CN117803500A

CN117803500A - Exhaust gas recirculation mixer and engine air intake and exhaust system with same

Info

Publication number: CN117803500A
Application number: CN202211175436.5A
Authority: CN
Inventors: 谢正海; 陈如彬
Original assignee: SAIC Motor Corp Ltd
Current assignee: SAIC Motor Corp Ltd
Priority date: 2022-09-26
Filing date: 2022-09-26
Publication date: 2024-04-02

Abstract

The invention provides an exhaust gas recirculation mixer and an engine air intake and exhaust system with the same, wherein the mixer comprises a main communication pipeline, an exhaust gas guide chamber, a valve cylinder and a rotary driving assembly. The main communication pipeline comprises an air cavity, a mixing cavity and an exhaust cavity which are sequentially arranged and communicated. The mixing chamber is provided with a plurality of exhaust gas through holes along the circumferential direction thereof. An annular housing of the exhaust gas guide chamber is disposed around and sealingly secured to the outer periphery of the mixing chamber. The valve cylinder is positioned in the waste gas ring cavity, is tightly sleeved on the periphery of the mixing cavity, can rotate around the axis of the mixing cavity along the periphery of the mixing cavity relative to the mixing cavity, and is provided with a valve hole along the circumferential direction of the valve cylinder. The driving part of the rotary driving assembly can rotate relative to the annular shell and drive the rotary part to rotate relative to the mixing cavity around the axis of the mixing cavity, so as to control the exhaust gas through hole to switch between the full-open state, the partial-open state and the full-closed state relative to the valve hole. The scheme can enable waste gas to be mixed more uniformly and reduce arrangement difficulty.

Description

Exhaust gas recirculation mixer and engine air intake and exhaust system with same

Technical Field

The invention relates to the technical field of engine exhaust gas recirculation, in particular to an exhaust gas recirculation mixer and an engine air intake and exhaust system with the same.

Background

The exhaust gas recirculation technique (Exhaust Gas Recirculation, EGR) is a technique of mixing exhaust gas burned at a high temperature in an engine with intake air and introducing the mixture into a cylinder of the engine to be burned again. The technology can control the in-cylinder combustion temperature of the engine and reduce the emission of nitrogen oxides, and can also improve the fuel economy.

Fig. 1 shows a schematic diagram of a prior art engine intake and exhaust system, in which air in the environment flows into a compressor 02 after impurities in the air are removed by an air cleaner 01, the air is compressed and then cooled by an intercooler 03 to reach a very high density, and the flow is controlled by a throttle valve 04 and is led into an intake manifold 05 and cylinders of an engine body 06. Exhaust gas discharged after the mixture combustion of the intake air and the fuel in the cylinder is discharged into the turbine 08 through the exhaust manifold 07 to do work on the compressor 02. The exhaust gas then flows further into the three-way catalyst 09 to the atmosphere.

In order to meet the increasingly stringent requirements for low fuel consumption and low emissions, many engines require exhaust gas recirculation systems. Specifically, an exhaust gas recirculation cooler is arranged in an engine air intake and exhaust system to cool high-temperature exhaust gas, and an exhaust gas recirculation valve is arranged to control the exhaust gas recirculation flow.

The exhaust gas recirculation system in the prior art mainly comprises two specific implementation modes of high-pressure exhaust gas recirculation and low-pressure exhaust gas recirculation. For high pressure exhaust gas recirculation, referring to fig. 1, the exhaust gas is typically cooled by a high pressure exhaust gas recirculation cooler 010 upstream of the turbine 08, and the amount of exhaust gas recirculation is controlled by a high pressure exhaust gas recirculation valve 011. The exhaust gas is then led downstream of the throttle valve 04. For the high-pressure exhaust gas recirculation system, the pressure difference between the exhaust manifold 07 and the air intake manifold 05 is the motive power for pushing the exhaust gas to circulate, and when the pressure difference is larger, higher exhaust gas circulation flow can be led in, namely, the exhaust gas circulation rate is higher; when the pressure difference is small or negative (low speed low load scenario), the exhaust gas recirculation gas is difficult to introduce into the intake manifold 05.

For low-pressure exhaust gas recirculation, referring to fig. 1, exhaust gas is generally led out from the front, middle or rear of the three-way catalyst 09 downstream of the turbine 08, the led-out exhaust gas is cooled by the low-pressure exhaust gas recirculation cooler 012, and the amount of exhaust gas is controlled by the low-pressure exhaust gas recirculation valve 013. The exhaust gas is led into a three-way T-joint upstream of the compressor 02 and mixed with air before flowing into the compressor 02. For the low-pressure exhaust gas recirculation system, although the suction effect of the compressor 02 is good, the working range of exhaust gas circulation can be ensured to be large, and the high exhaust gas circulation rate can be obtained even in a low-speed low-load scene, harmful components in the exhaust gas can pollute and corrode the compressor 02, the intercooler 03, the throttle valve 04 and pipeline accessories to a certain extent. Meanwhile, for the mixer 014 having a three-way T-shaped structure, the mixer 014 may make the uniformity of mixing the exhaust gas with the air worse, which may cause unstable operation and reduced efficiency of the compressor 02. In addition, the three-way T-shaped mixer 014 is to directly insert the exhaust gas pipeline into the air pipeline for mixing, and needs to reserve enough space for the exhaust gas pipeline and the air pipeline in combination with the low-pressure exhaust gas recirculation valve 013, so that the difficulty in arrangement of the air intake and exhaust system of the engine is improved.

Disclosure of Invention

The invention aims to solve the problems of poor mixing uniformity and high arrangement difficulty of an engine exhaust gas recirculation system in the prior art.

To solve the above problems, an embodiment of the present invention discloses an exhaust gas recirculation mixer including: the main communication pipeline comprises an air cavity for air inflow, a mixing cavity for mixing air and engine waste gas and an exhaust cavity for discharging the mixed gas, which are sequentially arranged and communicated, wherein the mixing cavity is provided with a plurality of waste gas through holes along the circumferential direction; the exhaust gas guiding chamber comprises an annular shell, the annular shell is arranged in a surrounding mode and is fixed on the periphery of the mixing cavity in a sealing mode, an exhaust gas ring cavity is formed between the inner periphery of the annular shell and the periphery of the mixing cavity, and an exhaust gas inlet for engine exhaust gas to enter the exhaust gas ring cavity is formed in the annular shell; the valve cylinder is positioned in the waste gas ring cavity, is tightly sleeved on the periphery of the mixing cavity, can rotate relative to the mixing cavity along the periphery of the mixing cavity around the axis of the mixing cavity, and is provided with a plurality of valve holes which are matched with the plurality of waste gas through holes one by one along the circumferential direction of the valve cylinder; and the rotary driving assembly comprises a rotary part fixedly arranged on the outer wall of the valve cylinder and a driving part rotatably arranged on the annular shell of the waste gas guide chamber and matched with the rotary part, and the driving part can rotate relative to the annular shell and drive the rotary part to link the valve cylinder to rotate relative to the mixing cavity around the axis of the mixing cavity so as to control the waste gas through hole to switch between the fully opened, partially opened and fully closed states relative to the valve hole.

By adopting the scheme, the exhaust gas guiding chamber is arranged around the periphery of the mixing cavity, so that the exhaust gas can be temporarily stored in the exhaust gas guiding chamber after entering from the exhaust gas inlet. When waste gas and air are required to be mixed, the waste gas in the waste gas guide chamber can quickly enter the mixing cavity to be mixed with the air, so that the mixing efficiency of the gas is improved. And, exhaust gas guide room encircles the structure of setting at the mixing chamber periphery and compares the structure of T shape pipeline among the prior art, occupation space is littleer. And the aperture of a channel formed by the valve hole and the exhaust gas through hole can be adjusted through the relative rotation of the mixing cavity and the valve barrel, so that the flow rate of the gas in the exhaust gas guide chamber entering the mixing cavity can be adjusted. The exhaust gas recirculation mixer thus has a self-regulating function of the exhaust gas flow, i.e. the amount of exhaust gas mixed with air can be regulated by itself. Therefore, when the exhaust gas recirculation mixer is arranged in an engine air intake and exhaust system, an exhaust gas recirculation valve for adjusting the flow of exhaust gas is not required to be additionally arranged, and the arrangement of the system is facilitated.

