JPWO2014083627A1 - Refrigerant distributor - Google Patents

Abstract

The refrigerant distributor (100) includes a main body (1), a pipe (2) through which the refrigerant flows into the main body (1), and the refrigerant distributed in the main body (1) into a plurality of heat exchange units (25a, 25b) and a plurality of connection pipes (3a, 3b) that respectively flow out, and a plurality of openings (31a, 31b) provided in the main body (1) and communicating with the plurality of connection pipes (3a, 3b), respectively. Heat is generated from the pressure of the refrigerant on the piping (2) side of the plurality of regulating valves (30a, 30b) whose opening degree is adjusted by the plurality of valve bodies (12a, 12b) and the openings (31a, 31b) in the main body (1). Based on the pressure difference obtained by subtracting the refrigerant pressure at the outlet on the side opposite to the connection pipe (3a, 3b) of the exchange unit (25a, 25b), the opening of the adjusting valve (30a, 30b) increases as the pressure difference increases. A drive device (40) for reducing . Thereby, the refrigerant | coolant divider | distributor (100) which can adjust the shunt ratio of a refrigerant | coolant according to various disturbances can be provided.

Description

  The present invention relates to a refrigerant distributor, and more particularly, to a refrigerant distributor used in an air conditioner.

  As a refrigerant distributor used in an air conditioner, a technique described in Japanese Patent Laid-Open No. 2003-4340 (Patent Document 1) is known. In this patent document 1, “a plurality of first valve bodies 5 that open and close the open ends of a plurality of outflow pipes 2 in the container body 3 that is a sealed container, and the plurality of first valve bodies 5 that are opened to the opening. An urging member 6 that urges each end so as to release the end, and a front end portion of the plurality of first valve bodies 5 approaches or abuts against the opening end against the urging force by the urging member 6. The adjusting unit 7 is composed of a cam 13 that adjusts the opening degree and the driving unit 8 that drives the adjusting unit 7, and arbitrarily adjusts the flow rate of the refrigerant branched into the plurality of outflow pipes 2. The adjusting means 4 is provided "(see the summary).

JP 2003-4340 A

  By the way, the shunt ratio of the refrigerant distributor used in the air conditioner for distributing the gas-liquid two-phase refrigerant flows in the indoor heat exchanger having a plurality of heat exchange units installed on the downstream side of the refrigerant distributor. Changes under the influence of pressure loss according to the flow rate of the refrigerant.

  The refrigerant distributor described in Patent Document 1 is connected to the body by arbitrarily adjusting the flow ratio of the refrigerant by adjusting the opening degree of the plurality of valve bodies by a plurality of cams incorporated in the body. Distribute the refrigerant to a plurality of outlet pipes. Therefore, according to the refrigerant distributor described in Patent Document 1, when the rotation speed or temperature condition of the compressor of the air conditioner changes, it is possible to select an appropriate diversion ratio corresponding to the change, and heat exchange The efficiency of the vessel is not reduced. That is, even if there is a change in the pressure loss in the indoor heat exchanger as a result of changes in the flow rate of the refrigerant flowing in the indoor heat exchanger due to changes in the rotational speed and temperature conditions of the compressor, An appropriate diversion ratio may be calculated in advance during design and adjusted during operation.

  However, the flow dividing ratio of the refrigerant distributor used in the air conditioner is influenced and changed not only by the pressure loss generated in the indoor heat exchanger but also by the refrigerant distributor itself. Specifically, the flow dividing ratio of the refrigerant distributor is the state of the two-phase flow of the refrigerant flowing into the refrigerant distributor in the gas-liquid two-phase state, the installation angle and manufacturing accuracy of the refrigerant distributor, and the air on which the refrigerant distributor is mounted. It changes also by other various disturbances, such as an installation angle of a harmony device main part.

  On the other hand, the diversion ratio adjusted in the refrigerant distributor described in Patent Document 1 is designed in accordance with changes in the rotational speed of the compressor and temperature conditions by a combination of cam diameter ratios of a plurality of cams provided in the container body. Sometimes it is uniquely determined. For this reason, the refrigerant distributor described in Patent Document 1 can control the diversion ratio according to the change in the refrigerant flow rate due to the change in the rotational speed of the compressor and the temperature condition. Has a problem that it cannot respond.

