JP4082068B2 - Spherical joint for pipe - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention belongs to the technical field of spherical joints for pipes applied to automobile exhaust pipes and the like.
[0002]
[Prior art]
Conventionally, as a spherical joint for pipes connecting an upstream pipe and a downstream pipe, one described in JP 2000-27640 A is known.
[0003]
In this prior art, a convex connection flange having a convex spherical seating surface toward the other connection end is provided at one connection end of either the upstream pipe or the downstream pipe, and the other The connection end portion is provided with a concave connection flange having a concave spherical seating surface toward one connection end portion, and the two sealing members each having a spherical seal surface slidably contacting these two spherical seating surfaces Two joint flanges are connected between the joint flanges so that they can be displaced relative to each other, and the center of curvature of each of the spherical seal faces is set at different positions so that two joints have two spherical seal faces in one joint. However, the assembly work of the seal member can be performed easily and efficiently.
[0004]
[Problems to be solved by the invention]
However, in the conventional spherical joint for pipes, by providing two sliding surfaces, the displacement in the axial direction of the pipe on the driving side of the upstream pipe or the downstream pipe is transmitted to the driven pipe. Although it has a difficult structure, since the two sliding surfaces are arranged close to each other in the same direction, the distance between the centers of curvature of each spherical seal surface is short, and in fact, sufficient transmission suppression performance cannot be obtained. was there.
[0005]
The present invention has been made paying attention to the above-mentioned problem, and the object of the present invention is excellent transmission suppression that makes it difficult to transmit the displacement in the direction of the pipe axis of either the upstream pipe or the downstream pipe to the other. An attempt is made to provide a spherical joint for pipes that can exhibit performance, and can also exhibit an excellent effect of making it difficult to transmit the displacement in the direction in which either the upstream pipe or the downstream pipe is away from the other to the other. To do.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, according to the present invention, a connection flange provided at the connection end of both the upstream pipe and the downstream pipe, a seal member that is in sliding contact with these two connection flanges, and the two connection flanges are relative to each other. In the spherical joint for pipes provided with a coupling means for coupling in a displaceable manner, the two connection flanges each have a spherical bearing surface that is concave toward the other connection flange side, and the upstream pipe side The center of curvature of the spherical seating surface is located downstream of the spherical seating surface of the downstream tube side and downstream of the downstream side of the spherical seating surface. The center of curvature of the seating surface is arranged upstream of the center of curvature of the spherical seating surface on the upstream side tube side and upstream of the spherical seating surface on the upstream side tube side .
[0007]
【The invention's effect】
In the present invention, the center of curvature of the spherical seating surface on the upstream tube side is located downstream of the center of curvature of the spherical seating surface on the downstream tube side and downstream of the spherical seating surface on the downstream tube side. Since the center of curvature of the spherical seating surface on the downstream side of the pipe is located upstream of the center of curvature of the spherical seating surface on the upstream side of the pipe and upstream of the spherical seating surface of the upstream side of the pipe , The distance between the centers of curvature can be made larger than that of the spherical joint for pipes in which the shapes of the two connecting flanges are set so that the center of curvature of both spherical bearing surfaces exists only on one of the upstream side and the downstream side.
[0008]
Therefore, by increasing the distance between the centers of curvature of both spherical bearing surfaces, it exhibits excellent transmission suppression performance that makes it difficult to transmit the displacement in the direction of the pipe axis of either the upstream pipe or the downstream pipe to the other. In addition, it is possible to exhibit an excellent effect of making it difficult to transmit the displacement in the direction in which either the upstream pipe or the downstream pipe is away from the other to the other.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the embodiments for implementing the pipe for the spherical joint of the present invention will be described with reference to the first to third embodiments.
[0010]
(First embodiment)
First, the configuration will be described.
FIG. 1 is a cross-sectional view showing a pipe spherical joint 1 according to a first embodiment.
In FIG. 1, 2 is an upstream side pipe, 3 is a downstream side pipe, and the cylinder inner diameter at the connection end of the downstream side pipe 3 is expanded so as to be larger than the cylinder inner diameter of the upstream side pipe 2. The fluid is easy to flow from the side to the downstream side.
