• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    intake device for internal combustion engine with supercompressor. a supercharger turbo compressor (5) (3) is located between an air flow meter (12) and a butterfly valve (13). an egr passage (21) is connected to an intake passage (10) at a joint (22), upstream of the compressor (5). to prevent a mixed fresh air and egr gas from flowing back into the air flow meter (12), the relationship (1) shown below is satisfied between an inlet throughput capacity (v1), of the air flow meter ( 12) for the junction point (22), an inlet passage capacity (v2), from the compressor (5) to the butterfly valve (13), and a maximum boost pressure (bp), under operational conditions in which the introduction of egr gas is done. (1)
    公开号:BR112013025594B1
    申请号:R112013025594-3
    申请日:2012-02-15
    公开日:2021-04-27
    发明作者:Daisuke Takaki
    申请人:Nissan Motor Co., Ltd.；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION
    [001] The present invention relates to an intake device having a recirculation valve, for use in an internal combustion engine equipped with a supercompressor, particularly of the type in which EGR gas is introduced from upstream of a supercompressor compressor. BACKGROUND
    [002] As described in patent document 1, an intake device for an internal combustion engine with a supercompressor is known, such as a supercompressor turbo, in which the intake device has a recirculation valve, for release a downstream boost pressure upstream of a supercompressor compressor, when a throttle valve is suddenly closed in an overloaded state. There is also a discharge gas recirculation (EGR) device for the fresh air discharge system upstream of the compressor, as described in patent document 1.
    [003] The problem presented below originates in the case in which the internal combustion engine equipped with a supercompressor uses the recirculation valve, whereby the supercharging pressure is released from the downstream to the upstream of the compressor, in combination with the device discharge gas recirculation, whereby EGR gas is introduced into the fresh air upstream of the compressor. When the recirculation valve is opened under operating conditions in which the exhaust gas recirculation is performed, the mixed fresh air and EGR gas flows back to the side upstream of the intake passage through the recirculation valve, way that an intake air flow meter is encrusted by the components of the EGR gas. DOCUMENTS OF THE PREVIOUS TECHNIQUE PATENT DOCUMENT
    [004] Patent Document 1: Publication of Japanese Patent Pending No. 2007-278110. SUMMARY OF THE INVENTION
    [005] In view of the above, the present invention provides an intake device for an internal combustion engine with a supercompressor, in which the intake device comprises an air flow meter, a butterfly valve and a valve recirculation; a supercompressor compressor is located between the air flow meter and the butterfly valve; the recirculation valve is adapted to release a pressure downstream of the compressor towards the upstream of the compressor, during closing of the butterfly valve; and an EGR passage is connected to a junction point joint upstream of the compressor, in order to introduce EGR gas into an intake system through the EGR passage.
    [006] In the present invention, an inlet passage capacity (V1), from the air flow meter to the junction point of the EGR passage, an inlet passage capacity (V2), from the compressor to the butterfly valve, and a maximum supercharging pressure (Pb), under operational conditions in which the introduction of EGR gas is made to satisfy a predetermined ratio, to prevent a mixed fresh air gas and EGR gas from flowing back, downstream of the compressor and reach the air flow meter when the recirculation valve is open.
    [007] More specifically, the relationship of the following formula (1) is satisfied between the intake passage capacity (V1), from the air flow meter to the junction point of the EGR passage, the intake passage capacity (V2) , from the compressor to the butterfly valve, and the maximum boost pressure (Pb), under operational conditions in which the introduction of EGR gas is made.

    [008] In the above formula, PI is a pressure upstream of the compressor, and K is a specific thermal ratio of the mixed fresh air gas and EGR gas downstream of the compressor.
    [009] Instead of formula (1), the relationship of formula (2) presented below can be satisfied between the inlet passage capacity (V1), from the air flow meter to the EGR passage junction point, the capacity of inlet passage (V2), from the compressor to the butterfly valve, and the maximum boost pressure (Pb), under operational conditions in which the introduction of EGR gas is made.

