JP2014132163A - Intercooler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent deterioration of an engine output by reducing a pressure loss of an intercooler inserted in a suction port of a cylinder head and cooling intake air.SOLUTION: An intercooler 1 can cool intake air near a cylinder while avoiding such a failure that the intake air receives heat from a cylinder head 3 by a water-cooling pipe 5 inserted and arranged in a suction port 4 of the cylinder head 3, so as to cool the intake air at high efficiency. Also, in the intercooler 1, a corrugated fin is not used for a portion for passing the intake air, and therefore, a pressure loss of the intake air due to the corrugated fin does not occur. Therefore, the pressure loss of the intake air can be restrained so as to prevent deterioration of an output of an engine 2. Furthermore, EGR gas can be cooled at high efficiency near the cylinder by the water-cooling pipe 5 arranged in the suction port 4, so as to increase an amount of the EGR gas and improve fuel consumption by the high EGR gas.

Description

  The present invention relates to a water-cooled intercooler (intake cooling device) that is inserted into an intake port of a cylinder head.

An intercooler has been proposed in which a water-cooled pipe is inserted into an intake port of an engine cylinder head and the intake air passing through the water-cooled pipe is cooled (for example, see Patent Document 1).
By inserting and arranging the water-cooled pipe inside the intake port of the cylinder head, the intake air can be cooled to the vicinity of the cylinder while preventing the intake air from being heated by heat received from the cylinder head. Air can be cooled with high efficiency.

However, in the well-known technique disclosed in Patent Document 1, a corrugated fin is provided at a passage portion of the intake air in order to enhance heat exchange between the cooling water and the intake air.
Since the corrugated fin is provided with a metal thin plate in a wave shape to increase the contact area with the intake air, the corrugated fin comes into contact with the intake air with high efficiency, thereby increasing the pressure loss of the intake air.
In particular, when the intake air amount increases at high engine speeds or high loads, the pressure loss due to the corrugated fins increases, resulting in a problem of lowering the engine output.

Japanese Unexamined Patent Publication No. 2012-219657

  The present invention has been made in view of the above problems, and an object of the present invention is to provide an intercooler that can reduce the pressure loss and maintain the high output of the engine.

Since the intercooler of the present invention does not use corrugated fins at the intake passage portions, intake air pressure loss due to the corrugated fins does not occur. For this reason, the pressure loss of the intake air by an intercooler can be suppressed, and the engine output fall by an intercooler can be prevented.
That is, according to the present invention, the intake air can be cooled to the vicinity of the cylinder while avoiding the problem that the intake air is received from the cylinder head by the water cooling pipe inserted and arranged in the intake port of the cylinder head. While being able to cool, the pressure loss of the intake air by an intercooler can be prevented, and an engine can be maintained at high output.

It is explanatory drawing of the intercooler assembled | attached to the engine. (A) The perspective view of an intercooler, (b) It is sectional drawing of a water cooling pipe (Example 1). (A) It is explanatory drawing of the intercooler provided in the intake outlet of the intake manifold, (b) It is explanatory drawing of the intercooler assembled | attached to the intake manifold (Example 1). (Example 2) which is explanatory drawing of the intercooler assembled | attached to the engine. (A) Perspective view of intercooler, (b) It is principal part sectional drawing of an intercooler (Example 2). (A), (b) It is a perspective view of an intercooler (Example 2). (A) Explanatory drawing which opened eddy current control valve, (b) It is explanatory drawing which closed the eddy current control valve (Example 3). (Example 5) which is explanatory drawing of the intercooler assembled | attached to the engine.

  [Description of Embodiments] [Mode for carrying out the invention] will be described in detail below.

  The following examples show specific examples, and it goes without saying that the present invention is not limited to the examples.

[Example 1]
Embodiment 1 will be described with reference to FIGS.
The intercooler 1 is used for an intake system of a vehicle travel engine 2 and includes a water cooling pipe 5 inserted and disposed in an intake port 4 of a cylinder head 3 and a piping joint 6 for delivering cooling water. .

  The water cooling pipe 5 is cooled by cooling water and cools the intake air passing through the inside of the water cooling pipe 5 (intake sucked into the cylinder). As shown in FIG. The pipe material in which 5a is formed is provided in a pipe shape.

A specific example of the water cooling pipe 5 will be described with reference to FIG.
The water cooling pipe 5
(I) A flat tube through which cooling water flows is formed in a half-pipe shape (substantially U-shaped, etc.)
(Ii) Two semi-pipe-shaped flat tubes are joined and provided in a pipe shape.

And
(I) The cooling water flowing from the intake upstream to the intake downstream (insertion back side) is caused to flow through the cooling water passage 5a of one flat tube,
(Ii) The cooling water flowing from the intake air downstream side to the intake air upstream side (insertion inlet side) flows through the cooling water channel 5a of the other flat tube.
A cooling water U-turn portion (header portion) that guides the cooling water from one flat tube to the other flat tube is provided at the end of the water cooling pipe 5 (the end on the insertion back side).

