CN107061037A - Cylinder liner for two-stroke cross head engine - Google Patents
Cylinder liner for two-stroke cross head engine Download PDFInfo
- Publication number
- CN107061037A CN107061037A CN201610936947.2A CN201610936947A CN107061037A CN 107061037 A CN107061037 A CN 107061037A CN 201610936947 A CN201610936947 A CN 201610936947A CN 107061037 A CN107061037 A CN 107061037A
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- China
- Prior art keywords
- cylinder liner
- cylinder
- support member
- recess
- axial
- 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.)
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Classifications
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- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
- F02F1/16—Cylinder liners of wet type
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- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/22—Other cylinders characterised by having ports in cylinder wall for scavenging or charging
-
- 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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
-
- 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
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/004—Cylinder liners
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
-
- 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
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
A kind of cylinder liner (1) for internal combustion engine particularly two-stroke cross head engine, the cylinder liner (1) includes：It is suitable for the first end engaged with cylinder head (22)；Scavenging port (18)；Being located near the first end in the wall of the cylinder liner (1) is used for the circumferential cooling recess (31) of liquid coolant, and the circumferential cooling recess (31) has the circumferentially extending opening in the outer surface of the wall of the cylinder liner (1)；Axial support member (36), the axial support member (36) is at least partially interposed in the peripheral recess, the axial support member (36) is by the circumferentially extending opening bridge joint, and the axial support member is provided with coolant channel outlet hole (42) and coolant channel ingate (43).
Description
Technical field
The disclosure is related to a kind of cylinder liner for explosive motor especially two-stroke cross head engine, the hair
Motivation has piston, and the piston can be transported in cylinder liner on its longitudinal direction (axial direction) direction between lower dead center and top dead centre
Dynamic, at the lower dead center, the scavenging port in the wall of cylinder liner is exposed to above piston crown surface, and in the top dead centre
When, piston is located at its tip position in cylinder liner.
Background technology
In large-sized two-stroke cross-head type compression-ignition, internal combustion engine, generally project upwards and pass through from cylinder block
The heat and pressure that the burned process in the top for the cylinder liner that cylinder head is clamped on the cylinder block is produced are subject to very heavy
Thermic load and mechanical load.Temperature levels on the inner running surface for piston of cylinder liner are for cylinder liner
There is decisive significance for service life, thus also there is decisive significance for the operation economy of engine.Such as
Really the temperature of the running surface is too high, and fire check may be produced in cylinder liner, and if temperature is too low, then carrys out spontaneous combustion
The sulfuric acid of product may be condensed in running surface, and this causes abrasion to increase due to the corrosive attack to lagging material, and
And cause the lubricating oil film of the cylinder oil in running surface to decompose and cause the increase of (expensive) cylinder oil consumption.
Running surface temperature generally changes with engine load, and because engine must can either be in high load capacity
It is lower again can longtime running at low load, bushing is traditionally manufactured so that the busy hour running surface in engine
Temperature is close to maximum safety temperature.High-temperature level allows maintains sufficiently high temperature to prevent acid cure in sub-load
Knot is in running surface.
Cylinder lubricating oil and cylinder liner material are influenceed by high temperature during full engine load, and the temperature increase can
Lubricant breakdown can be caused and the sustaining damage of fire check form is caused to cylinder liner material.
For big cylinder holes engine such as cylinder holes diameter be more than 50cm engine known cylinder bushing be provided with including
The cooling device of cylinder holes is cooled down, because the cylinder liner in large-sized two-stroke crosshead engine is always put with orthostatic position
Put, therefore the cooling cylinder holes is located in the axial range of cylinder liner closest in the part of cylinder head (i.e. positioned at axial model
In the top enclosed).The wherein compression ratio of combustion chamber is surrounded in the axial range of the cylinder liner closest to the top of cylinder head
Highest and the part for starting burning, therefore remainder of the top in the axial range with cylinder liner of cylinder liner
Compared to when be exposed to maximum temperature and pressure.Thus, the top of cylinder liner must cope with maximum pressure and temperature, and cylinder bush
Remaining bottom in the axial range of set is only exposed to lower temperature and lower pressure.Therefore, the wall thickness on the top of cylinder liner
The at most cooling of especially high and needs.The decline of temperature and pressure on the axial direction away from cylinder head is gradual, but
The reason for allowing in practice, is typically roughly divided into two or three grades by the wall thickness of cylinder liner, wherein most thin-walled
Thickness is arranged on cylinder liner closest at the axial end of scavenging port, and thickest is arranged on having with cylinder head for cylinder liner
Have at the axial end of interface.
