CN108368773A - Quartastroke engine - Google Patents
Quartastroke engine Download PDFInfo
- Publication number
- CN108368773A CN108368773A CN201680070913.8A CN201680070913A CN108368773A CN 108368773 A CN108368773 A CN 108368773A CN 201680070913 A CN201680070913 A CN 201680070913A CN 108368773 A CN108368773 A CN 108368773A
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- Prior art keywords
- port
- turbine
- piston
- exhaust
- stroke
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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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/04—Engines with prolonged expansion in main cylinders
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
- F01B17/02—Engines
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- 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
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
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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
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
Disclosed herein is a kind of internal combustion engine (2) comprising forms at least one cylinder unit (4) of combustion chamber (23).Engine (2) further includes at least one turbine (21) comprising turbine (26) and have turbine inlet area ATIN.Discharge duct (6) extends to turbine inlet area A from the port (15) in the lower half of casing bore (12) for being arranged in cylinder unit (4)TIN.Piston (10) has different piston stroke lengths, expansion stroke and exhaust stroke ratio induction stroke and compression stroke are long, so that port (15) are not covered during the part of expansion stroke and exhaust stroke by piston (10), and covered by piston (10) during induction stroke and compression stroke.
Description
Technical field
The present invention relates to a kind of quartastroke engines including turbine.
Background technology
In the quartastroke engine including turbine (such as turbocharger), the pressure at expulsion in cylinder is used to drive
The turbine of dynamic turbine.
The piston of quartastroke engine executes four strokes, induction stroke, compression stroke, expansion stroke and exhaust stroke.
Exhaust apparatus including such as internal combustion engine of arc exhaust poppet must reach its lower dead center BDC by piston during expansion stroke
Front opening.Otherwise, if exhaust apparatus will (such as when piston reaches BDC) opens later, from cylinder internal
The internal pressure of exhaust will prevent piston from being moved towards top dead centre TDC during exhaust stroke.Therefore available engine power
It can reduce.
Exhaust apparatus allows part exhaust to reach BDC in piston during expansion stroke in the front opening of the BDC of piston
It is escaped before by exhaust apparatus, is referred to as releasing.Term release can be used for before piston reaches BDC and piston
After reaching BDC, what exhaust was escaped by exhaust apparatus, while the pressure of cylinder internal is more than the exhaust system in exhaust apparatus downstream
Pressure in system.The energy (work() released, that is, energy of releasing are escaped by exhaust apparatus and are transmitted to internal combustion not via piston
The bent axle of machine.
US4535592 discloses a kind of internal combustion type Turbocompound engine drive, with traditional reciprocating piston,
Cylinder, manifold, fuel oxygen mixing arrangement or fuel injector, igniter or compression ignition device, and be combined with corresponding
Spray nozzle device improvement, for by heat high-pressure combustion product (exhaust) be transmitted to one or more turbines from corresponding cylinder
Machine.The arrival end of spray nozzle device and outlet end respectively with the corresponding boundary wall and turbine of corresponding combustion chamber or cylinder
Entrance connects.The nozzle group valve quickly opened will be vented from corresponding cylinder and introduce spray nozzle device.
US5775105 discloses a kind of plug of actuated by cams, opens and closes the air bleeding valve in engine cylinder bore
Port.Plug is mobile and forms the best variable geometry nozzles of the exhaust for being escaped from cylinder, by maximum speed energy
Amount assigns these exhausts, for being conveyed first with supersonic speed, then as cylinder pressure decaying to be conveyed compared with low velocity, to drive
The turbine of the dynamic axis or other service loads for delivering power to internal combustion engine.
The plug of nozzle group valve and actuated by cams discussed in above mentioned document can be proved to be real in practice
Now get up more complicated device.
Invention content
Including the quartastroke engine of turbine it is an object of the present invention to provide a kind of, wherein providing reliable device
To utilize exhaust energy.
According to an aspect of the present invention, which is realized by a kind of quartastroke engine, the quartastroke engine
At least one cylinder unit and bent axle including forming combustion chamber.At least one cylinder unit includes piston, connecting rod, cylinder
Hole and for the exhaust apparatus being discharged from casing bore will to be vented.Piston company of being pivotably connected at the first end of connecting rod
It bar and is arranged to move back and forth in casing bore in induction stroke, compression stroke, expansion stroke and exhaust stroke.Exhaust
Device includes the port being arranged in the lower half portion of casing bore.Quartastroke engine further includes at least one turbine, the whirlpool
Turbine includes turbine and has turbine inlet area ATIN.Discharge duct extends to turbine inlet area A from portTIN.Piston
With different piston stroke lengths, expansion stroke and exhaust stroke ratio induction stroke and compression stroke are longer, so that port
It is not covered by piston during the part of expansion stroke and exhaust stroke, and by piston during induction stroke and compression stroke
Covering is recruited.
Since piston has different length of piston travel, expansion stroke and exhaust stroke ratio induction stroke and compression
Stroke is longer so that port is not covered during the part of expansion stroke and exhaust stroke by piston, and in induction stroke and
It is covered by piston during compression stroke, therefore does not need any individual valve in discharge duct to open and close discharge duct.
As a result, realizing the purpose to be previously mentioned.
Further, since exhaust apparatus includes the port being arranged in the lower half of casing bore and discharge duct prolongs from port
Reach turbine inlet area ATIN, therefore the energy of releasing being vented is effectively utilised in the turbine.
Quartastroke engine may include more than one cylinder unit, and each cylinder unit has piston and exhaust apparatus.
Quartastroke engine may include more than one turbine.Turbine for example can be turbocharger, can form turbine
A part for hybrid engine, or can be the turbine for driving generator.Piston can be connected to internal combustion engine via connecting rod
Bent axle.Suitably, connecting rod can be connected indirectly to bent axle.The port may include a single-port.However, herein
Statement for port further includes being divided into the port of two or more port sections and being connected in casing bore is same
The more than one odd number port of a discharge duct.
Inside cylinder unit, there are combustion chambers above piston.Air inlet passes through cylinder during the induction stroke of piston
The inlet duct of device enters combustion chamber.Air inlet can be by turbocharger compresses.Internal combustion engine can be such as such as diesel-type
Compression ignition (CI) engine of engine or spark ignition (SI) engine of such as Otto h type engine h, and the latter's
In the case of include spark plug or similar device in cylinder unit.Fuel can be in the induction stroke of piston or the portion of compression stroke
It is injected into combustion chamber, or can be entrained together with air inlet between by stages.Fuel may piston compression stroke with do
Near TDC between work(stroke is lighted.
