CN201651397U - High-pressure heavy-caliber double gathering ball valve - Google Patents

High-pressure heavy-caliber double gathering ball valve Download PDF

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Publication number
CN201651397U
CN201651397U CN2010201778826U CN201020177882U CN201651397U CN 201651397 U CN201651397 U CN 201651397U CN 2010201778826 U CN2010201778826 U CN 2010201778826U CN 201020177882 U CN201020177882 U CN 201020177882U CN 201651397 U CN201651397 U CN 201651397U
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CN
China
Prior art keywords
valve
pressure
caliber
ball
ball valve
Prior art date
Application number
CN2010201778826U
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Chinese (zh)
Inventor
姚伟
佘恩亮
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四川赛尔阀门制造有限公司
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Priority to CN2010201778826U priority Critical patent/CN201651397U/en
Application granted granted Critical
Publication of CN201651397U publication Critical patent/CN201651397U/en

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Abstract

The utility model discloses a high-pressure heavy-caliber double gathering ball valve, belonging to the valve field. The high-pressure heavy-caliber double gathering ball valve comprises a high-pressure heavy-caliber ball valve and a second high-pressure heavy-caliber ball valve; the fluid center lines of balls of the high-pressure heavy-caliber ball valve and the second high-pressure heavy-caliber ball valve are consistent, therefore, the high-pressure heavy-caliber double gathering ball valve has the functions of replacing a high-pressure ball valve being sealed at the upstream with the effect of four single pistons and replacing a high-pressure ball valve with the effect of two double pistons. When the high-pressure heavy-caliber double gathering ball valve in the application is arranged on a pipeline, the pipeline is cut only by rotating one ball, and after a valve seat sealing assembly of the ball loses effectiveness, the other ball acts. Or the two balls act alternately, so that the applied product has longer service life, so as to achieve the function of at least two high-pressure heavy-caliber ball valves and play the roles of double insurance and double cutting for the pipeline. The two high-pressure ball valves are integrally formed, thereby avoiding the temporary debugging for the flow center lines of the two ball valves in installation, reducing one connecting point and one leakage point in the direct series installation of the two high-pressure ball valves and being safe and reliable.