The top being placed exactly in below the interface with cylinder head in the axial range of cylinder liner is provided with from external concave
The Cooling Holes at multiple relative close intervals that portion is got into the relatively thick wall of cylinder liner, so that straight Cooling Holes
Longitudinal axis has inclination or tilt route on the longitudinal axis of bushing.Insertion tube or guide plate are with will stream in each Cooling Holes
The liquid coolant entered is directed to the top dead centre end of cylinder holes from recess, and liquid coolant is flowed out in a chamber downward there-from,
Liquid coolant is transferred up in cylinder head from the chamber by means of pipe.Inclined cooling plate hole is evenly distributed in cylinder liner
In the circumferential scope on top.Nevertheless, the temperature of lagging material will not also be equally distributed the week on the top of cylinder liner
To in scope because closest to Cooling Holes cylinder liner material not as the material heat between two Cooling Holes.Thus,
When seeing in the circumferential, the material temperature in the top of cylinder liner will be fluctuated.It is this uneven in the top of cylinder liner
Circumference temp distribution due to cylinder liner material uneven temperature expansion and cause stress in cylinder liner material, this is again
Cause the uneven wear of cylinder liner and piston ring, because the running surface on the top of cylinder liner will not be complete
It is circular.It will become slightly more round after cylinder liner test running, but be due to new deformation under any new load and make
It will be never complete circle to obtain in known cylinder bushing.
The part being placed exactly in below top of cylinder liner is provided with one or more cooling collars, these cooling collars
The outer surface of cylinder liner is surrounded completely and provides space of circumferentially extending for liquid coolant.Typically, cooling collar
There is the top of Cooling Holes downwardly cylinder block extension equivalent length from cylinder liner, cylinder block is completely extended to sometimes.
From the cylinder liner of types described above known to WO97/42406.
GB 1219532 discloses a kind of internal combustion engine cylinder, and the cylinder has the upper flange provided with annular recess, should
Annular recess is used as water-cooling channel and by two-piece type ring in outer closures, and the height of the two-piece type ring is slightly larger than the groove
Corresponding part.One steel loop is contracted on the flange, and by hole supplies and discharge water.
The content of the invention
The purpose of the present invention is to overcome or at least reduce drawbacks referred to above.
According in a first aspect, the purpose is started by providing one kind for explosive motor particularly two-stroke crosshead
The cylinder liner of machine realizes that the cylinder liner includes：It is suitable for the first end engaged with cylinder head；Scavenging port；Described
It is used for the circumferential cooling recess of liquid coolant in the wall of the cylinder liner near first end, the circumferential cooling is recessed
Portion has the circumferentially extending opening in the outer surface of the wall of the cylinder liner；Axial support member, this axially supports structure
Part is at least partially interposed in the peripheral recess, and the axial support member bridges the circumferentially extending opening, and
The axial support member is provided with coolant channel hole.
Recess is cooled down by using circumferentially extending so that liquid coolant is substantially completely equably distributed in the circumferential, and
And essentially eliminate uneven temperature distribution and bring stress and uneven wear the problem of.Recess is cooled down in circumferentially extending
Circumferential openings in set axial support member cooling recess can be made deeper and larger, and can obtain can handle application extremely
The strong construction of huge compression stress at the top of cylinder liner.
In the first possible way of realization of first aspect, the axial support member is configured to the circumferential cooling
Recess provides axially support.
In the second possible way of realization of first aspect, the axial support member fills the axially opposing of the opening
Axial space between the surface of direction.
In the 3rd possible way of realization of first aspect, under the non-stress state of the cylinder liner, the opening
The axially opposing direction surface between the axial space be slightly larger than the axially opposing of the axial support member
Axial distance h between surface, so as to have small axial gap between the opening and the axial support member.
In the 4th possible way of realization of first aspect, the axial support member is by two or more section shapes
Into split ring.
In the 5th possible way of realization of first aspect, the circumferential cooling recess includes upper recess and alternatively recessed
Nest.
First aspect the 6th may in way of realization, the circumferential cooling recess include by the upper recess with it is described
The cylindrical surface of lower recess connection.
In the seven or four possible way of realization of first aspect, the axial support member includes annular recessed portion inwardly,
And the space for cooling agent is wherein limited between the annular recessed portion inwardly and the cylindrical surface.
The 8th in first aspect may be in way of realization, and the circumferential cooling recess described is axially propped up to being enough to store deeply
Component is supportted, without making the axial support member be protruded from the circumferential cooling recess.
