CN110425331B

CN110425331B - Electric valve

Info

Publication number: CN110425331B
Application number: CN201910727378.4A
Authority: CN
Inventors: 小林一也; 中川大树
Original assignee: Saginomiya Seisakusho Inc
Current assignee: Saginomiya Seisakusho Inc
Priority date: 2015-12-24
Filing date: 2016-10-28
Publication date: 2022-06-10
Anticipated expiration: 2036-10-28
Also published as: CN110388508A; JP6479648B2; CN110388505B; CN110388505A; CN106917913B; CN110388507A; CN106917913A; JP2017115989A; CN110425331A; CN110388506A

Abstract

The invention provides an electrically operated valve. In an electric valve for controlling the flow of refrigerant by opening and closing a valve port with a needle valve, noise generated by the flow of refrigerant at the valve port is reduced. A first port (11) having an inner diameter D1, a second port (12) having an inner diameter D2, a third port (13) having an inner diameter D3, a first tapered portion (14), and a second tapered portion (15) are formed in a valve housing (1) in a circular cross-sectional shape. When the flowing refrigerant flows out of the second port (12) from the gap between the first port (11) and the needle valve (5a), the flow is rectified and stabilized without rapidly restoring the pressure in the second port (12). Thereby suppressing the collapse of the cavitation. When the fluid flows from the second port (12) to the second tapered portion (15) and the third port (15), the flow velocity is reduced to reduce the flow velocity sound.

Description

Electric valve

The application is a divisional application; the parent application is '2016109732269', and the name of the invention is 'electric valve'.

Technical Field

The present invention relates to a needle valve type electric valve for controlling a flow rate of a refrigerant in an air conditioner or the like, and more particularly to an electric valve having an improved shape of a valve port with respect to a needle valve.

Background

Conventionally, in a refrigeration cycle, noise generated from an electric valve for controlling a flow rate of a refrigerant and generated with passage of a fluid often becomes a problem. An electrically operated valve disclosed in japanese patent No. 5696093 (patent document 1) is an example of an electrically operated valve for implementing such a noise countermeasure.

In the motor-operated valve of patent document 1, the valve port is composed of a first port and a second port, and a tapered portion is provided between the first port and the second port. Further, the inner diameter of the second port is made slightly larger than the inner diameter of the first port, and the length of the second port is made sufficiently longer than the length of the first port.

In the configuration of patent document 1, as shown in fig. 5, the refrigerant that has passed through the gap between the needle valve a and the first port b flows toward the secondary joint pipe through the tapered portion c and the second port d. At this time, the refrigerant passing through the gap between the needle valve a and the first port b flows along the inner wall of the second port d following the shape of the tapered portion c. The inner diameter of the second port d is only slightly larger than that of the first port b, so that the pressure is not abruptly restored during the flow from the first port b to the second port d. Also, since the length of the second port d is sufficiently long, the flow of the refrigerant is rectified at the second port d. Therefore, the collapse of the cavitation bubbles can be suppressed, and the flow of the refrigerant can be stabilized, so that the noise can be reduced.

Documents of the prior art

Patent document 1: japanese patent No. 5696093

The invention of patent document 1 also provides an effect of reducing noise, but noise may be generated in a specific refrigerant state. For example, in the solution of patent document 1, although the flow of the fluid can be rectified at the second port, the second port has an inner diameter slightly larger than that of the first port and a length sufficiently longer than that of the first port. Therefore, the fluid is rectified, but the flow velocity in the second port does not decelerate, and noise may be generated by a flow velocity sound (sound due to a high flow velocity). In particular, at high load, the differential pressure between the front and rear of the valve port is high, and this flow velocity noise becomes a significant factor.

Disclosure of Invention

The invention provides an electrically operated valve in which noise is reduced by improving a valve port.

