CN101699040B - Two-stage variable compression ratio system of gasoline engine and control method thereof - Google Patents

Two-stage variable compression ratio system of gasoline engine and control method thereof Download PDF

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CN101699040B
CN101699040B CN 200910236564 CN200910236564A CN101699040B CN 101699040 B CN101699040 B CN 101699040B CN 200910236564 CN200910236564 CN 200910236564 CN 200910236564 A CN200910236564 A CN 200910236564A CN 101699040 B CN101699040 B CN 101699040B
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cam
intake
valve
exhaust
engine
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CN 200910236564
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CN101699040A (en )
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王建昕
王志
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清华大学
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Abstract

The invention relates to a two-stage variable compression ratio system of a gasoline engine and a control method thereof. On two overhead camshafts corresponding to an intake valve and an exhaust valve of the engine, a big cam and a small cam, which correspond to the intake valve and the exhaust valve of each cylinder are respectively arranged; an intake valve cam profile switching mechanism is arranged on the intake valve of each cylinder and is used for switching the big cam and the small cam of the intake valve, which correspond to the intake valve; and an exhaust valve cam profile switching mechanism is arranged on the exhaust valve of each cylinder and is used for switching the big cam and the small cam of the exhaust valve, which correspond to the exhaust valve. The system and the method have the advantages of quickly changing the compression ratio, realizing the switching between SI and HCCI combustion modes in an engine cycle, obtaining low oil consumption by adopting a high compression ratio when the engine has a medium or low load, and obtaining a high-power density by adopting a low compression ratio to avoid detonation when the engine has a high load.

Description

汽油机两级可变压缩比系统及其控制方法 Two gasoline engine variable compression ratio system and control method

技术领域 FIELD

[0001] 本发明涉及内燃机技术领域,特别涉及采用HCCI/SI混合燃烧模式的汽油机,即中小负荷下采用高压缩比的均质混合气压缩着火燃烧(HCCI)模式实现高效低污染,大负荷时采用低压缩比的火花点火(SI)燃烧模式,获得高的功率密度且不发生爆震。 [0001] The present invention relates to the field when the internal combustion engine, and more particularly to gasoline using HCCI / SI mixed combustion mode, i.e., the use of small high load compression ratio of homogeneous mixtures of compression ignition combustion (HCCI) mode to achieve high efficiency and low pollution, high load low compression ratio spark-ignition (SI) combustion mode, a high power density is obtained without occurrence of knocking.

背景技术 Background technique

[0002] 汽油机中小负荷油耗高,比柴油机高出20%〜30%;而在大负荷时容易爆震,限制了功率输出。 [0002] High load small gasoline consumption, 20% ~ 30% higher than the diesel engine; and when a large load easily knock limit power output. 为了解决汽油机中小负荷油耗差的问题,需要提高压缩比;而要解决汽油机大负荷容易爆震的问题,需要降低压缩比。 In order to solve the small gasoline engine load problem of poor fuel economy, the need to improve the compression ratio; gasoline engine and to solve the problem of a large load easily knocking, the compression ratio needs to be reduced. 因此,最理想的方法是压缩比可变,这能使汽油机的油耗和功率输出大幅度改善,而且可以降低噪声与振动。 Thus, the best way is a variable compression ratio, which enables the fuel consumption and power output of the gasoline engine greatly improved, and noise and vibration can be reduced.

[0003] Saab汽车公司2002年利用其开发的VCR技术在一台自然吸气多缸发动机上研究了压缩比和进气温度对HCCI 燃烧的影响[Haraldsson G, et al. HCCI combustin phasing in a multi cylinder engine using variable compression ratio. SAE 2002-01-2858], 发现高压缩比可以代替进气加热实现HCCI,但VCR结构复杂,难以产业化。 [0003] The effect of compression ratio and intake air temperature of the HCCI combustion [Haraldsson G, et al in a multi-cylinder naturally aspirated engine Saab Automobile VCR technology in 2002 using its development. HCCI combustin phasing in a multi cylinder engine using variable compression ratio. SAE 2002-01-2858], we found that a high compression ratio can be implemented instead of the HCCI intake air heating, but the VCR complicated structure, industrialization is difficult. 日产公司在2006 年发明了一种压缩比可变的活塞连杆机构,在中低负荷工作时e =14,可显著提高热效率而不会揚燃,高负荷工作时e = 8. [M. Sekine, year book-Gasoline Engine, Journal of JSAE,Vol. 61,No. 8,2007]。 2006 Nissan invention the piston rod of the mechanism of a variable compression ratio, when operating in the low load e = 14, can significantly improve the thermal efficiency without burning Yang, high load operation when e = 8. [M. Sekine, year book-Gasoline Engine, Journal of JSAE, Vol. 61, No. 8,2007]. 但连续可变压缩比的方法目前对于车用发动机还不实用,成本太高,又増加了车用发动机控制系统优化复杂性。 But continuously variable compression ratio engine of the vehicle is not present, for practical, cost is too high, but also to increase in the complexity of optimizing the car with the engine control system.

