CN109253351A - A kind of dismountable moving annular ear mount - Google Patents
A kind of dismountable moving annular ear mount Download PDFInfo
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- CN109253351A CN109253351A CN201811135673.2A CN201811135673A CN109253351A CN 109253351 A CN109253351 A CN 109253351A CN 201811135673 A CN201811135673 A CN 201811135673A CN 109253351 A CN109253351 A CN 109253351A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16M—FRAMES, CASINGS OR BEDS OF ENGINES, MACHINES OR APPARATUS, NOT SPECIFIC TO ENGINES, MACHINES OR APPARATUS PROVIDED FOR ELSEWHERE; STANDS; SUPPORTS
- F16M7/00—Details of attaching or adjusting engine beds, frames, or supporting-legs on foundation or base; Attaching non-moving engine parts, e.g. cylinder blocks
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Abstract
The present invention relates to a kind of dismountable moving annular ear mounts, it include: annular ear mount ontology, backing plate, interconnecting piece and the Non-slip material of two same sizes, two annular ear mount ontologies are opposite to be set on drum equipment, annular ear mount ontology includes stiffening ring and gusset group, stiffening ring includes upper ring plate and lower ring plate, several groups gusset group is uniformly provided between upper ring plate and lower ring plate, gusset group and upper ring plate, lower ring plate form support；Since annular ear mount is made into detachable two annular ear mount ontologies, mounted and dismounted in equipment convenient for annular ear mount ontology, it is time saving and energy saving without subsequent pressure testing, leakage test etc. due to welding of not getting angry；And optimal annular ear mount ontology manufacture material and shape size may be selected, material is saved to greatest extent after the structural strength for reaching annular ear mount.
Description
Technical Field
The invention relates to an ear seat, in particular to a detachable movable annular ear seat.
Background
The annular ear seat on the existing chemical equipment is welded with the equipment body into a whole, and under the ordinary condition, the annular ear seat is welded with the equipment body in a manufacturing plant and then is transported to the site to be integrally installed from top to bottom in place. However, for the situation that the space of part of construction sites is narrow, the installation from top to bottom cannot be met, and only the installation method from bottom to top is adopted; however, the annular lug seat needs to be cut off when the device is installed from bottom to top, the lug seat needs to be welded secondarily on site after the device is installed in place, and subsequent pressure tests, leakage tests and the like are carried out, so that the time consumption is long, and the cost is high.
Disclosure of Invention
In order to overcome the defects, the invention provides a detachable movable annular ear seat.
The technical scheme adopted by the invention for solving the technical problems is as follows: a removable mobile ring ear mount comprising:
two annular ear mount bodies of equal size;
the backing plates are respectively arranged on the inner cambered surfaces of the annular ear seat bodies;
the connecting parts are respectively arranged at two ends of the annular ear seat body and are used for connecting the two annular ear seat bodies;
the anti-slip piece is arranged on the cylindrical equipment and plays a role in limiting the annular lug seat;
the two annular lug seat bodies are oppositely sleeved on the cylindrical equipment and comprise rigid rings and rib plate groups, each rigid ring comprises an upper ring plate and a lower ring plate, a plurality of rib plate groups are uniformly arranged between the upper ring plate and the lower ring plate, and the rib plate groups, the upper ring plate and the lower ring plate form a support.
In a preferred embodiment of the present invention, the anti-slip member is welded on the cylindrical device, the anti-slip member is an anti-slip block, and the area of the anti-shear section required by the welding seam of the anti-slip block is calculated by the following formula:
Aw＝0.7×T3×L3×n， (1)
wherein, T3Is the thickness of the antiskid block, L3Length of anti-skid block, n is the number of anti-skid blocks, T3And L3The units of (A) are all mm;
the calculation formula of the gravity required to bear the welding line of the antiskid block is as follows: fbe＝max(Fb,Fb'[σ]/[σ]0)， (2)
Wherein,M＝Fh×h1，M'＝Fh'×h1，
[σ]allowable stress at design temperature for rigid ring material, [ sigma ]]0Allowable stress of rigid ring material at normal temperature, GeFor eccentric loading of cylinder equipment, SeFor cylinder equipment eccentric distance, FLAdditional horizontal thrust for external objects acting on the cylinder equipment, h2Distance of horizontal thrust from bottom plate of supportN is the number of supports, DbIs the diameter of the central circle of the foundation bolt, moFor the operating mass of the cylinder apparatus, g is 9.81, h1Is the distance m from the lower surface of the lower ring plate of the support to the gravity center of the cylinder equipmenttThe quality of the cylinder equipment in the test is shown; fhFor horizontal forces acting on the cylinder apparatus during operation, Fh' horizontal force acting on the cylinder apparatus in the hydrostatic test, FbeThe gravity required to bear the welding line of the antiskid block;
the actual shear stress calculation formula that need bear of non-skid blocks is: τ ═ Fbe/Aw，
Wherein, FbeIs formula (2), AwIn equation (1), τ is the shear stress actually required to be borne by the anti-skid block.