The electric valve of claim 1 is an electric valve in which a valve chamber and a secondary joint that communicate with each other via a valve port that is opened and closed by a needle valve are allowed to communicate with each other, and the electric valve includes a first port on a valve chamber side, a second port having an inner diameter larger than that of the first port, and a first tapered portion that connects the first port and the second port to each other, the electric valve being characterized in that the valve port includes a third port on the secondary joint pipe side and a second tapered portion that connects the second port and the third port to each other, and the relationship among the inner diameter D1 of the first port, the inner diameter D2 of the second port, and the inner diameter D3 of the third port is D1 < D2 < D3.

Electric valve of claim 2 the electric valve of claim 1, wherein,

D2－D1≤D3－D2。

the electrically operated valve of claim 3, wherein the electrically operated valve of claim 1 or 2,

when the taper angle of the first tapered portion is θ 1, the taper angle of the second tapered portion is θ 2, the length of the first port is L1, the lengths of the first tapered portion and the second port are L2, and the lengths of the second tapered portion and the third port are L3, the following relationships are obtained:

1mm≤D1≤4.5mm，

60°≤θ1≤150°，

20°≤θ2≤90°，

0.1mm≤L1≤0.5mm，

1≤L2/L1≤39，

0.57≤L3/L2≤38，

1.03≤D2/D1≤1.5，

1.02≤D3/D2≤5.52。

The effects of the invention are as follows.

According to the motor-operated valve of claims 1 to 3, when the flowing refrigerant flows out from the gap between the first port and the needle valve to the second port, the pressure is not rapidly restored in the second port, the flow can be rectified to stabilize the flow of the refrigerant, and the collapse of the cavitation can be suppressed. In addition, when the fluid flows from the second port to the second tapered portion and the third port, the flow velocity is decelerated, and the flow velocity sound can be reduced. Therefore, noise can be reduced.

According to the motor-operated valve of claim 2, since D2-D1 is D3-D2, the diameter increases from the second tapered portion to the third port, as compared to the second port, and the deceleration effect of the flow velocity increases, and the flow velocity sound can be further reduced.

According to the electrically operated valve of claim 3, the noise can be effectively reduced even when the pressure difference between the front and rear of the valve port is high by satisfying the conditions of the size and angle of each portion.

Drawings

Fig. 1 is a longitudinal sectional view of an electrically operated valve according to an embodiment of the present invention.

Fig. 2 is an enlarged longitudinal sectional view of a main portion in the vicinity of a valve port of an electric valve according to an embodiment of the present invention.

Fig. 3 is a diagram illustrating the operation of the valve port of the electric valve according to the embodiment of the present invention.

Fig. 4 is a diagram showing an example of an air conditioner using an electrically operated valve according to an embodiment of the present invention.

Fig. 5 is a diagram illustrating the operation of the valve port of the conventional motor-operated valve.

In the figure:

1-a valve housing, 1A-a valve chamber, 11-a first port, 12-a second port, 13-a third port, 14-a first tapered portion, 15-a second tapered portion, 21-a primary joint pipe, 22-a secondary joint pipe, 3-a support member, 4-a valve holder, 5-a valve core, 5 a-a needle valve, 6-a stepper motor, and X-axis.

Detailed Description

Next, an embodiment of the motor-operated valve according to the present invention will be described with reference to the drawings. Fig. 1 is a longitudinal sectional view of an electric valve according to an embodiment, fig. 2 is an enlarged longitudinal sectional view of a main portion in the vicinity of a valve port of the electric valve according to the embodiment, fig. 3 is a view for explaining an operation of the valve port of the electric valve according to the embodiment, and fig. 4 is a view showing an example of an air conditioner using the electric valve according to the embodiment.

First, an air conditioner according to an embodiment will be described with reference to fig. 4. The air conditioner includes the motor-operated valve 10 of the embodiment, an outdoor heat exchanger 20 mounted on an outdoor unit 100, an indoor heat exchanger 30 mounted on an indoor unit 200, a flow path switching valve 40, and a compressor 50, and these elements are connected by pipes as shown in the drawing to constitute a heat pump type refrigeration cycle. This refrigeration cycle is an example of a refrigeration cycle to which the electric valve of the present invention is applied, and the electric valve of the present invention can also be applied to other systems such as an indoor unit-side throttle device of a multi-type air conditioner for a building.

