Flow regulating valve

Abstract

To effectively reduce the noise caused by pressure fluctuations and a refrigerant separation phenomenon when refrigerant passes through a valve port.SOLUTION: A flow regulating valve 1 is designed to obtain equal percentage characteristics or characteristics close thereto as flow characteristics, and comprises a valve element 30 having a curved portion 33 that changes the flow rate of fluid flowing through a valve port 10 in accordance with a lift amount, in which the curvature or control angle of the curved portion 33 is increased continuously or stepwise as it approaches the tip. In the flow regulating valve, the diameter of the valve port 10 is sequentially increased in three or more stages as it moves away from a valve chamber 6. Specifically, from the valve chamber 6 side, a first valve port portion 11 having a diameter D1, a second valve port portion 12 having a diameter D2 (>D1), and a third valve port portion 13 having a diameter D3 (>D2) are provided in this order.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a valve body having a valve chamber and a valve port (orifice), and a valve body that changes the valve opening depending on the amount of lift. The present invention relates to a flow rate control valve having a valve body that changes the flow rate of a fluid flowing through a valve port, and in particular, The present invention relates to a flow rate regulating valve suitable for regulating the flow rate of refrigerant in a pump-type heating and cooling system or the like. [Background technology]

[0002] The relationship between the valve opening (lift amount) and the flow rate in a flow control valve, that is, the flow rate characteristics, are as follows: The linear characteristic and the equal percentage characteristic are well known. The linear characteristic is This refers to the characteristic where the rate of change of flow rate is constant with respect to the change in valve opening. This refers to the characteristic in which the rate of change is proportional to the flow rate.

[0003] FIG. 5 shows the main part of an example of a flow control valve that is adapted to obtain equal percentage characteristics. The flow rate control valve 1' shown in the figure is used to control the flow rate of a refrigerant in a heat pump type heating and cooling system or the like. It is used to adjust the amount of water. It consists of a valve chamber 6, a valve seat 8 consisting of an inverted truncated cone surface, and a cylinder The valve body 5 has a valve orifice 15 formed of a surface, and the valve orifice 15 is opened and closed in accordance with the amount of lift from the valve seat 8. The valve body 20 changes the flow rate of the flowing fluid. As shown in the figure, the valve stem is provided with a male thread, the guide stem is provided with a female thread, and the step The valve seat 8 is raised and lowered by a screw-type lifting drive mechanism consisting of a lifting motor, etc. To be forced.

[0004] The valve body 20 has a contact surface 22 that contacts the valve seat 8 and a flow rate adjusting portion 23 that is connected to the lower side of the contact surface 22. The curved surface portion 23 is an elliptical sphere for obtaining an equal percentage characteristic. 23 has a shape similar to the lower half of an egg, and its outer periphery extends from an upper end 23a to a lower end 23b. The curve becomes gradually sharper (the curvature increases) towards b.

[0005] In the flow rate control valve 1' in which such an equal percentage characteristic is obtained, As shown by the bold arrow in FIG. 5, when the refrigerant flows from the valve chamber 6 to the valve port 15, the refrigerant The refrigerant flows along the curved surface 23, but when passing through the valve port 15, a sudden pressure fluctuation and refrigerant separation phenomenon occur. As a result, vortices and cavitation are more likely to occur and grow, resulting in relatively large There was a problem of noise generation.

[0006] In order to obtain the equal percentage characteristic as described above, the valve body 20 has an elliptical curved surface portion. Since providing 23 is problematic in terms of processing cost, cost-effectiveness, etc., the The flow rate control valve 1' is designed to obtain characteristics similar to the equal percentage characteristics. The flow rate control valve 1'' shown in the figure has a valve chamber forming member 6A fixed thereto. The valve comprises a first valve opening portion 17A having a short cylindrical surface and a second valve opening portion 17B having a truncated cone surface. A valve port 17 is provided, and a pipe joint 14 to which a conduit is connected is connected to the outer periphery of the lower part of the second valve port portion 17B. The flow rate of the fluid flowing through the valve port 17 is changed according to the amount of lift from the valve body 5 connected to the valve seat 8. and a valve body 30 for causing the valve to open.

