WO2016131211A1 - 带内冷油腔结构的内燃机活塞及内燃机 - Google Patents

带内冷油腔结构的内燃机活塞及内燃机 Download PDF

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Publication number
WO2016131211A1
WO2016131211A1 PCT/CN2015/075869 CN2015075869W WO2016131211A1 WO 2016131211 A1 WO2016131211 A1 WO 2016131211A1 CN 2015075869 W CN2015075869 W CN 2015075869W WO 2016131211 A1 WO2016131211 A1 WO 2016131211A1
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WIPO (PCT)
Prior art keywords
piston
ring body
combustion engine
internal combustion
ring
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PCT/CN2015/075869
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English (en)
French (fr)
Inventor
林风华
张国华
刘世英
马学军
章健
张红锋
刘涛
张屹林
王世利
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山东滨州渤海活塞股份有限公司
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Application filed by 山东滨州渤海活塞股份有限公司 filed Critical 山东滨州渤海活塞股份有限公司
Priority to US15/550,904 priority Critical patent/US20180045137A1/en
Publication of WO2016131211A1 publication Critical patent/WO2016131211A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/0015—Multi-part pistons
    • F02F3/003—Multi-part pistons the parts being connected by casting, brazing, welding or clamping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means
    • F02F3/18—Pistons  having cooling means the means being a liquid or solid coolant, e.g. sodium, in a closed chamber in piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/0015—Multi-part pistons
    • F02F3/003—Multi-part pistons the parts being connected by casting, brazing, welding or clamping
    • F02F2003/0061—Multi-part pistons the parts being connected by casting, brazing, welding or clamping by welding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means
    • F02F3/20—Pistons  having cooling means the means being a fluid flowing through or along piston
    • F02F3/22—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid

Definitions

  • the present invention relates to the field of internal combustion engine manufacturing technology, and more particularly to an internal combustion engine piston and an internal combustion engine with an internal cold oil chamber structure.
  • the forming process of the inner cooling oil chamber is the difficulty and key in the current piston production process of the internal combustion engine. Whether the forming process is reasonable or not can greatly affect the service life of the piston.
  • the internal combustion engine piston with the inner cold oil chamber structure usually includes the piston body. And a ring body coupled with the piston body, an inner cooling oil chamber is formed between the ring body and the piston body.
  • the top end of the ring body is welded to the piston body, and the welding surface is a closed cylindrical surface along the piston axis. One end of the closed cylindrical surface extends to the top of the piston, and the other end extends to the inner cold oil chamber.
  • such a method is highly prone to incomplete penetration, and if penetration is to be ensured, It will inevitably increase the heat affected zone of the piston head, which will adversely affect the deformation of the control piston head.
  • an aspect of the present invention provides an internal combustion engine piston with an internal cold oil chamber structure, so as to ensure the welding quality between the ring body and the piston body without increasing the heat affected zone of the welding.
  • Another aspect of the present invention is to provide an internal combustion engine having the above-described internal combustion engine piston.
  • the present invention provides the following technical solutions:
  • An internal combustion engine piston with an internal cold oil chamber structure includes a piston body and a ring body that cooperates with the piston body to form the inner cold oil chamber structure, and the ring body forms a first mating area with a top portion of the piston body The ring body forms a second mating area with the top end of the skirt of the piston body, wherein the first mating area includes:
  • a body fitting portion disposed on a top portion of the piston body, the body fitting portion including a body welding cylinder surface extending downward from a top portion of the piston body, and a bottom end of the body welding cylinder surface and along the piston a radially extending first support protrusion;
  • a ring body fitting portion disposed at a top of the ring body, the ring body fitting portion including a ring body welding cylinder surface for mating with the body welding cylinder surface, and a portion for the first support protrusion to be embedded a lap groove, and the body welding cylinder surface and the ring body welding cylinder surface are welded and connected.
  • the second mating area is a step overlapping area.