The flow path of the refrigeration cycle is switched by the flow path switching valve 40 to two flow paths, i.e., a heating mode and a cooling mode, and in the heating mode, the refrigerant compressed by the compressor 50 flows from the flow path switching valve 40 into the indoor heat exchanger 30, and the refrigerant flowing out of the indoor heat exchanger 30 flows into the electric valve 10 through the pipe line 60, as indicated by solid arrows. The refrigerant is expanded in the motor-operated valve 10 and circulates through the outdoor heat exchanger 20, the flow path switching valve 40, and the compressor 50 in this order. In the cooling mode, as indicated by a broken-line arrow, the refrigerant compressed by the compressor 50 flows from the flow path switching valve 40 into the outdoor heat exchanger 20, and the refrigerant flowing out of the outdoor heat exchanger 20 is expanded in the motor-operated valve 10, flows through the pipe line 60, and flows into the indoor heat exchanger 30. The refrigerant flowing into the indoor heat exchanger 30 flows into the compressor 50 via the flow switching valve 40. In the example shown in fig. 4, the refrigerant is caused to flow from the primary joint pipe 21 to the secondary joint pipe 22 of the electric valve 10 in the heating mode, but the connection of the pipes may be reversed, and the refrigerant may be caused to flow from the secondary joint pipe 22 to the primary joint pipe 21 in the heating mode.

The motor-operated valve 10 functions as an expansion device that controls the flow rate of the refrigerant, and in the heating mode, the outdoor heat exchanger 20 functions as an evaporator, and the indoor heat exchanger 30 functions as a condenser, thereby heating the inside of the room. In the cooling mode, the outdoor heat exchanger 20 functions as a condenser, and the indoor heat exchanger 30 functions as an evaporator, thereby performing cooling in the room.

Next, the motor-operated valve 10 according to the embodiment will be described with reference to fig. 1 and 2. The motor-operated valve 10 includes a valve housing 1, and a cylindrical valve chamber 1A is formed in the valve housing 1. The valve housing 1 is formed with a first port 11, a second port 12, and a third port 13. A first tapered portion 14 is formed between the first port 11 and the second port 12, and a second tapered portion 15 is formed between the second port 12 and the third port 13. Further, a primary joint pipe 2 communicating from the side surface side to the valve chamber 1A is attached to the valve housing 1, and a secondary joint pipe 22 is attached to one end portion of the valve chamber 1A in the axis X direction. The valve chamber 1A and the secondary joint pipe 22 can be communicated with each other through the first port 11, the first tapered portion 14, the second port 12, the second tapered portion 15, and the third port 13.

A support member 3 is attached to an upper portion of the valve housing 1. A guide hole 3a that is long in the axis X direction is formed in the support member 3, and a cylindrical valve holder 4 is fitted in the guide hole 3a so as to be slidable in the axis X direction. A valve holder 4 is mounted coaxially with the valve chamber 1A, and a valve body 5 having a needle valve 5a at an end thereof is fixed to a lower end portion of the valve holder 4. A spring seat 41 is provided in the valve holder 4 so as to be movable in the direction of the axis X, and a compression coil spring 42 is attached between the spring seat 41 and the valve body 5 in a state where a predetermined load is applied.

A case 61 of the stepping motor 6 is airtightly fixed to the upper end of the valve case 1 by welding or the like. A magnetic rotor 62 magnetized in a multi-pole manner in its outer periphery is rotatably provided in the housing 61, and a rotor shaft 63 is fixed to the magnetic rotor 62. The upper end of the rotor shaft 63 is rotatably fitted into a cylindrical guide 64 suspended from the top wall of the housing 61. A stator coil 65 is disposed on the outer periphery of the housing 61, and a pulse signal is applied to the stator coil 65 to rotate the magnetic rotor 62 in accordance with the number of pulses. Then, the rotor shaft 63 integrated with the magnetic rotor 62 is rotated by the rotation of the magnetic rotor 62. Further, a rotation stop mechanism 66 for the magnetic rotor 62 is provided on the outer periphery of the guide 64.

