JPS6354954B2 - - Google Patents

Description

[Detailed description of the invention]

The present invention relates to a gas flow rate adjustment valve in which the valve body advances and retreats as the valve body rotates.Even if the combustion gas to be used is different, special adjustments can be made by simply rearranging the parts. Particularly suitable for cooking utensils such as table stoves, which do not require
The purpose of the present invention is to provide a gas flow rate regulating valve. There are many types of combustion gas in Japan.
In order to provide gas appliances that are suitable for each type of combustion gas, gas appliances have traditionally been designed with nozzle shapes, parts that regulate the minimum gas flow rate, and other parts that control the gas flow rate. It is common for the parts involved in combustion to have different sizes and shapes. Therefore, if you live in the same place but have switched from city gas to natural gas, or if you have moved and the type of gas you use has changed, you may wish to continue using the same gas appliances. In order to respond to changes in the gas used, parts must be replaced,
This required troublesome adjustments and parts replacement. The present invention relates to a gas flow rate regulating valve in which the valve body advances and retreats as the valve body rotates, and can be easily installed without requiring any special tools when changing the gas used as described above. The purpose of this invention is to provide a gas flow rate regulating valve that does not require replacing with other parts or making any special adjustments just by rearranging the parts. By providing a gas appliance with the gas flow rate adjustment valve according to the present invention, even if the type of gas changes, a single appliance can adjust the gas flow rate between the required maximum flow rate and a constant minimum flow rate for each type of gas. It becomes possible to control the flow rate to a desired level. The above-mentioned constant minimum flow rate is determined by the type of burner of the gas appliance and the type of combustion gas used, and is a constant and stable flow rate that is determined by the type of burner of the gas appliance and the type of combustion gas used. The minimum flow rate that can cause combustion. The amount of displacement of the valve body of the gas flow rate regulating valve from the maximum flow rate to the minimum flow rate required for combustion is referred to as the effective displacement amount. Depending on the type of combustion gas used, the gas flow rate regulating valve must be able to maintain the effective displacement amount and minimum flow rate opening required for each gas. The present invention relates to a single gas flow rate regulating valve that can be used for many types of gas. A small number of cams with the same amount of displacement are provided, and the opening degree of the minimum flow rate can be easily changed depending on the type of gas, thereby providing the same gas flow rate adjustment valve that can be used for many types of gases. The configuration will be explained below with reference to the drawings. A first embodiment thereof is shown in FIGS. 1 to 4. A valve body 2 is fitted into a body 1 so as to be rotatable and slidable in the axial direction, and an inlet/outlet 3 is provided in the side surface of the body 1, and another inlet/outlet 4 is provided in the bottom surface of the body 1. The valve seat 5 is screwed on. A valve head 6 is formed at the lower end of the valve body 2, and a spring 7 is attached to the upper part of the valve head 6. The spring 7 causes the valve body 2 to move in a direction in which the valve head 6 approaches the valve seat 5. is being energized. The urging force applied to the valve body 2 is generated by a sliding portion 8 protruding near the upper end of the valve body 2 in a direction substantially perpendicular to its axis, and a cam 9 formed on the upper surface of the body 1. It is supported by the abutment of the In the illustrated position in FIGS. 1 to 3, the sliding part 8 is located at the cam 9.
This shows the position where the valve body 2 is at its lowest position and the valve head 6 is closest to the valve seat 5, that is, when the gas flow rate is at its minimum. In the illustrated example, a cam 9 and a cam 9a having different profiles are formed at symmetrical positions that allow the sliding portion 8 to rotate approximately 90 degrees. For example, cam 9 corresponds to the city gas group,
The cam 9a corresponds to different types of combustion gases, and within the same rotation angle range, the valve body 2 changes from the required minimum flow rate to the maximum flow rate depending on the calorific value, supply pressure, etc. of the gas used. The effective displacement amount is determined. The profile of the cams 9 and 9a is the fifth one, which is a developed view.
As shown in the figure, they have different shapes, and the rate of change dl/dφ of the cam lift l is determined so that the amount of displacement of the valve body differs depending on the rotation angle φ of the valve body 2, and the desired valve opening degree is determined. It is structured so as to obtain the following. FIG. 6 shows an example of the arrangement when the gas flow rate regulating valve is used in a table stove. In the illustrated arrangement example, the gas flow rate regulating valve 10 is provided between a nozzle 12 and a nozzle 11 for opening and closing the entire gas passage, and the aforementioned nozzle 11 is connected to a main pipe 13,
