KR0134244B1 - Structure of high performance intake and exhaustp ort for an automotive engine - Google Patents

Structure of high performance intake and exhaustp ort for an automotive engine

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Publication number
KR0134244B1
KR0134244B1 KR1019950016604A KR19950016604A KR0134244B1 KR 0134244 B1 KR0134244 B1 KR 0134244B1 KR 1019950016604 A KR1019950016604 A KR 1019950016604A KR 19950016604 A KR19950016604 A KR 19950016604A KR 0134244 B1 KR0134244 B1 KR 0134244B1
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KR
South Korea
Prior art keywords
valve
intake
exhaust
seat
exhaust port
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KR1019950016604A
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Korean (ko)
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KR970001923A (en
Inventor
윤석준
Original Assignee
한승준
기아자동차주식회사
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Priority to KR1019950016604A priority Critical patent/KR0134244B1/en
Publication of KR970001923A publication Critical patent/KR970001923A/en
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Publication of KR0134244B1 publication Critical patent/KR0134244B1/en

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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
    • F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
    • F02B31/04—Modifying induction systems for imparting a rotation to the charge in the cylinder by means within the induction channel, e.g. deflectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/001—Gas flow channels or gas chambers being at least partly formed in the structural parts of the engine or machine
    • 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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

본 발명은 차량엔진용 고성능 흡기/배기포트의 구조에 관한 것으로, 실린더헤드(1)에 형성되어 플로우와 스월성능을 향상시키도록 된 흡기포트(10)와 배기포트(20)에서, 상기 흡기포트(10)에 형성된 밸브와 시트접촉부의 인너시트구경(dv)을 44.6㎜으로 넓혀 베타(β)비를 0.164로 하고 랜드와이드(Lw)를 1.96㎜로 좁힘과 더불어, 상기 리브(3)를 안쪽으로 더 돌출시켜 공기유입영역(z)을 보다 좁히는 한편, 상기 배기포트(20)에 형성된 밸브와 시트접촉부의 인너트구경(dv)을 40.8㎜지름으로 넓혀 베타(β)비를 0.138으로 하고 랜드와이드(Lw)를 0.138로 좁힘과 더불어 배기가스의 배출흐름을 향상시키기 위해 상기 밸브시트부(20c)를 10㎜반지름으로 곡선처리시키게 되어 있다.The present invention relates to a structure of a high performance intake / exhaust port for a vehicle engine, wherein the intake port (10) and exhaust port (20) are formed in the cylinder head (1) to improve flow and swirl performance. The inner seat diameter (dv) of the valve and seat contact portion formed at (10) was widened to 44.6 mm, the beta (β) ratio was 0.164, and the landwide Lw was narrowed to 1.96 mm, and the rib 3 was inward. The air inflow zone z is further narrowed to extend the inlet diameter dv of the valve and seat contact portion formed in the exhaust port 20 to a diameter of 40.8 mm so that the beta ratio is 0.138. In order to narrow the wide Lw to 0.138 and improve the exhaust flow of the exhaust gas, the valve seat portion 20c is curved at a radius of 10 mm.

Description

차량엔진용 고성능 흡기/배기포트의 구조Structure of high performance intake / exhaust port for vehicle engine

제1도는 본 발명에 따른 흡기포트의 밸브시트와 밸브의 부분단면도.1 is a partial cross-sectional view of the valve seat and the valve of the intake port according to the present invention.

제2도는 제1도의 흡기포트의 립부형상에 대한 부분단면도.2 is a partial cross-sectional view of the lip shape of the intake port of FIG.

제3도는 본 발명에 따른 배기포트와 밸브시트와 밸브의 부분단면도.3 is a partial cross-sectional view of the exhaust port, the valve seat and the valve according to the present invention.

제4도의 (A)는 본 발명에 따른 플로우 및 스월의 개선관계도.4 (A) is an improved relationship between flow and swirl according to the present invention.

(B)는 스월번호와 플로우계수와의 상관관계도.(B) is a correlation diagram between swirl number and flow coefficient.

제5도는 종래구조로서, 제1도에 대응되는 흡기포트의 밸브시트와 밸브의 부분단면도.5 is a conventional structure, a partial cross-sectional view of the valve seat and the valve of the intake port corresponding to FIG.

제6도는 제5도의 흡기포트의 립부형상에 대한 부분단면도.6 is a partial cross-sectional view of the lip shape of the intake port of FIG.