According to another embodiment of the present invention, in the exhaust gas recirculation mixer of the engine intake and exhaust system disclosed in the embodiment of the present invention, in a cross section taken along an axis of the mixing chamber, an inner diameter dimension of the mixing chamber gradually decreases from both ends to a middle portion, and the inner diameter dimension of the mixing chamber is smallest in the middle portion of the mixing chamber; and, the plurality of exhaust gas through holes are arranged in the middle of the mixing chamber at uniform intervals in the circumferential direction of the mixing chamber.

By adopting the scheme, the exhaust gas through hole is arranged at the position with the smallest inner diameter size of the mixing cavity, so that the minimum static pressure is formed in the middle of the mixing cavity where the exhaust gas through hole is positioned when the exhaust gas and the air flow to the exhaust gas through hole, more exhaust gas can enter the exhaust gas guide chamber at a higher speed and enter the mixing cavity under the action of the minimum static pressure, and the exhaust gas circulation rate is further improved.

According to another embodiment of the present invention, an exhaust gas recirculation mixer is disclosed wherein the internal diameter of the mixing chamber decreases in size linearly from both ends to the middle, respectively, in a cross section taken along the axis of the mixing chamber.

By adopting the scheme, the inner diameter of the mixing cavity is linearly reduced from two ends to the middle part respectively, so that the inner wall of the mixing cavity is smooth, the air flow cannot be impacted or influenced, and the air flow can smoothly flow in one direction.

According to another embodiment of the present invention, an exhaust gas recirculation mixer is disclosed in which, in a cross section taken along the axis of the mixing chamber, the annular housing of the exhaust gas guide chamber is "pi" shaped, comprising an annular top wall, and a first side wall and a second side wall on either side of the annular top wall; the waste gas inlet penetrates through the annular top wall and is communicated with the waste gas ring cavity and the external waste gas pipeline; and, in the axis extending direction of the mixing chamber, one end of the first side wall away from the annular top wall is fixed to one end peripheral wall of the mixing chamber, and one end of the second side wall away from the annular top wall is fixed to the other end peripheral wall of the mixing chamber.

According to another embodiment of the present invention, an exhaust gas recirculation mixer disclosed in the embodiments of the present invention, the driving part includes a driving shaft penetrating the first sidewall; the driving member is positioned outside the waste gas guiding chamber and is fixedly connected with one end of the driving shaft, and the driven member is positioned inside the waste gas guiding chamber and is fixedly connected with the other end of the driving shaft; the rotary part is arranged on the outer wall of the valve cylinder at one side close to the driven component and corresponds to the driven component, and the driven component is abutted with the rotary part so as to drive the rotary part to link the valve cylinder to rotate.

According to another embodiment of the present invention, the exhaust gas recirculation mixer disclosed in the embodiment of the present invention is further provided with a limiting member for limiting the rotational position of the driving member at a position corresponding to the movement locus of the driving member on the outer peripheral wall surface of the first side wall.

According to another embodiment of the present invention, an exhaust gas recirculation mixer disclosed in the embodiment of the present invention, the driving member includes a first swing arm and a first fixing pin; the first swing arm extends along the radial direction of the driving shaft, one end of the first swing arm is fixedly connected with one end of the driving shaft, and the other end of the first swing arm is connected with one end of the first fixing pin; the limiting component is two limiting pins respectively positioned at two sides of the first swing arm on the motion track of the first swing arm, and the two limiting pins can be respectively abutted with two sides of the first swing arm; the driven member comprises a second swing arm and a second fixing pin; the second swing arm extends along the radial direction of the driving shaft, one end of the second swing arm is fixedly connected with the other end of the driving shaft, and the other end of the second swing arm is connected with one end of a second fixing pin; the rotating component is a shifting fork, an opening of the shifting fork extends along the radial direction of the valve cylinder, and the other end of the second fixing pin is in abutting connection with the inner wall of the opening and can slide along the opening in the radial direction of the valve cylinder.

By adopting the scheme, the rotary part is arranged as the shifting fork, the second fixing pin can be well limited by arranging the opening width of the shifting fork, and the opening of the shifting fork extends along the radial direction of the valve cylinder, so that the second fixing pin cannot be clamped when the second fixing pin moves, and the smoothness of movement is ensured.

According to another embodiment of the present invention, an exhaust gas recirculation mixer disclosed in the embodiment of the present invention, in an axial direction of a mixing chamber, a valve cylinder covers at least a part of an outer peripheral wall surface of the mixing chamber; the valve cylinder is positioned at one side close to the driving part in the waste gas annular cavity, and one side wall of the valve cylinder is abutted against the inner peripheral wall surface of the first side wall; and, be formed with a valve section of thick bamboo spacing step on the peripheral wall of mixing chamber, another lateral wall of valve section of thick bamboo butt valve section of thick bamboo spacing step.

According to another embodiment of the invention, an exhaust gas recirculation mixer is disclosed in which, in a cross section taken along the axis of the mixing chamber, the cross-sectional area of the cavity on the side of the exhaust gas guiding chamber adjacent to the exhaust gas inlet is greater than the cross-sectional area of the cavity on the other side of the exhaust gas guiding chamber, which is symmetrical to the side with respect to the axis of the mixing chamber, remote from the exhaust gas inlet.

By adopting the scheme, the gas quantity and the flow rate of the exhaust gas entering through the exhaust gas through holes at all positions can be uniform.

According to another embodiment of the present invention, the exhaust gas recirculation mixer disclosed in the embodiment of the present invention has an axis of the annular housing of the exhaust gas guiding chamber closer to the exhaust gas inlet side than the axis of the mixing chamber in a cross section taken along the axis of the mixing chamber, and a distance between the annular top wall of the exhaust gas guiding chamber on the side close to the exhaust gas inlet and the outer wall of the valve cylinder is larger than a distance between the annular top wall of the other side and the outer wall of the valve cylinder in a direction perpendicular to the axis of the mixing chamber; and/or, in the axial direction of the mixing chamber, the distance between the first side wall and the second side wall on the side of the exhaust gas guiding chamber close to the exhaust gas inlet is greater than the distance on the other side away from the exhaust gas inlet, and in the circumferential direction of the mixing chamber, the distance between the first side wall and the second side wall varies linearly and is smallest at a position opposite to the exhaust gas inlet.

According to another specific embodiment of the invention, the exhaust gas recirculation mixer disclosed in the embodiment of the invention, wherein the main communication pipeline comprises an air pipeline, a mixing pipeline and an exhaust pipeline which are sequentially connected end to end, and the cavities of the air pipeline form an air cavity, the cavities of the mixing pipeline form a mixing cavity, and the cavities of the exhaust pipeline form an exhaust cavity; wherein, two ends of the mixing pipeline in the axial direction are respectively clamped into bayonets at the corresponding ends of the air pipeline and the exhaust pipeline; and the annular shell of the exhaust gas guiding chamber is sleeved on the outer peripheral wall of the mixing pipeline.

According to another embodiment of the present invention, an exhaust gas recirculation mixer is disclosed in the embodiment of the present invention, wherein the annular top wall and the second side wall of the annular housing are integrally formed at one side end portion of the exhaust pipe, which is clamped with the mixing pipe; the first side wall of the annular shell is integrally formed at one end part of the air pipeline, which is clamped with the mixing pipeline; and, the first side wall abuts the respective ends of the annular top wall with an annular sealing member disposed therebetween.

According to another embodiment of the present invention, the exhaust gas recirculation mixer disclosed in the embodiment of the present invention further includes a first sealing member provided on an outer wall of the mixing chamber, surrounding an outer periphery of each of the exhaust gas through holes; the second sealing component is arranged on the outer wall of the mixing cavity, is clung to the outer wall of the mixing cavity, extends along the circumferential direction of the mixing cavity, and is connected with any two adjacent first sealing components; the third sealing component is arranged on the outer wall of the mixing cavity, is positioned at one side of the exhaust gas through hole, is clung to the outer wall of the mixing cavity and extends along the circumferential direction of the mixing cavity; the shaft sleeve is arranged between the driving shaft and the first side wall and covers the periphery of the driving shaft; a fourth sealing member disposed between the shaft sleeve and the first swing arm; and fifth sealing members provided on both side walls of the mixing chamber.