发明内容 SUMMARY

[0004] 本发明的目的就在于提供一种汽油机两级可变压缩比系统及其控制方法,以解决现有技术中的上述缺陷。 [0004] The object of the present invention to provide a gasoline two-step variable compression ratio system and control method to solve the above drawbacks of the prior art.

[0005] 为实现上述目的,本发明的技术方案是采用一种汽油机两级可变压缩比系统,在对应发动机进气门和排气门的两个顶置凸轮轴上,对应每缸的进气门和排气门分别设置大凸轮和小凸轮;在每缸的进气门上设置进气门凸轮型线切換机构,以用于切换与该进气门对应的进气门大凸轮和进气门小凸轮;在每缸的排气门上设置排气门凸轮型线切換机构, 以用于切換与该排气门对应的排气门大凸轮和排气门小凸轮。 [0005] To achieve the above object, the technical solution of the present invention is to use two-step variable compression ratio A gasoline engine system, on the corresponding engine intake and exhaust valves of the two overhead camshafts per cylinder corresponding to feed and exhaust valve cams are provided large and small cam; provided intake cam profile switching mechanism in the intake valve per cylinder, for a large intake cam switching corresponding to the intake valve and intake small cam valve; disposed exhaust cam profile switching mechanism on the exhaust valves per cylinder, for switching the exhaust valve corresponding to the exhaust valve and the exhaust valve cam large small cam.

[0006] 其中,所述进气门大凸轮的进气门关闭角设为60°CA ABDC〜90°CA [0006] wherein said large intake cam intake valve closing angle is 60 ° CA ABDC~90 ° CA

进气门小凸轮的进气门关闭角设为-10°C AABDC〜20°CA ABDC ;所述进气门小凸轮的进气门开启角设为80°CA ATDC〜0°CA ATDC ;所述排气门小凸轮的排气门关闭角设为_80°CA ATDC 〜0°CA ATDC。 Small intake cam intake valve closing angle is -10 ° C AABDC~20 ° CA ABDC; short cams of the intake valve opening angle of the intake valve is set to 80 ° CA ATDC~0 ° CA ATDC; the said exhaust cam is small exhaust valve closing angle is _80 ° CA ATDC ~0 ° CA ATDC.

[0007] 其中,当发动机的负荷小于预设值A吋,控制所述进气门凸轮型线切换机构将凸轮型线切换为进气门小凸轮,并且控制所述排气门凸轮型线切换机构将凸轮型线切换为排气门小凸轮;当发动机的负荷大于预设值A时,控制所述进气门凸轮型线切换机构将凸轮型线切换为进气门大凸轮,并且控制所述排气门凸轮型线切换机构将凸轮型线切換为排气门大凸轮。 [0007] wherein, when the engine load is less than a preset value A inch, the control of the intake valve cam profile switching mechanism to switch the cam profile of the intake valve cam small, and controls the exhaust cam profile switching the cam profile switching mechanism for the small exhaust valve cam; when the load of the engine is greater than a predetermined value a, the control of the intake valve cam profile of the cam profile switching mechanism is switched to the large intake cam, and the control said exhaust cam profile of the cam profile switching mechanism is switched to the large exhaust cams. [0008] 其中,当发动机的负荷小于预设值A且冷却水温低于预设值B时,采用火花点火燃烧模式;当发动机的负荷小于预设值A且冷却水温高于预设值B时,采用均质混合气压燃燃烧模式;当发动机的负荷大于预设值A时,采用火花点火燃烧模式。 When the load of the engine is less than a predetermined value A and the cooling water temperature is higher than the predetermined value B; [0008] wherein, when the load of the engine is less than a predetermined value A and the cooling water temperature is lower than the predetermined value B, in the spark-ignition combustion mode using HCCI combustion mode; when the load of the engine is greater than a predetermined value a, the spark-ignition combustion mode.