In a preferred embodiment of the present invention, the backing plate, the rib plate group, the upper ring plate and the lower ring plate are welded into a whole, the rib plate group comprises a plurality of rib plates, and the mechanical property calculation formulas corresponding to the backing plate, the rib plates, the upper ring plate and the lower ring plate are as follows:
the calculation formula of the force to be borne by the base plate is as follows: i ═ I1+I2+I3， (3)
Wherein,a1＝a-0.5×B，a2＝B+0.5×δ1-a，a3＝B+δ1+0.5×δ0-a，
Lsi＝min(Lsi',C+Lsi'/2,h/2+min(C,Lsi'/2))， (31)
a is the distance from the outer edge of the rigid ring to the inertial axis, B is the width of the rigid ring, T is the effective thickness of the rigid ring, and δ01The thickness of the base plate after deducting the additional amount of the wall thickness, C is the reinforcing width of the base plate, h is the height of the support, and delta0For deducting the thickness required by internal or external pressure calculation and the surplus thickness delta of the cylinder equipment after deducting the additional amount of the thickness1Nominal thickness of the backing plate, D0Is the outer diameter of the cylinder equipment, D01The outside diameter of the backing plate, a, B, T, delta01、C、h、δ0、δ1、D0And D01The units are all mm;
the calculation formula of the maximum compressive stress required to be borne by the rib plate is as follows:
σc,max＝FR/L1δ4+6eFR/L1 2δ4, (4)
wherein L is1＝(Dob-D01)sinβ/2，e＝(b-(Dob-D01)/4)sinβ，
β＝atan(hg/((Dob-D01)/2-B))， (5)
FRThe maximum compressive stress of the rib material is expressed in the unit of N, delta4The thickness of the web excluding the wall thickness, DobIs the outer diameter of the support, D01Is the outer diameter, σ, of the backing platecThe unit of the maximum compressive stress required to be borne by the rib plate is MPa; b is a reaction force FbThe distance from the outer wall of the shell, namely the distance from the intersection point of the neutral axis of the support and the lower surface of the lower ring plate to the outer wall of the cylinder equipment, hgIs the rib height, B is the width of the rigid ring, delta4、Dob、D01、b、hgAnd the units of B are both mm;
the calculation formula of the stress required to be borne by the upper ring plate and the lower ring plate is as follows:and sigma1≤[σ]And at the same time satisfyAnd sigma2≤[σ]WhereinTr1＝0.5F·ctgθ，A＝B×T+δ01×Lsi+δ0×Ls，Rs＝0.5×Ds，Ds＝D0+2×(δ1+ B-a), θ ═ pi/n, I is formula (3), a is the distance from the outer edge of the rigid ring to the axis of inertia, B is the width of the rigid ring, T is the effective thickness of the rigid ring, δ01The thickness of the base plate after deducting the additional amount of wall thickness, LsiIs represented by the formula (31), LsIs the formula (32), δ0For deducting the thickness required by internal or external pressure calculation and the excess thickness of the cylinder after deducting the additional amount of the thickness, FbeIs the formula (2), b is the reaction force FbThe distance from the outer wall of the shell, namely the distance from the intersection point of the neutral axis of the support and the lower surface of the lower ring plate to the outer wall of the cylinder equipment, h is the height of the support, and D is the distance from the lower surface of the lower ring plate to the outer wall of the cylinder equipment0Is the outer diameter of the shell of the cylindrical equipment, delta1Is the nominal thickness of the backing plate, n is the number of supports, a, B, T, delta01、h、δ0、δ1、D0And b are both in mm.