Said nozzle 12 is connected to a burner 14.
Note that the gas flow rate adjustment valve 10 may be provided closer to the main pipe 13 of the pot 11. A second embodiment is shown in FIGS. 8 to 11. A valve body 22 is fitted into the body 21 so as to be rotatable and slidable in the axial direction.
3 and 24, and a valve seat 25 is formed on the entrance/exit 24 side of the body 21. A valve head 26 is formed at the inner end of the valve body 22;
A spring 27 is attached to the valve body 22, and the spring 27 causes the valve body 22 to move against the valve head 26.
is biased toward the valve seat 25. The urging force applied to the valve body 22 is generated by a sliding portion 28 protruding near the outer end of the valve body 22 in a direction substantially perpendicular to its axis, and a cam formed on the outer end surface of the body 21. It is supported by contact with 29. In the illustrated position in FIGS. 8 to 11, the sliding portion 28 is at the lowest position of the profile of the cam 29, so that the valve body 22 is most inserted into the body 21, and the valve head 26 is at the lowest position of the profile of the cam 29.
indicates the position closest to the valve seat 25, that is, the state at the minimum gas flow rate. In this embodiment, as shown in FIGS. 9 and 10, a cam 29 and a cam 29a having different profiles are formed at symmetrical positions that allow the sliding portion 28 to rotate approximately 90 degrees. There is. The profiles of the aforementioned cams 9, 9a, 29, 29a are obtained as follows. As shown in Fig. 6, Gas pressure at the inlet of the main pipe 13: Pi Gas pressure at the outlet of the pot 11: P ₁ Gas flow rate at the outlet of the pot 11: V ₁ Maximum gas pressure at the outlet when the pot 11 is fully open: P _1nax Kotuku 11 Maximum gas flow rate at the outlet when fully open: V Gas flow rate at the outlet of _1nax nozzle 12: V Maximum gas flow rate at the outlet of _N nozzle 12: V Specific weight of _Nnax gas: γ (However, the gas pressure from the outlet of Kotoku 11 to the outlet of nozzle 12 The difference is small and the change in specific weight can be ignored.) Acceleration of gravity: g Pressure loss from Kotuku 11 outlet to nozzle 12 outlet: △P Pressure loss as above when Kotuku 11 is fully open: △P _nax Kotuku fully open If the pressure loss from the inlet of the main pipe 13 to the outlet of the pot 11 at the maximum gas flow rate is β, then according to Bernoulli's theorem, when the gas flow rate adjustment valve 10 is not present and the pot 11 is fully open, P ₁ + γ/ 2gV ² _1nax = γ / 2gV ² _Nnax + △P _nax ……(1) Pi−β＝P ₁ ……(2) In this state, that is, when the gas flow control valve 11 is fully open, the gas flow rate adjustment valve 10 (hereinafter referred to as the adjustment valve) 10) is installed, the pressure loss △P _V of this regulating valve 10 is added, so the nozzle 12 in this case
The outlet flow velocity is W _N (the flow velocity when Kotoku 11 is fully open is
W _Nnax ), then in order for equation (1) to hold, γ/2gW ² _Nnax = γ/2gV ² _Nnax −△P _Vnio ……(3) (where △P _Vnio is the pressure of the regulating valve at the maximum gas flow rate Therefore, the velocity energy of the regulating valve 10 is equal to the velocity energy obtained by subtracting the pressure loss ΔP _V of the regulating valve 10 from the velocity energy (pressure display) γ/2gV ² _Nnax of the gas at the exit of the conventional nozzle 12. It is necessary to change the nozzle hole of the nozzle 12 so that the gas flows before installation. The gas flow rate at a certain opening degree of the regulating valve 10 is Q,
Let Q _nax be the maximum gas flow rate, and let Q/Q _nax = ε...(4). The pressure loss △P _V of the regulating valve required to flow an arbitrary gas flow rate Q is given by (1), (2), and (3): △P _V = (P _i −βε ² ) (1 − ε ² ) ＋△P _Vnio ε ² ...(5) Gas flow rate Q that generally causes pressure loss △P _V
The opening area A of the regulating valve when is flowing is (However, the resistance coefficient of the regulating valve is assumed to be 1.) As shown in Fig. 7, the valve head 6 of the valve body 2, 22,
In the case of a combination in which 26 is a conical shape with an apex angle of 2θ and the valve seats 5, 25 are cylindrical holes, the valve head 6, 26 and the valve seat 5,
25, the shortest distance is a, the valve head 6, 26 and the valve seat 5, 2
The upward stroke of the valve heads 6, 26 from the contact position with the valve seats 5, 25 is S, the radius of the cylindrical hole of the valve seats 5, 25 is R,
As shown in the figure, the distance between the foot of the perpendicular line 4 drawn from the end of the cylindrical hole of the valve seat 5, 25 to the valve head 6, 26 (the length of this perpendicular line is a) and the axis of the valve head 6, 26 is x. Then, the opening area A of the regulating valve is A = π (R + x) S sin θ ... (7) x = R - S sin θ cos θ ... (8) From equations (6), (7), and (8) i.e. Now, S ₁ is set at the maximum flow rate (at this time, from equation (4), ε=
Q _nax /Q _nax = 1), and S ₂ is the cam displacement at the minimum flow rate (from equation (4), ε = Qmin / Q _nax , and ε at this time is ε _nio ). If it is a displacement, then the effective displacement amount of the cam S _E =S ₁ −S ₂ is obtained. In equation (9), the constants other than γ, Q _nax , ΔP _V , and ε are unrelated to the type of gas. Although ε is a variable, ε _nio = Q _nio /Q _nax , that is, the minimum calorific flow rate/maximum calorific flow rate can generally be considered to be unrelated to the type of gas, so if △P _V at ε _nio is expressed as △P _Vnax , Equation ( ₉ ) is