[0009] 其中,所述预设值A为O. 4MPa〜O. 5MPa。 [0009] wherein the predetermined value A is O. 4MPa~O. 5MPa.

[0010] 其中,所述预设值B为80°C〜90°C。 [0010] wherein the predetermined value B is 80 ° C~90 ° C.

[0011] 本发明还提供一种如上所述系统的控制方法,该方法包括: [0011] The present invention also provides a control method for a system as described above, the method comprising:

[0012] SI、检测发动机的负荷大小; [0012] SI, the size of the detected engine load;

[0013] S2、当所述负荷小于预设值A时,控制设置在每缸的进气门上的进气门凸轮型线切换机构,将凸轮型线切换为与该进气门对应的进气门小凸轮,并且控制设置在每缸的排气门上的排气门凸轮型线切换机构,将凸轮型线切换为与该排气门对应的排气门小凸轮; [0013] S2, when the load is less than the predetermined value A, the control set intake cam profile switching mechanism in the intake valve per cylinder, the cam profile is switched to the corresponding intake valve into small valve cam, the exhaust valve is provided and the control cam track switching mechanism on the exhaust valve per cylinder, the cam profile is switched to the exhaust valve corresponding to the small exhaust valve cam;

[0014] 当所述负荷大于预设值A时,在每缸的进气门上设置的进气门凸轮型线切换机构,将凸轮型线切换为与该进气门对应的进气门大凸轮,并且在每缸的排气门上设置的排气门凸轮型线切换机构,将凸轮型线切换为与该排气门对应的排气门大凸轮。 [0014] When the load is greater than a predetermined value A, on the intake valve per cylinder disposed intake cam profile switching mechanism to switch the cam profile of the intake valve corresponding to the large intake valve cam and exhaust cam profile provided on the exhaust valve per cylinder the switching mechanism, the exhaust valve cam profile switching cam is large corresponding to the exhaust valve.

[0015] 其中,所述控制方法还包括:S3、利用三效催化剂对尾气进行处理。 [0015] wherein said control method further comprises: S3, using a three-way catalyst for treatment of exhaust gas.

[0016] 其中,所述预设值A为O. 4Mpa〜O. 5MPa。 [0016] wherein the predetermined value A is O. 4Mpa~O. 5MPa.

[0017] 本发明的优点和有益效果在于,可以实现压缩比的快速改变;能够在一个发动机循环内实现SI和HCCI燃烧模式间切换;发动机中小负荷时,采用较高压缩比获得低油耗; 发动机大负荷时,采用较低压缩比避免爆震,获得高功率密度。 [0017] The advantages of the present invention and the advantageous effect that it can quickly change the compression ratio achieved; SI and HCCI can be achieved between modes in a combustion cycle of the engine; engine load is small, with a higher compression ratio to obtain lower fuel consumption; engine when the large load, a lower compression ratio to avoid knocking, high power density.

附图说明 BRIEF DESCRIPTION

[0018] 图I是本发明的实施例所涉及的汽油机两级可变压缩比系统的燃烧系统的示意图; [0018] FIG. I is a schematic view of two variable gasoline embodiments of the invention relates to the compression ratio system of a combustion system;

[0019] 图2是本发明的实施例所涉及的汽油机两级可变压缩比系统的四种凸轮升程曲线示意图; [0019] FIG. 2 is a two-step variable gasoline embodiments of the invention relates to the compression ratio of four kinds schematic lift curve of the cam drive system;

图3是本发明的实施例所涉及的高压缩比HCCI燃烧模式下的配气相位示意图; 图4是本发明的实施例所涉及的低压缩比SI燃烧模式下的配气相位示意图; FIG 3 is an embodiment of the present invention relates to high compression mode in the gas phase with a schematic view of the HCCI combustion ratio; FIG. 4 is a low compression embodiment of the present invention relates to a gas phase in the RATIO schematic SI combustion mode;

图5是本发明的实施例所涉及的汽油机两级可变压缩比系统的控制方法的流程 FIG 5 is a two-step variable gasoline embodiments of the present invention relates to a control method for a compression ratio of a flow system

[0020] [0020]

[0021] [0021]

[0022]图。 [0022] FIG.