In a preferred embodiment of the invention, the connecting part comprises a connecting plate and a bolt, the two ends of the annular lug seat body are provided with the connecting plates, and the connecting plates on the two annular lug seat bodies are connected through the bolt;
the calculation formula of the maximum compressive stress required to be born by the connecting plate is as follows: sigmac,max＝FR/L1δ4+6eFR/L1 2δ4Which isIn, σcIs formula (4);
the calculation formula of the actual shearing stress of the bolt required by the bolt is as follows: τ a ═ Fbe/(nA*A1) And τ A<[τA]，
Wherein, FbeIs formula (2), nATo connect the number of bolts, A1Is the bolt area in mm2，[τA]The allowable shearing stress of the bolt is in MPa, and the tau A is the actual shearing stress required by the bolt and is in MPa.
In a preferred embodiment of the present invention,
wherein L issiIs represented by the formula (31), LsIs equation (32), B is the width of the rigid ring, T is the effective thickness of the rigid ring, δ01The thickness, delta, of the shim plate after deducting the additional amount of wall thickness0For deducting the thickness required by internal or external pressure calculation and the surplus thickness of the cylinder equipment after deducting the additional amount of the thickness, B, T, delta01And delta0The units of (A) are all mm.
In a preferred embodiment of the invention, Fh＝max(Fw，Pe+0.25Fw)，Fh'＝Fw'，
Wherein, Fw＝1.2×f×qo×H×De×10-6，Fw'＝0.3Fw，
When Z is less than or equal to 5m, f is 0.794Z 0.24When Z is less than or equal to 10m, f is 0.479Z 0.32When Z is less than or equal to 15m, f is 0.2244Z 0.44When Z is less than or equal to 30m, f is 0.0798Z 0.60Z is the height of the center of mass of the cylinder equipment from the ground and has the unit of m and qoIs the basic wind pressure with the unit of Pa, the height of the equipment with the unit of mm, and the DeIs the effective equivalent diameter of the cylinder, and the unit is mm, FhActing when using the apparatusHorizontal force in cylindrical devices is given in units of N.
In a preferred embodiment of the invention, FR＝Fbe/(ksin β), wherein β is formula (5), FbeIs formula (2), k is the number of webs per carrier, FRIs the maximum compressive stress of the web material in units of N.
The invention has the beneficial effects that: the annular lug seats are made into the two detachable annular lug seat bodies, so that the annular lug seat bodies can be conveniently installed and detached on equipment, and the subsequent pressure test, leakage test and the like are not needed due to no dynamic fire welding, so that time and labor are saved; and each part of the annular ear seat body calculates each force to be born through a corresponding formula, and the optimal manufacturing material and shape and size of the annular ear seat body can be selected according to the calculation result, so that the material is saved to the maximum extent after the structural strength of the annular ear seat is reached.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is an enlarged view of the structure at A in FIG. 1;
FIG. 3 is a schematic structural view of the annular ear mount body of the present invention;
FIG. 4 is a right side view of FIG. 3;
FIG. 5 is a first diagram illustrating the specific locations of parameters in the present invention;
fig. 6 is a diagram illustrating the specific positions of parameters in the present invention.
Detailed Description
The following detailed description of the preferred embodiments of the present invention, taken in conjunction with the accompanying drawings, will make the advantages and features of the invention easier to understand by those skilled in the art, and thus will clearly and clearly define the scope of the invention.
As shown in fig. 1 to 6, a removable mobile ring ear holder comprises:
the annular ear seat bodies in the embodiment of the two annular ear seat bodies 1 with the same size are semicircular, and the two semicircular ear seat bodies are oppositely arranged to form a circular ear seat;
the backing plates 2 are respectively arranged on the inner arc surfaces of the annular ear seat body 1, and in the embodiment, the backing plates are welded on the inner arc surfaces of the annular ear seat body;
the connecting parts are respectively arranged at two ends of the annular ear seat body 1 and are used for connecting the two annular ear seat bodies 1, so that the two annular ear seat bodies form an integral circular ear seat;
the anti-slip piece 3 is arranged on the cylindrical equipment, has a limiting effect on the annular ear seat body 1 and prevents the annular ear seat body from falling off the equipment;
two annular ear seat body covers in opposite directions and establishes on drum equipment 4, annular ear seat body 1 includes rigidity ring 10 and muscle group, rigidity ring 10 includes crown plate 101 and lower crown plate 102, it evenly is equipped with a plurality of groups muscle group to go up crown plate 101 and lower crown plate 102 within a definite time, muscle group and crown plate 101, support 104 is constituteed to lower crown plate 102, because the backing plate welding is at the interior cambered surface of annular ear seat, when assembling annular ear seat body on drum equipment, backing plate and drum equipment direct contact, effectively slow down the vibrations that drum equipment caused the annular ear seat body when moving.