  • the step overlapping area comprises:
  • a second supporting protrusion disposed on a bottom surface of the ring body and extending along an axial direction of the piston, a width of the second supporting protrusion in a radial direction of the piston is smaller than a wall thickness of the ring body, and the second supporting protrusion
  • the inner wall is flush with the inner wall of the ring body
  • the step overlapping area comprises:
  • a second support protrusion disposed at a top end of the skirt body of the piston body and extending along the axial direction of the piston, a width of the second support protrusion in a radial direction of the piston being smaller than a wall thickness of the top end of the skirt, and An inner wall of the second support protrusion is flush with an inner wall of the top end of the skirt;
  • a lap gap is reserved between the bottom surface of the ring body and the top end of the skirt of the piston body.
  • the ring body and the piston body are made of 42CrMoA.
  • the ring body and the piston body are made of 38MnVS6.
  • the internal combustion engine disclosed in the present invention includes a cylinder and a piston provided in the cylinder, and the piston is an internal combustion engine piston having an internal refrigerant oil chamber structure disclosed in any of the above.
  • the ring body and the top of the piston body form a first mating area
  • the first mating area includes a body engaging portion disposed at the top of the piston body and is disposed on the ring body a top ring fitting portion
  • the body fitting portion is provided with a body welding cylinder surface extending downward from a top portion of the piston body, and a first support protrusion extending to a bottom end of the body welding cylinder surface and extending in a radial direction of the piston
  • the ring body fitting portion includes a ring body welding cylinder surface for mating with the body welding cylinder, and a first overlapping groove for the first support protrusion to be embedded, and the body welding cylinder surface and the ring body The welding cylinder is welded and connected.
  • the piston ring welding cylinder surface of the internal combustion engine disclosed in the present invention cooperates with the body welding cylinder surface, and the welded weld end extends to the top of the piston, and the other end extends to the first support.
  • the position where the protrusions meet, but does not extend into the inner cold oil chamber, and the connection between the ring body and the piston body is realized by welding and overlapping, and the invention is the same in the case where the thickness of the piston head is the same
  • the weld seam is significantly shortened, so that the head of the piston is more easily penetrated, and the purpose of effectively ensuring the welding quality of the piston head without increasing the heat affected zone of the piston head is achieved.
  • FIG. 1 is a schematic view showing the external structure of a piston of an internal combustion engine provided in an embodiment of the present invention
  • FIG. 2 is a schematic view showing the cooperation of a ring body and a piston body in a piston of an internal combustion engine according to an embodiment of the present invention
  • FIG. 3 is a schematic structural view of a piston semi-finished product formed by assembling a ring body and a piston body according to an embodiment of the present invention
  • FIG. 4 is a schematic structural view of the semi-finished piston of FIG. 3 after processing the ring groove and the oil band;
  • FIG. 5 is a schematic structural view of a second mating area disclosed in another embodiment of the present invention.
  • 1 is a ring body
  • 2 is a piston body
  • 11 is a ring body top surface
  • 12 is a ring groove
  • 1-1 is a first ring body mating surface
  • 1-2 is a second ring body mating surface
  • 1-3 is a third
  • 1-4 is the mating surface of the fourth ring body
  • 1-5 is the mating surface of the fifth ring body
  • 1-6 is the mating surface of the sixth ring body
  • 21 is the skirt part
  • 22 is the inner cavity
  • 23 is Pin seat
  • 24 is the piston top
  • 25 is the oil belt
  • 2-1 is the first body mating surface
  • 2-2 is the second body mating surface
  • 2-3 is the third body mating surface
  • 2-4 is the fourth body
  • the mating surface, 2-5 is the fifth body mating surface
  • 2-6 is the sixth body mating surface
  • a is the upper half cavity
  • b is the lower half cavity
  • c is the inner cooling oil
  • One of the cores of the present invention is to provide a piston of an internal combustion engine having an internal cold oil chamber structure so as to ensure the quality of welding between the ring body and the piston body without increasing the heat affected zone of the weld.
  • Another core of the present invention is to provide an internal combustion engine having the piston of the above internal combustion engine.
  • the piston of the internal combustion engine with the internal cold oil chamber provided in the embodiment of the present invention includes a piston body 2 and a ring body 1 which cooperates with the piston body 2 to form an inner cold oil chamber c, and the ring body 1
  • the piston body 2 There are two contact positions with the piston body 2, one of which is located at the top of the piston body 2, as shown in Fig. 3, the position is called the first mating area, and the other contact position is located at the skirt of the piston body 2.