  This invention is made | formed in view of an above described situation, and makes it a subject to provide the refrigerant distributor which can adjust the diversion ratio of a refrigerant | coolant according to various disturbances.

  In order to achieve the above-described object, a refrigerant distributor according to the present invention includes a main body having a space therein, a pipe through which the refrigerant flows into the main body, and the refrigerant distributed in the main body. A plurality of connecting pipes that respectively flow out toward the exchange part, a plurality of adjusting valves that are provided in the main body and that respectively adjust a plurality of openings that communicate with the plurality of connecting pipes by a plurality of valve bodies; Based on the pressure difference obtained by subtracting the pressure of the refrigerant at the outlet on the opposite side of the connection pipe of the heat exchange section from the pressure of the refrigerant on the piping side of the opening in the main body, the adjustment valve increases as the pressure difference increases. A driving device for reducing the opening degree of the.

According to the present invention, the adjusting valve of the refrigerant distributor adjusts the diversion ratio when the refrigerant is distributed toward each heat exchange unit based on the pressure loss from the refrigerant distributor to the outlet of each heat exchange unit. be able to. Therefore, the control amount of the diversion ratio is not disturbed by various disturbances such as refrigerant flow conditions, temperature conditions, refrigerant distributor installation angle and manufacturing accuracy. As a result, the path balance in the plurality of heat exchanging units can be maintained appropriately, and the performance of the heat exchanging units can be always kept in a good state.
That is, according to the present invention, it is possible to provide a refrigerant distributor capable of adjusting the refrigerant diversion ratio according to various disturbances.

It is a figure showing the outline of the whole composition of the air harmony device to which the refrigerant distributor concerning a 1st embodiment is applied. It is a partial cross section front view showing the outline of the composition of the refrigerant distributor concerning a 1st embodiment. It is a figure which shows the outline of the whole structure of the air conditioning apparatus with which the refrigerant distributor which concerns on 2nd Embodiment is applied. It is a section front view showing the outline of the composition of the refrigerant distributor concerning a 1st embodiment.

Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
Note that, in the drawings shown below, the same members or corresponding members are denoted by the same reference numerals, and redundant description is omitted. In addition, the size and shape of the member may be schematically represented by being modified or exaggerated for convenience of explanation.

<< First Embodiment >>
First, a first embodiment of the present invention will be described with reference to FIG. 1 and FIG.
FIG. 1 is a diagram schematically illustrating an overall configuration of an air conditioner to which a refrigerant distributor 100 according to the first embodiment is applied. FIG. 2 is a partial cross-sectional front view illustrating the outline of the configuration of the refrigerant distributor 100 according to the first embodiment.

  As shown in FIG. 1, an air conditioner to which the refrigerant distributor 100 according to the first embodiment of the present invention is applied includes a compressor 21, a four-way valve 22, an outdoor heat exchanger 23, and an outdoor heat exchanger expansion valve 24. The refrigerant distributor 100 and the indoor heat exchanger 25 are sequentially connected in an annular manner by a pipe member. That is, the refrigerant distributor 100 is used as an element device of the air conditioner.

  The compressor 21 sucks and compresses the refrigerant and discharges the compressed high-temperature gas refrigerant. The four-way valve 22 switches the refrigerant flow direction between the heating operation and the cooling operation. The outdoor heat exchanger 23 performs heat exchange between the outdoor air and the refrigerant. The outdoor heat exchanger expansion valve 24 decompresses the refrigerant during the heating operation. The refrigerant distributor 100 has a function of distributing the refrigerant that has flowed in during the cooling operation so as to have a predetermined diversion ratio and sending it to the indoor heat exchanger 25. Further, the refrigerant distributor 100 is provided with an expansion valve 5 (see FIG. 2), and the expansion valve 5 decompresses the refrigerant during the heating operation. The indoor heat exchanger 25 performs heat exchange between the indoor air and the refrigerant. The indoor heat exchanger 25 includes a plurality (here, two) of heat exchange units 25a and 25b having mutually independent passages.