The 3 welding of antiskid on drum equipment 4, 3 antiskid are the non slipping spur, and the required sectional area formula of shearing that the non slipping spur welding seam is: a. thew＝0.7×T3×L3×n， (1)
Wherein, T3Is the thickness of the antiskid block, L3Length of anti-skid block, n is the number of anti-skid blocks, T3And L3The units of (A) are all mm;
the calculation formula of the gravity required to bear the welding line of the antiskid block is as follows: fbe＝max(Fb,Fb'[σ]/[σ]0)， (2)
Wherein,M＝Fh×h1，M'＝Fh'×h1，
[σ]allowable stress at design temperature for rigid ring material, [ sigma ]]The unit is Mpa, [ sigma ]]0Is allowable stress of rigid ring material at normal temperature, and the unit is MPa, GeIs the eccentric load of the cylinder equipment, and the unit is N, SeIs the eccentric distance of the cylinder equipment, in mm, FLFor additional horizontal thrust of external objects acting on the cylinder apparatus, the units are N, h2Is the distance of the horizontal thrust from the bottom plate of the support, and has the unit of mm, n is the number of the supports, DbIs the diameter of the central circle of the foundation bolt, and the unit is mm, moThe mass of the cylinder apparatus in operation is kg, g is the acceleration of gravity 9.81, h1The distance from the lower surface of the lower ring plate of the support to the gravity center of the cylinder device is mm and mtThe mass in kg for the cylinder equipment test; fhFor horizontal forces acting on the cylinder apparatus during operation, the units are N, Fh' horizontal force applied to the cylinder apparatus in the hydrostatic test is in units of N, FbeThe unit of the gravity which is required to bear the welding line of the antiskid block is N;
the actual shear stress calculation formula that need bear of non-skid blocks is: τ ═ Fbe/Aw，
Wherein, FbeIs formula (2), AwAnd in formula (1), tau is the shear stress actually required to bear by the antiskid block and has a unit of MPa.
Backing plate, gusset group, go up the crown plate and weld as an organic wholely with lower crown plate, increased the holistic structural strength of annular ear seat body, gusset group includes a plurality of gussets, can adjust the quantity of gusset in the support as required, in this embodiment, goes up gusset group well gusset of going up crown plate and lower crown plate and is 2, and backing plate 2, gusset 103, the mechanical properties computational formula that upper ring plate 101 and lower crown plate 103 correspond are as follows:
the calculation formula of the force to be borne by the backing plate 2 is: i ═ I1+I2+I3， (3)
Wherein,a1＝a-0.5×B，a2＝B+0.5×δ1-a，a3＝B+δ1+0.5×δ0-a，
Lsi＝min(Lsi',C+Lsi'/2,h/2+min(C,Lsi'/2))， (31)
a is the distance from the outer edge of the rigid ring to the inertial axis, B is the width of the rigid ring, T is the effective thickness of the rigid ring, and δ01The thickness of the base plate after deducting the additional amount of the wall thickness, C is the reinforcing width of the base plate, h is the height of the support, and delta0The residual thickness delta of the cylinder equipment after the thickness required for calculation of the internal pressure or external pressure is deducted (calculated thickness) and the additional quantity of the deducted thickness (corrosion allowance and thickness negative deviation)1Nominal thickness of the backing plate, D0Is the outer diameter of the cylinder equipment, D01The outside diameter of the backing plate, a, B, T, delta01、C、h、δ0、δ1、D0And D01The units are all mm;
the maximum compressive stress that the rib plate 103 needs to bear is calculated by the formula:
σc,max＝FR/L1δ4+6eFR/L1 2δ4, (4)
wherein L is1＝(Dob-D01)sinβ/2，e＝(b-(Dob-D01)/4)sinβ，
β＝atan(hg/((Dob-D01)/2-B))， (5)