[0023] 图中:1、火花塞;2、喷油器;10、进气门;11、进气门凸轮型线切换机构;12、进气门小凸轮;13、进气门大凸轮;20、排气门;21、排气门凸轮型线切换机构;22、排气门小凸轮; 23、排气门大凸轮。 [0023] FIG: 1, the spark plug; 2, injector; 10, an intake valve; 11, intake cam profile switching mechanism; 12, small intake cam; 13, a large intake cam; 20 The exhaust valve; 21, exhaust cam profile switching mechanism; 22, the small exhaust valve cam; 23, an exhaust cam gate.

具体实施方式 detailed description

[0024] 以下实施例用于说明本发明,但不用来限制本发明的范围。 [0024] The following examples serve to illustrate the present invention but are not intended to limit the scope of the present invention.

[0025] 本实施例的汽油机两级可变压缩比系统,如图I所示,在对应发动机进气门和排气门的两个顶置凸轮轴上,对应每缸的进气门10和排气门20分别设置大凸轮和小凸轮; 在每缸的进气门10上设置进气门凸轮型线切换机构11,以用于切换与该进气门10对应的进气门大凸轮13和进气门小凸轮12 ;在每缸的排气门20上设置排气门凸轮型线切换机构21,以用于切换与该排气门20对应的排气门大凸轮23和排气门小凸轮22。 [0025] The gasoline engine of the present embodiment two variable compression ratio system, as shown in FIG. I, on two overhead camshafts corresponding to the engine intake and exhaust valves, the corresponding intake valves 10 per cylinder and exhaust valve 20 are provided large and small cam cam; provided intake cam profile switching mechanism 11 on the intake valve of each cylinder 10, 10 for switching corresponding to the large intake valve intake cam 13 small cam 12 and the intake valve; provided on the exhaust valves 20 per cylinder exhaust cam profile switching mechanism 21, 20 for switching to the corresponding exhaust valve of the exhaust valve and the exhaust valve cam 23 large small cam 22. 图2为上述四种凸轮升程曲线示意图。 Figure 2 is a schematic view of the above-described four kinds of cam lift curve.

[0026] 本发明的汽油机的几何压缩比设为13〜15,进气门大凸轮13的进气门关闭角(IVC)设为60°CA ABDC〜90°CA ABDC ;进气门小凸轮12的进气门关闭角(IVC)设为-10°CA ABDC〜20°CA ABDC ;进气门小凸轮12的进气门开启角(IVO)设为80°CA ATDC〜(TC AATDC ;排气门小凸轮22的排气门关闭角(EVC)设为_80°C AATDC〜(TC A ATDC0 Geometric compression [0026] The gasoline engine of the present invention that the ratio of 13~15, a large intake cam angle of the intake valve 13 is closing (IVC) is set to 60 ° CA ABDC~90 ° CA ABDC; small intake cam 12 angle of intake valve closing (IVC) is set to -10 ° CA ABDC~20 ° CA ABDC; intake cam small opening angle of the intake valve 12 (IVO) is set to 80 ° CA ATDC~ (TC AATDC; exhaust small door 22 closing the exhaust valve cam angle (the EVC) to _80 ° C AATDC~ (TC a ATDC0

[0027] 当发动机的负荷小于预设值A时,所述进气门凸轮型线切换机构将凸轮型线切换为进气门小凸轮,并且所述排气门凸轮型线切换机构将凸轮型线切换为排气门小凸轮,即切换为高压缩比工作模式。 [0027] When the engine load is less than the preset value A, the cam profile of the intake valve cam profile switching mechanism is switched to the small intake cam and the exhaust cam profile of the cam switching mechanism type line is switched to the exhaust valve cam small, i.e., switched to a high compression ratio operating mode. 当发动机的负荷大于预设值A时,所述进气门凸轮型线切换机构将凸轮型线切换为进气门大凸轮,并且所述排气门凸轮型线切换机构将凸轮型线切换为排气门大凸轮,即切换为低压缩比工作模式。 When the load of the engine is greater than a predetermined value A, the cam profile of the intake valve cam profile switching mechanism is switched to the large intake cam and the exhaust cam profile of the cam profile switching mechanism is switched to gate exhaust cams, i.e., switched to a low compression ratio mode of operation.