  • the position is referred to as a second mating area
  • the first mating area includes a body fitting portion disposed at a top of the piston body 2, the body mating portion specifically including a body welding cylinder surface extending downward from a top of the piston body 2, And a first supporting protrusion that is connected to the bottom end of the body welding cylinder and extends in a radial direction of the piston;
  • the first mating area further includes a ring body fitting portion disposed on the top of the ring body 1, and the ring body fitting portion specifically includes a ring-welding cylinder for mating with the body welding cylinder and for embedding the first support boss
  • the first overlapping groove, and the body welding cylinder surface and the ring body welding cylinder surface are welded and connected.
  • the ring body welding cylinder surface cooperates with the body welding cylinder surface, and the welded weld end extends to the top of the piston, and the other end extends to the first support protrusion.
  • the position does not extend into the inner cold oil chamber c, and the connection between the ring body 1 and the piston body 2 is realized by welding and lap joint, and the thickness of the piston head is the same as compared with the prior art.
  • the weld seam in the invention is obviously shortened, so that the head of the piston is more easily penetrated, and the purpose of effectively ensuring the welding quality of the piston head without increasing the heat affected zone of the piston head is achieved.
  • the first body mating surface 2-1 is the body welding cylinder surface in the above embodiment, and the first supporting protrusion is provided with a second body mating surface 2 - 2 and the third body mating surface 2-3, in the ring body 1 shown, the ring body top surface 11 is a planar structure, and the first ring body mating surface 1-1 is the ring body welding cylinder surface in the above embodiment
  • the second ring body mating surface 1-2 and the third ring body mating surface 1-3 constitute the first overlapping groove in the above embodiment; when the ring body 1 and the piston body 2 are assembled, the first supporting protrusion passes
  • the second body mating surface 2-2 supports the ring body, and the first body mating surface 2-1 is welded to the first ring body mating surface 1-1.
  • the ring body 1 and the piston body are 2 It is connected by the combination of lap joint and welding, and the piston adopting this kind of process has only a shallow depth annular weld at the top, the heat affected zone is small, and the welding quality is reliable.
  • the first body mating surface 2-1 and the first ring body mating surface 1-1 may be a clearance fit or an interference fit.
  • the gap value is not more than 0.05 mm.
  • the interference value is not more than 0.1 mm;
  • the third body mating surface 2-3 and the third ring body mating surface 1-3 may also be gap fit, or
  • the gap value is not more than 0.05 mm, and when the interference fit is used, the interference value is not more than 0.1 mm.
  • the total height of the first body mating face 2-1 and the third body mating face 2-3 is preferably between 4 and 40 mm, and the width of the second body mating face 2-2 in the radial direction of the piston It is preferably 20 mm or less.
  • the second mating zone may be a threaded connection zone, a weld zone, etc., so as to ensure that the second mating zone has good sealing performance, the upper half cavity a in the ring body 1 and the lower half cavity b in the piston body 2 are enclosed.
  • the second mating area is specifically a step overlapping area. As shown in FIG. 2 and FIG. 3, the so-called step overlapping area specifically means that the ring body 1 and the piston body 2 are overlapped in the second mating area, and in the longitudinal section, the overlapping position is a stepped shape. .
  • the overlapping region specifically includes: a second supporting protrusion and a second overlapping groove, wherein the second supporting protrusion is disposed on the bottom surface of the ring body 1 and extends along the axial direction of the piston, the second support
  • the width of the protrusion in the radial direction of the piston is smaller than the wall thickness of the ring body 1, and the inner wall of the second support protrusion is flush with the inner wall of the ring body 1, as shown in Fig. 2, the second overlapping groove is provided in the piston body 2
  • the top end of the skirt portion 21 serves to embed the second support projection.
  • the second support protrusion has a fifth ring body mating surface 1-5 and a sixth ring body mating surface 1-6, and the fourth ring body mating surface 1 - 4 is the bottom surface of the ring body 1.
  • the fifth body mating surface 2-5 and the sixth body mating surface 2-6 form the second overlapping groove
  • the fourth body mating surface 2 4 is the top surface of the skirt portion 21 of the piston body 2.
