JP6447104B2 - Intake manifold - Google Patents

Description

  The present invention relates to an intake manifold.

There is provided an intake manifold that has an intake passage for introducing intake air into an engine and into which EGR gas is introduced into the intake passage (see Patent Document 1).
In this intake manifold, four places spaced in the extending direction of one EGR pipe and four intake paths (branch pipes) are connected to each other, and EGR gas supplied to the EGR pipe is supplied with four intake paths. Are distributed and supplied.

JP 2005-120888 A

Since EGR gas flows in one direction through the EGR pipe, there is a difference in the flow rate of EGR gas between the intake passage connected to the upstream side of the EGR gas flow and the intake passage connected to the downstream side of the EGR gas flow. May occur.
For example, when the flow rate of the EGR gas flowing through the EGR pipe is high, the EGR gas flows vigorously toward the downstream side of the EGR pipe, so the EGR gas supplied to the intake passage connected to the upstream side of the EGR gas flow. The flow rate of the EGR gas supplied to the intake passage connected to the downstream side of the EGR gas flow tends to increase compared to the flow rate of the EGR gas.
On the other hand, when the flow rate of the EGR gas flowing through the EGR pipe is low, more EGR gas is supplied to the intake passage connected to the upstream side of the EGR gas flow, and therefore upstream of the EGR gas flow. Compared to the flow rate of EGR gas supplied to the connected intake passage, the flow rate of EGR gas supplied to the intake passage connected downstream of the flow of EGR gas tends to decrease.
Therefore, when the ratio of EGR gas in the intake air (sum of fresh air and EGR gas) supplied to each cylinder is defined as the EGR rate, the EGR rate differs between the cylinders, and NOx is generated. There is room for improvement in controlling.
The present invention has been made in view of such circumstances, and an object of the present invention is to provide an intake manifold that is advantageous in equalizing the EGR rate of each cylinder and suppressing the generation of NOx. .

In order to achieve the above object, an invention according to claim 1 is an intake manifold having a plurality of downstream intake passages connected to an intake port of a cylinder head, into which EGR gas is introduced into the downstream intake passage, An EGR introduction path that extends in a direction intersecting the plurality of downstream intake paths and has an EGR gas supply opening at one end in the extending direction; and an overall length of the EGR introduction path along the EGR introduction path And a communication portion having a cross-sectional area smaller than that of the EGR introduction passage extending through the intake passage and the EGR introduction passage, and one end of the first direction orthogonal to the extending direction of the communication portion is the A passage portion communicates with the EGR introduction passage over the entire length of the EGR introduction passage, and a plurality of downstream communication passages communicated with the plurality of downstream intake passages at the other end in the first direction orthogonal to the extending direction of the communication portion. Opening is provided Is, the EGR introduction path, the cross-sectional area of the side away from the EGR gas supply opening is formed smaller than the cross-sectional area of the side positioned in the EGR gas supply opening, the communicating portion, extending in the communicating portion The width of the passage portion and the opening in the direction and the second direction orthogonal to the first direction is larger on the side away from the EGR gas supply opening than on the side located in the EGR gas supply opening, The cross-sectional area on the side away from the EGR gas supply opening is provided with a larger cross-sectional area than the cross-sectional area on the side positioned on the EGR gas supply opening.
The invention according to claim 2 is characterized in that the EGR introduction path is formed so that the cross-sectional area gradually decreases as the distance from the EGR gas supply opening increases.
The invention according to claim 3 is characterized in that the communication portion is formed so that the cross-sectional area gradually increases as the distance from the EGR gas supply opening increases.
According to a fourth aspect of the present invention, there is provided a cooling unit that cools the intake air with a refrigerant.

According to the first aspect of the present invention, the flow rate of the EGR gas supplied to the intake passage connected to the upstream side of the EGR gas flow and the intake passage connected to the downstream side of the EGR gas flow are supplied. This is advantageous in achieving equalization with the flow rate of EGR gas, and is advantageous in achieving equalization of the EGR rate of each cylinder and suppressing the generation of NOx.
According to the second and third aspects of the invention, it is more advantageous to equalize the flow rate of the EGR gas supplied to the intake passage.
According to the fourth aspect of the present invention, it is advantageous in shortening the intake passage portion connected to the cooling portion as compared with the case where the cooling portion that cools the intake air with the traveling wind is provided separately from the intake manifold. Become. Therefore, it is possible to improve the responsiveness of the engine when the accelerator is depressed, and it is advantageous in reducing the space occupied by the intake passage portion.

