JP2012042121A - Refrigerant distributor, and refrigerating cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a distributor that does not result in large pressure loss and automatically returns distribution to be uniform, even if a refrigerant flow rate in each passage is non-uniform when a refrigerant passage is diverged into a plurality of passages.SOLUTION: In the refrigerant distributor, an inflow-side refrigerant passage 1 is connected on the upstream side of a passage branch part 9, and a plurality of outflow-side refrigerant passages 2 are connected on the downstream side of the passage branch part 9, and then a refrigerant flow which has flowed from the inflow-side refrigerant passage 1 is distributed to the plurality of outflow-side refrigerant passages 2. The distributor includes: a nozzle portion 7 having a passage-cross-section minimum part 6 on the downstream side of the inflow-side refrigerant passage 1 and on the upstream side of the passage branch part 9; and additionally a feedback passage 10 connecting with peripheries of the respective outflow-side refrigerant passages 2 and the downstream side of the passage-cross-section minimum part 6.

Description

  The present invention relates to a refrigerant distributor.

  Heat exchangers installed in indoor units and outdoor units in heat pump water heaters or air conditioners have multiple flow path configurations, and a refrigerant distributor is placed at the heat exchanger inlet to distribute refrigerant to each path. It is supposed to be.

  As a conventional technique related to this main refrigerant distributor, for example, Japanese Patent Laid-Open No. 2000-111205 discloses a refrigerant distribution.

JP 2000-111205 A

  Although the above-mentioned Patent Document 1 can uniformly distribute the refrigerant, since a pressure loss is generated by providing a plurality of channels having a small channel cross-sectional area, energy loss cannot be avoided.

  An object of the present invention is to provide a refrigerant distributor capable of suppressing the pressure loss and distributing the refrigerant uniformly to the heat exchanger while having a simple structure.

  In the present invention, an inflow side refrigerant flow path is connected to the upstream side of the flow path branching section, and a plurality of outflow side refrigerant flow paths are connected to the downstream side of the flow path branching section. In the refrigerant distributor that distributes the refrigerant flow to the plurality of outflow side refrigerant channels, a nozzle having a minimum channel cross-sectional area on the downstream side of the inflow side refrigerant channel and on the upstream side of the channel branching portion And a return flow path that connects a peripheral portion of each outflow side refrigerant flow path and a downstream side of the flow path cross-sectional area minimum portion.

  Moreover, in the above, the structure provided with the inlet part of the said return flow path connected to the circumference | surroundings of the inlet part of the said outflow side refrigerant flow path in both the outer side and the inner side of the inlet part of the said outflow side refrigerant flow path is preferable. .

  Moreover, in the above, the structure provided with the exit part of the said return flow path connected to the downstream of the said flow path cross-sectional area minimum part more than the number of the said outflow side refrigerant flow paths is preferable.

  In the above, it is preferable that the outlet portion of the return channel and the inlet portion of the return channel are provided in the same direction with respect to the central axis of the nozzle portion.

  Moreover, in the above, the structure provided with the exit part of the said return flow path and the inlet part of the said outflow side refrigerant | coolant flow path in a different direction with respect to the said nozzle part central axis is preferable.

  According to the present invention, it is possible to provide a refrigerant distributor and a refrigeration cycle apparatus that can suppress pressure loss and can evenly distribute refrigerant to heat exchangers with a simple structure.

It is a perspective view of a refrigerant distributor provided with one embodiment. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. It is CC sectional drawing of FIG. It is sectional drawing showing the behavior of the refrigerant | coolant in this embodiment. It is a perspective view showing the main body member of the refrigerant distributor provided with this embodiment. It is a perspective view showing the upper cover member of a refrigerant distributor provided with this embodiment. It is a perspective view showing the outer side member of the refrigerant distributor provided with this embodiment. It is a perspective view showing the assembly state of the refrigerant distributor provided with this embodiment. It is sectional drawing of the inlet_port | entrance part of the return flow path provided with other embodiment. It is sectional drawing of the exit part of the return flow path provided with other embodiment. It is the schematic showing a general refrigerating cycle. It is a block diagram of a general distributor.

  In recent years, an evaporator mounted on a refrigeration cycle apparatus such as a heat pump water heater or an air conditioner has been made up of a plurality of pipes because the pipes are reduced in diameter in order to increase thermal efficiency. For this reason, the distributor is split in order to flow through the plurality of pipes by a distributor attached immediately before the refrigerant flows into the evaporator.

  However, there is a problem that the current distributor structure cannot perform uniform distribution.