The upper end portion of the valve holder 4 is engaged with the lower end portion of the rotor shaft 63 of the stepping motor 6, and the valve holder 4 is rotatably suspended by the rotor shaft 63. The rotor shaft 63 is formed with a male screw portion 63a, and the male screw portion 63a is screwed to a female screw portion 3b formed in the support member 3.

According to the above configuration, the rotor shaft 63 moves in the axis X direction in accordance with the rotation of the magnetic rotor 62. The valve body 5 moves in the axis X direction together with the valve holder 4 due to the axial X direction movement of the rotor shaft 63 accompanying this rotation. The valve body 5 increases or decreases the opening area of the first port 11 at the portion of the needle valve 5a to control the flow rate of the fluid flowing from the primary joint pipe 21 to the secondary joint pipe 22.

The first port 11, the second port 12, and the third port 13 are formed in the shape of the side surfaces of a cylinder centered on the axis X, and as shown in fig. 2, the inner diameter D1 of the first port 11 is sized to fit the outer periphery of the needle valve 5 a. Further, the inner diameter D2 of the second port 12 is slightly larger than the inner diameter D1 of the first port 11. The inner diameter D3 of the third port 13 is a dimension that is larger than the inner diameter D21 of the second port 12 and is a dimension that is smaller than the inner diameter D4 of the secondary junction tube 22. In fig. 2, "Φ" indicating the diameter is given to each of the diameters D1 to D4. The length L1 of the first port 11 is a dimension less than the inner diameter D1 and the combined length L2 of the first tapered portion 14 and the second port 12 is a dimension greater than the length L1 of the first port 11. The combined length L3 of the second cone 15 and the third port 13 is a greater dimension than the combined length L2 of the first cone 14 and the second port 12.

The first tapered portion 14 and the second tapered portion 15 are formed in the shape of the side surfaces of a truncated cone centered on the axis X, the inner surface of the first tapered portion 14 is formed in a shape in which the inner diameter is enlarged from the first port 11 to the second port 12, and the inner surface of the second tapered portion 15 is formed in a shape in which the inner diameter is enlarged from the second port 12 to the third port 13. Then, a taper angle θ 1 as an opening angle of the first tapered portion 14 and a taper angle θ 2 as an opening angle of the second tapered portion 15 are appropriately set. Note that these dimensions and angles are not limited to the example shown in fig. 2, and the conditions of these dimensions and angles will be described below.

As shown in fig. 3, the refrigerant having passed through the gap between the needle valve 5a and the first port 11 flows into the secondary joint pipe 22 through the first tapered portion 14, the second port 12, the second tapered portion 15, and the third port 13. At this time, the gap between the needle valve 5a and the first port 11 is the narrowest portion where the flow velocity is maximized, but the length L1 of the first port 11 is as short as possible, and the refrigerant passing through the gap flows along the inner wall of the second port 12 immediately following the shape of the first tapered portion 14. The inner diameter D2 of the second port 12 is only slightly larger than the inner diameter D1 of the first port 11 so that the pressure is not abruptly restored during the flow from the first port 11 to the second port 12. Also, since the length of the second port 12 is long, the flow of the refrigerant is rectified at the second port 12. Therefore, the collapse of the cavitation bubbles can be suppressed, and the flow of the refrigerant can be stabilized.