By adopting the scheme, the waste gas can be sealed by arranging the sealing element, so that a large amount of waste gas leakage is avoided. In addition, the first sealing member, the second sealing member and the third sealing member can enable the relative rotation of the valve cylinder and the mixing cavity to be smoother, and clamping stagnation is avoided.

According to another embodiment of the present invention, the exhaust gas recirculation mixer disclosed in the embodiment of the present invention, the plurality of exhaust gas through holes and the plurality of valve holes each include at least one row of exhaust gas through holes and at least one row of corresponding valve holes arranged in the circumferential direction of the mixing chamber and the valve barrel in the axial direction of the main communication pipe; wherein, each row of exhaust gas through holes and corresponding valve holes are uniformly arranged along the axial interval of the mixing cavity.

Embodiments of the present invention disclose an engine intake and exhaust system comprising an exhaust gas recirculation mixer as described in any of the embodiments above; the air inlet end of the engine body is communicated with the air inlet pipeline, and the air outlet end of the engine body is communicated with the air outlet pipeline; the air inlet pipeline is provided with an air filter, an exhaust gas recirculation mixer, a gas compressor, an intercooler and a throttle valve which are used for enabling gas to flow through in sequence, and the exhaust pipeline is provided with a turbine and a catalyst which are used for enabling gas to flow through in sequence; the air inlet of the exhaust gas recirculation mixer is connected with the exhaust end of the air filter, and the mixer outlet of the exhaust gas recirculation mixer is connected with the air inlet end of the air compressor; and a high-pressure exhaust gas recirculation cooler and a high-pressure exhaust gas recirculation valve connected in series; the exhaust end of the high-pressure exhaust gas circulation cooler is communicated with the air inlet end of the engine body and the air inlet pipeline between the air inlet end of the throttle valve; and the low-pressure exhaust gas recirculation cooler is communicated with an exhaust pipeline between the turbine and the catalyst or an exhaust pipeline between the air inlet end of the low-pressure exhaust gas recirculation cooler and the exhaust end of the catalyst, and the exhaust end of the low-pressure exhaust gas recirculation cooler is communicated with an exhaust gas inlet of the exhaust gas recirculation mixer.

The beneficial effects of the invention are as follows:

the exhaust gas recirculation mixer that this scheme provided just can be through the bore of the passageway that adjusts valve opening and waste gas through-hole formation through the relative rotation of mixing chamber and valve section of thick bamboo, and then can adjust the flow that the indoor gas of waste gas guide got into mixing chamber. The exhaust gas recirculation mixer thus has a self-regulating function of the exhaust gas flow, i.e. the amount of exhaust gas mixed with air can be regulated by itself. Therefore, when the exhaust gas recirculation mixer is arranged in an engine air intake and exhaust system, an exhaust gas recirculation valve for adjusting the flow of exhaust gas is not required to be additionally arranged, and the arrangement of the system is facilitated.

According to the engine air inlet and exhaust system provided by the scheme, the regulation and control of the exhaust gas flow can be realized without arranging a low-pressure exhaust gas circulation valve. In addition, because the waste gas is temporarily stored in the waste gas guide chamber, the distance between the waste gas guide chamber and the mixing chamber is quite short, and therefore, the rapid mixing of air and waste gas can be realized; and the exhaust gas flows in from a plurality of exhaust gas through holes which are uniformly distributed in the vertical direction with the air flow, so that the mixing uniformity of the exhaust gas and the air can be further improved. In addition, the air and the exhaust gas can be quickly and uniformly mixed by the engine air inlet and exhaust system, and the mixing cavity forms a suction function of minimum static pressure at the exhaust gas through hole, so that the exhaust gas recirculation mixer can suck more exhaust gas and introduce the exhaust gas into the air inlet pipeline as much as possible, and the exhaust gas circulation rate is higher.

Drawings

FIG. 1 is a schematic diagram of a prior art supercharged engine exhaust and intake system;

FIG. 2 is a schematic diagram of an exhaust gas recirculation mixer of an engine intake and exhaust system according to an embodiment of the present invention;

FIG. 3 is a schematic view of a cross-section taken along the axis of a mixing chamber provided by an embodiment of the present invention;

FIG. 4 is a schematic view of a cross-section taken perpendicular to the axis of the mixing chamber provided by an embodiment of the present invention;

FIG. 5 is another schematic diagram of an exhaust gas recirculation mixer of an engine intake and exhaust system according to an embodiment of the present invention;

FIG. 6 is an exploded view of an exhaust gas recirculation mixer for an engine exhaust and intake system according to an embodiment of the present invention;

fig. 7 is a schematic diagram of an intake and exhaust system of an engine according to an embodiment of the present invention.

Description of the prior art reference numerals:

01. an air cleaner; 02. a compressor; 03. an intercooler; 04. a throttle valve; 05. an intake manifold; 06. an engine body; 07. an exhaust manifold; 08. a turbine; 09. a three-way catalyst; 010. a high pressure exhaust gas recirculation cooler; 011. a high pressure exhaust gas recirculation valve; 012. a low pressure exhaust gas recirculation cooler; 013. a low pressure exhaust gas recirculation valve; 014. a mixer.

Reference numerals of the present application illustrate:

1. an air chamber; 11. an air duct; 2. a mixing chamber; 21. a mixing pipe; 22. an exhaust gas through hole; 23. a valve cylinder limiting step; 24. a first sealing member; 25. a second sealing member; 26. a third sealing member; 3. an exhaust chamber; 31. an exhaust duct; 4. an exhaust gas guide chamber; 41. an exhaust gas inlet; 42. an annular top wall; 43. a first sidewall; 44. a second sidewall; 45. a limiting member; 46. an annular sealing member; 5. a valve cylinder; 51. a valve hole; 6. a rotating member; 7. a driving part; 71. a drive shaft; 72. a driving member; 73. a driven member; 74. a shaft sleeve; 75. a fourth sealing member; 8. an engine intake and exhaust system; 81. an exhaust gas recirculation mixer; 82. an air intake line; 821. an air cleaner; 822. a compressor; 823. an intercooler; 824. a throttle valve; 83. an exhaust line; 831. a turbine; 832. a catalyst; 84. a high-pressure exhaust gas recirculation cooler; 85. a high pressure exhaust gas recirculation valve; 86. a low pressure exhaust gas recirculation cooler; 87. an engine body.

Detailed Description

Further advantages and effects of the present invention will become apparent to those skilled in the art from the disclosure of the present specification, by describing the embodiments of the present invention with specific examples. While the description of the invention will be described in connection with the preferred embodiments, it is not intended to limit the inventive features to the implementation. Rather, the purpose of the invention described in connection with the embodiments is to cover other alternatives or modifications, which may be extended by the claims based on the invention. The following description contains many specific details for the purpose of providing a thorough understanding of the present invention. The invention may be practiced without these specific details. Furthermore, some specific details are omitted from the description in order to avoid obscuring the invention. It should be noted that, without conflict, the embodiments of the present invention and features of the embodiments may be combined with each other.

It should be noted that in this specification, like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further definition or explanation thereof is necessary in the following figures.

In the description of the present embodiment, it should be noted that the azimuth or positional relationship indicated by the terms "upper", "lower", "inner", "bottom", etc. are based on the azimuth or positional relationship shown in the drawings, or the azimuth or positional relationship in which the inventive product is conventionally put in use, are merely for convenience of describing the present invention and simplifying the description, and are not indicative or implying that the apparatus or element to be referred to must have a specific azimuth, be configured and operated in a specific azimuth, and therefore should not be construed as limiting the present invention.

The terms "first," "second," and the like are used merely to distinguish between descriptions and are not to be construed as indicating or implying relative importance.

In the description of the present embodiment, it should also be noted that, unless explicitly specified and limited otherwise, the terms "disposed," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present embodiment can be understood in a specific case by those of ordinary skill in the art.

For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

Example 1:

in order to solve the problems of poor mixing uniformity and high arrangement difficulty of an engine exhaust gas recirculation system in the prior art, the embodiment of the invention provides an exhaust gas recirculation mixer of an engine exhaust gas inlet system, which comprises a main communication pipeline, an exhaust gas guide chamber, a valve cylinder and a rotary driving assembly.