[0011]
An annular connection flange 4 is provided around the connection end of the upstream pipe 2, and bolt through holes 5 and 5 are formed in the connection flange 4 at symmetrical positions in the axial direction. Bolts 6 and 6 are inserted into the bolt through holes 5 and 5 from the upstream side, and a coil spring as an elastic member is interposed between the bolt head of the bolts 6 and 6 and the connection flange 4 via a washer. 7,7 are interposed.
[0012]
The bolt 6 is formed with a collar-shaped stopper 6a, and the inner diameter of the bolt through holes 5, 5 is such that the stoppers 6a, 6a can pass through. Further, a male screw portion is formed on the tip side of the bolts 6 and 6 sandwiching the stoppers 6a and 6a.
[0013]
An annular connection flange 8 is provided around the connection end of the downstream pipe 3, and bolt connection holes 9 and 9 are formed in the connection flange 8 at two symmetrical positions with respect to the center. ing. The bolt through-holes 9 and 9 and the bolt through-holes 5 and 5 of the connecting flange 4 correspond to each other at positions symmetrical with respect to the center, and the bolts 6 and 6 are respectively inserted into the corresponding positions. ing.
[0014]
Bolts 6, 6 inserted into the bolt through holes 5, 5 from the upstream side (left side in the figure) have their tips passed through the bolt through holes 9, 9, and the tips are fastened with nuts 22, 22. The screwing of the nuts 22 and 22 is restricted by the stoppers 6 a and 6 a provided on the bolts 6 and 6 coming into contact with the connection flange 8.
[0015]
The coupling means 10 that couples the two connection flanges 4 and 8 so as to be relatively displaceable from the bolts 6 and 6, the bolt through holes 5 and 5, the bolt through holes 9 and 9, the coil springs 7 and 7, and the nuts 22 and 22. Is configured.
[0016]
The two connection flanges 4 and 8 have spherical seating surfaces 11 and 12 having a concave shape on the other connection flange side. The center of curvature of the spherical seating surface 11 is located on the downstream side of the connecting flange 4, while the center of curvature of the spherical seating surface 12 is located on the upstream side of the connecting flange 8. A seal member 13 is interposed between the spherical seating surfaces 11 and 12.
[0017]
The seal member 13 is formed with convex spherical seal surfaces 16 and 17 corresponding to the two spherical seat surfaces 11 and 12, respectively, and is in sliding contact with the two spherical seat surfaces 11 and 12, respectively. That is, the shapes of the two spherical seating surfaces 11 and 12 correspond to the shapes of the seal members 16 and 17, respectively.
[0018]
Incidentally, the fact that the two spherical seating surfaces 11 and 12 correspond to the shapes of the respective spherical sealing surfaces 16 and 17 means that the curvatures of the spherical sealing surface and the spherical seating surface that are in sliding contact with each other are the same. Yes. Therefore, the center of curvature of each spherical sealing surface 16, 17 exists at the same position as the center of curvature of each spherical seating surface 11, 12 of each corresponding connecting flange 4, 8.
[0019]
The seal member 13 is formed by a gasket portion 13a in which spherical seal surfaces obtained by cutting off a part of a true spherical surface in an annular shape are formed on both left and right sides, and a cylindrical portion 13b attached to the annular inner surface of the gasket portion 13a. This cylindrical portion 13b has effects such as prevention of thermal deterioration and thermal aging of the gasket portion 13a due to direct impact of high-temperature exhaust, prevention of damage to the gasket portion 13a sandwiched in an elastically compressed state, and prevention of deformation of the gasket portion 13a. Yes.
[0020]
Next, the operation will be described.
[0021]
[Comparison of distance between centers of curvature]
FIG. 2 shows that when the first embodiment is compared with the conventional example, the distance between the centers of curvature of the first embodiment is longer than that of the conventional example. FIG. 2 is a sectional view showing a conventional spherical joint for exhaust pipe described in Japanese Patent Application Laid-Open No. 2000-27640.
