CN114962823A - Clamp and pipeline structure with same for internal combustion engine - Google Patents

Abstract

The invention discloses a clamp and a pipeline structure for an internal combustion engine with the same. The clamp includes two pipe hoops and bolt assembly, the pipe hoop includes pipe hoop portion and shoulder, pipe hoop portion is the arc structure, the both ends of the first radial direction of pipe hoop portion of edge of pipe hoop portion all are provided with the shoulder, the shoulder has the installation through-hole that the axis extends along the second radial direction of pipe hoop portion, the first radial direction of second radial direction perpendicular to, the size of the second radial direction of pipe hoop portion of edge of shoulder is H, the radius size of pipe hoop portion is R, the scope of H is 0.5R and is less than or equal to H and is less than or equal to R, bolt assembly includes bolt and nut, the bolt is used for wearing to locate behind the installation through-hole and nut is connected, in order to connect two pipe hoops. Therefore, the range of H is more than or equal to 0.5R and less than or equal to H, the rigidity and the strength of the pipe hoop can be increased, the possibility of local arching caused by bending deformation of the pipe hoop part is reduced, and the possibility of leakage caused by untight sealing of the pipeline at the joint can be further reduced.

Description

Clamp and internal combustion engine piping structure having the same

technical field

The invention relates to the field of pipeline connection, in particular to a clamp and a pipeline structure for an internal combustion engine having the same.

Background technique

With the development of internal combustion engines towards high power density and high reliability. The compact design of internal combustion engines has received increasing attention. Among them, the compact requirement of the exhaust pipe of the internal combustion engine is not only related to the reliability of the exhaust seal, but also to the safety of the whole machine. The clamp is used as a structure for connecting the exhaust pipe, and the rationality of the structure of the clamp directly affects the sealing performance of the exhaust pipe and the connection strength of the exhaust pipe.

The existing clip-on clamp includes a first clamp and a second clamp. The first clamp and the second clamp are used to clamp the exhaust pipe. The clamp has a shoulder. The shoulders are provided with mounting holes for arranging bolts and nuts, so as to connect the first clamp and the second clamp through the bolts and nuts, so that the first clamp and the second clamp clamp the exhaust pipe.

However, the existing wafer-type clamps have a small shoulder height dimension. When the first clamp and the second clamp are clamped to the pipe, and when the internal combustion engine is working, the shaft shoulder is easily deformed, thereby causing the pipe to leak.

Therefore, the present invention provides a clamp and a piping structure for an internal combustion engine having the same to at least partially solve the above problems.

SUMMARY OF THE INVENTION

A series of concepts in simplified form have been introduced in the Summary section, which are described in further detail in the Detailed Description section. The Summary of the Invention section of the present invention is not intended to attempt to limit the key features and essential technical features of the claimed technical solution, nor is it intended to attempt to determine the protection scope of the claimed technical solution.

In order to at least partially solve the above technical problems, the present invention provides a clamp, which includes:

Two pipe hoop, the pipe hoop includes a pipe hoop part and a convex shoulder part, the pipe hoop part is an arc structure, both ends of the pipe hoop part along the first radial direction of the pipe hoop part are provided with a convex shoulder part, and the convex shoulder part is provided. The part has an installation through hole whose axis extends along the second radial direction of the pipe hoop part, the second radial direction is perpendicular to the first radial direction, and the dimension of the shoulder part along the second radial direction of the pipe hoop part is H , the radius size of the pipe hoop is R, and the range of H is 0.5R≤H≤R,

Bolt assembly, the bolt assembly includes bolts and nuts, the bolts are used to pass through the installation through holes and connect with the nuts to connect two pipe clamps.

According to the clamp of the present invention, the range of H is 0.5R≤H≤R, which can increase the rigidity and strength of the pipe clamp, reduce the possibility that the pipe clamp part is bent and deformed and partially arched, and thus can reduce the sealing failure of the pipe at the connection. Strict and the possibility of leakage.

Optionally, the shoulder mounting surface of the shoulder portion close to the head of the bolt assembly is an inclined surface, the inclined surface has an inclined surface outer end and an inclined surface inner end, and along the first radial direction of the pipe hoop portion, the inclined surface outer end is located on the inclined surface. On the side of the inner end away from the center of the arc structure, along the second radial direction of the pipe hoop portion, the inner end of the inclined plane is located on the side of the outer end of the inclined plane close to the center of the arc structure.

