WO2018024174A1 - 多瓣斜平面卡箍及其管连接件 - Google Patents

多瓣斜平面卡箍及其管连接件 Download PDF

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Publication number
WO2018024174A1
WO2018024174A1 PCT/CN2017/095213 CN2017095213W WO2018024174A1 WO 2018024174 A1 WO2018024174 A1 WO 2018024174A1 CN 2017095213 W CN2017095213 W CN 2017095213W WO 2018024174 A1 WO2018024174 A1 WO 2018024174A1
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Prior art keywords
clamp
pipe
angle
trapezoidal
cone
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PCT/CN2017/095213
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English (en)
French (fr)
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杨顺立
郭霞将
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Individual
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Individual
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Priority to US16/322,490 priority Critical patent/US11506313B2/en
Priority to JP2019506360A priority patent/JP6821872B2/ja
Priority to KR1020197005924A priority patent/KR102063740B1/ko
Priority to EA201990414A priority patent/EA038839B1/ru
Priority to EP17836356.0A priority patent/EP3492793B1/en
Publication of WO2018024174A1 publication Critical patent/WO2018024174A1/zh
Anticipated expiration legal-status Critical
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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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/04—Flanged joints the flanges being connected by members tensioned in the radial plane
    • 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/04—Flanged joints the flanges being connected by members tensioned in the radial plane
    • F16L23/08—Flanged joints the flanges being connected by members tensioned in the radial plane connection by tangentially arranged pin and nut
    • 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/02—Flanged joints the flanges being connected by members tensioned axially
    • F16L23/036—Flanged joints the flanges being connected by members tensioned axially characterised by the tensioning members, e.g. specially adapted bolts or C-clamps
    • 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/02—Flanged joints the flanges being connected by members tensioned axially
    • F16L23/032—Flanged joints the flanges being connected by members tensioned axially characterised by the shape or composition of the flanges
    • 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/04—Flanged joints the flanges being connected by members tensioned in the radial plane
    • F16L23/08—Flanged joints the flanges being connected by members tensioned in the radial plane connection by tangentially arranged pin and nut
    • F16L23/10—Flanged joints the flanges being connected by members tensioned in the radial plane connection by tangentially arranged pin and nut with a pivoting or swinging pin

Definitions

  • the invention belongs to the field of machinery and relates to a clamp and a clamp pipe joint, which is suitable for pipeline connection in petroleum processing, chemical, pharmaceutical, electric power, metallurgy, boiler and other industries.
  • pipe connections are generally flanged and valves are flanged.
  • Flange can be described as messy, black, waste material, installation trouble, but there has been no good substitute.
  • Small-diameter pipes below DN50 can replace the flange with a live joint, which is easier to install than the flange.
  • the weight is only 20-30% of the flange, the cost is reduced by 30-50%, and the material and cost of the union valve is higher than that of the flange valve. It is also close to the same proportion.
  • the inventor's proposed triangular ring gasket has solved the sealing problem used in the chemical industry.
  • clamps For large diameter pipes, although the clamps can replace the flanges, the clamps are rubber seals and are only suitable for water pipe connections. They are currently only used in fire water pipes, food and pharmaceutical industries, and are rarely used in other industries.
  • the high-pressure clamps used in the petroleum industry use hard-sealed ring pads, which have high processing precision and high cost, and cannot be popularized.
  • the diameter of the inner cone is larger than the diameter of the outer cone of the high neck flange, and the same is true for other sections.
  • the two cones are not tightly combined, and the inner cone of the one-clamp and the outer cone of the high-neck flange Only one line fits in the middle of the tapered surface of the one-clamp, the two sides of the clamp are tilted up, and there are only two bonding lines for the two-clip. If there is no point b when the clamp is installed, the gasket is sealed or the nut is not moved. At this time, the one-clamp and the high-neck flange have two bonding wires, and the position is in the clamp. Outside, the middle of the clamp is bulged.
  • the existing clamp gasket can only be a soft seal, and a mandatory seal such as an asbestos board or a metal wound mat cannot be used.
  • the inner tapered surface of the clamp fits with the outer tapered surface of the nozzle cone, and there is no slight misalignment.
  • the clamp will be tilted up, and only the Self-tightening soft seal - rubber O-ring, rubber C-ring, the use of a very narrow surface.
  • the clamps are also used for the connection of high-pressure pipes.
  • the gaskets used are octagonal rings.
  • the manufacturing process is to install the clamps into the ring and then use the lathe to finish the car.
  • the price is expensive and can only be used for small calibers. pipeline.
  • GB150.3 "Pressure Vessel Part 3: Design” has pointed out that the clamp "seal ring should have self-tightening function" (p281), the seal ring can only use rubber O-ring and rubber C-ring.
  • the clamp has not been widely promoted in the industry. At present, it is only mandatory for the fire protection and the upper and lower water pipes by the management department, and the seal ring is a rubber C-ring. Most of the fluids transported by the chemical industry are flammable and explosive media, and the temperature is high. The gaskets generally do not allow the use of rubber materials, so the existing clamps cannot be applied to the chemical industry.
  • the object of the present invention is to propose a novel pipe connection clamp and its pipe connection member: a multi-lobed inclined plane clamp and a multi-lobed inclined plane clamp pipe connection, referred to as a flat hoop and a card.
  • a multi-lobed inclined plane clamp and a multi-lobed inclined plane clamp pipe connection referred to as a flat hoop and a card.
  • the technical proposal of the invention is that the multi-lobed inclined plane tube is connected with the clamp, and the clamp is divided into two groups, and the pinch flaps in the group are connected by pins, the pins are parallel to the connecting tube shaft, and the group and the group are bolted.
  • the bolts are perpendicular to the tube axis, and each of the clamps has a partial annular column shape, and the inner side is a circular arc groove.
  • the upper and lower surfaces of the groove are symmetrical inner inner tapered surfaces, and the clamps are connected into a ring to form a card chain. .
  • the number of petals N of the clamp is an even number, and N preferably does not exceed the number of bolts of the same diameter flange, such as 4 petals, 6 petals, 8 petals, 10 petals, 12 petals, 18 petals, and the like.
  • the middle portion of the inner tapered surface of each clamp protrudes into a trapezoidal plane, and the plane is parallel to the axial plane, that is, the oblique angle of the plane is equal to the taper angle of the tapered surface.
  • the present invention also proposes a pipe connector, i.e., a pipe, that mates with the above-described pipe connection clamp.
  • the conventional clamp standard refers to it as a high neck flange, which we call a nozzle.
  • One end of the nozzle is a tube head, and one end is a convex cone head.
  • the tube head is welded to the pipeline to be connected, and can also be screwed.
  • the outer cone angle of the cone is equal to the inner cone angle of the clamp, and the outer cone surface of the cone is cut by a turning tool with N concave trapezoidal inclined planes parallel to the tapered surface.
  • the total ⁇ of the trapezoidal total angle formed by the two sides of the trapezoidal oblique plane extending to the center angle of the nozzle is 20 ⁇ 180°, preferably 90-120°, and the ratio of the trapezoidal angle of the collar to the trapezoidal angle of the tube is ⁇ / ⁇ 1.1 Preferably, ⁇ / ⁇ ⁇ 2.
  • the bottom surface of the taper head is a sealing surface, and a mandatory sealing pad, such as an asbestos pad, a metal winding pad and a metal ring, is used, and the sealing surface type is a plane, a concave surface, a groove surface, a ring groove surface or a triangle ring. Inner groove surface, etc.
  • Soft seals with self-tightening function such as rubber O-rings and rubber C-rings, can also be used.
  • the above-mentioned card chain is combined with the nozzle to form a new pipe connection member: a multi-lobed inclined plane clamp pipe connection member, which is simply referred to as a snap connection.
  • a set of card chains and a pair of (two) take-ups form a set of snaps, a gasket is placed between the tapers of the two take-ups, and the connecting bolts of the two sets of clamps are tightened, and the heads of the two take-overs are respectively on the sides Pipe welding, the installation of the card is completed.
  • the card joint proposed by the present invention can be used for connection of DN15-3000 pipes, but preferably DN50-700.
  • the temperature is used from low to low temperatures.
  • the clamp material is galvanized by carbon steel, and can also be blackened, phosphatized, nickel plated, etc., or stainless steel.
  • the material of the take-up is carbon steel or stainless steel, and other materials can also be used.
  • the manufacture of clamps and nozzles is machined after forging blanks, mainly used in the chemical industry, and can also be used for civil pipe connections.
  • the card joint proposed by the invention removes the weight of the straight section of the connecting pipe, and compares with the weight of the pair of flanges, only 20 to 30% of the weight of the flange. If only the weight of the take-up after the straight pipe section is removed, the weight is only 2.5 to 6% of the pair of flanges.
  • the requirements for other sizes are not high and it is easy to manufacture.
  • the price of the low-pressure carbon steel card is only half of that of the flange, and the price advantage of the medium and high voltage is greater.
  • Stainless steel card connection the price is only 20 ⁇ 30% of the stainless steel flange.
  • the snap connection can be used for the manufacture of the valve, and the flanges on both sides of the valve are replaced by the connecting pipe, and the pipe is connected with the clamp, so that the manufacturing cost and the price of the valve are greatly reduced.