According to embodiment, when piston is in the lower dead center BDC between expansion stroke and exhaust stroke, the port of port
Area APORTIt can be with the turbine inlet area A of turbineTINAt least twice size.In this way it is possible to ensure to hold
Open area APORTThe outflow of exhaust is not limited during releasing.Therefore, the energy of releasing of exhaust can be effective in the turbine
Ground utilizes.
According to embodiment, the height of port can be between the top dead centre TDC and expansion stroke and exhaust stroke of piston
Lower dead center BDC between piston stroke length 8% to 16% in the range of.In this way, port can be uncovered,
To ensure that the energy of releasing of exhaust is released to turbine so as to effectively use wherein.According to some embodiments, work as piston
When reaching BDC, port will not covered by piston completely.In such an embodiment, the height of port will be upwardly extended from BDC
8% of piston stroke length between expansion stroke and exhaust stroke between the top dead centre TDC of piston and lower dead center BDC to
Height between 16%.
According to embodiment, which can have in piston between expansion stroke and exhaust stroke
Lower dead center BDC and the upper inner defining surface of combustion chamber between maximum volume VMAX.Port can be configured at piston
By port area A when lower dead center BDC between expansion stroke and exhaust strokePORTExpose as at least 0.44 × VMAXSize.
In this way, port area A when piston is in lower dead center BDCPORTSize may be set so that the energy of releasing of exhaust
Amount can be effectively utilised in the turbine.
It was found by the inventors that being had already turned on corresponding as the BDC that piston is between expansion stroke and exhaust stroke
It is multiplied by maximum volume V at least 0.44MAXSize port area APORTThe major part in energy that causes to release is passed to whirlpool
Turbine.That is, passing through exhaust flow area A in a manner of unrestricted by the initial burst of the exhaust for generation of releasingPORT
And it is transmitted to turbine inlet area A via discharge ductTIN, to be utilized in the turbine.
According to embodiment, cylinder unit can have the lower dead center in piston between expansion stroke and exhaust stroke
Maximum volume V between BDC and the upper inner defining surface of casing boreMAX.The instantaneous cylinder volume V of cylinder unit can be by
Instantaneous position of the piston during its reciprocating motion in casing bore defines, wherein
APORT(V) it indicates port area of the port during the expansion stroke of piston, is the letter of cylinder instantaneous volumetric V
Number, wherein
The exhaust gas flow area coefficient δ of port is defined as
δ=APORT(V)/(0.22×VMAX), APORTWith m2It indicates, and VMAXWith m3It indicates,
Wherein
Port has opening speed factor beta, is defined as
β=(V (δ=1)-V (δ=0.1))/VMAX, and wherein
Port area APORTWith opening speed factor beta<0.06.
In this way, port area APORTIt can be opened with the speed for providing low flow resistance in exhaust apparatus.
Therefore, effective transmission of the energy from combustion chamber to discharge duct of releasing can be promoted.
In other words, opening speed factor beta<0.06 means during expansion stroke, and cylinder volume increases less than 6%, and
APORTFrom 0.22 × VMAX10% increase to 100%.
According to embodiment, cylinder unit can have the lower dead center in piston between expansion stroke and exhaust stroke
Maximum volume V between BDC and the upper inner defining surface of casing boreMAX.Discharge duct can have discharge duct volume VEXH,
Wherein VEXHLess than or equal to maximum volume VMAX0.5 times.In this way, the energy of releasing of exhaust can be delivered effectively logical
Discharge duct is crossed, to be utilized in the turbine.
In addition, defined maximum discharge duct volume VEXHIt can in conjunction with opening speed factor beta that is defined over and discussing
To ensure that the initial burst of the exhaust generated by exhaust energy can be used for turbine.
According to embodiment, quartastroke engine may include the movable cylinder for being configured to the size for changing port
Wall part.Movable cylinder wall part can move between the first location and the second location, displaceable wall part this first
A part for port is formed at position, displaceable wall part is removed in the second place from port.In this way it is possible to
Realize variable port sizes.For example, when the speed of internal combustion engine to be increased, it can be by the way that displaceable wall part be located in
Increase port sizes at two positions, to accelerate the speed of turbine to increase with the speed of auxiliary engine.Once turbine
It has been accelerated that, displaceable wall part can be again positioned at its first position.
According to embodiment, exhaust apparatus may include the valve gear at the upper inner defining surface in casing bore,
Valve gear is fluidly connected with the exhaust line for extending to turbine downstream.In this way, it during exhaust stroke, is holding just
Before mouth is covered by piston, or after port is capped, the remaining exhaust in cylinder unit can be discharged by valve gear.
Since (i.e. during so-called scavenging), exhaust is no longer contributed to from the exhaust in turbine during the major part of exhaust stroke
Middle extraction work(, therefore can be wasted in the turbine to avoid energy around turbine using the exhaust line in turbine downstream.
According to embodiment, turbine can have standardized effective flowing area γ, be defined as
γ=ATURB/VMAX, wherein γ>0.22m-1, wherein ATURB=(ATIN/ATOT)×m’RED×(R/(κ(2/(κ+1
)X)))1/2, wherein X=(κ+1)/(κ -1), wherein ATOTIt is the main entrance area of turbine, and wherein ATURBIt is in turbine
Entrance side and outlet side between pressure ratio be 2.5-3.5 in the case of and in the tip speed of turbine be 450m/s
In the case of turbine reduction mass flow m 'REDLower acquisition.
In this way it is possible to a kind of turbine be provided, wherein can utilize by the production of releasing from a cylinder unit
It gives birth to and via defined port area APORTWith defined discharge duct volume VEXHIt is transmitted to turbine inlet area ATIN's
The initial burst of exhaust.In addition, in the turbine with the standardized effective flowing area γ defined in this way, energy of releasing
It can be extracted from exhaust in the degree in crank angle less than 80 degree of bent axle.Therefore, releasing energy can be from being connected to turbine
Each cylinder unit in independently extract because the exhaust from different cylinder units reaches at the different degree in crank angle of bent axle
To turbine.
