CN205495526U - High pressure organic glass reation kettle - Google Patents

Abstract

The utility model provides a high pressure organic glass reation kettle, include the barrel, be in through threaded connection the end cover at both ends about the barrel, the barrel is the organic glass barrel, the end cover is including integrative circular flat cover and the flat cover head that sets up, the end cover is the stainless steel end cover, the barrel with highly all setting up to 30mm of end cover junction screw thread, the utility model provides a high pressure organic glass reation kettle, can be used to gas hydrate synthetic with decompose the experimental study, provide a visual experimental apparatus for gas hydrate's synthesis and decomposition.

Description

A kind of high pressure lucite reactor

Technical field

This utility model relates to a kind of experimental provision for gas hydrates synthesis with decomposition, is specially one High pressure lucite reactor.

Background technology

Gas hydrates are acknowledged as the important alternative energy of 21 century, are mainly distributed on ocean and tundra, Be a kind of clear energy sources, be a kind of specific form that in nature, natural gas exists, have a very wide distribution, scale is big, Energy density is high, incendivity.Owing to gas hydrates are primarily present Yu Haiyang and tundra, in exploitation and profit During natural gas hydrate resources, the cryogenic high pressure condition in seabed is well suited for hydrate and generates, and water occurs The problem of compound blocking pipeline, has a strong impact on the exploitation of hydrate, even causes serious accident.Therefore, grind The synthesis studying carefully gas hydrates has important meaning to the natural gas in development and utilization natural gas hydrate resources.

Gas hydrates synthesis and the experimentation decomposed, frequently with stainless steel cauldron, stainless steel material energy Bear ambient condition and the Temperature-pressure Conditions of lanthanum chloride hydrate, but not it is observed that the state of lanthanum chloride hydrate and decomposition Change, it is impossible to realize the visualization of experiment.

Utility model content

The purpose of this utility model embodiment is to provide a kind of high pressure lucite reactor, can realize natural gas Lanthanum chloride hydrate and the visual research of catabolic process, grasp the state change of lanthanum chloride hydrate and decomposition.

This utility model uses technical scheme as follows:

This utility model provides a kind of high pressure lucite reactor, including cylinder, is threadedly attached in institute Stating the end cap at the upper and lower two ends of cylinder, described cylinder is lucite cylinder, and described end cap includes the circle being wholely set Shape flat cover and flat head, described end cap is rustless steel end cap, described cylinder and described end cap junction screw thread Highly it is disposed as 30mm.

Further, the interior diameter of described cylinder is 60mm, height is 107mm, unthreaded portion wall in the middle part of cylinder Thickness is 7.9mm, and it is 9mm that barrel end adds threaded portion wall thickness.

Further, described end cap includes circular flat cover and the flat head being wholely set, the thickness of described circular flat cover Being taken as 12mm, described flat head thickness is 3mm.

Further, described screw thread include external screw thread and female thread, the overall diameter of described screw thread be 78mm, middle diameter For 76.7mm, interior diameter be 75.8mm, pitch be 2mm, working depth be 1.1mm, at the bottom of described external screw thread tooth Width is 1.5mm, crest width is 0.25mm, and described female thread tooth bottom width degree is 1.75mm, crest width is 0.5mm, thread turns is 15 circles, and effectively screwing the number of turns is 13 circles.

The method for designing of this utility model this high pressure lucite reactor is the most experimental demand, really Determine the design parameter of reactor, more respectively to cylinder, end cap and cylinder and end cap threaded be designed and Analytical calculation, mainly includes the design of each design parameter, structure and strength check.

The design parameter of reactor is as follows:

Design volume: 300mL；

Ratio of height to diameter: 1～2；

Design temperature :-5～50 DEG C；

Design pressure: 12MPa；

Operating pressure: 10MPa；

Operating temperature: 0～30 DEG C；

Working media: deionized water, natural gas；

Main material: 304 rustless steels, PMMA.

The method for designing of this high pressure lucite reactor specifically includes following steps:

Step 1, determines reactor cylinder internal diameter and height

According to ratio of height to diameter and volume, choose initial inside diameter D_i, according toObtain height H.