It is explanatory drawing which shows the structure of the engine to which the intake manifold of embodiment was applied. It is a perspective view of the intake manifold of an embodiment. FIG. 3 is a sectional view taken along line AA in FIG. 2. FIG. 4 is a sectional view taken along line BB in FIG. 3. It is explanatory drawing which shows the shape of the internal space of an EGR introduction path. It is explanatory drawing which shows the shape of the internal space of an EGR introduction path, and the shape of a communication part.

(Embodiment)
Next, embodiments of the present invention will be described with reference to the drawings.
First, the configuration of an engine to which the intake manifold of the present invention is applied will be described.
In the present embodiment, a case where the engine is a diesel engine will be described. Of course, the present invention can also be applied to a gasoline engine.

  As shown in FIG. 1, an engine 10 includes an engine body 12, an intake passage 14, an exhaust passage 16, a supercharger 18, a low pressure EGR device 20, a high pressure EGR device 22, and an intake manifold according to the present invention. 24.

The engine body 12 includes a cylinder head 1202 and a cylinder block 1204.
A combustion chamber is formed in the cylinder head 1202, and a plurality of cylinders (cylinder chambers) that accommodate pistons are formed in the cylinder block 1204.

The intake passage 14 includes an intake pipe 1402, an intake manifold 24, and an intake port of the engine body 12.
The intake pipe 1402 is provided with an air cleaner 1410, a low pressure throttle 1412, a compressor 1802, and a high pressure throttle 1414 in this order from the upstream side to the downstream side of the intake air.
The exhaust passage 16 includes an exhaust port of the engine body 12, an exhaust manifold 1604, and an exhaust pipe 1602.
The exhaust pipe 1602 is provided with a turbine 1804 and an exhaust gas purification device 26 in this order from the upstream side to the downstream side of the exhaust.

  The supercharger 18 includes a compressor 1802 and a turbine 1804. The turbine 1804 is rotated by the energy of exhaust gas passing through the exhaust pipe 1602, and the compressor 1802 is rotated to compress the intake air in the intake pipe 1402, thereby compressing the high pressure. This is supplied to the engine body 12 as intake air.

The low pressure EGR device 20 returns the exhaust gas discharged from the exhaust gas purification device 26 to the location of the intake pipe 1402 on the upstream side of the compressor 1802 as low pressure EGR gas.
The low-pressure EGR device 20 includes a low-pressure EGR passage 2002 that recirculates the low-pressure EGR gas. In the low-pressure EGR passage 2002, foreign matter contained in the low-pressure EGR gas (welding spatter, slag, catalyst pieces, DPF pieces, etc. during exhaust system manufacturing) ), An air-cooled low-pressure EGR cooler 2006 that cools the low-pressure EGR gas, and a low-pressure EGR valve 2008 that controls the recirculation amount of the low-pressure EGR gas.

The high-pressure EGR device 22 recirculates the exhaust gas taken out from the location of the exhaust pipe 1604 upstream of the turbine 1804 to the intake manifold 24 positioned downstream of the compressor 1802 as EGR gas (high-pressure EGR gas).
The high-pressure EGR device 22 includes a high-pressure EGR passage 2202 that connects the exhaust pipe 1602 and the intake manifold 24 to recirculate EGR gas, and a high-pressure EGR valve 2204.

Next, the intake manifold 24 will be described in detail.
2 is a perspective view of the intake manifold of the embodiment, FIG. 3 is a cross-sectional view taken along line AA in FIG. 2, and FIG. 4 is a cross-sectional view taken along line BB in FIG. FIG. 5 is an explanatory view showing the shape of the internal space of the EGR introduction path, and FIG. 6 is an explanatory view showing the shape of the internal space of the EGR introduction path and the shape of the communication portion.

The intake manifold 24 includes an intake passage 36, an EGR introduction passage 38, and a communication portion 40.
The intake passage 36 introduces intake air into the engine 10.
In the present embodiment, the intake manifold 24 includes an intake inlet portion 42, a cooling portion 44 following the intake inlet portion 42, and an intake outlet portion 46 following the cooling portion 44.
Therefore, the intake passage 36 is constituted by the intake inlet portion 42, the intake passage portion of the cooling portion 44, and the intake outlet portion 46.

The cooling unit 44 cools the intake air with a refrigerant. In the present embodiment, the cooling unit 44 is provided integrally with the intake manifold 24.
The cooling unit 44 is configured to include a plurality of intake passage portions and a plurality of refrigerant passages that are arranged in parallel with each other (not shown).
As shown in FIG. 1, a radiator 28 and an electric water pump 30 are connected to the refrigerant path via a cooling water passage 32, and cooling water is circulated between the radiator 28 and the refrigerant path by the electric pump. . Thus, the cooling water heated by cooling the intake air flowing through the plurality of intake passage portions is cooled by the radiator 28.
In the present embodiment, the cooling unit 44 uses cooling water as the refrigerant, but it goes without saying that various known refrigerant gases and cooling liquids other than the cooling water may be used as the refrigerant.