[0007] The valve body 30 has a seating surface portion 32 that seats on the valve seat 8 and a flow It has a curved surface portion 33 for obtaining characteristics approximating equal percentage characteristics. The curved surface portion 33 is designed to have a control angle (across the central axis of the valve body 30) gradually decreasing toward the tip so as to approximate an ellipsoidal surface. A multi-stage (here, five stages) cone tape in which the intersection angle between line O and a parallel line is gradually increased. The first control angle θ1 of the uppermost conical tapered surface portion 33A is , usually set to 3°<θ1<15° (here, 5°), and the lowest conical tapered surface portion 33 E has a pointed conical surface.

[0008] On the other hand, in Patent Document 2, a flow control valve that is designed to obtain normal linear characteristics is described. The dimensions and shape of the valve port are specified, and the pressure fluctuations and There is disclosed a device that suppresses noise caused by the refrigerant separation phenomenon and the like. [Prior art documents] [Patent documents]

[0009] [Patent Document 1] JP 2012-172839 A [Patent Document 2] Patent No. 5696093 Summary of the Invention [Problem to be solved by the invention]

[0010] However, in the flow rate control valve described in Patent Document 2, the valve port length is set to be considerably long. This causes a large pressure loss and makes it difficult to obtain an appropriate refrigerant flow rate. Furthermore, the dimensions and shape of the valve port are adapted to the valve body for linear characteristics, so Even if applied to flow control valves with equal percentage characteristics or characteristics close to it, Noise reduction effect is obtained.

[0011] The present invention has been made in view of the above circumstances, and its object is to provide a valve passage that It is possible to effectively reduce the noise generated due to pressure fluctuations and refrigerant separation phenomena in the flow rate adjustment valve, and it is also possible to reduce pressure loss and the like.

Means for Solving the Problems

[0012] To achieve the above object, the flow rate adjustment valve according to the present invention basically includes a valve body provided with a valve chamber and a valve port, a pipe joint having an inner diameter of D4 connected to the valve port, and a valve body that changes the flow rate of the fluid flowing through the valve port according to the lift amount. The valve port is sequentially provided with a first valve port portion of a cylinder having a diameter of D1, a second valve port portion of a cylinder having a diameter of D2, and a third valve port portion of a cylinder having a diameter of D3 from the valve chamber side, and D1 < D2 < D3 < D4. The first valve port portion is provided with a valve seat. Between the first valve port portion and the second valve port portion, an upper conical frustum-shaped tapered surface portion is formed, and between the second valve port portion and the third valve port portion, a lower conical frustum-shaped tapered surface portion is formed. In the axial direction, the length of the lower conical frustum-shaped tapered surface portion is greater than or equal to the length of the upper conical frustum-shaped tapered surface portion. A valve body that changes the flow rate of the fluid flowing through the valve port according to the lift amount, and the valve port is sequentially provided with a first valve port portion of a cylinder having a diameter of D1, a second valve port portion of a cylinder having a diameter of D2, and a third valve port portion of a cylinder having a diameter of D3 from the valve chamber side, and D1 < D2 < D3 < D4. The first valve port portion is provided with a valve seat. A first valve port portion of a cylinder with a diameter of D1, a second valve port portion of a cylinder with a diameter of D2, and a third valve port portion of a cylinder with a diameter of D3 are provided, and D1 < D2 < D3 < D4. The first valve port portion is provided with a valve seat. A first valve port portion of a cylinder with a diameter of D1, a second valve port portion of a cylinder with a diameter of D2, and a third valve port portion of a cylinder with a diameter of D3 are provided, and D1 < D2 < D3 < D4. The first valve port portion is provided with a valve seat. Between the first valve port portion and the second valve port portion, an upper conical frustum-shaped tapered surface portion is formed, and between the second valve port portion and the third valve port portion, a lower conical frustum-shaped tapered surface portion is formed. In the axial direction, the length of the lower conical frustum-shaped tapered surface portion is greater than or equal to the length of the upper conical frustum-shaped tapered surface portion. Between the first valve port portion and the second valve port portion, an upper conical frustum-shaped tapered surface portion is formed, and between the second valve port portion and the third valve port portion, a lower conical frustum-shaped tapered surface portion is formed. In the axial direction, the length of the lower conical frustum-shaped tapered surface portion is greater than or equal to the length of the upper conical frustum-shaped tapered surface portion. Between the first valve port portion and the second valve port portion, an upper conical frustum-shaped tapered surface portion is formed, and between the second valve port portion and the third valve port portion, a lower conical frustum-shaped tapered surface portion is formed. In the axial direction, the length of the lower conical frustum-shaped tapered surface portion is greater than or equal to the length of the upper conical frustum-shaped tapered surface portion. It is characterized in that.