  • the popularization of the card connection of the present invention will set off a revolution in the field of industrial pipe valve parts and pipeline connection, and is of great significance to the development of modern industry and the national economy.
  • Figure 1 is a conventional clamp mounting diagram
  • B is a partial enlarged view of A.
  • Figure 2 is a three-dimensional view of the card, where A is the nose band, B is the ear band, and c is the assembly drawing.
  • Figure 3 is a three-dimensional projection of the snap-in assembly, where A is in contact, B is an ear cuff, and c is a nasal cuff.
  • Fig. 4 is a plan view of the card, wherein 1 is a nozzle, 2 is a gasket, 3 is a clamp, and 4 is a lower joint.
  • Fig. 5 is a diagram of the connection mark
  • a and B are respectively a longitudinal sectional view and a top view of the upper connection pipe
  • C is a partial enlarged view of B
  • D and E are respectively a top view and a longitudinal sectional view of the lower connection pipe.
  • Figure 6 Four-clip clamp logo.
  • a and B are respectively a longitudinal sectional view and a partial enlarged view of A
  • C and D are respectively sectional views of the AA left and right parts in the A picture
  • E and F are respectively two sectional views in the figure C
  • G and H are respectively in the figure D.
  • Figure 7 shows the six-clip clamp logo.
  • a and B are respectively a longitudinal sectional view and a partial enlarged view of A
  • C and D are respectively sectional views of the left and right parts and the upper and lower parts
  • E and F are respectively two sectional views in the drawings C and D.
  • the present invention is a novel product, and the products and components must be named prior to description, see Figures 2-7.
  • the invention divides the clamp into four or more petals, and changes the taper surface of the traditional clamp into a diagonal plane fit.
  • the scientific name should be called a multi-lobed inclined plane clamp, which is referred to as a flat hoop, and the conventional clamp is simply referred to as a cone. hoop.
  • the existing standard and literature of the clamp connector and the pipe are called high neck flange. We call it the nozzle.
  • the side connecting the pipe to the pipe is called the butt weld end, and the side connected to the clamp is called the cone. head.
  • the clamp pipe joint is composed of a clamp, a pipe, a bolt and a pin.
  • the clamp and the pipe are the main components, and the bolt and the pin are the connecting members (accessories).
  • the clamp is divided into two types, a side hoop and a middle hoop.
  • the side hoop is further divided into a nose hoop and an ear hoop.
  • the nose hoop, the ear hoop and the middle hoop are also referred to as a single hoop.
  • the number of petals in the clamp is a multiple of 2 (even) and a minimum of 4 petals.
  • FIG 2 3 is a three-dimensional and three-dimensional projection of the four-clamped pipe connection
  • A is the nose band
  • B is the ear band
  • c is the assembly picture (assembly drawing)
  • the abbreviation is called card connection.
  • One end of the side hoop (A, B) is a lug
  • the other end of the nose band (A) is a pin nose
  • the other end of the ear cuff (B) is a pin ear.
  • the four-clip clamp one nose band and one ear band are pinned together to form a set of clamps, and the two sets of clamps are bolted together to form a whole, which we call a card chain.
  • the card chain is connected to the take-up tube.
  • Figure 7 is a six-clip clamp.
  • the six-clip hoop is divided into two groups, one set of three-lobed, two-nose nose hoop, ear cuff, middle middle hoop, middle hoop one pin nose, one pin ear, middle hoop Connected to the side band by pin.
  • the card chain consisting of more than six petals is composed of three kinds of single hoops: nose cuff, ear cuff and middle hoop. It only needs to open three kinds of molds.
  • a set of chain and a pair of (two) take-ups form a set of pipe joints, the cone bottoms of the two joints are sealing faces, and the sealing faces and gaskets can be of various types, and the heads of the two pipes are respectively Pipe welding on both sides can also be screwed.
  • the card chain material is made of carbon steel, stainless steel and other metals. It is made of forged blank and machined. It is resistant to high temperature and high pressure and can be used for flammable and explosive media.
  • the clamp tube connector can be used for the connection of the valve manufacturing, that is, the flange on the conventional flange-connected valve is changed into the connector, and the valve and the pipe are connected by the above-mentioned card chain.
  • the clamp pipe connecting piece adopts a forced type sealing gasket, and the size is designed according to chemical and petrochemical design standards, and is used for connecting medium and high pressure, flammable and explosive medium pipelines and equipment.
  • the clamp can also be manufactured by casting, the pipe head of the pipe is welded or screwed to the pipe, and the gasket is a forced seal or a soft seal for civil, low pressure and non-combustible media.
  • the connection of the pipe can also be manufactured by casting, the pipe head of the pipe is welded or screwed to the pipe, and the gasket is a forced seal or a soft seal for civil, low pressure and non-combustible media.
  • the clamp pipe connecting member (snap) has a diameter of DN 15 to 3000, preferably DN 50 to 700.
  • Card connection is a new product, mainly used in chemical, petroleum, power generation, smelting and other industrial fields. To replace large diameter flanges above DN50, it must be designed according to the national standard for pressure vessels and the national standard for industrial metal pipes. Before deriving the design formula, you need to name and select the symbols for each part, see the attached figure.
  • ⁇ g the separation between the inclined plane of the taper head and the inclined plane of the clamp after the assembly of the joint
  • h n the thickness at the tangent point of the taper, that is, the thickness at the inscribed point of the take-up cone;
  • h w the height of the cylindrical section of the cone, that is, the thickness of the nozzle cone at the outer point;
  • N the number of petals of the clamp
  • r 2 the radius of the excessive arc in the machining, that is, the inner chamfering, taking 1 ⁇ 2mm;
  • r 3 the outer arc radius outside the machining, that is, the outer chamfer, take 0.5 ⁇ 1mm;
  • the angle between the plane and the oblique plane of the clamp and the axial section, the four angles are equal;
  • ⁇ takes the sum of the N trapezoidal angles of the cone head
  • ⁇ n takes the trapezoidal angle, based on the inscribed circle D n ;
  • ⁇ the sum of the trapezoidal angles of the N single-clamp clamps of the card chain
  • ⁇ C the length of the bow length, the length of the inclined plane bow of the clamp on the same circumference after installation is longer than the length of the oblique plane bow of the take-up cone, which means the same length on both sides;
  • ⁇ L the distance between the card joints, the edge of the card chain hole and the bottom line of the trapezoidal oblique plane of the nozzle cone;
  • ⁇ b1 tensile strength of the take-over material, MPa
  • ⁇ ——bow length ratio the ratio of the inclined plane of the clamp on the same circumference to the length of the bow of the inclined plane of the nozzle cone after installation.
  • the two sides of the oblique plane are straight lines, but are approximately straight lines.
  • the contact surface of the snap-fit connector (clamp-overtube inclined plane) is much larger than the flange contact surface (flange-bolt), and the warpage of the flange does not occur, and it is not necessary to
  • the inclined height of the bow of the cone is formed on the circumscribed circle Dw by the bow height v D
  • the oblique plane of the collar forms an arcuate bow height v E on the inscribed circle D n .
  • the distance ⁇ g between the inclined plane of the taper head and the oblique plane of the clamp is
  • the design requirement ⁇ g should be as large as possible, not less than 0.7 mm, ie the two cones should have as large a spacing as possible.
  • g D is equal everywhere, so v D is also equal everywhere, and the projection curve of the side of the trapezoidal oblique plane can be made according to the drawing, which is very close to the straight line. .
  • the bow length of the taper head is formed on the circumscribed circle D w (the cone bottom circle) to form an arcuate bow length C Dw
  • the bow length of the tapered head is formed on the inscribed circle, and the bow length c Dn is
  • the oblique plane of the collar forms an arcuate bow length c En on the inscribed circle.
  • the trapezoidal angle ⁇ w of the clamp on the circumscribed circle is
  • the oblique plane of the collar forms an arcuate bow length c Ew on the circumscribed circle
  • Bow length ratio ⁇ and bow length margin ⁇ C reflect the reliability of the angle between the inclined plane of the clamp and the inclined plane of the nozzle cone.
  • the design requirements are ⁇ 2, ⁇ C ⁇ 10mm.
  • the bow length ratio of the clamp and the take-up is very close to the ratio of the ⁇ to the trapezoidal angle, that is, ⁇ ⁇ ⁇ / ⁇ ⁇ 2.
  • the diameter of the circle at the shear point on the center line of the oblique plane of the taper head is D n
  • the diameter of the clamp hole is also D n .
  • the following design calculation formula mainly refers to the national standard GB 150-2011 "pressure vessel” standard interpretation, national standard GB 150.1 ⁇ 4-2.11 "pressure vessel”, national standard GB 50316-2000 “industrial metal pipeline design specification”, national chemical industry standard HG /T 20582-2.11 "Steel Chemical Container Strength Calculation Regulations”.
  • the pressure stress on the sealing surface should be 2m times the design pressure p in the operating state.
  • the axial tensile force F t in the operating state should be the sum of the axial force F G caused by the medium pressure and the axial force F p caused by the sealing compression stress required for the operating state of the gasket, which can be expressed as
  • the total tensile force on both sides of the clamp is radial pressure
  • the tensile force (total bolt load) of the two bolts on the opposite side of the clamp can be calculated, and the value is also equal to the total load of the two pairs of pins on the opposite side of the clamp.