The refrigerant after passing through the second port 12 flows into the third port 13 while returning to the pressure, that is, while increasing the pressure, following the shape of the second tapered portion 15. Since the inner diameter D3 of the third port 13 is larger than the inner diameter D2 of the second port 12, the flow velocity is decelerated while the flow follows the shape of the second tapered portion 15. That is, the flow velocity is immediately decelerated while being rectified to some extent at the second port 12, so that the flow velocity sound is reduced. Further, although the flow of the refrigerant decelerated by the second tapered portion 15 flows to the third port 13, the flow of the refrigerant is rectified at the second port 12, and therefore, the flow of the refrigerant is less likely to be turbulent in the third port 13, and the collapse of the cavitation bubbles can be suppressed.

In this way, the flow velocity can be decelerated while maintaining the flow rectification at the second tapered portion 15 by rectifying the flow to some extent at the second port 12 and flowing to the third port 13 via the second tapered portion 15. This reduces the turbulent flow at the third port 13 to suppress the collapse of the cavity, and reduces the flow velocity at the second tapered portion 15 to reduce the flow velocity noise. That is, the length of the second port 12 is shorter than that of the second port in patent document 1, and accordingly, the flow velocity sound can be reduced.

The electric valve 10 in the embodiment has a high effect of reducing the flow velocity noise when the pressure difference between the primary joint pipe 21 and the secondary joint pipe 22 is high, and the dimensions and angles of the respective portions of the first port 11, the second port 12, the third port 13, the first tapered portion 14, the second tapered portion 15, and the secondary joint pipe 22 are set to satisfy the following conditions.

Hereinafter, the conditions of the size and angle of each part of the embodiment in which the effect of reducing the flow velocity sound is high when the pressure difference between the primary joint pipe 21 and the secondary joint pipe 22 is high will be described. The inner diameter D1 of the first port 11 is more than or equal to 1mm and less than or equal to D1 and less than or equal to 4.5mm,

the inner diameter D2 of the second port 12 is more than or equal to 1.15mm and less than or equal to D2 and less than or equal to 4.9mm,

the inner diameter D3 of the third port 13 is more than or equal to 4.6mm and less than or equal to D3 and less than or equal to 6.35mm,

the inner diameter D4 of the secondary joint 22 is not less than 6.35mm and not more than D4.

The taper angle theta 1 of the first taper part 14 is in the range of 60 DEG to theta 1 to 150 DEG,

the taper angle theta 2 of the second tapered portion 15 is in the range of 20 DEG to theta 2 to 90 deg.

The length L1 of the first port 11 is 0.1mm L1 mm 0.5mm, and the shorter the L1, the lower the noise.

The length L2 of the first conical part 14 and the second port 12 is 0.5mm & lt L2 & lt 3.9mm,

the combination of the lengths L1 and L2 is set such that L1+ L2 is set to 1 mm. ltoreq. L1+ L2. ltoreq.4 mm.

And, the sum L1+ L2+ L3 of the length L1 of the first port 11, the length L2 of the first tapered portion 14 and the second port 12, and the length L3 of the second tapered portion 15 and the third port 13 is 6 mm. ltoreq.L 1+ L2+ L3. ltoreq.23 mm.

The ratio L2/L1 between the length L2 of the first tapered portion 14 and the second port 12 and the length L1 of the first port 11 is in the range of 1. ltoreq. L2/L1. ltoreq.39,

the ratio L3/L2 of the length L3 of the second tapered portion 15 and the third port 13 to the length L2 of the first tapered portion 14 and the second port 12 is in the range of 0.57. ltoreq.L 3/L2. ltoreq.38,

the size ratio D2/D1 of the inner diameter D2 of the second port 12 to the inner diameter D1 of the first port 11 is in the range of 1.03 to 1.5 of D2/D1,

the size ratio D3/D2 of the inner diameter D3 of the third port 13 to the inner diameter D2 of the second port 12 is in the range of 1.02 ≤ D3/D2 ≤ 5.52.