[Formula] and in S ₂

If [formula] is set to be constant regardless of the type of gas, the profile of the cams 9, 9a, 29, 29a,
In other words, the curve of the stroke S of the valve body with respect to the rotation angle φ of the valve bodies 2, 22 is as shown in FIG. 17 or 18.
As shown in the figure, the intermediate S position varies depending on the type of gas, but the effective displacement amount of the cam S _E =S ₁ -S ₂ can be constant regardless of the type of gas. However, since Equation (9) was derived with the flow coefficient μ = 1, in practice, Equation (9) is

【formula】 is, more precisely,

As [Formula], it will be necessary to calculate S ₁ , S ₂ , and S _E including μ. By the way, since Q _nax and γ are determined by the shape of the gas appliance and the type of gas, the only item that can be manipulated in terms of design is △ _PV .
ΔP _V is given by the above equation (5). (5) In the right-hand side of equation
P _i and β are constants determined by the gas appliance and the type of gas. Therefore, regarding the gas flow rate adjustment valve, the only operable item in terms of design is △P _Vnio in equation (5). The flow velocity V _N of the nozzle 12 before the installation of the gas flow rate adjustment valve 10 as shown in FIG.
0, the flow velocity W _N is reduced by the value of ΔP _Vnio so as to maintain the relationship: γ/2gW ² _Nnax = γ/2gV ² _Nnax −ΔP _Vnio (3). As mentioned above, the flow velocity W _Nnax of the gas ejected from the nozzle 12 also decreases or increases depending on the size of △P _Vnio . A predetermined gas flow rate can be obtained by adjusting the amount depending on the type of gas. As mentioned above, changing the operation of ΔP _Vnio in the gas flow rate regulating valve 10 has the same result as changing the nozzle pressure P _N and nozzle diameter in the nozzle 12. By performing the design operations described above, S _E = S ₁
−S ₂ can be kept constant regardless of the type of gas. The next problem is that the value of S ₂ differs depending on the type of gas. Types of gases that can hold the same S _E , e.g.
When two types of combustion gases, LPG and 13A, are grouped together, the same cam can be used, but the opening areas of the flow rate regulating valves 10 that provide the minimum flow rate do not necessarily match. The solution will be described below. As shown in the embodiments of FIGS. 8 to 11, the sliding portion 28 has a non-cylindrical projecting shaft 15 that projects at right angles to the rotation axis of the valve body 22, and a position where the projecting shaft 15 is inserted. It consists of a slider 16 that can be fitted by changing the slider. The protruding shaft 15 in this embodiment has a substantially flat shape, and is screwed onto a threaded portion 17 provided on the outer end side of the valve body 22, as shown in FIG. It is said to be adjustable. The slider 16 is shown in FIGS. 12, 13, and 14.
As shown in Figure A and Figure 14B, a fitting hole 18 into which the protruding shaft 15 is fitted is provided through the hole 18, and a flange 20 is formed in the center, which slides into contact with the cams 29, 29a on both sides of the flange 20. A plurality of sliding contact surfaces 19, 19a, 19b, 19c, and 19d are provided on the outer surface. Each sliding surface 19a, 19b, 19c,
19d is a cylindrical surface having a different contact radius with respect to the axis of the protruding shaft 15. The insertion position and direction of the slider 16 onto the protruding shaft 15 are selectively changed so that any one of the sliding contact surfaces 19a, 19b and 19c, 19d can come into sliding contact with the cams 29, 29a. The valve body 22 is always held against the valve seat 25 by a spring 27.
Since the slider 16 is pushed in the direction, the collar 20 of the slider 16 fitted into the protruding shaft 15 comes into contact with the inner surface of the cam, and the slider 16 does not deviate from the protruding shaft 15.
Or, it is in contact with 29a on the same selected sliding contact surface. As shown in FIGS. 8 to 11, the protruding shaft 15 is screwed onto the threaded portion 17 of the valve body 22, and the lock nut 30
Alternatively, since it is fixed by means such as welding, the screwing position with respect to the valve body 22 does not change during operation of the gas flow rate regulating valve, and the valve seat 25 and the valve head 2