Optionally, the shoulder mounting surface of the shoulder portion close to the head of the bolt assembly is perpendicular to the second radial direction of the pipe hoop portion, the clamp includes a wedge-shaped washer, and in the case of the bolt assembly connecting two pipe hoop, the wedge-shaped The washer is sleeved on the screw rod of the bolt, and the wedge-shaped washer is overlapped with the mounting surface of the shaft shoulder, so that the surface of the wedge-shaped washer close to the head of the adjacent bolt assembly is an inclined surface. In the radial direction, the thicker end of the wedge-shaped washer is used to be disposed on the side of the shank of the bolt away from the center of the arc structure.

Optionally, the included angle α between the inclined surface and the first radial direction of the pipe hoop portion is in the range of 0°<α≤20°.

Optionally, the coefficient of linear expansion of the material of the bolt is less than or equal to the coefficient of linear expansion of the material of the pipe collar.

Optionally,

The material of the bolt has a coefficient of linear expansion less than or equal to 14, and/or

The coefficient of linear expansion of the material of the pipe hoop is less than or equal to 17.

Optionally, the cross-sectional shape of the hoop portion has a V-shaped groove.

The present invention also provides a pipeline structure for an internal combustion engine. The pipeline structure for an internal combustion engine includes: at least two pipelines, and the aforementioned clamp, which is used to connect adjacent pipelines.

According to the pipeline structure for an internal combustion engine of the present invention, the pipeline structure for an internal combustion engine includes the aforementioned clamp, and the range of H is 0.5R≤H≤R, which can increase the rigidity and strength of the pipe clamp, and reduce the bending deformation of the pipe clamp and the partial arching of the pipe clamp. It is possible to reduce the possibility of leakage of pipelines due to poor sealing at the connection.

Optionally, the end of the pipeline is provided with a connecting flange, the clamp is used to connect the connecting flanges of the adjacent pipelines to connect the adjacent pipelines, and the pipeline structure also includes a sealing gasket, and the sealing gasket is used to be arranged on the adjacent pipelines. Between the connection flanges of adjacent pipes, in order to seal the gap between the connection flanges of adjacent pipes, the linear expansion coefficient of the material of the pipe hoop is less than or equal to the linear expansion coefficient of the material of the connection flange.

Description of drawings

In order that the advantages of the present invention may be more readily understood, the present invention briefly described above will be described in more detail by reference to specific embodiments shown in the accompanying drawings. Understanding that these drawings depict only typical embodiments of the invention and are therefore not to be considered limiting of its scope, the invention will be described and explained with additional specificity and detail.

FIG. 1 is a front view of a clamp according to a first preferred embodiment of the present invention, wherein part of the clamp is cut away;

Fig. 2 is a partial enlarged schematic view of part A of the clamp of Fig. 1, wherein bolts are not shown;

Fig. 3 is the sectional schematic diagram of the B-B place of the clamp of Fig. 1;

FIG. 4 is a schematic cross-sectional view of the connection flange and the sealing gasket of the clamp connection pipeline of FIG. 1;

Figure 5 is a front view of a clamp according to a second preferred embodiment of the present invention, wherein a portion of the clamp is cut away;

Fig. 6 is the partial enlarged schematic diagram of C of the clamp of Fig. 5;

Figure 7 is a graph of contact pressure distribution on the gasket surface of an experiment; and

Figure 8 is a stress diagram of the inside and outside of the threaded rod of another experiment.

Description of reference numerals

110, pipe hoop 111, pipe hoop part

112, shoulder 113, mounting through hole

114, the first pipe clamp 115, the second pipe clamp

116, V-groove 121, bolt

122, nut 131, inclined surface

132, the outer end of the bevel 133, the inner end of the bevel

140, gasket 150, connecting flange

211, pipe hoop part 212, shoulder part

221, Bolt 222, Nut

231, inclined surface 227, shoulder mounting surface

240, wedge gasket

Detailed ways

In the following description, numerous specific details are set forth in order to provide a more thorough understanding of the present invention. It will be apparent, however, to one skilled in the art that embodiments of the invention may be practiced without one or more of these details. In other instances, some technical features known in the art are not described in order to avoid confusion with the embodiments of the present invention.

Preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be noted that the terms "upper", "lower" and similar expressions used herein are only for the purpose of illustration and not for limitation.

Herein, ordinal numbers such as "first" and "second" referenced in this application are merely identifications and do not have any other meaning, such as a specific order, and the like. Also, for example, the term "first space member" by itself does not imply the existence of a "second space member", and the term "second space member" does not by itself imply the existence of a "first space member".