FRThe maximum compressive stress of the rib material is expressed in the unit of N, delta4The thickness of the web excluding the wall thickness, DobIs the outer diameter of the support, D01Is the outer diameter, σ, of the backing platecThe unit of the maximum compressive stress required to be borne by the rib plate is MPa; b is a reaction force FbThe distance from the outer wall of the shell, namely the distance from the intersection point of the neutral axis of the support and the lower surface of the lower ring plate to the outer wall of the cylinder equipment, hgIs the rib height, B is the width of the rigid ring, delta4、Dob、D01、b、hgAnd the units of B are both mm;
the calculation formula of the stress to be borne by the upper ring plate 101 and the lower ring plate 102 is as follows:and sigma1≤[σ]And at the same time satisfyAnd sigma2≤[σ]WhereinTr1＝0.5F·ctgθ，A＝B×T+δ01×Lsi+δ0×Ls，Rs＝0.5×Ds，Ds＝D0+2×(δ1+B-a)，θ＝π/n，[σ]the allowable stress at the design temperature for the rigid ring material, I is formula (3)A is the distance from the outer edge of the rigid ring to the inertial axis, B is the width of the rigid ring, T is the effective thickness of the rigid ring, and delta01Deducting L from the wall thickness of the backing platesThickness after addition of wall thickness, LsiIs formula (31), is formula (32), delta0The thickness required for calculation of the internal or external pressure (calculated thickness) and the residual thickness of the cylinder after the additional amount of the thickness (corrosion allowance and negative deviation of the thickness) is deducted, FbeIs formula (2), b is the distance from the counterforce Fb to the outer wall of the shell, h is the height of the support, D0Is the outer diameter of the shell of the cylindrical equipment, delta1Is the nominal thickness of the backing plate, n is the number of supports, a, B, T, delta01、h、δ0、δ1、D0And b are both in mm.
The connecting part comprises connecting plates 501 and bolts 502, the connecting plates 501 are arranged at two ends of the annular ear seat body 1, and the connecting plates 501 on the two annular ear seat bodies 1 are connected through the bolts 502;
the maximum compressive stress that the connecting plate 501 needs to bear is calculated by the formula: sigmac,max＝FR/L1δ4+6eFR/L1 2δ4Wherein σ iscIs formula (4);
the actual shear stress calculation formula of the bolt 502 is as follows: τ a ═ Fbe/(nA*A1) And τ A<[τA]，
Wherein, FbeIs formula (2), nATo connect the number of bolts, A1Is the bolt area in mm2，[τA]The allowable shearing stress of the bolt is in MPa, and the tau A is the actual shearing stress required by the bolt and is in MPa.
The distance a from the outer edge of the rigid ring to the inertia axis is calculated as follows:
wherein L issiIs represented by the formula (31), LsIs of formula (32) and B is a rigid ringWidth, T being the effective thickness of the rigid ring, delta01The thickness, delta, of the shim plate after deducting the additional amount of wall thickness0The residual thickness of the cylinder equipment after the thickness required by internal or external pressure calculation (calculated thickness) and the additional amount of the thickness (corrosion allowance and negative deviation of the thickness) are deducted is B, T, delta01And delta0The units of (A) are all mm.
Horizontal force F acting on the cylinder apparatus when the cylinder apparatus is used and when the cylinder apparatus is subjected to a hydraulic testhThe calculation formulas of (A) are respectively as follows: fh＝max(Fw，Pe+0.25Fw)，Fh'＝Fw'，
Wherein, Fw＝1.2×f×qo×H×De×10-6，Fw'＝0.3Fw，
When Z is less than or equal to 5m, f is 0.794Z 0.24When Z is less than or equal to 10m, f is 0.479Z 0.32When Z is less than or equal to 15m, f is 0.2244Z 0.44When Z is less than or equal to 30m, f is 0.0798Z 0.60Z is the height of the center of mass of the cylinder equipment from the ground and has the unit of m and qoIs the basic wind pressure with the unit of Pa, the height of the equipment with the unit of mm, and the DeIs the effective equivalent diameter of the cylinder, and the unit is mm, FhThe horizontal force acting on the cylindrical device when the device is in use is given in units of N.
