en) * | 2002-01-25 | 2003-07-30 | Federal Mogul Bradford Ltd | Piston with gap between crown and body portion to allow for heat expansion |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5413810A (en) | 1979-02-01 |
| FR2396172A1 (en) | 1979-01-26 |
| DE2730071A1 (en) | 1979-01-04 |
| DD136872A1 (en) | 1979-08-01 |
| IT7849735A0 (en) | 1978-06-06 |
| IT1105329B (en) | 1985-10-28 |
| NL7805990A (en) | 1979-01-04 |
| ES470881A1 (en) | 1979-02-01 |
| DK293178A (en) | 1979-01-03 |
| BR7803794A (en) | 1979-04-17 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PS | Patent sealed [section 19, patents act 1949] | ||
| PCNP | Patent ceased through non-payment of renewal fee |