For a thorough understanding of the embodiments of the present invention, detailed structures will be presented in the following description. Obviously, the implementation of the embodiments of the present invention is not limited to the specific details familiar to those skilled in the art. The preferred embodiments of the present invention are described in detail below, however, the present invention may have other embodiments in addition to these detailed descriptions.

first embodiment

The present invention provides a clamp. Please refer to Figure 1 to Figure 4, the clamp is used to connect two pipes. As shown in FIG. 4 , the ends of the pipes have connecting flanges 150 . The connecting flange 150 extends radially outward of the pipe. The connecting flange 150 is configured as a circumferentially continuous structure about the axis of the pipe. The connection flanges 150 of the two pipes are connected to communicate the two pipes. The clamp clamps the connecting flanges 150 of the two pipes connected together, thereby connecting the two pipes. A gasket 140 is disposed between the connecting flanges 150 to seal the gap between the two connecting flanges 150 . The gasket 140 may be a rubber gasket.

As shown in FIG. 1 , the clamp includes two pipe clamps 110 . The ferrule 110 includes a ferrule portion 111 and a shoulder portion 112 . The pipe hoop portion 111 has an arc-shaped structure. The clamp clamps the connection flange 150 of the pipe through the pipe clamp part 111 to connect the pipe.

Referring to FIGS. 1 and 2 , the shoulder portion 112 includes a first shoulder portion and a second shoulder portion. The first shoulder portion is located at one end of the ferrule portion 111 along the first radial direction D1 (the left-right direction in FIG. 1 ) of the ferrule portion 111 . The second shoulder portion is located at the other end of the collar portion 111 along the first radial direction D1 of the collar portion 111 . The shoulder portion 112 has a mounting through hole 113 . The axis of the mounting through hole 113 extends along the second radial direction D2 (the vertical direction in FIG. 1 ) of the collar portion 111 . The first radial direction D1 of the ferrule portion 111 is perpendicular to the second radial direction D2 of the ferrule portion 111 . Along the first radial direction D1 of the ferrule portion 111 , the position of the first shoulder portion and the position of the second shoulder portion are symmetrical with respect to the second radial direction D2 of the ferrule portion 111 .

The two ferrules 110 include a first ferrule 114 and a second ferrule 115 . The clamp also includes a bolt assembly. The bolt assembly includes a bolt 121 and a nut 122 . The bolts 121 are used to pass through the mounting through holes 113 . The openings of the first pipe collar 114 and the second pipe collar 115 are opposite to each other. The first shoulder portion of the first pipe collar 114 is opposite to the first convex portion of the second pipe collar 115 . The second shoulder portion of the first pipe collar 114 is opposite to the second convex portion of the second pipe collar 115 .

The bolts 121 pass through the shoulder portion 112 of the first pipe collar 114 and the shoulder portion 112 of the second pipe collar 115 in sequence, and then are connected with the nut 122 . Specifically, a bolt 121 passes through the first shoulder portion of the first pipe collar 114 and the first shoulder portion of the second pipe collar 115 in sequence, and is then connected to a nut 122 . Another bolt 121 passes through the second shoulder portion of the first pipe collar 114 and the second convex portion of the second pipe collar 115 in sequence, and is then connected with another nut 122 . In this way, by tightening the bolts 121 of the pipe clamp 110, the first pipe clamp 114 and the second pipe clamp 115 can be tightened to the connecting flange 150 of the pipe located therein.

The dimension of the shoulder portion 112 along the second radial direction D2 of the collar portion 111 is H. The radius dimension of the hoop portion 111 is R. The range of H is 0.5R≤H≤R. In this way, the rigidity and strength of the pipe hoop 110 can be increased, and the possibility that the pipe hoop portion 111 is bent and deformed and partially arched can be reduced. Further preferably, H=0.6R.

In this embodiment, the range of H is 0.5R≤H≤R, which can increase the rigidity and strength of the pipe hoop 110, reduce the possibility that the pipe hoop portion 111 is bent and deformed and partially arched, and thus can reduce the failure of the pipe to be sealed at the joint. Strict and the possibility of leakage.