[0028] 并且,当发动机的负荷小于预设值A且冷却水温低于预设值B时,采用火花点火燃烧模式(SI);当发动机的负荷大于预设值A且冷却水温高于预设值B时,采用均质混合气压燃燃烧模式(HCCI);当发动机的负荷大于预设值A时,采用火花点火燃烧模式(SI)。 [0028] Further, when the load of the engine is less than a predetermined value A and the cooling water temperature is lower than the predetermined value B, in spark-ignition combustion mode (the SI); when the load of the engine is greater than a predetermined value A and the cooling water temperature is higher than a preset when the value of B, in HCCI combustion mode (the HCCI); when the load of the engine is greater than a predetermined value a, the spark-ignition combustion mode (SI).

[0029] 上述中,预设值A的取值范围优选的是O. 4MPa〜O. 5MPa。 [0029] In the above, the preset value of the range A is preferably O. 4MPa~O. 5MPa.

[0030] 上述中,预设值B的取值范围优选的是80°C〜90°C。 [0030] In the above, the predetermined value B is preferably in the range of 80 ° C~90 ° C.

[0031] 下面以具体实施例说明本发明的汽油机两级可变压缩比系统及其控制方法。 [0031] The following specific examples illustrate the system than gasoline and a control method of the present invention two-step variable compression.

[0032] 本实施例中,发动机配气相位设计成如表I所示。 [0032] In this embodiment, the engine valve timing is designed to Table I below.

[0033]表 I [0033] TABLE I

[0034] [0034]

进气大凸轮 进气小凸轮 排气大凸轮 排气小凸轮EVO/0C A ABDC -55 -45EVC/VA ATDC 20 -65IV0/°CA ATDC -20 30 IVC/°CA ABDC 70 O 凸轮最大升程/mm 9. O 4. O 8. 6 4. O An intake cam intake large small large exhaust cam exhaust cam small cam EVO / 0C A ABDC -55 -45EVC / VA ATDC 20 -65IV0 / ° CA ATDC -20 30 IVC / ° CA ABDC 70 O maximum cam lift / mm 9. O 4. O 8. 6 4. O

[0035] 如图5所示,本实施例的汽油机两级可变压缩比系统的控制方法,包括如下步骤。 As shown in [0035] FIG 5, a control method of gasoline than the system of the present embodiment, two variable compression, comprising the following steps.

[0036] SI、检测发动机的负荷大小并进行判断。 [0036] The load size SI, the engine is detected and judged.

[0037] S2、当所述负荷小于O. 4MPa平均有效压力时,控制设置在每缸的进气门10上的进气门凸轮型线切换机构11,将凸轮型线切换为与该进气门10对应的进气门小凸轮12,并且控制设置在每缸的排气门20上的排气门凸轮型线切换机构21,将凸轮型线切换为与该排气门20对应的排气门小凸轮22,即切换为图3所示的高压缩比控制模式;当所述负荷大于 [0037] S2, when the load is less than the mean effective pressure O. 4MPa, control settings intake cam profile switching mechanism in the intake valve 10 of each cylinder 11, the cam profile is switched to the intake 10 corresponding to the small door intake cam 12 and an exhaust valve is provided to control the switching cam track means on each cylinder 21 of the exhaust valve 20, the switch 20 corresponding to the cam profile of the exhaust valve exhaust small door cam 22, i.e., switched to the high compression shown in FIG. 3 ratio control mode; when the load is greater than

