CN113047965A - Method for determining working compression ratio of reciprocating internal combustion engine - Google Patents
Method for determining working compression ratio of reciprocating internal combustion engine Download PDFInfo
- Publication number
- CN113047965A CN113047965A CN202110361040.9A CN202110361040A CN113047965A CN 113047965 A CN113047965 A CN 113047965A CN 202110361040 A CN202110361040 A CN 202110361040A CN 113047965 A CN113047965 A CN 113047965A
- Authority
- CN
- China
- Prior art keywords
- compression ratio
- cycle
- working
- temperature
- internal combustion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The invention relates to the technical field of internal combustion engines, in particular to a method for determining the working compression ratio of a reciprocating internal combustion engine, which comprises the following steps: determining the working temperature limit of the gas power cycle; determining a target compression ratio according to the working temperature limit, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine; the target compression ratio is the compression ratio corresponding to the maximum circulation specific work or the maximum circulation average effective pressure of the gas power cycle. The invention provides a method for determining the working compression ratio of a reciprocating internal combustion engine, which solves the problem that the working compression ratio of the existing internal combustion engine can be determined only by depending on experience.
Description
Technical Field
The invention relates to the technical field of internal combustion engines, in particular to a method for determining the working compression ratio of a reciprocating internal combustion engine.
Background
Reciprocating internal combustion engines for mobile tool applications, such as otto engines (reciprocating internal combustion engines with an otto cycle as the theoretical cycle), have a long history. Taking an Otto internal combustion engine as an example, the ideal working cycle is the Otto cycle (Otto cycle), which belongs to one of a plurality of gas power cycles. In the aspect of analyzing the thermodynamic performance of the gas power cycle performance, the working processes, cycle performance indexes (such as thermal efficiency and the like) and cycle performance analysis methods of an ideal gasoline engine cycle (Otto cycle or Otto cycle), Diesel engine Diesel cycle (Diesel cycle or Diesel cycle), Diesel engine hybrid heating cycle (Sabathe cycle, sabader cycle) and gas turbine unit cycle (Brayton cycle or Brayton cycle) indicate the change rule of the thermal efficiency along with related parameters. However, the above analysis method cannot determine the cycle optimum operating state; in application, it is not reasonable to design the gas power cycle device according to the high efficiency index. The compression ratio of modern Otto cycle internal combustion engines (gasoline engines) is generally 9-12, (the compression ratio of diesel engines is generally 17-22), and the determination of the value is also empirical and theoretically not an optimal value under the condition of allowable cycle working temperature, so that the comprehensive economy (comprehensive efficiency) in the using process does not reach the optimal value. The theoretical efficiency of an ideal otto-cycle engine is determined entirely by the compression ratio, and the higher the compression ratio, the higher the efficiency, which theoretically approaches the thermodynamic limit efficiency, the carnot cycle efficiency, at a given operating temperature limit (lowest and highest cycle temperature), and at this time the net work output of the engine per cycle will tend to zero. That is, the evaluation index of the otto cycle internal combustion engine aimed at the efficiency is not reasonable, and it is impossible to guide the actual work.
In summary, the design of reciprocating internal combustion engines such as otto cycle engines is not reasonable in terms of efficiency, and it is not possible to design a high performance engine. Because, by means of technological progress, when the actual engine works close to the theoretical limit under the given conditions, high efficiency can be achieved, and the output work of the internal combustion engine is very small, in order to achieve the given power output, the internal combustion engine is greatly enlarged, which results in much increased self-weight, which is equivalent to a large self-load of the internal combustion engine for the purpose of moving tools, and the actual use efficiency of the internal combustion engine is obviously reduced.
Disclosure of Invention
The invention provides a method for determining the working compression ratio of a reciprocating internal combustion engine, which aims to solve the problem that the working compression ratio of the conventional internal combustion engine can be determined only by depending on experience.