[0013] In a preferred embodiment, the pipe joint is connected to the valve body such that at least the third valve port portion is disposed inside the pipe joint. It is connected to the valve body such that at least the third valve port portion is disposed inside the pipe joint.

[0014] In another preferred embodiment, the valve body has a groove into which the end portion on the valve chamber side of the pipe joint is inserted, and the third valve port portion protrudes to the side opposite to the valve chamber side with respect to the outer peripheral portion of the groove. The valve body has a groove into which the end portion on the valve chamber side of the pipe joint is inserted, and the third valve port portion protrudes to the side opposite to the valve chamber side with respect to the outer peripheral portion of the groove.

Effects of the Invention

[0015] In the flow rate adjustment valve according to the present invention, since the diameter of the valve port gradually increases in three or more stages from the valve chamber side to the lower end side, the refrigerant pressure gradually recovers when passing through the valve port, and the pressure fluctuation is suppressed. Since the diameter of the valve port gradually increases in three or more stages from the valve chamber side to the lower end side, the refrigerant pressure gradually recovers when passing through the valve port, and the pressure fluctuation is suppressed. Also, (D2 / D1) and (D3 / D2) are within a certain range. By setting this, the generation and composition of vortices and cavitation caused by pressure fluctuations and refrigerant separation phenomena can be controlled. Furthermore, (D2 / D1)<(D3 / D2)<(D4 / D3) This allows for a smoother flow, so that, for example, equal percentage characteristics and similar In a flow control valve having such characteristics, the noise level can be significantly reduced.

[0016] Furthermore, by setting (L2 / D1) and (L4 / D1) in a specific range, the valve orifice The length L2 is that described in Patent Document 2 or that shown in FIG. 5. Since it is shorter than the valve 1', the pressure loss is small and an appropriate refrigerant flow rate can be obtained. . [Brief description of the drawings]

[0017] [Figure 1] 1 is a cross-sectional view showing a main portion of an embodiment of a flow rate regulating valve according to the present invention; [Diagram 2] In order to confirm and verify the effects of the present invention, (A) a table showing actual measurement data of verification valves No. 1 to 4 with some changes in specifications and parameters, and (B) a table showing verification conditions A to G. [Diagram 3] (A) A graph showing the actual measured values ​​of verification valves No. 1 to 4 for each verification condition A to G, with the aperture ratio: D2 / D1 on the horizontal axis and the noise level [dB] on the vertical axis. (B) A graph showing the actual measured values ​​of verification valves No. 1 to 4 for each verification condition A to G, with the aperture ratio: D3 / D2 on the horizontal axis and the noise level [dB] on the vertical axis. [Figure 4]In order to confirm and verify the effects of the present invention, (A) a table showing actual measurement data for verification valves No. 5 to 8 with some of the specifications and parameters changed, (B) a table showing verification conditions H and I, and (C) a graph showing the actual measurement values ​​for verification valves No. 5 to 8 for each verification condition H and I, with the valve orifice length ratio: L4 / D1 on the horizontal axis and the sound pressure level [dB] on the vertical axis. [Diagram 5] FIG. 2 is a partial cross-sectional view showing a main portion of an example of a flow control valve configured to obtain an equal percentage characteristic. [Figure 6] 1A and 1B are partial cross-sectional views showing the main part of an example of a flow control valve configured to obtain characteristics approximating equal percentage characteristics, in which (A) is a partial cross-sectional view when the valve is closed, and (B) is a partial cross-sectional view when the valve is open. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0018] Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