Step 2, determines thickness and the strength check of cylinder

An internal pressured cylinder thickness equations is:

In formula, [σ]^tThe allowable stress of material under design temperature；

D_iBarrel bore；

p_cCalculate pressure, take 12MPa；

φ welded joint coefficient, herein welding joint, take φ=1；

Substitution data obtain, and draw cylinder designed depth；

By cylinder calculated thickness rounding, obtain effective thickness δ_e。

The strength check of cylinder is:

Step 3, determines radial thickness and the strength check of end cap

The thickness equations of end cap is:

In formula, [σ]^tThe allowable stress of material under design temperature；

D_cOutside diameter of cylinder, D_c=D_i+2δ_e。

Other each parameters refer to same step 1, bring data into, by result rounding, draw the radial thickness of end cap. The strength check of end cap is with step 2.

Step 4, determines the bottom thickness δ of end cap_pAnd strength check

Computing formula is: ${\mathrm{\δ}}_p=D_c\sqrt{\frac{{\mathrm{Kp}}_c}{{\[\mathrm{\σ}\]}^t\mathrm{\φ}\mathrm{\η}}},$

Wherein, K flat head architectural feature coefficient, can table look-up and obtain；

D_cCylinder external diameter；

η perforate weakens coefficient,

Σd_iRadially each aperture widths summation on cross section；

Other parameters refer to same step 1, substitute into data and obtain the bottom thickness of end cap and its rounding is obtained δ_p；

The strength check of end cap is: ${\mathrm{\σ}}_{eq}=\frac{D_c^2\·{\mathrm{Kp}}_c}{{\mathrm{\δ}}_p^2\mathrm{\η}}\≤{\[\mathrm{\σ}\]}^t;$

Step 5, screw thread crushing strength is checked

Screw thread crushing strength σ_pCalculation formulas:

Internal and external threads is, ${\mathrm{\σ}}_p=\frac{F_1}{A}=\frac{F/z}{{\mathrm{\πd}}_{2}h}\≤\[{\mathrm{\σ}}_p\];$

Wherein, F is axial compression power；

Z is the effective thread number of turns；

F₁It is the averagely suffered axial force of a circle screw thread, F₁=F/z；

A is squish area, A=π d₂H=π D₂h；

H is screw thread working depth；

d₂For pitch diameter of external thread；

D₂For thread pitch diameter；

Step 6, screw thread shear strength is checked

Anti-shearing position is the root of screw thread, and wherein female thread is at Major Diam, and external screw thread is at diameter of thread. Female thread shear surface area is π DB, external screw thread shear surface area π d₁B, wherein, B, b are respectively internal and external screw thread Tooth bottom width degree.

Screw thread shear strength τ calculation formulas:

External screw thread, $\mathrm{\τ}=\frac{F_1}{A}=\frac{F/z}{{\mathrm{\πd}}_{1}b};$

Female thread, $\mathrm{\τ}=\frac{F_1}{A}=\frac{F/z}{\mathrm{\π}DB};$

Wherein, F is axial shearing force；

Z is the effective thread number of turns；

F₁It is the averagely suffered axial force of a circle screw thread, F₁=F/z；

A is the section of shear, female thread A=π DB, external screw thread A=π d₁b；

B is external screw thread Bottom of Thread width；

B is female thread Bottom of Thread width；

d₁For external screw thread path；

D is the big footpath of female thread；

Step 7, screw thread flexural strength is checked

Counter-bending dangerouse cross-section is ridge root, screw thread bending strength σ_bCalculation formulas:

Female thread, ${\mathrm{\σ}}_b=\frac{3Fh}{{\mathrm{\πDB}}^{2}z}$

External screw thread, ${\mathrm{\σ}}_b=\frac{3Fh}{{\mathrm{\πd}}_1{b}^{2}z}$

Wherein, F is axial force；

Z is the effective thread number of turns；

F₁It is the averagely suffered axial force of a circle screw thread, F₁=F/z；

Step 8, screw thread self-locking sex determination

Self-locking performance requires:

Lead angle

Equivalent friction angleEqulvalent coefficient of friction

The coefficient of sliding friction of f screw pair, dimensionless, under the conditions of intermittent oiling, desirable 0.13～0.17；

β tooth side angle, for the half of thread form angle α, β=α/2；

N helix of thread number, for ease of manufacturing, general n≤4, take n=1 here

Step 9, screw strength is checked

Cylinder does not consider pretightning force with the connection of end cap, only considers axial load, for only by the sky of axial load Heart cylinder bolt connects, and bolt institute tension stress is:

$\mathrm{\σ}=\frac{F}{{\mathrm{\πd}}_1^2/4-{\mathrm{\πd}}_0^2/4}\≤\[\mathrm{\σ}\]$

Wherein, F is axial load；

d₁For external screw thread path；

d₀For cylinder internal diameter；

Step 10, all kinds of parameter designing cylinders calculated based on step 1-9 and end cap, finally by cylinder and end cap Twisted together with arriving by screw thread, obtain high pressure lucite reactor.

Step 11, utilizes finite element software that high pressure lucite reactor is carried out parameter, strength modification.

The beneficial effects of the utility model:

This utility model provides a kind of high pressure lucite reactor, can realize gas hydrates synthesis and decompose The visual research of process, grasps the state change of lanthanum chloride hydrate and decomposition, grinds for gas hydrates experiment A kind of new method of offer is provided；It is and general high voltage reactor is stainless steel material due to reactor material, opaque, Can not realize the visualization of process, thus not it is observed that during state change.Be capable of process can It is in place of this high pressure lucite reactor is better than general high voltage reactor depending on change.It addition, the design selects organic Glass material design reactor, belongs to the design of non-standard component, can look into without standard.Additionally, utilize finite element soft Part is analyzed checking to reactor, obtains the high pressure lucite reactor that the design obtains and meets requirement of experiment, Thus demonstrate the feasibility of the design.

Accompanying drawing explanation

Fig. 1 is this utility model structural representation；

Fig. 2 is this utility model tube structure schematic diagram；

Fig. 3 is this utility model end cover structure schematic diagram；

In figure: 1, cylinder；2, upper end cover；3, bottom end cover.

Detailed description of the invention

Below in conjunction with the accompanying drawing in this utility model embodiment, to the technical scheme in this utility model embodiment It is clearly and completely described, it is clear that described embodiment is only a part of embodiment of this utility model, Rather than whole embodiments.Based on the embodiment in this utility model, those of ordinary skill in the art are not having Make the every other embodiment obtained under creative work premise, broadly fall into the scope of this utility model protection.

As shown in FIG. 1 to 3, for a kind of embodiment of the present utility model, including cylinder, it is threadedly attached in The end cap at the upper and lower two ends of described cylinder, described cylinder is lucite cylinder, and described end cap is rustless steel end cap, Cylinder volume is 300mL, and taking internal diameter is 60mm, cylinder height 107mm, unthreaded portion in the middle part of cylinder, Internal diameter 60mm, external diameter 75.8mm, wall thickness 7.9mm, highly 47mm, cylinder end adds threaded portion, interior Footpath 60mm, external diameter 78mm, wall thickness 9mm, highly 30 × 2, end socket bottom design wall thickness takes 12mm, flat Lid end socket radial thickness takes 3mm, screw thread specification M78 × 2, the biggest footpath 78mm, central diameter 76.7mm, path 75.8mm, pitch 2mm, working depth 1.1mm, external screw thread: tooth bottom width degree 1.5mm, crest width 0.25mm； Female thread tooth bottom width degree 1.75mm, crest width 0.5mm.Length of thread engagement N scope: 9.5 < N≤28mm, Take and effectively screw the number of turns 13 and enclose.Ratio of height to diameter: 1～2, design temperature-5～50 DEG C, design pressure 12MPa, work Pressure: 10MPa, operating temperature: 0～30 DEG C, working media deionized water, natural gas, main material 304 Rustless steel, PMMA.