Next, the actual measurement examples of the respective size ratios and noise reduction of the motor-operated valve according to the embodiment will be described. In this actual measurement example, under operating conditions in which the pressure in the primary joint pipe 21 is 2.8 to 3.4(MPa) and the pressure in the secondary joint pipe 22 is 1.2 to 1.8(MPa), the noise measured in the electric valve of the embodiment and the noise measured in the electric valve of patent document 1 (conditions thereof) were compared. That is, the present invention is an actual measurement example showing a particularly significant noise reduction effect under the condition that a flow velocity sound is likely to be generated at the time of high load. The actual measurement examples are shown in tables 1 to 6 below. In tables 1 to 6, the sound pressure is reduced by 2dB or more compared with the noise in the motor-operated valve of patent document 1 as indicated by "o", and the sound pressure is reduced by 1 to 2dB compared with the noise in the motor-operated valve of patent document 1 as indicated by "o". Further, the ". smallcircle" indicates that the sound pressure reduction is 1dB or less. Further, the a characteristic is used to evaluate the sound pressure.

Table 1 shows the relationship between L2/L1 and θ 1.

[ TABLE 1 ]

(L2/L1) relationship with θ 1

Table 2 shows the relationship between L2/L1 and D2/D1. [ TABLE 2 ]

Relationship between (L2/L1) and (D2/D1)

Table 3 shows the relationship between L2/L1 and θ 2.

[ TABLE 3 ]

(L2/L1) relationship with θ 2

Table 4 shows the relationship between L2/L1 and D3/D2.

[ TABLE 4 ]

Relationship between (L2/L1) and (D3/D2)

Table 5 shows the relationship between D3/D2 and θ 2.

[ TABLE 5 ]

(D3/D2) relationship with θ 2

Table 6 shows the relationship between D3/D2 and L3/L2.

TABLE 6 relationship between (D3/D2) and (L3/L2)

As is clear from the above table, by providing the third port and the second tapered portion, noise reduction is achieved more than in the past. Even when the pressure difference between the primary joint pipe 21 and the secondary joint pipe 22 is high, the noise can be reduced by 1dB or more within the range of "o" and "o", and a more significant effect can be obtained.

While the embodiments of the present invention have been described in detail with reference to the drawings, the specific configurations are not limited to these embodiments, and design changes and the like within a range not departing from the gist of the present invention are also included in the present invention.

Claims

1. An electric valve in which a valve chamber communicating with a primary joint pipe and a secondary joint pipe can communicate with each other through a valve port, the valve port including a first port provided on a valve chamber side and having an opening area increased or decreased by a needle valve, a second port having an inner diameter larger than that of the first port, and a port at an end of the valve port on the secondary joint pipe side,

The inner diameter of the end port is larger than the inner diameter of the second port,

the first port and the second port are connected by a first tapered portion, a second tapered portion is connected to the second port on the secondary joint pipe side,

the first port, the second port and the end port are formed in the shape of a side surface of a cylinder centered on an axis X,

the inner diameter of the port from the second port to the end portion is increased by a larger amount than the inner diameter from the first port to the second port,

the total length of the first tapered portion and the second port is shorter than the total length from the end of the second tapered portion on the second port side to the end of the port on the secondary joint pipe side of the end.

2. Electrically operated valve according to claim 1,

the length of the second port is longer than the length of the first port with respect to the direction of the axis.

3. Electrically operated valve according to claim 1,

the wall thickness of the end port is thinner than the wall thickness of the secondary joint pipe.

4. Electrically operated valve according to claim 1,

the amount of expansion of the inner diameter from the first port to the end port is greater than the amount of expansion of the inner diameter from the end port to the secondary adapter pipe.

5. Electrically operated valve according to claim 1,

the length of the second port is shorter than the length from the opening on the secondary joint pipe side in the second port to the opening on the secondary joint pipe side in the port of the end portion.

6. Electrically operated valve according to claim 5,

the taper angle of the taper connecting the first port and the second port is larger than the taper angle of the taper connecting the second port and the end portion.

7. Electrically operated valve according to claim 1,

the valve port is provided with the secondary joint pipe having an inner diameter not smaller than the end port.