  • an overlap gap is left between the fourth ring body mating surface 1-4 and the fourth body mating surface 2-4, and the overlap gap is preferably 0.1-1 mm, so that The second supporting protrusion is ensured to be in reliable contact with the second overlapping groove, and the fifth ring body mating surface 1-5 and the fifth body mating surface 2-5 may be a clearance fit or an interference fit.
  • the gap value is below 0.1mm.
  • the interference value is also below 0.1mm.
  • the fourth body mating surface 2-4 and the fifth body mating surface 2-5 form an outer limiting ring
  • the second supporting protrusion is disposed just inside the outer limiting ring, as shown in FIG. 3 and As shown in Fig. 4, during the working of the piston, the outer limiting ring can effectively limit the deformation of the piston head, thereby effectively reducing the air leakage and the oil consumption during the working process of the piston.
  • the second support protrusion is disposed at the top end of the skirt portion 21 of the piston body 2 and extends in the axial direction of the piston, and the corresponding second overlapping groove is disposed on the bottom surface of the ring body 1, and the second support protrusion is on the piston
  • the width in the radial direction is smaller than the wall thickness of the top end of the skirt portion 21, and the inner wall of the second supporting protrusion is flush with the inner wall of the top end of the skirt portion 21, and after the second supporting protrusion is abutted against the second overlapping groove, the ring body 1
  • a lap gap is also reserved between the bottom surface and the top end of the skirt portion 21 of the piston body 2.
  • the ring groove 12 is machined on the ring body 1
  • the oil band 25 is machined on the piston body 2
  • the combustion chamber structure is machined on the piston top 24.