Even if a minute adjustment is required to the opening area between 6 and 6, another adjustment can be made by changing the screwing position of the protruding shaft 15 with respect to the valve body 22. The slider 16 is refitted to the protruding shaft 15 in the following manner. The valve body 22 is pulled out toward the outer end against the biasing force of the spring 27, and the cam 2
9, 29a and the slider 16 are released, the slider 16 is pulled out from the protruding shaft 15, the insertion position with respect to the protrusion shaft 15 is changed, or the insertion direction is reversed, and the insertion is performed, for example, the initial sliding surface 19a The slider 16 that was in sliding contact with the cam is moved to the sliding contact surfaces 19b, 19
Insert so that either c or 19d is in sliding contact,
If the drawing force to the valve body 22 is released, the opening area between the valve seat 25 and the valve head 26 can be changed, and it is possible to cope with a change in S ₂ due to a change in the type of gas used. If the sliding surface 19b is brought into contact with the cam 29 and the relative position between the valve body 22 and the slider 16 is adjusted to match the minimum flow rate of 13A gas, then when changing the gas used to LPG, the sliding surface 19b can be brought into contact with the cam 29. By simply replacing the slider 16 so that the contact surface 19d contacts the cam 29, the position of the valve body 22 can be set to a position shifted by ΔH, as shown in FIG. 13, to match the minimum flow rate of LPG. In other words, the difference in minimum flow rate is as shown in Figures 14A and 14B.
Height of sliding surfaces 19a, 19b, 19c, 19d
Obtained by the difference between Ha, Hb, Hc, and Hd. As mentioned above, in the embodiments shown in FIGS. 8 to 11 or the embodiments using the slider 16 as shown in FIGS. 12 and 13, four types of gases with the same effective displacement amount are Can deal with gas. If the protruding shaft is a prism with a square cross section, on one side of the slider, R ₁ , R ₂ , R ₃ ,
It is possible to obtain a sliding surface that can handle four types of gas in the same group with a contact radius of R ₄ , and by using a shape with a protruding flange in the center as described above, the same By simply changing the insertion position and direction of the slider, it is possible to handle eight types of gases in the same group (4×2=8). Generally, by forming the protruding shaft 15 into a regular N-gon shape, it becomes possible to handle 2N types of gases in the same group with the same slider. Depending on the type of gas, the effective displacement amount of the valve body differs, so the same cam cannot be used, and there are gas types that cannot be grouped together in the same group. By using another cam 29a having a different effective displacement amount of the body 2, it is possible to group the body 2 into another group similar to that described above. Note that which surface of the slider 16 and the cams 29, 29a corresponds to which type of gas can be clearly indicated by displaying on the collar 20 of the slider 16, the side surface of the cams 29, 29a, etc. can. In addition, as mentioned above, by grouping gas types, gas types with the same effective displacement can be grouped together, but as shown in Figures 17 and 18, it is possible to group gas types with the same effective displacement amount. Even if the displacement amounts are equal, the cam profile required for each type of gas, that is, the stroke S of the valve body 2 relative to the rotation angle φ of the valve body 2 is not the same. The reason for this is that there is generally a desire to make the rotation angle φ of the valve body 2 proportional to the gas flow rate, and it is desirable to comply with this desire as much as possible. Conventionally, when adjusting the gas flow rate using the kettle of a table stove, as shown in Fig. 15,
When the knob was turned from fully open to fully closed, the flow rate did not change much at first for the same rotation angle, but the gas flow rate suddenly decreased midway through, making adjustment difficult. . This tendency is more pronounced for gases such as natural gas and LPG that have a larger calorific value per unit volume. In order for the rotation angle φ of the valve body 2 to be proportional to the gas flow rate, the following relationship is required: ε = φ / φ _nax = Q / Q _nax ... (10) (However, φ _nax is the rotation angle at Q _nax ) Therefore, by substituting φ/φ _nax for ε in equation (9) and substituting the above-mentioned equation (5) for △P _V , we get Equation (11) is an equation for determining the cam profile in the case shown in FIGS. 17 and 18. The specific procedure for calculating the cam profile is as follows. (b) From the calorific value of the gas appliance and the type of gas, P _i ,