제7도는 종래구조로서, 제3도에 대응되는 배기포트의 밸브시트와 밸브의 부분단면도이다.7 is a conventional structure, which is a partial sectional view of the valve seat and the valve of the exhaust port corresponding to FIG.

* 도면의 주요부분에 대한 부호의 설명* Explanation of symbols for main parts of the drawings

1 : 실린더 헤드 1c, 2c : 밸브시트부1: Cylinder head 1c, 2c: Valve seat part

2 : 흡기밸브 3 : 립(LIP)부2: Intake valve 3: Lip part

10 : 흡기포트 20 : 배기포트10: intake port 20: exhaust port

21 : 배기밸브 Lw : 랜드위드스(LandWidth)21: exhaust valve Lw: LandWidth

dv : 인너시트구경 Z : 공기유입영역dv: inner seat diameter Z: air inlet area

본 발명은 차량엔진용 고성능 흡기/배기포트의 구조에 관한 것으로, 특히 직접분사식엔진의 성능에 관련된 혼합기에 대한 플로우와 스월성능을 향상시킴과 더불어 유해배기가스의 발생을 격감시키도록 된 차량엔진용 고성능 흡기/배기포트의 구조에 관한 것이다.The present invention relates to a structure of a high performance intake / exhaust port for a vehicle engine, and particularly for a vehicle engine to improve the flow and swirl performance of a mixer related to the performance of a direct injection engine and to reduce the generation of harmful exhaust gas. It relates to a structure of a high performance intake / exhaust port.

일반적으로 직접분사식(Direct Injection)엔진의 경우, 엔진성능 결정의 주요인은 흡입혼합기에 대한 플로우(Flow)와 스월(Swirl) 성능인데 이들의 성능은 흡기포트와 배기포트의 형상에 크게 의존되는바, 종래에는 제5도에 도시된 흡기포트와 같이, 상기 흡기포트(10)의 하부에는 실린더헤드(1)에 일체로 형성되어지는 밸브시트부(1c)와 이곳에 흡기밸브(2)가 안착되며 제6도에 도시된 바와 같이, 공기를 유입하도록 일정한 공기유입영역(z)을 형성하는 립(LIP)부 (3)가 형성되는데, 여기서 인너시트구경(dv)이 43㎜지름을 갖고 보어구경이 110㎜지름으로 됨과 더불어, 밸브와 밸브시트의 접척폭인 랜드위드스(Lw)가 3.46㎜로 되어진다.In general, in the case of a direct injection engine, the main factors for determining engine performance are the flow and swirl performance of the intake mixer, and their performance is highly dependent on the shape of the intake and exhaust ports. Conventionally, like the intake port shown in FIG. 5, the lower portion of the intake port 10 has a valve seat portion 1c formed integrally with the cylinder head 1 and an intake valve 2 seated therein. As shown in FIG. 6, a lip (LIP) portion 3 is formed which forms a constant air inlet zone z to introduce air, wherein the inner seat diameter dv has a diameter of 43 mm and a bore diameter. In addition to the 110 mm diameter, Landweeds Lw, which is the contact width between the valve and the valve seat, is 3.46 mm.

따라서, 직접분사식 엔진의 성능에 크게 관련된 플로우성능은 플로우계수에 베타(β)비를 곱해 얻어지게 되므로, 상기 플로우성능을 좋게 하기 위해서는 상기 베타(β)비를 크게 하는 것이 매우 바람직하며 이때 베타(β)비는 다음 공식에 의해 얻어지게 된다.Therefore, the flow performance, which is highly related to the performance of the direct injection engine, is obtained by multiplying the flow coefficient by the beta (β) ratio. Therefore, in order to improve the flow performance, it is highly desirable to increase the beta (β) ratio. β) ratio is obtained by the following formula.

베타(β)비 = [인너시트구경(dv)보어구경(D)]2 Beta (β) ratio = [Inner seat diameter (dv) Bore diameter (D)] 2

또한, 상기 직접분사식엔진의 성능에 크게 관련된 또 다른 요인인 스월(Swirl) 번호는 밸브개폐량과 피스톤의 속도를 고려한 크랭크 각의 적분치로부터 얻어지게 된다.In addition, the swirl number, which is another factor related to the performance of the direct injection engine, is obtained from the integral value of the crank angle in consideration of the valve opening amount and the speed of the piston.