Please continue to refer to FIG. 1 and FIG. 2 . Specifically, please refer to FIG. 1 and FIG. 2 . Along the second radial direction D2 of the pipe hoop portion 111 , the side surface of the shoulder portion 112 away from the center of the arc structure is the shaft shoulder installation. noodle. The shoulder mounting surface is configured as an inclined surface 131 . The inclined surface 131 is inclined to the first radial direction D1 of the collar portion 111 . Specifically, the inclined surface 131 has an inclined surface outer end 132 and an inclined surface inner end 133 . Along the first radial direction D1 of the tube hoop portion 111 , the outer end 132 of the bevel is located on the side of the inner end 133 of the bevel away from the center of the arc structure. Along the second radial direction D2 of the tube hoop portion 111 , the inner end 133 of the bevel is closer to the center of the arc structure than the outer end 132 of the bevel.

When the bolt 121 is tightened, the mounting surface of the bolt assembly gradually approaches the shoulder portion 112 . In this way, the mounting surface of the bolt assembly abuts against the outer end 132 of the inclined surface first. During the continuous tightening of the bolts 121 , the mounting surface of the bolt assembly acts on the outer end 132 of the inclined surface to gradually deform the shoulder portion 112 , so that the shoulder mounting surface is gradually perpendicular to the second radial direction D2 of the pipe hoop portion 111 . When the bolts 121 are tightened to a predetermined pre-tightening force, the mounting surface of the shaft shoulder is substantially perpendicular to the second radial direction D2 of the pipe hoop portion 111 , and the mounting surface of the bolt assembly is fitted to the mounting surface of the shaft shoulder. At this time, the axis of the bolt 121 is substantially parallel to the second radial direction D2 of the collar portion 111 . In this way, the force of the rod body of the bolt 121 is uniform, which can reduce the stress on the inner side of the rod body of the bolt 121 (the side end of the rod body away from the outer end 132 of the inclined plane), and reduce the possibility of the bolt 121 breaking.

In addition, the force on the surface of the sealing gasket 140 between the connecting flanges 150 can be made uniform, and the sealing performance can be improved.

The included angle between the inclined surface 131 and the first radial direction D1 of the tube hoop portion 111 ranges from 0° to 20°. In this way, the inner stress of the rod body of the bolt 121 can be further reduced, thereby further reducing the possibility of the bolt 121 breaking.

Further preferably, the included angle between the inclined surface 131 and the first radial direction D1 of the tube hoop portion 111 is 5°.

Preferably, the coefficient of linear expansion of the material of the bolt 121 is less than or equal to the coefficient of linear expansion of the material of the pipe collar 110 . In this way, it can be avoided as much as possible that the connection of the first pipe collar 114 and the second pipe collar 115 connected by the bolts 121 is loosened when working in a high temperature environment, and further leakage can be avoided as much as possible.

Preferably, the linear expansion coefficient X1 of the material of the bolt 121 is in the range of 0<X1≦14. Thus, the selection of the bolt 121 is facilitated.

Preferably, the linear expansion coefficient X2 of the material of the pipe hoop 110 is in the range of 0<X2≤17. Therefore, the selection of the pipe hoop 110 is facilitated.

Preferably, the material of the bolt 121 is 06Cr25Ni20. Thus, the selection of the bolt 121 is facilitated.

Preferably, the material of the pipe collar 110 is 25Cr2MoVA. Therefore, the selection of the pipe hoop 110 is facilitated.

Preferably, the pipe collar 110 can be an integrally formed structure. For example, the ferrule 110 may be a casting. Thereby, the processing of the pipe collar 110 is facilitated. The structures of the first pipe collar 114 and the second pipe collar 115 may be the same. Thus, replacement is facilitated.

When the first pipe hoop 114 and the second pipe hoop 115 hold the connection flange tightly, along the first radial direction D1 of the pipe hoop portion 111 , there is a gap between the first pipe hoop 114 and the second pipe hoop 115 .

The invention also provides a pipeline structure for an internal combustion engine. As shown in FIG. 4 , the pipe structure includes at least two pipes, the aforementioned clamp, and the aforementioned sealing gasket 140 . The ends of the pipes have the aforementioned connecting flanges 150 . At least two pipes are connected in sequence so as to communicate. The pipe is used to connect to the exhaust port of the internal combustion engine for exhaust gas. Adjacent pipes are connected by clamps.

In this embodiment, the pipe structure includes the aforementioned clamp, and the range of H is 0.5R≤H≤R, which can increase the rigidity and strength of the pipe clamp 110, reduce the possibility of the pipe clamp portion 111 being bent and deformed and partially arched, and further It can reduce the possibility of leakage of pipes due to poor sealing at the connection.

