CN216975062U

CN216975062U - Air inlet mixing device for internal combustion engine

Info

Publication number: CN216975062U
Application number: CN202220851086.9U
Authority: CN
Inventors: 龚熠敏; 马谦
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2022-04-13
Filing date: 2022-04-13
Publication date: 2022-07-15
Anticipated expiration: 2032-04-13

Abstract

The utility model provides an air inlet mixing device of an internal combustion engine, which comprises: a mixer (110) having a mixer body (111) forming a mixing chamber therein and provided with an off-gas inlet (112) opening into the mixing chamber; a recirculation exhaust valve (120) having a valve body (121) forming a valve chamber (122) inside, provided with an intake port (123) and an exhaust port (124) opening into the valve chamber (122), and fixed to the mixer (110) so that the exhaust port (124) communicates with the exhaust inlet (112); and a heat-conducting member (130), the heat-conducting member (130) being in surface contact with the mixer (110) on one side so as to form a first heat exchange area (HEA1) on the outer surface of the mixer (110), and in surface contact with the recirculation off-gas valve (120) on the other side so as to form a second heat exchange area (HEA2) on the outer surface of the recirculation off-gas valve (120).

Description

Air inlet mixing device for internal combustion engine

Technical Field

The utility model relates to the field of internal combustion engines, in particular to an internal combustion engine air inlet mixing device for an internal combustion engine.

Background

With the development of internal combustion engine technology and the increasing emphasis on environmental protection, emission reduction technology is being increasingly applied to internal combustion engines (e.g., gas-type internal combustion engine)Engines, fuel-fired internal combustion engines, etc.). Exhaust Gas Recirculation (EGR) is a typical emission reduction technique applied to internal combustion engines. In internal combustion engines using exhaust gas recirculation, a portion of the engine exhaust is returned as recirculated exhaust gas to the intake path of the engine for introduction into the engine after mixing with fresh gas from the surrounding atmosphere (and possibly a fuel gas source). This dilutes oxygen in the engine intake and provides a gas inert to combustion to absorb the heat of combustion and thereby reduce engine cylinder peak temperatures, such as Nitrogen Oxides (NO)_X) Oxygen-rich high-temperature conditions required for the generation of such harmful gas components are broken, and thus the harmful gas components in the exhaust gas of the internal combustion engine are reduced. In addition, in a low temperature environment such as winter, the temperature of the fresh gas tends to be low, which may cause the lubricating oil to fail to form an oil film due to low temperature and thus cause the wear of the internal combustion engine to be increased if the fresh gas is directly fed into the internal combustion engine, and the temperature of the fresh gas may be increased by mixing the recirculated exhaust gas with the fresh gas, so that the generation of the oil film and the effective lubrication of the internal combustion engine may be ensured. It will be appreciated that the achievement of the various effects described above depends on the degree of homogeneity of the mixing of the fresh gas and the recirculated exhaust gas, which is linked to the temperature difference between the two and therefore the heat exchange efficiency. The heat exchange between the recirculated exhaust gas and the fresh gas is often promoted by the direct contact between the recirculated exhaust gas valve and the mixer in the prior art, however, due to the existence of manufacturing tolerance, an air gap inevitably exists between the recirculated exhaust gas valve and the mixer, and the air is a poor thermal conductor, so the heat exchange efficiency between the recirculated exhaust gas and the fresh gas in the prior art is low, the temperature difference is large, and therefore, the mixture is difficult to be uniform, and the effect of the exhaust gas recirculation technology is adversely affected. In order to eliminate the air gap, it is necessary to improve the manufacturing accuracy of the recirculated exhaust gas valve and the mixer, which inevitably increases the manufacturing, assembling and maintenance costs of the recirculated exhaust gas valve and the mixer significantly.

Therefore, there is a need in the art for a solution that improves the heat exchange efficiency of the recirculated exhaust gas with the fresh gas in a simple and reliable manner.