The technical scheme for solving the problems is as follows: a method for determining the operating compression ratio of a reciprocating internal combustion engine comprising the steps of:
s1: determining the working temperature limit of the gas power cycle;
s2: determining a target compression ratio according to the working temperature limit, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine;
and the target compression ratio is the compression ratio corresponding to the gas power cycle when the cycle specific work is maximum or when the cycle average effective pressure is maximum.
Preferably, when the target compression ratio in S2 is the compression ratio corresponding to the time when the cycle specific work is maximum, S2 specifically includes:
and calculating a target compression ratio by using an expression of the derivative cycle specific work according to the working temperature limit, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine.
Preferably, when the target compression ratio in S2 is the compression ratio corresponding to the maximum cycle average effective pressure, S2 specifically includes:
obtaining an expression of a compression ratio by utilizing an expression of the average effective pressure of the derivative cycle according to the working temperature limit; and solving the expression of the compression ratio to obtain a target compression ratio, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine.
Preferably, the gas power cycle is an otto cycle, and when the target compression ratio in S2 is a compression ratio corresponding to the maximum cycle specific work, the calculation formula of the target compression ratio is:
wherein, the
Is the cycle temperature ratio, T1For compressing the temperature, T, of the starting working medium3The highest temperature of the working medium after heat absorption, and kappa is the specific heat ratio of the working medium.
Preferably, the aerodynamic cycle is an otto cycle, and when the target compression ratio in S2 is a compression ratio corresponding to the maximum cycle average effective pressure, the expression of the target compression ratio is:
(τ+1)+(2κ-2)εκ-1(ε-1)＝(εκ-1+τε1-κ)[(κ-1)(ε-1)+1]
wherein, the
Is the cycle temperature ratio, T1For compressing the temperature, T, of the starting working medium3The highest temperature of the working medium after heat absorption, and kappa is the specific heat ratio of the working medium.
Preferably, the solving formula of the target compression ratio is solved by a trial algorithm.
Preferably, the temperature of the working medium at the compression starting point and the highest temperature of the working medium after heat absorption are working temperature limits of an Otto cycle.
Compared with the prior art, the invention has the beneficial effects that: compared with the internal combustion engine which is selected according to experience, the internal combustion engine which is more economical and reasonable and has high efficiency can be designed by using the working compression ratio of the invention as the design index of the internal combustion engine; the working compression ratio obtained by the invention can lead the internal combustion engine device to be miniaturized and improve the thermal efficiency when the internal combustion engine device outputs the same power; it is also possible to output more work at the same volume (or weight).
Drawings
FIG. 1 is a pressure-volume diagram of an ideal Otto cycle;
FIG. 2 is a temperature entropy diagram of an ideal Otto cycle;
FIG. 3 shows the same T1And T3Temperature entropy diagram of Otto cycle with different compression ratios;
fig. 4 is a flowchart illustrating the method for determining the operating compression ratio according to the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention.
A method for determining the operating compression ratio of a reciprocating internal combustion engine, as shown in fig. 4, comprising the steps of:
step 1: the operating temperature limit of the gas power cycle is selected based on the operating conditions of fuel properties, piston-cylinder material properties, etc., and includes, but is not limited to, Otto cycle (Otto cycle), Atkinson cycle (Atkinson cycle), Miller-Otto cycle (Miller-Otto cycle), Dual or sabatier cycle (hybrid heating cycle or sabadir cycle), Diesel cycle (Diesel cycle), Miller-Dual cycle (Miller-hybrid heating cycle or Miller-sabadir cycle), and Miller-Diesel cycle (Miller-Diesel cycle).
S2: determining a target compression ratio according to the working temperature limit, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine;
the target compression ratio is the compression ratio corresponding to the maximum circulation specific work or the maximum circulation average effective pressure of the gas power cycle.
As a preferred embodiment of the present invention, when the target compression ratio in S2 is the compression ratio corresponding to the time when the cycle specific work is maximum, S2 specifically includes:
and calculating by using an expression of the derivative cycle specific work according to the working temperature limit to obtain a target compression ratio, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine.
