WO2013170559A1 - 一种egr冷却器的废气进气端结构 - Google Patents

一种egr冷却器的废气进气端结构 Download PDF

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Publication number
WO2013170559A1
WO2013170559A1 PCT/CN2012/081228 CN2012081228W WO2013170559A1 WO 2013170559 A1 WO2013170559 A1 WO 2013170559A1 CN 2012081228 W CN2012081228 W CN 2012081228W WO 2013170559 A1 WO2013170559 A1 WO 2013170559A1
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WO
WIPO (PCT)
Prior art keywords
chamber
pipe
egr cooler
inlet
diameter end
Prior art date
Application number
PCT/CN2012/081228
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English (en)
French (fr)
Inventor
张文锋
覃小军
赵优琪
刘浩
Original Assignee
浙江银轮机械股份有限公司
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Application filed by 浙江银轮机械股份有限公司 filed Critical 浙江银轮机械股份有限公司
Priority to US14/110,116 priority Critical patent/US9157397B2/en
Priority to CN201280071544.6A priority patent/CN104797805B/zh
Priority to EP12876993.2A priority patent/EP2851548B1/en
Priority to EP16182156.6A priority patent/EP3153806B1/en
Publication of WO2013170559A1 publication Critical patent/WO2013170559A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements
    • F28F9/0239—Header boxes; End plates floating elements floating header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0295—Other particular headers or end plates comprising cooling circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention belongs to the technical field of heat exchangers, and relates to an improvement of the structural form of an engine exhaust gas recirculation cooler and an improvement of structural reliability, in particular to an exhaust gas inlet end structure of an EGR cooler. Background technique
  • Exhaust gas recirculation technology is one of the main technical routes for the engine to achieve national emissions above 4.
  • the exhaust gas is cooled to a certain temperature by an exhaust gas recirculation cooler (abbreviation: EGR cooler) before it enters the engine cylinder.
  • EGR cooler exhaust gas recirculation cooler
  • the operating temperature of the hot side of the EGR cooler on the hot side is generally between 120 ° C and 730 ° C, and the temperature of the cold side coolant is between 80 ° C and 120 ° C. Therefore, during the operation of the EGR cooler, the wall temperature of the cooling pipe is high, and the longitudinal thermal expansion causes deformation failure at the joint between the cooling pipe and the main plate.
  • the temperature of the exhaust end of the EGR cooler is usually between 500 ° C and 730 ° C.
  • the inside of the intake chamber is in direct contact with the exhaust gas, and the outside is directly in contact with the ambient air.
  • the temperature of the inner wall of the inlet chamber is usually reached. 400 ° C ⁇ 600 ° C;
  • the intake side of the main board is directly subjected to the frontal impact of high temperature exhaust gas, although the other side is in contact with the coolant, but the maximum temperature of the wall surface of the main board also reaches between 400 ° C ⁇ 600 ° C;
  • the high temperature thermal deformation of the inlet chamber and the main plate is another important cause of failure of the EGR cooler.
  • the periphery of the main board of the general EGR cooler is usually connected with the inlet chamber and the water shell at the same time.
  • the present invention has been made in view of the above problems in the prior art, and it is intended to provide an improved exhaust gas intake end structure for an EGR cooler for an engine, which significantly improves the reliability of the EGR cooler.
  • An exhaust gas intake end structure of an EGR cooler comprising a water casing, an intake pipe, a bellows, a heat insulating pipe inlet chamber, a pre-cooling water chamber and a main plate, wherein the water casing is provided with an inlet pipe, and the characteristic thereof
  • the intake pipe, the bellows, the pre-cooling water chamber and the water casing are sequentially connected; the heat insulating pipe is placed in the bellows, One end is coupled to the intake pipe and the other end is suspended;
  • the inlet chamber is a two-stage variable diameter pipe body, including a large diameter end, a middle portion pipe body and a small diameter end end, and the large diameter end portion is
  • the main board is coupled to form an air inlet chamber, and a space is reserved between the coupling portion and the water housing to form a coolant passage; the outer surface of the middle portion of the tube body and the bellows and/or pre-cooling water
  • the end of the chamber is coupled to form a pre-cooling chamber
  • the transition step plane between the middle portion of the EGR cooler inlet chamber and the large-diameter end has a certain axial displacement compensation function, which can adapt to the displacement compensation of the axial thermal expansion during operation of the EGR cooler.