Next, the flow of the refrigerant during the cooling operation will be described.
The refrigerant compressed and heated by the compressor 21 is sent to the outdoor heat exchanger 23 through a path indicated by a solid line in the four-way valve 22 of FIG. The refrigerant sent to the outdoor heat exchanger 23 passes through the outdoor heat exchanger 23 that acts as a condenser, exchanges heat with outdoor air, and is cooled and liquefied. The liquefied refrigerant that has passed through the outdoor heat exchanger 23 passes through the outdoor heat exchanger expansion valve 24 and flows into the refrigerant distributor 100. At this time, the outdoor heat exchanger expansion valve 24 is fully opened, and the refrigerant is not decompressed.

  The refrigerant sent to the refrigerant distributor 100 is depressurized to a predetermined pressure in the expansion valve 5 (see FIG. 2) attached to the refrigerant distributor 100, and then the refrigerant distributor 100 has a predetermined value as described later. It is distributed into a plurality (here, two) so as to have a flow rate ratio (diversion ratio), and flows into the respective heat exchanging portions 25a and 25b of the indoor heat exchanger 25 acting as an evaporator. The refrigerant that has flowed into the indoor heat exchanger 25 exchanges heat with the indoor air, is heated and gasified, and returns to the compressor 21. On the other hand, the indoor air is cooled in the indoor heat exchanger 25.

Next, the flow of the refrigerant during the heating operation will be described.
The refrigerant compressed and heated by the compressor 21 is sent to the indoor heat exchanger 25 through a path indicated by a broken line in the four-way valve 22 of FIG. The refrigerant sent to the indoor heat exchanger 25 passes through the indoor heat exchanger 25 acting as a condenser, exchanges heat with indoor air, is cooled and liquefied, and then flows into the refrigerant distributor 100. To do. On the other hand, indoor air is heated in the indoor heat exchanger 25. At this time, as will be described later, the regulating valves 30a and 30b (see FIG. 2) in the refrigerant distributor 100 do not act as refrigerant passage resistors.

  The refrigerant that has passed through the regulating valves 30a and 30b and the expansion valve 5 (see FIG. 2) passes through the outdoor heat exchanger expansion valve 24 and is reduced to a predetermined pressure, to the outdoor heat exchanger 23 that acts as an evaporator. Inflow. At this time, the expansion valve 5 is fully opened. The refrigerant that has flowed into the outdoor heat exchanger 23 exchanges heat with the outdoor air, is heated and gasified, and returns to the compressor 21.

  Next, the details of the refrigerant distributor 100 in the air conditioner as described above will be described with reference to FIG.

  As shown in FIG. 2, the refrigerant distributor 100 includes a main body 1 having a space inside, a pipe 2 for allowing the refrigerant to flow into the main body 1, and the refrigerant distributed in the main body 1 into a plurality of heat exchange portions 25 a. , 25b (see FIG. 1), a plurality of connection pipes 3a, 3b that respectively flow out, and a plurality of openings 31a, 31b provided in the main body 1 and communicating with the plurality of connection pipes 3a, 3b, respectively, And a plurality of regulating valves 30a and 30b for adjusting the opening degree by the bodies 12a and 12b, respectively. Here, the main body 1 is formed as a sealed container.

  An expansion valve 5 is connected to the end 43 of the pipe 2. That is, the expansion valve 5 is formed integrally with the refrigerant distributor 100. The distance L between the end 43 of the pipe 2 and the openings 31a and 31b is set to L / Di ≦ 10 when the inner diameter of the pipe 2 is Di. That is, the distance L is set to 10 times or less of the inner diameter Di of the pipe 2.

  In the main body 1, a plurality of (here, two) distribution units 11 a and 11 b for distributing the refrigerant flowing in from the pipe 2 are provided. The plurality of distribution units 11a and 11b are installed in a number corresponding to the number of heat exchange units 25a and 25b (see FIG. 1) in the indoor heat exchanger 25. The plurality of connection pipes 3a and 3b are connected to the plurality of distribution portions 11a and 11b, respectively, and the plurality of valve bodies 12a and 12b are disposed in the plurality of distribution portions 11a and 11b, respectively.