In the 9th possible way of realization of first aspect, the cylinder liner further comprises positioned at the cylinder liner
Multiple cylinder lubricating oil supply orifices in wall, this some holes is preferably in essentially identical level around the periphery of the cylinder liner point
Cloth.
According to second aspect, object above is also provided by a kind of two-stroke cross head engine to realize, this starts
Machine includes at least one cylinder liner according to first aspect and its any way of realization.
In terms of detailed description described below and embodiment will be clear that the these and other of the present invention.
Brief description of the drawings
In the following detail section of the disclosure, with reference to the accompanying drawings shown in example embodiment be described in more detail this
Invention, wherein：
Fig. 1 is the front view of the large-sized two-stroke diesel engine according to an example embodiment；
Fig. 2 is the side view of Fig. 1 large-sized two-stroke engine；
Fig. 3 is the schematic illustration of the large-sized two-stroke engine according to Fig. 1；
Fig. 4 is the sectional view of cylinder liner according to example embodiment and cylinder block, wherein being equipped with cylinder head
And air bleeding valve；
Fig. 5 is the side view of the cylinder liner according to example embodiment；
Fig. 6 is the partial sectional view of Fig. 5 cylinder liner；
Fig. 7 is the sectional view of the details on the top of Fig. 5 cylinder liner, shows circumferential cooling recess；
Fig. 8 is Fig. 7 details, and wherein axial support member is inserted in circumferential cooling recess；
Fig. 9 is Fig. 8 details, wherein circumferential supporting member surrounds the top of cylinder liner；
Figure 10 shows the details of axial support member；
Figure 11 shows Fig. 9 details, and wherein pipe fitting is used to supply the coolant to circumferential cooling recess；
Figure 12 shows Fig. 9 details, and wherein pipe fitting is used for from cooling recess discharge cooling agent；
Figure 13 shows circumferential supporting member with sectional view；
Figure 14 shows the positive exploded view of Fig. 5 cylinder liner, without circumferential supporting member；
Figure 15 shows the front view of Fig. 5 cylinder liner, without circumferential supporting member；
Figure 16 illustrates axial support member；
Figure 17 is the sectional view at the top of Fig. 5 cylinder liner；And
Figure 18 be a diagram that the curve of the temperature of the running surface of Fig. 6 cylinder liner and the cylinder liner of prior art
Figure.
Embodiment
In the following detailed description, by with reference to the large-sized two-stroke turbocharging compression ignition cross in example embodiment
Hair style explosive motor describes explosive motor.Fig. 1,2 and 3 show the large-sized low-speed turbine with bent axle 8 and crosshead 9
It is pressurized two-stroke diesel engine.Fig. 3 shows the large-sized low-speed turbocharging two-stroke bavin with its intake and exhaust system
The schematic diagram of oil turbine.In the illustrated embodiment, the engine has four cylinders in upright arrangement.Large-sized low-speed turbine
Supercharging two-stroke diesel engine generally has four to ten four single-row cylinder arrangements carried by engine frame 11.Engine example
It such as may be used as the sustainer or the stationary engine with the generator operated in power station of ship.The engine it is total defeated
Going out for example can be from 1,000kW to 110,000kW.
In the illustrated embodiment, the engine is two-stroke single streaming compression ignition engine, and the motor has
Scavenging port 18 at the lower area of cylinder liner 1 and the central discharge air valve 4 at the top of cylinder liner 1.Scavenging
Air is sent to the scavenging port 18 of each cylinder 1 from scavenging air receiver 2.The compression scavenging of piston 18 in cylinder liner 1 is empty
Gas, and from the Fuelinjection nozzle spray fuel in cylinder head 22, then occur to burn and produce exhaust.
When air bleeding valve 4 is opened, be vented by the exhaust passage associated with cylinder 1 flow into exhaust receiver 3 it is interior and
It flow to the turbine 6 of turbocharger 5 forward by first exhaust pipeline 19, the exhaust is by second exhaust pipeline via energy-conservation
Device 20 flows out to outlet 21 and enters air.Pass through an axle, the driving compressor 7 of turbine 6, so as to supply fresh via air inlet 12
Air.The scavenging air of pressurization is transported to the scavenging air pipeline 13 for leading to scavenging air receiver 2 by compressor 7.Pipeline 13
In scavenging air pass through intercooler 14, the intercooler 14 is cold by the scavenging air that compressor is left with about 200 DEG C
But to about 36 DEG C to 80 DEG C of temperature.