Maximum compressive stress F of rib materialRIs as follows, FR＝Fbe/(ksin β), wherein β is formula (5), FbeIs formula (2), k is the number of webs per carrier, FRIs the maximum compressive stress of the web material in units of N.
The cylindrical equipment can be conveniently installed from bottom to top only by loosening the connecting plate at the joint of the annular lug seat bodies and taking down the annular lug seat after the annular lug seats are made into the two detachable annular lug seat bodies in a manufacturing plant, and then the two annular lug seats are oppositely arranged and then are fixed on the cylindrical equipment again through the connecting plate and screws, so that the time and labor are saved because the circular lug seats are not subjected to dynamic fire welding, and subsequent pressure tests, leakage tests and the like are not required; and each part of the annular ear seat body calculates each force to be born through a corresponding formula, and the optimal manufacturing material and shape and size of the annular ear seat body can be selected according to the calculation result, so that the material is saved to the maximum extent after the structural strength of the annular ear seat is reached.
It is to be emphasized that: the above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications of equivalent structures and equivalent processes performed by the present specification and drawings, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (7)
1. A detachable mobile annular ear mount, comprising:
two annular ear mount bodies of equal size;
the backing plates are respectively arranged on the inner cambered surfaces of the annular ear seat bodies;
the connecting parts are respectively arranged at two ends of the annular ear seat body and are used for connecting the two annular ear seat bodies;
the anti-slip piece is arranged on the cylindrical equipment and plays a role in limiting the annular lug seat;
the two annular lug seat bodies are oppositely sleeved on the cylindrical equipment, each annular lug seat body comprises a rigid ring and a rib plate group, each rigid ring comprises an upper ring plate and a lower ring plate, a plurality of rib plate groups are uniformly arranged between the upper ring plate and the lower ring plate, and the rib plate groups, the upper ring plate and the lower ring plate form a support.
2. The removable mobile annular ear mount according to claim 1, wherein said anti-slip means are welded to the cylindrical device, said anti-slip means are anti-slip blocks, and the area calculation formula of the shear section required by the weld of said anti-slip blocks is:
Aw＝0.7×T3×L3×n， (1)
wherein, T3Is the thickness of the antiskid block, L3Length of anti-skid block, n is the number of anti-skid blocks, T3And L3The units of (A) are all mm;
the calculation formula of the gravity required to bear the welding line of the antiskid block is as follows: fbe＝max(Fb,Fb'[σ]/[σ]0)， (2)
Wherein,M＝Fh×h1，M'＝Fh'×h1，
[σ]allowable stress at design temperature for rigid ring material, [ sigma ]]The unit is Mpa, [ sigma ]]0Is allowable stress of rigid ring material at normal temperature, and the unit is MPa, GeIs the eccentric load of the cylinder equipment, and the unit is N, SeIs the eccentric distance of the cylinder equipment, in mm, FLFor additional horizontal thrust of external objects acting on the cylinder apparatus, the units are N, h2Is the distance of the horizontal thrust from the bottom plate of the support, and has the unit of mm, n is the number of the supports, DbIs the diameter of the central circle of the foundation bolt, and the unit is mm, moThe mass of the cylinder apparatus in operation is kg, g is the acceleration of gravity 9.81, h1The distance from the lower surface of the lower ring plate of the support to the gravity center of the cylinder device is mm and mtThe mass in kg for the cylinder equipment test; fhFor horizontal forces acting on the cylinder apparatus during operation, the units are N, Fh' horizontal force applied to the cylinder apparatus in the hydrostatic test is in units of N, FbeThe unit of the gravity which is required to bear the welding line of the antiskid block is N;
the actual shear stress calculation formula that needs to bear of non-skid blocks is: τ ═ Fbe/Aw，
Wherein, FbeIs formula (2), AwIn equation (1), τ is the shear stress actually required to be borne by the anti-skid block, and its unit is MPa.