  The regulating valves 30a and 30b have valve bodies 12a and 12b and openings 31a and 31b whose opening degrees are adjusted by the valve bodies 12a and 12b. Here, the openings 31a and 31b are formed at the inlets of the distributors 11a and 11b. Therefore, the regulating valves 30a and 30b have a function of adjusting the flow rate of the refrigerant flowing into the distributors 11a and 11b.

  The valve bodies 12a and 12b are provided with tip portions 36a and 36b having conical side surfaces 35a and 35b. In addition, inclined portions 13a and 13b are provided around the openings 31a and 31b so as to face the side surfaces 35a and 35b of the tip portions 36a and 36b.

  Compression coil springs 14a and 14b are mounted between the peripheral portions 37a and 37b of the openings 31a and 31b and the flange portions 38a and 38b provided on the base end sides of the valve bodies 12a and 12b. Further, stoppers 39a and 39b for restricting the movement of the flange portions 38a and 38b against the urging force of the compression coil springs 14a and 14b are provided on the opposite side of the openings 31a and 31b of the flange portions 38a and 38b. The stoppers 39a and 39b are provided at a plurality of locations (for example, three locations) on the inner peripheral surfaces of the distribution portions 11a and 11b separately in the circumferential direction.

  In addition, the refrigerant distributor 100 is located on the side opposite to the connection pipes 3a and 3b of the heat exchange sections 25a and 25b (see FIG. 1) from the refrigerant pressure (inlet pressure) on the pipe 2 side of the openings 31a and 31b in the main body 1. Based on the pressure difference obtained by subtracting the pressure of the refrigerant at the outlet (outlet pressure), a drive device 40 is provided that reduces the opening of the adjusting valves 30a and 30b as the pressure difference increases.

  In the first embodiment, the drive device 40 includes pistons 6a and 6b connected to the valve bodies 12a and 12b via rods 41a and 41b, and cylinders 4a and 4b in which the pistons 6a and 6b are slidably disposed. ,have. The cylinders 4a and 4b are disposed adjacent to the distribution portions 11a and 11b, and the distribution portions 11a and 11b and the cylinders 4a and 4b are partitioned by partition walls 42a and 42b. The partition walls 42a and 42b are formed with through holes into which the rods 41a and 41b are inserted so as to be movable in the axial direction. A seal member (not shown) is provided between the rods 41a and 41b and the through holes. It is sealed.

  The cylinders 4a and 4b are partitioned into first pressure chambers 7a and 7b and second pressure chambers 8a and 8b by pistons 6a and 6b. Here, the first pressure chambers 7a and 7b are formed on the valve bodies 12a and 12b side of the pistons 6a and 6b in the cylinders 4a and 4b, and the second pressure chambers 8a and 8b are formed in the cylinders 4a and 4b. The pistons 6a and 6b are formed on the opposite side to the valve bodies 12a and 12b.

  The driving device 40 includes first communication passages 9a and 9b that communicate the first pressure chambers 7a and 7b with the outlets on the opposite side of the connection pipes 3a and 3b of the heat exchange portions 25a and 25b (see FIG. 1). Moreover, it has the 2nd communication path 10 which connects 2nd pressure chamber 8a, 8b and the piping 2 side of opening 31a, 31b in the main body 1 is provided. In this manner, the valve bodies 12a and 12b are configured so that the piston 6a is based on the difference between the pressures (P1a and P1b) in the first pressure chambers 7a and 7b and the pressures (P2) in the second pressure chambers 8a and 8b. 6b and rods 41a and 41b.

Next, the operation of the refrigerant distributor 100 configured as described above will be described.
During the cooling operation, the refrigerant sent to the refrigerant distributor 100 is decompressed to a predetermined pressure at the expansion valve 5 attached to the refrigerant distributor 100.

  The pistons 6a and 6b of the driving device 40 in the refrigerant distributor 100 are based on the difference between the pressures (P1a and P1b) in the first pressure chambers 7a and 7b and the pressures (P2) in the second pressure chambers 8a and 8b. Move. Since the pistons 6a and 6b are connected to the valve bodies 12a and 12b of the regulating valves 30a and 30b, the valve bodies 12a and 12b of the regulating valves 30a and 30b move according to the movement amount of the pistons 6a and 6b, and are opened. The opening degree of 31a, 31b is changed.