SUMMERY OF THE UTILITY MODEL

In order to solve the above-mentioned problems in the prior art, the present invention proposes an improved intake air mixing device for an internal combustion engine, comprising: a mixer having a mixer body forming a mixing chamber therein and provided with an exhaust gas inlet opening into the mixing chamber; a recirculation exhaust valve having a valve body forming a valve chamber therein, provided with an intake port and an exhaust port opening into the valve chamber, and fixed to the mixer such that the exhaust port communicates with the exhaust inlet; and a heat-conducting member in surface contact with the mixer on one side to form a first heat exchange area on an outer surface of the mixer, and in surface contact with the recirculated exhaust gas valve on the other side to form a second heat exchange area on an outer surface of the recirculated exhaust gas valve.

According to an alternative embodiment of the present invention, the heat-conducting member is in surface contact with the mixer main body and the valve body, respectively, such that the first heat exchange region is formed on the outer surface of the mixer main body and the second heat exchange region is formed on the outer surface of the valve body.

According to an alternative embodiment of the utility model, the second heat exchange area is formed in a recess recessed from an outer surface of the valve body.

According to an alternative embodiment of the utility model, the valve chamber defines an air flow path extending from the inlet port to the outlet port, a third heat exchange area being formed on the inner surface of the valve body at a position opposite the second heat exchange area, and wherein the third heat exchange area is positioned such that the air flow path changes direction; and/or, the third heat exchange region is positioned spaced apart from the exhaust port; and/or the recirculated exhaust gas valve is provided with a plurality of exhaust ports, and the gas flow path is dispersed at the third heat exchange area into a plurality of branches extending toward the plurality of exhaust ports.

According to an alternative embodiment of the utility model, the third heat exchange area is formed in a recess recessed from an inner surface of the valve body.

According to an alternative embodiment of the utility model, the third heat exchange area is positioned in alignment with the air inlet.

According to an alternative embodiment of the utility model, the mixer body is provided with a boss on its outer surface, which boss extends towards the valve body and terminates in an end surface from which the first heat exchange area is formed.

According to an alternative embodiment of the utility model, the end surface is shaped in such a way as to conform to the outer surface of the valve body, so that a gap extending along the end surface is formed between the end surface and the outer surface of the valve body, the heat-conducting member being filled in the gap.

According to an alternative embodiment of the utility model, the mixer is provided with a duct for the flow of a heat exchange fluid, the duct having a portion adjacent to the first heat exchange area and a portion adjacent to the mixing chamber.

According to an alternative embodiment of the utility model, the heat-conducting member comprises one or more layers of sheets of heat-conducting material stacked together.

The utility model may be embodied in the form of exemplary embodiments shown in the drawings. It is to be noted, however, that the drawings are designed solely for purposes of illustration and that any variations which come within the teachings of the utility model are intended to be included within the scope of the utility model.

Drawings

The drawings illustrate exemplary embodiments of the utility model. These drawings should not be construed as necessarily limiting the scope of the utility model, wherein:

fig. 1 is a schematic perspective view of an internal combustion engine intake air mixing device for an internal combustion engine according to the present invention;

FIG. 2 is another schematic perspective illustration of the engine intake air mixing device of FIG. 1 with a recirculation exhaust valve of the engine intake air mixing device partially cut away; and

fig. 3 is a schematic perspective view of a mixer of the intake air mixing device for the internal combustion engine shown in fig. 1 and 2.

Detailed Description

Further features and advantages of the present invention will become apparent from the following description, which proceeds with reference to the accompanying drawings. Exemplary embodiments of the utility model are illustrated in the drawings and the various drawings are not necessarily drawn to scale. This invention may, however, be embodied in many different forms and should not be construed as necessarily limited to the exemplary embodiments set forth herein. Rather, these exemplary embodiments are provided only to illustrate the present invention and to convey the spirit and substance of the utility model to those skilled in the art.