O. 4MPa平均有效压力时,控制设置在每缸的进气门10上的进气门凸轮型线切换机构11,将凸轮型线切换为与该进气门10对应的进气门大凸轮13,并且控制设置在每缸的排气门20 上的排气门凸轮型线切换机构21,将凸轮型线切换为与该排气门20对应的排气门大凸轮23,即切换为图4所示的低压缩比控制模式,此时采用火花点火燃烧模式(SI)。 When O. 4MPa mean effective pressure, control settings intake cam profile switching mechanism in the intake valve 10 of each cylinder 11, the switch 10 corresponding to the cam profile of the intake cam 13 large intake and controlling the exhaust valve cam profile is provided the switching means in each cylinder 21 of the exhaust valve 20, the switch 20 corresponding to the cam profile of the exhaust valve and an exhaust valve cam 23 large, i.e. is switched to FIG. 4 FIG low compression ratio control mode in which the spark-ignition combustion mode (SI). 当汽油机工作在低压缩比模式时,判断冷却水的温度,当冷却水的温度低于85°C时,采用火花点火燃烧模式(SI);当冷却水的温度高于某值时,采用均质混合气压燃燃烧模式(HCCI)。 When the gasoline engine is operating in a low compression ratio mode, the temperature of cooling water is determined, when the temperature of the cooling water is below 85 ° C, spark-ignition combustion mode (the SI); when the temperature of the cooling water is higher than a certain value, are employed mass mixed compression ignition combustion mode (HCCI).

[0038] S3、利用三效催化剂对尾气进行处理。 [0038] S3, processing of exhaust gas by a three-way catalyst.

[0039] 即,发动机负荷小于0. 4MPa平均有效压カ且冷却水的温度高于85°C时,采用稀薄HCCI燃烧,利用三效催化剂氧化HC和CO排放,负荷大于0. 4MPa平均有效压カ或冷却水的温度低于85°C时,采用当量比SI燃烧,对有害排放物——HC、CO、NOx同时催化净化。 [0039] That is, the engine load is less than 0. 4MPa grades and average effective pressure at the coolant temperature is higher than 85 ° C, using lean HCCI combustion, the use of three-way catalysts oxidize HC and CO emissions, the load is greater than 0. 4MPa mean effective pressure when the temperature of cooling water or grades below 85 ° C, using the SI combustion equivalence ratio, harmful emissions --HC, CO, NOx purification catalyst simultaneously.

[0040] 本实施例利用凸轮型线切换机构实现配气相位的快速变化从而达到实现两级可变实际压缩比(如9和13)的目的,满足汽油机SI和HCCI燃烧模式的切換的要求。 [0040] The present embodiment utilizes a cam profile switching mechanism for rapid changes in the valve timing so as to achieve an actual two-step variable compression ratio achieved (e.g., 9 and 13) of the object, to meet the requirements of gasoline SI and HCCI combustion mode switching. 同时由于配气相位的特殊设计,中小负荷下实现了提高压缩比和減少泵气损失获得显著节油效果,大负荷时减小压缩比,避免了汽油机采用SI燃烧的爆震。 And because of the special design phase of the valve, the small load to achieve improved compression ratio and reduce the pumping loss achieve significant fuel efficiency, reducing the compression ratio when the load is large, to avoid the use of gasoline SI combustion knock. 另外,采用进气门晚关降低有效压缩比抑制SI燃烧爆震的同时,充气系数也相应降低。 Further, the use of the intake valve late off reducing the effective compression ratio while suppressing knocking SI combustion, volumetric efficiency is reduced accordingly. 为保证发动机大负荷时的功率密度,发动机进气量通过增压来补偿。 To ensure that the power density when the engine load is large, the intake air amount of the engine via a boost to compensate.

[0041] 并且,当发动机小负荷且冷却水温较低时,通过节气门控制进气量实现高压缩比下的当量比混合气SI燃烧工作模式,三效催化剂对NOx、HC和CO同时进行催化净化;当发动机中小负荷且冷却水温较高时,节气门全开,实现高压缩比下的稀混合气HCCI燃烧工作模式。 [0041] Further, when the low load and low engine coolant temperature, the intake air amount by the throttle control to achieve high compression SI combustion mode of air-fuel mixture ratio when the ratio of NOx, HC and CO at the same time the three-way catalyst for catalytic purification; small when the engine load is high and the cooling water temperature, wide open throttle, to achieve lean burn mode of the HCCI combustion at high compression ratios. 此工作模式下NOx排放极低(小于IOppm),主要产生HC和CO排放,三效催化剂只需对HC和CO排放进行氧化处理。 Low NOx emissions this mode of operation (less than IOppm), mainly produced HC and CO emissions, only three-way catalyst for oxidizing HC and CO emissions treatment. 大负荷时,采用低压缩比下的SI燃烧工作模式,三效催化剂对NOx、HC和CO同时进行催化净化。 When the large load, a low compression ratio of the SI combustion mode of operation, for NOx, HC and CO at the same time for the catalytic three-way catalyst.