The each parameter verification of embodiment

Hereinafter it is all 1 to verify by safety coefficient.

Cylinder strength verifies:

Internal pressure cylinder thickness equations is:

Mathematical expressions recognition: p≤0.4 [σ]^tφ, K=D_o/D_i≤1.5。

In formula, [σ]^tThe allowable stress of material, lucite under design temperature, take [σ]^t=55MPa；

D_iBarrel bore, 60mm；

p_cCalculate pressure, take design pressure 12MPa；

φ welded joint coefficient, (welding joint herein, take φ=1)；

Substitution data obtain, the calculated thickness of cylinderIt is (corresponding that design thickness takes 7.9mm The screw thread specification of cylinder end is M78 × 2: big footpath 78mm, central diameter 76.7mm, path 75.8mm).

Size in the middle part of cylinder: internal diameter D_i=60mm, outer diameter D_o=75.8mm, effective thickness takes δ_e=7.9mm, cylinder K=D is compared in body footpath_o/D_i=1.26 (genus thick cyclinders), calculate pressure p_c=12MPa.

The calculating stress of cylinder is:

Maximum allowable working pressure under design temperature is:

Substitution data obtain, σ^t=51.57MPa, p_w=12.80MPa.

Calculating stress on cylinder is 51.57MPa, less than material allowable stress 55MPa, therefore the design of cylinder thickness Meet the requirements.

Seal Head Strength is checked:

By cylinder external diameter 78mm as the internal diameter of end cap.Can calculate the radial thickness of end cap:

Calculated wall thickness $\mathrm{\&delta;}=\frac{p_c{D}_i}{2{\&lsqb;\mathrm{\&sigma;}\&rsqb;}^t\mathrm{\&phi;}-p_c}=\frac{12\&times;78}{2\&times;205-12}=2.35,$ Design wall thickness takes 3mm.

According to GB150-2011, check in flat head architectural feature coefficient and take K=0.207.

According to GB150-2011, opening in flat head Strengthening Design, finally determine the bottom thickness δ of circular flat cover_pCalculate Formula is: ${\mathrm{\&delta;}}_p=D_c\sqrt{\frac{{\mathrm{Kp}}_c}{{\&lsqb;\mathrm{\&sigma;}\&rsqb;}^t\mathrm{\&phi;}\mathrm{\&eta;}}},$

Wherein, [σ]^tThe allowable stress of material under design temperature, 304 rustless steels, take [σ]^t=205MPa；

p_cCalculate pressure, take design pressure 12MPa；

D_cFlat cover calculated diameter, negates and answers kettle barrel external diameter 78mm；

φ welded joint coefficient, (welding joint herein, take φ=1)；

η perforate weakens coefficient,

Σd_iRadially each aperture widths summation, mm on cross section.

Consider to need to leave in the actual application of upper end cover thermometer hole, air inlet, pressure inverting connect hole, perforate internal diameter Maximum is followed successively by 12mm, 8mm, 12mm, calculates perforate and weakens coefficient η=0.59.

Substitution data obtain, ${\mathrm{\&delta;}}_p=D_c\sqrt{\frac{{\mathrm{Kp}}_c}{{\&lsqb;\mathrm{\&sigma;}\&rsqb;}^t\mathrm{\&phi;}\mathrm{\&eta;}}}=78\&times;\sqrt{\frac{0.207\&times;12}{205\&times;1\&times;0.59}}=11.18mm,$ Design thickness takes 12mm.

When welding coefficient is 1, strength checking formulae:

Substitution data obtain, and end cap calculates stress σ_eq=177.88MPa, less than material allowable stress 205MPa, therefore Ending cover thickness design meets the requirements.

Cylinder threadeds strength check with end cap:

Thread parameter: big footpath 78mm, central diameter 76.7mm, path 75.8mm, pitch 2mm, working depth 1.1mm, tooth bottom width degree: external screw thread 1.5mm, female thread 1.75mm, effectively screw the number of turns and take 13 circles.

Mixer design pressure p=12MPa, end cap compression area A₀=π 30²=900 π mm², therefore axial load F=pA₀=10800 π N=33929N.