[0022]
In FIG. 2, the respective curvature centers O ₀₁ and O ₀₂ are determined by the curvature radii R ₀₁ and R ₀₂ of the spherical bearing surfaces 011 and 012. The curvature centers O ₁ and O ₂ are determined by the radii of curvature R ₁ and R ₂ of the spherical bearing surfaces 11 and 12 of the first embodiment shown in FIG.
[0023]
That is, in FIG. 2, in the case of the conventional example in which only the upstream pipe 02 has two centers, the distance D ₀₁ between the curvature centers is a distance between the two curvature centers O ₀₁ and O ₀₂ . On the other hand, in the case of the first embodiment having centers in the upstream pipe and the downstream pipe, the distance D ₁ between the curvature centers is the distance between the curvature centers O ₁ and O ₂ .
[0024]
Therefore, when one of the curvature centers O ₀₂ and O ₂ is set at the same position, it is clear that the curvature center distance D ₁ of the first embodiment is longer than the curvature center distance D _{01 of} the conventional example. is there.
[0025]
[Relationship between center of curvature distance and displacement transmission suppression performance]
Next, in a spherical joint for pipes having two spherical sealing surfaces in one joint, as an index of the transmission suppression performance of the displacement in the straight direction of the pipe axis transmitted from either the upstream pipe or the downstream pipe to the other. The fact that the distance between the centers of curvature of the two spherical seal surfaces is effective will be described.
[0026]
In the case of a spherical joint for pipes having two spherical sealing surfaces in one joint, including the conventional example and the first embodiment, the center of curvature determined by each spherical seating surface of the upstream pipe and the downstream pipe, and the spherical seat The relative position (distance) with respect to the center of curvature of each spherical seal surface on the seal side corresponding to the surface is always 0, and the distance between the centers of curvature of the two spherical seat surfaces is displaced in one tube. And the distance is equal to the distance between the centers of curvature of the spherical sealing surfaces on the seal side.
[0027]
That is, if one of the upstream side pipe or the downstream side pipe is a driving side pipe that causes displacement, and the other side is a driven side pipe that is displaced by the driving side pipe, the position of the driven side pipe is The relative position (distance) is 0 with respect to the center of curvature of the spherical seating surface of the tube, and this depends on the position of the center of curvature of the spherical sealing surface on the seal side in sliding contact with the spherical seating surface.
[0028]
At this time, the displacement of the center of curvature of the spherical seal surface on the seal side that is in sliding contact with the driving side tube is determined by the displacement of the center of curvature of the spherical seating surface on the side of the driving side, and the curvature of the spherical seal surface on the sealing side that is in sliding contact with the driven side tube. The displacement of the center is determined at the position where the stress generated in the support structure of the driven side pipe determined by the displacement amount of the driven side pipe and the constraint condition of the driven side support structure is the smallest.
[0029]
That is, the displacement suppression performance of the displacement in the direction perpendicular to the pipe axis satisfies the condition of the spherical joint for pipes having the two spherical sealing surfaces in one joint, and is determined by the constraint condition of the driven pipe. When the distance between the two spherical seal surface curvature centers is long, the displacement amount of the center of curvature of the spherical seating surface of the driven side tube is smaller than the unit displacement amount of the driving side tube. If you can prove that, it's good.
[0030]
FIGS. 4 to 7 show the proof. FIG. 4 is a schematic diagram when the tube 02 is displaced in the axial direction in the conventional schematic diagram shown in FIG. 3 (a). FIG. 5 is a schematic diagram of the conventional example shown in FIG. It is a schematic diagram when displaced in the straight direction. On the other hand, FIG. 6 is a schematic diagram in the case where the pipe 2 is displaced in the direction perpendicular to the axis in the schematic diagram of the first embodiment shown in FIG. 3 (B), and FIG. 7 is the first embodiment shown in FIG. 3 (B). In a schematic diagram, it is a mimetic diagram when pipe 3 is displaced in the direction of axis straight. These schematic diagrams show that in each case, the longer the distance between the two spherical seal surface curvature centers, the smaller the displacement amount of the driven side tube relative to the unit displacement amount of the driving side tube. This will be described as a representative example.