  • a preload condition is also specified for the clamp strength calculation.
  • the two sealing faces are close to each other, and the outer tapered surface of the high neck flange moves outward with respect to the inner cone of the clamp, and an inward frictional force F is generated on the tapered surface of the clamp.
  • the sealing faces of the two sealing faces have a tendency to move, and the outer tapered surface of the high neck flange moves relative to the inner tapered surface of the clamp, and the frictional direction of the contact surface of the clamp and the high neck flange is opposite to the direction of the preloaded state, in the clamp An outward frictional force F is generated on the tapered surface.
  • the existing formulas for calculating the size of the clamps are very complicated, such as up to 37 calculation formulas in GB 150.3.
  • the thickness at the tangent point of the nozzle only the 1/4 of the circumference of the tangent point is calculated, and the remaining 3/4 circumferences can be strengthened. effect. Therefore, for the calculation of the size of the clamp and the joint, only the wall thickness ⁇ of the nozzle, the effective thickness h n at the tangent point of the nozzle, and the thickness f w at the point of the clamp are calculated. It is not necessary to consider the nozzle cone and the clamp. The bending deformation of the tapered surface greatly simplifies the design calculation process.
  • the calculation result of the above formula is the same as the calculation result of the calculation formula in GB 50316.
  • the gap angle between the lug and the pin of the card chain bolt is 60°, that is, the total circumference of the arc of the N clamps is 300/360 of the circumference of the chain, which is obtained by force balance.
  • the total empty angle of the chain should be less than 60°.
  • Each pin has four shear faces, balanced by force
  • the height of the pin ear is u 1
  • the height of the pin nose is u 2
  • u 2 2u 1
  • u 2 + 2u 1 0.8F
  • u 1 0.2F.
  • GB 150 states that “the safety factor currently used in pressure vessel safety regulations and technical standards is extensive. Since many details are guaranteed by the safety factor, this makes it impossible to accurately assess the safety margin of the device or equipment. problem".
  • the safety factor adopts the lower of the national standards - the British standard, and the DN ⁇ 15, PN ⁇ 100 pipe fitting factor 2 (the most prone to operational error overpressure), DN20 ⁇ 25, PN ⁇ 40 pipe fitting coefficient 1.5, DN32 ⁇ 50, PN ⁇ 40 pipe fitting coefficient 1.2.
  • the mechanical properties of the materials used in the examples of the present invention are taken from GB 150.2-2011 and GB/T 1220-2000, see Table 5-2.
  • the force of the upper bolt only needs to be increased a little, but it must be evenly distributed, that is, when the bolt is bolted, it should be slowly turned on the opposite side, which is higher than the requirements of the asbestos pad. .
  • the upper chain is very simple, as long as the bolts are used, this is one of the advantages of the card.
  • the dimensions of the DN50-600 card connection are calculated, the pressures are PN25, 40, 63, the sealing surface is the groove surface, the gasket is stainless steel-graphar spiral wound gasket, the gasket thickness is 3.2, and the design is taken over.
  • Tables 6-1, 2, and 3 are typical embodiments. It can be seen from the data in the table that the bow length is 13 to 37 mm, the card spacing is 4.7 to 6.3 mm, and the processing precision is not high, and it is easy to manufacture.
  • the size of the clamp is significantly smaller than the flange. Large-diameter snaps do not require very thick bolts like flanges, and the price will be much lower than the flange.
  • the card weight When comparing the weight of the snap and flange, the flange should be a pair (two pieces) of weight.
  • the weight of the card should be the weight of a set of clamps plus the weight of a pair of nozzle cones.
  • the inner diameter When calculating the weight of the cone, the inner diameter should be taken from the outer diameter of the pipe, that is, the pipe is also removed when the flange is installed. Cone weight.
  • the weight of the bolted bolt is lighter than the bolt of the flange. Because the bolt value is low, the weight of the two bolts is not counted.
  • the weight of the flange is taken from GB/T 9124-2010, plate type flat welding flange. The calculation results are listed in the table.
