CN201382193Y - Valve seat for ball valve and ball valve using same - Google Patents
Valve seat for ball valve and ball valve using same Download PDFInfo
- Publication number
- CN201382193Y CN201382193Y CN200920148741U CN200920148741U CN201382193Y CN 201382193 Y CN201382193 Y CN 201382193Y CN 200920148741 U CN200920148741 U CN 200920148741U CN 200920148741 U CN200920148741 U CN 200920148741U CN 201382193 Y CN201382193 Y CN 201382193Y
- Authority
- CN
- China
- Prior art keywords
- valve seat
- valve
- axial
- annular
- ball valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Taps Or Cocks (AREA)
Abstract
The utility model discloses a valve seat for a ball valve. The valve seat is annular and comprises a first axial annular end surface, a second axial annular end surface, a radial inner surface and a radial outer surface. The radial inner surface comprises a contacting surface contacted with a ball body as a start-stop component. The valve seat has at least one of the following structural characteristics: a. an annular projection is formed on the first axial annular end surface and is positioned between the radial inner end and the radial outer end of the first axial annular end surface; and b. an annular groove extending inwards from the radial outer surface in a radial direction is formed on the radial outer surface, the annular groove comprises a first wall surface positioned on one side of the first axial annular end surface and a second wall surface positioned on one side of the second axial annular end surface, an annular skirt part is formed between the contact surface positioned on the radial inner surface and contacted with the ball body and the second wall surface of the annular groove, a penetration channel is formed on the annular skirt part, and a fluid in the penetration channel is communicated with the space at the two sides in an axial direction of the annular skirt part.
Description
Technical field
The utility model relates to a kind of ball valve that is used for the valve seat of ball valve and adopts this valve seat.
Background technique
Ball valve is widely used in various fluid delivery systems such as in the refrigeration system.Except other index, the quality of leaking performance in ball valve is anti-is to estimate an important indicator of its quality good or not.Though the fluid that leaks in the ball valve does not flow to the outside, its harm is also very important.If it is leak in ball valve takes place, light then influence the quality of product, heavy then owing to seepage leads to serious accident.
Fig. 1 is a perspective view, and it is the common structure that example illustrates ball valve with the ball valve that is used for refrigeration system.As shown in Figure 1, ball valve 100 comprises valve body 2, the urosome 1 that is connected with valve body one end, be arranged in the valve pocket, as the spheroid 5 of open-shut device, in order to drive the valve rod 3 that spheroid rotates and to be arranged on the valve seat 4 that is positioned at spheroid 5 axial two ends in the valve pocket, wherein valve seat 4 is mainly born the interior leakage sealing function of ball valve.Be formed with groove 7 and penetration hole 8 on the spheroid 5, and that an end of valve rod 3 is formed with is suitable and be plugged in shank in this groove with groove 7.In the operating process of ball valve, drive spheroid 5 by valve rod 3, make it between closed position and open position, to switch.
Fig. 2 is a partial cross sectional views, specifically illustrates valve seat 4 and the configuration structure of spheroid 5 in valve pocket.As Fig. 2 in detail shown in, spheroid 5 two supports in the time of on spheroid 5 is in the closed position, leaks in realizing by means of fitting tightly between spheroid 5 and the valve seat 4 and seal on valve seat 4.
In order to realize the sealing between spheroid 5 and the valve seat 4, the scheme that is adopted in traditional ball valve design is: under the effect of original state pretightening force and/or hydrodynamic pressure, spheroid and valve seat are compressed, and make valve seat produce plastic deformation and reach sealing.Its sealing effect depends on valve seat under the effect of hydrodynamic pressure and/or pretightening force, can compensate the degree of spheroid out of roundness and spherome surface and/or valve base surface nao-and micro relief.Therefore traditional way is, in order to obtain better seal, and makes valve seat produce bigger plastic deformation, and the negative effect that brings thus is to produce bigger running torsion thus.And follow the ball valve lengthening of running time, and valve seat produces wearing and tearing, and interior leakage sealing effect is variation gradually, so that loses efficacy.
In conventional art, the valve seat that is adopted is the rigid seal valve seat.Fig. 3 illustrates that the spheroid lower end does not have fixed bearing and the ball valve that is provided with ralocatable mode.When ball valve is closed, under the effect of entry end pressure medium, spheroid will leave the entry end seal valve seat and produce certain displacement amount δ, and be pressed on and make it to produce distortion δ 2 on the outlet end seal valve seat, thereby medium is stopped at the outlet end seal valve seat.Be that in fact Float ball valve brings into play seal action by the outlet end seal valve seat when closing, and keep a very little flying height δ 1 between entry end seal valve seat and spheroid, therefore do not produce seal action basically.
When ball valve during in the work of little aperture, as shown in Figure 4, because the pressure differential deltap p of entry end and outlet end, make the top of inlet side valve seat produce deflection (for convenience of explanation, the deflection that produces is in the drawings by exaggerative), in pressure differential deltap p when fluctuation, just cause the vibration of valve easily, the reason of the bivalve seat globe valve is not used in basically little aperture work that Here it is.
In order to guarantee the sealing of ball valve when the medium working pressure is low, must form certain pretension specific pressure between spheroid and the seal valve seat.In the rigid seal valve seat, the reliability of ball valve work and working life, depend on the pre compressed magnitude of correct selection seal valve seat.The pre compressed magnitude deficiency can not guarantee the low pressure seal of ball valve; And if pre compressed magnitude is excessive, then can cause the friction torque between spheroid and the seal valve seat to increase, thereby influence the performance of ball valve, and may cause the plastic deformation of seal valve seat, cause seal failure.From the above, the big young pathbreaker of rigid seal valve seat pre compressed magnitude directly has influence on the reliability of leaking sealing in the ball valve.In addition, the machining error of valve seat also can have influence on the effect of sealing, so in the rigid seal seat design and in using, reasonably assembling is the key that obtains excellent sealing with adjusting.Simultaneously, in use, after the seal valve seat wearing and tearing, the self-regulation ability of pretension specific pressure is very poor or almost do not have, so the working life of rigid seal valve seat ball valve is shorter relatively.
The model utility content
As mentioned above, in traditional ball valve design, leak sealing in realizing reliably, the scheme that is adopted is: under the effect of original state pretightening force or hydrodynamic pressure, spheroid and valve seat are compressed, and make valve seat generation plastic deformation and reach sealing.Yet, adopting traditional anti-interior encapsulation scheme of leaking, it can not solve anti-interior contradiction of leaking between sealing effect and the ball valve performance well; And traditional ball valve do not have the dynamic compensation function of internal leakage sealing, therefore follows the ball valve lengthening of running time, and valve seat produces wearing and tearing, and interior leakage sealing effect is variation so that lost efficacy gradually.
Therefore, the demand that has the long ball valve of, good seal performance low, life-span in the industry to cost.
For this reason, the purpose of this utility model provides a kind of ball seat, and it can realize good interior leakage sealing effect and long service life.
Another purpose of the present utility model provides a kind of ball seat, and it can make full use of hydrodynamic pressure self and improve the interior sealing of leaking.
Another purpose of the present utility model provides a kind of ball seat, and it can internally leak and be sealed into the compensation of action attitude, and then improves sealing effect.
Another purpose of the present utility model provides a kind of ball valve, and it has good interior leakage sealing effect, can reduce the running moment of torsion of ball valve, and long service life, be convenient to the operation.
For achieving the above object,, provide a kind of valve seat that is used for ball valve according to the utility model first aspect, this valve seat ringwise and comprise:
The first axial annular end face;
The second axial annular end face;
Inner radial surface; And
Radially-outer surface;
Wherein, described inner radial surface comprises and is suitable for the contact surface that contacts with spheroid as open-shut device, and wherein said valve seat has at least one in the following structure characteristic:
A. the described first axial annular end face is provided with annular projection, and this annular projection is between the radial inner end and radial outer end of the described first axial annular end face;
B. be formed with the circular groove that radially extends internally from described radially-outer surface on the described radially-outer surface, this circular groove comprises first wall that is positioned at first axial annular end face one side and is positioned at second wall of second axial annular end face one side, between second wall that is suitable for the described contact surface that contacts with spheroid and described circular groove of described inner radial surface, form ring-shaped skirt, on described ring-shaped skirt, be formed with penetrating via, the space of the axial both sides of the described ring-shaped skirt of this penetrating via fluid communication.
Preferably, described penetrating via is form on the radially-outer surface of described ring-shaped skirt axially grooved.
Preferably, form ring-shaped step at the radially-outer surface and the handing-over position between the second axial annular end face of described ring-shaped skirt, the radial dimension of this ring-shaped step is more than or equal to the radial depth of described fluting.
Preferably, described valve seat is made by pure polytetrafluoroethylene, and this polytetrafluoroethylene is PTFE1700 preferably.
Preferably, the cross section semicircular in shape of described annular projection.
Preferably, second wall of described circular groove from radially inner side to radial outside towards the described second axial annular end slope.
Preferably, the contact surface that contacts with spheroid of being suitable for of described inner radial surface is made of first conical surface and second conical surface that is connected in first conical surface.
Preferably, on first axial end of described valve seat, be formed with annular groove in the annular projection radially inner side, elastic element is fitted in this annular groove, makes the part that is positioned at the annular groove both sides of valve seat open tendency outside forming under the elastic force effect of elastic element.
Preferably, described elastic element is a leaf spring.
Preferably, described annular groove cross section takes the shape of the letter U or V-arrangement, and described leaf spring cross section is corresponding U-shaped or V-arrangement.
Preferably, described annular groove from radially inner side to radial outside towards the described second axial annular end slope.
Preferably, described leaf spring also comprise be positioned at radially inner side, substantially with the axial vertical ring plate part of valve seat, and be formed with the lower dent that leads to described annular groove on first axial end of described valve seat, described ring plate partly is fitted in this lower dent.
According to the utility model on the other hand, provide a kind of ball valve, comprised as the spheroid of open-shut device and the valve seat that is arranged on these spheroid both sides, wherein, at least one valve seat in the described valve seat is according to the described valve seat of the utility model first aspect.
Preferably, described ball valve is the ball valve that is used for refrigeration system.
Adopt the technical solution of the utility model, can make full use of hydrodynamic pressure self and improve the interior sealing of leaking; By adopting the hyperstatic structural design in valve seat shirt rim, the increase of valve seat rigidity when helping the system pressure fluctuation; When the internal system specific pressure changed, ball valve of the present utility model had dynamic compensation function and can regulate seal pattern adaptively, and interior leakage sealing is stable, long service life; And can realize that system's releasing pressure automatically, running moment of torsion are less and cost is low.
Description of drawings
Below in conjunction with drawings and Examples the utility model is described in further detail, wherein
Fig. 1 is a perspective view, and it is the common structure that example illustrates ball valve with the ball valve that is used for refrigeration system;
Fig. 2 is a partial cross sectional views, illustrates valve seat and the spheroid configuration structure in valve pocket;
Fig. 3 is a partial cross sectional views, illustrates that the spheroid lower end does not have fixed bearing and with the conventional ball valve ralocatable mode setting, that be equipped with the rigidity valve seat;
Fig. 4 illustrates the situation of ball valve when little aperture is worked among Fig. 3;
Fig. 5 A and 5B are the axial section views of ball valve, illustrate the standard-sized sheet working state and the complete shut-down working state of ball valve respectively;
Fig. 6 A is the perspective view according to the ball valve sealing valve seat with dynamic compensation function of the utility model first preferred embodiment;
Fig. 6 B is the axial section view of the valve seat shown in Fig. 6 A;
Fig. 6 C is the partial enlarged view of part A among Fig. 6 B;
Fig. 7 A is a partial cross sectional views, illustrates the principle of leaking sealing in the utility model valve seat improves under the ball valve entry end situation equal with the outlet end hydrodynamic pressure;
Fig. 7 B is a schematic representation, illustrates valve seat under fluid pressure action, and valve seat is the bending deflection situation that fulcrum produces with hard fulcrum;
Fig. 7 C is the zoomed-in view of part B among Fig. 7 A, illustrate before assembling and the hard fulcrum in assembling back and urosome end face between different contact conditions;
Fig. 8 A is the view that is similar to Fig. 7 A, illustrates the utility model valve seat and improves interior principle of leaking sealing;
Fig. 8 B is a schematic representation, illustrates valve seat under fluid pressure action, and valve seat is the distortion situation that fulcrum produces with hard fulcrum;
Fig. 9 A illustrates under the situation that hard fulcrum has broken away from urosome, and spheroid concerns with respect to the position between the valve body with respect to valve seat and valve seat;
Fig. 9 B illustrates under the situation that hard fulcrum has broken away from urosome, leaks the principle of sealing in the utility model valve seat improves;
Fig. 9 C is a schematic representation, illustrates valve seat under fluid pressure action, the distortion situation that the valve seat each several part produces;
Figure 10 A is a partial cross sectional views, illustrates the ball valve sealing valve seat with dynamic compensation function according to the utility model second preferred embodiment; And
Figure 10 B-10F is a partial cross sectional views, illustrates the various remodeling embodiments of elastic element respectively.
Embodiment
In conjunction with every preferred embodiment the utility model is described in detail below with reference to accompanying drawings.At this, should be pointed out that embodiment of the present utility model only is exemplary, it only is used to illustrate principle of the present utility model and unrestricted the utility model.
In the following description, identical or similar structure member will be given identical reference character in institute's drawings attached.
For ball valve, structurally finalize the design and almost do not have room for improvement as the spheroid 5 of open-shut device.Therefore, the structure of valve seat and Manufacturing material play crucial effects to the interior leakage sealing effect of ball valve.Therefore, the utility model aims to provide selecting for use of a kind of improved valve seat construction and proportioning valve seat material, realizes a kind of valve seat that leaks sealing effect in good that has, and and then provides a kind of ball valve that leaks sealing effect in good that has.
Ball valve is in two kinds of working staties usually: standard-sized sheet working state and complete shut-down working state, Fig. 5 A and 5B illustrate this two kinds of working staties.Except these two kinds of working staties, if ball valve is when the work of little aperture, because the still old low flow rate liquid in ball valve inside, so leak the problem of sealing in not existing.
At first referring to Fig. 6 A-6C, wherein Fig. 6 A is the perspective view according to the ball valve sealing valve seat with dynamic compensation function of the utility model first preferred embodiment; Fig. 6 B is the axial section view of the valve seat shown in Fig. 6 A; And Fig. 6 C is the partial enlarged view of part A among Fig. 6 B.
As the material of making the utility model valve seat, can select PTFE, rubber, carbon fiber, asbestos, graphite, ceramic fiber for use, be suitable for the material of this purpose such as metals such as cobalt base alloy and other, wherein polytetrafluoroethylene is the comparatively preferable material that is used to make valve seat.When ball valve is used as refrigerating ball valve, preferably select pure polytetrafluoroethylene, for example PTFE1700 etc. for use, because it is corrosion-resistant, good with the refrigeration agent compatibility, surface friction drag is low and good seal performance.
Describe structure in detail below with reference to Fig. 6 A-6C according to the ball valve sealing valve seat with dynamic compensation function of the utility model first preferred embodiment.
Shown in Fig. 6 A-6C, with the valve seat of reference character 4 expression axisymmetricly annular shape on the whole, be included in superposed first axial end 11 among the figure, be positioned at second axial end 12, inner radial surface 13 and the radially-outer surface 14 of bottom.Inner radial surface 13 comprises the cylndrical surface 131 adjacent with first axial end 11, second conical surface 133 that is connected in first conical surface 132 of cylndrical surface 131 and is connected in first conical surface 132, and the combining surface that is made of first conical surface 132 and second conical surface 133 is as the contact surface that contacts with spheroid 5.In illustrated embodiment, combining surface comprises two conical surfaces, but the Professional visitors be it is evident that, combining surface is also nonessential to be made of two conical surfaces, and the combining surface that is made of three or more conical surfaces is feasible equally.In addition, contact surface also is not limited to be made of some conical surfaces, and it also can be made of single curved surface, or forms the compound curved surface that is made of some curved surfaces.
As shown in the figure, be formed with annular projection 111 on first axial end 11, this annular projection can be used as balance pivot (hereinafter will be described in detail), and is called hard fulcrum hereinafter.The cross section semicircular in shape of hard fulcrum, its radius R is not limited to specific value, but (leakage quantity, the size of ball valve running torsion, the working pressure of system etc. in initial) are chosen according to actual needs.With the refrigeration system is example, and when working pressure was 20bar, the value of R was preferably about 0.3mm.Though the cross section of hard fulcrum is semicircular in shape preferably, other sectional shape also can adopt such as half elliptic and other curve form.Hard fulcrum is not limited to specific value apart from the size of the ratio L1/L of the radial distance L between the radial distance L1 between the cylndrical surface 131 and cylndrical surface 131 and the radially-outer surface 14, determine but can for example design initial interior leakage quantity, the size of ball valve running torsion and the size of internal system pressure etc. according to concrete application, therefore its preferred value is different because of concrete application, and the value of selecting for use is L1/L=1/3 in claimant's test products.
Be formed with circular groove 141 on radially-outer surface 14, the cross section of circular groove 141 is tapered, and its cross-sectional dimension narrows down gradually towards the axle center of valve seat 4.In illustrated embodiment, circular groove 141 comprises first wall 145 adjacent with first axial end 11 and second wall 146 adjacent with second axial end 12, and bottom surface 147.Wherein, first wall 145 is arranged essentially parallel to first axial end 11, and second wall 146 is with respect to first wall 145 angle beta that tilts, and first wall 145 and second wall 146 interconnect via bottom surface 147.Preferably, bottom surface 147 is an arc-shaped curved surface, can reduce stress thus and concentrate.Wherein, angle beta is not special to be limited, and considers Economics of Processing, can for example select the angle about 45 degree for use, and first wall 145 also can be not parallel to first axial end 11.In addition, first wall 145 and second wall 146 also are not limited to the plane, and they also can be curved surfaces.By on the radially-outer surface 14 of valve seat 4, forming circular groove 141, define the ring-shaped skirt 9 between the contact surface that contacts with spheroid 5 and second wall 146.
In addition, shown in Fig. 6 A-6C, be formed with a fluting 91 on the radially-outer surface of ring-shaped skirt 9, this fluting runs through ring-shaped skirt 9 vertically and has radial depth ξ, and the function of this fluting will be addressed hereinafter.The size of fluting 91 radial depth ξ is not limited to specific numerical value, can determine that the radial depth ξ that selects for use usually is of a size of 0.3mm-1mm according to the specific pressure of the radial dimension of valve seat 4, seat material, system etc.Here the number that it may be noted that fluting is not limited to one, also can be two or more along circumferential spaced apart setting, and notching construction also is not limited to specific forms, as long as it can obtain expectation function of the present utility model.
As a kind of selection scheme, can form a ring-shaped step 92 at the radially-outer surface 14 of valve seat 4 and the handing-over position between second axial surface 12, the radial dimension of this step is more than or equal to the radial depth ξ of fluting, shown in Fig. 6 B and 6C.
Summary is got up, and the main structure of the utility model first embodiment's valve seat 4 is characterized by the following aspects:
Feature a: be formed with ring-shaped skirt 9, this ring-shaped skirt 9 has the sealing compensation function;
Feature b: on the radially-outer surface of ring-shaped skirt 9, be formed with the fluting 91 that axially runs through, this fluting allows fluid to flow out space that circular groove 141 limited and realizes that inside rushes down pressure, and allow fluid to flow into the space that circular groove 141 is limited, thereby under dynamic pressure, form the rigidity that statically indeterminate structure strengthens valve seat 4 on the one hand, and the sealing compensation function that realizes ring-shaped skirt 9 on the other hand by means of hydrodynamic pressure;
Feature c: on first axial end 11, be formed with hard fulcrum, leak the dynamic compensation of sealing in being used for, guarantee that the dynamic pressure state strengthens sealing down.
Sealing principle below in conjunction with accompanying drawing 7-9 explanation the utility model ball valve.
Ball valve operates mainly under following three kinds of situations (specifically referring to Fig. 2):
P1＝P2
P1＞P2
P1＜P2
1.P1=P2 the time
See also Fig. 7 A-7C, wherein Fig. 7 A is a partial cross sectional views, illustrates under the ball valve entry end situation equal with the outlet end hydrodynamic pressure, leaks sealing effect in how the utility model valve seat improves; Fig. 7 B is a schematic representation, illustrates valve seat 4 under fluid pressure action, and valve seat 4 is the bending deflection situation that fulcrum produces with hard fulcrum; And Fig. 7 C illustrates before assembling and the hard fulcrum in assembling back and urosome 1 end face between contact condition: state, assembling back generally pressured state and overvoltage condition before the assembling.
Shown in Fig. 7 A,, under the assembled state of ball valve, between first axial end 11 of the axial end 20 of urosome 1 and valve seat 4, produced gap delta because first axial end 11 of valve seat 4 is provided with hard fulcrum 111.Therefore, the pressure fluid of entry end enters the space between first axial end 11 of the axial end 20 of urosome 1 and valve seat 4, thereby hydrodynamic pressure P1 acts on first axial end 11 of valve seat 4 (referring to Fig. 7 A), forcing valve seat 4 is that fulcrum rotates (referring to Fig. 7 B) with hard fulcrum, make the part that is positioned at hard fulcrum radially inner side further push spheroid 5, strengthened the interior leakage sealing of ball valve.
As described in top background technique part, the interior leakage sealing of conventional ball valve is decided by the elasto plastic deformation of valve seat 4 with the initial compression generation of spheroid 5.And employing the utility model by the design of hard fulcrum, has strengthened the interior leakage sealing effect of ball valve.Therefore, on the one hand, under the certain situation of the plastic deformation that the initial compression of valve seat 4 and spheroid 5 produces, adopt technical solutions of the utility model to leak sealing effect in can significantly improving; And on the other hand, obtaining and leaking under the situation of sealing effect in conventional ball valve is identical, can reduce the amount of elasto plastic deformation of the initial compression generation of valve seat 4 and spheroid 5, thereby to reduce the running moment of torsion of ball valve.
In addition, adopt the hard fulcrum be designed to arc, when it during in overcompression, can on the overcompression inclined-plane, produce and compress the component of urosome 1, thereby can reduce the vibration of valve seat 4 in the middle of running, reduce the operation noise then, shown in Fig. 7 C.
2.P1＞P2
Under the situation of P1＞P2, there are two kinds of situations:
(1) the hard fulcrum of entry end does not have and the urosome disengaging; And
(2) the hard fulcrum of entry end breaks away from urosome.
At first the situation that the hard fulcrum of entry end does not have and urosome 1 breaks away from is described below with reference to Fig. 8 A-8B.Fig. 8 category-A is similar to Fig. 7 A, illustrates the utility model valve seat 4 and how to improve the interior sealing effect that leaks; Fig. 8 B is a schematic representation, illustrates valve seat 4 under fluid pressure action, and valve seat 4 is the distortion situation that fulcrum produces with hard fulcrum.
Under the situation that the hard fulcrum of entry end does not have and urosome 1 breaks away from, be similar to the situation of P1=P2 in the above explanation, hydrodynamic pressure P1 acts on first axial end 11 of valve seat 4 (referring to Fig. 8 A), make that the part of the hard fulcrum of being positioned at of valve seat 4 both sides is that fulcrum rotates (referring to Fig. 8 B) with hard fulcrum, force the part of the hard fulcrum radially inner side of being positioned at of valve seat 4 further to push spheroid 5, strengthened the interior leakage sealing of ball valve.
The situation that has broken away from urosome 1 below with reference to the hard fulcrum of Fig. 9 A-9C explanation entry end.Fig. 9 A illustrate hard fulcrum and the situation lower sphere 5 that breaks away from of urosome 1 concern with respect to the position between the valve body with respect to valve seat 4 and valve seat 4; Fig. 9 B illustrates valve seat 4 of the present utility model and how to improve the interior sealing effect that leaks; And Fig. 9 C illustrates valve seat 4 under fluid pressure action, the distortion situation that valve seat 4 each several parts produce.
Under the situation that the hard fulcrum of entry end has broken away from urosome 1, produce between urosome 1 and the valve seat 4 gap and/or between spheroid 5 and valve seat 4 generation gap delta 1, shown in Fig. 9 A.System entry end pressure fluid Q enters valve pocket 6 via the gap delta 1 of gap that produces between urosome 1 and the valve seat 4 and/or generation between spheroid 5 and valve seat 4, and the pressure fluid extruding that enters valve pocket 6 exports the end valve seat, forms inlet end valve seat and breaks away from and the form of outlet end valve base sealing.That is to say, in this case, leak sealing in the ball valve and bear by the outlet end valve seat.
Shown in Fig. 9 B is concrete, the system entry end pressure fluid Q that enters valve pocket 6 enters the space that circular groove 141 is limited via the fluting 91 of the ring-shaped skirt 9 of outlet end valve seat, and enters first wall 145 and second wall 146 (referring to Fig. 9 B) that pressure fluid in the space that circular groove 141 limited acts on circular groove 141.The pressure that acts on second wall 146 of circular groove 141 forces ring-shaped skirt 9 to produce distortion; And the pressure that acts on first wall 145 of circular groove 141 forces hard fulcrum more closely to be posted by the axial end 20 of urosome 1, and force valve seat be positioned at hard fulcrum radially the part of both sides rotate (referring to Fig. 9 C) around hard fulcrum.As its result, make the contact surface that contacts with spheroid 5 of valve seat 4 more closely be posted by spheroid 5, form stronger interior leakage sealability thus.
Simultaneously, because the project organization of ring-shaped skirt 9 is general statically indeterminate structures, according to the strut buckling condition, at this moment the rigidity of valve seat increases.
3.P1 during＜P2
Under the situation of P1＜P2, its effect is equivalent to the situation of P1＞P2, repeats no more here.
Below in conjunction with the ball valve sealing valve seat with dynamic compensation function of accompanying drawing 10A-10F explanation according to the utility model second preferred embodiment.The structure of the ball seat with dynamic compensation function of the general structure of the ball seat with dynamic compensation function of the utility model second preferred embodiment and the utility model first preferred embodiment is basic identical, and difference is that it also is provided with the rigidity that elastic element improves valve seat.
For ball seat can more worked under the high specific pressure,, can in valve seat, set up elastic element for example to remedy by the rigidity deficiency of the valve seat of making such as pure polytetrafluoroethylmaterial materials such as PTFE 1700.Figure 10 A-10F illustrates the valve seat that is provided with elastic element.
Shown in Figure 10 A, on first axial end 11 of valve seat 4, be formed with an annular groove 40 in hard fulcrum inboard, annular groove 40 comprises pair of sidewalls opposite each other and diapire; And the spring 501 of an annular leaf spring form is fitted in this annular groove.The cross section of annular leaf spring 501 takes the shape of the letter U, and comprises two opposed sidepieces 51 and the bottom 52 that connects two sidepieces 51.Under annular leaf spring 501 was installed in situation in the annular groove 40, the bottom 52 of annular leaf spring 501 contacted with the diapire of annular groove 40, and the sidepiece 51 of annular leaf spring 501 elasticity are pressured in the sidewall of annular groove 40 respectively.Thus, make the part that is positioned at annular groove 40 both sides of valve seat 4 open tendency outside under the effect of the elastic force of annular leaf spring 501, forming.
As a kind of remodeling of elastic element, can also adopt the annular leaf spring 502 shown in Figure 10 B.Annular leaf spring 502 shown in Figure 10 B is that with the difference of the annular leaf spring 501 shown in Figure 10 A the annular leaf spring 502 shown in Figure 10 B also comprises the ring plate part 53 that is connected with the sidepiece 51 that is positioned at radially inner side.For suitable, on first axial end 11 of valve seat 4, be formed with the recessed portion 60 that leads to annular groove with the annular leaf spring 502 of this kind form.
In addition, except above-described annular leaf spring, can also adopt the annular leaf spring of other various ways, Figure 10 C-F illustrates some other examples of the multi-form annular groove that can adopt and the annular leaf spring 503,504,505,506 suitable with it.
Therefore, by in valve seat, setting up elastic element, except the rigidity deficiency that for example can remedy the valve seat of making by teflon, also can compensate the hypodynamic shortcoming of making by for example single polytetrafluoroethylmaterial material of sealing seat energy of deformation, the reliability and the working life of improving ball valve sealing thus by the elastic force of elastic element.Under the lower situation of fluid medium pressure, by the stronger elastic deformability of spring, make the valve seat of for example making open tendency outside under the effect of elastic element elastic force, forming and produce pre-compression force by teflon, the position that contacts with spheroid of valve seat is compressed to spheroid, and compensation medium pressure reduces the seal pressure deficiency that causes.As long as distortion is in the elastic force scope of elastic element, can guarantee the reliable sealing of ball valve under the lower pressure condition.
According to above explanation as can be seen, adopt valve seat of the present utility model, the sealability of valve seat and performance, no longer rely on or rely on separately by seal valve seat being carried out precompression to make it to produce the initial deformation amount and adjust, and can adjust by the specific pressure of ball valve both sides or the elastic element that is equipped in the valve seat.The valve seat of valve seat of the present utility model and band elastic element also can compensate the pretension specific pressure by the elastic force of hydrodynamic pressure P and elastic element except that can obtaining necessary pre compressed magnitude.Therefore, the sealability of ball valve be improved and working life longer relatively.
The Professional visitors be it is evident that valve seat of the present utility model includes but not limited to be used in the refrigerating ball valve of refrigeration system applicable to the ball valve of any kind.
Below in conjunction with the accompanying drawings and embodiments the utility model is illustrated, but those skilled in the art are to be understood that, the foregoing description only is exemplary and nonrestrictive, under the condition that does not deviate from spirit and scope of the present utility model, can make all improvement to the foregoing description.
Such as, in the above-described embodiments, in order to make fluid can pass in and out the space that circular groove 141 is limited, on the radially-outer surface of ring-shaped skirt 9, be formed with fluting 91, run through through hole and replace slotting but also can between second axial end 12 of second wall 146 of circular groove 141 and valve seat 4, form.
In addition, in the above-described embodiments, valve seat be provided with annular projection 111 and circular groove 141 both, but this is not to realize that the model utility purpose is necessary.Also the structure that can adopt is, in annular projection 111 and the circular groove 141 only is set on the valve seat.
And as ball valve, it can only adopt valve seat of the present utility model at an axial end portion place and adopt other valve seat at another axial end portion place; Perhaps all adopt valve seat of the present utility model at place, axial two ends.
Claims (15)
1. valve seat that is used for ball valve, this valve seat be ringwise and comprise:
The first axial annular end face;
The second axial annular end face;
Inner radial surface; And
Radially-outer surface;
Wherein, described inner radial surface comprises and is suitable for the contact surface that contacts with spheroid as open-shut device, and wherein said valve seat has at least one in the following structure characteristic:
A. the described first axial annular end face is provided with annular projection, and this annular projection is between the radial inner end and radial outer end of the described first axial annular end face;
B. be formed with the circular groove that radially extends internally from described radially-outer surface on the described radially-outer surface, this circular groove comprises first wall that is positioned at first axial annular end face one side and is positioned at second wall of second axial annular end face one side, between second wall that is suitable for the described contact surface that contacts with spheroid and described circular groove of described inner radial surface, form ring-shaped skirt, on described ring-shaped skirt, be formed with penetrating via, the space of the axial both sides of the described ring-shaped skirt of this penetrating via fluid communication.
2. valve seat as claimed in claim 1 is characterized in that, described penetrating via is form on the radially-outer surface of described ring-shaped skirt axially grooved.
3. valve seat as claimed in claim 2 is characterized in that, forms ring-shaped step at the radially-outer surface and the handing-over position between the second axial annular end face of described ring-shaped skirt, and the radial dimension of this ring-shaped step is more than or equal to the radial depth of described fluting.
4. valve seat as claimed in claim 1 is characterized in that described valve seat is made by pure polytetrafluoroethylene.
5. valve seat as claimed in claim 4 is characterized in that, described pure polytetrafluoroethylene is PTFE1700.
6. valve seat as claimed in claim 1 is characterized in that, the cross section semicircular in shape of described annular projection.
7. valve seat as claimed in claim 1 is characterized in that, second wall of described circular groove from radially inner side to radial outside towards the described second axial annular end slope.