  • the piston of the internal combustion engine with the internal cold oil chamber structure disclosed in the present invention is a forged steel piston, and the material of the ring body 1 and the piston body 2 is 42CrMoA or 38MnVS6.
  • the first mating zone of the piston of the internal combustion engine disclosed in the present invention adopts the method of welding and lap jointing, which effectively shortens the length of the weld bead at the top of the piston and achieves no increase in heat influence.
  • the second mating zone adopts the direct overlapping fit mode, which greatly simplifies the processing mode of the piston, and can release and reduce the residual stress after the ring body 1 and the piston body 2 are combined. Small ring-shaped area deformation plays an important role.
  • the present invention also discloses an internal combustion engine, the piston of which is the piston of the internal combustion engine disclosed in any of the above embodiments.
  • the internal combustion engine employs the piston of the internal combustion engine disclosed in the above embodiments, the internal combustion engine has the corresponding advantages of the above-described internal combustion engine piston, which will not be further described in this application.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

一种带内冷油腔结构的内燃机活塞及内燃机，包括活塞本体（2）和环体（1），环体与活塞本体的顶部形成第一配合区，环体与活塞本体的裙部（21）顶端形成第二配合区，第一配合区包括：本体配合部，本体配合部包括由活塞本体的顶部向下延伸的本体焊接柱面，和与本体焊接柱面的底端相接且沿活塞的径向延伸的第一支撑凸起；环体配合部，环体配合部包括用于与本体焊接柱面配合的环体焊接柱面，和可供第一支撑凸起嵌入的第一搭接槽，且本体焊接柱面和环体焊接柱面焊接相连；第二配合区为阶梯搭接区。该内燃机活塞的头部更加容易焊透，实现了在不增大活塞头部热影响区的前提下有效保证活塞头部焊接质量的目的。

Description

带内冷油腔结构的内燃机活塞及内燃机
本申请要求于2015年02月16日提交中国专利局、申请号为201510084881.4、发明名称为“带内冷油腔结构的内燃机活塞及内燃机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及内燃机制造技术领域，更具体地说，涉及一种带内冷油腔结构的内燃机活塞及内燃机。
背景技术
近年来，发动机正在向着高强化和轻量化的方向不断发展，缸内压力和温度也在不断升高，这就使得活塞所承受的载荷越来越高，随之，活塞冷却功能和材料强度的重要性也越发明显。
目前，柴油机缸内最大爆发压力已经超过了25MPa，铝合金材料已远不能满足如此高的承载要求，为此制造商开始使用锻钢材料以及铸铁材料，效果颇为显著；但该种活塞也存在以下弊端：虽然锻钢材料能承受较高的温度载荷，但是较高温度环境会使润滑油性能急剧下降，从而增加了活塞与气缸间的摩擦损失，同时积碳增加。因此在活塞内部设置内冷油腔来加强冷却效果就成为了必然，带有内冷油腔的锻钢活塞可以较好的满足高爆压、高温度的工作环境要求。