As a preferred embodiment of the present invention, when the target compression ratio in S2 is the compression ratio corresponding to the maximum cycle average effective pressure, S2 specifically includes:
obtaining an expression of a compression ratio by utilizing an expression of the average effective pressure of the derivative cycle according to the working temperature limit; and solving the expression of the compression ratio to obtain a target compression ratio, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine.
As a preferred embodiment of the present invention, the gas power cycle is an otto cycle, and when the target compression ratio in S2 is a compression ratio corresponding to the maximum cycle specific work, the calculation formula of the operating compression ratio of the reciprocating internal combustion engine is:
wherein, is
Is the cycle temperature ratio, T1For compressing the temperature, T, of the starting working medium3The highest temperature of the working medium after heat absorption, and kappa is the specific heat ratio of the working medium.
As a preferred embodiment of the present invention, the gas power cycle is an otto cycle, and when the target compression ratio in S2 is a compression ratio corresponding to when the cycle average effective pressure is maximum, the expression of the compression ratio is:
(τ+1)+(2κ-2)εκ-1(ε-1)＝(εκ-1+τε1-κ)[(κ-1)(ε-1)+1]
wherein, is
Is the cycle temperature ratio, T1For compressing the temperature, T, of the starting working medium3The highest temperature of the working medium after heat absorption, and kappa is the specific heat ratio of the working medium.
As a preferred embodiment of the invention, the solving formula of the work compression is solved by adopting a trial algorithm.
As a preferred embodiment of the invention, the temperature of the working medium at the starting point of compression and the highest temperature of the working medium after heat absorption are working temperature limits.
Example 1: the method for determining the working compression ratio of the Otto cycle internal combustion engine comprises the following steps:
1.1 determining the temperature of the working medium at the compression start point of the Otto cycle and the maximum temperature of the working medium after heat absorption
The thermal efficiency of an ideal otto cycle is expressed as:
wherein kappa is the specific heat ratio of the working medium,
for the cyclic compression ratio, the respective temperatures are kelvin temperatures.
The temperature at each state point in the otto cycle is expressed as:
T3＝T1τ (3)
as can be seen from formula (1): increasing the compression ratio can increase the theoretical thermal efficiency of the otto cycle. As can be seen from fig. 1 and 2, when the temperatures at 1 and 3 points (lowest and highest operating temperature of the cycle) are determined, when the compression ratio is high enough, the temperature at 2 points (i.e. at the end of compression) will approach 3 points, the temperature at 4 points (i.e. at the end of expansion) will approach 1 point, the cycle will approach the carnot cycle, and the efficiency of the gasoline engine will approach the efficiency of the carnot cycle. As can be seen from the equations (2), (3) and (4), the temperature (i.e. T) is determined when the states are 1 and 3 points (cycle lowest and highest working temperature)1And T3Known), only the temperature of 2 out of the temperatures of the remaining two state points (2 points and 4 points) of the otto cycle is changed (when the temperature of 2 points is determined, the temperature of 4 points is also determined), and 2The point temperature depends on the temperature of 1 point and the compression ratio. That is, from point 1, after the compression ratio is determined, the otto cycle is also determined.