Q _nax is determined. (b) One of φ _nax and θ and ΔP _Vnio are determined in advance. (c) If φ _nax is determined in advance, φ _nax , that is, θ at Q _nax is determined. If θ is determined in advance, the corresponding φ _nax is determined. (d) Estimate β in advance through experiment. (e) Calculate using equation (11). The shape of the valve head 26 is not conical as shown in FIG.
When the surface of rotation is a special generating curve such as the rotating object surface shown in Fig. 9, a relational expression representing the stroke of the valve head and the opening area between the valve seat and the stroke of the valve head is determined from the equation representing the generating curve. , [formula corresponding to the above-mentioned formula (7)], and the following similar calculations can be used to obtain the cam profile. Similar calculations can be made for valve heads with disc-shaped valve heads. In this way, a regulating valve having the relationship between the gas flow rate Q and the rotation angle φ as shown in FIG. 20 can be obtained. The S-φ curve obtained as described above is the first
These are the curves for each type of gas shown in FIGS. 6 to 18. As is clear from the curves shown in Figures 17 and 18, the ideal cam profile depending on the type of gas has the effective displacement S _E = S ₁ - S ₂ as described above. Even if you try to make them equal, they are not the same. I want to keep the number of cams as low as possible. Maximum displacement of the curve for each group as a next best option
By setting the average curve when S ₁ and the minimum displacement S ₂ are the same as the cam curve, a curve that more closely approximates any of the ideal curves that differ depending on the type of gas,
That is, S ₁ and S ₂ match, and although the rotation angle of the valve body 2 and the gas flow rate are not completely proportional, it is possible to obtain a curve that is more similar to the rotation angle of the valve body 2. For example, the cam 29 is connected to the gas type shown in FIG.
For the average curves of 13A and LPG, the cam 29a can be selected for the average curves of gases 4C and 6B shown in FIG. The former average curve is the L curve which is the profile of the cam for LPG gas shown in FIG. 16, and the latter average curve is the T curve which is the profile of the city gas cam. FIG. 19 shows a curve of flow rate ratio ε versus rotation angle φ, which is predicted by calculating the characteristics of the gas flow rate regulating valve when using the two types of cams determined as described above. As shown in FIG. 19, it is desirable that the relationship between ε and φ ideally be the straight line shown in the figure, which is an ideal characteristic. By doing so, the relationship between ε and φ can be made to have a characteristic close to a straight line. The present invention has the structure described in claim 1, and the effective displacement amount of the gas flow rate regulating valve is made the same for a plurality of types of combustion gas in a group that can be aggregated. This makes it possible to use extremely few types of cams to handle many types of combustion gases, and by simply rearranging parts, a single body, valve body, etc. can be used. , it has become possible to provide a gas flow rate regulating valve that can be easily handled without requiring any special adjustment. In addition, in the case of the structure described in claim 2, by providing a slider that can be fitted to the protruding shaft so that the insertion position and direction can be changed,
It is now possible to extremely easily determine the minimum flow rate of gas within the flammable range of the burner depending on the type of combustion gas, and it is possible to determine the minimum flow rate that allows continuous and stable combustion without causing gas blow-off or backfire phenomena. It has become possible to maintain this. Furthermore, in the case of the configuration described in claim 3, the sliding part is configured to allow easy adjustment of the position of the valve body in the axial direction, thereby improving the distance between the valve body and the valve seat. This makes it possible to make minute adjustments to the opening area.