Description

High-pressure large-caliber duplex gathering ball valve
Technical field
The utility model relates to a kind of valve, particularly a kind of ball valve.
Background technique
The rational method of shipment of petroleum gas resources economy is to adopt long-distance pipe to carry, and the high pressure heavy caliber is the development trend of oil-gas gathering and transportation pipeline, the high-pressure large-caliber ball valve of installing on high pressure large-caliber gas-oil transfer line at present has been the high-pressure large-caliber ball valve of single cutting action, as shown in Figure 1, it on this high-pressure large-caliber ball valve internal structure structure of a valve rod of a spheroid of two valve components containings, specifically comprise entrance point, outlet end, operator, valve rod, spheroid, valve gap and support plate, valve gap connects with valve body by double-screw bolt scyewed joint or welding and connects the formation one, and spheroid leans on support plate by mode and valve gaps such as pins, fixing and consistent between the valve body with valve metering orifice center line; Valve rod and spheroid link into an integrated entity by flat side, and operator and valve rod are integral by key connecting, and the handwheel of rotating operation device will drive spheroid and rotate, and spheroid and runner are switched on or off.
On the internal structure of this single high-pressure large-caliber ball valve product owing to be the structure of the valve rod of a spheroid that contains of two valve components, when product uses on the oil-gas gathering and transportation pipeline, particularly in comparatively crucial installation position, valve is because improper use or other reasons cause seal failure, will form valves leakage so, valve just must be changed in the scene, because the oil-gas gathering and transferring pipeline many places are in the depopulated zone, desert, the cost of changing high pressure heavy caliber ball valve is high, and high pressure heavy caliber ball valve weight is up to more than ten tons, the on-the-spot installation and the very inconvenience of replacing ball valve, and pipe oil gas need be carried when changing valve and cut off and to change, influence the normal conveying of oil gas, cause inconvenience.
If existing high-pressure large-caliber ball valve is directly connected, can reach the effect of dual fail-safe, a ball valve is revealed and can be adopted another ball valve to seal, but there is following difficult point in this serial fashion: the one, if two valve bodies are connected by modes such as bolt connections, the spheroid of two ball valves will guarantee two ball valves when Installation and Debugging metering orifice center line is the unusual difficulty of unanimity relatively, not only very time-consuming and two high-pressure ball valves directly junctions of series connection are many possible leak source that leaks, the 2nd, if two existing ordinary ball valve are connected into a valve body, can make the length of valve body longer, when deep hole processing, must select large-scale numerical control borer or numerically controlled lathe to process, cost height, and inefficiency.How both to have guaranteed to adopt two even more valve bodies to form multiple anti-leak function, can guarantee the simple and convenient of the processing technology of valve body own again, and the unanimity that does not need the flow center line of interim Installation and Debugging ball valve is that a true unsolved difficult problem is wanted to solve in related domain always.
The model utility content
Model utility purpose of the present utility model is: at the problem of above-mentioned existence, provide a kind of have having a double meaningly close function, dual fail-safe is used, can thoroughly realize the high-pressure large-caliber duplex gathering ball valve of zero leakage.
The technical solution adopted in the utility model is such: a kind of high-pressure large-caliber duplex gathering ball valve, comprise the high-pressure large-caliber ball valve, described high-pressure large-caliber ball valve comprises entrance point, outlet end, operator, valve rod, spheroid, valve gap and support plate, also comprise the second high-pressure large-caliber ball valve identical with the high-pressure large-caliber ball valve, the described second high-pressure large-caliber ball valve correspondence comprise second entrance point, second outlet end, second operator, second valve rod, second spheroid, second valve gap and second support plate, the second high-pressure large-caliber ball valve is connected with the high-pressure large-caliber ball valve, and described outlet end is communicated with second entrance point becomes a valve body.
As preferably: the described outlet end and second entrance point are one-body molded.
As preferably: be provided with valve seat bearing ring and valve seat between described spheroid and valve gap, the valve body, be provided with the second valve seat bearing ring and second valve seat between described second spheroid and second valve gap, the valve body equally; Simultaneously, between valve seat bearing ring and valve gap, O-ring seals is arranged, between the second valve seat bearing ring and second valve gap, second O-ring seals is arranged.
As preferably: the external diameter of O-ring seals is greater than the sealed diameter of valve seat, simultaneously the sealed diameter that seals greater than valve seat bearing ring and O-ring seals internal diameter of the sealed diameter of valve seat.