[0019] FIG. 1 is a cross-sectional view showing a main part of an embodiment of a flow control valve according to the present invention. In addition, in FIG. 1, the various parts of the conventional flow control valve 1 ″ shown in FIG. 6 are The parts that correspond to each other are given common reference numerals.

[0020] The flow rate control valve 1 of the illustrated embodiment is the same as the conventional flow rate control valve 1 ″ shown in FIG. In the same way, it is possible to obtain characteristics close to equal percentage characteristics, and the valve chest formation The member 6A is fixed, and the valve port 10 (described in detail later), which is a characteristic feature of the present invention, is provided. The valve body 5 is provided with a valve seat 8, and the flow rate of the fluid flowing through the valve port 10 is changed according to the amount of lift from the valve seat 8. The valve body 30 has the same structure as the conventional flow rate control valve 1 ″ shown in FIG. The valve seat 8 is seated on a seating surface portion 32, and the lower side of the seating surface portion 32 is connected to the seating surface portion 32. and a curved surface portion 33 for obtaining characteristics approximating equal percentage characteristics. 3 has a plurality of (here, five) conical tapered surface portions 33A to 33E with the control angle (the intersection angle between the central axis O of the valve body 30 and the parallel line) gradually increased in steps as approaching the tip so as to approximate an ellipsoid surface. The first control angle θ1 of the uppermost conical tapered surface portion 33A is set to 3° < θ1 < 15° (here, 5°), and the lowermost conical tapered surface portion 33E is a pointed conical surface. And the valve port 10 opening into the valve chamber 6 has, in order from the valve chamber 6 side, a cylindrical first valve port portion 11 with a diameter of D1, a cylindrical second valve port portion 12 with a diameter of D2, and a cylindrical third valve port portion 13 with a diameter of D3. A pipe joint 14 with an inner diameter of D4 to which a conduit is connected is connected to the lower outer periphery of the third valve port portion 13. Here, D1 < D2 < D3 < D4, and the diameter of the valve port 10 is sequentially increased in three steps as it is away from the valve chamber 6.

[0021] Here, in this embodiment, (diameter ratio: D2 / D1) < (diameter ratio: D3 / D2) < (diameter ratio: D4 / D3), and (D2 / D1) and (D3 / D2) are each set within a specific range, that is, 1.08 < (D2 / D1) < 1.37 and 1.05 < (D3 / D2) < 1.43, based on trial production experiments and the like. Also, a frustum-shaped tapered surface portion 16 with a taper angle of θu is formed between the first valve port portion 11 and the second valve port portion 12 (the stepped portion therebetween), and a frustum-shaped tapered surface portion 18 with a taper angle of θv is formed between the second valve port portion 12 and the third valve port portion 13 (the stepped portion therebetween).

[0022] Furthermore, the valve port length (the length in the direction of the central axis O) of the first valve port portion 11 is L1, and that of the second valve port portion 12 is L2, and the valve port length of the third valve port portion 13 is L3. Here, L1 < L2 < L3, and the valve port length of the valve port 10 is sequentially increased in three steps as it is away from the valve chamber 6. Here, L1 < L2 < L3, and the valve port length of the valve port 10 is sequentially increased in three steps as it is away from the valve chamber 6.

[0023] In addition, a frustum-shaped tapered surface portion 16 with a taper angle of θu is formed between the first valve port portion 11 and the second valve port portion 12 (the stepped portion therebetween), and a frustum-shaped tapered surface portion 18 with a taper angle of θv is formed between the second valve port portion 12 and the third valve port portion 13 (the stepped portion therebetween).