  Since the first pressure chambers 7a and 7b communicate with the downstream side of the heat exchange portions 25a and 25b via the first communication passages 9a and 9b, the pressures (P1a and P1b) in the first pressure chambers 7a and 7b Is detected as substantially the same pressure as the outlet pressure on the downstream side of the heat exchange sections 25a, 25b. Further, since the second pressure chambers 8a and 8b communicate with the upstream side of the distribution portions 11a and 11b via the second communication passage 10, the pressure (P2) in the second pressure chambers 8a and 8b is distributed. It is detected as substantially the same pressure as the inlet pressure on the upstream side of the portions 11a and 11b. At this time, P2> P1a and P1b are satisfied due to pressure loss.

  Therefore, the refrigerant flowing out from each of the connection pipes 3a and 3b has a pressure difference obtained by subtracting the outlet pressure on the downstream side of the heat exchanging portions 25a and 25b from the inlet pressure on the upstream side of the distributing portions 11a and 11b in the refrigerant distributor 100. Is adjusted to a flow rate ratio (diversion ratio) and flows into the heat exchange units 25a and 25b of the indoor heat exchanger 25, respectively.

  Here, the pistons 6a and 6b of the driving device 40 have a pressure difference ΔPa = P2 obtained by subtracting the pressure (P1a, P1b) in the first pressure chambers 7a, 7b from the pressure (P2) in the second pressure chambers 8a, 8b. The larger the −P1a and ΔPb = P2−P1b, the longer the moving distance. Thereby, the opening degree of the openings 31a and 31b by the valve bodies 12a and 12b moving together with the pistons 6a and 6b is adjusted so as to decrease as the pressure differences ΔPa and ΔPb increase (to the closing side), and the pressure differences ΔPa and ΔPb. Is adjusted so as to increase as it becomes smaller (toward the opening side).

  Generally, the flow rate (G) of the refrigerant flowing into the indoor heat exchanger 25 acting as an evaporator is proportional to the pressure loss (ΔP) generated from the refrigerant distributor 100 to the outlet of the indoor heat exchanger 25. (G∝ΔP). For this reason, in this embodiment, the opening degree of the openings 31a and 31b by the valve bodies 12a and 12b of the regulating valves 30a and 30b is smaller as the pressure differences ΔPa and ΔPb detected as pressure loss (ΔP) are larger. The pressure difference ΔPa, ΔPb is increased as it is smaller, that is, it is changed in the opposite direction.

  On the other hand, during heating operation, P2 <P1a and P1b are satisfied due to pressure loss. Therefore, the valve bodies 12a and 12b of the regulating valves 30a and 30b in the refrigerant distributor 100 move in the direction of increasing the opening degree of the openings 31a and 31b. That is, since the regulating valves 30a and 30b are set to the maximum opening degree (the opening degree indicated by the right regulating valve 30a in FIG. 2) at which the flange portions 38a and 38b contact the stoppers 39a and 39b, the refrigerant distributor 100 is It does not act as a refrigerant passage resistor.

  As described above, the refrigerant distributor 100 according to the present embodiment includes the main body 1, the pipe 2 that allows the refrigerant to flow into the main body 1, and the refrigerant distributed in the main body 1 into a plurality of heat exchange units 25 a and 25 b. A plurality of connection pipes 3a and 3b that respectively flow out toward each other, and a plurality of openings 31a and 31b provided in the main body 1 and communicating with the plurality of connection pipes 3a and 3b, respectively, are opened by a plurality of valve bodies 12a and 12b. The pressure of the refrigerant at the outlet on the opposite side to the connection pipes 3a, 3b of the heat exchange sections 25a, 25b from the pressure of the refrigerant on the pipe 2 side of the openings 31a, 31b in the main body 1 And a drive device 40 that reduces the opening degree of the regulating valves 30a and 30b as the pressure difference increases.

  As a result, the regulating valves 30a and 30b of the refrigerant distributor 100 change the diversion ratio when the refrigerant is distributed toward the heat exchange parts 25a and 25b of the indoor heat exchanger 25 from the refrigerant distributor 100 to the heat exchange parts. It can adjust based on the pressure loss to the exit of 25a, 25b.