As preferably: sealing surface is provided with fire-protection ring between described valve seat bearing ring and the valve gap, and sealing surface also is provided with fire-protection ring between valve seat bearing ring and the valve body; Sealing surface is provided with second fire-protection ring between the second valve seat bearing ring and second valve gap, and sealing surface also is provided with second fire-protection ring between the second valve seat bearing ring and the valve body.
As preferably: be provided with anti-static device between spheroid and support plate, the valve rod; Be provided with second anti-static device between second spheroid and second support plate, second valve rod.
In sum, owing to adopted technique scheme, the beneficial effects of the utility model are: valve just has the high-pressure ball valve that replaces 4 single piston effect upstream seal like this, substitutes the high-pressure ball valve of two double-piston effects (upstream and downstream sealing).When on pipeline, the application's valve being installed, when pipeline need cut off, only need the operator of rotating sphere correspondence or any one in pairing second operator of second spheroid that pipeline is cut off, the only just action after the valve base sealing component failures of this spheroid of another spheroid.Also but two spheroids of alternating movement make the longer service life of the application's product, reach the function of at least two high-pressure large-caliber ball valves, pipeline are used reach dual fail-safe, two cutting action.Two high-pressure ball valves are one-body molded, do not need to debug when mounted the flow center line of two ball valves temporarily, also reduced a tie point and the possible leak source that leaks during two high-pressure ball valves directly are installed in series, and are safe and reliable.
Description of drawings
Fig. 1 is the utility model prior art constructions schematic representation;
Fig. 2 is the partial enlarged drawing of the I portion of Fig. 1;
Fig. 3 is the utility model embodiment 1 a structural representation;
Fig. 4 is the partial enlarged drawing of I portion among Fig. 3.
Mark among the figure: 1.1 is valve gap; 1.2 be second valve gap; 2 is valve body; 3.1 be spheroid; 3.2 be second spheroid; 4.1 and 4.2 be the valve seat bearing ring; 9.1 and 9.2 be the second valve seat bearing ring; 5.1 and 5.2 be valve seat; 10.1 and 10.2 be second valve seat; 6.1 and 6.2 be fire-protection ring; 14.1 and 14.2 be second fire-protection ring; 7.1 and 7.2 cluster spring; 12.1 and 12.2 be second cluster spring; 8.1 and 8.2 be O-ring seals; 8.3 and 8.4 be former little O-ring seals; 11.1 and 11.2 be second O-ring seals; 13.1 be valve rod; 13.2 be second valve rod; 15.1 and 15.2 be support plate; 16.1 and 16.2 be second support plate; 17.1 be operator, 17.2 is second operator; 18.1 be anti-static device; 18.2 be second anti-static device; 19.1 be entrance point; 19.2 be outlet end, 19.3 is second outlet end, D0 is the external diameter of O-ring seals; D1 is the sealed diameter of valve seat; Dm is the sealed diameter of valve seat bearing ring and the sealing of O-ring seals internal diameter.
Embodiment
Below in conjunction with accompanying drawing, the utility model is done detailed explanation.
In order to make the purpose of this utility model, technological scheme and advantage clearer,, the utility model is further elaborated below in conjunction with drawings and Examples.Should be appreciated that specific embodiment described herein only in order to explanation the utility model, and be not used in qualification the utility model.
Embodiment 1:
As shown in Figure 3 and Figure 4, a kind of high-pressure large-caliber duplex gathering ball valve, comprise the high-pressure large-caliber ball valve, described high-pressure large-caliber ball valve comprises entrance point, outlet end, operator 17.1, valve rod 13.1, spheroid 3.1, valve gap 1.1, support plate 15.1 and 15.2, also comprise the second high-pressure large-caliber ball valve identical with the high-pressure large-caliber ball valve, the described second high-pressure large-caliber ball valve correspondence comprise second entrance point, second outlet end, second operator 17.2, second valve rod 13.2, second spheroid 3.2, second valve gap 1.2, second support plate 16.1 and 16.2, the second high-pressure large-caliber ball valve is connected with the high-pressure large-caliber ball valve, described outlet end is communicated with second entrance point becomes a valve body 2, the outlet end and second entrance point are one-body molded, make whole valve body 2 have an entrance point and an outlet end, medium flows to from entrance point 19.1, flows out from second outlet end 19.3;
Be provided with between spheroid 3.1 and valve gap 1.1, the valve body 2 valve seat bearing ring 4.1 and 4.2, and valve seat 5.1 and 5.2, the second spheroids 3.2 and second valve gap 1.2, valve body 2 between be provided with the second valve seat bearing ring 9.1 and 9.2 equally, reach second valve seat 10.1 and 10.2;
On one side of high-pressure large-caliber ball valve, sealing surface is provided with fire-protection ring 6.1 between valve seat bearing ring 4.1 and the valve gap 1.1, and at the another side of high-pressure large-caliber ball valve, sealing surface is provided with fire-protection ring 6.2 between valve seat bearing ring 4.2 and the valve body 2; Same, on one side of the second high-pressure large-caliber ball valve, sealing surface is provided with that sealing surface also is provided with second fire-protection ring 14.1 between second fire-protection ring, 14.2, the second valve seat bearing rings 9.1 and the valve body 2 between the second valve seat bearing ring 9.2 and second valve gap 1.2; Between spheroid 3.1 and the support plate 15.1, be provided with anti-static device 18.1 between spheroid 3.1 and the valve rod 13.1; Be provided with second anti-static device 18.2 between second spheroid 3.2 and second support plate 16.1, second spheroid 3.2 and 13.2 second valve rods.