  • the EGR cooler exhaust gas inlet end of the main board is connected with the inlet chamber and has a certain space between the water housing and the water housing to form a cooling liquid passage of the pre-cooling chamber, and the periphery of the main board is not covered by the water housing. Constrained, able to adapt to the need for lateral thermal expansion of the motherboard.
  • the inner surface of the small-diameter end of the inlet chamber of the EGR cooler is in contact with the middle of the heat-insulating tube and is not fixed, and the heat-insulating tube is radially supported, and the axial direction can be slipped, thereby improving the heat-insulating tube. Its anti-vibration performance provides excellent protection for insulated pipes and bellows.
  • the intake end of the EGR cooler exhaust gas is connected to the pre-cooling water chamber and the intake pipe through a bellows, and has a large degree of freedom displacement compensation function, and can adapt to the displacement compensation requirement caused by the thermal expansion deformation of the intake pipe.
  • the pre-cooling water chamber is added, which reduces the wall temperature of the main board and the inlet chamber, and significantly improves the reliability of the EGR cooler.
  • the intermediate portion of the air inlet chamber is designed with an expansion joint, which can increase the axial displacement compensation amount, and can better adapt to the displacement compensation of the axial thermal expansion of the EGR cooler during operation.
  • the suspension end of the heat insulating tube is a bell mouth, which can function to improve the air flow.
  • the bellows has a double-layer structure, and the inner and outer layers of the bellows are only in contact with each other without welding; the thickness of the single-layer bellows is 0.25-0.6 mm, and the number of nodes is 5 ⁇ 10, the height of the node is 6 ⁇ 12 mm. Since the bellows has a two-layer structure, the bellows joint strength can be improved.
  • the EGR cooler inlet pipe is disposed close to the main board position At the location, the coolant can fully enter the pre-cooling chamber, directly cooling the main board and the outdoor surface of the intake air, reducing the wall temperature of the main board and the inlet chamber, and reducing the amount of thermal expansion and deformation.
  • the present invention also provides an intake end structure of another structure of an EGR exhaust gas cooler, comprising a water casing, an intake pipe, a heat insulating pipe inlet chamber, a pre-cooling water chamber and a main plate, wherein the water casing is provided
  • the inlet pipe is characterized in that the two ends of the pre-cooling water chamber are respectively coupled with the intake pipe and the water casing; the insulated pipe is placed in the pre-cooling water chamber, one end is connected with the intake pipe, and the other end is connected Suspension; the inlet chamber is a reducer tube, including a large diameter end and a small diameter end, the large diameter end is coupled with the main plate to form an air inlet chamber, and between the coupling portion and the water housing A space is reserved to form a coolant passage; the outer surface of the small diameter end is coupled to the end of the pre-cooling water chamber to form a pre-cooling chamber in communication with the coolant passage.
  • the exhaust gas inlet end structure of the above EGR cooler provided by the invention is characterized in that: the pre-cooling water chamber is added, the wall surface temperature of the main board and the inlet chamber is lowered; the support is increased in the middle of the heat insulating tube, and the heat insulating tube is improved Anti-vibration performance;
  • the special structure of the inlet chamber increases the axial thermal expansion displacement compensation capability of the EGR cooler.
  • the present invention significantly improves the reliability of the EGR cooler by the above improvements.
  • FIG. 1 is a schematic view showing the overall configuration of a first embodiment of an exhaust gas inlet end structure of an EGR cooler of the present invention.