[Brief explanation of the drawing]

Fig. 1 is a side view of the first embodiment, Fig. 2 is an axial longitudinal cross-sectional view of the above, Fig. 3 is a plan view of the above, Fig. 4 is a bottom view of the above, and Fig. 5 is a circumferential direction of the cam portion of the above. 6 is a side view schematically showing the mounting relationship, FIG. 7 is a partial sectional view of an embodiment of the valve head-valve seat relationship, and FIG. 8 is a side view schematically showing the mounting relationship.
9 is a sectional view taken along the line in FIG. 8, FIG. 10 is a top side view of the same, FIG. 11 is a back view of the same, and FIG. Figure 13 is an elevational view of the same as above, Figure 14A, Figure 14
Figures B are both side views of the same slider, No. 15.
The figure shows a conventional Kotsuk ε-φ diagram, FIG. 16 shows an S-φ average curve diagram for two groups of combustion gases in the example, and FIG. 17 shows an S-φ average curve diagram for two types of combustion gases in the same group. φ curve diagram, FIG. 18 is an S-φ curve diagram suitable for two types of combustion gas examples of another group,
FIG. 19 is an ε-φ diagram of the example, and FIG. 20 is a Q-φ diagram.
It is a φ ideal diagram. 1, 21: Body, 2, 22: Valve body, 5, 2
5: Valve seat, 6, 26: Valve head, 8, 28: Sliding part,
9, 9a, 29, 29a: cam, 10: gas flow rate adjustment valve, 15, 15a: protruding shaft, 16, 16a: slider, 17: threaded portion, 19, 19a, 19b,
19c, 19d: Sliding surface.

Claims (1)

[Scope of Claims] 1. A sliding portion protruding from a valve body inserted into the body so as to be rotatable and movable in the axial direction comes into contact with a cam provided on the body. and the valve head of the valve body moves forward and backward with respect to the valve seat as the sliding part slides into contact with the cam as the valve body rotates around the axis. In the valve, a plurality of the cams are provided, and the sliding part is configured to selectively abut on any one of the cams, and each cam has a valve body that is attached to the valve body according to the type of gas. A gas flow rate regulating valve characterized in that each valve is set to a profile capable of giving an effective displacement amount. 2. The sliding part protruding from the valve body is fitted onto a non-cylindrical protruding shaft that protrudes at right angles to the rotation axis of the valve body, and the fitting position and direction can be changed with respect to the protruding shaft. The sliding surface of the slider with the cam has a cylindrical shape having a different contact radius with respect to the axis of the protruding shaft by changing the insertion position of the slider on the protruding shaft. The gas flow rate regulating valve according to claim 1, wherein the gas flow rate regulating valve is constituted by a plurality of surfaces. 3 The sliding part protruding from the valve body is
The gas flow rate regulating valve according to claim 1 or 2, wherein the valve body is screwed into a threaded portion screwed on the outer end side so that the position of the valve body in the axial direction can be adjusted.