  • the weight of the card is only 10 to 30% of the flange.
  • the weight of the effective taper of the card joint pipe is only 2.5 to 6% of the weight of the flange.
  • the clamp can be made of carbon steel (galvanized, nickel plated), stainless steel clamped. The price advantage for stainless steel flanges is even greater.
  • Nominal diameter DN 50 65 80 100 125 150 200 250 300 350 400 500 600 Clamping number N 4 4 4 6 6 8 8 8 12 12 16 16 Takeover material 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# Clamp material 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 30CrMo 30CrMo Tube wall thickness ⁇ D 3.5 3.5 3.5 3.5 4 6 8 8 10 10 14 14 Theoretical value 1.4 1.9 2.2 2.7 3.3 4.0 5.4 6.8 6.6 7.6 8.6 10.7 12.7 Takeover height H 50 50 50 50 50 50 50 50 50 50 50 50 50 50 50 50 50 50 50 50 Shear thickness h w1 4 4 4 4 4 4 4 4 4 4 4 4 h w2 6 6 6 6 6 6 6 6 6 6 6 6 6 6 h n1 5.9 5.9 6.1 6.3 6.5 7.0 8.3 8.5 8.0 8.7 8.7 9.1 9.1 h

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Flanged Joints, Insulating Joints, And Other Joints (AREA)
  • Gasket Seals (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Joints With Sleeves (AREA)

Abstract

一种多瓣斜平面的管连接卡箍和管连接件，卡箍分为2组，组内各瓣卡箍之间用销连接，销平行于连接管轴，组与组之间用螺栓连接，螺栓垂直于管轴，每个卡箍的外形均为部分圆环柱，里面为圆弧凹槽，凹槽的上下面为对称的部分内锥面，各卡箍连接成环后形成卡链。

Description

多瓣斜平面卡箍及其管连接件 技术领域
本发明属于机械领域，涉及一种卡箍和卡箍管连接件，适用于石油加工、化工、制药、电力、冶金、锅炉等行业的管路连接。
背景技术
工业上，管道连接一般都采用法兰，阀门也是法兰式阀门。法兰可谓是傻大黑粗，浪费材料，安装麻烦，但一直没有好的替代品。DN50以下小口径管道，可以用活接替代法兰，比法兰安装方便，重量只是法兰的20～30％，成本降低30～50％，活接式阀门比法兰式阀门的材料和成本也降低接近同样的比例，虽然现在只在民用管连接行业使用，在化工行业普及也是早晚的事，本发明者提出的三角环密封垫已经解决了活接在化工行业使用的密封问题，见CN 203756982 U，CN 204717181 U。对于大口径管道，虽然卡箍可以替代法兰，但卡箍为橡胶密封，只适用于水管道的连接，目前仅用于消防水管道、食品和制药行业，其他行业很少使用。石油工业用的高压卡箍，采用硬密封环垫，加工精度要求高，造价高，也不能普及。
现有卡箍主要用于水管的连接，由卡箍、高颈法兰、螺栓和密封垫组成，见图1。卡箍一般为2瓣，最多3瓣(可参见国标)，安装后卡箍的内锥面和高颈法兰的外锥面完全贴合，图中b为切点。假定密封垫片为石棉垫，使用一段时间后发现有泄漏现象，需要上紧，上紧螺栓后卡箍向内收缩，切点由b移至c点，此时在轴向截面D-D上卡箍内锥圆直径大于高颈法兰外锥圆直径，在其他截面上也是如此，这时两个锥面已经不是紧密结合了，一瓣卡箍的内锥面与高颈法兰的外锥面只有一条线贴合，位置在一瓣卡箍内锥面的中部，卡箍两边翘起来了，对两瓣卡箍只有两条贴合线。如果在安装卡箍时没有上到b点，垫片就已经密封好或上不动螺母了，这时一瓣卡箍和高颈法兰锥面有两条贴合线，位置在卡箍的外边，卡箍中间鼓起来了，由于相邻两瓣卡箍的凸耳距离很近，两条贴合线的作用和一条相当。由此可以看出，现有的卡箍密封垫只能是软密封，不能采用石棉板、金属缠绕垫等强制性密封垫。
总之现有的卡箍安装后都是卡箍的内锥面与接管锥头的外锥面贴合，不能有丝毫的错位，上到位后螺栓紧一点卡箍就会翘起来，只能用有自紧作用的软密封——橡胶O型环、橡胶C型环，使用面非常窄。
石油工业中也有将卡箍用于高压管道连接的，采用的密封垫为八角环，制造过程是将卡箍加垫片安装成环后用车床精车，价格昂贵，而且只能用于小口径管道。实际上，GB150.3《压力容器第3部分：设计》中已经指出，卡箍“密封环应具有自紧功能”(p281)，密封环只能采用橡胶O型环和橡胶C型环。
因此，卡箍在工业上一直未能普遍推广，目前仅在消防及上下水管上由管理部门强制普及，密封环为橡胶C型环。化工行业管道输送的流体大部分都是易燃易爆介质，而且温度高，垫片一般都不允许使用橡胶材料，故现有卡箍无法应用到化工行业。
发明内容
在传统卡箍的基础上，本发明目的是，提出了一种新型管连接卡箍及其管连接件：多瓣斜平面卡箍和多瓣斜平面卡箍管连接件，简称平箍和卡接。卡箍与接管锥头的结合面为斜平面，可以采用石棉垫、金属缠绕垫及金属环等各种密封垫，可以替代DN50以上口径的法兰，用于低压、中高压和易燃易爆介质管道的连接。
本发明的技术方案是，多瓣斜平面管连接卡箍，卡箍分为2组，组内各卡箍瓣之间用销连接，销平行于连接管轴，组与组之间用螺栓连接，螺栓垂直于管轴，每个卡箍的外形均为部分圆环柱，里面为圆弧凹槽，凹槽的上下面为对称的部分内锥面，各卡箍连接成环后形成卡链。
所述的卡箍，卡箍内锥面的锥角，即内锥面法向与卡链轴向的夹角α＝5～80°，最好为10～20°。所述卡箍的瓣数N为偶数，N最好不超过同口径法兰的螺栓数，如4瓣、6瓣、8瓣、10瓣、12瓣、18瓣等。
所述的卡箍，每个卡箍内锥面的中间部分凸出变为梯形平面，平面与轴面平行，即平面的斜角与锥面的锥角相等。
所述的卡箍，单个卡箍梯形斜平面两侧边延至卡链圆心所形成的梯形角γ的总合Γ＝40～330°，最好为180～300°，单个卡箍的梯形角γ＝Γ/N。
本发明还提出了一种与上述管连接卡箍匹配的管连接件即接管，传统卡箍标准将其称为高颈法兰，我们称为接管。接管的一端为管头，一端为凸出的锥头，管头与待接管道焊接，也可以用螺纹连接。锥头的外锥角与卡箍的内锥角相等，锥头的外锥面用车刀削出N个与锥面平行的凹进的梯形斜平面。接管梯形斜平面两侧边延至接管圆心角所形成的梯形总角的总合Β＝20～180°，最好为90～120°，卡箍梯形角与接管梯形角的比值γ/β≥1.1，最好为γ/β≥2。
所述的接管，接管锥头底面为密封面，采用强制性密封垫，如石棉垫、金属缠绕垫及金属环等，密封面型式为平面、凹凸面、榫槽面、环槽面或三角环内槽面等。也可以采用有自紧功能的软密封垫，如橡胶O型环、橡胶C型环。
上述卡链与接管结合，形成了一种新的管路连接件：多瓣斜平面卡箍管连接件，简称为卡接。一套卡链和一对(两个)接管组成一套卡接，两个接管的锥头之间放置密封垫，上紧两组卡箍的连接螺栓，两个接管的管头分别与两边的管道焊接，就完成了卡接的安装。
有益效果：本发明所提出的卡接，可以用于DN15～3000管道的连接，但最好是DN50～700。使用压力，从低压到高压。使用温度，从零下低温到高温。卡箍材料为碳钢镀锌，也可以发黑、磷化、镀镍等，也可以采用不锈钢材料。接管材料为碳钢或不锈钢，也可以采用其他材料。卡箍和接管的制造，都采用锻造毛坯后机加工，主要用于化工行业，用于民用管道连接也可以铸造。
本发明所提出的卡接，剔除接管直段的重量，与一对法兰的重量比较，只是法兰重量的20～30％。如果仅算剔除直管段后的接管重量，重量只是一对法兰的2.5～6％。卡接的制造，除对锥角有严格要求外，对其他尺寸要求多不高，很容易制造。卡接市场化后，低压碳钢卡接接价格只是法兰的一半，中高压价格优势更大。不锈钢卡接，价格只是不锈钢法兰的20～30％。卡接可以用于阀门的制造，将阀门两边的法兰换成接管，与管道用卡箍连接，使阀门的制造成本和价格大幅下降。本发明卡接的普及，将会掀起工业管阀件行业和管道连接领域的一场革命，对现代工业的发展和国民经济意义重大。
附图说明
图1中A传统卡箍安装图,B为A的局部放大图。
图2卡接三维图，其中A为鼻边箍，B为耳边箍，c为组装图。
图3卡接组件三维投影图，其中A接管，B为耳边箍，c为鼻边箍。
图4卡接刨面图，其中1为接管，2为密封垫，3为卡箍，4为下接管。
图5接管标识图，A、B为分别为上接管纵剖视图及俯视图，C为B中一局部放大图，D、E分别为下接管俯视及纵剖视图。
图6四瓣卡箍标识图。A、B分别为纵剖视图及A中局部放大图俯视图，C、D分别A图中A-A左右件的剖视图，E、F分别为图C中的两处剖视图，G、H分别为为图D中的两处剖视图。
图7六瓣卡箍标识图。其中A、B分别为纵剖视图及A中局部放大图俯视图，C、D分别A图中左右件和上下件的剖视图，E、F分别为图C、D中的两处剖视图。
具体实施方式
1.命名
本发明为新型产品，在描述之前先须对产品及部件进行命名，参见图2～7。
本发明将卡箍分成四瓣以上，将传统卡箍的锥面贴合改成斜平面贴合，学名应称为多瓣斜平面卡箍，我们简称为平箍，传统卡箍我们简称为锥箍。卡箍连接件与管道焊接的部分，现有的标准和文献都称为高颈法兰，我们称为接管，接管与管道连接的一边称为对焊端，与卡箍连接的一边称为锥头。