The intake manifold 24 has a body 34. In the figure, the symbol W indicates the width direction of the body 34, the symbol H indicates the height direction of the body 34, and the symbol L indicates the length direction of the body 34.
As shown in FIG. 2, the intake inlet portion 42 and the intake outlet portion 46 are provided at both ends in the extending direction of the body 34, and the openings of the intake ports of a plurality of cylinders are linearly arranged on the end surface of the cylinder head 1202. It has a horizontally long shape with a width in the other direction and a height smaller than this width.

In the present embodiment, the body 34 is formed from an aluminum casting.
The following effects are produced by forming the body 34 from an aluminum casting.
1) Since it is excellent in corrosion resistance, corrosion due to acidic condensed water generated in the cooling section 44 can be avoided, which is advantageous in improving durability.
2) Since the thermal conductivity is high, it is advantageous for improving the cooling efficiency.
3) Since the surface becomes rough due to the sand core at the time of molding, it is possible to improve the heat transfer coefficient, which is advantageous for improving the cooling efficiency.
4) Since welding and caulking joining are not required as compared with the case where the body 34 is made of sheet metal, it is advantageous in improving reliability by preventing leakage of cooling water due to breakage of the joining portion. .
5) Compared to the case where the body 34 is made of sheet metal, it is advantageous in reducing the size by omitting the space of the joint portion.

  The intake passage portion is a portion where the intake air is cooled by the refrigerant, and extends in the longitudinal direction L of the body 34 inside the body 34 and connects the intake inlet portion 42 and the intake outlet portion 46.

A refrigerant inlet 48 is provided at the other end in the length direction L of the body 34, and a refrigerant outlet 50 is provided at one end in the length direction L of the body 34.
The refrigerant inlet 48 is a portion to which cooling water is supplied, and the outlet of the electric water pump 30 is connected to the refrigerant inlet 48.
The refrigerant outlet portion 50 is a portion for discharging cooling water from the refrigerant passage, and is provided adjacent to the intake downstream side of the intake inlet portion 42 at one end in the longitudinal direction L of the body 34. 50 is connected to the radiator 28.

The refrigerant path extends in the length direction L of the body 34 along the intake passage portion, and connects the refrigerant inlet portion 48 and the refrigerant outlet portion 50.
As the structure of the intake passage and the refrigerant path constituting the cooling unit 44, various well-known structures of the intake passage and the refrigerant path can be adopted.

The intake inlet portion 42 and the intake outlet portion 46 are formed integrally with the body 34.
As shown in FIG. 2, the upstream end of the intake pipe 1402 is connected to the lower portion of the intake inlet portion 42.
As shown in FIGS. 3 and 4, the intake outlet portion 46 includes a pair of upper and lower walls 5402 and 5404 positioned at both ends in the height H direction of the body 34, and a pair of both ends positioned in the width W direction of the body 34. And a flange 5408 attached to the end surface of the cylinder head 1202 is formed at the ends of the walls 5402, 5404, and 5406.

As shown in FIG. 3, the intake outlet 46 includes an upstream outlet 46A that follows the cooling part 44, and a downstream outlet 46B that follows the upstream outlet 46A.
The upstream outlet portion 46 </ b> A is formed on the inner surface of the wall surface 52 of the body 34 where the downstream ends of the plurality of intake passage portions are located, the upper wall 5402, the lower wall 5404, and the pair of side walls 5406. The upstream outlet portion 46A extends in the length L direction while extending in the entire width W direction of the body 34 and decreasing in the height H direction as it approaches the downstream outlet portion 46B. .
As shown in FIG. 4, the downstream outlet 46 </ b> B includes a plurality of downstream intake passages 56 partitioned in the width W direction of the body 34.
The upstream ends of the plurality of downstream intake passages 56 communicate with the downstream ends of the upstream outlet portion 46A, and the downstream ends of the plurality of downstream intake passages 56 are connected to the intake ports that open to the end face of the cylinder head 1202.
As shown in FIG. 3, the upper wall 5402 of the upstream outlet portion 46A is formed of an inclined surface 5402A that gradually approaches the lower wall 5404 as it approaches the downstream outlet portion 46B.
The upper wall 5402 of the downstream outlet 46B is connected to the lower end of the inclined surface 5402A and is formed at the same height as the lower end.