  Therefore, according to the refrigerant distributor 100 according to the present embodiment, the control amount of the diversion ratio is disturbed by various disturbances such as the refrigerant flow condition, the temperature condition, the installation angle of the refrigerant distributor 100, and the manufacturing accuracy. There is no. As a result, the path balance in the plurality of heat exchanging parts 25a and 25b can be kept appropriate, and the performance of the heat exchanging parts 25a and 25b can always be kept in a good state.

  Moreover, in this embodiment, the some distribution part 11a, 11b is provided in the main body 1, and the some connecting pipe 3a, 3b is each connected to the some distribution part 11a, 11b. According to such a configuration, the openings 31a and 31b whose opening degrees are adjusted by the valve bodies 12a and 12b can be provided, for example, at the inlets of the distribution portions 11a and 11b. Thereby, the freedom degree of layout, such as adjustment valve 30a, 30b, the drive device 40, increases, and the refrigerant distributor 100 can be made compact.

  In the present embodiment, the valve bodies 12a and 12b include tip portions 36a and 36b having conical side surfaces 35a and 35b, around the openings 31a and 31b, and on the side surfaces 35a and 35b of the tip portions 36a and 36b. Opposing inclined portions 13a and 13b are provided. According to such a configuration, a smooth channel shape can be formed, and the passage resistance of the refrigerant can be reduced.

  In the present embodiment, the compression coil springs 14a and 14b are mounted between the peripheral portions 37a and 37b of the openings 31a and 31b and the flange portions 38a and 38b provided on the proximal ends of the valve bodies 12a and 12b. Stoppers 39a and 39b that restrict the movement of the flange portions 38a and 38b against the urging force of the compression coil springs 14a and 14b are provided on the opposite sides of the flange portions 38a and 38b from the openings 31a and 31b. According to such a configuration, the difference between the pressures (P1a, P1b) in the first pressure chambers 7a, 7b and the pressures (P2) in the second pressure chambers 8a, 8b is small, and the pistons 6a, 6b are compressed coils. When the force pushing toward the springs 14a, 14b is smaller than the elastic force (reaction force) of the compression coil springs 14a, 14b, the valve bodies 12a, 12b are urged by the compression coil springs 14a, 14b, and the flange portions 38a, 38b can be stopped and held at a position where it abuts against the stoppers 39a and 39b. As a result, in the case where the refrigerant flows in the direction opposite to the flow assumed by the refrigerant distributor 100 (for example, during heating operation), the regulating valves 30a and 30b operate on the opening side and have a constant opening degree. Thus, the refrigerant can be made to flow and unnecessary flow rate adjustment is not required.

  In the present embodiment, the pipe 2 has an end portion 43 on the side connected to the expansion valve 5, and the distance L between the end portion 43 of the pipe 2 and the openings 31 a and 31 b is the same as that of the pipe 2. When the inner diameter is Di, L / Di ≦ 10 is set. That is, the distance L is set to 10 times or less of the inner diameter Di as compared with the inner diameter Di of the pipe 2. Here, the state of the refrigerant phase at the outlet of the expansion valve 5 is a sprayed state in which liquid-gas components are uniformly mixed. By setting L / Di ≦ 10, the refrigerant that has flowed out of the expansion valve 5 can be caused to flow into the main body 1 of the refrigerant distributor 100 while maintaining a sprayed state in which the gas and liquid are in a homogeneous state. . Therefore, the problem that the liquid refrigerant is biased to a part of the distribution sections (for example, 11a) hardly occurs, and the sprayed refrigerant can be distributed. Therefore, the refrigerant diversion ratio is controlled without depending on the phase state. Can do.

<< Second Embodiment >>
Next, a second embodiment of the present invention will be described with reference to FIGS.
FIG. 3 is a diagram illustrating an outline of an overall configuration of an air conditioner to which the refrigerant distributor 101 according to the second embodiment is applied. FIG. 4 is a cross-sectional front view showing an outline of the configuration of the refrigerant distributor 101 according to the second embodiment.