Preferably, as shown in FIG. 4 , the side of the connecting flange 150 away from the sealing gasket 140 is a flange inclined surface. The flange slope is inclined to the radial direction of the pipe. The flange inclined surfaces of the two connecting flanges 150 connected together form a cross-section (the cross-section extending through the axis of the pipeline) as a V-shaped structure.

As shown in FIGS. 3 and 4 , the cross-section of the collar portion 111 (the cross-section extending through the axis of the arcuate structure) is shaped with a V-shaped groove 116 opening toward the center of the arcuate structure. The V-shaped structure formed by the connecting flange 150 enters the V-shaped groove 116 . The side surface of the V-shaped groove 116 is attached to and hugs the inclined surface of the flange, and further hugs the connecting flange 150 . Thereby, the connection flange 150 can be fixed more firmly.

Preferably, the coefficient of linear expansion of the material of the pipe collar 110 is less than or equal to the coefficient of linear expansion of the material of the connection flange 150 . In this way, it can be avoided as much as possible that the connection between the clamp and the connection flange 150 is loosened when working in a high temperature environment, and further leakage can be avoided as much as possible.

Second Embodiment

In the second embodiment, please refer to FIGS. 5 and 6 , the shoulder mounting surface 227 of the shoulder portion 212 is perpendicular to the second radial direction D2 of the collar portion 211 . The clamp also includes a wedge washer 240 . The end surface of the wedge-shaped washer 240 is inclined to the axial direction of the wedge-shaped washer 240 . In this way, the thickness of the first end of the wedge-shaped spacer 240 in the radial direction thereof is greater than the thickness of the second end. The wedge-shaped washer 240 is sleeved on the outer circumference of the screw rod of the bolt 221 . The wedge washer 240 is located between the head of the bolt assembly (the head of the bolt 221 and the nut 222 ) and the shoulder mounting surface 227 . The first end of the wedge-shaped washer 240 is disposed on the outer side of the screw along the first radial direction D1 of the tube hoop portion 211 (along the first radial direction D1 of the tube hoop portion 211, a portion of the screw rod away from the center of the arc-shaped structure) side).

When one end surface of the wedge-shaped washer 240 is overlapped with the shoulder mounting surface 227 , the surface of the wedge-shaped washer 240 close to the head of the bolt assembly is the inclined surface 231 . The function of the inclined surface 231 is substantially the same as the function of the inclined surface 131 of the first embodiment, and will not be repeated here.

Other settings of the second embodiment are substantially the same as those of the first embodiment, and will not be repeated here.

Assemble a clamp on the exhaust pipe of an internal combustion engine for testing. In this test, the first improved clamp and the first test clamp with H=0.1R are used for test comparison. The H=0.6R of the first improved clamp. The other test conditions for the first test clamp and the first modified clamp were approximately the same. When the internal combustion engine using the first test clamp is working, there is air leakage at the sealing gasket of the exhaust pipe. However, when the internal combustion engine using the first improved clamp is working, there is no air leakage at the sealing gasket of the exhaust pipe.

In addition, during the test, the contact pressure on the surface of the gasket when the internal combustion engine is in operation is collected. Under the same predetermined pre-tightening force for tightening the bolts, the contact pressure on the surface of the sealing gasket is more uniform in the circumferential direction with the first improved clamp than with the first test clamp, see Figure 7 for details.

Assemble a clamp on the exhaust pipe of an internal combustion engine for testing. In this test, the second improved clamp and the second test clamp are used for test comparison. The shoulder mounting surface of the second test clamp is perpendicular to the second radial direction D2 of the pipe hoop portion, and the second test clamp has no wedge-shaped washer of the second embodiment. The second improved clamp has the inclined surface of the present application. The other test conditions for the second test clamp and the second modified clamp were approximately the same. The outer side of the screw of the bolt (the side of the bolt that is far from the center of the arc structure along the first radial direction D1 of the pipe hoop) and the inner side (the side of the bolt that is close to the arc structure along the first radial direction D1 of the pipe hoop part) One side of the circle center) are provided with strain gauges (the strain gauges are located between the first clamp and the second clamp). Under the same condition of the predetermined pre-tightening force for tightening the bolt, when the second improved clamp is used, the stress difference between the inner side and the outer side of the bolt is about smaller, and does not exceed the yield of the material. When the second test clamp is used, the stress difference between the inner and outer sides of the bolt is relatively large (over 200MPa), and as the predetermined pre-tightening force gradually increases, the difference also increases, see Figure 8 for details, in which the bolt 1 and bolt 2 are the two bolts connecting the clamp.