卡箍管连接件由卡箍、接管、螺栓和销四种零件组成，卡箍和接管是主件，螺栓和销是连接件(附件)。卡箍分为两种，边箍和中箍，边箍又分为鼻边箍和耳边箍，鼻边箍、耳边箍和中箍又都称为单箍。卡箍的瓣数为2的倍数(偶数)，最少为4瓣。图2、3为四瓣箍的管路连接件三维图和三维投影图，A为鼻边箍，B为耳边箍，c为总成图(组装图)，我们将卡箍管连接件总成简称为卡接。边箍(A、B)的一头为凸耳，鼻边箍(A)的另一头为销鼻，耳边箍(B)的另一头为销耳。对四瓣构成的卡箍，一个鼻边箍和一个耳边箍用销连接在一起，成为一组卡箍，两组卡箍用螺栓连接在一起，成为一个整体，我们称之为卡链，卡链与接管组成卡接。
图7为六瓣卡箍，六瓣箍分为两组，一组三瓣，两头为鼻边箍、耳边箍，中间为中箍，中箍一头为销鼻、一头为销耳，中箍通过销与边箍连接。六瓣以上卡箍组成的卡链，都是由鼻瓣箍、耳边箍和中箍这三种单箍组成，制造只需开三种模具。
一套卡链和一对(两个)接管组成一套管路连接件，两个接管的锥底为密封面，密封面和密封垫片可以采用各种型式，两个接管的管头分别与两边的管道焊接，也可以用螺纹连接。
卡链材料为碳钢、不锈钢等金属，采用锻造毛坯、机加工的方法制造，耐高温高压，可用于易燃易爆介质。
所述的卡箍管连接件可用于阀门制造的连接，即将传统法兰连接式阀门上的法兰改成所述的接管，阀门与管道用所述的卡链连接。
所述的卡箍管连接件，采用强制型密封垫，尺寸按化工和石油化工设计标准设计，用于中高压、易燃易爆介质管路和设备的连接。
所述的卡箍管连接件中，卡箍也可以采用铸造的方法制造，接管的管头与管道焊接或螺纹连接，垫片采用强制密封垫或软密封垫，用于民用、低压和不燃介质管道的连接。
所述的卡箍管连接件(卡接)，接管的口径为DN15～3000，最好为DN50～700。
2.定义
卡接是一种新产品，主要用于化工、石油、发电、冶炼等工业领域，替代DN50以上大口径法兰，必须按照压力容器国标和工业金属管道国标的规范进行设计。在推导设计公式之前，先需对各部位进行命名和选择标识符号，参见附图。
b——密封垫片的有效宽度；
C1——接管对焊端管壁厚负偏差，C1＝12.5％；
CDn——接管锥头斜平面在内切圆Dn上形成弓形的弓长，计算时圆直径应取Dn+2vD；
CDw——接管锥头斜平面在外切圆Dw上形成弓形的弓长；
CEn——卡箍斜平面在内切圆Dn上形成弓形的弓长，计算时圆直径应取Dn+2vE；
CEw——卡箍斜平面在外切圆Dw上形成弓形的弓长；
Di——接管对焊端内径；
Do——接管对焊端外径；
D1——接管—锥面过度弧与锥面相交形成圆的直径，D1＝Do+2r1(1—sinα)；
Dn——内剪切圆直径，即接管锥头切点处直径，也等于卡链的孔径；
Dw——外剪切圆直径，即接管锥头的底径；
DG——密封面的有效直径；
d1——螺柱的最小截面直径；
d2——螺栓孔直径；
d3——销的直径；
d4——销孔直径；
d5——销耳外径；
Ei——卡箍内径；
Eo——卡箍外径；
fn——卡箍孔处直段高度，即内切点处卡箍的厚度；
fw——卡箍切点处的厚度，即外切点处卡箍的厚度；
gD——接管锥头锥面和斜平面的间距；
gE——卡箍锥面与斜平面的间离；
Δg——卡接组装后接管锥头斜平面和卡箍斜平面的间离；
hn——接管锥头切点处的厚度，即接管锥头在内切点处的厚度；
hw——接管锥头圆柱段的高度，即接管锥头在外切点处的厚度；
La——凸耳的力臂长度；
Lw——凸耳的宽度；
Ln——凸耳的厚度；
m——垫片系数，无因次；
N——卡箍的瓣数；
nb——材料抗拉强度的安全系数；
ns——材料屈服强度的安全系数；
PN——公称压力，设计的最大使用压力，bar；
p——内压，MPa，p＝(PN+1)/10；
r1——接管—锥面过度圆弧的半径；
r2——加工内过度弧半径，即内倒角，取1～2mm；
r3——加工外过度弧半径，即外倒角，取0.5～1mm；
u1——销耳高度；
u2——销鼻高度；
vD——接管锥头斜平面在外切圆上形成弓形的弓高；
vE——卡箍斜平面在内切圆上形成弓形的弓高；
y——垫片的密封比压，MPa；
α——锥角或斜角，锥面的与锥底的夹角，即锥面法向与锥轴向的夹角，包括接管头外锥面和卡箍内锥面的锥角，接管斜平面和卡箍斜平面与轴向截面的夹角，四个角相等；
Β——接管锥头N个梯形角的总和；
βw——接管梯形角，接管锥头梯形斜平面两侧边延至接管圆心所形成的梯形角，以外切圆Dw为基准，β＝Β/N；
βn——接管梯形角，以内切圆Dn为基准；
Γ——卡链N个单卡箍卡箍梯形角的总和；
γn——卡箍的梯形角，单个卡箍梯形斜平面两侧边延至卡链圆心所形成的梯形角，以内切圆Dn为基准，γ＝Γ/N；
γw——卡箍的梯形角，以外切圆Dw为基准；
δD——接管对焊端壁厚；
δE——卡箍圆筒段壁厚；
ΔC——弓长余量，安装后在同一圆周上卡箍斜平面弓长比接管锥头斜平面弓长多出的长度，指两边多出的同样长度；
ΔL——卡接间距，卡链孔边与接管锥头梯形斜平面上底线的距离；
μ——摩擦角，钢-钢的μ＝５～８°，小值μ1＝5°，大值μ2＝8°；
σb1——接管材料的抗拉强度，MPa；
σb2——卡箍材料的抗拉强度，MPa；
σs3——螺栓和销材料的屈服强度，MPa；
[σ]b1——接管材料的许用应力，MPa；
[σ]b2——卡箍材料的许用应力，MPa；
[σ]s3——螺栓和销(轴)材料的许用应力，MPa；
Figure PCTCN2017095213-appb-000001
——焊接系数，接管对焊端设计有坡口，电焊，可以取
Figure PCTCN2017095213-appb-000002
ω——弓长比，安装后在同一圆周上卡箍斜平面与接管锥头斜平面的弓长之比。
3.配合尺寸
(1)梯形角
梯形斜平面两侧边延至圆心所形成的梯形角的简称，实际上斜平面的两个侧边并是直线，只是近似为直线。我们规定接管斜平面面积为接管外锥总面积的1/4，即接管梯形角的总和Β＝90°，以接管锥头圆柱段直径Dw为基准，接管锥头上单个斜平面的夹角为
Figure PCTCN2017095213-appb-000003
这样的设计，卡接的连接件接触面(卡箍—接管斜平面)比法兰的连接件接触面(法兰—螺栓)要大的多，不会出现法兰的翘曲现象，不必对垫片名义宽度b0进行矫正，即b＝b0。
卡箍梯形角的总和为Γ，经设计方案比较，宜取Γ＝180～300°，以卡箍孔直径Dn为基准，每个卡箍的斜平面夹角为
Figure PCTCN2017095213-appb-000004
考虑到公差、加工误差和安装时的错位，为保证卡箍斜平面和接管斜平面完全贴合，宜取γ/β≥2。
(2)斜平面与锥面的间距
如图5，接管锥头斜平面在外切圆Dw上形成弓形的弓高vD为
Figure PCTCN2017095213-appb-000005
接管锥头斜平面和锥面的间距gD为
Figure PCTCN2017095213-appb-000006
如图6，卡箍斜平面在内切圆Dn上形成弓形的弓高vE为
Figure PCTCN2017095213-appb-000007
卡箍锥面与斜平面的距离gE为
Figure PCTCN2017095213-appb-000008
卡接组装后，接管锥头斜平面和卡箍斜平面的距离Δg为
Δg＝gE-gD      (3-7)
设计要求Δg应尽可能大，不能小于0.7mm，即两个锥面应有尽可能大的间距。
因斜平面与锥面平行，gD在每一处都是相等的，故vD在每一处也都是相等的，绘图时可以据此作出梯形斜平面侧边的投影曲线，很接近直线。
(3)弓长比
如图5，接管锥头斜平面在外切圆Dw(锥底圆)上形成弓形的弓长CDw为
Figure PCTCN2017095213-appb-000009
因斜平面与锥面平行，gD在每一处都是相等的，故vD在每一处也是相等的，由此可得在内切圆Dn(卡链孔圆)上接管锥头的梯形角βn为
Figure PCTCN2017095213-appb-000010
接管锥头斜平面在内切圆上形成弓形的弓长cDn为
Figure PCTCN2017095213-appb-000011
同理可得，卡箍斜平面在内切圆上形成弓形的弓长cEn为
Figure PCTCN2017095213-appb-000012
外切圆上卡箍的梯形角γw为
Figure PCTCN2017095213-appb-000013
卡箍斜平面在外切圆上形成弓形的弓长cEw为
Figure PCTCN2017095213-appb-000014
卡箍与接管锥头在内外剪切圆上的弓长之比分别为
Figure PCTCN2017095213-appb-000015
Figure PCTCN2017095213-appb-000016
卡箍与接管锥头在内外剪切圆上的弓长余量分别为
Figure PCTCN2017095213-appb-000017
Figure PCTCN2017095213-appb-000018
弓长比ω和弓长余量ΔC反映了卡箍斜平面与接管锥头斜平面贴合的可靠程度，对于DN50及以上卡接，设计要求ω≥2，ΔC≥10mm。卡箍和接管的弓长比ω与梯形角比很接近，即ω≈γ/β≥2。
(4)卡接间距
接管锥头斜平面中心线上剪切点处圆直径为Dn，卡箍孔的直径也为Dn。接管外径—锥面过度弧r1与锥面相交形成圆的直径为D1，接管锥头梯形斜平面梯形上底边线与圆D1相交。我们将卡链孔边(Dn圆)与接管锥头梯形斜平面梯形上底边线(D1圆处)的距离称为卡接间距ΔL，由图5可得
Figure PCTCN2017095213-appb-000019
设计取ΔL＝4～6mm，对大口径卡接，应取较大的ΔL。
4.应力分析
下面的设计计算公式，主要参照国标GB 150-2011《压力容器》标准释义，国标GB 150.1～4-2.11《压力容器》，国标GB 50316-2000《工业金属管道设计规范》，国家化工行业标准HG/T 20582-2.11《钢制化工容器强度计算规定》。
4.1轴向载荷
(1)内压作用在接管轴向截面上的拉力Fi为
Figure PCTCN2017095213-appb-000020
Figure PCTCN2017095213-appb-000021
(2)内压作用在卡箍和接管锥头上的轴向拉力FG为
Figure PCTCN2017095213-appb-000022
(3)垫片的轴向预紧力Fm为
Fm＝πDGby       (4-3)
当采用自紧式密封垫时，Fm＝0。
式中b＝b0，因卡链接管锥头不存在法兰的翘曲现象。
(4)操作状态下卡箍承受的总轴向拉力
各国压力容器标准都是根据20世纪40年代的研究成果，认为在操作状态时密封面上的压紧应力应是设计压力p的2m倍，即
Figure PCTCN2017095213-appb-000023
其中m称为垫片系数，根据垫片材料、形式和尺寸。当采用自紧式密封垫时，Fp＝0。
操作状态下的轴向拉伸力Ft应是由介质压力所引起的轴向力FG与垫片操作状态所需密封压紧应力所引起轴向力Fp之和，可表示为