Specifically, referring to fig. 2 and 3, the main communication pipe includes an air chamber 1 into which air flows, a mixing chamber 2 into which air and engine exhaust gas are mixed, and an exhaust chamber 3 from which the mixed gas is discharged, which are sequentially arranged and communicated. Wherein, referring to fig. 3, the mixing chamber 2 is provided with a plurality of exhaust gas through holes 22 in its circumferential direction. More specifically, the number of exhaust gas through holes 22 is not preferably too small, which would affect the efficiency of the exhaust gas entering the mixing chamber 2. The specific number of the arrangement may be determined according to the areas of the exhaust gas through-holes 22 and the valve holes 51, and the distance between points of the adjacent two exhaust gas through-holes 22 closest to each other should be greater than or equal to the diameter of the valve holes 51. With such a structure, when the valve cartridge 5 rotates relative to the mixing chamber 2, the valve hole 51 has enough movable space to control the state of the exhaust gas through-hole 22 to be switched between the fully opened, partially opened, and fully closed state, otherwise the fully closed state of the exhaust gas through-hole 22 cannot be achieved. In this embodiment, it is preferable that one exhaust gas through hole 22 is provided in each of the wall surfaces of the mixing chamber 2 corresponding to the upper, lower, left and right sides of the axis of the mixing chamber 2.

Referring to fig. 2 and 3, the exhaust gas guiding chamber 4 includes an annular housing which is disposed around and is sealed and fixed to the outer circumference of the mixing chamber 2, an exhaust gas ring chamber is formed between the inner circumference of the annular housing and the outer circumference of the mixing chamber 2, and an exhaust gas inlet 41 for engine exhaust gas to enter the exhaust gas ring chamber is provided on the annular housing. Specifically, the annular housing is fixedly connected with the outer periphery of the mixing cavity 2 in a manner including, but not limited to, integral molding and clamping. The exhaust gas inlet 41 may be provided at any position of the annular housing, and in this embodiment the exhaust gas inlet 41 is provided at the top position of the annular housing, and in fact, the exhaust gas inlet 41 is provided at neither the middle position nor the lower position of the annular housing, which does not affect the entry and flow of the exhaust gas. More specifically, since the exhaust gas guiding chamber 4 is circumferentially provided at the outer periphery of the mixing chamber 2, the exhaust gas can be temporarily stored into the exhaust gas guiding chamber 4 after entering from the exhaust gas inlet 41. When the exhaust gas is required to be mixed with the air, the exhaust gas in the exhaust gas guide chamber 4 can quickly enter the mixing cavity 2 to be mixed with the air, so that the mixing efficiency of the gas is improved. And, the structure in which the exhaust gas guide chamber 4 is disposed around the outer periphery of the mixing chamber 2 occupies a smaller space than the structure in which the T-shaped pipe is combined with the low pressure exhaust gas recirculation valve in the prior art.

Referring to fig. 3, the valve cartridge 5 is located in the waste gas ring chamber, is fitted snugly around the outer periphery of the mixing chamber 2, and is rotatable about its axis along the outer periphery of the mixing chamber 2 with respect to the mixing chamber 2. The outer periphery of the mixing chamber 2 is circular, and the inner periphery of the valve cylinder 5 is circular matched with the outer periphery of the mixing chamber 2. Also, the valve cylinder 5 is provided with a plurality of valve holes 51 in a circumferential direction thereof, which are matched one by one with the plurality of exhaust gas through holes 22. Specifically, the one-to-one matching of the exhaust gas through holes 22 and the valve holes 51 in this embodiment means that the number and shape of the exhaust gas through holes 22 and the valve holes 51 are the same, and when the center of one exhaust gas through hole 22 coincides with the center of the corresponding valve hole 51, the centers of the other exhaust gas through holes 22 and the centers of the corresponding valve holes 51 also coincide. That is, the states of all the exhaust gas through holes 22 are changed synchronously. However, the exhaust gas passage 22 and the valve hole 51 may be the same or different in size. When the size of the exhaust gas through-hole 22 is different from that of the valve hole 51, the size of the valve hole 51 is slightly larger than that of the exhaust gas through-hole 22.

Referring to fig. 3, the rotary driving assembly includes a rotary member 6 fixedly provided on an outer wall of the valve cartridge 5, and a driving member 7 rotatably provided on an annular housing of the exhaust gas guiding chamber 4, mated with the rotary member 6, the driving member 7 being rotatable with respect to the annular housing to drive the rotary member 6 to rotate about an axis of the mixing chamber 2 in association with the valve cartridge 5 with respect to the mixing chamber 2 to control the exhaust gas through-hole 22 to be switched between a fully opened, partially opened, and fully closed state with respect to the valve hole 51.

More specifically, with such a structure, by the relative rotation of the mixing chamber 2 and the valve barrel 5, the flow rate of the gas in the exhaust gas guide chamber 4 into the mixing chamber 2 can be regulated by adjusting the caliber of the passage formed by the valve hole 51 and the exhaust gas through hole 22. The exhaust gas recirculation mixer thus has a self-regulating function of the exhaust gas flow, i.e. the amount of exhaust gas mixed with air can be regulated by itself. Therefore, when the exhaust gas recirculation mixer is arranged in an engine air intake and exhaust system, an exhaust gas recirculation valve for adjusting the flow of exhaust gas is not required to be additionally arranged, and the arrangement of the system is facilitated.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, in a cross section taken along the axis A-A of the mixing chamber 2, the inner diameter dimension of the mixing chamber 2 is gradually reduced from both ends to the middle, and the inner diameter dimension of the mixing chamber 2 is smallest in the middle of the mixing chamber 2. And, the plurality of exhaust gas through holes 22 are arranged in a central portion of the mixing chamber 2 at regular intervals in the circumferential direction of the mixing chamber 2. In this way, the exhaust gas through hole 22 is arranged at the position with the smallest inner diameter size of the mixing cavity 2, so that when air flows to the exhaust gas through hole 22, the smallest static pressure is formed in the middle part of the mixing cavity 2 where the exhaust gas through hole 22 is arranged, and more exhaust gas can enter the exhaust gas guiding chamber 4 and enter the mixing cavity 2 at a faster speed under the suction action of the smallest static pressure, so that the exhaust gas circulation rate is further improved.

Still further, in a preferred embodiment according to the present invention, referring to fig. 3, in a cross section taken along the axis A-A of the mixing chamber 2, the inner diameter dimension of the mixing chamber 2 is linearly reduced from both ends to the middle, respectively. With such a structure, since the inner diameter dimension of the mixing chamber 2 is linearly reduced from both ends to the middle portion, respectively, the inner wall of the mixing chamber 2 is smooth, and the air flow can be smoothly caused to flow in one direction without impact or other influence.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, in a cross section taken along the axis A-A of the mixing chamber 2, the annular housing of the exhaust gas guiding chamber 4 has a "pi" shape including an annular top wall 42, and first and second side walls 43 and 44 located on both sides of the annular top wall 42. And, an exhaust gas inlet 41 is penetratingly formed at the annular top wall 42, communicating the exhaust gas ring cavity with an external exhaust gas pipe. And, in the extending direction of the axis A-A of the mixing chamber 2, one end of the first side wall 43 away from the annular top wall 42 is fixed to an outer peripheral wall of one end of the mixing chamber 2, and one end of the second side wall 44 away from the annular top wall 42 is fixed to an outer peripheral wall of the other end of the mixing chamber 2. Specifically, the first side wall 43 is connected to the annular top wall 42 in a threaded manner, and is connected to the outer peripheral wall of one end of the mixing chamber 2 in an adhesive or snap-fit manner; the second side wall 44 is integrally formed with the annular top wall 42 and is connected to the outside Zhou Bika of the other end of the mixing chamber 2. In this way, an annular housing having an annular cavity structure can be formed by only the annular top wall 42, the first side wall 43 and the second side wall 44, and the structure is simple.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, the driving part 7 includes a driving shaft 71 penetrating the first side wall 43, and driving members 72 and driven members 73 respectively provided at both ends of the driving shaft 71. The drive shaft 71 is used to move the linkage driven member 73 in the same manner of movement as the drive member 72 moves. Wherein the driving member 72 is located outside the exhaust gas guiding chamber 4 and fixedly connected with one end of the driving shaft 71, and the driven member 73 is located inside the exhaust gas guiding chamber 4 and fixedly connected with the other end of the driving shaft 71. The manner in which the driving member 72, the driven member 73, and the drive shaft 71 are fixedly connected includes, but is not limited to, welding, screwing, and integrally forming.