内冷油腔的成型工艺是目前内燃机活塞生产过程中的难点和关键，其成型工艺是否合理往往能够在很大程度上影响活塞的使用寿命，带内冷油腔结构的内燃机活塞通常包括活塞本体和与活塞本体配合连接的环体，环体与活塞本体之间形成内冷油腔，目前的内燃机活塞中，环体的顶端与活塞本体焊接相连，其焊接面为沿活塞轴线的闭合圆柱面，该闭合圆柱面的一端延伸至活塞顶部，另一端延伸至内冷油腔，对于头部厚度较大的活塞，采用该种方式极易出现无法焊透的现象，而若要保证焊透，则必然会加大活塞头部的热影响区，这会对控制活塞头部的形变带来不利影响。
因此，如何能够在不加大焊接时热影响区的情况下，保证环体与活塞本体 的焊接质量是目前本领域技术人员亟需解决的技术问题。
发明内容
有鉴于此，本发明一方面在于提供一种带内冷油腔结构的内燃机活塞，以便能够实现在不加大焊接热影响区的情况下，保证环体与活塞本体之间的焊接质量。
本发明另一方面还在于提供一种具有上述内燃机活塞的内燃机。
为达到上述目的，本发明提供如下技术方案：
一种带内冷油腔结构的内燃机活塞，包括活塞本体和与所述活塞本体配合形成所述内冷油腔结构的环体，所述环体与所述活塞本体的顶部形成第一配合区，所述环体与所述活塞本体的裙部顶端形成第二配合区，其中所述第一配合区包括：
设置在所述活塞本体顶部的本体配合部，所述本体配合部包括由所述活塞本体的顶部向下延伸的本体焊接柱面，和与所述本体焊接柱面的底端相接且沿活塞的径向延伸的第一支撑凸起；
设置在所述环体顶部的环体配合部，所述环体配合部包括用于与所述本体焊接柱面配合的环体焊接柱面，和可供所述第一支撑凸起嵌入的第一搭接槽，且所述本体焊接柱面和所述环体焊接柱面焊接相连。
优选地，所述第二配合区为阶梯搭接区。
优选地，所述阶梯搭接区包括：
设置在所述环体底面上且沿活塞轴向延伸的第二支撑凸起，所述第二支撑凸起在活塞径向上的宽度小于所述环体的壁厚，且所述第二支撑凸起的内壁与所述环体的内壁平齐；
设置在所述活塞本体的裙部顶端，且可供所述第二支撑凸起嵌入的第二搭接槽。
优选地，所述阶梯搭接区包括：
设置在所述活塞本体的裙部顶端，且沿活塞轴向延伸的第二支撑凸起，所述第二支撑凸起在活塞径向上的宽度小于所述裙部顶端的壁厚，且所述第二支撑凸起的内壁与所述裙部顶端的内壁平齐；
设置在所述环体底面上，且可供所述第二支撑凸起嵌入的第二搭接槽。
优选地，在所述第二支撑凸起与所述第二搭接槽相抵后，所述环体底面与所述活塞本体的裙部顶端之间还预留有搭接间隙。
优选地，所述环体和所述活塞本体的材质为42CrMoA。
优选地，所述环体和所述活塞本体的材质为38MnVS6。
本发明中所公开的内燃机中，包括缸体和设置在缸体内的活塞，并且所述活塞为上述任意一项中所公开的带内冷油腔结构的内燃机活塞。
由以上技术方案可以看出，本发明中所公开的内燃机活塞中，环体与活塞本体的顶部形成第一配合区，第一配合区包括设置在活塞本体顶部的本体配合部和设置在环体顶部的环体配合部，其中本体配合部设置有由活塞本体的顶部向下延伸的本体焊接柱面，和与本体焊接柱面的底端相接且沿活塞的径向延伸的第一支撑凸起，环体配合部包括用于与本体焊接柱面配合的环体焊接柱面，和可供第一支撑凸起嵌入的第一搭接槽，且所述本体焊接柱面和所述环体焊接柱面焊接相连。
相比于现有技术，本发明中所公开的内燃机活塞环体焊接柱面与与本体焊接柱面相互配合，并且完成焊接后的焊缝一端延伸至活塞顶部，另一端延伸至与第一支撑凸起相接的位置，而并未延伸至内冷油腔中，通过焊接与搭接相结合的形式实现环体与活塞本体之间的连接，在活塞头部厚度相同的情况下，本发明中的焊缝明显缩短，从而使得活塞的头部更加容易焊透，实现了在不增大活塞头部热影响区的前提下有效保证活塞头部焊接质量的目的。
附图说明
为了更清楚地说明本发明实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本发明实施例中所提供的内燃机活塞的外部结构示意图；
图2为本发明实施例中所提供的内燃机活塞中环体与活塞本体的配合示意图；
图3为本发明实施例中环体与活塞本体装配后所形成的活塞半成品的结构示意图；
图4为图3中的活塞半成品加工环槽和油带后的结构示意图；
图5为本发明另一实施例中所公开的第二配合区的结构示意图。
标号说明：
1为环体，2为活塞本体，11为环体顶面，12为环槽，1-1为第一环体配合面，1-2为第二环体配合面，1-3为第三环体配合面，1-4为第四环体配合面，1-5为第五环体配合面，1-6为第六环体配合面，21为裙部，22为内腔，23为销座，24为活塞顶，25为油带，2-1为第一本体配合面，2-2为第二本体配合面，2-3为第三本体配合面，2-4为第四本体配合面，2-5为第五本体配合面，2-6为第六本体配合面，a为上半腔，b为下半腔，c为内冷油腔。