In addition, the outer diameter D 0 of O-ring seals 8.2 is greater than the sealed diameter D1 of valve seat 5.2, the sealed diameter D1 of valve seat 5.2 is greater than the sealed diameter Dm of valve seat bearing ring 4.2 with the sealing of O-ring seals 8.2 internal diameters simultaneously, like this, no matter medium flows to A from L and still flows to L from A and all can seal, very convenient when installing and using like this.
And for present ball valve, as Fig. 2, about respectively be provided with two O-ring seals, be O-ring seals 8.1 and 8.2, former little O-ring seals 8.3 and 8.4, the sealed diameter of the external diameter of O-ring seals 8.2 and valve seat bearing ring 4.2 and the sealing of O-ring seals 8.2 internal diameters is all greater than the sealed diameter of valve seat 5.2, and this structured media can seal when A flows to L, and medium can not seal when L flows to A.
During use, medium enters from entrance point 19.1, because piston effect by valve seat bearing ring 4.1 and 4.2, valve seat bearing ring 4.1 and 4.2 all can move forward and backward, at entrance point, be adjacent to spheroid 3.1 by pressure medium promotion valve seat bearing ring 4.1 drive valve seats 5.1 and form sealing, form sealing like this between valve seat 5.1 and the spheroid 3.1, between valve seat bearing ring 4.1 and the valve gap 1.1 O-ring seals 8.1 is arranged, medium is just kept apart by valve seat bearing ring 4.1, valve seat 5.1, spheroid 3.1 like this, and is promptly sealed at entrance point 19.1.Lower end at 3.1 spheroids, if owing to the seal failure between valve seat bearing ring 4.1, valve seat 5.1, the spheroid 3.1, medium will enter valve seat bearing ring 4.2, valve seat 5.2, spheroid 3.1 positions, shown in the partial enlarged drawing of Fig. 3, when the A cavity pressure was higher than the L cavity pressure, the active force effect that the area difference of D0 and D1 produces promoted 5.2 and compresses spheroid generation sealing; On the contrary, when the L cavity pressure was higher than the A cavity pressure, the active force effect that the area difference of D1 and Dm produces promoted valve seat 5.2 and compresses spheroid generation sealing.Therefore when medium no matter from the upstream extremity of valve seat bearing ring or from the downstream of valve seat bearing ring, the capital utilizes the action principle of above-mentioned piston effect to form the sealing of valve, therefore has medium also can not leak into the position of A shown in Fig. 3 in the cavity that forms between valve seat bearing ring 4.1, valve seat 5.1, spheroid 3.1 and valve seat bearing ring 4.2, valve seat 5.2 and valve body 2 and valve gap 1.1.
Medium will flow to the second valve seat bearing ring, 9.1 positions after two seal valve seat assemblies seal failure at 3.1 spheroid positions, the second valve seat bearing ring 9.1 and 9.2 structural type and processing dimension and valve seat bearing ring 4.1,4.2 are in full accord, pressure medium will promote the second valve seat bearing ring, 9.1 drives, second valve seat 10.1 and be adjacent to spheroid 3.2 formation sealings, second O-ring seals 11.1 is arranged between the second valve seat bearing ring 9.1 and the valve body 2, medium is just kept apart by the second valve seat bearing ring 9.1, second valve seat 10.1, spheroid 3.2 like this, seals at spheroid 3.2 positions.If this position sealing was also lost efficacy, medium just flow to the second valve seat bearing ring, 9.2 positions, action principle by the double-piston effect, medium enters the second valve seat bearing ring, 9.2 backs and second O-ring seals, 11.2 places, and medium promotes the second valve seat bearing ring 9.2 and is adjacent to spheroid 3.2 formation sealings together with second valve seat 10.2.The same with spheroid 3.1 positions, two cover valve components at spheroid 3.2 positions adopt the design of double-piston effect structure in like manner also to replace the high-pressure ball valve of two traditional single piston effect upstream seal.
The application has the high-pressure ball valve that replaces 4 single piston effect upstream seal, substitutes the high-pressure ball valve of two double-piston effects (upstream and downstream sealing).When on pipeline, the application's valve being installed, when pipeline need cut off, only need the operator 17.1 of rotating sphere 3.1 correspondences or any one in the spheroid 3.2 pairing operators 17.2 that pipeline is cut off, the only just action after the valve base sealing component failures of this spheroid of another spheroid.Also but two spheroids of alternating movement make the longer service life of the application's product, reach the function of at least two high-pressure large-caliber ball valves, pipeline are used reach dual fail-safe, two cutting action.Two high-pressure ball valves are one-body molded, do not need to debug when mounted the flow center line of two ball valves temporarily, also reduced a tie point and the possible leak source that leaks during two high-pressure ball valves directly are installed in series, and are safe and reliable.
The above only is preferred embodiment of the present utility model; not in order to restriction the utility model; all any modifications of within spirit of the present utility model and principle, being done, be equal to and replace and improvement etc., all should be included within the protection domain of the present utility model.