The present invention is directed to an improved internal combustion engine intake mixing device that is installed on an intake path of an internal combustion engine (e.g., a gas-type internal combustion engine, a fuel-type internal combustion engine, etc.) and is adapted to mix a portion of exhaust gas discharged from the internal combustion engine (referred to herein as recirculated exhaust gas) with fresh gas to generate a mixed gas that is to be delivered into the internal combustion engine such that chemical energy contained in the mixed gas is converted into mechanical energy of a piston, a crankshaft, etc. in the internal combustion engine. The fresh gas generally comprises fresh air (e.g., air from the atmosphere and turbocharged), and in the case of a gas-fired internal combustion engine, also comprises fuel gas (e.g., natural gas, methane, etc.) from a fuel gas source. In addition, as previously mentioned, the degree of uniformity of mixing of the fresh gas with the recirculated exhaust gas directly affects the operating efficiency of the internal combustion engine. The internal combustion engine intake air mixing device according to the utility model can reduce the temperature difference between the fresh air and the recirculated exhaust gas through the novel design, so that the fresh air and the recirculated exhaust gas can be mixed together more uniformly, and the uniformity of the temperature of the mixed gas can be improved, which helps to ensure that the internal combustion engine has higher working efficiency.

An alternative but non-limiting embodiment of an internal combustion engine intake air mixing device according to the present invention is described in detail below with reference to the various drawings.

Referring to fig. 1, there is shown a schematic perspective view of an internal combustion engine intake air mixing device for an internal combustion engine according to the present invention. As shown in fig. 1, the engine intake air mixing device 100 generally includes a mixer 110 and a recirculated exhaust gas valve 120. The mixer 110 comprises a mixer body 111 forming internally a mixing chamber for mixing fresh gas with recirculated exhaust gas, which mixer body 111 may be part of the housing of the mixer 110, and the mixer 110 is further provided with a fresh gas inlet opening into the mixing chamber (i.e. in gaseous communication with the mixing chamber), an exhaust gas inlet opening and a mixed gas outlet opening, wherein, in case the internal combustion engine is a fuel-fired internal combustion engine, the fresh gas may contain fresh air from the atmosphere, which, in case of need, may be pre-compressed; in the case where the internal combustion engine is a gas-type internal combustion engine, the fresh gas may contain, in addition to the fresh air, a fuel gas (e.g., natural gas, methane, etc.) from a fuel gas source, that is, the fresh gas may be a mixed gas of the fresh air and the fuel gas. In operation, fresh gas is fed into the mixing chamber through the fresh gas inlet and a portion of the exhaust gas of the internal combustion engine is fed into the mixing chamber through the exhaust gas inlet as recirculated exhaust gas, whereupon the fresh gas and the recirculated exhaust gas are mixed in the mixing chamber to produce a mixed gas which can then be discharged from the mixing chamber through the mixed gas outlet and fed into the internal combustion engine. A recirculated exhaust gas valve 120 is provided at the exhaust gas inlet 112 (shown in fig. 3) of the mixer 110 to adjust the amount of recirculated exhaust gas entering the exhaust gas inlet 112, for example, according to a control signal of an Electronic Control Unit (ECU).

Referring to fig. 2, there is shown a schematic perspective view of an internal combustion engine intake mixing arrangement for an internal combustion engine according to the present invention, with the recirculation exhaust valve 120 partially cut away. As shown in fig. 2, the recirculation exhaust valve 120 includes a valve body 121 defining a valve chamber 122 therein, the valve body 121 may be part of the housing of the recirculated exhaust valve 120, and the recirculated exhaust valve 120 is provided with an inlet port 123 and an outlet port 124 that open into the valve cavity 122 (i.e., are in gaseous communication with the valve cavity 122), wherein the gas inlet 123 is adapted to receive recirculated exhaust gas as part of the exhaust of the internal combustion gases, the exhaust port 124 is used to exhaust the recirculated exhaust gas, and the valve chamber 122 is used to direct the recirculated exhaust gas from the inlet port 123 to the exhaust port 124, that is, the valve chamber 122 places the inlet port 123 in gaseous communication with the outlet port 124, thereby defining a flow path P (shown in phantom in figure 2) for the recirculated exhaust gas extending from the inlet port 123 to the outlet port 124, wherein the recirculated exhaust gas entering the valve chamber 122 from the inlet 123 will flow along the gas flow path P to the outlet 124. The recirculated exhaust gas valve 120 also includes a valve spool 125 disposed in the valve chamber 122 (i.e., disposed on the gas flow path P) for controlling the amount of recirculated exhaust gas flowing along the gas flow path P. Returning to fig. 1, the recirculated exhaust valve 120 is secured to the mixer 110 (e.g., via a flange 126 protruding from the valve body 121) such that an exhaust port 124 of the recirculated exhaust valve 120 is in gaseous communication with the exhaust inlet 112 of the mixer 110, preferably in isolated/sealed manner with respect to the exterior. In operation, a portion of the engine exhaust is delivered as recirculated exhaust gas to the intake port 123 of the recirculated exhaust valve 120 and enters the valve cavity 122 from the intake port 123, the recirculated exhaust gas in turn flows along the gas flow path P toward the exhaust port 124, while the valve spool 125 controls (e.g., adjusts in accordance with control signals of the electronic control unit) the amount of recirculated exhaust gas such that a controlled amount of recirculated exhaust gas flows to the exhaust port 124 and in turn from the exhaust port 124 into the exhaust gas inlet 112 of the mixer 110, and then the controlled amount of recirculated exhaust gas enters the mixing chamber of the mixer 110 through the exhaust gas inlet 112 to be mixed with fresh gas.