    [010] In the above formula, P1 is a pressure upstream of the compressor, T2 is a temperature of the gas downstream of the compressor, under maximum boost pressure (Pb), and T3 is a temperature of the gas released upstream of the compressor by recirculation valve.
    [011] In this case, counterflow occurs due to the expansion of the supercharging gas (mixed fresh air gas and EGR gas) highly pressurized in the inlet passage capacity V2, from the compressor to the butterfly valve, when the recirculation valve is open. As the pressure upstream of the compressor is approximately equal to atmospheric pressure, the amount of gas backflow generally increases with the boost pressure. If the amount of gas backflow exceeds the inlet passage capacity V1, from the air flow meter to the junction point of the EGR passage (in which only fresh air without EGR gas exists before opening the recirculation valve), the mixed fresh air gas and EGR gas reaches the air flow meter. The mixed gas containing EGR gas can thus be prevented with certainty from reaching the air flow meter and causing the air flow meter to become encrusted by adjusting the inlet passage capacity V1, from the air flow meter to the junction point of the EGR passage. , with the inlet passage capacity V2, from the compressor to the butterfly valve (or the inlet passage capacity V2, from the compressor to the butterfly valve, relative to the inlet passage capacity V1, from the air flow meter to the junction of the EGR passage), as appropriate according to the maximum boost pressure (Pb), under the operating conditions under which the EGR gas is introduced.
    [012] In the present invention, the intake passage capacities are properly adjusted according to the maximum boost pressure, under the operating conditions under which the introduction of EGR gas is made, as mentioned above. It is therefore possible to safely protect the EGR gas fouling air flowmeter, even when the recirculation valve is opened, during discharge gas recirculation. BRIEF DESCRIPTION OF THE DRAWINGS
    [013] Figure 1 is a schematic configuration diagram of an intake device for an internal combustion engine, according to an embodiment of the present invention, shown together with an internal combustion engine discharge system.
    [014] Figure 2 is a characteristic diagram showing the relationship between a maximum boost pressure and an exhaust gas volume from the internal combustion engine. DESCRIPTION OF THE ACCOMPLISHMENTS
    [015] An exemplary embodiment of the present invention will be described below with reference to the drawings.
    [016] Figure 1 is a schematic view showing an intake and discharge system for the internal combustion engine 1, in which an intake device, according to an embodiment of the present invention, is mounted. In the present embodiment, the internal combustion engine 1 is a gasoline engine. In the discharge passage 2 of the internal combustion engine 1, the discharge turbine 4 of the supercompressor turbo 3 is arranged. The catalytic converter 6 with, for example, a three-way catalyst, is arranged downstream of the discharge turbine 4 in the discharge passage 2. Although not shown in the drawing, a discharge muffler is disposed downstream of the catalytic converter 6 in the passage discharge 2, so that the discharge passage 2 is open to the outside by the discharge silencer. The discharge turbine 4 has a known type of discharge gate valve 7 for controlling the boost pressure. The internal combustion engine 1 has, for example, a direct injection configuration, in which each cylinder is equipped with a fuel injection valve, to inject fuel into the cylinder, although not shown in the drawing.
    [017] In the intake passage 10 of the internal combustion engine 1, the air filter 11, the air flow meter 12 and the butterfly valve 13 are arranged in the order mentioned from the upstream side. The compressor 5 of the supercharger turbo 3 is arranged between the air flow meter 12 and the butterfly valve 13, in the intake passage 10. In this arrangement, the intake passage 10 is generally divided into three portions: passage passage portion on the side a upstream of compressor 10a, upstream of compressor 5; passage portion on the downstream side of the compressor 10b, between the compressor 5 and the butterfly valve 13; and the passage portion on the downstream side of the butterfly 10c, between the butterfly valve 13 and the respective cylinders. In the present embodiment, the water-cooled or oil-cooled type 14 chiller is arranged in the passage portion on the downstream side of the butterfly 10c, so that a portion of the passage portion on the downstream side of the butterfly 10c, downstream of the intercooler 14, is branched into inlet taps for the respective cylinders. Alternatively, the intermediate cooler 14 can be a type of air-cooled.