Cooled scavenging air is by the auxiliary blower 16 that is driven by electric notor 17, when the compression of turbocharger 5
, i.e., should under the underload or localised load state of engine when machine 7 can not convey the enough pressure for scavenging receiver 2
Auxiliary blower 16 pressurizes to scavenging air stream.When engine load is higher, the conveying quilt of compressor 7 of turbocharger
The scavenging air fully compressed, then bypasses auxiliary blower 16 via check valve 15.
Fig. 4, Fig. 5 and Fig. 6 show be indicated generally at 1 the cylinder bush for large-sized two-stroke crosshead engine
Set.According to size of engine, the cylinder liner 1 can be manufactured with different sizes, wherein cylinder cylinder holes generally from 250mm to
1000mm scope, and corresponding typical length is in the range of from 1000mm to 4500mm.Cylinder liner 1 is general with cast iron
Manufacture, and can be integral or be divided into two or more parts assembled end to end.In bush
In the case of, steel making top can also be used.Large-sized two-stroke crosshead engine is effectively compressed such as very high
1:16 to 1:20 and develop, this certainty needing to bear element such as cylinder liner 1, the piston 10 of internal pressure of combustion chamber
Heavy load is acted on on piston ring (not shown).
In Fig. 4, cylinder liner 1 is shown as being arranged in cylinder block 23, and wherein cylinder head 22 is placed on cylinder liner 1
Top on, between cylinder head 22 and cylinder liner 1 have air-tight interfaces.In Fig. 4, piston 10 is not shown, to carry
For the clear view with its cylinder lubrication hole 25 and the cylinder liner 1 of cylinder lubricating wire 24, the cylinder lubrication hole 25 and cylinder
Lubricating wire 24 allows the supply cylinder lubricating oil when piston 10 is by lubricating wire 24, and cylinder lubricating oil is distributed in by piston ring afterwards
In the running surface of cylinder liner.
Pipe fitting 26 is used for the cooling at the top positioned at cylinder liner 1 and the liquid coolant of stiffening device 30 for example
Water.Pipe fitting 28 is used to liquid coolant being transported to cylinder head 22 from cooling and stiffening device 30.Pipe fitting 27 is used for liquid is cold
But agent is discharged to cooling system from cylinder head 22.Liquid coolant supplied to cooling and stiffening device 30 is by commonly known per se cold
But system (not shown) is provided, and the cooling system provides liquid coolant with controlled supply temperature, and is discharged from cylinder head 22
Cooling agent return to cooling system and adjusted again.The wall 29 of cylinder liner 1 has change on the axial range of cylinder liner
Thickness.In the embodiment shown, the thinnest section of wall 29 is located at the bottom of cylinder liner 1, i.e., under scavenging port 18
At the part of side.The thick of the wall 29 of cylinder liner 1 is located in the top in the axial range of cylinder liner 1.In cylinder
Near the centre of the axial range of bushing 1, the drastically transition of the thickness of cylinder liner 1 is used as allowing cylinder to be placed in cylinder block 23
On shoulder.Cylinder head 22 is squeezed on the upper surface of cylinder liner 1 using the larger power applied by tensioning bolt.
Fig. 5 and Fig. 6 illustrate in greater detail cylinder liner 1, the wherein axial axis X of the cylinder liner 1 and cooling and
Support meanss 30 are closed in rectangular broken line frame in figure 6.The top part of cylinder liner 1 is that cylinder liner 1 is closest
The cylinder liner, prolong from the top of cylinder liner 1 on certain distance with the part of longitudinal end of the formation interface of cylinder head 22
Stretch, as shown by arrow U.This is exposed to the maximal pressure of combustion process closest to the region of the upper end of cylinder liner 1 for cylinder liner
The region of power and maximum temperature.Therefore, compared with the remaining range of cylinder liner, the region must have it is maximally effective cooling and
Most firm construction.
The top part U extends since shoulder 89, and the shoulder 89 is by cylinder liner body towards the upper of the cylinder liner 1
Increased diameter segment is formed upwards at end.
Fig. 7 illustrates in greater detail cooling and support meanss 30.The cooling and support meanss 30 are arranged on cylinder liner 1
At the U of part, axial ends with cylinder head 22 formation interface of the part U closest to cylinder liner 1.Part U or cylinder bush
The maximum pressure exposed to combustion process of set and the part of temperature.Therefore, the thickness of the wall 29 of cylinder liner is in cylinder liner 1
The part in it is of a relatively high.