(1) the anti-extrusion calculating of screw thread pair

When screw thread is anti-extrusion, compressive plane is and axially vertical face, and for equivalent face, i.e. squish area A is equivalent to The threadingly girth π d of central diameter₂(or π D₂) and the product of screw thread working depth h, due to the central diameter of internal and external screw thread Identical, therefore A=π d₂H=π D₂h.In the design, female thread is end cap screw thread, and external screw thread is cylinder screw.

Screw thread crushing strength σ_pCalculation formulas:

External screw thread, ${\mathrm{\&sigma;}}_p=\frac{F_1}{A}=\frac{F/z}{{\mathrm{\&pi;d}}_{2}h}\&le;\&lsqb;{\mathrm{\&sigma;}}_p\&rsqb;;$

Female thread, ${\mathrm{\&sigma;}}_p=\frac{F_1}{A}=\frac{F/z}{{\mathrm{\&pi;D}}_{2}h}\&le;\&lsqb;{\mathrm{\&sigma;}}_p\&rsqb;.$

Wherein, F is axial compression power, F=33929N；

Z is the effective thread number of turns, and z=13 encloses；

F₁It is the averagely suffered axial force of a circle screw thread, F₁=F/z=2610N；

A is squish area, A=π d₂H=π D₂h；

H is screw thread working depth, h=1.1mm；

d₂For pitch diameter of external thread, d₂=76.7mm；

D₂For thread pitch diameter, D₂=76.7mm；

[σ_p] it is material extrusion stress allowable, pmma material, [σ_p]=55MPa；304 stainless steels Material, [σ_p]=205MPa.

Substitution data obtain, and internal and external screw thread crushing strength is

It is F that one circle female thread bears maximum extrusion pressure_max=π D₂h·[σ_p]=π 76.7 1.1 205=54337N；

It is F that one circle external screw thread bears maximum extrusion pressure_max=π d₂h·[σ_p]=π 76.7 1.1 55=14578N.

Determine that maximum extrusion pressure, the maximum extrusion pressure that i.e. one circle screw thread can bear are according to pmma material 14578N, more than actual axial force 2610N；And actual thread crushing strength is 9.85MPa, permitted less than material Use extrusion stress 55MPa.Therefore effective thread is when taking 13 circle, the anti-extrusion ability of screw thread meets the requirements.(according to meter The screw thread maximum extrusion pressure calculated, thread turns needs >=3 circles) the 13 circle maximum extrusion pressures that can bear of screw threads are 14578 × 13=189514N.

(2) screw thread shear strength is checked:

Anti-shearing position is the root of screw thread, and wherein female thread is at Major Diam, and external screw thread is at diameter of thread. The design selects regular screw threads P=2mm, now, external screw thread b=1.5mm, female thread B=1.75mm.

Screw thread shear strength τ calculation formulas:

External screw thread, $\mathrm{\&tau;}=\frac{F_1}{A}=\frac{F/z}{{\mathrm{\&pi;d}}_{1}b}\&le;\&lsqb;\mathrm{\&tau;}\&rsqb;;$

Female thread, $\mathrm{\&tau;}=\frac{F_1}{A}=\frac{F/z}{\mathrm{\&pi;}DB}\&le;\&lsqb;\mathrm{\&tau;}\&rsqb;.$

Wherein, F is axial shearing force, F=33929N；

Z is the effective thread number of turns, and z=13 encloses；

F₁It is the averagely suffered axial force of a circle screw thread, F₁=F/z=2610N；

A is the section of shear, female thread A=π DB, external screw thread A=π d₁b；

B is external screw thread Bottom of Thread width, b=1.5mm；

B is female thread Bottom of Thread width, B=1.75mm；

d₁For external screw thread path, d₁=75.8mm；

D is the big footpath of female thread, D=78mm；

[τ] is material shear stress allowable, pmma material, [τ]=55MPa；304 stainless steel materials, [τ]=0.6 [σ]=123MPa.