The piping joint 6 is
(I) an inlet pipe 6a that receives supply of cooling water from the outside;
(Ii) An outlet pipe 6b that guides the cooling water that has passed through the water cooling pipe 5 to the outside.

And
(I) The inlet pipe 6a is connected to the one flat tube described above inside the pipe joint 6,
(Ii) The outlet pipe 6 b is connected to the other flat tube described above inside the pipe joint 6.

  The cooling water supplied to the intercooler 1 circulates between the intercooler 1 and a radiator (radiator) mounted on a portion that receives vehicle traveling wind (such as the interior of the front grill of the vehicle). A water pump for circulating and driving the cooling water is provided in the circulation path. The cooling water may be used in common with the engine cooling water, or may be a cooling water having a circulation system different from the engine cooling water.

Intercooler 1
(A) As shown in FIG. 2 (a), one water-cooled pipe 5 may be provided with one piping joint 6,
(B) As shown in FIG. 3B, one piping joint 6 may be provided for a plurality of water-cooled pipes 5 (in the drawing, two water-cooled pipes 5 are connected to one pipe joint 6). An example is provided).

The attachment means of the intercooler 1 is not limited,
(A) As shown in FIG. 3 (a), the intercooler 1 may be provided independently of the intake manifold 7 and connected to the outlet portion of the intake manifold 7.
(B) As shown in FIG. 3 (b), the intercooler 1 is assembled to the intake manifold 7, the water cooling pipe 5 is exposed to the outside from the surge tank 7 a of the intake manifold 7, and the intake manifold 7 is fixed to the cylinder head 3. In this case, the water cooling pipe 5 may be provided so as to be inserted into the intake port 4.

  The intercooler 1 for each cylinder shown in FIG. 2A is coupled to the coupling base 1a shown in FIG. 3A, and the coupling base 1a on which the plurality of intercoolers 1 are mounted is the cylinder head 4. Between the intake manifold 7 and the intake manifold 7.

The intercooler 1 of the first embodiment does not use corrugated fins at the intake passage portion. Since the corrugated fin is provided with a metal thin plate in a wave shape to increase the contact area with the intake air, the pressure loss of the intake air increases.
On the other hand, in the first embodiment, the pressure loss of the intake air due to the corrugated fin does not occur. For this reason, the intercooler 1 of the first embodiment can suppress the pressure loss of the intake air as compared with the prior art.

As described above, the intercooler 1 according to the first embodiment avoids the problem that the intake air is received from the cylinder head 3 by the water-cooled pipe 5 that is inserted into the intake port 4 of the cylinder head 3 and sucks the air to the vicinity of the cylinder. Since the intake air can be cooled with high efficiency, the pressure loss of the intake air in the intercooler 1 can be suppressed, and the high output of the engine 2 can be maintained.
In addition, since the EGR gas can be cooled to the vicinity of the cylinder with high efficiency by the water cooling pipe 5 inserted and arranged in the intake port 4, the amount of EGR gas can be increased, and the fuel consumption can be improved by the high EGR gasification. become.

[Example 2]
A second embodiment will be described with reference to FIGS. In the following embodiments, the same reference numerals as those in the first embodiment denote the same functional objects.
In the second embodiment, an inclined slope 11 is provided on the inner side of the water-cooled pipe 5 on the intake downstream side to restrict the inside of the pipe toward the intake downstream side.
The slope 11 restricts the intake air entering the cylinder at the intake outlet of the water-cooled pipe 5, so that the intake air flow can be strengthened to increase the flow velocity of the intake air entering the cylinder.

  Here, since the water cooling pipe 5 is inserted into the intake port 4, the distance from the intake outlet of the water cooling pipe 5 to the intake valve 12 is short. For this reason, the strong intake flow whose flow velocity is increased by the throttle effect of the slope 11 can be sucked into the cylinder while maintaining the high flow velocity.

In particular, in the second embodiment, as shown in FIG. 4, the strong intake flow whose flow velocity is increased by the throttle effect of the slope 11 is directed to the gap α formed between the intake valve 12 and the valve seat 13. That is, a strong intake flow by the slope 11 is blown out aiming at the gap α.
For this reason, the strong intake flow whose flow velocity is increased by the slope 11 can be more effectively sucked into the cylinder while maintaining the high flow velocity.

As described above, the second embodiment employs a configuration in which the strong intake flow having the flow velocity increased by the slope 11 is directly put into the cylinder, so that the vortex flow (tumble flow or swirl flow) in the cylinder can be enhanced.
As a result, the combustion speed of the air-fuel mixture in the cylinder can be increased, and fuel consumption can be improved.

The position where the slope 11 is provided is not limited to the vertical position shown in FIG.
(A) As shown to Fig.6 (a), you may provide the slope 11 in the horizontal position of the water cooling pipe 5,
(B) As shown in FIG. 6B, the slope 11 may be provided on the entire circumference of the water-cooled pipe 5.