Other than the capacity usage ratio of releasing in turbine improves, the quartastroke engine of type discussed above also has
There is excellent gas exchanges performance.That is, since the quick of port is opened and the big available exhaust flow surface in port
Characteristic defined by the upper surface of product and turbine, therefore exhaust is influenced by low back pressure.In the exhaust system of internal combustion engine
Low back pressure promotes the high efficiency of exhaust, low energy discharge.In the quartastroke engine as defined by certain embodiments above
In, realize the discharge of this low energy, while using largely letting out still in the turbine with characteristic as defined above
Exoergic amount.In other words, a large amount of available energy of releasing is recovered in the turbine, without being unfavorable for high inner cylinder pressure
Exhaust stroke, this will cause high negative piston to pump work(.
According to another aspect of the present invention, it includes according to any aspect discussed in this article and/or implementation to provide one kind
The vehicle of the quartastroke engine of mode.
When studying appended claims and detailed description below, further characteristic of the invention and advantage will become
Obviously.
Description of the drawings
According to the illustrative embodiments discussed in detailed description below and attached drawing, this hair will readily appreciate that
Bright various aspects, including its special characteristic and advantage, wherein：
Fig. 1 a and 1b schematically show the quartastroke engine according to embodiment,
Fig. 1 c and 1d show the partial cross section view of the alternate embodiments of quartastroke engine,
Fig. 2 shows the chart of the mass flow on the exhaust apparatus of quartastroke engine,
Fig. 3 shows the chart of the exhaust flow area of exhaust apparatus,
Fig. 4 shows the illustrative examples of the turbine figure of turbocharger,
Fig. 5 shows the implementation of the illustrative embodiments of quartastroke engine and the vehicle including quartastroke engine
Mode,
Fig. 6 and 7 shows that two cylinder units are connected to the embodiment of turbine.
Specific implementation mode
Each aspect of the present invention will be described more fully now.Identical number refers to identical element always.For letter
For the sake of clean and/or clear, well-known function or structure can be not necessarily described in detail.
Fig. 1 a and 1b schematically show the quartastroke engine 2 according to embodiment.Referring to Fig. 1 a, four-stroke ic
Machine 2 includes at least one cylinder unit 4, discharge duct 6 and at least one turbine (21) for forming combustion chamber 23, the turbine
Machine is schematically illustrated as a part for turbocharger 8 in these embodiments.
At least one cylinder unit 4 include piston 10, connecting rod 22, casing bore 12, for make exhaust from casing bore 12 flow
Exhaust apparatus 14, ingress port device 16 and the fuel injection device 18, and/or ignition device gone out.Piston 10 is in connecting rod 22
It is pivotably connected to connecting rod 22 at first end, and is arranged in induction stroke, compression stroke, expansion stroke and exhaust punching
It is moved back and forth in casing bore 12 in journey.
Exhaust apparatus 14 includes the port 15 being arranged in the lower half portion of casing bore 12.Discharge duct 6 prolongs from port 15
Reach turbine inlet area ATIN.Piston 10 has different piston stroke lengths, and expansion stroke and exhaust stroke compare induction stroke
It is longer with compression stroke, so that port 15 is not covered during the part of expansion stroke and exhaust stroke by piston 10, and
It is covered by piston 10 during induction stroke and compression stroke.In Fig. 1 a and 1b, piston 10 is shown in phantom in its tDC.
In fig 1 a, it is shown with solid line at BDC of the piston 10 between its induction stroke and compression stroke, middle port 15 is capped.
In Figure 1b, it is shown with solid line at BDC of the piston 10 between its expansion stroke and exhaust stroke, middle port 15 is not coating
Lid.Therefore, when piston moves back and forth in piston hole 12, the port area A of the port 15 of exhaust apparatus 14PORTBe opened and
It closes.Length of piston travel between the TDC and BDC of piston 10 of the height of port 15 between expansion stroke and exhaust stroke
8-16% within the scope of.In these embodiments, only when piston 10 reaches BDC, port 15 is not covered completely by piston 10.
In an alternative embodiment, port can be positioned to higher along casing bore, so that port is complete before piston reaches BDC
It is uncovered.The advantages of exhaust is discharged using the port in casing bore is at least part (i.e. port area in exhaust stream region
APORT) quick opening speed.In the embodiment that the front port for wherein reaching BDC in piston is uncovered completely, realize
Further advantage, i.e. port area APORTOpening speed even than wherein only when piston reaches BDC port ability it is complete
Port area A in the embodiment being uncoveredPORTOpening speed faster.
In Fig. 1 a and 1b, piston 10 has been shown more shorter than in practice.I.e. practical upper piston 10 should suitably have
There is certain length, so that port 15 is covered when it is in its TDC by piston 10, to avoid in discharge duct 6 and four strokes
The crankcase of combustion engine 2 is connected to.
The different length of piston travel of piston 10 can be by the mechanism that connect connecting rod 22 with the bent axle 20 of internal combustion engine 2
27 realize.Mechanism 27 is schematically shown in Fig. 1 a and 1b.Various such mechanisms are known, such as in patent document
In so-called Atkinson cycle engine disclosed in US367496, or as can disclosed in patent document US4517931
Become in Stroke Engine.
In these embodiments, port 15 is only formed by fixed component.That is, port 15 is by casing bore 12
Fixed-size one or more openings formed.Therefore, in these embodiments, port area APORTIt is immutable.
During the reciprocating motion of piston 10, cylinder unit 4 has instantaneous cylinder volume V.That is, cylinder unit
Instantaneous cylinder volume V is defined by instantaneous position of the piston 10 in casing bore 12.Therefore, port area APORTIt can be expressed as wink
When cylinder volume V function, i.e. APORT(V).As will be discussed below, A is utilized during the expansion stroke of piston 10PORT(V)
Opening speed for limiting port 15.Exhaust apparatus 14 further includes the valve at the upper inner defining surface 24 of casing bore 12
Device 17.Valve gear 17 is fluidly connected with the discharge duct 19 for extending to 21 downstream of turbine.Valve gear 17 has past in piston
The exhaust flow area A changed during multiple movementCYL.More specifically, exhaust flow area ACYLDuring exhaust stroke just
It is started to open at before or after port 15 are completely covered in piston 10.
According to some embodiments, valve gear 17 can be fluidly connected selectively with the discharge duct of turbine upstream 6.