[0024] Furthermore, the valve port length (the length in the direction of the central axis O) of the first valve port portion 11 is L1, the valve port length of the second valve port portion 12 is ​​The valve orifice length is L2, the valve orifice length of the third valve orifice portion 13 is L3, and the distance from the upper end of the second valve orifice portion 12 to the third valve orifice portion 13 is L4. The length to the bottom of 3 is L4, (valve orifice length ratio: L2 / D1) and (valve orifice length ratio: L4 / D1 ) are within a specific range, i.e., 1.0<(L2 / D1 )<2.0 and 2.3<(L4 / D1)<4.0.

[0025] In the flow rate control valve according to the present invention having such a configuration, the diameter of the valve port 10 is separated from the valve chamber 6. The refrigerant pressure increases in three stages as the valve is opened. The pressure fluctuation is suppressed and the flow is rectified. By setting the ratio of 3 / D2 within a specific range, vortices and other phenomena caused by pressure fluctuations and refrigerant separation phenomena are prevented. The occurrence and growth of cavitation is reliably suppressed. Furthermore, (D2 / D1)<(D3 / By making D2 < (D4 / D3), the flow becomes smoother, so the equal par In a flow control valve having a centrifugal characteristic or a characteristic similar thereto, the noise level is considerably reduced. It is possible.

[0026] Furthermore, by setting (L2 / D1) and (L4 / D1) in a specific range, L2 (or L1) has the equal percentage characteristics described in Patent Document 2 and shown in FIG. Since it is shorter than the flow rate control valve 1', the pressure loss is small and the appropriate refrigerant flow rate can be obtained. can.

[0027] [Verification test to verify the appropriate range of aperture ratio and valve length ratio and its results] In order to confirm and verify the above-mentioned effects, the present inventors have As shown in the table, some of the specifications and parameters have been changed, and the aperture ratio (D2 / D1), (D 3 / D2)》Verification valves No.1 to 4, and valve length ratio《(L4 / D1)》Verification valve No.5 2(B) and conditions A to G shown in FIG. 2(B) and conditions H and I shown in FIG. The verification test was carried out under the following conditions. Valve diameter ratio {(D2 / D1), (D3 / D2)} Verification valve No. The test results for 1 to 4 are shown in Figure 3 (A) and (B). The test results for Nos. 5 to 8 are shown in FIG. 4(C).

[0028] In Fig. 3(A), the horizontal axis represents the aperture ratio: D2 / D1, and the vertical axis represents the noise level [dB]. The graph in Fig. 3(B) shows the actual measured values ​​of the verification valves No. 1 to 4 for each verification condition A to G. The horizontal axis is the aperture ratio: D3 / D2, and the vertical axis is the noise level [dB]. The graph in Figure 4(C) shows the actual measured values ​​of o.1 to o.4 for each verification condition A to G. The horizontal axis shows the valve orifice length ratio. : L4 / D1 is taken on the vertical axis, and sound pressure level [dB] is taken on the vertical axis. This is a graph showing the values ​​for each verification condition H and I.

[0029] In the graphs of FIG. 3(A), (B) and FIG. 4(C), level 0 (standard) is the The flow control valve 1 has a characteristic similar to the conventional equal percentage characteristic shown in FIG. The figures show the noise levels and sound pressure levels of the conventional product.

[0030] From the graph in FIG. 3(A), the aperture ratio: (D2 / D1) is 1.05 to 1.45 (not shown). The noise level is lower than that of conventional products in almost all ranges, especially valve No. 3 and valve No. The noise reduction effect is large around o.2, but (D2 / D1) is 1.08 (valve No. 4 diameter ratio )~1.37(≒(1.31+1.42) / 2, the aperture ratio is approximately halfway between valve No. 2 and valve No. 1. ) it was confirmed that noise could be significantly reduced compared to conventional products.

[0031] From the graph in FIG. 3(B), the aperture ratio (D3 / D2) is 1.00 to 1.50 (not shown). The noise level is lower than that of conventional products in almost all ranges, especially valve No. 3 and valve No. The noise reduction effect is large at around 0.2, but (D3 / D2) is 1.08 to 1.43 (≒(1. 35+1.50) / 2, approximately halfway between valve No. 3 and valve No. 4. It was confirmed that the noise could be significantly reduced compared to the previous product.