  If the distribution of refrigerant in the current distributor becomes non-uniform, the drying phenomenon in the pipe where the flow rate is reduced is accelerated, resulting in a loss of energy and a corresponding decrease in cooling performance. Therefore, uniform refrigerant distribution is essential.

  Now, a general refrigeration cycle described in Patent Document 1 will be described with reference to FIG. 12, and a general distributor will be described with reference to FIG.

  FIG. 12 is a schematic diagram showing a general refrigeration cycle.

  FIG. 13 is a configuration diagram of a general distributor.

  In FIG. 12, in the case of heating operation, as indicated by an arrow, the high-temperature and high-pressure refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 103 via the four-way valve 102, condenses, and indoor air and heat. Replace and heat the room. The refrigerant that has become liquid in the indoor heat exchanger 103 flows into the distributor 107 from the expansion valve 104 through the inflow pipe 106 of the refrigerant circuit 105. The distributor 107 distributes the refrigerant through the plurality of outflow pipes 108 and then supplies the refrigerant to the plurality of outdoor heat exchangers 109. The refrigerant evaporated in the plurality of outdoor heat exchangers 109 returns to the compressor 101 via the four-way valve 102.

  On the other hand, in the case of cooling operation, the refrigerant flows backward by switching the four-way valve 102 as indicated by the dotted arrow, so that the indoor heat exchanger 103 serves as an evaporator, so that the room can be cooled.

  In FIG. 13, the refrigerant that has flowed into the inflow pipe 106 enters the pressure chamber 107a as shown by an arrow, and flows into the refrigerant flow path 107b branched into a plurality of branches from the pressure chamber 107a. The refrigerant merge branch 107c that has flowed in once joins (in FIG. 13, two refrigerant merge branches 107c are provided). The refrigerant that has exited the refrigerant junction branch 107 c joins at the outlet junction 107 d and flows to the outdoor heat exchanger 109 through the outflow pipe 108.

  Although such a distributor 107 can uniformly distribute the refrigerant, since a plurality of channels having a small channel cross-sectional area are provided, the pressure loss is large and energy loss occurs. In addition, the structure becomes complicated, leading to an increase in production costs.

  Accordingly, the inventors of the present invention applied fluidics (fluid elements) and studied various distributors with a simple structure and low energy loss. As a result, the following embodiments were obtained.

  An embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a perspective view of a refrigerant distributor including an embodiment.

  2 is a cross-sectional view taken along the line AA in FIG.

  3 is a cross-sectional view taken along the line BB of FIG.

  4 is a cross-sectional view taken along the line CC of FIG.

  FIG. 5 is a cross-sectional view showing the behavior of the refrigerant in the present embodiment.

  FIG. 6 is a perspective view showing a main body member of the refrigerant distributor provided with this embodiment.

  FIG. 7 is a perspective view showing the upper cover member of the refrigerant distributor provided with this embodiment.

  FIG. 8 is a perspective view showing an outer member of the refrigerant distributor provided with this embodiment.

  FIG. 9 is a perspective view showing an assembled state of the refrigerant distributor including the present embodiment.

  In FIG. 1, one inflow side refrigerant flow path 1 and a plurality of outflow side refrigerant flow paths 2 are connected to a refrigerant distributor body 3. In the present embodiment, the case where there are three outflow side refrigerant flow paths 2 is shown.

  In FIG. 2, a nozzle portion 7 is disposed downstream of the inflow side refrigerant flow path 1. The nozzle portion 7 includes a contracted flow portion 4 where the flow path cross-sectional area gradually decreases, a flow path cross-sectional area minimum portion 6, and a flow path expanding portion 5 where the flow path cross-sectional area rapidly increases. A flow path branching section 9 having a protrusion 8 is connected to the downstream side of the flow path expanding section 5, and three outflow side refrigerant flow paths 2 are connected to the downstream side (see FIG. 2 is a cross-sectional view of FIG. 1 taken along line AA, so that only two outflow-side refrigerant channels are visible). Reference numeral 11 denotes an outer entrance portion, 12 denotes an inner entrance portion, 10 denotes a return flow path, and 13 denotes an exit portion, the details of which will be described later.

  FIG. 3 is a cross-sectional view of the inlet surface of the outflow side refrigerant flow channel 2 to which the inlet portion of the return flow channel 10 is connected. FIG. 4 is a channel cross-sectional view on the downstream side of the channel cross-sectional area minimum portion 6 to which the outlet portion 13 of the return channel 10 is connected.