In this way, under some operating conditions, valve gear 17 can be connected in the upstream of turbine.For example, adding to improve
Engine loading response during speed.As shown in Figure 1 b, two-way valve 25 can be provided, for selectively connecting exhaust line 19
It is connected to discharge duct 6.Two-way valve 25 can be controlled by the control system (not shown) of quartastroke engine 2.
Turbine 21 includes turbine 26.Turbine 21 includes turbine inlet area ATIN.Turbine inlet area ATINIt is set
In the opening of the shell of turbine 21, exhaust enters turbine 26 in the opening.Turbine inlet area ATINCan be suitably
The nozzle throat region of turbine.Nozzle throat region can also be referred to as turbine casing throat region, turbine casing closes
Key range or similar portions, and can usually be provided for specific turbine.It is provided not being directed to specific turbine
Nozzle throat and/or in the case of not providing the position in nozzle throat region, turbine inlet area ATINPerpendicular to the flowing of exhaust
Direction extends.Discharge duct is extended along a part for turbine wheel and (such as is extended with volute, such as in binary vortices formula whirlpool wherein
Take turns booster in) turbine embodiment in, turbine inlet area ATINBe limited at discharge duct keeps turbine sudden and violent first
It is exposed to from the section for the exhaust that related cylinder unit is sent out.
Cylinder unit 4 has in the BDC between the expansion stroke and exhaust stroke of piston 10 and the top of combustion chamber 23
Maximum volume V between side defining surface 24MAX.Combustion chamber 23 is formed in inside cylinder unit 4 above piston 10.Piston 10
It is connected to the bent axle 20 of internal combustion engine 2.More specifically, piston 10 can be connected indirectly to bent axle via connecting rod 22 and mechanism 27
20。
Cylinder unit 4 has always sweeping in the casing bore 12 during expansion stroke and exhaust stroke between BDC and TDC
Air volume VS.Cylinder unit 4 has geometrical compression ratio, ε=VMAX/VMIN。VMAXIt can be represented as：VMAX=VS×(ε/(ε-
1))。
Port 15 is connect by discharge duct 6 with turbine 21.Discharge duct 6 has discharge duct volume VEXH.In Fig. 1 a and
In 1b, discharge duct volume VEXHIt is shown as box.In fact, discharge duct 6 is in port area APORTWith turbine inlet area
ATINBetween extend.Therefore, discharge duct volume VEXHBy discharge duct in port area APORTWith turbine inlet area ATINBetween
Volume formed.Discharge duct 6 is only by port 15 and turbine inlet area ATINIt fluidly connects.That is, 6 shape of discharge duct
At in port area APORTWith turbine inlet area ATINBetween the independent pipeline that extends.Independent pipeline does not have any other use
Entrance in exhaust or outlet.Therefore, turbine inlet area ATINIt is for via the coupled port 15 of discharge duct 6
The special inlet area of turbocharger 8.
Discharge duct volume VEXHLess than or equal to maximum volume VMAX0.5 times, i.e. VEXH≤0.5×VMAX.In addition, working as piston
When lower dead center BDC between expansion stroke and exhaust stroke, the port area A of port 15PORTIt can be with turbine
Turbine inlet area ATINAt least twice size.Size additional for port 15 or the standard substituted can be,
It is configured as port area A when piston is in the lower dead center BDC between expansion stroke and exhaust strokePORTIt exposes as at least
0.44×VMAXSize, i.e. APORT≥0.44×VMAX.Therefore, when piston 10 is between expansion stroke and exhaust stroke
When BDC, meet standard：APORT/VMAX≥0.44m-1。
The turbine 26 of turbine 21 in turbocharger 8 is connected to for compressing and being transported to air inlet port dress by air inlet
Set 16 impeller (not shown).
According to some embodiments, turbine 26 can be axial turbine.Turbine including axial turbine can provide this
The low back pressure that text is discussed.However, according to alternate embodiments, turbine can be radial turbine, can also provide this paper institutes
The low back pressure discussed.Turbine 21 can be impulse turbine machine or reaction turbine.
According to some embodiments, cylinder unit 4 can in piston in casing bore 12 expansion stroke and exhaust
Total scavenging volume V between lower dead center BDC between stroke and top dead centre TDCS, and wherein 0.3<VS<4 liters.It is purely acting as reality
It applies example to mention, in VSRelatively low range in, cylinder unit 4 can form the part of the internal combustion engine for car, and in VSIn
Between and more high scope in, cylinder unit 4 can be formed for the interior of heavy-duty vehicle (such as truck, bus or construction vehicle)
A part for combustion engine.Equally in VSHigher range in, cylinder unit 4, which can be formed, is used for such as generator unit (generator
Group), the part of internal combustion engine that is used with Yu Haiyang or used for railway (train).
Fig. 1 c and 1d show the partial cross section view of the alternate embodiments of quartastroke engine 2.These embodiments
It is largely analogous to the embodiment of Fig. 1 a and 1b, however, quartastroke engine 2 includes being configured to for changing port 15
Size movable cylinder wall part 31.Movable cylinder wall part 31 can move between the first location and the second location
Dynamic, displaceable wall part 31 forms the top of port 15 at the first position, and displaceable wall part 31 is in the second place
It is removed from port 15.Therefore, during the operation of quartastroke engine 2, the port area A of port 15PORTIt can change.For
The size of control port 15, movable cylinder wall part 31 can be controlled by controller system (not shown).In figure 1 c,
Movable cylinder wall part 31 is shown at its first position to form extension of the casing bore 12 in port 15, and
In Fig. 1 d, movable cylinder wall part 31 is shown in its second place removed from port 15 and casing bore 12.
In Fig. 1 c and 1d, piston 10 has been shown more shorter than in practice.That is, practical upper piston 10 should have
There is such length so that piston 10 covers port 15 when in its top dead centre TDC, to avoid discharge duct 6 and crankcase
It is connected to (if it is quartastroke engine 2).