이에따라, 상기 흡기포트(10)의 베타(β)비는 (43/110)2으로부터 약 0.153의 수치를 갖게 됨과 더불어, 상기 배기포트(20)의 베타(β)비는 (36.5/110)2으로부터 약 0.110의 수치를 갖게 되어 직접분사식엔진 118의 스트로그와 6728cc 직렬 6기통에서 표-1과 같은 성능을 나타내게 된다.Accordingly, the beta (β) ratio of the intake port 10 has a value of about 0.153 from (43/110) 2 , and the beta (β) ratio of the exhaust port 20 is (36.5 / 110) 2. It has a value of about 0.110 from the STROK of the direct injection engine 118 and 6728cc in series 6 cylinders, as shown in Table-1.

그러나 상기와 같은 흡기포트(10)의 베타(β)비가 0.153이고, 배기포트(20)의 베타(β)비가 0.110으로 되면 플로우성능만이 성능결정의 주요인인 간접분사식엔진의 경우와는 달리 플로우와 스월의 두요인에 의해 성능이 결정되어지는 직접분사식엔진의 경우와는 상기 표-1가 같이 스모크(smoke)나 배기가스의 발생이 높아져 한층 강화되고 있는 유해배기가스 규제를 만족시키지 못하게 되는 중대한 문제가 발생되어지게 된다.However, when the beta (β) ratio of the intake port 10 is 0.153 and the beta (β) ratio of the exhaust port 20 is 0.110, the flow performance is different from that of the indirect injection engine, in which only the flow performance is the main factor. As in the case of the direct injection engine whose performance is determined by the two factors of Swirl and Swirl, as shown in Table 1 above, the generation of smoke or exhaust gas is high, and thus it is not possible to satisfy the stricter exhaust gas regulations. Problems will arise.

이에 본 발명은 상기와 같은 문제를 해소하기 위해 발명된 것으로, 직접분사식엔진의 성능이 크게 관여되는 플로우와 스월의 성능을 전체적으로 향상시켜 엔진성능을 좋게 할 뿐만 아니라 엔진에서 발생되어지는 스모크와 유해배기가스의 발생을 격감시키도록 된 차량엔진용 고성능 흡기/배기포트의 구조를 제공함에 그 목적이 있다.Therefore, the present invention was invented to solve the above problems, and improves the overall performance of the flow and swirl, which are directly involved in the performance of the direct injection engine, and improves the engine performance as well as smoke and harmful exhaust generated from the engine. It is an object of the present invention to provide a structure of a high performance intake / exhaust port for a vehicle engine to reduce the generation of gas.

상기와 같은 목적을 달성하기 위한 본 발명은, 실린더헤드에 형성되어 플로우와 스월성능을 향상시키도록 된 흡기포트와 배기포트에서, 상기 흡기포트에 형성된 밸브와 인너시트구경(dv)을 44.6㎜으로 넓혀 베타(β)비를 0.164로 하고 랜드위드스(Lw)를 1.96㎜로 좁힘과 더불어, 상기 립부를 안쪽으로 더 돌출시켜 공기유입영역(z)을 보다 좁히는 한편, 상기 배기포트 하부에 형성된 인너트구경(dv)을 40.8㎜지름으로 넓혀 베타(β)비를 0.138으로 하고 랜드위드스(Lw)를 0.138로 좁힘과 더불어 배기가스의 배출흐름을 향상시키기 위해 상기 밸브시트부를 10㎜반지름으로 곡선처리형상을 갖춘 구조로 되어 있다.The present invention for achieving the above object, in the intake port and exhaust port formed in the cylinder head to improve the flow and swirl performance, the valve and inner seat diameter (dv) formed in the intake port to 44.6mm Widening the beta (β) ratio to 0.164 and narrowing the Landweeds (Lw) to 1.96 mm, further protruding the lip further inward to narrow the air inlet region z, and the inner formed at the lower portion of the exhaust port. The valve seat is curved to a radius of 10 mm to widen the diameter (dv) to 40.8 mm and to reduce the beta (β) ratio to 0.138, to narrow the Landweeds (Lw) to 0.138 and to improve the exhaust flow. It has a structure with a processing shape.

이하 본 발명을 첨부된 예시도면을 참조로 상세히 설명한다.Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

제1도는 본 발명에 따른 흡기포트의 밸브시트와 밸브의 부분단면도이고, 제2도는 흡기포트의 립부형상에 대한 부분단면도이며, 제3도는 본 발명에 따른 배기포트의 밸브시트와 밸브의 부분단면도이고, 제4도의 (A)와 (B)는 각각 밸브개폐량에 따른 플로우용량의 관계도와 스월번호에 따른 플로우계수의 관계도인데, 종래구조를 도시한 제5도와 제6도 및 제7도와 동일한 참조부호를 붙이면서 그 설명을 생략한다.1 is a partial cross-sectional view of the valve seat and the valve of the intake port according to the invention, Figure 2 is a partial cross-sectional view of the lip shape of the intake port, Figure 3 is a partial cross-sectional view of the valve seat and valve of the exhaust port in accordance with the present invention (A) and (B) in FIG. 4 are the relationship between the flow capacity according to the valve opening and closing rate and the flow coefficient according to the swirl number, respectively. FIG. 5 and FIG. 6 and FIG. The same reference numerals are used to omit the description.