As shown in FIG. 3, the EGR introduction path 38 is disposed above the downstream outlet 46B near the upstream outlet 46A. Specifically, the EGR introduction path 38 extends in the width W direction of the body 34 on the upper wall 5402 on the upstream side of the downstream outlet 46B.
The EGR introduction passage 38 extends in a direction orthogonal to the plurality of downstream intake passages 56 and intersects with the plurality of downstream intake passages 56. At one end portion in the extending direction, as shown in FIGS. 58 is provided.
As shown in FIGS. 4 and 5, the EGR introduction path 38 is formed such that the cross-sectional area on the side away from the EGR gas supply opening 58 is smaller than the cross-sectional area on the side positioned at the EGR gas supply opening 58.
In the present embodiment, the EGR introduction path 38 is formed so that the cross-sectional area gradually decreases as the distance from the EGR gas supply opening 58 increases. More specifically, the EGR introduction path 38 is formed such that the height gradually decreases as the distance from the EGR gas supply opening 58 increases, and the width along the length L direction of the body 34 gradually decreases.
5 and 6, the broken line indicates the outline of the EGR introduction path 38 when the EGR introduction path 38 is formed with a uniform cross section along the extending direction.

The communication part 40 is a part that communicates the intake path 36 and the EGR introduction path 38. In the present embodiment, the communication portion 40 includes a passage portion 41A extending along the width W direction along the EGR introduction passage 38 below the EGR introduction passage 38 and above each downstream intake passage 56, and the passage portion 41A. And a plurality of openings 41 </ b> B communicating with each downstream intake passage 56.
Therefore, the communication part 40 supplies EGR gas from the upper part to the lower part inside the intake outlet part 46.
As shown in FIGS. 4 and 6, the passage portion 41 </ b> A is provided with a larger cross-sectional area on the side away from the EGR gas supply opening 58 than the cross-sectional area on the side positioned at the EGR gas supply opening 58. .
In the present embodiment, the passage portion 41 </ b> A is formed so that the cross-sectional area gradually increases as the distance from the EGR gas supply opening 58 increases. More specifically, the width of the passage portion 41A along the length L direction of the body 34 is formed so as to gradually increase as the distance from the EGR gas supply opening 58 increases. Correspondingly, the width of the opening 41B along the length L direction of the body 34 is formed so as to gradually increase as the distance from the EGR gas supply opening 58 increases.

Next, the function and effect will be described.
During operation of the engine 10, intake air is introduced from the intake inlet portion 42 of the intake manifold 24 into the cooling portion 44.
At this time, the high-pressure EGR valve 2204 is opened, and the EGR gas introduced from the EGR gas supply opening 58 is supplied from the upper part to the lower part in the intake outlet 46 through the communication part 40 from the EGR introduction passage 38. .
The intake air cooled by passing through the intake passage portion of the cooling portion 44 is mixed with the EGR gas supplied from the communication portion 40 and introduced into each intake port from the plurality of downstream intake passages 56.

When the flow rate of the EGR gas introduced into the EGR introduction path 38 from the EGR gas supply opening 58 is high, the EGR gas flows vigorously through the EGR introduction path 38, and therefore the downstream intake path connected to the upstream side of the EGR gas flow. Compared to the flow rate of the EGR gas supplied to 56, the flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the EGR gas flow tends to increase.
In the present embodiment, the EGR introduction path 38 is formed so that the cross-sectional area on the side away from the EGR gas supply opening 58 is smaller than the cross-sectional area on the side positioned at the EGR gas supply opening 58, so that the EGR gas flow The flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the gas is suppressed.
Therefore, the flow rate of EGR gas supplied to the downstream intake passage 56 connected to the upstream side of the EGR gas flow and the flow rate of EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the EGR gas flow. This is advantageous in achieving equalization.

On the other hand, when the flow rate of the EGR gas introduced into the EGR introduction passage 38 from the EGR gas supply opening 58 is low, more EGR gas is supplied to the downstream intake passage 56 connected to the upstream side of the EGR gas flow. Therefore, compared with the flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the upstream side of the EGR gas flow, the EGR gas flow is supplied to the EGR gas flow connected to the downstream side of the EGR gas flow. The flow rate of the EGR gas tends to decrease.
In the present embodiment, the communication portion 40 is provided with a larger cross-sectional area on the side farther from the EGR gas supply opening 58 than the cross-sectional area on the side located at the EGR gas supply opening 58. The flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the flow is increased.
Therefore, the flow rate of EGR gas supplied to the downstream intake passage 56 connected to the upstream side of the EGR gas flow and the flow rate of EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the EGR gas flow. This is advantageous in achieving equalization.