[0031]
In FIG. 3, when the tube 02 moves by Y in the direction perpendicular to the tube axis, that is, when the center of curvature O ₀₁ is displaced by Y to O ₀₁ ′ in FIG. 4, O ₀₂ ′ has a distance D from O ₀₁ ′. Somewhere on the arc. The position is an intersection with the displacement vector of O ₀₂ → O ₀₂ ′ determined from the constraint condition of the tube 03. Therefore, when the constraint conditions of the tube 03 are the same, it is only necessary to prove that the longer the distance D, the smaller the displacement amount of O ₀₂ .
[0032]
FIG. 4 shows how the displacement of O ₀₂ changes, with the difference between the case where D is long and the case where D is short superimposed on the basis of the position before displacement of O ₀₂ . As is clear from FIG. 4, if the direction of the displacement vector of O ₀₂ is the same, it can be seen that the longer the distance D, the smaller the displacement amount (as an example of comparison of O ₀₂ ′, when D is short When comparing O ₀₂ ′ A and O ₀₂ ′ B when D is long, O ₀₂ ′ B is closer to O ₀₂ ).
[0033]
FIG. 5 also shows that the same can be said when the tube 03 is displaced. Furthermore, also for the first embodiment, it is clear from FIGS. 6 and 7 that the displacement amount of the driven side tube is smaller when the distance D between the centers of curvature is longer.
[0034]
From the above four examples, it can be said that it is effective to increase the distance D between the centers of curvature in order to make the displacement amount of the driven side tube as small as possible with respect to the axial displacement amount of the driving side tube. In other words, the displacement amount of the driven tube relative to the displacement amount of the driving tube depends on the distance D between the centers of curvature. In addition, based on the same idea as above, the center of curvature determined by the spherical seating surface of the driving side tube is also effective for displacement in a direction away from the center of curvature determined by the spherical seating surface of the driven side tube. I understand.
[0035]
[Setting example of distance between curvature centers]
Next, an example in which the first embodiment can increase the distance between the centers of curvature of the two spherical seal surfaces as compared with the conventional example.
[0036]
First, the dimensions of each part of the joint are defined. FIG. 8 schematically shows the dimensions of each part of the conventional example and the first embodiment. In the figure, one of the two spherical seal surfaces has the same or larger radius of curvature as R, and the radius of a spherical seal surface different from the spherical seal surface having this R is r (that is, , R ≧ r). Further, the axial width of the spherical seating surfaces of both connecting flanges is H, the axial width formed by the two connecting flanges is L, the axial width of the connecting flange having the radius of curvature R is T, and the radius of curvature is R. The connection flange end face having a radius of curvature R with respect to the intersection of the spherical seal surface of the spherical bearing surface of the connection flange and the tube center axis is G, the axial width of the connection flange having the radius of curvature r is t, and the connection having the radius of curvature r. Let g be the distance of the end face of the connecting flange having a radius of curvature r with respect to the intersection of the spherical sealing surface of the spherical bearing surface of the flange and the tube center axis.
[0037]
At this time, L and H are determined from constraints such as the size of the joint, and T, t, G, and g are determined from the spherical seal surface radius of curvature R, r, the pipe diameter, and the size of the joint. In addition, R and r are restricted in design from the sealing performance, durability, allowable bending angle, joint dimensions, etc. as a joint. However, as long as the application part of the joint is the same, the conventional example and the first embodiment Since the constraint conditions are considered to be the same, the dimensions of the respective parts in the conventional example and the first embodiment have the same dimension values at the same symbols.
[0038]
Here, assuming that the distance between the centers of curvature of the conventional example is D ₀ and the distance between the centers of curvature of the first embodiment is D, D ₀ and D can be expressed by the following equations using symbols in the drawing, respectively. .