Still further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, the rotating member 6 is provided on the outer wall of the valve cylinder 5 on the side close to the driven member 73 at a position corresponding to the driven member 73, and the driven member 73 abuts against the rotating member 6 to drive the rotating member 6 to rotate in conjunction with the valve cylinder 5. In the present embodiment, the driving member 7 is provided on the first side wall 43 of the exhaust gas guiding chamber 4 on the left side of fig. 3, and therefore the rotating member 6 is also provided on the side of the valve cylinder 5 close to the first side wall 43. In fact, the driving member 7 may also be provided on the second side wall 44 of the exhaust gas guiding chamber 4 on the right side of fig. 3, in which case the rotating member 6 is provided on the side of the valve cylinder 5 close to the second side wall 44.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 2 and 6, a limiting part 45 for limiting the rotational position of the driving member 72 is further provided at a position corresponding to the movement locus of the driving member 72 on the outer peripheral wall surface of the first side wall 43. Of course, the limiting means 45 is used to limit the movement stroke of the driving member 72, and in this embodiment, the limiting means 45 is preferably disposed at a position corresponding to the movement track of the driving member 72, and in fact, the limiting means 45 may be disposed at a position corresponding to the movement track of the driven member 73 to limit the driving member 72. Also, when the driving member 72 is located at the second side wall 44, the limiting part 45 should be disposed at a corresponding position of the second side wall 44.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, the driving member 72 includes a first swing arm and a first fixing pin. The first swing arm extends along the radial direction of the driving shaft 71, one end of the first swing arm is fixedly connected with one end of the driving shaft 71, and the other end of the first swing arm is connected with one end of the first fixing pin. Referring to fig. 2, the limiting part 45 is two limiting pins respectively located at two sides of the first swing arm on the motion track of the first swing arm, and the two limiting pins can respectively abut against two sides of the first swing arm. The distance between the two stop pins is determined by the matching apertures and positions of the valve hole 51 and the exhaust gas through hole 22.

Still further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, the driven member 73 includes a second swing arm and a second fixing pin. The second swing arm extends along the radial direction of the driving shaft 71, one end of the second swing arm is fixedly connected with the other end of the driving shaft 71, and the other end of the second swing arm is connected with one end of the second fixing pin.

Still further, referring to fig. 4, the rotating member 6 is a fork, an opening of which extends in the radial direction of the valve cylinder 5, and the other end of the second fixing pin abuts against an inner wall of the opening and is slidable in the radial direction of the valve cylinder 5 along the opening. The sliding of the second fixing pin in the opening of the fork is a minute sliding amount due to the sliding of the driven member 73 in the radial direction of the driving shaft 71 when the driven member 73 makes a rotational movement around the driving shaft 71. And set up rotary part as the shift fork, through setting up the opening width of shift fork, set up the opening width of shift fork to equal with the diameter of second fixed pin, can play better spacing effect to the second fixed pin, and because the opening of shift fork extends along the radial direction of valve section of thick bamboo 5, can not block the second fixed pin when the second fixed pin moves, guaranteed the smoothness nature of motion. Of course, a person skilled in the art may choose other implementations of the rotating member 6, such as a long hole arranged in the radial direction of the valve cylinder 5, or a circular hole having a diameter slightly larger than the diameter of the second fixing pin. However, in this embodiment, in order to make the movement of the second fixing pin smoother and more stable, the rotary member 6 is preferably provided as a fork.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, the valve cylinder 5 covers at least a portion of the outer peripheral wall surface of the mixing chamber 2 in the direction of the axis A-A of the mixing chamber 2. The valve cylinder 5 is located on the side close to the driving member 7 in the exhaust gas annular chamber, and one side wall of the valve cylinder 5 abuts against the inner peripheral wall surface of the first side wall 43. And, referring to fig. 3, a valve cylinder limit step 23 is formed on the outer circumferential wall surface of the mixing chamber 2, and the other side wall of the valve cylinder 5 abuts against the valve cylinder limit step 23. With such a structure, the valve cylinder stopper step 23 can restrict the movement of the valve cylinder 5 in the axial direction thereof, not only can ensure that the driven member 73 is not separated from the rotary member 6, but also can prevent the center points of the valve hole 51 and the exhaust gas through hole 22 from being offset by a large amount, thereby affecting the control of the state of the exhaust gas through hole 22.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, in a cross section taken along the axis A-A of the mixing chamber 2, the cavity sectional area of the exhaust gas guiding chamber 4 on the side close to the exhaust gas inlet 41 is larger than the cavity sectional area of the other side, which is symmetrical to one side with respect to the axis of the mixing chamber 2, away from the exhaust gas inlet 41. Specifically, since the amount of exhaust gas at the exhaust gas inlet 41 is largest and the flow rate of exhaust gas is highest, the amount of exhaust gas becomes smaller and the flow rate becomes smaller at the position distant from the exhaust gas inlet 41, it is necessary to dispose the volume of the exhaust gas guiding chamber 4 on the side close to the exhaust gas inlet 41 to a larger volume and the volume of the exhaust gas guiding chamber 4 on the side distant from the exhaust gas inlet 41 to a smaller volume, so that the amount and flow rate of exhaust gas entering through the exhaust gas through holes 22 at the respective positions can be made uniform.

Still further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, in a cross section taken along the axis A-A of the mixing chamber 2, referring to fig. 4, the axis B-B of the annular housing of the exhaust gas guiding chamber 4 is closer to the exhaust gas inlet side than the axis D-D of the mixing chamber 2, and in the vertical direction C-C of the axis D-D of the mixing chamber 2, the distance between the annular top wall 42 of the exhaust gas guiding chamber 4 on the side close to the exhaust gas inlet 41 and the outer wall of the valve cylinder 5 is larger than the distance between the annular top wall 42 on the other side and the outer wall of the valve cylinder 5; and/or the distance between the first side wall 43 and the second side wall 44 on the side of the exhaust gas guiding chamber 4 close to the exhaust gas inlet 41 is greater than the distance on the other side away from the exhaust gas inlet 41 in the direction of the axis A-A of the mixing chamber 2, and the distance between the first side wall 43 and the second side wall 44 varies linearly in the circumferential direction of the mixing chamber 2, being smallest at a position opposed to the exhaust gas inlet 41. That is, in order to realize that the volume of the exhaust gas guiding chamber 4 on the side close to the exhaust gas inlet 41 is larger than the volume of the exhaust gas guiding chamber 4 on the side away from the exhaust gas inlet 41 in the present embodiment, there are three realization modes: first, the distance between the first side wall 43 and the second side wall 44 is set to be equal everywhere, but on the side close to the exhaust gas inlet 41, the distance between the annular top wall 42 and the valve cartridge 5 is larger, and on the side far from the exhaust gas inlet 41, the distance between the annular top wall 42 and the valve cartridge 5 is smaller. Second, the distance between the annular top wall 42 and the valve cartridge 5 is equal on both the side close to the exhaust gas inlet 41 and the side away from the exhaust gas inlet 41, but the distance between the first side wall 43 and the second side wall 44 is set to linearly decrease in the direction away from the exhaust gas inlet 41. Third, the distance between the first side wall 43 and the second side wall 44 is set to linearly decrease in the direction away from the exhaust gas inlet 41 while the distance between the annular top wall 42 and the valve cartridge 5 is larger on the side close to the exhaust gas inlet 41 and the distance between the annular top wall 42 and the valve cartridge 5 is smaller on the side away from the exhaust gas inlet 41.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, the main communication pipe includes the air pipe 11, the mixing pipe 21, and the exhaust pipe 31, which are connected end to end in this order. Also, the cavity of the air duct 11 forms the air chamber 1, the cavity of the mixing duct 21 forms the mixing chamber 2, and the cavity of the exhaust duct 31 forms the exhaust chamber 3. Wherein, both ends of the mixing pipe 21 in the axial direction are respectively clamped into bayonets of the corresponding ends of the air pipe 11 and the exhaust pipe 31. The annular housing of the exhaust gas guide chamber 4 is fitted over the outer peripheral wall of the mixing duct 21. Specifically, the air duct 11 and the mixing duct 21 are provided with stepped surfaces on the side thereof, and the exhaust duct 31 and the mixing duct 21 are provided with stepped surfaces on the side thereof, and the mixing duct 21 is abutted against the corresponding stepped surfaces to thereby achieve the engagement. In this way, the air duct 11, the mixing duct 21 and the exhaust duct 31 can be firmly connected, and the step surface has good sealing performance, so that gas loss can be avoided.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, an annular top wall 42 of the annular housing is integrally formed with a second side wall 44 at one side end portion of the exhaust duct 31 that is engaged with the mixing duct 21. The first side wall 43 of the annular housing is integrally formed at one end portion of the air duct 11 engaged with the mixing duct 21. And, referring to fig. 6, the first side wall 43 abuts against the respective ends of the annular top wall 42 with an annular sealing member 46 provided therebetween. The provision of the annular sealing member 46 also further improves the sealing performance of the egr mixer, preventing outflow of exhaust gas.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 5, a first seal member 24 provided on the outer wall of the mixing chamber 2 surrounding the outer periphery of each exhaust gas through hole 22 is further included. And a second seal member 25 provided on the outer wall of the mixing chamber 2, extending in the circumferential direction of the mixing chamber 2 in close contact with the outer wall of the mixing chamber 2, and connecting any adjacent two of the first seal members 24. The first sealing member 24 and the second sealing member 25 can fill the gap between the inner wall surface of the valve cylinder 5 and the outer wall surface of the mixing chamber 2 to seal the exhaust gas and prevent a large amount of exhaust gas from leaking. The first seal member 24 and the second seal member 25 are preferably made of a material having a small friction coefficient, so that the relative rotation between the valve cartridge 5 and the mixing chamber 2 can be ensured to be smoother without causing any sticking.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 5, a third seal member 26 provided on the outer wall of the mixing chamber 2, located on one side of the exhaust gas through hole 22 and extending in the circumferential direction of the mixing chamber 2 in close proximity to the outer wall of the mixing chamber 2 is further included. The third sealing member 26 may be provided at either side of the exhaust gas through-hole 22 or at both sides of the exhaust gas through-hole 22, functioning as an auxiliary seal and an auxiliary sliding guide.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, referring to fig. 3, a boss 74 provided between the drive shaft 71 and the first side wall 43 and covering and supporting the drive shaft 71 is further included. The bushing 74 is fixedly connected to the first side wall 43 and rotatably connected to the drive shaft 71. And a fourth sealing member 75 disposed between the sleeve 74 and the first swing arm of the driving member 72, a disc spring structure may be employed to prevent leakage of exhaust gas between the sleeve 74 and the driving shaft 71 while suppressing axial play of the driving shaft 71 (fig. 6). Further, fifth sealing members (not shown) provided on both side walls of the mixing chamber 2 are also included, which can achieve an effect of sealing the exhaust gas.