  • Figure 2 is a schematic view showing the structure of the intake chamber of the embodiment of Figure 1, wherein Figure 2 (1) is a cross-sectional view, and Figures 2 (2), (3) and (4) are right side views of different cross-sectional shapes.
  • Fig. 3 is a schematic structural view showing another embodiment of the EGR cooler exhaust gas inlet end structure of the present invention.
  • Fig. 4 is a schematic view showing the structure of the intake chamber of the embodiment of Fig. 3, wherein Fig. 3 (1) is a cross-sectional view, and Figs. 3 (2) and (3) are right side views of different cross-sectional shapes.
  • Figure 5 is a schematic view showing the structure of an inlet chamber with an expansion joint in the intake end structure of the exhaust gas of the EGR cooler of the present invention, wherein Figure 5 (1) is a two-stage variable diameter pipe body, and Figure 5 (2) is a first-order variable diameter pipe. Tube body.
  • an exhaust gas intake end structure of an EGR cooler of the present invention includes a water housing 3, an intake pipe 9, a bellows 8, an inlet chamber 6, a preheating water chamber 7, and The main body 5, the water casing 3 is provided with an inlet pipe 2, and the water casing 3 is provided with a heat dissipation core 4, and one end of the heat dissipation core 4 is coupled with the main plate 5.
  • the intake pipe 9, the bellows 8, the pre-cooling water chamber 7, and the water casing 3 are sequentially coupled by brazing or argon arc welding.
  • the heat insulating tube 10 is placed in the bellows 8 and has one end welded to the air inlet tube 9 and the other end suspended.
  • the inlet chamber 6 is a two-stage variable diameter pipe body, including a large diameter end 22, a middle portion pipe body 14 and a small diameter end portion 15, and the large diameter end 22 is welded with the main plate 5 to form an intake cavity.
  • a space is reserved between the coupling portion and the water housing 3 to form a coolant passage 23; an outer surface of the intermediate portion tubular body 14 and an end portion of the bellows 8 and the pre-cooling water chamber 7 Welding forms a pre-cooling chamber 13 in communication with the coolant passage 23;
  • the small-diameter end 15 is in contact with the outer surface of the intermediate portion of the heat insulating tube 10 but is not fixedly coupled, and the small diameter of the inlet chamber 6
  • the end supports the radial direction of the insulated pipe 10, and the axial direction can still be relatively slipped.
  • the suspension end of the heat insulating tube 10 is a bell mouth 31, which can function to improve the air flow.
  • the bellows 8 has a double-layer structure, and only the inner and outer layers of the bellows are in contact with each other without welding; the thickness of the single-layer bellows is 0.25-0.6 mm, and the number of nodes is 5-10, The height is 6 ⁇ 12 mm.
  • the double-layer structure can improve the connection strength of the bellows.
  • the inlet pipe 2 is disposed adjacent to the main plate 5, and the coolant can fully enter the pre-cooling chamber 7, directly cooling the outer surfaces of the main plate 5 and the inlet chamber 6, and lowering the wall surface temperature of the main plate 5 and the inlet chamber 6, Reduce thermal expansion and deformation.
  • the exhaust gas intake end structure of the EGR cooler for an engine of the present invention described above comprises three parts of an intake manifold, an intake chamber and a pre-cooling chamber.
  • the intake pipe 9, the double-layer bellows 8 and the heat-insulating pipe 10 constitute an intake pipe group;
  • the periphery of the main plate 5 is welded with the large-diameter end of the intake chamber 6 to form an intake air chamber 24 in the intake chamber 6;
  • the gas chamber 6 is welded to the pre-cooling water chamber to form a pre-cooling chamber between the outer surface of the inlet chamber 6 and the inner surface of the pre-cooling water chamber 7; meanwhile, the pre-cooling water chamber 7 is coupled with the water housing 3, in the water
  • a coolant passage 23 is formed between the casing 3 and the outer periphery of the main plate and the large diameter end 22 of the intake chamber.