However, it is necessary to pressure cooling is carried out, and must be by the portion for forcing cooling to be arranged to be relatively close to cylinder liner 1
The running surface divided, so as to which the temperature of the running surface of the part of cylinder liner 1 is maintained at into acceptable level (according to gas
The material type of cylinder liner 1, maximum running surface temperature have to be lower than e.g., from about 300 DEG C or be below about in some cases
280℃).On this, peripheral recess 31 is set in the top U of cylinder liner 1 to provide for receiving liquid coolant
Space.Recess 31 towards cylinder liner 1 outer surface opening and be provided with upper recess 32 in one embodiment and recessed
Nest 33.The opening of the recess is towards lower support surface 34 and upward between support surface 35 with axial height H.
The recess 31 can be formed by milling process, or can be as this in the case where bushing is cast article
A part for casting process and formed.In the latter cases, it should the recess is processed into what is be accurately defined after the casting
Shape.
The curved surface of upper recess 32 and lower recess 33 is consistent with the shape calculated, and this, which is calculated, is shaped such that cylinder liner
Stress in 1 material is minimum.
Arrow F in Fig. 7 represents the power that cylinder head 22 is applied on the top surface of cylinder liner 1.Power F size is such
It is big so that if the cylinder if towards lower support surface 34 and upward in the gap between support surface 35 without axially support
Bushing 1 will be deformed.This is axially supported in Fig. 8 and shown.Axial support member 36 is inserted into annular recessed portion 31, so as to fill out substantially
It is full towards lower surface 34 and towards the gap between upper surface 35 with span H.As shown in figure 8, axial support member 36 supports gas
The structure of cylinder liner jacket wall, and power F sizable part is transmitted, the upper deformation of cylinder liner 1 is thus prevented, such as vertical arrow
Shown in head.Figure 10 shows the details of axial support member 36.The axial support member can take the form of a collar, for example with
The split ring of two or more parts (shows the split ring with two parts, but those skilled in the art in figure
It is clear that the axial support member can be formed by more than two multiple components, and the plurality of part need not be formed
Continuous loop, and can be suitable for providing axially multiple posts of support etc. to annular recessed portion 31 without hesitation).Axial support member 36
Towards upper surface 39 and towards between lower surface 40 have axial range h.The axial range h of axial support member 36 is preferably slightly small
The axial range H in the gap in the opening of peripheral recess 31, so as to axially support structure when cylinder head 22 is without applying power F
There is gap between part and the gap.The gap will allow cylinder liner 1 slightly to deform, until towards lower support surface 34 and upward
Support surface 35 is corresponding with axial support member 36 to abut towards upper surface 39 and towards lower surface 40.The top of cylinder liner 1
Material it is this slightly deformation cause around recess 32 and around lower recess 33 lagging material generation it is pre-tensioner, it is this pre-
Tensioning counteracts the risk that crackle is formed in corresponding recess 31,32.
Tension force can also be otherwise controlled using zero clearance or negative clearance.
Figure 14, Figure 15 and Figure 16 illustrate in greater detail circumferential supporting member 36 and its component.In the example embodiment
In, axial support member 36 includes 2 half portions 48,49 for forming ring together.Two half-unit 48,49 is loosely inserted into circumference
In recess 31, and they are not connected to each other.Figure 14 shows that two half-unit 48 in assembling process, 49, Figure 15 show group
Two half-unit 48,49 after dress.
Each half portion 48,49 is provided with the slit that coolant entrance is formed in opening 43 and forms coolant outlet aperture 42
Slit.The slit for forming coolant outlet aperture 42 is the T-shaped with blunt end, to avoid producing due to the stress in material
Crackle.
As shown in figure 9, circumferential supporting member 37 is placed around the top of cylinder liner 1.Circumferential supporting member 37 is down
Surface be shelved in the top U of cylinder liner 1 towards on upper shoulder 38.Circumferential supporting member 37 gives the upper part U of cylinder liner 1
Radial support is provided, this is represented by horizontal arrow in fig .9.In an example embodiment, circumferential supporting member 37 is height
The integral type annular body of strength steel.In order to improve the ability that circumferential supporting member 37 provides radial support, its shrink-fit is in gas
The top periphery of cylinder liner 1 is opened in advance with thus being produced in cylinder liner material and in the material of circumferential supporting member 37
Tightly.As shown in a pair of opposite arrows on the top in Fig. 9, circumferential supporting member 37 circumferentially cooling recess 31 top it is pre-tensioner
Around the axial range of cylinder liner, and as shown in a pair of opposite arrows of the bottom in Fig. 9, circumferential supporting member 37 is in week
It is pre-tensioner around the axial range of cylinder liner 1 below to cooling recess 31.