Further, in the exhaust gas recirculation mixer of the engine intake and exhaust system according to the present invention, the plurality of exhaust gas through holes 22 and the plurality of valve holes 51 each include at least one row of exhaust gas through holes 22 and at least one row of corresponding valve holes 51 arranged in the circumferential direction of the mixing chamber 2 and the valve barrel 5 in the axial direction of the main communication pipe. Wherein each row of exhaust gas through holes 22 and the corresponding valve holes 51 are uniformly arranged along the axial interval of the mixing chamber 2.

Example 2:

this embodiment describes an assembly process of an exhaust gas recirculation mixer of an engine intake and exhaust system according to embodiment 1.

Referring to fig. 6 and 3, the air duct 11 and the exhaust duct 31 are respectively engaged with the side wall of the mixing duct 21. The air duct 11 is integrally formed with a first side wall 43 at a position where the mixing duct 21 is engaged. The exhaust duct 31 is integrally formed with a second side wall 44 at a position where the mixing duct 21 is engaged. And, the second side wall 44 is also integrally formed with the annular top wall 42.

The valve cylinder 5 is sleeved on the outer wall of the mixing pipe 21, and the outer peripheral wall of the mixing pipe 21 is provided with an exhaust gas through hole 22 in advance and is stuck or integrally formed with the mixing pipe 21 with a first sealing member 24, a second sealing member 25 and a third sealing member 26. The outer wall surface of the valve cylinder 5 is integrally formed or welded with a shift fork.

The first side wall 43 is provided with a through hole through which the sleeve 74 passes. The sleeve is of a circular cylindrical structure, the outer circumference of the sleeve is fixedly mounted in the through hole of the first side wall 43, the outer circumference of the driving shaft 71 is covered, the driving shaft 71 is inserted into the inner hole of the sleeve 74, a fourth sealing member 75 is mounted between the driving member 72 of the driving shaft 71 and the sleeve 74, and then the driving member 72 and the driven member 73 are mounted at both ends of the driving shaft 71. Thereafter, two limiting members 45 are mounted and fixed at positions of the first side wall 43 corresponding to the driving members 72.

An annular sealing member 46 is placed at one side end of the annular top wall 42 adjacent to the first side wall 43, and the first side wall 43 is connected to the annular top wall 42 with the air duct 11 in a screw-coupling manner. In addition, the second fixing pin of the driven member 73 is inserted into the opening of the fork at the time of assembly.

An air inlet of the air duct 11 is connected to an outlet of an air cleaner in an intake and exhaust system of the engine. The exhaust gas inlet 41 is connected to a low pressure exhaust gas recirculation cooler in the engine's exhaust gas intake system to receive cooled exhaust gas. The exhaust port of the exhaust duct 31 is connected to the input port of the compressor.

In order to ensure corrosion resistance and rigidity of the egr mixer, the valve cylinder 5 is preferably made of a metal material, and the main communication pipe may be made of a metal material or other nonmetallic mixed materials with good thickness and rigidity. The rotating member 6 and the driving member 7 functioning as a rotation driving function are preferably provided as a steel material.

Example 3:

this embodiment describes the operation of the exhaust gas recirculation mixer of the engine intake and exhaust system according to embodiment 1.

Referring to fig. 2, air filtered through the air cleaner enters through the inlet of the air chamber 1, and engine exhaust cooled through the low pressure exhaust gas recirculation cooler enters from the exhaust gas inlet 41 and is temporarily stored inside the exhaust gas guiding chamber 4.

Referring to fig. 3, an output shaft of a motor (not shown) is fixedly connected to one end of a connecting rod (not shown) extending in a radial direction of the mixing chamber 2, and a rotation axis of the output shaft of the motor is parallel to a rotation axis of the valve cylinder 5. The other end of the link is fixedly connected with a first fixing pin of the driving member 72. When the motor rotates, the output shaft drives the connecting rod to rotate around the output shaft, and the connecting rod drives the driving member 72 to rotate. The driving member 72 rotates the driven member 73 via the driving shaft 71. Since the second fixing pin of the driven member 73 penetrates the rotating part 6, when the driven member 73 rotates, the rotating part 6 can be driven to rotate around the axis of the valve cylinder 5, and the valve cylinder 5 fixedly connected with the rotating part 6 can be linked to rotate around the axis of the valve cylinder.

Referring to fig. 3, when the valve cartridge 5 is rotated until the valve hole 51 is completely overlapped with the exhaust gas through-hole 22, i.e., the center of the valve hole 51 coincides with the center of the exhaust gas through-hole 22, the exhaust gas through-hole 22 is in a fully opened state. The exhaust gas temporarily stored in the exhaust gas guide chamber 4 at this time largely enters the mixing chamber 2 through the passage for the exhaust gas to circulate formed by the valve hole 51 and the exhaust gas through hole 22, and is mixed with air.

When the valve cartridge 5 continues to rotate, the center of the valve hole 51 is not coincident with the center of the exhaust gas through hole 22, and the wall of the valve cartridge 5 partially covers the exhaust gas through hole 22, the exhaust gas through hole 22 is in a partially opened state. At this time, a small amount of exhaust gas temporarily stored in the exhaust gas guide chamber 4 enters the mixing chamber 2 through the passage formed by the valve hole 51 and the exhaust gas through-hole 22 through which the exhaust gas flows, and is mixed with air.

The valve cylinder 5 is continuously rotated, and the opening area of the exhaust gas through hole 22 becomes smaller, that is, the aperture of the passage through which the exhaust gas flows becomes smaller. When the valve cartridge 5 is rotated to completely cover the exhaust gas through-hole 22, the exhaust gas through-hole 22 is in the fully closed state. At this time, the waste gas temporarily stored in the waste gas guiding chamber 4 does not enter the mixing chamber 2 and is not mixed with air.