Figure PCTCN2017095213-appb-000024
Figure PCTCN2017095213-appb-000025
4.2径向载荷
(1)垫片预紧时产生是径向内压力FDj为
Fmj＝πDGbytan(α+μ2)     (4-6)
(2)操作状态下卡箍承受的总径向外压力Ftj为
Figure PCTCN2017095213-appb-000026
钢—钢摩擦系数f＝0.1～1.5，摩擦角μ＝tan-1f＝5.71～8.53°≈5～8°，为使计算结果可靠，预紧时μ取大值μ2＝8°，使用状态μ取小值μ1＝5°，即应力取可能的最大值。
4.3螺栓和销的载荷
在卡箍的任意径向截面上，其承受的向两边的总拉力为径向压力的
Figure PCTCN2017095213-appb-000027
倍，由此可以计算出卡箍对面两个螺栓所承受的拉力(螺栓总载荷)，其值也等于卡箍对面两对销的总载荷。
(1)预紧状态下螺栓的总载荷FmM为
FmM＝2DGby tan(α+μ2)     (4-8)
(2)操作状态下螺栓的总载荷Ftm为：
FtM＝DGp(DG+4b m)tan(α-μ1)           (4-9)
计算螺栓尺寸时，应取FmM、FtM中的最大值，即
FM＝max(FmM，FtM)            (4-10)
4.4说明
现有的卡箍管连接件，卡箍和高颈法兰的锥面只能有一种结合状态—刚好贴合，这种状态是不可改变的，螺栓只起到固定作用，因此可以说，标准和文献的应力分析和强度计算公式都是建立在不实假设基础上的。
在GB 150.3中，对卡箍强度计算还规定了一个预载状态。卡箍连接件在预紧状态时两密封面相互靠拢，高颈法兰的外锥面相对于卡箍的内锥面向外移动，在卡箍锥面上产生向里的摩擦力F。在操作状态，两密封面有分离趋势，高颈法兰外锥面相对于卡箍内锥面向里移动，卡箍与高颈法兰接触面的摩擦力方向和预紧状态方向相反，在卡箍锥面上产生向外的摩擦力F。在由预紧状态转到操作状态的过程中，卡箍斜面上的摩擦力F由向里转到向外。介质压力升起时，在两密封面将要有分离趋势的瞬间，作用在卡箍斜面的摩擦力仍然向里，此时称为预载状态，螺栓荷载与轴向应力的关系是将式(4-9)中的(α-μ1)换成(α+μ)。实际上，这是针对生 产中的一种特征情况—开始时操作不当造成瞬间超压，这种情况对DN15～25以下的小口径管道容易发生，而卡箍只适应于DN50以上大口径管道的连接，这种情况是不会发生的，或者说发生的几率非常小。
在GB 150.3中，内压作用在卡箍和接管锥头上的轴向载荷Fp计算
Figure PCTCN2017095213-appb-000028
这只是内压作用在卡箍和接管锥头轴向的单面应力，显然是错误的。在GB 150.1中，规定：碳素钢、低合金钢材料的抗拉强度安全系数nb＝2.7，屈服强度安全系数ns＝1.5，螺栓除外；碳素钢螺栓材料的屈服强度安全系数nsm＝2.7。nsm/ns＝1.8，增大螺栓屈服强度的安全系数，实际上是对式(4-2a)错误的补偿。我们采用式(4-2)计算内压的轴向载荷，螺栓屈服强度安全系数取1.5，与采用GB 150.3的计算结果其实是一样的，而且更可靠，这样做还取消了对螺栓材料安全系数的特殊规定，简化了设计计算方法。
5.尺寸计算
现有的卡箍尺寸设计计算公式，都非常复杂，如GB 150.3中计算公式多达37个。我们已经设定接管斜平面的面积占接管外锥面积的1/4，计算接管锥头切点处厚度时仅对切点处圆周的1/4进行强度计算，其余3/4圆周可以起加强作用。因此，对于卡箍和接管的尺寸计算，仅计算接管的管壁厚δ、接管锥头切点处的有效厚度hn、卡箍切点处的厚度fw，不必考虑接管锥头和卡箍锥面的弯折变形，设计计算过程大大简化。
5.1接管的管壁厚
现有的管壁厚计算公式都是简化近似式，计算过程复杂，这是在计算机和计算器出现之前得到的公式。由应力平衡，可以得到管壁厚的精确计算公式：
Figure PCTCN2017095213-appb-000029
上式的计算结果和GB 50316中计算公式的计算结果相同。
5.2卡箍的壁厚
设卡链螺栓凸耳和销处的空隙角总计为60°，即设N个卡箍的圆弧总周长为卡链圆周长的300/360，由力平衡可得
Figure PCTCN2017095213-appb-000030
Figure PCTCN2017095213-appb-000031
销耳和螺栓凸耳设计时，卡链的总空角应小于60°。
5.3接管锥头切点处的厚度
由力平衡可得
Figure PCTCN2017095213-appb-000032
Figure PCTCN2017095213-appb-000033
0.8[σ]b1为许用剪切应力。
5.4卡箍切点处的厚度
Figure PCTCN2017095213-appb-000034
5.5螺栓
(1)螺柱直径
对单凸耳卡箍，由力平衡可得
Figure PCTCN2017095213-appb-000035
Figure PCTCN2017095213-appb-000036
对双凸耳卡箍计算公式为
Figure PCTCN2017095213-appb-000037
(2)凸耳计算
卡箍凸耳的抗弯折强度，对面两对螺栓的总载荷由4个凸耳分担，可得下式
Figure PCTCN2017095213-appb-000038
Figure PCTCN2017095213-appb-000039
取力臂Lw＝螺母外接圆直径+5～6。凸耳宽La，单凸耳取La＝0.8E，双凸耳取La＝1.5×螺母外接圆直径。螺栓孔径d2＝1.2d1。
5.6)销
(1)销的直径
每个销有四个剪切面，由力平衡得
Figure PCTCN2017095213-appb-000040
Figure PCTCN2017095213-appb-000041
(2)销耳和销鼻(每卡箍两端的连接件)
取孔直径为销直径的1.2倍，d4＝1.2d3。设销耳高度为u1，销鼻的高度为u2，取u2＝2u1，u2+2u1＝0.8F，故u1＝0.2F。由力平衡可得
Figure PCTCN2017095213-appb-000042
Figure PCTCN2017095213-appb-000043
5.7材料的安全系数
计算材料的许用应力，需要材料抗拉强度安全系数nb和屈服强度安全系数ns。GB 150指出，“目前在压力容器安全法规和技术标准中采用的安全系数是粗放型的，由于将许多细节问题一概通过安全系数进行保障，这就造成了无法准确评估装置或设备安全裕度的问题”。我们采用GB 150介绍的美国动态安全系数理念，安全系数采用各国标准中的较低者—英国标准，对DN≤15、PN≤100管件乘系数2(最容易出现操作失误超压)，DN20～25、PN≤40管件乘系数1.5，DN32～50、PN≤40管件乘系数1.2。
表5-1英国标准材料的安全系数
材料 抗拉强度nb 屈服强度ns
碳钢和低合金钢 2.35 1.5
奥氏体不锈钢 2.5 1.5
5.8材料参数
(1)力学性质
本发明实例所用材料的力学性质，取自GB 150.2-2011、GB/T 1220-2000，见表5-2。
表5-2钢材锻件的力学性质MPa
材料 20# 35# 16Mn 30CrMo 304 321 316
抗拉强度σb 410 510 480 620 520 520 520
屈服强度σs 235 265 305 440      
(2)垫片系数
本发明实例密封垫片采用不锈钢—石墨缠绕垫片，垫片系数m＝3，垫片比压y＝17，取石棉垫比压11的1.5倍。本发明实例密封面采用榫槽面，计算用垫片宽度b＝(榫宽+垫片宽度)/2。标准和文献中不锈钢—石墨缠绕垫片的比压y＝90，按此计算法兰由石棉垫换成金属垫后，上螺栓的力度需增大8倍，法兰的厚度也需增加8倍，这是一个明显的错误，或是机器测量的简单结果。实际上，法兰由石棉垫换成金属垫后，上螺栓的力只需增加一点，但必须上均匀，即上螺栓时要对面一圈一圈慢慢上，这点比上石棉垫要求高。上卡链很简单，只要用力上螺栓就行，这也是卡接的优势之一。
6.本发明设计计算结果
按前述的本发明设计方法，计算了DN50～600卡接的尺寸，压力PN25、40、63，密封面为榫槽面，垫片为不锈钢—石墨缠绕垫片，垫片厚度3.2，设计接管列于表6-1、2、3，均为典型的实施例。从表中数据可以看出，弓长余量13～37mm，卡接间距4.7～6.3mm，对加工精度要求不高，很容易制造。卡箍的尺寸明显比法兰小很多，大口径卡接并不像法兰一样需要很粗的螺栓，价格会比法兰低很多。
为了进一步和法兰比较，我们计算了卡接重量。在比较卡接和法兰重量时，法兰应为一对(两片)的重量。卡接重量应为一套卡箍的重量加一对接管锥头的重量，计算接管锥头重量时内径应取管外径，即剔除法兰安装时也有的管子，为便于叙述我们称为有效锥头重量。卡接螺栓加销的重量，比法兰一套螺栓的重量轻，因螺栓价值低，两者重量比较时不计此项。法兰的重量取自GB/T 9124-2010，板式平焊法兰。计算结果列于表中，可以看出，卡接的重量只是法兰的10～30％，口径越大，压力越高，卡接比法兰越轻。卡接接管有效锥头的重量只是法兰重量的2.5～6％，因替卡接代法兰时仅接管需换成不锈钢，卡箍可以使用碳钢(镀锌、镀镍)，不锈钢卡接对不锈钢法兰的价格优势更大。
表6-1压力PN25卡接设计结果
公称直径DN 50 65 80 100 125 150 200 250 300 350 400 500 600
卡箍瓣数N 4 4 4 4 6 6 8 8 8 12 12 16 16
锥角α 15 15 15 15 15 15 15 15 12 10 10 10 10
Β 90 90 90 90 90 90 90 90 90 90 90 90 90
βw 22.5 22.5 22.5 22.5 15 15 11.2 11.2 11.2 7.5 7.5 5.6 5.6
Γ 240 240 240 240 300 300 300 300 300 300 300 300 300
γn 60 60 60 60 50 50 37.5 37.5 37.5 25 25 18.75 18.75
密封槽宽 9 9 9 9 9 10.5 12.5 14 14.5 16 15.5 17 17
榫槽间隙 0.8 0.8 0.8 0.8 0.8 0.8 0.8 0.8 0.8 0.8 0.8 0.8 0.8
B 5.2 6.1 6.1 6.1 6.1 6.85 7.85 8.6 8.85 9.6 9.35 10.1 10.1