1.2 calculating to obtain the optimal working compression ratio according to the temperature of the working medium at the compression starting point and the highest temperature of the working medium after heat absorption based on a derivation formula
When operating temperature limit of Otto cycle (i.e. maximum T of cycle)3Minimum temperature T1) When determined, there is an optimum compression ratio epsilon with the largest cyclic workopt. As shown in fig. 3, at T1And T3Temperature entropy (T-s) plot of three cycles with different compression ratios. The compression ratio of the compression process of the cycle 1 → 2' → 3' → 4' → 1 is very small, so that the cycle is not only low in heat efficiency, but also very small in cycle specific work (the work done by 1kg of working medium to complete one cycle, namely the area enclosed by the process line); the compression ratio of the cycle 1 → 2"→ 3" → 4"→ 1 is large, the thermal efficiency is high (the limit is the efficiency of the same temperature limit intercarty carnot cycle), but the cyclic specific work is small (the limit is the net work done, or the cyclic specific work is zero); the compression ratio of cycle 1 → 2 → 3 → 4 → 1 is centered, the thermal efficiency is centered, but the duty ratio is relatively large. That is, it is inevitably at T according to the change of the compression ratio1And T3There is a maximum cyclic specific work, and there is also a maximum cyclic average effective pressure. The circulation ratio work is large, namely the work done by 1kg of working medium is large; the average effective pressure is large, i.e. the power density (or power per liter) is large.
1.2.1 when selecting the compression ratio corresponding to the time when the specific work of the cycle is maximum as the optimum operating compression ratio
The expression for the specific work of the otto cycle is:
wnet＝q1-q2＝cV(T3-T2)-cV(T4-T1)＝cV(T3-T2-T4+T1) (5)
in the expression of the cyclic specific work, only T2Is variable with compression ratio, so the expression for the cyclic work is derived,
equations (6) and (7) show that the variation with compression ratio (i.e., T)2Change of (d) the cyclic ratio does have a maximum value. From the formula (6), it can be obtained
The expression of the compression ratio corresponding to the maximum cyclic work in equations (2) and (8) is:
the expression for the maximum cyclic work at this time is:
1.2.2 when selecting the compression ratio corresponding to when the average effective pressure of the cycle is the maximum as the optimum compression ratio,
the expression for the cyclic average effective pressure is:
in the formula (12), only T2Is varied with compression ratio, so
Or
Derivative the formula (14) and order
Is provided with
(τ+1)+(2κ-2)εκ-1(ε-1)＝(εκ-1+τε1-κ)[(κ-1)(ε-1)+1] (15)
Equation (15) is an implicit function of the compression ratio ε, which is solved (solved using a trial algorithm) as
Substituting the formula (14) to obtain the maximum circulating average effective pressure; and (5) substituting the temperature of the state points 2 and 4 into the formulas (2) and (4), and obtaining the corresponding circulation specific work when the maximum circulation average effective pressure is obtained.
Because of the power per liter
I.e. the maximum cyclic average effective pressure regime corresponds to the maximum power-up regime. In the formula, PLThe power is increased for the engine, kW/L; m is the working mass in the cylinder, kg; vhIs the engine displacement, m3(ii) a n is the engine speed, rpm; n ' is the number of revolutions the engine completes a cycle (four-stroke engines have n ' 2 revolutions/cycle; two-stroke engines have n ' 1 revolution/cycle).
In practical application, the engine can be used in
And
one compression ratio is selected as the Otto cycleDesign criteria for a ring engine.
The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all equivalent structures or equivalent flow transformations made by using the contents of the specification and the drawings, or applied directly or indirectly to other related systems, are included in the scope of the present invention.
Claims (7)
1. A method for determining the operating compression ratio of a reciprocating internal combustion engine, comprising the steps of:
s1: determining the working temperature limit of the gas power cycle;
s2: determining a target compression ratio according to the working temperature limit, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine;
and the target compression ratio is the compression ratio corresponding to the gas power cycle when the cycle specific work is maximum or when the cycle average effective pressure is maximum.
2. The method of claim 1, wherein when the target compression ratio at S2 is the compression ratio corresponding to the maximum work of cycle ratio, S2 specifically comprises:
and calculating a target compression ratio by using an expression of the derivative cycle specific work according to the working temperature limit, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine.
3. The method of claim 1, wherein when the target compression ratio in S2 is the compression ratio corresponding to the maximum average effective pressure of the cycle, S2 specifically comprises:
obtaining an expression of a compression ratio by utilizing an expression of the average effective pressure of the derivative cycle according to the working temperature limit; and solving the expression of the compression ratio to obtain a target compression ratio, and taking the target compression ratio as the working compression ratio of the reciprocating internal combustion engine.