[0032] From the graph in FIG. 4(C), the valve orifice length ratio (L4 / D1) was 2.00 to 4.00 (as shown in the figure). The sound pressure level is equal to or lower than that of conventional products in almost all ranges where the valve is used. The noise reduction effect around No. 6 is large, but (L4 / D1) is 2.30 (valve No. 5 valve port If the ratio is within the range of 4.00 (valve length ratio of valve No. 8), noise will be reduced compared to conventional products. The effect is obtained (for example, the sound pressure level is 2 dB or more lower than the standard under condition I). Confirmed.

[0033] Although illustrations are omitted, if the valve orifice length ratio (L2 / D1) is within the range of 1.0 to 2.0, If this is done, the sound pressure level will be equal to or lower than that of conventional products, and noise reduction effects will be greater than with conventional products. It has also been confirmed.

[0034] In the above embodiment, the flow rate adjusting valve having characteristics approximating the equal percentage characteristics is used. Although the present invention has been described as being applied to the valve 1, the present invention is not limited to this. As shown in FIG. 5, the flow rate control valve 1' having the equal percentage characteristic is of course also applicable. The present invention can also be applied to flow control valves having linear characteristics as described in patent documents 1 and 2.

[0035] In the above embodiment, the control angle of the curved surface of the valve body is gradually increased toward the tip end. However, the present invention is not limited to this, and the following may be used. The ellipsoidal surface portion as shown in FIG. 1 or the lower end portion (ellipsoidal crown portion) of the ellipsoidal surface portion is cut off. Alternatively, a combination of an elliptical spherical surface portion and one or more conical tapered surface portions may be used. It may be configured as follows.

[0036] In the above embodiment, the third valve port portion 13 is connected to the pipe joint 14 having an inner diameter D4. The valve is configured as a fourth valve orifice having a diameter of D4 formed on the opposite side of the valve chamber from the third valve orifice 13. However, it goes without saying that the same effects as those described above can be obtained. [Explanation of symbols]

[0037] 1 Flow control valve 5 Valve body 6 Valve chamber 10. Valve Orifice 11 First valve orifice 12 Second valve orifice 13 Third valve orifice 14 Pipe fittings 30 Valve body 33 Curved part D1 First valve orifice diameter D2: Diameter of the second valve orifice D3 Diameter of the third valve orifice D4 Pipe fitting inner diameter L1 Length of the first orifice L2: Length of the second orifice L3: Length of the third orifice L4 2nd to 3rd valve orifice length

Claims

1. A valve body having a valve chamber and a valve port, a pipe joint having an inner diameter of D4 connected to the valve port, a valve body that changes a flow rate of the fluid flowing through the valve port in accordance with a lift amount, The valve ports are, in order from the valve chamber side, a first valve port portion of a cylinder having a diameter of D1, a second valve port portion of a cylinder having a diameter of D2, A valve orifice portion and a third valve orifice portion of a cylinder of D3 are provided, and D1<D2<D3<D4. And, the first valve port portion includes a valve seat; Between the first valve port and the second valve port, there is an upper stage truncated cone tapered surface portion, and A lower truncated cone tapered surface portion is formed between the valve orifice portion and the third valve orifice portion, In the axial direction, the length of the lower truncated cone tapered surface portion is equal to the length of the upper truncated cone tapered surface portion. A flow control valve, characterized in that the length of the face portion is greater than or equal to the length of the face portion.

2. The pipe joint is configured to have at least the third valve port portion disposed inside the pipe joint.

2. The flow control valve according to claim 1, further comprising a valve body connected thereto.

3. the valve body has a groove into which an end portion of the pipe joint on the valve chest side is inserted, The third valve port portion protrudes from an outer periphery of the groove toward the opposite side to the valve chamber. The flow rate control valve according to claim 1 or 2.

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