본 발명은, 흡기밸브와 배기밸브가 접촉되어지는 흡·배기밸브시트 및 포트에 관한 것인데, 상기 흡기밸브(2)가 안착되는 실린더헤드(1)에 일체로 형성되어져 밸브시트부(1c)와 혼합기를 유입하도록 일정한 혼합기 영역(z)을 형성시키는 립부(3)가 구비되는 한편, 상기 흡기포트(10)와 동일하게 실린더헤드(1)에 일체로 형성되어 배기밸브(21)가 안착되는 밸브시트부(2c)를 형성하게 된다.The present invention relates to an intake / exhaust valve seat and a port in which an intake valve and an exhaust valve come into contact with each other. The intake valve 2 is integrally formed with the cylinder head 1 on which the intake valve 2 is seated. A lip portion 3 is formed to form a constant mixer zone z so that the mixer is introduced therein, while a valve is formed integrally with the cylinder head 1 in the same manner as the intake port 10 so that the exhaust valve 21 is seated. The sheet portion 2c is formed.

여기서, 상기 흡기포트(10)는 플로우성능에 관계된 베타(β)비를 보다 크게 하기 위해 인너시트구경(dv)을 44.6㎜지름으로 넓히고 랜드위드스(Lw)를 1.96㎜로 흡입과 더불어 스월성능을 향상시키기 위해 흡기포트의 립부(3)를 안쪽으로 더 돌출시켜 혼합기유입영역(z)을 보다 좁게 형성하는 한편, 상기 배기포트(20)의 밸브시트부(2c)는 배기가스의 배출흐름을 향상시키기 위해 전체적으로 10㎜반지름으로 곡선처리하고, 상기 인너시트부(20b)의 인너시트구경(dv)을 4.08㎜지름으로 넓힘과 더불어 랜드위드스(Lw)를 1.84㎜로 좁게 형성시키게 된다.Here, the intake port 10 has a wider inner seat diameter (dv) to 44.6 mm diameter and landweeds (Lw) to 1.96 mm to increase the beta (β) ratio related to the flow performance. In order to improve the efficiency, the lip portion 3 of the intake port is further protruded inward to form a narrower mixer inflow zone z, while the valve seat portion 2c of the exhaust port 20 In order to improve the overall curve to a radius of 10mm, the inner sheet diameter (dv) of the inner sheet portion 20b is widened to 4.08mm diameter, and Landweeds (Lw) is narrowly formed to 1.84mm.

따라서 직접분사식엔진의 성능을 좌우하는 플로우성능에 관계된 베타(β)비는 흡기포트(10)의 경우 (44.6/110) 으로부터 약 0.164가 되고, 배기포트(20)의 경우 (40.8/110) 으로부터 약 0.138으로 되어 직접분사식엔진(118스트로크와 6728cc 직렬 6기통)에서 표-2와 같이 기존의 경우보다 더욱 향상된 성능을 나타내게 된다.Therefore, the beta (β) ratio related to the flow performance that influences the performance of the direct injection engine is (44.6 / 110) for the intake port (10). 0.164 from, for exhaust port 20 (40.8 / 110) It is about 0.138 from the direct injection engine (118 strokes and 6728cc in series six cylinders) shows a more improved performance than the conventional case as shown in Table-2.

또한 제4도의 (A)는 밸브개폐량에 따른 플로우용량과의 상관관계를 나타낸 상태도인데, 실선으로 표시된 개선전 상태의 점선과 파선으로 표시된 개선후의 상태가 도시된 바와 같이 밸브개폐량이 클수록 더욱 증가되어져 플로우성능이 향상된다.In addition, (A) of FIG. 4 is a state diagram showing a correlation with the flow capacity according to the valve opening and closing amount, and as the valve opening and closing amount is increased as shown by the dotted line and the broken line, respectively, before the improvement is indicated by the solid line. The flow performance is improved.

여기서, 상기 그래프상의 점섬 및 파선은 각각 최고 및 최저 실험측정치를 나타내는 것이다.Here, the point islands and dashed lines on the graph represent the highest and lowest experimental measurements, respectively.