In another embodiment, the circumferential supporting member 37 (solid support part) for loosening and installing has been used.Come from
The thermal expansion of cylinder liner will produce the contact with circumferential supporting member (solid support part).
In one embodiment, circumferential supporting member 37 has sizable wall thickness, and is considered firm
Supporting member.
As shown in a pair of horizontal arrows on the top in Fig. 9 at the top of circumferential supporting member 37 and such as Fig. 9 in
Shown in a pair of horizontal arrows of bottom at the bottom of circumferential supporting member 37, radial load is in cylinder liner 1 and circumferential support structure
Transmitted between part 37.The centre portion of circumferential supporting member 37 does not handle any significant radial load, and is axially supporting structure
There is no the radial load of any notable size between part 36 and circumferential supporting member 37.
Circumferential supporting member 37 is provided with annular recessed portion 47 to provide the space that cooling agent passes through for liquid.There is provided being used for
By the pad (not shown) of the transition seal between cylinder liner 1 and circumferential supporting member 37 to ensure liquid-tight seal.Figure 13 with
Sectional view illustrates in greater detail circumferential supporting member 37.
As shown in Figure 11, inlet bore 46 is arranged in circumferential supporting member 37.The inlet bore 46 is placed substantially
In the region (such as intermediate altitude) of the low stress level of circumferential supporting member, that is, it is placed on circumferential supporting member 37
In the part for not handling any notable radial load.Inlet bore 46 is connected to the peripheral recess inwardly in circumferential supporting member 37
47.There can be more than one inlet bore 46, it is not believed that this is necessary or favourable.Inlet bore 46 be connected to from
The liquid coolant supply line 26 of cooling system supply coolant.Liquid coolant can be via in axial support member 36
Inlet bore 43 is flowed into peripheral recess 31.Via inlet bore 43, liquid coolant can be directly entered lower recess 33, and
The liquid coolant can be in axial support member 36 the peripheral recess 41 being directed inwardly toward and flow to upper recess 41.In Figure 11
Arrow substantially indicates the flow direction of liquid coolant.
As shown in figure 12, the company that flow export pipe 44 extends to the outside positioned at circumferential supporting member 37 from upper recess 32 is tilted
Connect block 50.Flow export pipe 44 is tilted to extend through the outlet opening 42 in axial support member 36 and further extend through basic cloth
Put the angling hole 45 in the intermediate altitude of circumferential supporting member 37.Being in tilted layout for flow export pipe 44 ensures entering for flow export pipe 44
Mouth is located at the highest portion office of peripheral recess 31, i.e., in fovea superior nest 32；And the incline direction of flow export pipe 44 allow by
Angling hole 45 is placed on the intermediate altitude of circumferential supporting member 37, that is, is placed on not handling for circumferential supporting member 37 any notable
In the part of radial load.Tilt the outlet of flow export pipe 44, such as via the weld flange positioned at one end of flow export pipe 44, and
It is connected to contiguous block 50.
Contiguous block 50 is fixed to the outer surface of circumferential supporting member 37.Contiguous block 50 is provided with angled hole, and
The cooling water transfer pipe 28 upwardly extended is connected to the upside of contiguous block 50.Cooling water transfer pipe 28 is used for liquid cooling
Agent guides to cool down the latter to cylinder head 22.Arrow in Figure 12 substantially indicates the flowing side of liquid coolant
To.
Figure 17 is the top U of cylinder liner 1 sectional view, shows the entrance and exit cloth of cooling and support meanss 30
Put.With in prior art design in the top of cylinder liner compared with the big ups and downs temperature of cylinder liner material, the cooling and
The construction of support meanss 30 provides the temperature substantially homogeneous in the circumferential of cylinder wall material in the top U of cylinder liner 1
Distribution.
Figure 18 is the cylinder liner 1 for showing the range determination relative to the matching surface (top surface) with cylinder head 22
The curve map of the temperature of running surface.Non- interrupt line represents present invention design i.e. according to the embodiment described in this document
The temperature curve of cylinder head.Broken curve represents prior art cylinder liner such as from cylinder bush known to WO97/42406
The temperature curve of set.In the top U of cylinder liner 1, for present invention design and the temperature curve of prior art design in reality
It is overlapping i.e. identical to trample.This is anticipated, because no matter in the design of the present invention or in prior art design
In, the top U of cylinder liner 1 is forced cooling.Difference is that present invention design is provided using circumferential cooling recess
The cooling of substantially uniformity in the circumferential, and multiple angling holes of prior art design can not provide uniform cooling in the circumferential,
So as to cause the circumferential scope on top of the temperature along cylinder liner 1 to fluctuate.However, this can not see in figure 18, because figure
18 be always to draw temperature on axial direction rather than week.The two curves cylinder liner 1 axial range just
Part below the U of top is dramatically different, and (in the plot, top is from 0 tool extended to below about 0.3m, and the top
The part for having dramatically different temperature extends to 1.3m from about 0.3m, it should be noted that these numerals are only for concrete shape
Cylinder liner 1 with size is effective, and may be very different in other designs).