具体实施方式
本发明的核心之一在于提供一种带内冷油腔结构的内燃机活塞，以便能够实现在不加大焊接热影响区的情况下，保证环体与活塞本体之间的焊接质量。
本发明的另一核心在于提供一种具有上述内燃机活塞的内燃机。
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
请参阅图1至图5，本发明实施例中所提供的带内冷油腔的内燃机活塞中，包括活塞本体2和与活塞本体2配合形成内冷油腔c的环体1，环体1与活塞本体2之间共有两个接触位置，其中一个接触位置位于活塞本体2的顶部，如图3中所示，该位置称为第一配合区，另外一个接触位置位于活塞本体2的裙部21顶端，该位置称为第二配合区，并且第一配合区中包括设置在活塞本体2顶部的本体配合部，本体配合部具体包括由活塞本体2的顶部向下延伸的本体焊接柱面，和与本体焊接柱面的底端相接且沿活塞的径向延伸的第一支撑凸起；第一配合区中还包括设置在环体1顶部的环体配合部，环体配合部具体包括用于与本体焊接柱面配合的环体焊接柱面，和可供第一支撑凸起嵌入的 第一搭接槽，且本体焊接柱面和环体焊接柱面焊接相连。
上述实施例中所公开的内燃机活塞中，环体焊接柱面与与本体焊接柱面相互配合，并且完成焊接后的焊缝一端延伸至活塞顶部，另一端延伸至与第一支撑凸起相接的位置，而并未延伸至内冷油腔c中，通过焊接与搭接相结合的形式实现环体1与活塞本体2之间的连接，相比于现有技术，在活塞头部厚度相同的情况下，本发明中的焊缝明显缩短，从而使得活塞的头部更加容易焊透，实现了在不增大活塞头部热影响区的前提下有效保证活塞头部焊接质量的目的。
请具体参考图2，在所示的活塞本体2中，第一本体配合面2-1即为上述实施例中的本体焊接柱面，第一支撑凸起上设置有第二本体配合面2-2和第三本体配合面2-3，在所示的环体1中，环体顶面11为平面结构，第一环体配合面1-1即为上述实施例中的环体焊接柱面，第二环体配合面1-2和第三环体配合面1-3构成上述实施例中的第一搭接槽；当环体1与活塞本体2完成组装后，第一支撑凸起通过第二本体配合面2-2对环体进行支撑，第一本体配合面2-1与第一环体配合面1-1焊接相连，可见，在第一配合区中，环体1与活塞本体2通过搭接和焊接相结合的方式相连，并且采用该种工艺的活塞，仅在顶部具有一条深度较浅的环形焊缝，热影响区小，焊接质量可靠。
需要进行说明的是，在本发明实施例中，第一本体配合面2-1与第一环体配合面1-1之间可以为间隙配合也可为过盈配合，当采用间隙配合时，间隙值不大于0.05mm，当采用过盈配合时，过盈值不大于0.1mm；第三本体配合面2-3和第三环体配合面1-3之间同样可以为间隙配合，也可为过盈配合，当采用间隙配合时，间隙值不大于0.05mm，当采用过盈配合时，过盈值不大于0.1mm。
如图2中所示，第一本体配合面2-1和第三本体配合面2-3的总高度优选的在4-40mm之间，第二本体配合面2-2在活塞径向上的宽度优选的在20mm以下。
第二配合区可以为螺纹连接区、焊接区等，只要能够保证第二配合区具有良好的密封性能，使环体1中的上半腔a与活塞本体2中的下半腔b围合形成完整的内冷油腔c即可，在本发明实施例中，第二配合区具体为阶梯搭接区， 如图2和图3中所示，所谓阶梯搭接区具体是指在第二配合区中，环体1与活塞本体2之间为搭接，并且在纵剖面中，搭接位置呈阶梯形状。
在一种实施例中，搭接区具体包括：第二支撑凸起和第二搭接槽，其中第二支撑凸起设置在环体1底面上，且沿活塞的轴向延伸，第二支撑凸起在活塞径向上的宽度小于环体1的壁厚，并且第二支撑凸起的内壁与环体1的内壁平齐，如图2中所示，第二搭接槽设置在活塞本体2的裙部21顶端，其作用是供第二支撑凸起嵌入。
请具体参考图2，在所示的环体1中，第二支撑凸起上具有第五环体配合面1-5和第六环体配合面1-6，第四环体配合面1-4即为环体1的底面，在所示的活塞本体2中，第五本体配合面2-5和第六本体配合面2-6形成上述第二搭接槽，第四本体配合面2-4即为活塞本体2裙部21的顶面。当环体1与活塞本体2完成组装后，第二支撑凸起中第六环体配合面1-6与活塞本体2中的第六本体配合面2-6接触，从而形成对环体1的支撑。
当完成环体1与活塞本体2的组装后，第四环体配合面1-4与第四本体配合面2-4之间留有搭接间隙，搭接间隙优选的为0.1-1mm，以便保证第二支撑凸起与第二搭接槽可靠的接触，第五环体配合面1-5与第五本体配合面2-5之间可以为间隙配合也可为过盈配合，当采用间隙配合时，间隙值在0.1mm以下，当采用过盈配合方式时，过盈值也在0.1mm以下。