D ₀ = R + L + g−r−G−T
D = r + R−L−G−g
And by setting the joint specification as in the following equation that satisfies D−D ₀ > 0 under the above-mentioned constraints, the distance between the centers of curvature can be made longer than before, that is, the transmission of displacement. Suppression performance can be improved reliably.
(R−g)> LT−2
Here, the reason why this is realistic is that the other spherical seal surface is arranged inside the one spherical seal surface arc, and the radius equal to or larger than the one spherical seal surface curvature radius is set to the other spherical seal surface curvature. The following is shown using the example of FIG. 2 in which the distance between the center of curvature of the spherical seal surfaces can be taken the longest in the conventional example given to the radius.
[0039]
In order to increase the distance between the center of curvature of the spherical seal surface in the conventional example, there are roughly the following three methods.
The first method is shown in FIG. 9, and in order to make the original center-of-curvature distance D ₀₁ of the conventional example the same as the distance D ₁ between the center of the spherical seal surface curvatures of the first example, The curvature radius of the spherical sealing surface is increased to R ₀₃ while keeping the position of the spherical seating surface 011 provided on the pipe 02 with the curvature radius O ₀₁ and the curvature radius R ₀₁ so that the outer dimension of the connection flange does not change. by center is spherical seating surface 011a such that O _03, in which attempts to achieve a curvature center distance D ₀₂ of the curvature center distance D ₁ and the same length as the first embodiment.
[0040]
However, if the distance between the spherical sealing surfaces curvature center and long distance in this way, sealability as described above, durability, the radius of curvature for receiving the design constraints of the allowable bending angle and joint dimensions and the like are allowed even R ₀₃ If so, as shown in the figure, in the first embodiment, a spherical seat surface 11 ′ having a curvature radius R ₃ and a curvature center position O ₃ having the same length as the curvature radius R ₀₃ can be realized. also it is possible to further have a long-range spherical sealing surface curvature center distance D ₂ from, it can be said that the advantage of the first embodiment does not change.
[0041]
The second method is shown in FIG. 10. The thickness of the conventional seal 013 is increased in the tube axis direction, that is, the radius of curvature of the spherical seating surface 012 of the connection flange 08 provided on the tube 03 is As it is, by moving the spherical bearing surface position to 012 ′ in order to move the center of curvature from O ₀₂ to O ₀₄ , the same length as the distance D ₁ between the centers of curvature of the first embodiment shown in FIG. A spherical seal surface curvature center distance D ₀₃ having a sq. However, as is apparent from the figure, in order to realize the center-of-curvature distance D ₀₃ , the problem arises that the outer dimension of the connection flange becomes large, so the first embodiment is superior to the conventional example. .
[0042]
The third method is shown in FIG. 11, and the spherical seal surface curvature center O ₀₂ of the spherical seating surface 012 provided on the tube 03 in the conventional example is changed to the spherical shape of the spherical seating surface 011 provided on the tube 02. In order to move away from the seal surface curvature center O _{01, the} radius of curvature of the spherical seat surface of the tube 03 is reduced as R ₅ , the spherical seat surface is 012 ", and the spherical seal surface curvature center is O ₀₅ . However, as is apparent from the figure, this method not only increases the outer dimension of the connection flange, but also causes the spherical seal surface curvature center closer to the tube 03 than the position of the straight end surface of the connection flange 08 near the tube 02 to the tube 02. It is impossible to dispose O _05. Therefore, even if it is attempted to increase the distance between the spherical seal surface curvature centers, it can only be increased to the spherical seal surface curvature center distance D ₀₄ in the figure.
[0043]
From the above, the first embodiment is practically superior to the conventional example for improving the transmission suppression performance of the displacement in the pipe axis direct direction.
[0044]
Next, the effect will be described.
(1) Since the connecting flanges 4 and 8 have spherical seating surfaces 11 and 12 that are concave toward the other connecting flange, respectively, the distance between the centers of curvature can be set longer than in the conventional example. As a result, the upstream pipe 2 or the downstream pipe 3 can exhibit an excellent transmission suppressing performance that makes it difficult to transmit the displacement in the direction of the pipe axis of either the upstream pipe 2 or the downstream pipe 3 to the other. 3 An excellent effect of making it difficult to transmit the displacement in the direction in which one of them is separated from the other to the other can be exhibited.