According to alternate embodiments, more than one cylinder unit can be connected to turbine at a position of turbine 21
Machine 21.Fig. 6 is shown in which two cylinder units 4 via a turbine inlet area ATINIt is connected to the embodiment party of turbine 21
Formula, i.e. two cylinder units 4 share same turbine inlet area ATIN.Therefore, the row from the port of two cylinder units 4 15
The connection of airway branch 6 ', 6 " leads to turbine 21 and turbine inlet area A to be formedTINPublic exhaust manifolds 6.Due to working as
Exhaust flow to turbine inlet area A from one of cylinder unit 4TINWhen, exist between Liang Ge discharge ducts branch 6 ', 6 "
A degree of cross flow one, therefore standard discussed above：VEXH≤0.5×VMAXFor Liang Ge exhaust manifolds branch 6 ',
6 " and public exhaust manifolds 6 common discharge duct volume VEXHIt is effective.Fig. 7 is shown in which that two cylinder units 4 pass through
The embodiment of turbine 21 is connected to by two individual exhaust manifolds 6, each exhaust manifolds lead to a turbine inlet face
Product ATIN1, ATIN2.Turbine inlet area ATIN1, ATIN2Positioning adjacent to each other so that they may be considered that the one of turbine 21
Turbine 21 is connected at a position.Two turbine inlet area ATIN1, ATINCross flow one between 2 can be ignored.Cause
This, is for each discharge duct 6, standard discussed above：VEXH≤0.5×VMAXIt is effective.
In general, being not considered as that the volume of the connection of disengaging discharge duct 6 forms discharge duct volume VEXHA part, if
If such connection has the cross-sectional area less than limiting value.According to embodiment, discharge duct volume VEXHDo not include all
It is less than or equal to 0.022m via having in its narrowest part-1It is multiplied by maximum volume VMAXSmallest connection cross-sectional area ACONConnection
And it is connected to the volume of discharge duct 6.That is, cross-sectional area ACONLimiting value be when piston 10 be in expansion stroke with
About port area A when lower dead center BDC between exhaust strokePORTThe upper surface of discussed the 5% of standard.Using small in this way
Cross-sectional area ACON, exhaust can be ignored by any cross flow one of connection.In the figure 7 it has been noted that with connecting
Meet cross-sectional area ACONTwo examples connection 7.It is purely acting as embodiment to mention, this connection 7 can form exhaust gas recirculatioon
(EGR) part for system, or may be coupled to sensor etc..
Fig. 2 shows the charts of the mass flow on the exhaust apparatus of quartastroke engine.Along the X-axis of the chart,
Four strokes of the piston in the casing bore of the cylinder unit of internal combustion engine, expansion stroke 30, exhaust stroke 32, induction stroke 34,
And compression stroke 36 is instructed between the lower dead center BDC and top dead centre TDC of piston.The angle of the bent axle of internal combustion engine is also in X
It is provided on axis.0 crank angle is set at the tDC between exhaust stroke 32 and induction stroke 34.By exhaust apparatus with
Kg/s is that the exemplary mass flow of unit provides in Y-axis.
The curve graph of chart shows the mass flow of exhaust apparatus.At point 38, exhaust apparatus starts to open at.In point 40
Place, exhaust apparatus are again switched off.Therefore, in the period between point 38 and 40, exhaust flow area is exposed and increases
To maximum value, then reduces and close.In period between point 38 and 40, exhaust is arranged via exhaust apparatus from cylinder unit
Go out.Period between point 38 and 40 can be roughly divided into two parts, that is, release 42 and cleaning 44.In 42 periods of releasing, with row
The pressure in flow of air area downstream is compared, and there are excessive pressure in the exhaust in casing bore.Excessive pressure causes to be vented
It is spontaneously flowed out from casing bore via exhaust flow area.Excessive pressure can be for example utilized in the turbine.According to this
Invention, in 42 periods of releasing, the port of exhaust apparatus is not covered by piston.It is thereby achieved that effectively will exhaust via port
It is discharged to turbine, this contributes to the height of the energy of releasing in turbine to utilize.During cleaning 44, with exhaust flow area
The pressure in downstream is compared, and no longer there is excessive pressure in the exhaust in casing bore, and be vented when it in casing bore to
It is discharged on exhaust apparatus by piston when upper traveling.Specifically, as discussed above in conjunction with Fig. 1 a and 1b, exhaust can
To be discharged by valve gear 17 during cleaning.
Vent sequence starts at point 38, terminates at point 40, and indicated by reference numeral 46.In addition, doing work
At BDC (- 180.0 degree) between stroke 30 and exhaust stroke 32, port area APORTIt has already turned on to APORT≥0.44×VMAX
Degree.
Fig. 3 shows the chart of the exhaust flow area of exhaust apparatus.Each such exhaust apparatus forms cylinder unit
A part, which further includes the piston for being arranged to move back and forth in casing bore.Along Y-axis with mm2To exhaust
The exemplary exhaust flow area of device.Relative cylinder volume is provided along X-axis, that is, calculates instantaneous cylinder volume V and holds with maximum
Product VMAXBetween ratio V/VMAX.Therefore, at ratio 1, piston is at its BDC, i.e., in embodiments of the present invention
BDC between expansion stroke and exhaust stroke.
Two curve graphs 50,54 are shown in chart.First curve graph 50 be related to include standard cams axis control exhaust
The exhaust apparatus of poppet.First curve graph 50 shows that poppet is opened with about 0.82 ratio, and the exhaust of poppet
Flow area is gradually increased as piston is advanced towards BDC, and is reached with 0.88 ratio as piston is advanced towards TDC
To its maximum exhaust flow area.Second curve graph 54 is related to including the exhaust for being arranged in the port at the lower half portion of casing bore
Device.Second curve graph 54 shows that exhaust apparatus is opened with about 0.88 ratio, and port area is as piston is towards doing
BDC between work(stroke and exhaust stroke advances and gradually increases.
As will be discussed below, the first curve graph 50 shows the characteristic of the exhaust apparatus of the prior art, and second is bent
Line chart 54 shows the characteristic of the exhaust apparatus of embodiments discussed herein.
According to embodiment, the instantaneous cylinder volume V of cylinder unit by piston during its reciprocating motion in casing bore
Instantaneous position definition.APORT(V) it indicates port area of the port during the expansion stroke of piston, is instantaneous cylinder volume
The function of V.The exhaust flowing area coefficient δ of port is defined as δ=APORT(V)/(0.22×VMAX), APORTWith m2It indicates, and
And VMAXWith m3It indicates.In the chart of Fig. 3, as ratio increases, the expansion stroke of piston is in right direction.Expansion stroke
Terminate at ratio 1.As ratio reduces, in the left direction of the exhaust stroke of piston in the graph.It is beaten in addition, port has
Velocity coeffficient β is opened, β=(V (δ=1)-V (δ=0.1))/V is defined asMAX.That is, V (δ=1) is represented when δ is equal to 1
When instantaneous cylinder volume V, and V (δ=0.1) represent when δ be equal to 0.1 when cylinder instantaneous volumetric V.Because δ is based on exhaust
Flow area, thus opening speed factor beta represent open cylinder unit specific exhaust apparatus speed have how soon.Opening speed
Factor beta is lower, and the speed that specific exhaust apparatus will expose exhaust flow area is faster.