It is cold without forcing in part just in the axial range below the top for the cylinder liner 1 that the present invention is designed
But cause the temperature of running surface considerably higher, temperature difference is up to 50 DEG C.In area just below the top U of cylinder liner 1
The temperature of running surface in domain, which increases, make it that the condensation of acidic combustion products is less, so that the corrosion of cylinder liner 1 subtracts
Less and cause cylinder oil consumption reduce (cylinder oil have be used for compensation combustion product in acidity basis).Along
Running surface is further downward, i.e., be greater than about from cylinder head at 1.3m, the running surface that present invention design and prior art are designed
Temperature it is identical, need not equally increase temperature because due to the expansion of combustion chamber, the acidic combustion products of high concentration less than
Up to the part of the running surface of cylinder liner.Under less than the 100% of Continuous Maximum Rating engine load, except
To cylinder liner force the advantage no less important of cooling outside the top U of cylinder liner.Just in the upper of cylinder liner
Running surface below portion U in axial cylinder bushing 1 obtains higher temperature and is equally applicable to relatively low engine load.
Combined various embodiments here describe the present invention.However, by studying accompanying drawing, the disclosure and institute
Attached claim, when putting into practice invention claimed, it will be appreciated by those skilled in the art that and performing to disclosed implementation
The various changes that mode is carried out.In the claims, wording " comprising " is not precluded from other element or steps, and indefinite article
" one " is also not excluded for multiple.The unique fact for some measurements quoted from mutually different dependent claims is not intended that this
The combination measured a bit can not be used for outstanding advantages.The reference used in the claims is not construed as entering scope
Row limitation.
Claims (11)
1. a kind of cylinder liner (1) for two-stroke cross head engine, the cylinder liner (1) includes：
It is suitable for the first end engaged with cylinder head (22)；
Scavenging port (18)；
Being located near the first end in the wall of the cylinder liner (1) is used for the circumferential cooling recess of liquid coolant
(31), the circumferential cooling recess (31) has the circumference in the outer surface of the wall of the cylinder liner (1)
Extension opening；
Axial support member (36), the axial support member (36) is at least partially interposed in the peripheral recess, the axle
To supporting member (36) by the circumferentially extending opening bridge joint, and the axial support member is provided with coolant channel outlet
Hole (42) and coolant channel ingate (43).
2. cylinder liner (1) according to claim 1, wherein the axial support member (36) is configured to the week
Axially support is provided to cooling recess.
3. cylinder liner (1) according to claim 1 or 2, wherein the axial support member (36) fills the opening
Axially opposing direction surface (34,35) between axial space.
4. cylinder liner (1) according to claim 3, wherein under the non-stress state of the cylinder liner, it is described to open
The axial space (H) between the surface (34,35) of the axially opposing direction of mouth is slightly larger than the axially support structure
Axial axial distance h between the axially opposed surfaces of part (36), so that in the opening and the axial support member (36)
Between have small axial gap.
5. cylinder liner (1) according to any one of claim 1 to 4, wherein the axial support member (36) be by
The split ring of two or more sections (49,48) formation.
6. cylinder liner (1) according to any one of claim 1 to 5, wherein the circumferential cooling recess (31) includes
Upper recess (32), and alternatively also include lower recess (33).
7. cylinder liner (1) according to claim 6, wherein the circumferential cooling recess (31) is included the upper recess
(32) cylindrical surface (51) being connected with the lower recess (33).
8. cylinder liner (1) according to claim 7, wherein the ring-type that the axial support member (36) is included inwardly is recessed
Portion (41), and wherein limited between the annular recessed portion (41) and the cylindrical surface (51) inwardly for cooling agent
Space.
9. cylinder liner (1) according to any one of claim 1 to 8, wherein the circumferential cooling recess (21) is arrived deeply
It is enough to store the axial support member (36), without making the axial support member (36) from the circumferential cooling recess (31)
It is prominent.