Claims (6)

1. high-pressure large-caliber duplex gathering ball valve, comprise the high-pressure large-caliber ball valve, described high-pressure large-caliber ball valve comprises entrance point, outlet end, operator, valve rod, spheroid, valve gap and support plate, it is characterized in that: also comprise the second high-pressure large-caliber ball valve identical with the high-pressure large-caliber ball valve, the described second high-pressure large-caliber ball valve correspondence comprise second entrance point, second outlet end, second operator, second valve rod, second spheroid, second valve gap and second support plate, the second high-pressure large-caliber ball valve is connected with the high-pressure large-caliber ball valve, and described outlet end is communicated with second entrance point becomes a valve body.
2. according to the described high-pressure large-caliber duplex gathering ball valve of claim 1, it is characterized in that: the described outlet end and second entrance point are one-body molded.
3. according to the described high-pressure large-caliber duplex gathering ball valve of claim 1, it is characterized in that: be provided with valve seat bearing ring and valve seat between described spheroid and valve gap, the valve body, be provided with the second valve seat bearing ring and second valve seat between described second spheroid and second valve gap, the valve body equally; Simultaneously, between valve seat bearing ring and valve gap, O-ring seals is arranged, between the second valve seat bearing ring and second valve gap, second O-ring seals is arranged.
4. according to the described high-pressure large-caliber duplex gathering ball valve of claim 3, it is characterized in that: the external diameter of O-ring seals is greater than the sealed diameter of valve seat, and the sealed diameter of valve seat is greater than the sealed diameter of valve seat bearing ring and the sealing of O-ring seals internal diameter simultaneously.
5. according to the described high-pressure large-caliber duplex gathering ball valve of claim 4, it is characterized in that: sealing surface is provided with fire-protection ring between described valve seat bearing ring and the valve gap, and sealing surface also is provided with fire-protection ring between valve seat bearing ring and the valve body; Sealing surface is provided with second fire-protection ring between the second valve seat bearing ring and second valve gap, and sealing surface also is provided with second fire-protection ring between the second valve seat bearing ring and the valve body.
6. according to claim 4 or 5 described high-pressure large-caliber duplex gathering ball valves, it is characterized in that: be provided with anti-static device between spheroid and support plate, the valve rod; Be provided with second anti-static device between second spheroid and second support plate, second valve rod.
CN2010201778826U 2010-05-04 2010-05-04 High-pressure heavy-caliber double gathering ball valve CN201651397U (en)

Priority Applications (1)

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Application Number Priority Date Filing Date Title
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101900212A (en) * 2010-05-04 2010-12-01 四川赛尔阀门制造有限公司 High-pressure large-caliber duplex gathering ball valve
CN102758933A (en) * 2012-07-18 2012-10-31 嘉士凯(苏州)阀门配件有限公司 Ball valve for high temperature and high pressure
CN103335160A (en) * 2013-07-12 2013-10-02 上海市通用机械技术研究所有限公司 Fluid stop valve
CN103398189A (en) * 2013-08-13 2013-11-20 天津诺威流体控制科技有限公司 Subsea valve
CN110686094A (en) * 2019-10-30 2020-01-14 广船国际有限公司 Ball valve

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101900212A (en) * 2010-05-04 2010-12-01 四川赛尔阀门制造有限公司 High-pressure large-caliber duplex gathering ball valve
CN102758933A (en) * 2012-07-18 2012-10-31 嘉士凯(苏州)阀门配件有限公司 Ball valve for high temperature and high pressure
CN103335160A (en) * 2013-07-12 2013-10-02 上海市通用机械技术研究所有限公司 Fluid stop valve
CN103335160B (en) * 2013-07-12 2016-03-30 上海市通用机械技术研究所有限公司 A kind of fluid shut off valve
CN103398189A (en) * 2013-08-13 2013-11-20 天津诺威流体控制科技有限公司 Subsea valve
CN110686094A (en) * 2019-10-30 2020-01-14 广船国际有限公司 Ball valve

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GR01 Patent grant
C17 Cessation of patent right
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20101124

Termination date: 20120504