According to embodiments discussed herein, port area APORTThere can be opening speed factor beta<0.06, to have
Effect ground utilizes the energy of releasing in turbine.
In the chart of Fig. 3, for having specific VMAXCylinder unit exhaust apparatus opening speed factor beta by
Correlation curve Figure 50 extends through the corresponding line for representing the point 56,60 of V (δ=1) and representing the point 64,66 of V (δ=0.1) on 54
Item represents.Therefore, opening speed factor beta 1 proposes the exhaust for including the standard cams axis control represented by the first curve graph 50
For the exhaust apparatus of lift valve, β 1=0.09.For the exhaust apparatus represented by the second curve graph 54, β 2=0.025.Cause
This, the exhaust apparatus represented by the second curve graph 54 meets the requirements β<0.06.
It is not covered by piston in port in curve graph 54 in conjunction with the vent sequence of embodiments described herein being previously mentioned
In the case of start, reach BDC to the right in the graph then along curve graph 54, then along curve graph direction to the left in the graph
TDC, while valve gear is opened.The beginning of vent sequence is only represented in the graph.Ratio less than 0.80 is not shown in the graph.
Due to the relatively large exhaust flow area A of portPORTWith the quick opening speed of port, therefore second at ratio 1 is bent
Line chart 54 extends to the outside of chart.Therefore, for the exhaust apparatus represented by the second curve graph 54, and for by first
It is compared for the prior art exhaust apparatus that curve graph 50 represents, the shorter part in vent sequence is shown in the graph.
For specific turbine, turbine platform experiment result is plotted in turbine figure.Based on this turbine
Machine figure can be that specific quartastroke engine selects suitable turbine.In a type of turbine figure, it can be directed to
Multiple turbine speed lines are drawn in corrected flowing and pressure ratio on turbine.This turbine trip speed line can indicate example
Such as the turbine speeds RPM of so-called reductionRED.Corrected flow can be by the mass flow m ' of such as reductionREDIt indicates.
m’RED=m ' × (T) 1/2/P,
Wherein m ' is the actual mass flow by turbine, T be turbine before delivery temperature, and before P is turbine
Pressure at expulsion.The illustrative examples of the turbine figure of turbocharger are shown in FIG. 4.Standard SAEJ1826 and
SAEJ922 is related to test program, nomenclature and the term of turbocharger, and is incorporated herein by reference with acquisition and turbine
The further details of booster relevant turbine figure and parameter.
According to embodiment, turbine, which has, is defined as γ=ATURB/VMAXStandardization effective flowing area γ.Cause
This, turbine inlet area ATINIt can be relative to the maximum volume V of cylinder unitMAXTo define.That is,
ATURB=(ATIN/ATOT)×m’RED× (R/ (κ (2/ (κ+1) X))) 1/2,
Wherein X=(κ+1)/(κ -1).As mentioned above, ATINIt is attached to the turbine of the exhaust apparatus of cylinder unit
Inlet area.Turbine may have more than one inlet area.Therefore, ATOTIt is the main entrance area of turbine, i.e. ATIN
With any additional turbine inlet area ATINXDeng (ATOT=ATIN+ATINX+...).R is specific gas constant.The example value of R
Can be 287.κ=CP/CV, wherein CPIt is the specific heat capacity being vented under a constant, and CVIt is vented under constant volume
Specific heat capacity.When temperature is 293K, the example value of κ can be 1.4.
ATURBIt is under the 2.5-3.5 pressure ratios between the entrance side and outlet side of turbine and in turbine
In the turbine mass flow m ' of reduction under the tip speed of 450m/sREDLower acquisition.A for specific turbineTURBIt can be with
Such as by from the relative turbine for the corresponding turbine speed of tip speed related under related pressure ratio
The quality stream flow m ' of reduction is extracted in figureRED, and utilize the correlation data calculation A for turbine and its service conditionTURB
To obtain.Later, γ can be calculated.According to embodiments described herein, γ>0.22m-1。
As discussed above, exhaust apparatus is configured to be in the lower dead center between expansion stroke and exhaust stroke when piston
By port area A when BDCPORTExpose as at least 0.44 × VMAXSize.With standardized effective flowing area γ>
0.22m-1Turbine in, when piston is in lower dead center BDC between expansion stroke and exhaust stroke, turbine inlet area
ATINIt can correspond to port area A as defined abovePORT(APORT≥0.44×VMAX).In other words, in the expansion stroke of piston
Exhaust flowing area coefficient at lower dead center BDC between exhaust stroke is δ >=2.Therefore, in conjunction with defined VEXH≤0.5
×VMAX, the energy that may be implemented to release is from exhaust apparatus to turbine inlet area ATINEffective transmission.Therefore, as exhaust is from vapour
Cylinder assembly is transmitted to turbine, can provide low pressure drop, and as exhaust expands on the turbine of turbine, energy of releasing can
To be converted into useful work.Moreover, discussed above have opening speed factor beta<The quick opening of 0.06 discharge valve apparatus
Potentially contribute to the low pressure drop from cylinder unit to turbine.
Fig. 5 shows the first example embodiment of quartastroke engine 2 and the second example reality of quartastroke engine 2
Apply mode, and the embodiment of the vehicle 1 including quartastroke engine 2.
Using solid line, the first exemplary implementation of the quartastroke engine 2 including three cylinder units 4 is shown in Fig. 5
Mode.Each cylinder unit 4 includes the exhaust apparatus with port 15, wherein individual discharge duct 6 is only by each port 15
With the individual inlet area A of turbine 21TINIt fluidly connects.Each cylinder unit 4 is the vapour as discussed in conjunction with Fig. 1 a and 1b
Cylinder assembly 4.
Discussed in the above and definition opening speed factor beta and standardized effective flowing area γ are filled suitable for cylinder
Set at least one of 4.According to embodiment, each cylinder unit 4 has opening speed factor beta as herein defined<
0.06.According to some embodiments, discussed in the above and definition opening speed factor beta and standardized effective flowing area γ
Each suitable for cylinder unit 4 and turbine 21 connected to it.