    [018] The recirculation line 16 is provided in an inlet passage 14, in order to provide communication between the upstream and downstream sides of the compressor 5. The recirculation valve 7 is arranged in the recirculation line 16. The recirculation 17 has a mechanical actuator, operating in response to a pressure difference between the upstream and downstream sides of the butterfly valve 5, or an electrical actuator, operating in response to a control signal from a control unit, not shown in drawings, in order to open the recirculation line 16, according to a pressure increase in the passage portion on the downstream side of the compressor 10b, and thereby release the pressure within the passage portion on the downstream side of the compressor. 10b for the passage portion on the upstream side of the compressor 10a, for recirculating the intake air. The recirculation line 16 extends and connects between a point on the passage portion on the side downstream of compressor 10b, next to compressor 5, and a point on the passage portion on the side upstream of compressor 10a, next to compressor 5.
    [019] The EGR 21 passage, which constitutes a portion of a discharge recirculation device, is branched from a point downstream of the catalytic converter 6 in the discharge passage 2. One end of the EGR 21 passage is connected at the point of junction 22 in the passage portion on the upstream side of the compressor 10a. The junction point 22 is located on one side relative to the downstream portion of the upstream side of the compressor 10a, that is, in a position close to the compressor 5, but it is located in a position upstream of the junction point 20 of the recirculation line 16 and the passage portion on the upstream side of the compressor 10a. The EGR gas cooler of the oil cooling type or the water cooling type is arranged in the passage of EGR 21, for cooling the EGR gas. Furthermore, the discharge recirculation control valve 24 is arranged in a position downstream of the gas cooler EGR 23, to control the amount of discharge gas recirculation according to a desired discharge recirculation rate.
    [020] In the configuration mentioned above, the EGR gas is introduced upstream from the compressor 5 by the discharge recirculation control valve 24, under predetermined operational conditions in which the discharge recirculation must be done including and not the supercharging bands. In a supercharging range, the mixed fresh air gas and EGR gas is pressurized by the compressor 5, passes through the butterfly valve 13 and the intermediate cooler 14 and is fed to the respective cylinders of the internal combustion engine 1. When the butterfly valve 13 is suddenly closed by, for example, operation of the driver's accelerator pedal, in the charge range, the recirculation valve 17 is opened in response to the closing of the butterfly valve 13, so that the highly pressurized fresh air / gas mixture in the passage on the downstream side of the compressor 10b is released to the passage portion on the upstream side of the compressor 10a. The fresh air / gas mixture released is circulated through the recirculation line 16, even if the compressor 5 is rotating under the action of the rotor inertia. This makes it possible to avoid the abnormal noise caused by the pulsation of the compressor 5.
    [021] When the recirculation valve 17 is opened in response to the closing of the butterfly valve 13, under the operating conditions in which the exhaust gas recirculation is conducted, the relatively highly pressurized mixed gas of fresh air and EGR gas, in passage portion on the downstream side of the compressor 10b, expands through the recirculation valve 17. Consequently, a counterflow of the mixed fresh air gas and EGR gas occurs to the passage portion on the upstream side of the compressor 10a. If the mixed fresh air gas and EGR gas flow back and reach air flow meter 12, air flow meter 12 will be unfavorably encrusted by the components of EGR gas.
    [022] To prevent the mixed fresh air gas and EGR gas from reaching the air flow meter 12, the ratio of formula (1) shown below is satisfied, between the V1 capacity of the passage portion on the side a upstream of the compressor 10a and, more specifically, part of the passage portion on the upstream side of the compressor 10a, from the air flow meter 12 to the junction point 22 of the EGR passage, and the passage portion on the upstream side of the compressor 10a , in which only fresh air without EGR gas exists, capacity V2 of the passage portion on the downstream side of compressor 10b (part of compressor 5 for butterfly valve 13), in which the mixed gas of fresh air and gas Pressurized EGR exists and the maximum supercharging pressure Pb (kPa), under operational conditions in which the introduction of the EGR gas is conducted in the present invention.