(2) Since the spherical sealing surfaces 16 and 17 of the sealing member 13 are formed in a convex shape corresponding to the spherical seating surfaces 11 and 12, a large contact area for the sealing function is ensured and high sealing performance is achieved. be able to.
[0045]
(Second embodiment)
The second embodiment is an example in which the pipe spherical joint 1 of the first embodiment is applied to the exhaust pipe of the engine E.
[0046]
That is, as shown in FIG. 12, in the engine E of the automobile, it is an arrangement example against vibration in the roll direction generated by the combustion excitation force, and the spherical joint for pipe 1 of the first embodiment is connected to the engine E (prime mover) and the silencer. And an extended line of a line connecting the centers of curvature of the two spherical seating surfaces is arranged so as to pass through the roll center point of the engine E. This arrangement example mainly takes into account the vibration mode during idle rotation or low engine rotation.
[0047]
Explaining the operation, as described above, the spherical joint for pipes 1 of the first embodiment is excellent in transmission suppressing performance in a direction perpendicular to the axis of the driving side pipe or in a direction away from the driven side pipe.
[0048]
Therefore, in order to utilize the effect of the spherical joint for pipes 1 of the first embodiment more effectively, it is necessary to dispose the driving side pipe so that the displacement of the driving side pipe is in the direction perpendicular to the pipe axis or away from the driven side pipe.
[0049]
On the other hand, in the second embodiment, the movement of the engine E in the roll direction gives displacement to the driving side pipe in the direction perpendicular to the axis or away from the driven side pipe. The exhaust system vibration at the time can be effectively reduced.
[0050]
As described above, in the spherical joint for pipes of the second embodiment, the spherical joint for pipes 1 of the first embodiment is applied to the exhaust pipe of the engine E, and the two of the driving side exhaust pipe and the driven side exhaust pipe are used. The connection flange is set so that the extension line of the line connecting the centers of curvature of the two spherical bearing surfaces passes through the roll center point of the engine E, so that the movement of the engine E in the roll direction is relative to the driving side pipe. It is possible to effectively reduce the exhaust system vibration during idle rotation or low engine rotation that gives displacement in the direction perpendicular to the axis or away from the driven side pipe.
[0051]
(Third embodiment)
The third embodiment is an example in which the pipe spherical joint 1 of the first embodiment is applied to the exhaust pipe of the engine E as in the second embodiment.
[0052]
That is, as shown in FIG. 13, in the engine E of the automobile, this is an arrangement example for translational vibration due to the inertial excitation force in the translational direction generated by the translational motion of a mass such as a piston. The pipe spherical joint 1 is connected to the exhaust pipe between the engine E (prime mover) and the silencer, and the extension line of the line connecting the centers of curvature of the two spherical seating surfaces is perpendicular to the translational displacement direction of the engine E. It arrange | positions so that it may become. This arrangement example mainly takes into account the vibration mode during high engine rotation. Here, the term “perpendicular” includes not only perfect vertical but also an angle approximated thereto.
[0053]
Explaining the operation, in the third embodiment, as is apparent from FIG. 13, since the displacement component in the direction perpendicular to the pipe axis enters the driving side pipe, the exhaust system vibration at the time of high engine rotation is effective as a result. Can be reduced.
[0054]
As described above, in the pipe spherical joint of the third embodiment, the pipe spherical joint 1 of the first embodiment is applied to the exhaust pipe of the engine E, and the two of the driving side exhaust pipe and the driven side exhaust pipe are used. The connection flange is set so that the line connecting the centers of curvature of the two spherical seating surfaces is perpendicular to the translational displacement direction of the engine E. The vibration of the exhaust system at the time of high engine rotation resulting in the displacement of can be effectively reduced.