  • the large-diameter end 22 of the inlet chamber 6 is in the shape of a cabinet (as shown in Fig. 2 (2) and 2 (4) shown or round (as shown in Figure 2 (3)), the middle part of the inlet chamber 6 has a cross-sectional shape of a cabinet shape (as shown in Figure 2 (4)) or a circle (As shown in Fig. 2 (2) and Fig. 2 (3)), the small-diameter end 15 of the inlet chamber 6 is circular in shape, and the large-diameter end 22 of the inlet chamber 6 and the intermediate portion of the tubular body 14 are formed by a flat step. 12 transitional connections.
  • another structure of an exhaust gas intake end of an EGR cooler of the present invention includes a water casing 3, an intake pipe 5, a heat insulating pipe 50 inlet chamber 56, a pre-cooling water chamber 57, and a main plate 55.
  • the water housing 53 is provided with an inlet pipe 52, wherein the two ends of the pre-cooling water chamber 57 are respectively coupled with the inlet pipe 5 and the water casing 3; In the pre-cooling water chamber 57, one end is coupled to the intake pipe 5, and the other end is suspended.
  • the suspension end is a bell mouth 51;
  • the inlet chamber 56 is a reducing pipe, including a large diameter end 53 and a small
  • the caliber end 54, the large-diameter end 53 is coupled with the main plate 55 to form an air inlet chamber 63, and a space is reserved between the coupling portion and the water housing 53, forming a coolant passage 64;
  • the outer surface of the bore end 54 is coupled to the end of the pre-cooling water chamber 57 to form a pre-cooling chamber 65 in communication with the coolant passage 64.
  • the large-diameter end 53 of the inlet chamber 56 is in the shape of a cabinet (as shown in FIG. 4 (2)) or a circle (as shown in FIG. 4 (3)), and the inlet chamber 56.