    [023] In formula (1), P1 is a pressure (kPa) in the passage portion on the upstream side of compressor 10a, which is downstream of compressor 5, and K is a specific thermal ratio of the mixed fresh air gas and EGR gas in the passage portion on the downstream side of the compressor 10b, which is downstream of the compressor 5. The pressure P1 upstream of the compressor 5 can be considered substantially as the atmospheric pressure.
    [024] The above relation can be expressed alternatively by the formula (2) presented below, using the temperature T2 (° K) of the gas in the passage portion on the downstream side of the compressor 10b, under the maximum boost pressure Pb and the temperature T3 (° K) of the gas released upstream of the compressor 5 by the recirculation valve 17.

    [025] The temperature of gas T2 is given by the formula (3) presented below based on a compressor efficiency ^ comp (%) of compressor 5.

    [026] In formula (3), T2 'is a temperature (° K) of the gas after theoretical isentropic compression of pressure P1 upstream of compressor 5 for the maximum boost pressure Pb.
    [027] Furthermore, the temperature of the T3 gas is given by the formula (4) shown below.

    [028] In general, the first term on the right side of formula (1) presented above corresponds to the volume of excess gas, which would flow out of the passage portion on the upstream side of the compressor 10a through the recirculation valve 17, when the gas, under the boost pressure Pb, expands to the pressure P1 upstream of the compressor 5, and the second term on the right side of the formula (1) presented above corresponds to the term for correction according to the variation in the temperature of the gas. When counter-flowing the gas, the gas in the passage portion on the upstream side of the compressor 10a (more specifically, in the portion of the passage portion on the upstream side of the compressor 10a, from the air flow meter 13 to the junction point 22 of the EGR passage, and of the passage portion on the upstream side of the compressor 10a) flows first through the air flow meter 12, in an inverse condition. The gas in this part, however, is fresh air without EGR and does not cause fouling of the air flow meter. Consequently, it must be considered that in view of the expansion of the gas (volume: V2, pressure: Pb) existing in the passage portion on the downstream side of the compressor 10b, when opening the recirculation valve 17.
    [029] The formula presented below is based on the general "P x VK = constant" ratio for adiabatic gas variation, where P (kPa) is a pressure of the gas; V (m3) is a volume of the gas, and K is a specific thermal ratio. In the formula presented below, the subscript α indicates a state before the variation, and the subscript β indicates a state after the variation.

    [030] The formula (5) presented below is derived from the formula mentioned above.

    [031] The formulas presented below are also based on the general relationship of "T x VK-1 = constant".

    [032] The formula (6) presented below is then derived by replacing the formulas mentioned above in formula (5).

    [033] On the other hand, the volume of excess gas, when volume gas V2, under the boost pressure Pb in the passage portion on the downstream side of compressor 10b, expands at pressure P1, is expressed by the first term on the right side of the formula (1) presented above, as mentioned above. This volume is a value at temperature T2, under the supercharged state. The volume of gas at temperature T3, after opening the recirculation valve 17, is (T3 / T2) times the value mentioned above.
    [034] The Vflow volume of the excess gas (exhaust gas), released by the recirculating gas 17, is, therefore, given by the formula presented below, as on the right side of the formula (2) mentioned above.

    [035] In this case, the temperature of the T3 gas is expressed by the following formula (7), as derived from the formula (6) mentioned above.

    [036] Formula (7) is replaced in the formula above.