As shown in fig. 2, the internal combustion engine intake air mixing device 100 further includes a heat conductive member 130 disposed between the mixer 110 and the recirculated exhaust gas valve 120, the heat conductive member 130 being a good conductor of heat and being attached to the outer surface of the mixer 110 on one side, i.e., the heat conductive member 130 being in surface contact with the outer surface of the mixer 110 on the one side, such that a heat exchange region (hereinafter referred to as a first heat exchange region HEA1) that exchanges heat with the heat conductive member 130 is formed on the outer surface of the mixer 110, and the heat conductive member 130 being attached to the outer surface of the recirculated exhaust gas valve 120 on the other side, i.e., the heat conductive member 130 being in surface contact with the outer surface of the recirculated exhaust gas valve 120 on the one side, such that a heat exchange region (hereinafter referred to as a second heat exchange region HEA2) that exchanges heat with the heat conductive member 130 is formed on the outer surface of the recirculated exhaust gas valve 120. In this configuration, the mixer 110 and the recirculated exhaust gas valve 120 can perform efficient heat exchange through the heat conductive member 130. Specifically, the temperature of the recirculated exhaust gas tends to be high and the temperature of the fresh gas tends to be low, and by the heat exchange, the mixer 110 can be heated by the heat of the recirculated exhaust gas in the recirculated exhaust gas valve 120, and the mixer 110 will in turn heat the fresh gas therein, which can reduce the temperature of the recirculated exhaust gas and increase the temperature of the fresh gas, which can reduce the temperature difference therebetween, which helps to mix the two together more uniformly and improve the uniformity of the temperature of the generated mixed gas, which helps to control the temperature of the mixed gas delivered to the internal combustion engine more accurately. It is worth mentioning that the above configuration is very advantageous for the low temperature environment operation of the internal combustion engine, for example, during the winter operation, the temperature of the fresh gas is often very low (even lower than zero), if the low temperature gas is directly delivered to the internal combustion engine, which may cause the lubricating oil in the internal combustion engine to form an oil film, thereby causing the abrasion of the internal combustion engine to be seriously increased, in order to solve the problem, the recirculated exhaust gas valve 120 may be opened to conduct the recirculated exhaust gas, at which time the recirculated exhaust gas will heat the recirculated exhaust gas valve 120 to raise the temperature thereof, due to the action of the heat conducting member 130, the temperature of the mixer 110 will be also described, and the mixer 110 may further heat the fresh gas, thereby raising the temperature of the gas delivered to the internal combustion engine, and therefore, the above configuration is helpful for ensuring the lubrication of the internal combustion engine in the low temperature environment. In addition, the above configuration is also advantageous for normal-temperature and high-temperature ambient operation of the internal combustion engine, for example, in summer operation, the temperature of fresh gas tends to be high, if the high-temperature gas is directly delivered to the internal combustion engine, it may result in an insufficient intake air amount of the internal combustion engine (because the density of the high-temperature gas is low) to affect the power output of the internal combustion engine, and may cause overheating damage to the engine, to address this problem, the recirculated exhaust valve 120 may be closed to shut off the recirculated exhaust, at which time, the temperature of the recirculated exhaust valve 120 will drop, due to the heat-conducting member 130, the recirculated exhaust gas valve 120 will absorb the heat of the mixer 110, and thus cause the temperature of the mixer 110 to drop, the mixer 110, in turn, can cool the fresh air therein, and therefore, the above configuration also helps to ensure the intake air amount of the internal combustion engine in a high temperature environment and helps to prevent the internal combustion engine from overheating in a high temperature environment. In addition, it is worth mentioning that the presence of the heat-conducting member 130 enables the heat exchange between the mixer 110 and the recirculated exhaust valve 120 to be achieved in a simple manner, whereas in the prior art it is often necessary to manufacture the mixer 110 and the recirculated exhaust valve 120 with a very high precision, so as to achieve the above-mentioned heat exchange by means of a positive fit (direct surface contact) of the two, and therefore the above-mentioned arrangement reduces the production, assembly and maintenance costs of the internal combustion engine intake air mixing device 100 by reducing the manufacturing precision requirements for manufacturing the mixer 110 and the recirculated exhaust valve 120, compared to the prior art.