  • the small-diameter end 54 is circular in shape, and the large-diameter end 53 of the inlet chamber 56 and the small-diameter end 54 are transiently coupled by a planar step 52.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Exhaust Silencers (AREA)

Abstract

一种EGR冷却器的废气进气端结构，包括：水壳体（3）、进气管（11）、波纹管（8）、隔热管（10）、进气室（6）、预冷水室（7）和主板（5）。水壳体（3）上设有进水管（2）；隔热管（10）置于波纹管（8）内，一端与进气管（11）联接，另一端悬置；进气室的大口径端（22）与主板（5）联接形成进气腔室（24），联接部分与水壳体之间形成冷却液通道（23）；中间部分管体（14）的外表面与波纹管（8）端部联接形成与冷却液通道联通的预冷却腔室（13）；进气室的小口径端（15）与隔热管（10）中间部分的外表面接触。通过增加预冷水室，降低了主板和进气室的壁面温度；由于小口径端对隔热管的支承，提高了隔热管的抗振动性能；由于进气室的特殊结构，增加了EGR冷却器内部轴向热膨胀位移补偿能力。因此，该EGR冷却器的可靠性被显著提高。

Description

一种 EGR冷却器的废气进气端结构
技术领域
本发明属于热交换器技术领域，涉及一种发动机废气再循环冷却器的结构形 式改进和结构可靠性的提高， 具体地说是一种 EGR冷却器的废气进气端结构。 背景技术
废气再循环技术是发动机实现国 4以上排放的主要技术路线之一。废气再循 环进入发动机汽缸之前需要通过废气再循环冷却器 （简称： EGR冷却器） 冷却 到一定温度。 EGR冷却器的热侧高温废气的工作温度一般在 120°C~730°C之间， 冷侧冷却液温度在 80°C~120°C之间。 因此， EGR冷却器在工作过程中， 冷却管 的壁面温度较高，纵向热膨胀会导致冷却管与主板联接处出现变形失效。而 EGR 冷却器的废气进气端温度通常在 500°C~730°C之间， 通常情况下， 进气室内侧直 接与废气接触， 外侧直接环境空气接触， 进气室的内壁面温度通常达到 400°C~600°C之间； 主板的进气侧直接受到高温废气的正面冲击， 虽然另一侧与 冷却液接触， 但是主板的壁面最高温度同样达到 400°C~600°C之间； 进气室与主 板的高温热变形是导致 EGR冷却器失效的另一重要原因。一般的 EGR冷却器的 主板周边通常与进气室、水壳体同时相联接， 当进气室与主板出现高温横向热膨 胀时会受到温度相对低的水壳体的约束而产生变形，当变形严重时就会导致 EGR 冷却器失效。因此， 降低 EGR冷却器壁面温度和释放热膨胀是提高 EGR冷却器 可靠性的有效措施之一。 另外， 一般 EGR冷却器进气管设计波纹管时内衬的隔 热管仅有一端与进气管固定联接， 当隔热管较长时， 在工作过程中由于振动的原 因会导致波纹管或者隔热管失效。 发明内容
本发明要解决的是现有技术存在上述问题，旨在是提供一种改进型的用于发 动机的 EGR冷却器的废气进气端结构， 使 EGR冷却器可靠性得到显著提高。
本发明是通过具有以下技术方案来实现的：
一种 EGR冷却器的废气进气端结构， 包括水壳体、 进气管、 波纹管、 隔热 管进气室、预冷水室和主板， 所述的水壳体上设有进水管， 其特征在于所述的进 气管、波纹管、预冷水室和水壳体依次联接；所述的隔热管置于所述的波纹管内， 一端与所述的进气管联接， 另一端悬置； 所述的进气室为两级变径管体， 包括大 口径端、中间部分管体和小口径端， 所述的大口径端与所述的主板联接形成进气 腔室， 联接部分与水壳体之间保留有一定的空间， 形成冷却液通道； 所述的中间 部分管体的外表面与所述的波纹管和 /或预冷水室的端部联接形成与所述的冷却 液通道联通的预冷却腔室； 所述的小口径端与所述隔热管中间部分的外表面接 触。