  The second embodiment is different from the first embodiment in that an electric drive device 50 is provided instead of the mechanical drive device 40 according to the first embodiment. Hereinafter, the second embodiment will be described with a focus on differences from the first embodiment, and description of common points will be omitted.

  In the second embodiment, the driving device 50 includes first pressure detection units S1a and S1b that detect refrigerant pressure at the outlets of the heat exchange units 25a and 25b opposite to the connection pipes 3a and 3b, and openings in the main body 1. A second pressure detection unit S2 for detecting the pressure of the refrigerant on the pipe 2 side of 31a, 31b; drive units 51a, 51b for moving the valve bodies 12a, 12b closer to or away from the openings 31a, 31b; And a control unit 56 that controls the drive units 51a and 51b based on the difference between the detection values of the detection units S1a and S1b and the detection value of the second pressure detection unit S2.

  The drive parts 51a, 51b are rods 52a, 52b connected to the base end sides of the valve bodies 12a, 12b, and female screw parts screwed into male screw parts formed on the outer peripheral surfaces of the base end sides of the rods 52a, 52b. Nut members 53a, 53b formed on the inner surface, drive gears 54a, 54b meshing with teeth formed on the outer peripheral surfaces of the nut members 53a, 53b, and an electric motor 55a, which rotates the drive gears 54a, 54b. 55b. The nut members 53a and 53b are configured such that axial movement is restricted by a restriction member (not shown). Further, the rods 52a and 52b are configured such that rotation around the axis is restricted by a restriction member (not shown).

  Here, when the nut members 53a and 53b are rotated by the operation of the electric motors 55a and 55b, the rods 52a and 52b are moved in the axial direction by the screw feeding action. As a result, the valve bodies 12a and 12b can be moved closer to or away from the openings 31a and 31b. The power transmission mechanism for converting the rotational driving force of the electric motors 55a and 55b into the linear motion force in the axial direction of the valve bodies 12a and 12b is not limited to the above-described structure, and is arbitrary, for example, a ball A screw mechanism may be used.

  In such 2nd Embodiment, the control part 56 of the drive device 50 is the opposite side to the connection pipes 3a and 3b of the heat exchange parts 25a and 25b from the pressure of the refrigerant | coolant by the side of the piping 2 of the opening 31a and 31b in the main body 1. FIG. Based on the pressure difference obtained by subtracting the pressure of the refrigerant at the outlet, the drive units 51a and 51b are controlled so that the opening degree of the adjusting valves 30a and 30b decreases as the pressure difference increases.

  Therefore, according to the second embodiment, the same effects as those of the first embodiment can be obtained. Moreover, according to 2nd Embodiment, the freedom degree of opening degree control of the regulating valves 30a and 30b increases, and the performance of the heat exchange parts 25a and 25b can be kept more favorable.

  As mentioned above, although this invention was demonstrated based on embodiment, this invention is not limited to above-described embodiment, Various modifications are included. For example, the above-described embodiment has been described in detail for easy understanding of the present invention, and is not necessarily limited to one having all the configurations described. Also, a part of the configuration of one embodiment can be replaced with the configuration of the other embodiment, and the configuration of the other embodiment can be added to the configuration of the one embodiment. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

  For example, in the above-described embodiment, the refrigerant sent to the refrigerant distributors 100 and 101 is configured to be divided into two, but the present invention is not limited to this, and for example, four, etc. It may be configured to be distributed to any plurality of the above.

  Moreover, in the said embodiment, the some distribution part 11a, 11b is provided in the main body 1, and the some connecting pipe 3a, 3b is each connected to the some distribution part 11a, 11b, but this invention is this. It is not limited. For example, a plurality of connecting pipes 3 a and 3 b may be connected to the outer wall of the main body 1 without providing the plurality of distribution portions 11 a and 11 b in the main body 1. In this case, the openings 31a and 31b whose opening degree is adjusted by the valve bodies 12a and 12b can be provided at the end portions on the main body side of the plurality of connecting pipes 3a and 3b.