According to an alternative embodiment of the present invention, as shown in fig. 2, the heat conductive member 130 is disposed between the mixer main body 111 of the mixer 110 and the valve body 121 of the recirculated exhaust gas valve 120 such that the first heat exchange area HEA1 is formed on the outer surface of the mixer main body 111 and the second heat exchange area HEA2 is formed on the outer surface of the valve body 121. This configuration is advantageous because the recirculated exhaust gas flows in the valve chamber 122 in the valve body 121 and the fresh gas flows in the mixing chamber in the mixer main body 111, and thus the above configuration improves the heat exchange efficiency of the recirculated exhaust gas and the fresh gas by disposing the heat conductive member 130 between the valve body 121 and the mixer main body 111.

In particular, as shown in fig. 2, a third heat exchange region HEA3 is formed on the inner surface of the valve body 121 at a position opposite to the second heat exchange region HEA2, wherein the third heat exchange region HEA3 is spaced apart from the second heat exchange region HEA2 by the thickness of the valve body 121, and the third heat exchange region HEA3 is positioned at a position such that the airflow path P is turned (i.e., changed in direction), and in the case shown in fig. 2, the third heat exchange region HEA3 changes the airflow path P from the vertical direction to the lateral direction. In this configuration, the arrangement further increases the heat exchange efficiency of the recirculated exhaust gas with the fresh gas because the airflow path P will turn after encountering the third heat exchange region HEA3, and thus the recirculated exhaust gas will decelerate at the third heat exchange region HEA3 and come into sufficient contact with the third heat exchange region HEA3, which helps to transfer heat from the recirculated exhaust gas to the third heat exchange region HEA3 and further to the mixer body 111 through the second heat exchange region HEA2, the thermally conductive member 130 and the first heat exchange region HEA 1.

In particular, as shown in fig. 2, the second heat exchange region HEA2 and the third heat exchange region HEA3 are spaced apart from the exhaust port 124, which makes it unnecessary to provide an opening in the second heat exchange region HEA2 or the third heat exchange region HEA3 through which the exhaust port 124 passes, whereby the areas of the second heat exchange region HEA2 and the third heat exchange region HEA3 can be set larger, which contributes to improving the heat exchange efficiency of the recirculated exhaust gas with the fresh gas.

Specifically, as shown in fig. 2, the recirculation exhaust valve 120 is provided with a plurality of exhaust ports 124 (two are shown), the mixer 110 is provided with the same number of exhaust inlets 112, and the flow path P is divided at the third heat exchange area HEA3 into a plurality of branches extending toward the plurality of exhaust ports 124.