According to embodiment, each in three cylinder units 4 may be disposed to about 240 degree of crankshaft angles compartment
Dot interlace fire.
According to the second illustrative embodiments being shown in FIG. 5, quartastroke engine 2 includes six cylinder units 4,
4’.These embodiments include three cylinder units 4 of aforementioned embodiments and three cylinder units 4 ' being represented by dashed line.
Equally, each cylinder unit 4,4 ' includes the exhaust apparatus with port 15,15 ', wherein individual discharge duct 6,6 ' only will
Each individual inlet area A of one in port 15,15 ' and turbine 21,21 'TINIt fluidly connects.In these embodiment party
In formula, internal combustion engine includes two turbines 21,21 '.Three individual discharge ducts 6 are connected to the first turbine 21, and three
A individual discharge duct 6 ' is connected to the second turbine 21 '.Equally, each cylinder unit 4,4 ' is as combined Fig. 1 a and 1b institutes
The cylinder unit 4,4 ' of discussion.Discussed in the above and definition opening speed factor beta and standardized effective flowing area γ are suitable
For cylinder unit 4, at least one of 4 '.According to some embodiments, discussed in the above and definition opening speed factor beta
It is suitable for each in cylinder unit 4,4 ' and turbine 21,21 ' connected to it with standardized effective flowing area γ.
According to embodiment, three cylinder units 4,4 ' in six cylinder units 4,4 ' can be arranged to about 240 degree
Crankcase angular separation interval igniting.
According to other embodiment, quartastroke engine may include the cylinder unit 4 of different number, such as two,
Four, five or eight cylinder units 4.
Vehicle 1 is schematically shown in Figure 5.Vehicle 1 includes showing according to the first illustrative embodiments or according in Fig. 5
The quartastroke engine 2 of the second illustrative embodiments gone out.
The present invention should not be construed as limited to embodiment set forth herein.It would be recognized by those skilled in the art that not
In the case of being detached from the scope of the present invention being defined by the following claims, the difference of embodiments disclosed herein can be combined
Feature creates the embodiment other than embodiment described here.Although being described by reference to illustrative embodiments
The present invention, but to those skilled in the art, many different changes, modification etc. will become obvious.For example,
In the embodiment discussed in conjunction with Fig. 1-5, at least one turbine in turbocharger form has been discussed.It substitutes
Ground, turbine can be attached to the turbine of the bent axle of internal combustion engine, or be connected to the turbine of generator.Therefore, it should manage
Solution, foregoing teachings are the explanations to various illustrative embodiments, and the invention is solely defined by the appended claims.
As it is used herein, term " include " or " contain " is open, and include one or more statements
Feature, element, step, component or function, but do not preclude the presence or addition of other one or more features, step, component, function
Or combinations thereof.
Claims (14)
1. a kind of quartastroke engine (2), including at least one cylinder unit (4) and bent axle (20) of combustion chamber (23) are formed,
Wherein
At least one cylinder unit (4) include piston (10), connecting rod (22), casing bore (12) and for make exhaust from
The exhaust apparatus (14) of casing bore (12) outflow, wherein
The piston (10) is pivotably connected at the first end of the connecting rod (22) described to connecting rod (22) and to be arranged to
It is moved back and forth in casing bore (12) in induction stroke, compression stroke, expansion stroke and exhaust stroke, wherein
The exhaust apparatus (14) includes the port (15) being arranged in the lower half portion of the casing bore (12), wherein
The quartastroke engine (2) further includes at least one turbine (21), and the turbine includes turbine (26) and has
There is turbine inlet area ATIN, and wherein,
Discharge duct (6) extends to the turbine inlet area A from the port (15)TIN
It is characterized in that：
The piston (10) has different piston stroke lengths, air inlet punching described in the expansion stroke and exhaust stroke ratio
Journey and the compression stroke are longer so that the port (15) during the part of the expansion stroke and the exhaust stroke not
It is covered by the piston (10), and is covered by piston (10) during the induction stroke and the compression stroke.
2. quartastroke engine (2) according to any one of the preceding claims, wherein when the piston (10) is located at institute
When stating the lower dead center BDC between expansion stroke and the exhaust stroke, the port area A of the port (15)PORTWith at least
The turbine inlet area A of twice turbine (21)TINSize.
3. quartastroke engine (2) according to claim 2, wherein the height of the port (15) is in the piston
(10) the piston punching between top dead centre TDC and the lower dead center BDC between the expansion stroke and the exhaust stroke
In the range of the 8%-16% of Cheng Changdu.
4. quartastroke engine (2) according to claim 2 or 3, wherein at least one cylinder unit (4) has
The top of the lower dead center BDC and the combustion chamber (23) of the piston (10) between the expansion stroke and the exhaust
Maximum volume V between inside defining surface (24)MAX, wherein the port (15) are configured to be in institute when the piston (10)
By the port area A when stating the lower dead center BDC between expansion stroke and the exhaust strokePORTExpose as at least 0.44 ×
VMAXSize.
5. quartastroke engine (2) according to any one of the preceding claims, wherein the cylinder unit (4) has
The top of the lower dead center BDC and the casing bore (12) of the piston (10) between the expansion stroke and the exhaust
Maximum volume V between the defining surface of insideMAX, wherein the instantaneous cylinder volume V of the cylinder unit (4) is by the piston
(10) the instantaneous position definition during its reciprocating motion in the casing bore (12), wherein
APORT(V) port area for indicating the port (15) during the expansion stroke of the piston (10), is the wink
When cylinder volume V function, wherein
The exhaust flowing area coefficient δ of the port (15) is defined as
δ=APORT(V)/(0.22×VMAX), APORTWith m2It indicates, and VMAXWith m3It indicates, wherein
The port (15) has opening speed factor beta, is defined as
β=(V (δ=1)-V (δ=0.1))/VMAX, and wherein
The opening speed factor beta of the port (15)<0.06.
6. quartastroke engine (2) according to any one of the preceding claims, wherein the cylinder unit (4) has
The top of lower dead center BDC and the casing bore (12) of the piston (10) between the expansion stroke and the exhaust stroke
Maximum volume V between inside defining surface (24)MAX, wherein the discharge duct (6) has discharge duct volume VEXH, and
Wherein VEXHThe maximum volume V is multiplied by less than or equal to 0.5MAX。
7. quartastroke engine (2) according to any one of the preceding claims, wherein the discharge duct (6) is only by institute
State port (15) and the turbine inlet area ATINIt fluidly connects.