接管材料 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20#
卡箍材料 20# 20# 20# 20# 20# 20# 20# 20# 35# 35# 35# 35# 35#
管外径Do 57 76 89 108 133 159 219 273 325 377 426 530 630
管内径Di 50 69 82 101 126 151 207 261 311 361 410 510 610
过度圆r1 6 6 6 7 7 8 8 10 10 10 10 10 10
D1 65.9 84.9 97.9 118.4 143.4 170.9 230.9 287.8 340.8 393.5 442.5 546.5 646.5
Dn 77 96 109 130 155 183 244 301 354 407 456 560 660
Dw 93 112 127 150 175 207 270 329 384 439 488 596 696
DG 55.6 74.6 87.6 107.6 132.6 157.6 214.6 268.6 318.6 368.6 418.6 519.6 619.6
gD 0.24 0.29 0.33 0.39 0.20 0.24 0.17 0.21 0.20 0.08 0.09 0.06 0.07
gE 1.38 1.72 1.96 2.33 1.95 2.30 1.73 2.14 2.00 0.85 0.95 0.66 0.78
Δg 1.14 1.43 1.63 1.95 1.75 2.06 1.56 1.93 1.80 0.77 0.86 0.60 0.70
管壁厚δD 3.5 3.5 3.5 3.5 3.5 4 6 6 7 8 8 10 10
理论值 0.6 0.8 0.9 1.1 1.4 1.7 2.3 2.8 3.4 3.9 4.4 5.5 6.6
接管高度H 50 50 50 50 50 50 50 50 50 50 50 50 50
剪切厚度hw1 4 4 4 4 4 4 4 4 4 4 4 4 4
hw2 6 6 6 6 6 6 6 6 6 6 6 6 6
hn1 5.9 5.9 6.1 6.3 6.5 7.0 8.3 8.5 8.0 8.7 8.7 9.1 9.1
hn2 7.9 7.9 8.1 8.3 8.5 9.0 9.3 9.5 9.0 8.7 8.7 9.1 9.1
理论值 0.23 0.29 0.30 0.31 0.37 0.43 0.57 0.69 0.56 0.45 0.51 0.62 0.72
卡箍外径Eo 111 130 147 170 197 229 296 355 411 467 516 626 726
卡箍内径Ei 101 120 136 159 185 217 280 339 395 451 500 610 710
壁厚δE 5 5 5.5 5.5 6 6 8 8 8 8 8 8 8
理论值 0.55 0.79 0.89 1.06 1.28 1.52 2.07 2.59 2.43 2.80 3.15 3.88 4.60
切点厚fn 6.85 7.89 8.17 8.96 8.77 9.77 8.94 9.71 10.26 10.01 10.02 9.64 9.65
切点厚fw 8.99 10.04 10.58 11.64 11.45 12.99 12.42 13.46 13.45 12.83 12.84 12.81 12.82
理论值 0.19 0.25 0.25 0.27 0.33 0.38 0.51 0.63 0.41 0.34 0.38 0.47 0.55
卡箍高度F 32 34 35 37 37 40 40 42 42 42 42 42 42
单凸耳螺栓d1 8 8 8 10 12 12 14 16 16 16 16 22 24
理论值 3.9 4.9 5.4 6.0 7.1 8.4 11.1 13.6 12.5 12.1 13.5 16.5 19.4
La 20 20 20 24 26 26 30 34 34 38 41    
Lw 25.6 27.2 28 29.6 29.6 32 32 33.6 33.6 33.6 33.6    
Lh 6 7 7 8 10 11 13 15 15 16 18    
Lh理论值 3.6 4.4 4.7 5.6 6.9 7.8 11.1 14.1 12.3 12.6 14.6    
双凸耳螺栓d1 6 6 6 8 10 10 12 14 14 14 14 14 16
理论值 2.8 3.5 3.8 4.3 5.0 5.9 7.9 9.6 8.8 8.5 9.5 11.7 13.7
La 17 17 17 20 25 25 27 30 30 30 30 33 33
Lw 18 18 18 23 28 28 32 37 37 37 37 37 42
Lh 6 7 7 7 8 8 10 11 11 11 12 13 14
Lh理论值 2.8 3.5 3.8 4.1 4.9 5.8 7.4 8.9 7.8 7.5 8.4 10.8 11.9
销直径d3 6 6 6 8 8 8 10 10 10 10 10 12 14
理论值 2.1 2.6 2.8 3.2 3.8 4.4 5.9 7.2 6.3 6.1 6.8 8.3 9.8
耳直径d5 12 12 12 15 17 17 20 20 20 20 20 22 24
理论值 7.0 7.2 7.3 9.7 10.0 10.4 13.7 14.9 14.0 13.8 14.5 18.4 22.6
弓长比ω 2.5 2.4 2.4 2.4 3.1 3.1 3.1 3.1 3.2 3.2 3.2 3.2 3.2
弓长余量ΔC 13.5 13.8 15.7 18.7 22 25.9 26.6 32.9 38.8 30.2 33.9 31.4 37.1
卡接余量ΔL 4.7 4.5 4.3 4.4 5.1 5.2 5.9 5.8 5.7 6.3 6.2 6.4 6.3
法兰重量kg 5.46 6.96 8.64 12.14 16.38 20.6 28.6 40.2 53.2 83.6 115.2 174 254
卡箍重量kg 1.66 2.19 2.90 3.97 5.03 7.32 11.6 16.6 19.5 22.8 26.3 38.7 48.5
卡接/法兰重％ 30.5 31.5 33.6 32.7 30.7 35.5 40.6 41.3 36.7 27.2 22.8 22.3 19.1
锥头/法兰重％ 8.7 8.6 8.6 8.4 7.4 8.4 9.4 9.4 8.2 6.4 5.2 4.6 3.7
表6-2压力PN40卡接设计结果
公称直径DN 50 65 80 100 125 150 200 250 300 350 400 500 600
卡箍瓣数N 4 4 4 4 6 6 8 8 8 12 12 16 16
接管材料 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20#
卡箍材料 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 30CrMo 30CrMo
管壁厚δD 3.5 3.5 3.5 3.5 3.5 4 6 6 7 8 8 10 12
理论值 0.92 1.2 1.4 1.8 2.2 2.6 3.6 4.4 5.3 6.1 6.9 8.6 10.2
接管高度H 50 50 50 50 50 50 50 50 50 50 50 50 50
剪切厚度hw1 4 4 4 4 4 4 4 4 4 4 4 4 4
hw2 6 6 6 6 6 6 6 6 6 6 6 6 6
hn1 5.9 5.9 6.1 6.3 6.5 7.0 8.3 8.5 8.0 8.7 8.7 9.1 9.1
hn2 7.9 7.9 8.1 8.3 8.5 9.0 9.3 9.5 9.0 8.7 8.7 9.1 9.1
理论值 0.36 0.45 0.47 0.49 0.58 0.68 0.90 1.09 0.88 0.72 0.80 0.97 1.14
卡箍外径Eo 111 130 147 170 197 229 296 355 411 467 516 626 726
卡箍内径Ei 101 120 136 159 185 217 280 339 395 451 500 610 710
壁厚δE 5 5 5.5 5.5 6 6 8 8 8 8 8 8 8
理论值 0.70 1.00 1.13 1.34 1.62 1.92 2.62 3.27 3.81 4.40 4.95 5.02 5.95
切点厚fn 6.85 7.89 8.17 8.96 8.77 9.77 8.94 9.71 10.26 10.01 10.02 9.64 9.65
切点厚fw 8.99 10.04 10.58 11.64 11.45 12.99 12.42 13.46 13.45 12.83 12.84 12.81 12.82
理论值 0.24 0.31 0.32 0.34 0.41 0.48 0.65 0.80 0.65 0.53 0.60 0.60 0.71
卡箍高度F 32 34 35 37 37 40 40 42 42 42 42 42 42
单凸耳螺栓d1 8 8 8 10 12 14 18 18 18 18      
理论值 4.7 5.9 6.3 7.1 8.4 9.9 13.1 16.1 15.7 15.2 16.9 16.1 18.9
La 20 20 20 24 26 30 38 38 38 38      
Lw 25.6 27.2 28 29.6 29.6 32 32 33.6 33.6 33.6      
Lh 6 7 7 8 10 11 13 20 20 20      
Lh理论值 4.0 4.9 5.2 6.3 7.7 9.4 14.0 16.8 16.3 15.8      
双凸耳螺栓d1 3.3 4.1 4.5 5.0 6.0 7.0 9.3 11.4 11.1 10.7 12.0 11.4 13.4
理论值 6 6 6 8 10 10 14 14 14 14 14 14 18
La 17 17 17 20 25 25 27 30 30 30 30 33 37
Lw 18 18 18 23 28 28 32 37 37 37 37 37 42
Lh 6 7 7 7 8 8 10 11 11 11 12 14 16