本发明的一种 EGR冷却器的废气进气端结构具有以下有益效果：
1、 所述的 EGR冷却器进气室的中间部分管体与大口径端之间的过渡台阶 平面具有一定的轴向位移补偿功能， 能适应 EGR冷却器工作时轴向热膨胀的位 移补偿。
2、 所述的 EGR冷却器废气进气端主板的周边与进气室联接后与水壳体之 间保留有一定的空间，形成预冷却腔室的冷却液通道，主板周边不受水壳体约束， 能够适应主板横向热膨胀释放的需要。
3、 所述的 EGR冷却器进气室小口径端内表面与隔热管的中间接触而不固 定，对隔热管起到径向支承作用，轴向则可以滑移，提高了隔热管的抗振动性能， 能够对隔热管和波纹管起到很好的保护作用。
4、 所述的 EGR冷却器废气进气端通过波纹管与预冷水室和进气管联接， 具有较大自由度的位移补偿功能， 能适应进气管热膨胀变形产生的位移补偿要 求。
5、 增加了预冷水室， 降低了主板和进气室的壁面温度， 显著地提高 EGR 冷却器的可靠性。
作为本发明的进一步改进， 所述进气室的中间部分设计有膨胀节， 可以增 加轴向位移补偿量， 能更好地适应 EGR冷却器工作时轴向热膨胀的位移补偿。
作为本发明的更一步改进， 所述隔热管的悬置端为呈喇叭口， 可以起到改 善气流的作用。
作为本发明的再进一步改进， 所述的波纹管为双层结构， 内外二层波纹管 壁面之间仅接触， 而不进行焊接； 单层波纹管材料厚度为 0.25~0.6mm， 波节数 量为 5~10个， 波节高度为 6~12 mm。 由于波纹管采用双层结构， 可以提高波纹 管联接强度。
作为本发明的更进一步改进，所述的 EGR冷却器进水管布置在靠近主板位 置处， 冷却液能够充分进入预冷却腔室， 直接对主板和进气室外表面进行冷却， 降低主板和进气室的壁面温度， 减少热膨胀和变形量。
本发明还要提供另一种结构的 EGR废气冷却器的进气端结构， 包括水壳 体、 进气管、 隔热管进气室、 预冷水室和主板， 所述的水壳体上设有进水管， 其 特征在于所述的预冷水室两端分别与所述的进气管和水壳体联接；所述的隔热管 置于预冷水室内， 一端与所述的进气管联接， 另一端悬置； 所述的进气室为一变 径管，包括大口径端和小口径端， 所述的大口径端与所述的主板联接形成进气腔 室， 联接部分与水壳体之间保留有一定的空间， 形成冷却液通道； 所述的小口径 端的外表面与所述的预冷水室的端部联接形成与所述的冷却液通道联通的预冷 却腔室。
本发明提供的上述 EGR冷却器的废气进气端结构，其特点是：增加了预冷 水室， 降低了主板和进气室的壁面温度； 隔热管中间增加了支承， 提高了隔热管 的抗振动性能； 进气室的特殊结构， 增加了 EGR冷却器内部轴向热膨胀位移补 偿能力。 本发明通过以上改进， 显著地提高 EGR冷却器可靠性。
附图说明
图 1是本发明的 EGR冷却器废气进气端结构的第一种实施方式的总体结构 示意图。
图 2是图 1实施方式的进气室结构示意图， 其中图 2 ( 1 ) 为剖视图， 图 2 (2)、 (3) 和 （4) 为不同截面形状时的右视图。
图 3是与本发明 EGR冷却器废气进气端结构的另一种实施方式的结构示意 图。
图 4是本图 3实施方式的进气室结构示意图， 其中图 3 ( 1 )为剖视图， 图 3 (2) 和 （3) 为不同截面形状时的右视图。
图 5是本发明的 EGR冷却器废气进气端结构中带有膨胀节的进气室结构示 意图， 其中图 5 ( 1 ) 为两级变径管体， 图 5 (2) 为一级变径管体。
图中， 1-进水口， 2-进水管， 3-水壳体， 4-， 5-散热芯子， 5-主板， 6-进气室， 7-预冷水室， 8-波纹管， 9-进气管， 10-隔热管， 11-进气管， 12-台阶平面， 13-预 冷却腔室， 14-进气室的中间部分管体， 15-进气室的小口径端， 16-波纹管的一端， 18-圆管， 20-方管， 21-膨胀节， 22-进气室大口径端， 23-冷却液通道， 24-进气腔 室， 31-隔热管的喇叭口， 50-隔热管， 51-喇叭口， 52-进气室的台阶平面， 53-进 气室的大口径端， 54-进气室的小口径端， 55-主板， 56-进气室， 57-预冷水室， 59-进气管， 63-进气腔室， 64-冷却液通道， 65-预冷却腔室。