  In FIG. 3, the center points of the three outflow-side refrigerant channels 2 are arranged every 120 degrees on one circle centering on the channel branching portion 9. Three outflow-side refrigerant flow paths 2 are attached around the protrusion 8 of the flow path branching section 9 shown in FIG. The outer inlet portion 11 and the inner inlet portion 12 of the return flow path 10 are located on the outer side and the inner side of the circle connecting the center points of the outflow side refrigerant flow paths 2, respectively.

  The outer inlet portion 11 and the inner inlet portion 12 of the return channel 10 are installed on the same plane as the inlet portion of the outflow side refrigerant channel 2. The return flow path 10 passes through the outside of the main refrigerant flow path and is connected to the outlet portion 13 of the return flow path 10 installed on the downstream side of the flow path cross-sectional area minimum portion 6 shown in FIG.

  In FIG. 4, the outer inlet portion 11, the inner inlet portion 12, and the outlet portion 13 of the return flow path 10 constituting one return flow path 10 are in the same direction with respect to the central axis of the nozzle section 7. In this example, since the number of the return flow paths 10 is 6, the return flow paths every 60 degrees centering on the center point of the main refrigerant flow path in FIG. 4 and the center point of the flow path branching portion 9 in FIG. Ten outlet portions 13, an outer inlet portion 11, and an inner inlet portion 12 are arranged.

  The behavior of the refrigerant flow in the main refrigerant flow path will be described with reference to FIG.

  In FIG. 5, the downstream side of the inflow-side refrigerant flow path 1 is a contraction portion 4, and the flow path cross-sectional area gradually decreases. Due to the relationship expressed by the continuous equation, the flow velocity increases as the flow path cross-sectional area decreases, so that the static pressure of the refrigerant flow that flows in from the inflow side refrigerant flow path 1 decreases simultaneously with the increase in dynamic pressure. The static pressure eventually becomes minimum at the flow path cross-sectional area minimum portion 6, and at the same time, the momentum of the refrigerant flow becomes maximum. As the momentum increases, the inertial force increases, so that the flow does not expand along the wall surface in the flow path expanding section 5 on the downstream side of the flow path cross-sectional area minimum section 6, thus causing separation.

  As a result, the refrigerant flow is in a turbulent state where only the central portion of the flow path expanding portion 5 has a high flow velocity. The refrigerant flow 14A that has passed through the flow path expanding section 5 reaches the flow path branching section 9 (shown in FIG. 2) on the downstream side, and the refrigerant flow 14A collides with the protrusion 8 so that the refrigerant flow is 3 Branches to the outflow side refrigerant flow path 3 of the book.

  The behavior of the refrigerant flow in the return flow path 10 will be described.

  Since the flow path cross-sectional area of the flow path branching portion 9 is larger than the flow path cross-sectional area minimum portion 6, the static pressure is high. Since the downstream side of the minimum flow path cross-sectional area 6 and the flow path branching section 9 are connected by the return flow path 10, the static pressure at the outer inlet section 11 and the inner inlet section 12 of the return flow path 10 is the flow path cross-sectional area. It becomes close to the static pressure of the minimum part 6.

  As a result, a part of the refrigerant flow 14A branched at the flow path branching section 9 does not flow to the outflow side refrigerant flow path 2, but to the outer inlet section 11 and the inner inlet section 12 of the return flow path 10 having a low static pressure. And then flows out from the outlet portion 13 of the return flow path 10 connected to the downstream side of the flow path cross-sectional area minimum portion 6.

The operation when the refrigerant distribution is non-uniform and the refrigerant flow 14A flowing out from the nozzle portion 7 is deflected toward the outflow-side refrigerant flow path 2A will be described with reference to FIG.
When the refrigerant flow path 14A is deflected toward the outflow side refrigerant flow path 2A, the refrigerant flow rate in the outflow side refrigerant flow path 2A increases, and the refrigerant flow rates in the three outflow side refrigerant flow paths 2 become uneven. When nonuniformity occurs in the refrigerant flow rate, the ratio of the refrigerant flow rate flowing into the six return flow paths 10 changes. The refrigerant flow that has flowed into the return flow path 10 eventually flows out from the outlet section 13 of the return flow path 10 provided on the downstream side of the flow path cross-sectional area minimum portion 6. At this time, since the flow rate ratios of the outlet portions 13 of the six return flow paths 10 are different, the refrigerant flow from the outlet section 13 of the return flow path 10 having a high flow rate has a large momentum and a low flow rate. The refrigerant flow from the 10 outlet portions 13 has a small momentum.