10. cylinder liner (1) according to any one of claim 1 to 9, the cylinder liner further comprises positioned at described
Multiple cylinder lubricating oil supply orifices (25) in the wall of cylinder liner (1), this some holes is preferably surrounded in essentially identical level
The circumferential distribution of the cylinder liner (1).
11. a kind of two-stroke cross head engine, the engine includes at least one according to any one of claim 1 to 10
Described cylinder liner (1).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201570706A DK178937B9 (en) | 2015-11-02 | 2015-11-02 | A cylinder liner for a two-stroke crosshead engine |
| DKPA201570706 | 2015-11-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107061037A true CN107061037A (en) | 2017-08-18 |
| CN107061037B CN107061037B (en) | 2018-10-09 |
Family
ID=58767703
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610936947.2A Active CN107061037B (en) | 2015-11-02 | 2016-11-01 | Cylinder liner for two-stroke cross head engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6258445B2 (en) |
| KR (1) | KR101860474B1 (en) |
| CN (1) | CN107061037B (en) |
| DK (1) | DK178937B9 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB488780A (en) * | 1936-11-06 | 1938-07-13 | Alessandro Tebaldi | Improvements in cylinders for internal combustion engines |
| WO1994028296A1 (en) * | 1993-05-26 | 1994-12-08 | Man B & W Diesel A/S | A method and an internal combustion engine |
| CN1218540A (en) * | 1996-05-07 | 1999-06-02 | 曼B与W狄赛尔公司 | Cylinder liner for IC engine |
| CN1460789A (en) * | 2002-05-21 | 2003-12-10 | 曼B与W狄赛尔公司 | Supporting board for large two-stroke internal combustion engine cylinder jacket |
| CN201535205U (en) * | 2009-09-24 | 2010-07-28 | 常州朗锐活塞有限公司 | 230 diesel engine cylinder jacket |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1751176A1 (en) * | 1968-04-17 | 1970-08-06 | Maschf Augsburg Nuernberg Ag | Water-cooled cylinder for internal combustion engines |
| US4244330A (en) * | 1978-11-13 | 1981-01-13 | Cummins Engine Company, Inc. | Engine cylinder liner having a mid stop |
| US5150668A (en) * | 1992-02-20 | 1992-09-29 | Caterpillar, Inc. | Cylinder liner with coolant sleeve |
| US5979374A (en) * | 1998-06-12 | 1999-11-09 | Cummins Engine Company, Inc. | Control cooled cylinder liner |
| JP3011920B2 (en) * | 1998-06-16 | 2000-02-21 | 川崎重工業株式会社 | Cylinder liner cooling structure |
| US6532915B2 (en) * | 2001-07-27 | 2003-03-18 | Caterpillar Inc | Sealing arrangment for a cylinder liner |
| JP5721595B2 (en) | 2011-09-14 | 2015-05-20 | 三菱重工業株式会社 | Internal combustion engine cooling structure |
-
2015
- 2015-11-02 DK DKPA201570706A patent/DK178937B9/en active
-
2016
- 2016-11-01 KR KR1020160144333A patent/KR101860474B1/en active IP Right Grant
- 2016-11-01 CN CN201610936947.2A patent/CN107061037B/en active Active
- 2016-11-02 JP JP2016215626A patent/JP6258445B2/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB488780A (en) * | 1936-11-06 | 1938-07-13 | Alessandro Tebaldi | Improvements in cylinders for internal combustion engines |
| WO1994028296A1 (en) * | 1993-05-26 | 1994-12-08 | Man B & W Diesel A/S | A method and an internal combustion engine |
| CN1218540A (en) * | 1996-05-07 | 1999-06-02 | 曼B与W狄赛尔公司 | Cylinder liner for IC engine |
| CN1460789A (en) * | 2002-05-21 | 2003-12-10 | 曼B与W狄赛尔公司 | Supporting board for large two-stroke internal combustion engine cylinder jacket |
| CN201535205U (en) * | 2009-09-24 | 2010-07-28 | 常州朗锐活塞有限公司 | 230 diesel engine cylinder jacket |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017089643A (en) | 2017-05-25 |
| DK201570706A1 (en) | 2017-05-03 |
| KR20170051363A (en) | 2017-05-11 |
| CN107061037B (en) | 2018-10-09 |
| DK178937B9 (en) | 2017-07-03 |
| KR101860474B1 (en) | 2018-05-23 |
| DK178937B1 (en) | 2017-06-19 |
| JP6258445B2 (en) | 2018-01-10 |
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Address after: Copenhagen Patentee after: Man energy solutions (man energy solutions, Germany Ag) branch Address before: Copenhagen Patentee before: Man Diesel AS |