The present invention has been described by the above-mentioned embodiments, but it should be understood that the above-mentioned embodiments are only for the purpose of illustration and description, and are not intended to limit the present invention to the scope of the described embodiments. In addition, those skilled in the art can understand that the present invention is not limited to the above-mentioned embodiments, and more variations and modifications can also be made according to the teachings of the present invention, and these variations and modifications all fall within the protection claimed in the present invention. within the range. The protection scope of the present invention is defined by the appended claims and their equivalents.

Unless otherwise defined, technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the technical field of this invention. The terminology used herein is for the purpose of describing a particular implementation only and is not intended to limit the present invention. Terms such as "component" appearing herein can refer to either a single part or a combination of parts. Terms such as "installed", "provided" and the like appearing herein can mean either the direct attachment of one component to another component or the attachment of one component to another component through an intermediate piece. A feature described herein in one embodiment may be used in another embodiment alone or in combination with other features, unless the feature is not applicable in the other embodiment or stated otherwise.

The present invention has been described by the above-mentioned embodiments, but it should be understood that the above-mentioned embodiments are only for the purpose of illustration and description, and are not intended to limit the present invention to the scope of the described embodiments. It will be appreciated by those skilled in the art that various variations and modifications can be made according to the teachings of the present invention, which all fall within the scope of the claimed protection of the present invention.

Claims (9)

1. A clamp, comprising:

the pipe hoop comprises two pipe hoops and a convex shoulder part, the pipe hoop part is of an arc structure, the convex shoulder part is arranged at two ends of the pipe hoop part along a first radial direction of the pipe hoop part, the convex shoulder part is provided with an installation through hole of which the axis extends along a second radial direction of the pipe hoop part, the second radial direction is perpendicular to the first radial direction, the size of the convex shoulder part along the second radial direction of the pipe hoop part is H, the radius size of the pipe hoop part is R, the range of H is more than or equal to 0.5R and less than or equal to H and less than or equal to R,

the bolt assembly comprises a bolt and a nut, and the bolt is used for being connected with the nut after penetrating through the installation through hole so as to connect the two pipe hoops.

2. The clamp of claim 1, wherein the shoulder mounting surface of the shoulder portion proximate the head portion of the bolt assembly is an inclined surface having an outer inclined surface end and an inner inclined surface end, the outer inclined surface end being located on a side of the inner inclined surface end distal from a center of the arcuate structure in a first radial direction of the band portion, and the inner inclined surface end being located on a side of the outer inclined surface end proximal to the center of the arcuate structure in a second radial direction of the band portion.

3. The clamp of claim 1, wherein a shoulder mounting surface of the shoulder portion adjacent to the head portion of the bolt assembly is perpendicular to the second radial direction of the pipe clamp portion, the clamp includes a wedge-shaped spacer, and when the bolt assembly connects two pipe clamps, the wedge-shaped spacer is sleeved on the screw of the bolt, and the wedge-shaped spacer is overlapped on the shoulder mounting surface, so that a surface of the wedge-shaped spacer adjacent to the head portion of the bolt assembly is an inclined surface.

4. Clamp according to claim 2 or 3, wherein the angle α between the inclined surface and the first radial direction of the band portion is in the range 0 ° < α ≦ 20 °.

5. The clamp of claim 1, wherein the coefficient of linear expansion of the material of the bolt is less than or equal to the coefficient of linear expansion of the material of the pipe clamp.

6. Clamp according to claim 1,

the coefficient of linear expansion of the material of the bolt is less than or equal to 14, and/or

The coefficient of linear expansion of the material of the pipe clamp is less than or equal to 17.

7. The clamp of claim 1, wherein the cross-sectional shape of the band portion has a V-shaped groove.

8. A pipe structure for an internal combustion engine, characterized by comprising: at least two pipes, and a clamp according to any one of claims 1 to 7 for connecting adjacent said pipes.

9. The piping structure of claim 8, wherein the ends of the pipes are provided with connection flanges, and the pipe clamp is used for connecting the connection flanges of the adjacent pipes to connect the adjacent pipes, and further comprising a sealing gasket for being arranged between the connection flanges of the adjacent pipes to seal a gap between the connection flanges of the adjacent pipes, and the material of the pipe clamp has a coefficient of linear expansion smaller than or equal to that of the connection flanges.

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