8. quartastroke engine (2) according to any one of the preceding claims, wherein the port (15) are only by fixing
Component is formed.
9. quartastroke engine (2) according to any one of claim 1 to 7, including be configured to for changing the end
The movable cylinder wall part (31) of the size of mouth (15), wherein the movable cylinder wall part (31) can be in first position
It is moved between the second position, the displaceable wall part (31) forms one of the port (15) at the first position
Point, the displaceable wall part (31) is removed in the second position from the port (15).
10. quartastroke engine (2) according to any one of the preceding claims, wherein the exhaust apparatus (14) includes
Valve gear (17) at upper inner defining surface in the casing bore (12), the valve are arranged (17) and are extended to described
The exhaust line (19) in turbine (21) downstream fluidly connects.
11. quartastroke engine (2) according to claim 10, wherein the valve gear (17) can selectively with institute
The discharge duct (6) for stating turbine (21) upstream fluidly connects.
12. quartastroke engine (2) according to any one of the preceding claims, wherein the turbine (21) has mark
Standardization effective flowing area γ, is defined as
γ=ATURB/VMAX, wherein γ>0.22m-1, wherein
ATURB=(ATIN/ATOT)×m’RED×(R/(κ(2/(κ+1)X)))1/2, wherein X=(κ+1)/(κ -1), wherein ATOTIt is institute
State the main entrance area of turbine (21), and wherein ATURBIt is between the entrance side and outlet side of the turbine (21)
In the turbine in the case that pressure ratio is 2.5-3.5 and in the case where the tip speed of the turbine is 450m/s
(21) the mass flow m ' of reductionREDLower acquisition.
13. quartastroke engine (2) according to any one of the preceding claims, wherein the cylinder unit (4) has
The top dead centre of the lower dead center BDC and the piston (10) in the casing bore (12) between expansion stroke and exhaust stroke
Total scavenging volume V between TDCS, and wherein 0.3<VS<4 liters.
14. a kind of vehicle (1) comprising quartastroke engine (2) according to any one of the preceding claims.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE1551416A SE539658C2 (en) | 2015-11-03 | 2015-11-03 | Four Stroke Internal Combustion Engine |
| SE1551416-9 | 2015-11-03 | ||
| PCT/SE2016/051070 WO2017078597A1 (en) | 2015-11-03 | 2016-11-01 | Four stroke internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108368773A true CN108368773A (en) | 2018-08-03 |
Family
ID=58662959
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680070913.8A Pending CN108368773A (en) | 2015-11-03 | 2016-11-01 | Quartastroke engine |
Country Status (4)
| Country | Link |
|---|---|
| CN (1) | CN108368773A (en) |
| DE (1) | DE112016004553T5 (en) |
| SE (1) | SE539658C2 (en) |
| WO (1) | WO2017078597A1 (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1592133A (en) * | 1977-03-07 | 1981-07-01 | Semt | Control of effective compression ratio of internal combustion engines |
| GB2138075B (en) * | 1983-04-12 | 1987-12-31 | Specialty Systems Inc | Driving a turbine by ic engine exhaust gases |
| US5775105A (en) * | 1997-03-27 | 1998-07-07 | Zinsmeyer; Herbert G. | Combination nozzle and valve with variable geometry for increased power recovery from internal combustion engine exhaust gas |
| JP2010255506A (en) * | 2009-04-24 | 2010-11-11 | Toyota Motor Corp | Four-cycle reciprocating piston engine |
| CN102777257A (en) * | 2011-05-12 | 2012-11-14 | 福特环球技术公司 | Turbocharged engine with separate exhaust manifolds and method for operating such an engine |
| US20120306207A1 (en) * | 2010-02-03 | 2012-12-06 | Hotchkiss Super Deltic Ltd. | Reciprocating internal combustion engine with two-stage exhaust system |
| CN202970888U (en) * | 2011-01-28 | 2013-06-05 | 艾克莫特国际公司 | Internal combustion engine and internal combustion engine system |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US367496A (en) | 1887-08-02 | atkinson | ||
| GB589094A (en) * | 1945-02-09 | 1947-06-11 | Hsin Ya Tien | Improvements in or relating to resilient driving gear for four-stroke internal combustion engines |
| US4517931A (en) | 1983-06-30 | 1985-05-21 | Nelson Carl D | Variable stroke engine |
-
2015
- 2015-11-03 SE SE1551416A patent/SE539658C2/en unknown
-
2016
- 2016-11-01 DE DE112016004553.0T patent/DE112016004553T5/en active Pending
- 2016-11-01 WO PCT/SE2016/051070 patent/WO2017078597A1/en active Application Filing
- 2016-11-01 CN CN201680070913.8A patent/CN108368773A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1592133A (en) * | 1977-03-07 | 1981-07-01 | Semt | Control of effective compression ratio of internal combustion engines |
| GB2138075B (en) * | 1983-04-12 | 1987-12-31 | Specialty Systems Inc | Driving a turbine by ic engine exhaust gases |
| US5775105A (en) * | 1997-03-27 | 1998-07-07 | Zinsmeyer; Herbert G. | Combination nozzle and valve with variable geometry for increased power recovery from internal combustion engine exhaust gas |
| JP2010255506A (en) * | 2009-04-24 | 2010-11-11 | Toyota Motor Corp | Four-cycle reciprocating piston engine |
| US20120306207A1 (en) * | 2010-02-03 | 2012-12-06 | Hotchkiss Super Deltic Ltd. | Reciprocating internal combustion engine with two-stage exhaust system |
| CN202970888U (en) * | 2011-01-28 | 2013-06-05 | 艾克莫特国际公司 | Internal combustion engine and internal combustion engine system |
| CN102777257A (en) * | 2011-05-12 | 2012-11-14 | 福特环球技术公司 | Turbocharged engine with separate exhaust manifolds and method for operating such an engine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2017078597A1 (en) | 2017-05-11 |
| SE539658C2 (en) | 2017-10-24 |
| SE1551416A1 (en) | 2017-05-04 |
| DE112016004553T5 (en) | 2018-06-21 |
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