Example 4:

based on the exhaust gas recirculation mixer of the engine air intake and exhaust system described above, the present embodiment provides an engine air intake and exhaust system, and in particular, refer to fig. 7. The engine intake and exhaust system 8 provided in this embodiment includes the exhaust gas recirculation mixer 81, the engine body 87, the high-pressure exhaust gas recirculation cooler 84, the high-pressure exhaust gas recirculation valve 85, and the low-pressure exhaust gas recirculation cooler 86 of the engine intake and exhaust system described in the above embodiments.

Further, in the engine intake and exhaust system according to the present invention, the intake end of the engine body 87 communicates with the intake pipe 82, and the exhaust end communicates with the exhaust pipe 83. Wherein, an air filter 821, an exhaust gas recirculation mixer 81, a compressor 822, an intercooler 823 and a throttle valve 824 through which gas flows in sequence are arranged on the air inlet pipeline 82, and a turbine 831 and a catalyst 832 through which gas flows in sequence are arranged on the air outlet pipeline 83; wherein an air inlet of the exhaust gas recirculation mixer 81 is connected to an exhaust end of the air cleaner 821 and a mixer outlet of the exhaust gas recirculation mixer 81 is connected to an intake end of the compressor 822.

Further, in the engine intake and exhaust system according to the present invention, the high-pressure exhaust gas recirculation cooler 84 and the high-pressure exhaust gas recirculation valve 85 are connected in series. Wherein the intake end of the high-pressure exhaust gas recirculation cooler 84 communicates with an exhaust line between the exhaust end of the engine block 87 and the turbine 831, the exhaust end of the high-pressure exhaust gas recirculation cooler 84 communicates with the intake end of the high-pressure exhaust gas recirculation valve 85, and the exhaust end of the high-pressure exhaust gas recirculation valve 85 communicates with the intake line 82 between the intake end of the engine block 87 and the throttle valve 824.

Further, in this engine intake and exhaust system according to the present invention, the intake end of the low-pressure exhaust gas recirculation cooler 86 communicates with the exhaust gas line 83 between the turbine 831 and the catalyst 832, or with the internal exhaust gas output port of the catalyst 832, or with the exhaust gas line 83 of the exhaust end of the catalyst 832, and the exhaust end of the low-pressure exhaust gas recirculation cooler 86 communicates with the exhaust gas inlet 41 of the exhaust gas recirculation mixer 81. That is, the intake end of the low-pressure egr cooler 86 has three connection points, the first being the exhaust line 83 connected between the turbine 831 and the catalyst 832; the second is an internal exhaust gas outlet connected to the catalyst 832, and the third is an exhaust pipe 83 connected to the exhaust end of the catalyst 832.

Further, in the engine intake and exhaust system according to the present invention, referring to fig. 7, air in the environment flows into the compressor 822 after impurities in the air are removed by the air cleaner 821. The gas is compressed by the compressor 822 and cooled by the intercooler 823, and a high-density low-temperature gas is output. The low-temperature high-density gas is introduced into the engine block 87 by controlling the flow rate of the gas through the throttle valve 824. In the engine block 87, the gas and the fuel are mixed and combusted to generate exhaust gas, and the exhaust gas is discharged to the turbine 831 to apply work to the compressor 822, and then flows into the catalyst 832 to be subjected to catalytic treatment and then discharged to the atmosphere.

The high-pressure exhaust gas recirculation cooler 84 may cool the high-temperature exhaust gas discharged from the engine block 87 before the exhaust gas is discharged to the turbine 831, and may circulate the exhaust gas to the engine block 87 by controlling the flow rate thereof through the high-pressure exhaust gas recirculation valve 85 and then feeding the exhaust gas into the intake line 82. The low-pressure exhaust gas recirculation cooler 86 may cool the exhaust gas flowing through the turbine 831 and may introduce the cooled exhaust gas into the exhaust gas inlet 41 of the exhaust gas recirculation mixer 81 shown in fig. 6.

With such a structure, since the exhaust gas recirculation mixer 81 provided in the engine intake and exhaust system 8 has the valve barrel 5 and the mixing chamber 2 which are relatively rotatable, and the mixing chamber 2 is provided with the exhaust gas through-hole 22 in the circumferential direction thereof, the valve barrel 5 is provided with the valve hole 51 corresponding to the exhaust gas through-hole 22 in the circumferential direction thereof. By means of the relative rotation of the mixing chamber 2 and the valve cylinder 5, the flow rate of the gas in the exhaust gas guiding chamber 4 into the mixing chamber 2 can be regulated by regulating the caliber of the channel formed by the valve hole 51 and the exhaust gas through hole 22. Therefore, the engine air intake and exhaust system 8 can realize regulation and control of the exhaust gas flow without arranging a low-pressure exhaust gas circulation valve. In addition, because the waste gas is temporarily stored in the waste gas guiding chamber 4, the distance between the waste gas guiding chamber 4 and the mixing cavity 2 is quite close, so that the rapid mixing of air and waste gas can be realized; and the exhaust gas flows in from the plurality of exhaust gas through holes 22 which are uniformly distributed in the vertical direction with respect to the air flow, the mixing uniformity of the exhaust gas and the air can be further improved. In addition, since the engine intake and exhaust system 8 can achieve rapid and uniform mixing of air and exhaust gas, and the mixing chamber 2 forms a suction function of minimum static pressure at the exhaust gas through hole 22, the exhaust gas recirculation mixer 81 can suck more exhaust gas and introduce exhaust gas into the intake pipe 82 as much as possible, and the exhaust gas circulation rate is high.

While the invention has been shown and described with reference to certain preferred embodiments thereof, it will be understood by those skilled in the art that the foregoing is a further detailed description of the invention with reference to specific embodiments, and it is not intended to limit the practice of the invention to those descriptions. Various changes in form and detail may be made therein by those skilled in the art, including a few simple inferences or alternatives, without departing from the spirit and scope of the present invention.

Claims

1. An exhaust gas recirculation mixer, comprising:

the main communication pipeline comprises an air cavity for air inflow, a mixing cavity for mixing air and engine waste gas and an exhaust cavity for discharging the mixed gas, which are sequentially arranged and communicated, wherein the mixing cavity is provided with a plurality of waste gas through holes along the circumferential direction;

the exhaust gas guiding chamber comprises an annular shell, the annular shell is arranged in a surrounding mode and is fixed on the periphery of the mixing cavity in a sealing mode, an exhaust gas ring cavity is formed between the inner periphery of the annular shell and the periphery of the mixing cavity, and an exhaust gas inlet for engine exhaust gas to enter the exhaust gas ring cavity is formed in the annular shell;

The valve cylinder is positioned in the waste gas annular cavity, is tightly sleeved on the periphery of the mixing cavity, can rotate relative to the mixing cavity along the periphery of the mixing cavity around the axis of the mixing cavity, and is provided with a plurality of valve holes which are matched with the plurality of waste gas through holes one by one along the circumferential direction of the valve cylinder; and

the rotary driving assembly comprises a rotary part fixedly arranged on the outer wall of the valve cylinder and a driving part rotatably arranged on the annular shell of the waste gas guide chamber and matched with the rotary part, and the driving part can rotate relative to the annular shell and drive the rotary part to link the valve cylinder to rotate relative to the mixing cavity around the axis of the mixing cavity so as to control the waste gas through hole to switch between the full-open state, the partial-open state and the full-closed state relative to the valve hole.

2. The exhaust gas recirculation mixer of claim 1, wherein in a cross section taken along the axis of the mixing chamber, the inner diameter dimension of the mixing chamber tapers from both ends to a middle portion, and the inner diameter dimension of the mixing chamber is smallest in the middle portion of the mixing chamber; and is also provided with

The plurality of exhaust gas through holes are uniformly arranged in the middle of the mixing cavity at intervals along the circumferential direction of the mixing cavity.

3. The egr mixer of claim 2, wherein the inner diameter dimension of the mixing chamber is linearly reduced from both ends to the middle portion, respectively, in a cross section taken along the axis of the mixing chamber.