Lh理论值 3.1 3.9 4.3 4.6 5.5 6.5 8.4 10.1 9.8 9.5 10.6 12.3 14.4
销直径d3 6 6 6 8 8 8 10 10 10 10 10 12 14
理论值 2.4 3.0 3.2 3.6 4.3 5.0 6.6 8.1 7.9 7.7 8.5 9.5 11.1
耳直径d5 12 12 12 15 17 17 20 20 20 20 20 22 24
理论值 7.1 7.4 7.5 9.9 10.3 10.8 14.4 16.0 15.7 15.4 16.5 19.9 24.7
法兰重量kg 5.46 6.96 8.64 12.14 16.38 21.6 35.8 59.6 90.2 133.4 194.2    
卡箍重量kg 1.66 2.19 2.90 3.97 5.03 7.32 11.62 16.60 19.55 22.77 26.29 38.75 48.54
卡接/法兰重％ 30.5 31.5 33.6 32.7 30.7 33.9 32.4 27.9 21.7 17.1 13.5    
锥头/法兰重％ 8.7 8.6 8.6 8.4 7.4 8.0 7.5 6.3 4.9 4.0 3.1    
表6-3压力PN63卡接设计结果
公称直径DN 50 65 80 100 125 150 200 250 300 350 400 500 600
卡箍瓣数N 4 4 4 4 6 6 8 8 8 12 12 16 16
接管材料 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20# 20#
卡箍材料 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 35# 30CrMo 30CrMo
管壁厚δD 3.5 3.5 3.5 3.5 4 6 8 8 8 10 10 14 14
理论值 1.4 1.9 2.2 2.7 3.3 4.0 5.4 6.8 6.6 7.6 8.6 10.7 12.7
接管高度H 50 50 50 50 50 50 50 50 50 50 50 50 50
剪切厚度hw1 4 4 4 4 4 4 4 4 4 4 4 4 4
hw2 6 6 6 6 6 6 6 6 6 6 6 6 6
hn1 5.9 5.9 6.1 6.3 6.5 7.0 8.3 8.5 8.0 8.7 8.7 9.1 9.1
hn2 7.9 7.9 8.1 8.3 8.5 9.0 9.3 9.5 9.0 8.7 8.7 9.1 9.1
理论值 0.56 0.70 0.73 0.77 0.90 1.03 1.34 1.64 1.08 0.89 1.00 1.24 1.45
卡箍外径Eo 111 130 147 170 197 229 296 355 411 467 516 626 726
卡箍内径Ei 101 120 136 159 185 217 280 339 395 451 500 610 710
壁厚δE 5 5 5.5 5.5 6 6 8 8 8 8 8 8 8
理论值 0.70 1.00 1.13 1.34 1.62 1.92 2.62 3.27 3.81 4.40 4.95 5.02 5.95
切点厚fn 6.85 7.89 8.17 8.96 8.77 9.77 8.94 9.71 10.26 10.01 10.02 9.64 9.65
切点厚fw 8.99 10.04 10.58 11.64 11.45 12.99 12.42 13.46 13.45 12.83 12.84 12.81 12.82
理论值 0.37 0.49 0.50 0.54 0.64 0.73 0.97 1.20 0.82 0.68 0.77 0.96 1.13
卡箍高度F 32 34 35 37 37 40 40 42 42 42 42 42 42
单凸耳螺栓d1 8 10 10 12 14 16 20 24 18 18      
理论值 5.8 7.3 7.9 8.9 10.5 12.2 16.1 19.7 15.1 14.7 16.4 20.3 23.8
La 20 20 20 24 26 30 38 38 38 38      
Lw 25.6 27.2 28 29.6 29.6 32 32 33.6 33.6 33.6      
Lh 6 7 7 8 10 11 13 20 20 20      
Lh理论值 5.0 6.1 6.6 7.8 9.6 11.6 17.2 20.5 18.3 17.9      
双凸耳螺栓d1 6 6 6 8 10 10 14 16 14 14 14 18 20
理论值 4.1 5.2 5.6 6.3 7.4 8.6 11.4 14.0 10.6 10.4 11.6 14.4 16.8
La 17 17 17 20 25 25 30 33 31 31 31 36 40
Lw 18 18 18 23 28 28 37 42 37 37 37 47 52
Lh 6 7 7 7 8 10 13 14 13 14 14 16 18
Lh理论值 3.9 4.9 5.3 5.7 6.9 8.0 10.0 12.1 11.2 10.9 12.2 14.4 16.9
销直径d3 6 6 6 8 8 8 10 12 12 12 12 14 16
理论值 2.9 3.7 4.0 4.5 5.3 6.2 8.1 10.0 8.9 8.6 9.7 12.0 14.0
耳直径d5 12 12 12 15 17 17 20 22 22 22 22 28 34
理论值 7.4 7.9 8.0 10.5 11.2 11.8 16.2 20.6 19.1 18.8 20.2 26.1 32.3
法兰重量kg 3.99 4.73 5.9 8.05 11.7 16.9 20.5 42.1 59.1 88.7 121    
卡箍重量kg 1.66 2.19 2.9 3.97 5.03 7.32 11.6 16.6 19.5 22.7 26.3 40.2 51.8
卡接/法兰重％ 20.8 23.2 24.6 24.7 21.5 21.7 28.3 19.7 16.5 12.8 10.9    
锥头/法兰重％ 6.0 6.4 6.3 6.3 5.2 5.1 6.6 4.5 3.7 3.0 2.5    
7.实例：
1)DN100PN25卡接，按表6-1数据制造，试验水压5MPa，保压24小时，无泄漏。
2)DN150PN40卡接，按表6-2数据制造，试验水压10MPa，保压24小时，无泄漏。
以上所述仅是本发明的优选实施方式，应当指出：对于本技术领域的普通技术人员来说，在不脱离本发明原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也应视为本发明的保护范围。

Claims (10)

  1. 多瓣斜平面的管连接卡箍，其特征是所述卡箍分为2组，组内各瓣卡箍之间用销连接，销平行于连接管轴，组与组之间用螺栓连接，螺栓垂直于管轴，每个卡箍的外形均为部分圆环柱，里面为圆弧凹槽，凹槽的上下面为对称的部分内锥面，各卡箍连接成环后形成卡链。
  2. 根据权利要求1所述的管连接卡箍，其特征是卡箍内锥面的锥角即内锥面法向与卡链轴向的夹角α＝10～20°；所述卡箍的瓣数N为偶数，N不超过同口径法兰的螺栓数。
  3. 根据权利要求1所述的管连接卡箍，其特征是每个卡箍内锥面的中间部分凸出变为梯形平面，平面与锥面平行，即平面的斜角与锥面的锥角相等。
  4. 根据权利要求1所述的管连接卡箍，其特征是单个卡箍梯形斜平面两侧边延至卡链圆心所形成的梯形角γ的总合Γ＝180～300°，单个卡箍的梯形角γ＝Γ/N。
  5. 一种与权利要求1-4之一所述的管连接卡箍匹配的接管，其特征是一端为管头，一端为凸出的锥头，管头与管道焊接，锥头的外锥角与卡箍的内锥角相等，锥头的外锥面削出N个与锥面平行的凹的梯形斜平面。
  6. 根据权利要求5所述的接管，其特征是接管锥头上梯形斜平面两侧边延至接管圆心所形成的梯形角的总合Β＝90～120°，卡箍梯形角与接管梯形角的比值γ/β≥2。
  7. 根据权利要求5所述的接管，其特征是接管锥头底面为密封面，采用强制性密封垫，密封面型式为平面、凹凸面、榫槽面、环槽面或三角环内槽面，也能够采用有自紧功能的软密封垫。
  8. 根据权利要求5所述的接管，其特征是接管的管头与管道用螺纹连接。
  9. 一种管路连接件，由权利要求1所述的卡链和权利要求5所述的接管组成，其特征是一套卡链和一对接管组成一套管路连接件，两个接管的锥头之间放置密封垫，两个接管的管头分别与两边的管道焊接或用螺纹连接。
  10. 根据权利要求9所述的管路连接件，其特征是用于阀门制造，即将传统法兰连接式阀门上的法兰改成权利要求5所述的接管，阀门与管道用权利要求1所述的卡链连接；接管的口径为DN为DN50～700。
PCT/CN2017/095213 2016-08-01 2017-07-31 多瓣斜平面卡箍及其管连接件 Ceased WO2018024174A1 (zh)

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US16/322,490 US11506313B2 (en) 2016-08-01 2017-07-31 Multi-petaled oblique-plane hoop and pipe connector thereof
JP2019506360A JP6821872B2 (ja) 2016-08-01 2017-07-31 オレンジピール型の斜平面クランプ及びその管連結部材
KR1020197005924A KR102063740B1 (ko) 2016-08-01 2017-07-31 다판 경사면 후프 및 파이프 커넥터
EA201990414A EA038839B1 (ru) 2016-08-01 2017-07-31 Многолепестковый наклонный зажим и соединитель труб, содержащий его
EP17836356.0A EP3492793B1 (en) 2016-08-01 2017-07-31 Multi-petaled oblique-flat-surface hoop and pipe connector system thereof

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