具体实施方式
下面结合附图以具体实施例对本发明进行进一步描述。
参照图 1和图 2， 本发明的一种 EGR冷却器的废气进气端结构， 包括水壳 体 3、 进气管 9、 波纹管 8、 隔热管 10进气室 6、 预冷水室 7和主板 5， 所述的 水壳体 3上设有进水管 2， 水壳体 3内设有散热芯子 4， 散热芯子 4的一端与主 板 5联接。 所述的进气管 9、 波纹管 8、 预冷水室 7和水壳体 3通过钎焊或氩弧 焊依次联接。 所述的隔热管 10置于所述的波纹管 8内， 一端与所述的进气管 9 焊接， 另一端悬置。 所述的进气室 6为两级变径管体， 包括大口径端 22、 中间 部分管体 14和小口径端 15， 所述的大口径端 22与所述的主板 5焊接形成进气 腔室 24， 联接部分与水壳体 3之间保留有一定的空间， 形成冷却液通道 23; 所 述的中间部分管体 14的外表面与所述的波纹管 8和预冷水室 7的端部焊接形成 与所述的冷却液通道 23联通的预冷却腔室 13; 所述的小口径端 15与所述隔热 管 10中间部分的外表面接触但无固定联接， 进气室 6的小口径端对于隔热管 10 的径向起到支承作用， 轴向则仍可以相对滑移。
所述隔热管 10的悬置端为喇叭口 31， 可以起到改善气流的作用。
所述的波纹管 8为双层结构， 内外二层波纹管壁面之间仅接触， 而不进行 焊接； 单层波纹管材料厚度为 0.25~0.6mm， 波节数量为 5~10 个， 波节高度为 6~12 mm。 采用双层结构， 可以提高波纹管联接强度。
所述的进水管 2设置在靠近主板 5处， 冷却液能够充分进入预冷却腔室 7， 直接对主板 5和进气室 6外表面进行冷却， 降低主板 5和进气室 6的壁面温度， 减少热膨胀和变形量。
上述本发明的一种用于发动机的 EGR冷却器的废气进气端结构，包括进气 管组、 进气腔室和预冷却腔室三大部份。 其中， 进气管 9、 双层波纹管 8和隔热 管 10组成进气管组； 主板 5的周边与进气室 6的大口径端焊接后在进气室 6内 形成进气腔室 24; 进气室 6与预冷水室 Ί焊接后形成进气室 6的外表面与预冷 水室 7的内表面之间的预冷却腔室； 同时， 预冷水室 7与水壳体 3联接后， 在水 壳体 3与主板外围和进气室的大口径端 22之间形成冷却液通道 23。
如图 2所示， 所述的进气室 6的大口径端 22形状为柜形（如图 2 (2)和图 2 (4) 所示） 或圆形 （如图 2 ( 3 ) 所示）， 进气室 6的中间部分管体 14横截面 形状为柜形 （如图 2 (4) 所示） 或圆形 （如图 2 (2) 和图 2 ( 3 ) 所示）， 进气 室 6的小口径端 15形状为圆形， 进气室 6的大口径端 22与中间部分管体 14由 一平面台阶 12过渡联接。
如图 3所示， 本发明一种 EGR冷却器的废气进气端的另一种结构， 包括水 壳体 3、 进气管 5、 隔热管 50进气室 56、 预冷水室 57和主板 55， 所述的水壳体 53上设有进水管 52， 其特征在于所述的预冷水室 57两端分别与所述的进气管 5 和水壳体 3联接； 所述的隔热管 50置于预冷水室 57内， 一端与所述的进气管 5 联接， 另一端悬置， 该悬置端为喇叭口 51 ; 所述的进气室 56为一变径管， 包括 大口径端 53和小口径端 54， 所述的大口径端 53与所述的主板 55联接形成进气 腔室 63， 联接部分与水壳体 53之间保留有一定的空间， 形成冷却液通道 64; 所 述的小口径端 54的外表面与所述的预冷水室 57的端部联接形成与所述的冷却液 通道 64联通的预冷却腔室 65。 如图 4所示， 所述的进气室 56的大口径端 53形 状为柜形 （如图 4 (2) 所示） 或圆形 （如图 4 ( 3 ) 所示）， 进气室 56的小口径 端 54形状为圆形， 进气室 56的大口径端 53与小口径端 54由一平面台阶 52过 渡联接。