한편, 제4도의 (B)의 스월번호와 플로우계수와의 상관관계를 나타낸 상태도인데, 세모형상으로 표시된 개선전 상태보다 열십자형상과 네모형상으로 표시된 개선후상태가 스월번호가 현저히 큰쪽으로 분포되는데 이는 스월번호 클수록 스월성능이 좋은 것을 의미하므로 스월성능이 향상되어지게 된다.On the other hand, it is a state diagram showing the correlation between the swirl number and the flow coefficient of (B) in FIG. This means that the greater the swirl number, the better the swirl performance, so the swirl performance is improved.

여기서, 상기 열십자형상 및 네모형상은 각각 개선효과의 최고 및 최저실험측정치를 나타낸다.Here, the crisscross shape and the square shape represent the highest and lowest experimental measurements of the improvement effect, respectively.

이상 설명한 바와 같이 본 발명에 의하면, 흡기포트와 배기포트의 형상이 베타(β)비를 크게 함과 더불어 상기 흡기포트의 혼합기유입영역을 보다 작게 형성시켜 전체적으로 플로우와 스월의 성능을 향상시켜 엔진의 성능을 향상함과 더불어 스모크와 유해배기가스의 발생을 이게 되는 효과가 있다.As described above, according to the present invention, the shape of the intake port and the exhaust port increases the beta (β) ratio, and the mixer inlet area of the intake port is made smaller, thereby improving the performance of the flow and swirl as a whole. In addition to improving performance, there is an effect that leads to the generation of smoke and harmful exhaust gas.

Claims (1)

실린더헤드(1)에 형성된 흡기포트(10)가 공기유입통로인 밸브시트부(1c)와 흡기밸브(2)가 안착되어 기밀을 유지시키는 시트와 밸브의 접촉부를 형성함과 더불어 일정량의 공기를 유입시키도록 립브(3)에 의해 일정한 공기유입영역(z)을 형성하는 한편, 연소후 발생되는 배기가스가 배출되어지기 위한 배기포트(20)가 배기가스 배출통로인 밸브시트부(20c)와 배기밸브(21)가 안착되어 기밀을 유지시키는 시트와 밸브의 접촉부를 형성한 차량엔진용 고성능 흡기/배기포트의 구조에 있어서, 상기 흡기포트(10)의 하부에 형성된 인너시트구경(dv)을 44.6㎜으로 넓혀 베타(β)비를 0.164로 하고 랜드위드스(Lw)를 1.96㎜로 좁힘과 더불어, 상기 립부(3)를 안쪽으로 더 돌출시켜 공기유입영역(z)을 보다 좁히는 한편, 상기 배기포트 하부에 형성된 인너트구경(dv)을 40.8㎜지름으로 넓혀 베타(β)비를 0.138으로 하고 랜드위드스(Lw)를 0.138로 좁힘과 더불어 배기가스의 배출흐름을 향상시키기 위해 상기 밸브시트부(2c)를 10㎜반지름으로 곡선 형상을 갖추도록 된 차량엔진용 고성능 흡기/배기포트의 구조.The intake port 10 formed in the cylinder head 1 is provided with a valve seat portion 1c, which is an air inflow passage, and an intake valve 2 to form a contact portion between the seat and the valve for maintaining airtightness, and a predetermined amount of air. The air inlet zone z is formed by the ribs 3 so as to flow therein, while the exhaust port 20 for exhausting the exhaust gas generated after combustion is provided with a valve seat 20c which is an exhaust gas discharge passage. In the structure of a high performance intake / exhaust port for a vehicle engine in which the exhaust valve 21 is seated to form a contact portion between the seat and the valve, the inner seat diameter dv formed under the intake port 10 is While the beta (β) ratio was widened to 44.6 mm to 0.164, and the Landweeds (Lw) were narrowed to 1.96 mm, the lip portion 3 was further protruded inward to further narrow the air inflow area z. Inner diameter (dv) formed in the lower part of exhaust port The valve seat 2c has a curved shape with a radius of 10 mm to widen the beta (β) ratio to 0.138 and to narrow the Landweeds (Lw) to 0.138 and to improve the exhaust flow. High performance intake / exhaust port structure for vehicle engine.
KR1019950016604A 1995-06-21 1995-06-21 Structure of high performance intake and exhaustp ort for an automotive engine KR0134244B1 (en)

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KR20030039466A (en) * 2001-11-13 2003-05-22 현대자동차주식회사 Intake port apparatus
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