In particular, as shown in fig. 2, the third heat exchange area HEA3 is positioned in alignment with the gas inlet 123, for example, along the gas flow path P, which causes the recirculated exhaust gas entering the valve chamber 122 from the gas inlet 123 to flow towards the third heat exchange area HEA3 without being diverted before encountering the third heat exchange area HEA3, which also helps to improve the heat exchange efficiency of the recirculated exhaust gas with the fresh gas.

In particular, as shown in fig. 2, the second heat exchange region HEA2 may be formed in a recess recessed from the outer surface of the valve body 121, and the third heat exchange region HEA3 may be formed in a recess recessed from the inner surface of the valve body 121. This configuration reduces the distance between the second heat exchange region HEA2 and the third heat exchange region HEA3 (i.e., the thickness of the material therebetween), and thus improves the heat exchange efficiency of both. In addition, the edges of the recess where the third heat exchange area HEA3 is located (for example, the steps 127 on the left and right sides of the third heat exchange area HEA3 in fig. 2) obstruct the flow of the recirculated exhaust gas, thereby further prolonging the contact of the recirculated exhaust gas with the third heat exchange area HEA3 and thus improving the heat exchange efficiency of the recirculated exhaust gas with the third heat exchange area HEA 3.

Referring to fig. 1-3, fig. 3 shows a schematic perspective view of mixer 110, according to an alternative embodiment of the present invention. As shown in fig. 1-3, the mixer body 111 has a boss 113 formed on an outer surface thereof, the boss 113 extending toward the valve body 121 and terminating at an end surface 114, the end surface 114 forming said first heat exchange area HEA 1. As shown in fig. 1, after the recirculated exhaust gas valve 120 is fixed to the mixer 110, the end surface 114 is adjacent to the outer surface of the valve body 121, and the heat conductive member 130 is disposed therebetween. In particular, the end surface 114 is shaped in such a way as to conform to the outer surface of the valve body 121, so that both have substantially the same shape, for example, the end surface 114 and the outer surface of the valve body 121 are both cylindrical, which makes it possible for the end surface 114 to be adjacent to the outer surface of the valve body 121 over its entire extension, so as to form a gap between the end surface 114 and the outer surface of the valve body 121, extending along the end surface 114, in which gap it can be considered that the heat-conducting member 130 is filled and fills the gap. In this configuration, the distance between the first heat exchange area HEA1 and the second heat exchange area HEA2 is reduced, and therefore the heat exchange efficiency therebetween is improved.

According to an alternative embodiment of the utility model, as shown in fig. 2, inside the mixer 110 (in particular the mixer body 111) there is also provided a duct 115 for the flow of a heat exchange fluid (for example water), this duct 115 having a portion adjacent to the first heat exchange area HEA1 and a portion adjacent to the mixing chamber. In particular, the duct 115 has a portion arranged to extend around the mixing chamber. In this configuration, the heat exchange fluid will exchange heat with the first heat exchange region HEA1 when flowing proximate to the first heat exchange region HEA1 and exchange heat with the mixing chamber when flowing proximate to the mixing chamber, which helps to increase the heat exchange efficiency of the first heat exchange region HEA1 with the mixing chamber.

According to an alternative embodiment of the present invention, the heat conducting member 130 may comprise or consist of one or more layers of stacked sheets of heat conducting material (e.g., good conductors of heat such as graphite sheets), and the number of sheets of heat conducting material may be determined by the distance between the first heat exchanging area HEA1 and the second heat exchanging area HEA2 (e.g., the thickness of the gap between the end surface 114 and the outer surface of the valve body 121). With this configuration, an appropriate number of sheets of the heat conductive material can be selected to be placed between the first heat exchange area HEA1 and the second heat exchange area HEA2 to constitute the heat conductive member 130, which further reduces the requirements on the manufacturing accuracy of the mixer 110 and the recirculated exhaust gas valve 120 because the thickness of the heat conductive member 130 can be changed by adjusting the number of sheets of the heat conductive material, and in addition, the heat exchange efficiency between the first heat exchange area HEA1 and the second heat exchange area HEA2 can be improved because the heat conductive material such as graphite has good heat conductivity. Of course, the thermal conductive member 130 may also include or be made of other materials suitable for thermal conduction (e.g., thermal conductive silicone grease, etc.).