DESCRIPTION OF SYMBOLS 1 Main body 2 Piping 3a, 3b Connection pipe 4a, 4b Cylinder 5 Expansion valve 6a, 6b Piston 7a, 7b 1st pressure chamber 8a, 8b 2nd pressure chamber 9a, 9b 1st communicating path 10 2nd communicating path 11a, 11b Distribution Part 12a, 12b Valve body 13a, 13b Inclined part 25 Indoor heat exchanger 25a, 25b Heat exchange part 30a, 30b Regulating valve 31a, 31b Opening 35a, 35b Side face 36a, 36b Tip part 37a, 37b Peripheral part 38a, 38b Flange part 39a, 39b Stopper 40 Drive unit 43 End 50 Drive unit 51a, 51b Drive unit 56 Control unit 100, 101 Refrigerant distributor Di Inner diameter L Distance S1a, S1b First pressure detection unit S2 Second pressure detection unit ΔPa, ΔPb Pressure difference

Claims (10)

A body having a space inside;
Piping for flowing refrigerant into the body;
A plurality of connecting pipes for allowing the refrigerant distributed in the main body to flow out toward the plurality of heat exchange sections,
A plurality of adjusting valves provided in the main body, each of which adjusts the opening degree of the plurality of openings respectively communicating with the plurality of connecting pipes by a plurality of valve bodies;
Based on the pressure difference obtained by subtracting the pressure of the refrigerant at the outlet on the opposite side of the connection pipe of the heat exchange section from the pressure of the refrigerant on the piping side of the opening in the main body, the adjustment valve increases as the pressure difference increases. A drive device for reducing the opening of
A refrigerant distributor comprising: The driving device includes:
A piston connected to the valve body;
A cylinder in which the piston is slidably disposed;
A first communication passage that communicates a first pressure chamber formed on the valve body side of the piston in the cylinder and an outlet on the opposite side of the connection pipe of the heat exchange section;
A second pressure chamber formed on the opposite side of the piston to the valve body in the cylinder and a second communication path communicating with the pipe side of the opening in the main body;
2. The refrigerant distributor according to claim 1, wherein the valve body is moved via the piston based on a difference between a pressure in the first pressure chamber and a pressure in the second pressure chamber.   The plurality of distribution units for distributing the refrigerant flowing in from the pipe are provided in the main body, and the plurality of connection pipes are connected to the plurality of distribution units, respectively. The refrigerant distributor according to 1.   The refrigerant according to claim 2, wherein the valve body includes a tip portion having a conical side surface, and an inclined portion is provided around the opening so as to face the side surface of the tip portion. Distributor.   A compression coil spring is mounted between a peripheral portion of the opening and a flange portion provided on the proximal end side of the valve body, and resists the biasing force of the compression coil spring on the opposite side of the opening of the flange portion. The refrigerant distributor according to claim 2, further comprising a stopper for restricting movement of the flange portion.   The pipe has an end connected to an expansion valve, and the distance L between the end of the pipe and the opening satisfies L / Di ≦ 10, where Di is the inner diameter of the pipe. The refrigerant distributor according to any one of claims 2 to 5, wherein the refrigerant distributor is set. The driving device includes:
A first pressure detection unit that detects a pressure of the refrigerant at an outlet of the heat exchange unit opposite to the connection pipe;
A second pressure detector for detecting the pressure of the refrigerant on the pipe side of the opening in the body;
A drive unit for moving the valve body toward or away from the opening;
A control unit that controls the drive unit based on a difference between a detection value by the first pressure detection unit and a detection value by the second pressure detection unit;
2. The refrigerant distributor according to claim 1, comprising:   In the main body, a plurality of distribution portions for distributing the refrigerant flowing in from the pipe are provided, the plurality of connection pipes are connected to the plurality of distribution portions, respectively, and the plurality of valve bodies are the plurality of the plurality of valve bodies. The refrigerant distributor according to claim 7, wherein the refrigerant distributor is disposed in each distribution section.   The refrigerant according to claim 7, wherein the valve body includes a tip portion having a conical side surface, and an inclined portion is provided around the opening so as to face the side surface of the tip portion. Distributor.   The pipe has an end connected to an expansion valve, and the distance L between the end of the pipe and the opening satisfies L / Di ≦ 10, where Di is the inner diameter of the pipe. The refrigerant distributor according to any one of claims 7 to 9, wherein the refrigerant distributor is set.

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