4. The method of claim 2, wherein the gas power cycle is an otto cycle, and when the target compression ratio at S2 is the compression ratio corresponding to the maximum work of the cycle, the target compression ratio is calculated by the formula:
wherein, the
Is the cycle temperature ratio, T1For compressing the temperature, T, of the starting working medium3The highest temperature of the working medium after heat absorption, and kappa is the specific heat ratio of the working medium.
5. The method of claim 3 wherein the gas power cycle is an Otto cycle and when the target compression ratio at S2 is the compression ratio corresponding to the maximum average effective pressure of the cycle, the target compression ratio is expressed as:
(τ+1)+(2κ-2)εκ-1(ε-1)＝(εκ-1+τε1-κ)[(κ-1)(ε-1)+1]
wherein, the
Is the cycle temperature ratio, T1For compressing the temperature, T, of the starting working medium3The highest temperature of the working medium after heat absorption, and kappa is the specific heat ratio of the working medium.
6. The method of claim 5, wherein said target compression ratio is solved using a trial algorithm.
7. A method for determining the operating compression ratio of a reciprocating internal combustion engine as claimed in any one of claims 4 to 6, wherein the temperature of the working fluid at the start of compression and the maximum temperature of the working fluid after heat absorption are the operating temperature limits of the Otto cycle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110361040.9A CN113047965B (en) | 2021-04-02 | 2021-04-02 | Method for determining working compression ratio of reciprocating internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110361040.9A CN113047965B (en) | 2021-04-02 | 2021-04-02 | Method for determining working compression ratio of reciprocating internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113047965A true CN113047965A (en) | 2021-06-29 |
| CN113047965B CN113047965B (en) | 2022-05-03 |
Family
ID=76517208
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110361040.9A Active CN113047965B (en) | 2021-04-02 | 2021-04-02 | Method for determining working compression ratio of reciprocating internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113047965B (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4133172A (en) * | 1977-08-03 | 1979-01-09 | General Motors Corporation | Modified Ericsson cycle engine |
| CN101560897A (en) * | 2009-05-26 | 2009-10-21 | 广东大华仁盛科技有限公司 | New loop optimization method of non-supercharged high-efficiency energy-saving internal-combustion engine |
| CN101765706A (en) * | 2007-05-29 | 2010-06-30 | Ab引擎有限公司 | High efficiency internal combustion engine |
| CN102777269A (en) * | 2011-05-10 | 2012-11-14 | 通用汽车环球科技运作有限责任公司 | Compression ratio determination and control systems and methods |
| US20130255641A1 (en) * | 2012-04-02 | 2013-10-03 | Pao Chi Pien | Reciprocating internal combustion engine |
| CN103975154A (en) * | 2012-01-20 | 2014-08-06 | 三菱重工业株式会社 | Combustion control device and control method for internal combustion engine |
| WO2014185124A1 (en) * | 2013-05-14 | 2014-11-20 | 日産自動車株式会社 | Internal combustion engine control device and control method |
| US20140345572A1 (en) * | 2012-04-02 | 2014-11-27 | Pao Chi Pien | Reciprocating internal combustion engine |
| CN106988943A (en) * | 2017-05-05 | 2017-07-28 | 刘峰 | A kind of high-pressure co-rail diesel machine and its design method |
-
2021
- 2021-04-02 CN CN202110361040.9A patent/CN113047965B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4133172A (en) * | 1977-08-03 | 1979-01-09 | General Motors Corporation | Modified Ericsson cycle engine |
| CN101765706A (en) * | 2007-05-29 | 2010-06-30 | Ab引擎有限公司 | High efficiency internal combustion engine |
| CN101560897A (en) * | 2009-05-26 | 2009-10-21 | 广东大华仁盛科技有限公司 | New loop optimization method of non-supercharged high-efficiency energy-saving internal-combustion engine |