4. The exhaust gas recirculation mixer of claim 1, wherein the annular housing of the exhaust gas guide chamber is "pi" shaped in cross section taken along the axis of the mixing chamber, comprising an annular top wall, and first and second side walls on either side of the annular top wall; and is also provided with

The waste gas inlet is formed on the annular top wall in a penetrating manner and is communicated with the waste gas annular cavity and an external waste gas pipeline; and is also provided with

In the axis extending direction of the mixing cavity, one end of the first side wall far away from the annular top wall is fixed on one end peripheral wall of the mixing cavity, and one end of the second side wall far away from the annular top wall is fixed on the other end peripheral wall of the mixing cavity.

5. The exhaust gas recirculation mixer of claim 4, wherein the drive member comprises a drive shaft disposed therethrough on the first side wall; and

The driving component and the driven component are respectively arranged at two ends of the driving shaft, wherein the driving component is positioned outside the waste gas guiding chamber and is fixedly connected with one end of the driving shaft, and the driven component is positioned inside the waste gas guiding chamber and is fixedly connected with the other end of the driving shaft; and is also provided with

The rotary part is arranged on the outer wall of the valve cylinder, which is close to one side of the driven component, and corresponds to the driven component, and the driven component is abutted to the rotary part so as to drive the rotary part to link the valve cylinder to rotate.

6. The exhaust gas recirculation mixer according to claim 5, wherein the outer peripheral wall surface of the first side wall is further provided with a stopper member for restricting a rotational position of the driving member at a position corresponding to a movement locus of the driving member.

7. The egr mixer of claim 6, wherein the drive member includes a first swing arm and a first fixed pin; wherein the method comprises the steps of

The first swing arm extends along the radial direction of the driving shaft, one end of the first swing arm is fixedly connected with one end of the driving shaft, and the other end of the first swing arm is connected with one end of the first fixing pin;

The limiting component is two limiting pins which are respectively positioned at two sides of the first swing arm on the motion track of the first swing arm, and the two limiting pins can be respectively abutted with two sides of the first swing arm; and is also provided with

The driven member comprises a second swing arm and a second fixing pin; wherein the method comprises the steps of

The second swing arm extends along the radial direction of the driving shaft, one end of the second swing arm is fixedly connected with the other end of the driving shaft, and the other end of the second swing arm is connected with one end of the second fixing pin;

the rotary part is a shifting fork, an opening of the shifting fork extends along the radial direction of the valve cylinder, and the other end of the second fixing pin is in butt joint with the inner wall of the opening and can slide along the opening in the radial direction of the valve cylinder.

8. The exhaust gas recirculation mixer according to claim 7, wherein the valve cylinder covers at least a part of an outer peripheral wall surface of the mixing chamber in an axial direction of the mixing chamber; wherein the method comprises the steps of

The valve cylinder is positioned in the exhaust gas annular cavity and is close to the side where the driving part is positioned, and one side wall of the valve cylinder is abutted against the inner peripheral wall surface of the first side wall; and is also provided with

The outer peripheral wall surface of the mixing cavity is provided with a valve cylinder limiting step, and the other side wall of the valve cylinder is abutted against the valve cylinder limiting step.

9. The exhaust gas recirculation mixer of any of claims 1-8, wherein a cross-sectional area of a cavity of the exhaust gas guide chamber on a side near the exhaust gas inlet is greater than a cross-sectional area of a cavity on the other side, symmetrical to the one side with respect to the axis of the mixing chamber, remote from the exhaust gas inlet in a cross-section taken along the axis of the mixing chamber.

10. The exhaust gas recirculation mixer of any of claims 4-8, wherein, in a cross section taken along the axis of the mixing chamber,

the axis of the annular housing of the exhaust gas guiding chamber is closer to the exhaust gas inlet side than the axis of the mixing chamber, and in the direction perpendicular to the axis of the mixing chamber, the distance between the annular top wall of the exhaust gas guiding chamber on the side close to the exhaust gas inlet and the outer wall of the valve cylinder is larger than the distance between the annular top wall on the other side and the outer wall of the valve cylinder; and/or

The distance between the first side wall and the second side wall on one side of the exhaust gas guiding chamber near the exhaust gas inlet is larger than the distance on the other side away from the exhaust gas inlet in the axial direction of the mixing chamber, and the distance between the first side wall and the second side wall in the circumferential direction of the mixing chamber varies linearly and is smallest at a position opposite to the exhaust gas inlet.

11. The exhaust gas recirculation mixer of claim 10, wherein

The main communication pipeline comprises an air pipeline, a mixing pipeline and an exhaust pipeline which are sequentially connected end to end, wherein the cavity of the air pipeline forms the air cavity, the cavity of the mixing pipeline forms the mixing cavity, and the cavity of the exhaust pipeline forms the exhaust cavity; wherein the method comprises the steps of

Two ends of the mixing pipeline in the axial direction are respectively clamped into bayonets at the corresponding ends of the air pipeline and the exhaust pipeline; and is also provided with

The annular shell of the exhaust gas guiding chamber is sleeved on the peripheral wall of the mixing pipeline.

12. The exhaust gas recirculation mixer of claim 11, wherein

The annular top wall and the second side wall of the annular shell are integrally formed at one end part of the exhaust pipeline, which is clamped with the mixing pipeline; and is also provided with

The first side wall of the annular shell is integrally formed at one side end part of the air pipeline, which is clamped with the mixing pipeline; and is also provided with

The first side wall abuts a respective end of the annular top wall with an annular sealing member disposed therebetween.

13. The exhaust gas recirculation mixer of claim 12, further comprising

A first sealing member provided on an outer wall of the mixing chamber, surrounding an outer periphery of each of the exhaust gas through holes;

the second sealing component is arranged on the outer wall of the mixing cavity, is clung to the outer wall of the mixing cavity, extends along the circumferential direction of the mixing cavity, and is connected with any two adjacent first sealing components;

the third sealing component is arranged on the outer wall of the mixing cavity, is positioned at one side of the exhaust gas through hole, is clung to the outer wall of the mixing cavity and extends along the circumferential direction of the mixing cavity;

a shaft sleeve arranged between the driving shaft and the first side wall and coating the periphery of the driving shaft;

a fourth sealing member disposed between the sleeve and the first swing arm; and

and a fifth sealing member arranged on two side walls of the mixing cavity.

14. The exhaust gas recirculation mixer of claim 1, wherein the plurality of exhaust gas through holes and the plurality of valve holes each include at least one row of exhaust gas through holes and at least one row of corresponding valve holes arranged in the circumferential direction of the mixing chamber and the valve barrel in the axial direction of the main communication pipe; wherein the method comprises the steps of

Each row of exhaust gas through holes and corresponding valve holes are uniformly arranged along the axial interval of the mixing cavity.

15. An engine exhaust and intake system comprising an exhaust gas recirculation mixer according to any one of claims 1 to 14; and

the engine body, the air inlet end of the said engine body is communicated with air inlet pipeline, exhaust end is communicated with exhaust pipeline; the exhaust system comprises an exhaust pipe, an exhaust gas recirculation mixer, an air compressor, an intercooler and a throttle valve, wherein an air filter, the exhaust gas recirculation mixer, the air compressor, the intercooler and the throttle valve are arranged on the exhaust pipe, and a turbine and a catalyst are arranged on the exhaust pipe, wherein the air filter, the air compressor, the intercooler and the throttle valve are used for enabling gas to flow through in sequence; the air inlet of the exhaust gas recirculation mixer is connected with the exhaust end of the air filter, and the mixer outlet of the exhaust gas recirculation mixer is connected with the air inlet end of the air compressor; and

a high-pressure exhaust gas recirculation cooler and a high-pressure exhaust gas recirculation valve connected in series; wherein an air inlet end of the high-pressure exhaust gas recirculation cooler is communicated with the air inlet pipeline between the air inlet end of the engine body and the turbine, an air outlet end of the high-pressure exhaust gas recirculation cooler is communicated with an air inlet end of the high-pressure exhaust gas recirculation valve, and an air outlet end of the high-pressure exhaust gas recirculation valve is communicated with the air inlet pipeline between the air inlet end of the engine body and the throttle valve; and

A low pressure egr cooler, the inlet end of which communicates with the exhaust line between the turbine and the catalyst, or with the exhaust line of the exhaust end of the catalyst, the exhaust end of which communicates with the exhaust gas inlet of the egr mixer.