JP2019070449A - Motor valve and refrigeration cycle system - Google Patents

Abstract

To reduce noise caused by flow of a refrigerant in a valve port at a motor valve which opens or closes the valve port with a needle valve to control a flow rate of the refrigerant.SOLUTION: A valve housing 1 is formed with a first port 11 having a circular cross section and an inner diameter D1, a second port 12 having an inner diameter D2, a third port 13 having an inner diameter D3, a first taper part 14, and a second taper part 15. When a refrigerant flowing from a gap between the first port 11 and a needle valve 5a flows into the second port 12, the flow is rectified to be stabilized without rapidly recovering pressure in the second port 12. The action inhibits rupture of cavitation. When the refrigerant flows from the second port 12 to the second taper part 15 and the third port 13, a flow velocity is reduced to reduce flow velocity sound.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a needle valve type motor-operated valve for controlling the flow rate of refrigerant in an air conditioner or the like, and more particularly to a motor-operated valve in which the shape of a valve port for the needle valve is improved.

  Heretofore, in the refrigeration cycle, noise accompanying fluid passage, which is generated from a motor-operated valve that controls the flow rate of refrigerant, is often problematic. For example, Japanese Patent No. 5696093 (Patent Document 1) discloses a motor-operated valve designed to take such noise measures.

  In the motor-operated valve of Patent Document 1, the valve port is configured 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 slightly larger than the inner diameter of the first port, and the length of the second port is sufficiently longer than the length of the first port.

  And in the thing of patent document 1, as shown in FIG. 5, the refrigerant | coolant which passed through the clearance gap between needle valve a and the 1st port b flows to the secondary joint pipe side through the taper part c and the 2nd port d. . At this time, the flow of the refrigerant that has passed through the gap between the needle valve a and the first port b follows the taper portion c and flows along the inner wall of the second port d. The inner diameter of the second port d is only slightly larger than the inner diameter of the first port b, and the pressure does not rapidly recover while flowing 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 burst of cavitation can be suppressed, the flow of the refrigerant can be stabilized, and the noise can be reduced.

Patent No. 5696093

  Although the invention of Patent Document 1 also has the effect of reducing noise, it may generate noise in a specific refrigerant state. For example, Patent Document 1 can rectify fluid flow at the second port, but the second port has a slightly larger inner diameter than the first port, and its length is sufficiently larger than that of the first port. It is getting longer. Therefore, although the fluid is rectified, the flow velocity in the second port does not decrease, and noise may be generated due to the flow velocity noise (sound caused by the high flow velocity). In particular, when the load is high, the differential pressure across the valve port is high, and this flow velocity noise is a major cause of noise.

  An object of the present invention is to provide a motor-operated valve with reduced noise by improving the valve port.

  The motor-operated valve according to claim 1 is a motor-operated valve which enables communication between a valve chamber to which a primary joint pipe is in communication and a secondary joint via a valve port which is opened and closed by a needle valve. In a motor-operated valve including a first port on the chamber side, a second port having a larger inner diameter than the first port, and a first taper portion connecting the first port and the second port, the valve port And a second tapered portion connecting the second port and the third port, wherein an inner diameter D1 of the first port, an inner diameter D2 of the second port, and the third port are provided. The relationship between the port and the inner diameter D3 is D1 <D2 <D3, and the first port, the second port, and the third port have the shape of a side surface of a cylinder centered on each axis. The taper angle of the first taper portion is the taper angle of the second taper portion In the direction of the axis, the combined length of the second tapered portion and the third port is longer than the combined length of the first tapered portion and the second port. It features.

The motor operated valve according to claim 2 is the motor operated valve according to claim 1, wherein
D2-D1 ≦ D3-D2
Motor-operated valve characterized by being.

In the motor-operated valve, the taper angle of the first taper portion is θ1, the taper angle of the second taper portion is θ2, the length of the first port is L1, and the lengths of the first taper portion and the second port When the length is L2, and the length between the second tapered portion and the third port is L3,
1 mm ≦ D1 ≦ 4.5 mm,
60 ° ≦ θ1 ≦ 150 °,
20 ° ≦ θ2 ≦ 90 °,
0.1 mm ≦ L1 ≦ 0.5 mm,
1 ≦ L2 / L1 ≦ 39
1 <L3 / L2 ≦ 38
1.03 ≦ D2 / D1 ≦ 1.5
1.02 ≦ D3 / D2 ≦ 5.52
It is preferable that

  According to the motor-operated valve of the first or second aspect, when the refrigerant flowing from the gap between the first port and the needle valve flows out to the second port, the pressure is not rapidly recovered in the second port, and the flow is It is possible to stabilize the flow of the refrigerant by rectifying it and to suppress the cavitation burst. Furthermore, since the flow velocity is reduced when flowing from the second port to the second tapered portion and the third port, the flow velocity noise can be reduced. Therefore, noise can be reduced.

  According to the motor-operated valve of claim 2, since D2-D1 D D3-D2, the diameter is greatly expanded from the second tapered portion to the third port with respect to the second port, so the velocity reduction effect of the flow velocity is obtained. It is possible to further increase the flow velocity noise.

It is a longitudinal cross-sectional view of the motor operated valve of embodiment of this invention. It is a principal part enlarged longitudinal cross-sectional view of the valve port vicinity in the motor operated valve of embodiment of this invention. It is a figure explaining the effect | action of the valve port in the motor operated valve of embodiment of this invention. It is a figure which shows an example of the air conditioner using the motor operated valve of embodiment of this invention. It is a figure explaining the effect | action of the valve port of the conventional motor operated valve.

  Next, an embodiment of the motor operated valve of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of the motor-operated valve of the embodiment, FIG. 2 is an enlarged longitudinal cross-sectional view of an essential part in the vicinity of the valve port in the motor-operated valve of the embodiment, and FIG. FIG. 4 is a view showing an example of an air conditioner using the motor-operated valve of the embodiment.

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

  The flow path of the refrigeration cycle is switched to two flow paths of the heating mode and the cooling mode by the flow path switching valve 40, and in the heating mode, as shown by solid arrows, the refrigerant compressed by the compressor 50 is flow path switched The refrigerant flowing into the indoor heat exchanger 30 from the valve 40 and flowing out from the indoor heat exchanger 30 flows into the motor-operated valve 10 through the pipe line 60. Then, the refrigerant is expanded by the motor-operated valve 10 and circulated in the order of the outdoor heat exchanger 20, the flow path switching valve 40, and the compressor 50. In the cooling mode, the refrigerant compressed by the compressor 50 flows into the outdoor heat exchanger 20 from the flow path switching valve 40 and the refrigerant flowing out of the outdoor heat exchanger 20 flows through the motor-operated valve 10 as shown by the broken arrow. It is expanded, flows through the pipe 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 path switching valve 40. In the example shown in FIG. 4, the refrigerant is flowed from the primary joint pipe 21 to the secondary joint pipe 22 of the motor operated valve 10 in the heating mode, but the pipe connection is reversed and the heating mode is selected. The refrigerant may be made to flow from the secondary joint pipe 22 to the primary joint pipe 21.

  The motor operated valve 10 functions as a throttling device for controlling the flow rate of the refrigerant, and in the heating mode, the outdoor heat exchanger 20 functions as an evaporator, the indoor heat exchanger 30 functions as a condenser, and the room is heated. . In the cooling mode, the outdoor heat exchanger 20 functions as a condenser, and the indoor heat exchanger 30 functions as an evaporator, thereby cooling the room.

  Next, the motor operated valve 10 of the embodiment will be described based on FIGS. 1 and 2. The motor-operated valve 10 has a valve housing 1, and a cylindrical cylindrical valve chamber 1 A is formed in the valve housing 1. Further, a first port 11, a second port 12 and a third port 13 are formed in the valve housing 1. Further, a first taper portion 14 is formed between the first port 11 and the second port 12, and a second taper portion 15 is formed between the second port 12 and the third port 13. Furthermore, a primary joint pipe 21 communicating with the valve chamber 1A from the side is attached to the valve housing 1, and a secondary joint pipe 22 is attached to one end of the valve chamber 1A in the direction of the axis X. The valve chamber 1A and the secondary joint pipe 22 can be electrically connected via 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 the top of the valve housing 1. A guide hole 3a long in the direction of the axis X is formed in the support member 3, and a cylindrical valve holder 4 is slidably fitted in the direction of the axis X in the guide hole 3a. The valve holder 4 is mounted coaxially with the valve chamber 1A, and a valve body 5 having a needle valve 5a at its end is fixed to the lower end of the valve holder 4. In the valve holder 4, a spring receiver 41 is provided movably in the direction of the axis X, and a compression coil spring 42 is attached between the spring receiver 41 and the valve body 5 in a state where a predetermined load is applied. ing.

  The case 61 of the stepping motor 6 is airtightly fixed to the upper end of the valve housing 1 by welding or the like. In the case 61, a magnet rotor 62 whose outer peripheral portion is magnetized into multiple poles is rotatably provided, and a rotor shaft 63 is fixed to the magnet rotor 62. An upper end portion of the rotor shaft 63 is rotatably fitted in a cylindrical guide 64 suspended from a ceiling portion of the case 61. A stator coil 65 is disposed on the outer periphery of the case 61. When a pulse signal is given to the stator coil 65, the magnet rotor 62 is rotated according to the number of pulses. The rotation of the magnet rotor 62 rotates the rotor shaft 63 integral with the magnet rotor 62. A rotation stopper mechanism 66 for the magnet 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 supported by the rotor shaft 63 so as to be rotatably suspended. Further, a male screw portion 63 a is formed on the rotor shaft 63, and the male screw portion 63 a is screwed to a female screw portion 3 b formed on the support member 3.

  With the above configuration, the rotor shaft 63 moves in the direction of the axis X along with the rotation of the magnet rotor 62. By the movement of the rotor shaft 63 in the direction of the axis X along with the rotation, the valve holder 5 is moved together with the valve holder 4 in the direction of the axis X. And the valve body 5 increases / decreases the opening area of the 1st port 11 in the part of the needle valve 5a, and controls the flow volume of the fluid which flows 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 in the shape of a side of a cylinder centered on the axis X, and as shown in FIG. 2, the inner diameter D1 of the first port 11 is the needle valve 5a. It is the size according to the circumference of. 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 larger than the inner diameter D21 of the second port 12 and smaller than the inner diameter D4 of the secondary joint pipe 22. In FIG. 2, “φ” indicating the diameter is appended to each of the diameters D1 to D4. The length L1 of the first port 11 is smaller than the inner diameter D1, and the total length L2 of the first tapered portion 14 and the second port 12 is larger than the length L1 of the first port 11 It has become. The combined length L3 of the second tapered portion 15 and the third port 13 is larger than the combined length L2 of the first tapered portion 14 and the second port 12.

  The first tapered portion 14 and the second tapered portion 15 have a shape of a side surface of a truncated cone centered on the axis line X, and the inner side surface of the first tapered portion 14 has an inner diameter from the first port 11 to the second port 12 The inner side surface of the second tapered portion 15 has a shape in which the inner diameter is expanded from the second port 12 to the third port 13. A taper angle θ1 which is an opening angle of the first taper portion 14 and a taper angle θ2 which is an opening angle of the second taper portion 15 are appropriately set. These dimensions and angles are not limited to those shown in FIG. 2, and the conditions of these dimensions and angles will be described later.

  As shown in FIG. 3, the refrigerant having passed through the gap between the needle valve 5 a and the first port 11 passes through the first tapered portion 14, the second port 12, the second tapered portion 15 and the third port 13 to form a secondary joint Flow to tube 22. At this time, the gap between the needle valve 5a and the first port 11 is the narrowest point, and the flow velocity is maximum at this point, but the length L1 of the first port 11 is as short as possible. The flow of the refrigerant immediately follows the first taper portion 14 and flows along the inner wall of the second port 12. The inner diameter D2 of the second port 12 is only slightly larger than the inner diameter D1 of the first port 11, and the pressure does not suddenly recover while flowing from the first port 11 to the second port 12. Further, since the length of the second port 12 is long, the refrigerant flow is rectified at the second port 12. Therefore, the rupture of cavitation can be suppressed, and the flow of the refrigerant can be stabilized.

  The flow of the refrigerant passing through the second port 12 flows to the third port 13 while recovering or increasing the pressure following 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 reduced while flowing along the second tapered portion 15. That is, the flow velocity noise is reduced because the flow velocity is immediately reduced while the second port 12 is partially rectified. Furthermore, the flow of refrigerant decelerated through the second taper portion 15 flows to the third port 13, but since the flow of refrigerant is already rectified at the second port 12, the flow of refrigerant is reduced in the third port 13. The refrigerant flow is less likely to be disturbed, and cavitation bursting can be suppressed.

  As described above, by rectifying the second port 12 to a certain extent and supplying the second port 12 to the third port 13 through the second taper portion 15, the flow velocity can be reduced while maintaining the rectification in the second taper portion 15. Thereby, the disturbance of the flow in the third port 13 can be reduced to suppress the cavitation burst, and the flow velocity can be reduced by the second taper portion 15 to reduce the flow velocity noise. That is, since the length of the second port 12 is shorter than that of Patent Document 1, the flow velocity noise can be reduced.

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

Below, when the pressure difference between the primary joint pipe 21 and the secondary joint pipe 22 is high, conditions of dimensions and angles of each part of the embodiment in which the reduction effect of the flow velocity sound is high will be shown. The inner diameter D1 of the first port 11 is
1 mm ≦ D1 ≦ 4.5 mm
And the inner diameter D2 of the second port 12 is
1.15 mm ≦ D2 ≦ 4.9 mm
And the inner diameter D3 of the third port 13 is
4.6 mm ≦ D3 ≦ 6.35 mm
And the inner diameter D4 of the secondary joint 22 is
6.35 mm ≦ D4
It is.

Further, the taper angle θ1 of the first taper portion 14 is
60 ° ≦ θ1 ≦ 150 °
And the taper angle θ 2 of the second taper portion 15 is
20 ° ≦ θ2 ≦ 90 °
Range.

Also, the length L1 of the first port 11 is
0.1 mm ≦ L1 ≦ 0.5 mm
The noise decreases as this L1 is shorter. The length L2 of the first taper portion 14 and the second port 12 is
0.5 mm ≦ L2 ≦ 3.9 mm
In combination with these lengths L1 and L2, L1 + L2 is
1 mm ≦ L1 + L2 ≦ 4 mm
It is set by the condition which becomes. Further, the sum L1 + L2 + L3 of the length L1 of the first port 11, the lengths L2 of the first tapered portion 14 and the second port 12, and the lengths L3 of the second tapered portion 15 and the third port 13 is
6 mm ≦ L1 + L2 + L3 ≦ 23 mm
It is.

Further, the ratio L2 / L1 of the length L2 of the first taper portion 14 and the second port 12 and the length L1 of the first port 11 is
1 ≦ L2 / L1 ≦ 39
The ratio L3 / L2 of the length L3 of the second taper portion 15 and the third port 13 and the length L2 of the first taper portion 14 and the second port 12 is
0.57 <L3 / L2 ≦ 38 (preferably, 1 <L3 / L2 ≦ 38)
The dimensional ratio D2 / D1 of the inner diameter D2 of the second port 12 to the inner diameter D1 of the first port 11 is
1.03 ≦ D2 / D1 ≦ 1.5
The dimensional ratio D3 / D2 of the inner diameter D3 of the third port 13 to the inner diameter D2 of the second port 12 is
1.02 ≦ D3 / D2 ≦ 5.52
Range.

  Next, an example of measurement of each dimension ratio and noise reduction of the motor operated valve of the embodiment will be described. In this operating example, 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 by the motor-operated valve of the embodiment is compared with the noise measured by the motor-operated valve (the condition thereof) of Patent Document 1. That is, this is an example of measurement showing that the effect of noise reduction is particularly remarkable under the condition that flow velocity noise is easily generated at high load. The measurement examples are shown in Tables 1 to 6 below. In Tables 1 to 6, “○○○” indicates that the sound pressure is reduced by 2 dB or more than the noise in the motor-operated valve of Patent Document 1 and “○○” indicates that the sound pressure is reduced by 1 to 2 dB. It shows. Moreover, the case where the drop in sound pressure is 1 dB or less is indicated by “o”. Sound pressure is evaluated using A characteristic.

  Table 1 shows the relationship between L2 / L1 and θ1.

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

  Table 3 shows the relationship between L2 / L1 and θ2.

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

  Table 5 shows the relationship between D3 / D2 and θ2.

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

  As can be seen from these tables, the provision of the third port and the second tapered portion achieves noise reduction more than in the prior art. Further, even when the pressure difference between the primary joint pipe 21 and the secondary joint pipe 22 is high, noise can be reduced by 1 dB or more by setting in the range of “○○” and “○○○”, which is more remarkable. You can get the effect.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and changes in design etc. within the scope of the present invention are not limited. Are included in the present invention.

DESCRIPTION OF SYMBOLS 1 valve housing 1A valve chamber 11 1st port 12 2nd port 13 3rd port 14 1st taper part 15 2nd taper part 21 primary joint pipe 22 secondary joint pipe 3 support member 4 valve holder 5 valve body 5a needle valve 6 Stepping motor X axis

The present invention relates to a needle valve type motor-operated valve that controls the flow rate of refrigerant in an air conditioner or the like, and more particularly, a motor-operated valve having an improved shape of a valve port for the needle valve , and a refrigeration cycle system including such motor-operated valve About.

An object of the present invention is to provide a motor-operated valve with reduced noise by improving the valve port , and a refrigeration cycle system including such a motor-operated valve .

Electric valve according to claim 1, and a valve chamber in which the primary joint pipe is communicated with a secondary coupling tube, an electric valve that passes with each other through the valve port, the valve port, provided in the valve chamber side A motor-operated valve comprising a first port whose opening area is increased or decreased by a needle valve, a second port whose inner diameter is larger than the first port, and a first tapered portion connecting the first port and the second port The valve port includes a third port located on the secondary joint pipe side, and a second tapered portion connecting the second port and the third port, and the inner diameter D1 of the first port and the second port The relationship between the inner diameter D2 of the port and the inner diameter D3 of the third port is D1 <D2 <D3, and the first port, the second port, and the third port are centered on their respective axes. has the shape of a side surface of the cylinder, the direction of said axis, said first The length of the port, and wherein the shorter than the length from the opening of the secondary coupling tube side in the second port to the opening of the secondary coupling tube side of the valve port.
The motor-operated valve according to claim 2 is a motor-operated valve in which the valve chamber to which the primary joint pipe is in communication and the secondary joint pipe are in communication via the valve port, and the valve port is provided on the valve chamber side A motor-operated valve comprising a first port whose opening area is increased or decreased by a needle valve, a second port whose inner diameter is larger than the first port, and a first tapered portion connecting the first port and the second port. The valve port includes a third port located on the secondary joint pipe side, and a second tapered portion connecting the second port and the third port, and the inner diameter D1 of the first port and the second port The relationship between the inner diameter D2 of the first port and the inner diameter D3 of the third port is D1 <D2 <D3, and the first port, the second port, and the third port are cylinders centered on their respective axes. The shape of the side surface of the Assuming that the length of the port is L1, the length of the first tapered portion and the second port is L2, and the length of the second tapered portion and the third port is L3, 1 ≦ L3 / L2 ≦ It is characterized in that it is five.
The motor-operated valve according to claim 3 is the motor-operated valve according to claim 1 or 2, characterized in that the first tapered portion and the first tapered portion are extended from the first port to the opening on the secondary joint pipe side in the valve port. The inner diameter is expanded over a plurality of steps including a 2-tapered portion, and the diameter expansion ratio is set to be greater than 1.5 times in at least one of the plurality of steps. .
The motor-operated valve according to claim 4 is the motor-operated valve according to any one of claims 1 to 3, wherein the inner diameter of the second port is larger than the length of the second port, and the third port The inner diameter of the second port is larger than the length of the third port.
The motor-operated valve according to claim 5 is the motor-operated valve according to any one of claims 1 to 4, wherein the inner diameter of the secondary joint pipe is three or more times the inner diameter of the first port. It is characterized by
The refrigeration cycle system according to claim 6 comprises a compressor for compressing a refrigerant, a condenser for condensing the compressed refrigerant, an expansion device for expanding the condensed refrigerant, and an evaporator for evaporating the expanded refrigerant. And the motor-operated valve according to any one of claims 1 to 5 is used as the throttling device.

Electric valve train is,
D2-D1 ≦ D3-D2
It is preferable that

According to the motor-operated valve of claims 1 to 5 and the refrigeration cycle system of claim 6, when the refrigerant flowing from the gap between the first port and the needle valve flows out to the second port, the pressure is rapidly increased in the second port. Without recovering, the flow can be rectified to stabilize the flow of the refrigerant, and cavitation burst can be suppressed. Furthermore, since the flow velocity is reduced when flowing from the second port to the second tapered portion and the third port, the flow velocity noise can be reduced. Therefore, noise can be reduced.

Further , according to the preferred motor-operated valve described above, since D2-D1 ≦ D3-D2, the diameter is greatly expanded from the second tapered portion to the third port with respect to the second port, so the flow velocity is reduced. The effect is enhanced, and the flow velocity noise can be further reduced.

Claims (1)

A motor-operated valve enabling communication between a valve chamber to which a primary joint pipe is communicated and a secondary joint via a valve port opened and closed by a needle valve, wherein the valve port has a first port on the valve chamber side, In a motor-operated valve provided with a second port having a larger inner diameter than a first port, and a first taper portion connecting the first port and the second port,
The valve port includes a third port located on the secondary joint pipe side, and a second tapered portion connecting the second port and the third port, and the inner diameter D1 of the first port and the second port The relationship between the inner diameter D2 of the second port and the inner diameter D3 of the third port is D1 <D2 <D3.
The first port, the second port, and the third port have a shape of a side surface of a cylinder centered on each axis,
The taper angle of the first taper portion is larger than the taper angle of the second taper portion,
In the direction of the axis, the combined length of the second tapered portion and the third port is longer than the combined length of the first tapered portion and the second port. valve.

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