| CN102777269A (en) * | 2011-05-10 | 2012-11-14 | 通用汽车环球科技运作有限责任公司 | Compression ratio determination and control systems and methods |
| CN103975154A (en) * | 2012-01-20 | 2014-08-06 | 三菱重工业株式会社 | Combustion control device and control method for internal combustion engine |
| US20130255641A1 (en) * | 2012-04-02 | 2013-10-03 | Pao Chi Pien | Reciprocating internal combustion engine |
| US20140345572A1 (en) * | 2012-04-02 | 2014-11-27 | Pao Chi Pien | Reciprocating internal combustion engine |
| WO2014185124A1 (en) * | 2013-05-14 | 2014-11-20 | 日産自動車株式会社 | Internal combustion engine control device and control method |
| CN106988943A (en) * | 2017-05-05 | 2017-07-28 | 刘峰 | A kind of high-pressure co-rail diesel machine and its design method |
Non-Patent Citations (1)
| Title |
|---|
| 辛海升、岳海军: "《汽车发动机原理与汽车理论》", 31 March 2017, 国防工业出版社 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113047965B (en) | 2022-05-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US3961607A (en) | Internal combustion engine | |
| US20110094461A1 (en) | Combustion engine having mutually connected pistons | |
| Gonca et al. | Performance analysis and simulation of a diesel-miller cycle (DiMC) engine | |
| CN114510799B (en) | Free piston engine thermal efficiency improving method based on driving process control | |
| Gonca | An optimization study on an eco-friendly engine cycle named as dual-miller cycle (DMC) for marine vehicles | |
| CN113047965B (en) | Method for determining working compression ratio of reciprocating internal combustion engine | |
| Noga et al. | Increase of efficiency of SI engine through the implementation of thermodynamic cycle with additional expansion | |
| Dorić et al. | The realization and analysis of a new thermodynamic cycle for internal combustion engine | |
| CN114357647B (en) | High-heat-efficiency molded line design method for cam-driven engine | |
| Fatehi et al. | Energy and exergy analyses of homogeneous charge compressin ignition (HCCI) engine | |
| CN114510825B (en) | Method and system for obtaining optimal phase difference of opposed piston engine | |
| Dorić et al. | Efficiency characteristics of a new quasi-constant volume combustion spark ignition engine | |
| Wu et al. | Optimization of the power, efficiency and ecological function for an air-standard irreversible Dual-Miller cycle | |
| Ghahfarokhi et al. | Energy and exergy analyses of homogeneous charge compression ignition engine | |
| Arabacı | Thermodynamic analysis of endoreversible six-stroke Otto cycle with respect to equivalence ratio, residual gas fraction and mean piston speed | |
| Cakir | The numerical thermodynamic analysis of otto-miller cycle | |
| Gultekin et al. | A thermodynamic comparison of rhombic-drive and slider–crank mechanisms for a two-stroke SI engine | |
| Alqahtani et al. | Evaluation of the effect of variable compression ratios performance on opposed piston 2-stroke engine | |
| Drabik et al. | Effective compression ratio of combustion engine as a way of increasing efficiency | |
| Sikora et al. | Theoretical analysis of determining the thermal efficiency in engine with Atkinson cycle | |
| CN115234387B (en) | Full-working-condition power and thermal efficiency binary regulation and control method for opposed-piston engine | |
| Zhang et al. | Sensitivity and effect of key operational parameters on performance of a dual-cylinder free-piston engine generator | |
| Yin et al. | Exergy analysis of ideal thermodynamic cycle for the four stroke free piston engine (FPE) | |
| Topgül | Design, Manufacturing, and Thermodynamic Analysis of a Gamma-type Stirling Engine Powered by Solar Energy | |
| Opaliński et al. | The closed-cycle model numerical analysis of the impact of crank mechanism design on engine efficiency |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |