Ball valve

Abstract

A ball valve includes: a main body having a fluid inlet passage, a fluid outlet passage, and a column-shaped depression communicating with these passages and opening upward; a ball including a fluid communication passage and disposed at the column-shaped depression of the main body rotatably about a reference axis; an operating mechanism configured to cause the ball to rotate about the reference axis; a ball seat having a required opening on a peripheral wall thereof and disposed between the ball and the main body; a ball seat presser configured to press the ball seat; and a pressing screw configured to press the ball seat presser downward. The ball is rotated to achieve communication and cutoff. The ball seat has a substantially frustoconical shape having a bottom surface larger than a bottom of the depression in diameter, and an upper surface slightly smaller than the bottom surface in diameter.

Claims

1. A ball valve comprising: a main body having a fluid inlet passage, a fluid outlet passage, and a column-shaped depression communicating with the fluid inlet passage and the fluid outlet passage and opening upward; a ball including a fluid communication passage and being disposed at the column-shaped depression of the main body so as to be rotatable about a reference axis, the ball being rotated about the reference axis to achieve communication and cutoff between the fluid inlet passage and the fluid outlet passage: an operating mechanism configured to cause the ball to rotate about the reference axis; a ball seat provided with a required opening on a peripheral wall thereof and disposed between the ball and the main body; a ball seat presser provided above the ball seat and configured to press the ball seat; and a pressing screw configured to engage an inner periphery of the depression and press the ball seat presser downward, wherein the ball seat has a frustoconical shape having a bottom surface larger than a bottom of the depression in diameter, and an upper surface smaller than the bottom surface in diameter.

2. The ball valve according to claim 1, further comprising a retainer internally fitted into the opening of the ball seat.

3. The ball valve according to claim 1, wherein a spring member is provided between the ball seat presser and the pressing screw.

4. The ball valve according to claim 1, wherein a bottom surface of the depression is subjected to surface roughening.

5. The ball valve according to claim 2, wherein a spring member is provided between the ball seat presser and the pressing screw.

6. The ball valve according to claim 2, wherein a bottom surface of the depression is subjected to surface roughening.

7. The ball valve according to claim 3, wherein a bottom surface of the depression is subjected to surface roughening.

8. The ball valve according to claim 5, wherein a bottom surface of the depression is subjected to surface roughening.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 illustrates an appearance view of a first example of a ball valve according to the invention;

(2) FIGS. 2A to 2C are enlarged views illustrating a ball seat, a ball, and a stem of the ball valve according to the invention;

(3) FIGS. 3A and 3B are partial perspective views of the ball seat used in the ball valve of the invention;

(4) FIG. 4 illustrates surface pressures between the ball seat and the main body of a ball valve of the related art and the ball valve of the invention;

(5) FIG. 5 illustrates surface pressures between the ball seat and the ball of the ball valve in the related art and the ball valve of the invention; and

(6) FIG. 6 illustrates a relationship between a disc spring load and a seal pressure of the ball valve in the related art and the ball valve of the invention.

DETAILED DESCRIPTION OF THE INVENTION

(7) Embodiments of the invention will be described below with reference to the drawings. In the following description, expressions “upper and lower” correspond to “upper and lower” of the drawings. The expressions “upper and lower” are used for the sake of convenience, and the apparatus may be installed upside down or horizontally depending on circumstances.

(8) FIG. 1 illustrates an example of a ball valve 1 of the invention. The ball valve 1 is provided with a main body 10. The main body includes a fluid inlet passage 11, a fluid outlet passage 12, and a depression 13 configured to communicate the fluid inlet passage 11 and the fluid outlet passage 12. The fluid inlet passage 11 and the fluid outlet passage 12 each are provided with a joint member 14.

(9) The depression 13 receives therein a ball 20 configured to cut off and communicate a fluid, and the ball 20 is provided with a fluid communication passage 21 configured to serve as a fluid passage. A bottom surface of the depression 13 is subjected to surface roughening. A ball seat 40 formed of PTFE (polytetrafluoroethylene), which is a synthetic resin material, is disposed between the ball 20 and the main body 10. Leakage of the fluid is prevented by applying a compression load to the ball seat 40 from above.

(10) A retainer 50 formed of a metal into a substantially ring shape is disposed at each of two openings which serve as inlet and outlet of the ball seat 40. The retainer 50 serves to prevent the ball seat 40 from being deformed and blocking the passage and is made of stainless steel. A stem 22 continuing from the ball 20 is formed above the ball 20, and an upper end portion of the stem 22 is coupled to a handle 31 of an operating mechanism 30. By rotating the handle 31, the ball 20 rotates and communication and cutoff of the fluid are achieved. However, the operating mechanism is not limited to those of a manual type, and other types that rotate with an electrical appliance or by air pressure is also applicable.

(11) A cylindrical protrusion 16 protrudes upward from an upper part of the main body 10, and in an internal space of the protrusion 16 and the depression 13, a ring-shaped ball seat presser 41 that comes into contact with the ball seat, a disc spring 43, and a ball seat pressing screw 42 are arranged from the bottom.

(12) A protrusion female thread 16b is formed on an inner surface of the protrusion 16 and engages a ball seat pressing screw male thread 42a formed on an outer surface of the ball seat pressing screw 42. The ball seat pressing screw 42 is rotated to apply a load from above and compress the disc spring 43, then a repulsive force of the disc spring 43 applies a load to the ball seat presser 41 from above, which is in turn transmitted to the ball seat 40, so that the ball seat 40 is compressed by the load applied from above.

(13) A protrusion male thread 16a is formed on an outer surface of the protrusion 16 and engages a panel nut female screw 15a formed on an inner surface of a panel nut 15. A panel or the like can be sandwiched between the panel nut 15 and an upper surface of the main body 10.

(14) FIG. 2A to 2C illustrate the enlarged ball 20, the stem 22, and the ball seat 40. The ball seat 40 is provided with retainer accommodating spaces 45 for accommodating the retainers 50 at the openings 44 and is provided with an upper opening 46 formed in an upper portion thereof. A notch 22a is formed at an upper end portion of the stem 22, and the notch 22a engages the handle 31, so that the stem 22 and the ball 20 is rotated by the rotation of the handle 31, and the communication and cutoff of the fluid are achieved. FIG. 2A illustrates a state in which a fluid communicates, FIG. 2B illustrates a state in which the fluid is cut off, and FIG. 2C is a side view of the state illustrated in FIG. 2A.

(15) In FIG. 2C, reference sign D.sub.1 denotes a diameter of a bottom surface of the ball seat 40, and reference sign D.sub.2 denotes a diameter of an upper surface of the ball seat 40. The diameter D.sub.2 is slightly smaller than the diameter D.sub.1 in the ball valve of the invention. The diameter D.sub.1 is larger than the depression 13 of the main body 10, and the diameter D.sub.2 is the same as a diameter of the depression 13 of the main body 10. Therefore, there is no gap present between a side surface of the ball seat 40 and an inner peripheral surface of the depression 13. In this example, an outer shape of the ball seat is a frustoconical shape. For example, however, a ball seat having a slight vertical rising part at a lower end portion and a frustoconical-shaped part formed upward therefrom is also applicable. In this sense, the shape of the ball seat is a substantially frustoconical shape.

(16) FIGS. 3A and 3B illustrate models for calculating a surface pressure distribution in a case where the load is applied to the ball seat from above. FIG. 3A illustrates an outer side of the ball seat, and FIG. 3B illustrates an inner side of the ball seat. Calculations were performed for three types of the ball seat, including a conventional type (the diameter of the upper surface: 27.0 mm, the diameter of the lower surface: 27.0 mm) and two new types (the diameter of the upper surface: 27.0 mm, the diameter of the lower surface: 27.2 mm) and (the diameter of the upper surface: 27.0 mm and the diameter of the lower surface: 27.5 mm). The results are shown in Table 1 and Table 2. These Tables 1 and 2 shows values of the surface pressure resulted from application of a load 9000 N from above to respective types of the ball seat. Respective rows correspond to positions P.sub.1 to P.sub.3 shown in FIGS. 3B and Q.sub.1 to Q.sub.3 shown in FIG. 3A.

(17) TABLE-US-00001 TABLE 1 Conventional type New Type New Type (φ27) (φ27-27.2) (φ27-27.5) Upper 18.7 19.2 20.3 position (Q.sub.1) Middle 12.5 20.6 21.1 position (Q.sub.2) Lower 16.2 16.2 16.4 position (Q.sub.3) (Unit: MPa)

(18) TABLE-US-00002 TABLE 2 Conventional type New Type New Type (φ27) (φ27-27.2) (φ27-27.5) Upper 16.7 20.5 20.6 position (P.sub.1) Middle 15.3 24.5 25.9 position (P.sub.2) Lower 21.1 20.2 21.5 position (P.sub.3) (Unit: MPa)

(19) FIG. 4 is a graph showing the value in Table 1. In contrast to the surface pressure of 12.5 MPa at the middle position (Q.sub.2) of the conventional type, the new type (φ27-27.2) has the surface pressure of 20.6 MPa, which is 8.1 MPa higher, and the new type (φ27-27.5) has the surface pressure of 21.1 MPa, which is 8.6 MPa higher.

(20) FIG. 5 is a graph showing the value in Table 2. In contrast to the surface pressure of 15.3 MPa at the middle position (P.sub.2) of the conventional type, the new type (φ27-27.2) has the surface pressure of 24.5 MPa, which is 9.2 MPa higher, and the new type (φ27-27.5) has the surface pressure of 25.9 MPa, which is 10.6 MPa higher.

(21) From FIG. 4 and FIG. 5, the fact that the surface pressure of the ball seat of the conventional type varies, whereas the surface pressures of the ball seat of the new types are subjected to less variation, so that portions having low surface pressure, which may cause leakage occurred in the conventional type, may be eliminated.

(22) FIG. 6 illustrates a relationship between the disc spring load (N) and the seal pressure (MPa). The seal pressure is a pressure at which leakage from the ball seat occurred when a pressure is applied in a state in which the interior of the ball valve 1 is sealed, and the disc spring load is a load applied from the disc spring 43 to the ball seat. The disc spring load was calculated from an amount of deflection and a spring constant of the disc spring 43.

(23) Reference signs a1, a2, and a3 represent the ball seats 40 of the conventional type, and diameters of an upper surface and a lower surface thereof are both 27.0 mm, whereas reference signs b1, b2, and b3 represent the ball seats of the new type and diameters of the upper surface and the lower surface thereof are 27.0 mm and 27.5 mm, respectively. Three each of samples are prepared for the conventional type and the new type.

(24) The disc spring load required for achieving the same seal pressure is smaller for the new type after improvement than for the conventional type. Therefore, the disc spring load for preventing leakage of the fluid can be reduced, and deformation of the components such as a retainer is avoided correspondingly. In order to achieve the seal pressure of 19 MPa, a load close to 10000 N is required for those of the conventional type, whereas only on the order of 8000 N is required for those of the new type after improvement.

(25) The ball valve of the invention contributes to uniformization of positional distribution of the contact surface pressures between the ball seat and the ball and between the ball seat and the main body. Therefore, in comparison with the ball valve in the related art, leakage of the fluid from between the ball seat and the ball and between the ball seat and the main body is prevented even without increasing the load from above.