[0042] 以上为本发明的最佳实施方式,依据本发明公开的内容,本领域的普通技术人员能够显而易见地想到ー些雷同、替代方案,这些方案均应落入本发明保护的范围。 [0042] The preferred embodiment of the present invention described above, according to the present disclosure, those of ordinary skill in the art to conceive ー more apparent similarity Alternatively, these programs shall fall within the scope of the invention.

Claims (8)

  1. 1. 一种汽油机两级可变压缩比系统,其特征在于,在对应发动机进气门和排气门的两个顶置凸轮轴上,对应每缸的进气门和排气门分别设置大凸轮和小凸轮;在每缸的进气门上设置进气门凸轮型线切换机构,以用于切换与该进气门对应的进气门大凸轮和进气门小凸轮;在每缸的排气门上设置排气门凸轮型线切换机构,以用于切换与该排气门对应的排气门大凸轮和排气门小凸轮;当发动机的负荷小于预设值A时,控制所述进气门凸轮型线切换机构将凸轮型线切换为进气门小凸轮,并且控制所述排气门凸轮型线切换机构将凸轮型线切换为排气门小凸轮;当发动机的负荷大于预设值A时,控制所述进气门凸轮型线切换机构将凸轮型线切换为进气门大凸轮,并且控制所述排气门凸轮型线切换机构将凸轮型线切换为排气门大凸轮。 A two gasoline engine variable compression ratio system, characterized in that, on the corresponding engine intake and exhaust valves of the two overhead camshafts per cylinder corresponding to the intake and exhaust valves are provided large small cam and cam; disposed on the intake valve per cylinder intake cam profile switching mechanism for switching a large intake cams corresponding to intake valves and the cams of the intake valve small; in each cylinder set exhaust cam profile switching mechanism the exhaust valve, an exhaust valve for a large exhaust cam and the cam switching small corresponding to the exhaust valve; and when the engine load is less than the preset value a, the control said intake cam profile switching mechanism to switch the cam profile of the intake valve cam small, and controls the exhaust cam profile of the cam profile switching mechanism is switched to the small exhaust valve cam; when the engine load is greater than when the preset value A, the control of the intake valve cam profile of the cam profile switching mechanism is switched to the large intake cam and the exhaust valve control cam profile switching mechanism to switch the cam profile of the exhaust valve big cam.
  2. 2.如权利要求I所述的汽油机两级可变压缩比系统,其特征在于,所述进气门大凸轮的进气门关闭角设为60°CA ABDC〜90°C AABDC ;所述进气门小凸轮的进气门关闭角设为-10°CA ABDC〜20°CA ABDC ;所述进气门小凸轮的进气门开启角设为80°CA ATDC〜0°C AATDC ;所述排气门小凸轮的排气门关闭角设为_80°CA ATDC〜0°CA ATDC。 2. I claim the two gasoline engine variable compression ratio system, wherein said large intake cam intake valve closing angle is 60 ° CA ABDC~90 ° C AABDC; the intake small valve cam intake valve closing angle is -10 ° CA ABDC~20 ° CA ABDC; short cams of the intake valve opening angle of the intake valve is set to 80 ° CA ATDC~0 ° C AATDC; the small exhaust cam exhaust valve closing angle is _80 ° CA ATDC~0 ° CA ATDC.
  3. 3.如权利要求I所述的汽油机两级可变压缩比系统,其特征在于,当发动机的负荷小于预设值A且冷却水温低于预设值B时,采用火花点火燃烧模式; 当发动机的负荷小于预设值A且冷却水温高于预设值B时,采用均质混合气压燃燃烧模式;当发动机的负荷大于预设值A时,采用火花点火燃烧模式。 3. I claim the two gasoline engine variable compression ratio system, wherein, when the load of the engine is less than a predetermined value A and the cooling water temperature is lower than the predetermined value B, in the spark-ignition combustion mode; when the engine when the load is less than the predetermined value a and the cooling water temperature is higher than the predetermined value B, in HCCI combustion mode; when the load of the engine is greater than a predetermined value a, the spark-ignition combustion mode.
  4. 4.如权利要求I或3所述的汽油机两级可变压缩比系统,其特征在于,所述预设值A为O. 4MPa 〜O. 5MPa。 I gasoline two-step variable or 3 as claimed in claim compression ratio system, characterized in that said predetermined value A is O. 4MPa ~O. 5MPa.