    [037] In this way, the volume of the exhaust gas is given by formula (8).
    [038] To prevent the counterflow gas from reaching the air flow meter 12, the inlet passage capacity V1, from the junction point of the passage to the air flow meter 12, needs to be greater than the volume of the flow gas. Vflow discharge. It is, therefore, necessary to satisfy the relationship of formula (1) mentioned above.
    [039] In other words, it is possible to adjust the capacity of the inlet passage V1 to be greater than the volume of the exhaust gas Vflow, at the maximum boost pressure Pb, under the operating conditions under which the introduction of the EGR gas is made to protect the air flow meter 12 from fouling by the EGR gas, in view of the fact that the volume of the Vflow exhaust gas varies, depending on the supercharging pressure Pb, as shown in Figure 2.
    [040] As mentioned above, the gas temperature T2 is given by formula (3), based on the efficiency of the compressor ^ comp (%) of the compressor 5.
    [041] The formula (9) presented below is derived from formula (6), in which T1 is a gas temperature upstream of compressor 5, and T2'is a gas temperature, after theoretical isentropic compression of pressure P1 at maximum boost pressure Pb by compressor 5.
    (9)
    [042] In this case, it is defined that: πc is a pressure ratio (πc = Pb / Pi); ΔT is a difference between the pressure of the Ti gas and the temperature T2 ', after theoretical isotropic compression (ΔT = T2' - Ti); and qcom> (%) is a compressor efficiency. The increase in gas temperature is expressed by ΔT / (^ comp / 100).

    [043] The temperature of the gas, after compression, is thus given by formula (3).
    [044] Furthermore, the temperature of the T3 gas is given by the formula (4) shown below (4), as derived from the formula (6) presented above using the pressure ratio πc.

    [045] The factor on the right side of the formula (i) mentioned above is approximately 0.67, based on the assumption that the maximum boost pressure Pb is i80 kPa, the pressure Pi upstream of compressor 5 is i00 kPa and the specific thermal ratio K is 1.4.
    [046] The fouling of the air flow meter i2 by the gas counterflow can thus be substantially avoided by simply adjusting the capacities of the inlet passages V1 and V2 in such a way as to satisfy the following relationship:

    [047] It is due to the fact that, although the embodiment, mentioned above, refers specifically to the case in which the supercompressor turbo 3, having the compressor 5 and the discharge turbine 4 connected coaxially to each other, is adopted as the su-percompressor, the supercompressor is not limited to this supercompressor in the present embodiment. Any type of supercompressor can be applied as long as the intake device is equipped with the recirculation valve.
    权利要求:
    Claims (3)
    [0001]
    1. Inlet device for an internal combustion engine (1) with a super-compressor (3), the inlet device comprising an inlet passage equipped with an air flow meter (12), a butterfly valve (13) and a recirculation valve (17), a supercompressor compressor (5) (3) being located between the air flow meter (12) and the butterfly valve (13), the recirculation valve (17) being adapted to release a pressure downstream of the compressor (5) towards the upstream of the compressor (5) during closing of the butterfly valve (13), an EGR passage (21) of the internal combustion engine (1) being connected to the intake passage in a junction (22) upstream of the compressor (5), in order to introduce EGR gas into an intake system through the EGR passage (21), CHARACTERIZED by the fact that the intake device is configured to satisfy one of the two formulas between an intake passage capacity (V1) of the air flow meter (12) to the junction (22) of the intake passage and EGR passage (21), an intake passage capacity (V2) from the compressor (5) to the butterfly valve (13) and a maximum boost pressure (Pb) under operating conditions in the which EGR gas is introduced:
    [0002]
    2. Intake device for an internal combustion engine with a supercompressor according to claim 1, CHARACTERIZED by the fact that the temperature of gas T2 is given by the formula presented below based on an efficiency (^ comp) of the compressor (5),
    [0003]
    3. Intake device for an internal combustion engine with a super-compressor (3) according to claim 1 or 2, CHARACTERIZED by the fact that the gas temperature T3 is given by the formula presented below: where πc is a pressure ratio (Pb / PO of the compressor (5).
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    法律状态:
    2018-03-27| B15K| Others concerning applications: alteration of classification|Ipc: F02M 35/10 (2006.01), F02B 37/00 (2006.01), F02B 3 |
    2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-12-31| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-03-30| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-04-27| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 15/02/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    JP2011138414|2011-06-22|
    JP2011-138414|2011-06-22|
    PCT/JP2012/053478|WO2012176490A1|2011-06-22|2012-02-15|Intake device for internal combustion engine with supercharger|
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