3. The detachable movable ring-shaped ear seat according to claim 1, wherein the backing plate, the rib plate group, the upper ring plate and the lower ring plate are welded into a whole, the rib plate group comprises a plurality of rib plates, and the corresponding mechanical property calculation formulas of the backing plate, the rib plates, the upper ring plate and the lower ring plate are as follows:
the calculation formula of the force required to be borne by the base plate is as follows: i ═ I1+I2+I3， (3)
Wherein,a1＝a-0.5×B，a2＝B+0.5×δ1-a，a3＝B+δ1+0.5×δ0-a，
Lsi＝min(Lsi',C+Lsi'/2,h/2+min(C,Lsi'/2))， (31)
a is the distance from the outer edge of the rigid ring to the inertial axis, B is the width of the rigid ring, T is the effective thickness of the rigid ring, and δ01The thickness of the base plate minus the additional amount of wall thickness, C the reinforcing width of the base plate, and h the supportHeight, delta0For deducting the thickness required by internal or external pressure calculation and the surplus thickness delta of the cylinder equipment after deducting the additional amount of the thickness1Nominal thickness of the backing plate, D0Is the outer diameter of the cylinder equipment, D01The outside diameter of the backing plate, a, B, T, delta01、C、h、δ0、δ1、D0And D01The units are all mm;
the calculation formula of the maximum compressive stress required to be borne by the rib plate is as follows:
σc,max＝FR/L1δ4+6eFR/L1 2δ4, (4)
wherein L is1＝(Dob-D01)sinβ/2，e＝(b-(Dob-D01)/4)sinβ，
β＝atan(hg/((Dob-D01)/2-B))， (5)
FRThe maximum compressive stress of the rib material is expressed in the unit of N, delta4The thickness of the web excluding the wall thickness, DobIs the outer diameter of the support, D01Is the outer diameter, σ, of the backing platecThe unit of the maximum compressive stress required to be borne by the rib plate is MPa; b is a reaction force FbThe distance from the outer wall of the shell, namely the distance from the intersection point of the neutral axis of the support and the lower surface of the lower ring plate to the outer wall of the cylinder equipment, hgIs the rib height, B is the width of the rigid ring, delta4、Dob、D01、b、hgAnd the units of B are both mm;
the calculation formula of the stress required to be borne by the upper ring plate and the lower ring plate is as follows:and sigma1≤[σ]And at the same time satisfyAnd sigma2≤[σ]WhereinTr1＝0.5F·ctgθ，A＝B×T+δ01×Lsi+δ0×Ls，Rs＝0.5×Ds，Ds＝D0+2×(δ1+ B-a), θ ═ pi/n, I is formula (3), a is the distance from the outer edge of the rigid ring to the axis of inertia, B is the width of the rigid ring, T is the effective thickness of the rigid ring, δ01The thickness of the base plate after deducting the additional amount of wall thickness, LsiIs represented by the formula (31), LsIs the formula (32), δ0For deducting the thickness required by internal or external pressure calculation and the excess thickness of the cylinder after deducting the additional amount of the thickness, FbeIs the formula (2), b is the reaction force FbThe distance from the outer wall of the shell, namely the distance from the intersection point of the neutral axis of the support and the lower surface of the lower ring plate to the outer wall of the cylinder equipment, h is the height of the support, and D is the distance from the lower surface of the lower ring plate to the outer wall of the cylinder equipment0Is the outer diameter of the shell of the cylindrical equipment, delta1Is the nominal thickness of the backing plate, n is the number of supports, a, B, T, delta01、h、δ0、δ1、D0And b are both in mm.
4. The detachable movable ring-shaped ear seat according to claim 1, characterized in that said connecting part comprises a connecting plate and a bolt, both ends of said ring-shaped ear seat body are provided with connecting plates, and the connecting plates on the two ring-shaped ear seat bodies are connected by the bolt;
the calculation formula of the maximum compressive stress required to be borne by the connecting plate is as follows: sigmac,max＝FR/L1δ4+6eFR/L1 2δ4Wherein σ iscIs formula (4);
the calculation formula of the actual shearing stress of the bolt required by the bolt is as follows: τ a ═ Fbe/(nA*A1) And τ A<[τA]，
Wherein, FbeIs disclosedFormula (2), nATo connect the number of bolts, A1Is the bolt area in mm2，[τA]The allowable shearing stress of the bolt is in MPa, and the tau A is the actual shearing stress required by the bolt and is in MPa.