  5. 5.如权利要求3所述的汽油机两级可变压缩比系统,其特征在于,所述预设值B为80°C〜90°C。 Gasoline engine as claimed in claim two variable compression ratio system of claim 3, wherein said predetermined value B of 80 ° C~90 ° C.
  6. 6. —种如权利要求I所述系统的控制方法,其特征在于,该方法包括:51、检测发动机的负荷大小;52、当所述负荷小于预设值A时,控制设置在每缸的进气门上的进气门凸轮型线切换机构,将凸轮型线切换为与该进气门对应的进气门小凸轮,并且控制设置在每缸的排气门上的排气门凸轮型线切换机构,将凸轮型线切换为与该排气门对应的排气门小凸轮;当所述负荷大于预设值A时,在每缸的进气门上设置的进气门凸轮型线切换机构,将凸轮型线切换为与该进气门对应的进气门大凸轮,并且在每缸的排气门上设置的排气门凸轮型线切换机构,将凸轮型线切换为与该排气门对应的排气门大凸轮。 6. - I kind of claim system control method, characterized in that, the method comprising: 51 detecting an engine load size; 52, when the load is less than the preset value A, the control is provided per cylinder intake cam profile switching mechanism on the intake valve, the cam profile is switched to the intake valve corresponding to the small intake cam and an exhaust valve control cam provided on the exhaust valve per cylinder line switching mechanism, the cam profile is switched to the exhaust valve corresponding to the small exhaust valve cam; when the load is greater than a predetermined value a, is disposed on the intake valve per cylinder intake cam profile the switching mechanism, the cam profile of the cam is switched to the large intake valve corresponding to the intake valve and the exhaust valve cam profile switching mechanism is provided in the exhaust valve per cylinder, the cam profile is switched to the exhaust valve corresponding to the exhaust valve cam large.
  7. 7.如权利要求6所述的控制方法,其特征在于,所述控制方法还包括:S3、利用三效催化剂对尾气进行处理。 7. The control method according to claim 6, characterized in that the control method further comprises: S3, using a three-way catalyst for treatment of exhaust gas.
  8. 8.如权利要求6所述的控制方法,其特征在于,所述预设值A为O. 4MPa〜O. 5MPa。 The control method as claimed in claim 6, wherein the predetermined value A is O. 4MPa~O. 5MPa.
CN 200910236564 2009-10-26 2009-10-26 Two-stage variable compression ratio system of gasoline engine and control method thereof CN101699040B (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1603579A (en) 2003-09-30 2005-04-06 三菱扶桑卡客车公司 Variable valve mechanism for engine
CN1824926A (en) 2006-01-19 2006-08-30 清华大学 Method for realizing fast change-over of gasoline engine distributing phase and device thereof
CN101078375A (en) 2007-07-27 2007-11-28 奇瑞汽车有限公司 Gasoline engine valve lift and the phase variable system
CN101457678A (en) 2008-12-31 2009-06-17 奇瑞汽车股份有限公司 Novel lift range valve mechanism for variable valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1603579A (en) 2003-09-30 2005-04-06 三菱扶桑卡客车公司 Variable valve mechanism for engine
CN1824926A (en) 2006-01-19 2006-08-30 清华大学 Method for realizing fast change-over of gasoline engine distributing phase and device thereof
CN101078375A (en) 2007-07-27 2007-11-28 奇瑞汽车有限公司 Gasoline engine valve lift and the phase variable system
CN101457678A (en) 2008-12-31 2009-06-17 奇瑞汽车股份有限公司 Novel lift range valve mechanism for variable valve

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
周能辉,谢辉,张岩,陈韬,赵华.HCCI/SI双模式汽油机全可变气门控制的研究.《内燃机学报》.2007,第25卷(第5期),全文.
张鹏,高世伦.在汽油机上实现HCCI与SI双模式发动机技术综述.《小型内燃机与摩托车》.2008,第37卷(第6期),全文.
田国弘,王志,葛强强,王建昕,帅石金.缸内直喷汽油机SI-HCCI-SI燃烧模式切换的研究.《内燃机学报》.2007,第25卷(第3期),全文.

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