Substitution data obtain, cylinder shear strength

End cap shear strength $\mathrm{\&tau;}=\frac{10800\mathrm{\&pi;}/13}{\mathrm{\&pi;}\&CenterDot;78\&CenterDot;1.75}=6.09MPa.$

The maximum shear F that one circle female thread bears_max=π DB [τ]=π 78 1.75 123=52746N；

The maximum shear F that one circle external screw thread bears_max=π d₁B [τ]=π 75.8 1.5 55=19646N.

Determine that axial maximum shear, the maximum shear that i.e. one circle screw thread can bear are according to cylinder pmma material 19646N, more than actual axial force 2610N；And actual shearing intensity is less than the shear stress allowable of respective material. Therefore effective thread is when taking 13 circle, screw thread anti-shear ability meets the requirements.(according to the screw thread maximum shear calculated, Thread turns needs >=2 circles) the 13 circle maximum shear stress that can bear of screw threads are 19646 × 13=255398N.

(3) screw thread flexural strength is checked:

Counter-bending dangerouse cross-section is ridge root.Screw thread bending strength σ_bCalculation formulas:

Female thread, ${\mathrm{\&sigma;}}_b=\frac{3Fh}{{\mathrm{\&pi;DB}}^{2}z}\&le;\&lsqb;{\mathrm{\&sigma;}}_b\&rsqb;$

External screw thread, ${\mathrm{\&sigma;}}_b=\frac{3Fh}{{\mathrm{\&pi;d}}_1{b}^{2}z}\&le;\&lsqb;{\mathrm{\&sigma;}}_b\&rsqb;$

Wherein, F is axial force, F=33929N；

Z is the effective thread number of turns, and z=13 encloses；

F₁It is the averagely suffered axial force of a circle screw thread, F₁=F/z=2610N；

[σ_b] it is material permissible bending stress, pmma material, [σ_b]=90MPa；304 stainless steels Material, [σ_b]=1～1.2 [σ]=205～246MPa.

Substitution data obtain, female thread bending strength ${\mathrm{\&sigma;}}_b=\frac{3\&CenterDot;10800\mathrm{\&pi;}\&CenterDot;1.1}{\mathrm{\&pi;}\&CenterDot;78\&CenterDot;{1.75}^2\&CenterDot;13}=11.48MPa;$

External screw thread bending strength ${\mathrm{\&sigma;}}_b=\frac{3\&CenterDot;10800\mathrm{\&pi;}\&CenterDot;1.1}{\mathrm{\&pi;}\&CenterDot;75.8\&CenterDot;{1.5}^2\&CenterDot;13}=16.07MPa.$

Maximum axial force F that one circle female thread bears_max=π DB²·[σ_b]/3h=46619N；

Maximum axial force F that one circle external screw thread bears_max=π d₁b²·[σ_b]/3h=14613N.

Determine that maximum axial force, the maximum axial force that i.e. one circle screw thread can bear are according to cylinder pmma material 14613N, more than actual axial force 2610N；And actual flexion intensity is less than the permissible bending stress of respective material. Therefore effective thread is when taking 13 circle, screw thread bending resistance meets the requirements.(according to the screw thread maximum axial force calculated, Thread turns needs >=3 circles) the 13 circle maximum axial force that can bear of screw threads are 14613 × 13=189969N.

(4) screw thread self-locking service check:

In order to prevent nut from automatically unclamping under responsive to axial force, it must is fulfilled for self-locking for the fastening screw thread connected Condition, the condition of self-locking of non-rectangle screw thread

Wherein, lead angle

Equivalent friction angleEqulvalent coefficient of friction

The coefficient of sliding friction of f screw pair, dimensionless, under the conditions of intermittent oiling, desirable 0.13～0.17；

β tooth side angle, for the half of thread form angle α, β=α/2

N helix of thread number, for ease of manufacturing, general n≤4, take n=1 here.

Substitution data obtain,

Lead angle；

Equivalent friction angle

I.e.Screw thread meets self-locking requirement.

