US2013200247A1PendingUtilityA1
Pipe support structure
Est. expiryOct 1, 2030(~4.1 yrs left)· nominal 20-yr term from priority
Inventors:Hironori Miki
Y10T29/49959F16D 2048/0224F16L 3/16F16L 55/035F16L 11/08
28
PatentIndex Score
0
Cited by
0
References
0
Claims
Abstract
A pipe support structure which is constructed to utilize the Coriolis force and the reaction force caused, thereby making it possible to suppress the hose compliance amount in the high temperature area while maintaining the degree of freedom of mountability specific for the resin pipe and to realize the above suppressing effect by the simple construction and at a low cost.
Claims
exact text as granted — not AI-modified1 . A pipe support structure for supporting a pipe supported at a first clamp position and a second clamp position, the pipe having a fluid passage formed therein to allow a fluid at a high temperature to pass therethrough, and made of a resilient material, comprises:
a retaining member for resiliently retaining the outer peripheral portion at at least one of the first clamp position and the second clamp position, the pipe having an inclined portion inclined with respect to a horizontal plane perpendicular to the gravity direction, and a bent portion having a predetermined radius of curvature, the inclined portion and the bent portion being disposed between the first clamp position and the second clamp position, the retaining member having a predetermined spring constant and a predetermined attenuation coefficient, the pipe being subjected to a Coriolis force and having a heat expansion amount caused by the Coriolis force when the fluid passage allows the fluid at the high temperature, the retaining member having a reaction force acting against the Coriolis force, at least one of the first clamp position and the second clamp position and the shape of the bent portion being set, and the spring constant and the attenuation coefficient of the retaining member being set in such a manner that the reaction force of the retaining member generated in response to the Coriolis force generated on the pipe acts to suppress the heat expansion amount caused by the Coriolis force from being increased when the fluid passage allows the fluid at the high temperature.
2 . A pipe support structure as set forth in claim 1 , in which when the Coriolis force is represented by F c , the fluid angular speed of the fluid passing through the fluid passage is represented by ω, and the time is represented by t, the Coriolis coercive force f c temporally varying in response to the vibration of the pipe is given by f c (t)=F c sin ωt,
when the reaction force caused on the retaining member against the Coriolis force F c is represented by F r , and the clamp reaction force caused on the retaining member and temporally varying in response to the Coriolis coercive force f c (t) is represented by f r (t), the clamp reaction force f r (t) is given by f r (t)=Fr sin(ωt−φ),
when the coefficient to be determined in response to the ratio of the clamp reaction force f r (t) with respect to the Coriolis coercive force f c (t) is “k”, the first clamp position, the second clamp position, the shape of the bent portion, the spring constant, and the attenuation coefficient are set to have the coefficient “k” in the following equation (1) approach the number of 1
f c ( t )=−κ f r ( t ) (1)
3 . A pipe support structure as set forth in claim 2 , in which when the fluid mass of the fluid passing through the fluid passage between the first clamp position and the second clamp position is represented by “m”, and the fluid speed passing through the fluid passage is represented by “V”, the Coriolis force is given by the following equation (2),
F c =2 mωV (2)
when the fluid density of the fluid is represented by “ρ”, the fluid speed passing through the fluid passage between the first clamp position and the second clamp position is represented by “v”, and the radius of curvature of the bent portion is represented by “r”, the fluid mass “m” and the fluid angular speed ω in the above equation (2) are given by the following equations (3) and (4), respectively,
m
=
ρ
·
v
(
3
)
ω
=
V
r
(
4
)
at least one of the first clamp position and the second clamp potion is adjusted, and the fluid mass “m” indicated in the above equation (3) is adjusted to adjust the Coriolis force F c indicative of the amplitude of vibration in the above Coriolis coercive force f c (t), and
the radius of curvature “r” of the bent portion is adjusted to adjust the fluid annular speed ω.
4 . A pipe support structure as set forth in claim 2 , in which
when the inherent vibration number of the retaining member is represented by ω n , the damping ratio is represented by ζ, and the spring constant is represented by “k”, the reaction force F r and the phase difference φ indicative of the amplitude in the clamp reaction force f r (t) are given by the following equations (5) and (6),
F
r
≃
F
c
/
k
{
1
-
(
ω
ω
n
)
2
}
2
+
(
2
ζ
ω
ω
n
)
2
(
5
)
φ
=
tan
-
1
{
2
ζ
ω
ω
n
1
-
(
ω
ω
n
)
2
}
(
6
)
when the attenuation coefficient is represented by “h”, and a total mass totaling the fluid mass of the whole fluid passage and the mass of the pipe is represented by “M”, the inherent angular vibration number ω n and the damping ratio ζ in the above equations (5) and (6) are given by the following equations (7) and (8), respectively,
ω
n
=
k
M
(
7
)
ζ
=
h
2
Mk
(
8
)
the spring constant “k” and the attenuation coefficient “h” are adjusted to adjust the phase difference φ and the reaction force F 1 .
5 . A pipe support structure as set forth in claim 3 , in which
when the inherent vibration number of the retaining member is represented by ω n , the damping ratio is represented by ζ, and the spring constant is represented by “k”, the reaction force F r and the phase difference φ indicative of the amplitude in the clamp reaction force f r (t) are given by the following equations (5) and (6),
F
r
≃
F
c
/
k
{
1
-
(
ω
ω
n
)
2
}
2
+
(
2
ζ
ω
ω
n
)
2
(
5
)
φ
=
tan
-
1
{
2
ζ
ω
ω
n
1
-
(
ω
ω
n
)
2
}
(
6
)
when the attenuation coefficient is represented by “h”, and a total mass totaling the fluid mass of the whole fluid passage and the mass of the pipe is represented by “M”, the inherent angular vibration number ω n and the damping ratio in the above equations (5) and (6) are given by the following equations (7) and (8), respectively,
ω
n
=
k
M
(
7
)
ζ
=
h
2
Mk
(
8
)
the spring constant “k” and the attenuation coefficient “h” are adjusted to adjust the phase difference φ and the reaction force F 1 .Join the waitlist — get patent alerts
Track US2013200247A1 — get alerts on status changes and closely related new filings.
We store only your email — no account needed. See our privacy policy.