如图 5所示， 所述的进气室 6、 进气室 56中间部分设计有膨胀节 21。 应该理解到的是：上述实施例只是对本发明的说明，而不是对本发明的限制， 任何不超出本发明实质精神范围内的发明创造， 均落入本发明的保护范围之内。

Claims

权 利 要 求 书 、 一种 EGR冷却器的废气进气端结构， 包括水壳体（3)、 进气管（9)、 波纹管
( 8)、 隔热管 （10)进气室 （6)、 预冷水室 （7)和主板 （5)， 所述的水壳体 (3)上设有进水管 （2)， 其特征在于所述的进气管 （9)、 波纹管 （8)、 预冷 水室 （7) 和水壳体 （3) 依次联接； 所述的隔热管 （10) 置于所述的波纹管 ( 8) 内， 一端与所述的进气管 （9) 联接， 另一端悬置； 所述的进气室 （6) 为两级变径管体，包括大口径端（22)、中间部分管体（14)和小口径端（15)， 所述的大口径端 （22) 与所述的主板 （5) 联接形成进气腔室 （24)， 联接部 分与水壳体 （3) 之间保留有一定的空间， 形成冷却液通道 （23 ); 所述的中 间部分管体 （14) 的外表面与所述的波纹管 （8)和 /或预冷水室 （7) 的端部 联接形成与所述的冷却液通道（23)联通的预冷却腔室（13); 所述的小口径 端 （15) 与所述隔热管 （10) 中间部分的外表面接触。
、 如权利要求 1所述的一种 EGR冷却器的废气进气端结构，其特征在于所述进 气室 （6) 的中间部分管体 （14) 上设有膨胀节 （21 )。
、 如权利要求 1所述的一种 EGR冷却器的废气进气端结构，其特征在于所述进 气室 （6) 的横截面的形状为圆管或方管结构， 进气室 （6) 的中间部分管体
( 14) 与大口径端 （22) 之间由一台阶平面 （12) 过渡联接。
、 如权利要求 1所述的一种 EGR冷却器的废气进气端结构，其特征在于所述隔 热管 （10) 的悬置端为喇叭口 （31 )。
、 如权利要求 1所述的一种 EGR冷却器的废气进气端结构，其特征在于所述的 波纹管 （8) 为双层结构， 内外二层波纹管壁面之间仅接触， 而不进行焊接； 单层波纹管材料厚度为 0.25~0.6mm， 波节数量为 5~10个， 波节高度为 6~12 mm。
、 如权利要求 1-5任何一项所述的一种 EGR冷却器的废气进气端结构，其特征 在于所述的进水管 （2) 设置在靠近主板 （5) 处。
、 一种 EGR冷却器的废气进气端结构， 包括水壳体（3)、 进气管（5)、 隔热管
(50) 进气室 （56)、 预冷水室 （57 ) 和主板 （55 )， 所述的水壳体 （53) 上 设有进水管（52)， 其特征在于所述的预冷水室（57)两端分别与所述的进气
1 管 （5) 和水壳体 （3) 联接； 所述的隔热管 （50) 置于预冷水室 （57) 内， 一端与所述的进气管 （5)联接， 另一端悬置； 所述的进气室 （56) 为一变径 管， 包括大口径端 （53)和小口径端 （54)， 所述的大口径端 （53)与所述的 主板（55)联接形成进气腔室（63)， 联接部分与水壳体（53)之间保留有一 定的空间， 形成冷却液通道（64); 所述的小口径端（54) 的外表面与所述的 预冷水室 （57) 的端部联接形成与所述的冷却液通道 （64) 联通的预冷却腔 室 （65)。
、 如权利要求 Ί所述的一种 EGR冷却器的废气进气端结构，其特征在于所述进 气室（56)的横截面的形状为圆管或方管结构，进气室（56)的小口径端（54) 与大口径端 （53) 之间由一台阶平面 （52) 过渡联接。
、 如权利要求 Ί或 8所述的一种 EGR冷却器的废气进气端结构，其特征在于所 述隔热管 (50) 的悬置端为喇叭口 （51)。
2
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