[Example 3]
A third embodiment will be described with reference to FIGS.
In the third embodiment, a vortex flow control valve 21 (such as a tumble flow control valve or a swirl flow control valve) is provided at the intake port of the water-cooled pipe 5.
The vortex control valve 21 changes the passage area of the intake port of the water-cooled pipe 5 to generate a vortex in the cylinder.

Specifically, the vortex control valve 21 is
(A) During high rotation of the engine 2 (when the intake air amount is large), as shown in FIG. 7A, the intake port of the water-cooled pipe 5 is opened to suppress the generation of intake resistance,
(A) When the engine 2 is running at a low speed (when the intake air amount is small), the intake port of the water-cooled pipe 5 is closed and the intake air is provided by the throttle opening 21a provided in the vortex control valve 21, as shown in FIG. In this case, a strong intake flow is generated by narrowing down, and a vortex flow is generated in the cylinder even when the intake amount is small.

Inside the water-cooled pipe 5, as shown in FIG. 8, the intake air flow is enhanced to guide the intake air flow that is throttled by the vortex control valve 21 (strong intake air flow that has passed through the throttle opening 21 a) to the intake outlet of the water-cooled pipe 5. A plate 22 is provided.
Thus, the strong intake air flow that has passed through the throttle opening 21a is blown out from the water-cooled pipe 5 without being attenuated.

  Here, since the water cooling pipe 5 is inserted and arranged in the intake port 4 as described above, the distance from the intake outlet of the water cooling pipe 5 to the intake valve 12 is short. For this reason, the strong intake flow maintained by the intake flow reinforcement plate 22 (strong intake flow blown out from the water-cooled pipe 5) can be sucked into the cylinder while maintaining a high flow velocity.

In particular, the intake flow reinforcement plate 22 of the third embodiment directs the strong intake flow that has passed through the partition passage by the intake flow reinforcement plate 22 to the gap α formed between the intake valve 12 and the valve seat 13. That is, a strong intake flow is blown out aiming at the gap α.
As a result, the strong intake flow blown out from the water-cooled pipe 5 is sucked into the cylinder while maintaining a high flow rate by the throttling effect of the vortex control valve 21 and the flow rate maintaining effect by the intake flow reinforcing plate 22. Can do.

As described above, the third embodiment employs a configuration in which the strong intake flow whose flow velocity is increased by the vortex control valve 21 and the intake flow reinforcing plate 22 is directly blown into the cylinder. Stream and swirl flow).
As a result, the combustion speed of the air-fuel mixture in the cylinder can be increased, and fuel consumption can be improved.

On the other hand, in the third embodiment, the airflow reinforcing plate 22 increases the contact area of the intake air. Thus, the intake air cooling plate 22 is provided by a thin plate having excellent thermal conductivity such as aluminum as in the case of the water-cooled pipe 5, whereby the intake air cooling performance can be enhanced.
Further, the intake flow reinforcing plate 22 is provided across the interior of the water-cooled pipe 5. For this reason, the rigidity of the water-cooled pipe 5 can be increased, and as a result, the strength of the intercooler 1 can be improved.

  The intercooler 1 is preferably used for an intake system using an intake supercharger (turbocharger, supercharger, etc.), but is not limited, and is used for an intake system not equipped with an intake supercharger. You may provide so that EGR gas etc. may be cooled.

  The present invention may be applied to a gasoline engine or a diesel engine.

1 Intercooler 3 Cylinder head 4 Intake port 5 Water cooling pipe

Claims (5)

A water-cooled pipe (5) inserted and arranged in the intake port (4) of the cylinder head (3) is provided. The water-cooled pipe (5) is cooled by cooling water and passes through the water-cooled pipe (5). In the water-cooled intercooler (1) that cools
This intercooler (1) is an intercooler characterized in that corrugated fins provided with corrugated thin plates are not used as intake passage portions. Intercooler (1) according to claim 1,
An intercooler characterized in that an inclined slope (11) for restricting the inside of the pipe toward the intake downstream side is provided inside the water cooling pipe (5) on the intake downstream side. Intercooler (1) according to claim 2,
The slope (11) directs the strong intake flow whose flow velocity is increased by the throttle effect of the slope (11) to the gap (α) formed between the intake valve (12) and the valve seat (13). Characteristic intercooler. In the intercooler (1) according to any one of claims 1 to 3,
The intake port of the water-cooled pipe (5) is provided with a vortex control valve (21) that changes the passage area of the intake port of the water-cooled pipe (5) to generate a vortex in the engine cylinder,
Inside the water cooling pipe (5), there is provided an intake flow reinforcing plate (22) for guiding the intake air flow restricted by the vortex control valve (21) to the intake outlet of the water cooling pipe (5). Characteristic intercooler. Intercooler (1) according to claim 4,
The intake air flow reinforcing plate (22) is a gap (α) formed between the intake valve (12) and the valve seat (13) by causing the strong intake air flow that has passed through the partition passage by the intake air flow reinforcing plate (22). Intercooler characterized by being directed to.

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