8. valve seat as claimed in claim 1 is characterized in that, the contact surface that being suitable for of described inner radial surface contacts with spheroid is made of first conical surface and second conical surface that is connected in first conical surface.
9. valve seat as claimed in claim 1, it is characterized in that, on the first axial annular end face of described valve seat, be formed with annular groove in the radially inner side of annular projection, elastic element is fitted in this annular groove, makes the part that is positioned at the annular groove both sides of valve seat open tendency outside forming under the elastic force effect of elastic element.
10. valve seat as claimed in claim 9 is characterized in that, described elastic element is a leaf spring.
11. valve seat as claimed in claim 10 is characterized in that, described annular groove cross section takes the shape of the letter U or V-arrangement, and described leaf spring cross section is corresponding U-shaped or V-arrangement.
12. valve seat as claimed in claim 11 is characterized in that, described annular groove from radially inner side to radial outside towards the described second axial annular end slope.
13. valve seat as claimed in claim 11, it is characterized in that, described leaf spring also comprise be positioned at radially inner side, substantially with the axial vertical ring plate part of valve seat, and being formed with the lower dent that leads to described annular groove on the first axial annular end face of described valve seat, described ring plate partly is fitted in this lower dent.
14. a ball valve comprises as the spheroid of open-shut device and the valve seat that is arranged on these spheroid both sides, wherein, at least one valve seat in the described valve seat is each described valve seat among the claim 1-13.
15. ball valve as claimed in claim 14 is characterized in that, described ball valve is the ball valve that is used for refrigeration system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200920148741U CN201382193Y (en) | 2009-03-27 | 2009-03-27 | Valve seat for ball valve and ball valve using same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200920148741U CN201382193Y (en) | 2009-03-27 | 2009-03-27 | Valve seat for ball valve and ball valve using same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201382193Y true CN201382193Y (en) | 2010-01-13 |
Family
ID=41525668
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200920148741U Expired - Lifetime CN201382193Y (en) | 2009-03-27 | 2009-03-27 | Valve seat for ball valve and ball valve using same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201382193Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101949458A (en) * | 2010-08-16 | 2011-01-19 | 宣达实业集团有限公司 | Ball valve |
| CN101846208B (en) * | 2009-03-27 | 2012-07-18 | 丹佛斯（天津）有限公司 | Valve seat for spherical valve and ball valve using same |
-
2009
- 2009-03-27 CN CN200920148741U patent/CN201382193Y/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101846208B (en) * | 2009-03-27 | 2012-07-18 | 丹佛斯（天津）有限公司 | Valve seat for spherical valve and ball valve using same |
| CN101949458A (en) * | 2010-08-16 | 2011-01-19 | 宣达实业集团有限公司 | Ball valve |
| CN101949458B (en) * | 2010-08-16 | 2012-01-25 | 宣达实业集团有限公司 | Ball valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2933540A1 (en) | Electronic expansion valve | |
| CN201953991U (en) | C-shaped sealing ring | |
| CN201382193Y (en) | Valve seat for ball valve and ball valve using same | |
| CN101846208B (en) | Valve seat for spherical valve and ball valve using same | |
| CN208237076U (en) | A kind of axis sealing combination device | |
| CN206299844U (en) | A kind of high-pressure check valve of low leakage | |
| CN201954002U (en) | Cassette type oil seal | |
| CN210196563U (en) | Eccentric micro-pressure loss check valve | |
| CN211574378U (en) | Electromagnetic valve | |
| CN205504053U (en) | Sealed valve holder structure of elasticity of fixed ball valve | |
| CN210716072U (en) | Fixed ball valve | |
| CN113074275B (en) | Electromagnetic valve | |
| CN210461693U (en) | Wide-face double-spring universal plug seal | |
| CN208281547U (en) | valve seat | |
| CN220134706U (en) | Pressure relief valve and air conditioning system | |
| CN113757380B (en) | U-shaped low damping sealing ring for double-acting shaft | |
| CN201373129Y (en) | Sealing device and valve | |
| CN218817805U (en) | Hydraulic stop structure used in shock absorber | |
| CN210034419U (en) | Shaft diameter upstream pumping sealing structure | |
| CN210978585U (en) | Double-body type fixed ball valve | |
| CN110966177A (en) | Oil inlet and outlet valve assembly for diaphragm pump and oil inlet and outlet mechanism | |
| CN219809228U (en) | Balance ring sealing structure | |
| CN214662019U (en) | Rotary sealing structure with supporting lip | |
| CN218992456U (en) | Butterfly type butt-clamp double-flap check valve | |
| CN211648808U (en) | Bearing sealing structure for magnetic transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20100113 Effective date of abandoning: 20090327 |
|
| RGAV | Abandon patent right to avoid regrant |