在上述实施例中，第四本体配合面2-4和第五本体配合面2-5构成一个外侧限位环，第二支撑凸起刚好设置在该外侧限位环的内部，如图3和图4中所示，在活塞工作的过程中，外侧限位环可以有效限制活塞头部变形，从而有效降低活塞工作过程中的漏气量和机油耗。
当然，在上述实施例的基础上，本领域技术人员还可以对搭接区的配合方式进行多种演化变形，如图5中就提供了另外一种搭接区的配合方式，在该实施例中，第二支撑凸起设置在活塞本体2的裙部21顶端，且沿活塞的轴向延伸，与其相应的第二搭接槽设置在环体1的底面上，第二支撑凸起在活塞径向上的宽度小于裙部21顶端的壁厚，且第二支撑凸起的内壁与裙部21顶端的内壁平齐，当第二支撑凸起与第二搭接槽相抵之后，环体1的底面与活塞本体2的裙部21顶端之间还预留有搭接间隙。
完成环体1与活塞本体2的组装后，在环体1上加工出环槽12，在活塞本体2上加工出油带25，并在活塞顶24上加工出燃烧室结构。
本发明中所公开的带内冷油腔结构的内燃机活塞为锻钢活塞，环体1和活塞本体2的材质为42CrMoA或38MnVS6。
由以上实施例中可以看出，本发明中所公开的内燃机活塞的第一配合区采用焊接和搭接相配合的方式，有效缩短了活塞顶部焊缝的长度，达到了在不增大热影响区的前提下提高焊接质量的目的，第二配合区采用直接搭接的配合方式，极大的简化了活塞的加工方式，并且可以对环体1和活塞本体2结合后残余应力的释放以及减小环岸区变形起到重要作用。
本发明还公开了一种内燃机，该内燃机中的活塞为上述任意一实施例中所公开的内燃机活塞。
由于该内燃机采用了上述实施例中所公开的内燃机活塞，因而该内燃机兼具上述内燃机活塞的相应优点，本申请文件中对此不再进行赘述。
本说明书中各个实施例采用递进的方式描述，每个实施例重点说明的都是与其他实施例的不同之处，各个实施例之间相同相似部分互相参见即可。
对所公开的实施例的上述说明，使本领域专业技术人员能够实现或使用本发明。对这些实施例的多种修改对本领域的专业技术人员来说将是显而易见的，本文中所定义的一般原理可以在不脱离本发明的精神或范围的情况下，在其它实施例中实现。因此，本发明将不会被限制于本文所示的这些实施例，而是要符合与本文所公开的原理和新颖特点相一致的最宽的范围。

Claims (8)

  1. 一种带内冷油腔结构的内燃机活塞，包括活塞本体(2)和与所述活塞本体(2)配合形成所述内冷油腔结构的环体(1)，其特征在于，所述环体(1)与所述活塞本体(2)的顶部形成第一配合区，所述环体(1)与所述活塞本体(2)的裙部顶端形成第二配合区，其中所述第一配合区包括：
    设置在所述活塞本体(2)顶部的本体配合部，所述本体配合部包括由所述活塞本体(2)的顶部向下延伸的本体焊接柱面，和与所述本体焊接柱面的底端相接且沿活塞的径向延伸的第一支撑凸起；
    设置在所述环体(1)顶部的环体配合部，所述环体配合部包括用于与所述本体焊接柱面配合的环体焊接柱面，和可供所述第一支撑凸起嵌入的第一搭接槽，且所述本体焊接柱面和所述环体焊接柱面焊接相连。
  2. 如权利要求1所述的带内冷油腔结构的内燃机活塞，其特征在于，所述第二配合区为阶梯搭接区。
  3. 如权利要求2所述的带内冷油腔结构的内燃机活塞，其特征在于，所述阶梯搭接区包括：
    设置在所述环体(1)底面上且沿活塞轴向延伸的第二支撑凸起，所述第二支撑凸起在活塞径向上的宽度小于所述环体(1)的壁厚，且所述第二支撑凸起的内壁与所述环体(1)的内壁平齐；
    设置在所述活塞本体(2)的裙部(21)顶端，且可供所述第二支撑凸起嵌入的第二搭接槽。
  4. 如权利要求2所述的带内冷油腔结构的内燃机活塞，其特征在于，所述阶梯搭接区包括：
    设置在所述活塞本体(2)的裙部(21)顶端，且沿活塞轴向延伸的第二支撑凸起，所述第二支撑凸起在活塞径向上的宽度小于所述裙部(21)顶端的壁厚，且所述第二支撑凸起的内壁与所述裙部(21)顶端的内壁平齐；
    设置在所述环体(1)底面上，且可供所述第二支撑凸起嵌入的第二搭接槽。
  5. 如权利要求3或4所述的带内冷油腔结构的内燃机活塞，其特征在于， 在所述第二支撑凸起与所述第二搭接槽相抵后，所述环体(1)的底面与所述活塞本体(2)的裙部(21)顶端之间还预留有搭接间隙。
  6. 如权利要求1所述的带内冷油腔结构的内燃机活塞，其特征在于，所述环体(1)和所述活塞本体(2)的材质为42CrMoA。
  7. 如权利要求1所述的带内冷油腔结构的内燃机活塞，其特征在于，所述环体(1)和所述活塞本体(2)的材质为38MnVS6。
  8. 一种内燃机，包括缸体和设置在所述缸体内的活塞，其特征在于，所述活塞为权利要求1-7任意一项所述的带内冷油腔结构的内燃机活塞。
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