5. Removable mobile annular ear cup according to claim 2 or 3, characterized in that said removable mobile annular ear cup is a removable annular ear cup
Wherein L issiIs represented by the formula (31), LsIs equation (32), B is the width of the rigid ring, T is the effective thickness of the rigid ring, δ01The thickness, delta, of the shim plate after deducting the additional amount of wall thickness0For deducting the thickness required by internal or external pressure calculation and the surplus thickness of the cylinder equipment after deducting the additional amount of the thickness, B, T, delta01And delta0The units of (A) are all mm.
6. The removable mobile annular ear mount according to claim 2, characterized in that said removable mobile annular ear mount comprises a base and a cover
Fh＝max(Fw，Pe+0.25Fw) Said Fh'＝Fw'，
Wherein, Fw＝1.2×f×qo×H×De×10-6，Fw'＝0.3Fw，
When Z is less than or equal to 5m, f is 0.794Z 0.24When Z is less than or equal to 10m, f is 0.479Z 0.32When Z is less than or equal to 15m, f is 0.2244Z 0.44，
When Z is less than or equal to 30m, f is 0.0798Z 0.60Z is the height of the center of mass of the cylinder equipment from the ground and has the unit of m and qoIs the basic wind pressure with the unit of Pa, the height of the equipment with the unit of mm, and the DeIs the effective equivalent diameter of the cylinder, and the unit is mm, FhThe horizontal force acting on the cylindrical device when the device is in use is given in units of N.
7. Removable mobile annular ear cup according to claim 3, characterized in that FR＝Fbe/(ksin β), wherein β is formula (5), FbeIs formula (2), k is the number of webs per carrier, FRIs the maximum compressive stress of the web material in units of N.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811135673.2A CN109253351A (en) | 2018-09-28 | 2018-09-28 | A kind of dismountable moving annular ear mount |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811135673.2A CN109253351A (en) | 2018-09-28 | 2018-09-28 | A kind of dismountable moving annular ear mount |
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| CN109253351A true CN109253351A (en) | 2019-01-22 |
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| CN201811135673.2A Pending CN109253351A (en) | 2018-09-28 | 2018-09-28 | A kind of dismountable moving annular ear mount |
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| FR2229300A7 (en) * | 1973-01-29 | 1974-12-06 | Trelleborgs Gummifabriks Ab | Bolted flanged joint for flexible pipes - has two flanged half shells with projecting teeth on interior |
| DE3702949A1 (en) * | 1987-01-31 | 1988-08-11 | Agintec Ag | Pipe coupling |
| JPH05272670A (en) * | 1992-03-26 | 1993-10-19 | Hayashi Eng Kk | Pipe coupling structure for synthetic resin pipe |
| CN2378612Y (en) * | 1999-07-07 | 2000-05-17 | 陈模 | Clip type releasable pipe flange |
| CN202670519U (en) * | 2012-07-02 | 2013-01-16 | 南京德邦金属装备工程股份有限公司 | Detachable rigid annular lug seat on zirconium equipment |
| CN202880908U (en) * | 2012-11-16 | 2013-04-17 | 苏州海涛化工钛设备有限公司 | Detachable lug |
| CN205504272U (en) * | 2016-02-23 | 2016-08-24 | 浙江伟鑫金属制品有限公司 | Flange clamp |
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2018
- 2018-09-28 CN CN201811135673.2A patent/CN109253351A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2229300A7 (en) * | 1973-01-29 | 1974-12-06 | Trelleborgs Gummifabriks Ab | Bolted flanged joint for flexible pipes - has two flanged half shells with projecting teeth on interior |
| DE3702949A1 (en) * | 1987-01-31 | 1988-08-11 | Agintec Ag | Pipe coupling |
| JPH05272670A (en) * | 1992-03-26 | 1993-10-19 | Hayashi Eng Kk | Pipe coupling structure for synthetic resin pipe |
| CN2378612Y (en) * | 1999-07-07 | 2000-05-17 | 陈模 | Clip type releasable pipe flange |
| CN202670519U (en) * | 2012-07-02 | 2013-01-16 | 南京德邦金属装备工程股份有限公司 | Detachable rigid annular lug seat on zirconium equipment |
| CN202880908U (en) * | 2012-11-16 | 2013-04-17 | 苏州海涛化工钛设备有限公司 | Detachable lug |
| CN205504272U (en) * | 2016-02-23 | 2016-08-24 | 浙江伟鑫金属制品有限公司 | Flange clamp |
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Application publication date: 20190122 |
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