[0055]
(Other examples)
The spherical joint for pipes of the present invention has been described based on the first to third embodiments. However, the specific configuration is not limited to these embodiments, and each claim of the claims Design changes and additions are permitted without departing from the spirit of the invention according to the paragraph.
[0056]
For example, in the second and third embodiments, the pipe spherical joint 1 is applied to an exhaust pipe of an automobile engine. However, the pipe spherical joint of the present invention is applied to various pipe systems to which vibration displacement is transmitted. Can be applied.
[Brief description of the drawings]
FIG. 1 is a side view showing a spherical joint for pipes of a first embodiment.
FIG. 2 is an explanatory diagram showing a comparison of the distance between the centers of curvature in the conventional example and the first embodiment.
FIG. 3 is a schematic structural view (A) of a conventional example, and a schematic structural view (B) of a first embodiment.
4 is a schematic diagram when the pipe 02 is displaced in the direction perpendicular to the axis in FIG.
FIG. 5 is a schematic view when the tube 03 is displaced in the direction perpendicular to the axis in FIG.
6 is a schematic view when the pipe 2 is displaced in the direction perpendicular to the axis in FIG.
7 is a schematic view when the tube 3 is displaced in the direction perpendicular to the axis in FIG.
FIG. 8 is a schematic diagram (a) of each part of the conventional example and a schematic diagram (b) of each part of the first embodiment.
FIG. 9 is an explanatory diagram showing a comparison of difficulty in increasing the distance between the centers of spherical seal surface curvatures in the conventional example and the first example.
FIG. 10 is an explanatory view showing a comparison of difficulty in increasing the distance between the centers of spherical seal surface curvatures of the conventional example and the first example.
FIG. 11 is an explanatory diagram showing a comparison of difficulty in increasing the distance between the centers of spherical seal surface curvatures in the conventional example and the first example.
FIG. 12 is a schematic diagram showing a configuration of a second embodiment.
FIG. 13 is a schematic diagram showing a configuration of a third embodiment.
[Explanation of symbols]
1 spherical joint for pipe 2 upstream pipe 3 downstream pipe 4, 8 connecting flange 5, 9 bolt through hole 6 bolt 7 coil spring 10 coupling means 11, 12 spherical bearing surface 13 sealing members 16, 17 spherical sealing surface

Claims (4)

A connection flange provided at the connection end of both the upstream pipe and the downstream pipe;
A seal member in sliding contact with these two connection flanges;
A coupling means for coupling the two connection flanges in a relatively displaceable manner;
In a spherical joint for pipes with
The two connection flanges each have a spherical bearing surface that is concave toward the other connection flange side,
The center of curvature of the spherical seating surface on the upstream tube side is located downstream of the center of curvature of the spherical seating surface on the downstream tube side and downstream of the spherical seating surface on the downstream tube side , and downstream The center of curvature of the spherical seating surface on the side tube side is arranged upstream of the center of curvature of the spherical seating surface on the upstream side of the tube and upstream of the spherical seating surface of the upstream side of the tube. Spherical joint for pipes. In the spherical joint for pipes described in Claim 1,
The spherical joint for pipes, wherein the seal member has convex spherical seal surfaces respectively corresponding to the two spherical seating surfaces. In the spherical joint for pipes described in Claim 1 or Claim 2,
The upstream side pipe and the downstream side pipe are a driving side exhaust pipe and a driven side exhaust pipe respectively connected to a prime mover,
The two connection flanges of the driving side exhaust pipe and the driven side exhaust pipe are set so that an extension line of the line connecting the respective curvature centers of the two spherical seating surfaces passes through the roll center point of the driving machine. A spherical joint for pipes. In the spherical joint for pipes described in Claim 1 or Claim 2,
The upstream side pipe and the downstream side pipe are a driving side exhaust pipe and a driven side exhaust pipe respectively connected to a prime mover,
The two connecting flanges of the driving side exhaust pipe and the driven side exhaust pipe are characterized in that a line connecting the centers of curvature of the two spherical seating surfaces is set to be perpendicular to the translational displacement direction of the prime mover. Spherical joint for pipes.

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