(5) screw strength is checked:

Cylinder does not consider pretightning force with the connection of end cap, only considers axial load.For only by the sky of axial load Heart cylinder bolt connects, and bolt institute tension stress is:

$\mathrm{\&sigma;}=\frac{F}{{\mathrm{\&pi;d}}_1^2/4-{\mathrm{\&pi;d}}_0^2/4}\&le;\&lsqb;\mathrm{\&sigma;}\&rsqb;$

Wherein, F is axial load, F=pA=10800 π N=33929N；

d₁For external screw thread path, take 75.8mm；

d₀For cylinder internal diameter, take 60mm.

[σ] is material permissible tensile stress, takes lucite, 55MPa；

Substitution data obtain, the tensile stress sigma=20MPa of cylinder.

Cylinder bears maximum pull $F_{max}=\&lsqb;\mathrm{\&sigma;}\&rsqb;\&CenterDot;({\mathrm{\&pi;d}}_1^2-{\mathrm{\&pi;d}}_0^2)/4=55\&CenterDot;\mathrm{\&pi;}\&CenterDot;({75.8}^2-{60}^2)/4=92685N.$

The maximum pull that cylinder can bear is 92685N, more than axial load 33929N；And actual tension is 20MPa, less than material allowable tensile stress 55MPa.Therefore bolt strength meets the requirements.

To sum up, to a circle screw thread, actual axial load 2610N is born, i.e. 2.6KN.The theoretical maximum that can bear Extruding force 14578N, maximum shear stress 19646N, maximum axial force 14613N, three takes minimum, therefore screw thread The maximum pull that can bear is 14578N, i.e. 15KN.

To 13 circle screw threads, actual bear axial load 33929N, i.e. 34KN.The theoretical maximum extruding that can bear Power 189514N, maximum shear stress 255398N, maximum axial force 189969N, three takes minimum, therefore screw thread energy The maximum pull born is 189514N, i.e. 190KN.

To screw rod (cylinder), actual bear axial load 33929N, i.e. 34KN, theoretical maximum bears pulling force 92685N, the maximum pull that i.e. screw rod (cylinder) can bear is 93KN.

The maximum of comprehensive screw thread and screw rod bears pulling force, takes minimum, i.e. meets screw thread and screw rod normally works, energy The maximum pull born is 93KN.

3, finite element software checking

The reactor using ABAQUS finite element analysis software to obtain above-mentioned design carries out intensity analysis, obtains The intensity of each structure of reactor meets requirement.Specific as follows:

The foregoing is only preferred embodiment of the present utility model, not in order to limit this utility model, all at this Within the spirit of utility model and principle, any modification, equivalent substitution and improvement etc. made, should be included in Within protection domain of the present utility model.

Claims (4)

1. a high pressure lucite reactor, it is characterised in that: include cylinder, be threadedly attached in The end cap at the upper and lower two ends of described cylinder, described cylinder is lucite cylinder, and described end cap includes being wholely set Circular flat cover and flat head, described end cap is rustless steel end cap, described cylinder and described end cap junction The height of screw thread is disposed as 30mm.

A kind of high pressure lucite reactor the most according to claim 1, it is characterised in that: described The interior diameter of cylinder is 60mm, height is 107mm, and in the middle part of cylinder, unthreaded portion wall thickness is 7.9mm, It is 9mm that barrel end adds threaded portion wall thickness.

A kind of high pressure lucite reactor the most according to claim 1, it is characterised in that: described End cap includes that circular flat cover and the flat head being wholely set, the thickness of described circular flat cover are taken as 12mm, institute Stating flat head thickness is 3mm.

A kind of high pressure lucite reactor the most according to claim 1, it is characterised in that: described Screw thread include external screw thread and female thread, the overall diameter of described screw thread be 78mm, in a diameter of 76.7mm, Interior diameter is 75.8mm, pitch is 2mm, working depth is 1.1mm, and described external screw thread tooth bottom width degree is 1.5mm, crest width are 0.25mm, and described female thread tooth bottom width degree is 1.75mm, crest width is 0.5mm, thread turns is 15 circles, and effectively screwing the number of turns is 13 circles.