  Therefore, regardless of the flow rate of the EGR gas introduced into the EGR introduction passage 38 from the EGR gas supply opening 58, the flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the upstream side of the EGR gas flow , The flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the EGR gas flow can be equalized, the EGR rate of each cylinder can be equalized, and the generation of NOx can be suppressed. This is advantageous.

Further, in the present embodiment, the EGR introduction path 38 is formed so that the cross-sectional area gradually decreases as the distance from the EGR gas supply opening 58 increases.
Therefore, when the flow rate of the EGR gas introduced into the EGR introduction path 38 from the EGR gas supply opening 58 is high, the flow rate of the EGR gas supplied to the downstream intake path 56 connected to the upstream side of the EGR introduction path 38; This is more advantageous in achieving equalization with the flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the EGR introduction passage 38.

In the present embodiment, the communication portion 40 is formed so that the cross-sectional area gradually increases as the distance from the EGR gas supply opening 58 increases.
Therefore, when the flow rate of the EGR gas introduced into the EGR introduction passage 38 from the EGR gas supply opening 58 is low, the flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the upstream side of the EGR gas flow, This is more advantageous in achieving equalization with the flow rate of the EGR gas supplied to the downstream intake passage 56 connected to the downstream side of the EGR gas flow.

Further, in the present embodiment, the intake manifold 24 includes the cooling unit 44 that cools the intake air with the refrigerant, so that a cooling unit (intercooler) that cools the intake air with running air is provided separately from the intake manifold. This is advantageous in shortening the intake passage portion connected to the cooling section.
Therefore, it is possible to improve the responsiveness of the engine when the accelerator is depressed, and it is advantageous in reducing the space occupied by the intake passage portion.

In the present embodiment, the case where the EGR introduction path 38 communicates with the downstream outlet 46B has been described. That is, the EGR introduction path 38 includes a plurality of partitions that are partitioned from each other in the width W direction of the body 34. Although the case where it communicates with the downstream intake passage 56 has been described, the present invention is similarly applied to the case where the EGR introduction passage 38 communicates with the upstream outlet 46A that is a single space that is not partitioned from each other. Is possible.
Moreover, when the communicating part 40 communicates with the downstream outlet part 46B as in the present embodiment, the communicating part 40 may be configured with only a plurality of openings 41B. In addition, when the communicating part 40 communicates with the upstream outlet part 46A, the communicating part 40 is formed only by the passage part 41A.
Further, in the embodiment, the case where the intake manifold 24 is configured integrally with the cooling unit 44 has been described. However, the cooling unit 44 is configured separately from the intake manifold 24 and is disposed upstream of the intake manifold 24. It may be arranged.

10 Engine 24 Intake manifold 36 Intake passage 38 EGR introduction passage 40 Communication portion 44 Cooling portion 56 Downstream intake passage (intake passage)
58 EGR gas supply opening

Claims (4)

An intake manifold having a plurality of downstream intake passages connected to an intake port of a cylinder head , wherein EGR gas is introduced into the downstream intake passages;
An EGR introduction path extending in a direction intersecting with the plurality of downstream intake paths and having an EGR gas supply opening provided at one end in the extending direction;
A communication portion extending along the EGR introduction path over the entire length of the EGR introduction path and having a smaller cross-sectional area than the EGR introduction path communicating the intake passage and the EGR introduction path;
One end of the first direction orthogonal to the extending direction of the communicating portion is a passage portion communicating with the EGR introducing path over the entire length of the EGR introducing path, and the first direction orthogonal to the extending direction of the communicating portion. The other end of the direction is provided with a plurality of openings communicating with the plurality of downstream intake passages,
The EGR introduction path is formed such that a cross-sectional area on the side away from the EGR gas supply opening is smaller than a cross-sectional area on the side located at the EGR gas supply opening,
The communication portion is configured such that the width of the passage portion and the opening in the extending direction of the communication portion and the second direction orthogonal to the first direction is greater than the side where the EGR gas supply opening is positioned. The side away from the supply opening is enlarged, and the cross-sectional area on the side away from the EGR gas supply opening is provided with a larger cross-sectional area than the side area located on the EGR gas supply opening.
Intake manifold characterized by that. The EGR introduction path is formed so that the cross-sectional area gradually decreases as the distance from the EGR gas supply opening increases.
The intake manifold according to claim 1. The communication portion is formed so that the cross-sectional area gradually increases as the distance from the EGR gas supply opening increases.
The intake manifold according to claim 1 or 2, characterized in that A cooling unit for cooling the intake air with a refrigerant;
The intake manifold according to any one of claims 1 to 3, wherein the intake manifold is provided.

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