Alternative but non-limiting embodiments of the internal combustion engine intake air mixing device according to the utility model have been described in detail above with the aid of the accompanying drawings. Modifications and additions to the techniques and structures, as well as re-combinations of features in various embodiments, which do not depart from the spirit and substance of the disclosure, will be readily apparent to those of ordinary skill in the art as they are deemed to be within the scope of the utility model. Accordingly, such modifications and additions that can be envisaged within the teachings of the present invention are to be considered as part of the present invention. The scope of the utility model includes both equivalents known at the time of filing and equivalents which may not have been foreseen.

Claims

1. An internal combustion engine intake air mixing device comprising:

a mixer (110) having a mixer body (111) forming a mixing chamber therein and provided with an off-gas inlet (112) opening into the mixing chamber;

-a recirculating exhaust valve (120) having a valve body (121) forming a valve chamber (122) inside, provided with an inlet (123) and an outlet (124) opening into the valve chamber (122), and fixed to the mixer (110) so that the outlet (124) communicates with the exhaust inlet (112), characterized in that the engine inlet mixing device further comprises:

a heat-conducting member (130), the heat-conducting member (130) being in surface contact with the mixer (110) on one side so as to form a first heat exchange area (HEA1) on an outer surface of the mixer (110), and in surface contact with the recirculation off-gas valve (120) on the other side so as to form a second heat exchange area (HEA2) on an outer surface of the recirculation off-gas valve (120).

2. The internal combustion engine intake mixing device according to claim 1, wherein the heat-conducting member (130) is in surface contact with the mixer main body (111) and the valve body (121), respectively, such that the first heat exchange region (HEA1) is formed on an outer surface of the mixer main body (111) and the second heat exchange region (HEA2) is formed on an outer surface of the valve body (121).

3. The internal combustion engine intake mixing device according to claim 2, characterized in that the second heat exchange region (HEA2) is formed in a recess that is recessed from an outer surface of the valve body (121).

4. The internal combustion engine intake mixing device according to claim 2 or 3, wherein the valve chamber (122) defines an airflow path (P) extending from the intake port (123) to the exhaust port (124), a third heat exchange region (HEA3) is formed on an inner surface of the valve body (121) at a position opposite to the second heat exchange region (HEA2), and wherein,

said third heat exchange area (HEA3) being positioned so that said airflow path (P) changes direction; and/or the presence of a gas in the gas,

the third heat exchange region (HEA3) is positioned spaced apart from the exhaust outlet (124); and/or the presence of a gas in the gas,

the recirculation exhaust valve (120) is provided with a plurality of exhaust ports (124), and the gas flow path (P) is dispersed into a plurality of branches extending toward the plurality of exhaust ports (124) at the third heat exchange area (HEA 3).

5. The internal combustion engine intake mixing device of claim 4, wherein the third heat exchange area (HEA3) is formed in a recess recessed from an inner surface of the valve body (121).

6. The internal combustion engine intake mixing arrangement of claim 4, wherein the third heat exchange region (HEA3) is positioned in alignment with the intake port (123).

7. An internal combustion engine intake mixing arrangement according to claim 2 or 3, characterized in that the mixer body (111) is provided with a boss (113) on its outer surface, which boss (113) extends towards the valve body (121) and terminates in an end surface (114), the first heat exchange area (HEA1) being formed by the end surface (114).

8. The internal combustion engine intake mixing device according to claim 7, characterized in that the end surface (114) is shaped in a manner conforming to an outer surface of the valve body (121) so as to form a gap extending along the end surface (114) between the end surface (114) and the outer surface of the valve body (121), the heat conductive member (130) being filled in the gap.

9. An internal combustion engine intake mixing arrangement according to any one of claims 1-3, wherein the mixer (110) is provided with a duct (115) for the flow of a heat exchange fluid, the duct (115) having a portion adjacent to the first heat exchange region (HEA1) and a portion adjacent to the mixing chamber.

10. An internal combustion engine intake mixing arrangement according to any one of claims 1-3, wherein the thermally conductive member (130) comprises one or more stacked sheets of thermally conductive material.