  As a result, the refrigerant flow 14B that has flowed out of the flow path cross-sectional area minimum portion 6 receives a fluid force corresponding to the momentum ratio of the refrigerant flow that flows out of the outlet portions 13 of the six return flow paths 10. Here, since the outflow direction of the refrigerant flow flowing out from the outlet portion 13 of the return flow path 10 having a large flow rate faces the deflection direction of the refrigerant flow 14B, the deflected refrigerant flow 14B is on the central axis of the nozzle portion 7. It will receive a correction force that will be returned to. By this series of operations, the direction of the refrigerant flow 14A is adjusted so that the refrigerant is evenly distributed to the three outflow-side refrigerant channels 2 at all times.

  The inner inlet 12 of the return channel 10 will be described.

  When only the outer inlet portion 11 of the return flow path 10 is provided, a sufficient flow rate difference in the return flow path 10 for correcting the direction of the refrigerant flow 14B cannot be obtained unless the refrigerant flow 14B is largely deflected. . As a result, the refrigerant flow 14B vibrates greatly, and the response time until the distribution returns to uniform is delayed.

  On the other hand, since the inner inlet portion 12 is provided in addition to the outer inlet portion 11 of the return flow path 10, the flow rate difference of the return flow path 10 can be increased even if the refrigerant flow 14A is slightly deflected. It becomes possible. Thereby, the uniform distribution of the refrigerant is realized more quickly than when only the outer inlet 11 of the return flow path 10 is installed.

  The number of return flow paths 10 will be described.

  Generally, an apparatus that controls refrigerant flow using the return flow path 10 has a two-dimensional flow path, and in many cases, there are two outflow side refrigerant paths and the outflow side refrigerant. The number of flow paths is the same as the number of return flow paths. However, in this example, six return flow paths 10 that are equal to or more than the number of outflow-side refrigerant flow paths 2 are provided, and no matter which part of the inner wall surface of the flow path expanding portion 5 is bent, The corrective power is obtained.

  The configuration of the refrigerant distributor body 3 will be described with reference to FIGS.

  The refrigerant distributor main body 3 shown in this example is composed of three members: a main body member 15, an upper lid member 16, and an outer member 17. As shown in FIG. 2, the main body member 15 has a nozzle portion 7 composed of a contracted portion 4, a channel cross-sectional area minimum portion 6, and a channel expanding portion 5, and the downstream end of the channel expanding portion 5 is opened. It has a different shape. Six holes constituting the return channel 10 pass through the inner wall surface on the downstream side of the channel cross-sectional area minimum portion 6 and the outer wall surface of the main body member 15. The upper lid member 16 has a configuration in which a protrusion 8 serving as a flow path branching portion 9 is added to a disk, and three holes serving as inlet portions of the outflow side refrigerant flow path 2 are formed on the surface, and the return flow path 10 is provided. There are twelve holes for the outer inlet 11 and the inner inlet 12.

  The outer member 17 has a configuration in which the inner side of the cylinder is hollowed out, and six grooves constituting the return flow path 10 and three holes for connecting the outflow side refrigerant flow path 2 are added.

  As shown in FIG. 9, it is possible to obtain a complex-shaped refrigerant distributor with an extremely simple structure by simply covering the main body member 15 with the upper cover member 16 and then covering the main body member 15 with the outer member 17 from the outside.

  A second embodiment of the present invention will be described with reference to FIGS.

  The second embodiment differs from the first embodiment in the positions of the inlet portions 11 and 12 and the outlet portion 13 of the return flow path 10.

  FIG. 10 is a channel cross-sectional view of the inlet portion of the outflow side refrigerant channel 2.

  The outer inlet portion 11 and the inner inlet portion 12 of the outflow side refrigerant flow path 2 are installed on the outer side and the inner side of the three outflow side refrigerant flow paths 2.

  FIG. 11 is a channel cross-sectional view on the downstream side of the channel cross-sectional area minimum portion 6 to which the outlet portion 13 of the return channel 10 is connected.

  10 and 11, the outlet portion 13 of the return flow path 10 is installed in a direction different from the inlet portions 11 and 12 of the return flow path 10 with respect to the nozzle central axis. Comparing FIG. 10 and FIG. 11, the return flow path 10 is located on the inner side of the outer inlet portion 11D and the inner side of the pair of return flow paths 10 closest to another outflow side refrigerant flow path 2C adjacent to the outflow side refrigerant flow path 2A. The inlet 12E is connected to the outlet 13B. In this example, since the number of outflow-side refrigerant channels is three, the number of return channels is also three. Further, the outlet portion 13 of the return flow path 10 is disposed at a position obtained by rotating the positions of the inlet portions 11 and 12 of the return flow path 10 by 60 degrees counterclockwise with respect to the center of the main refrigerant flow path.

  The operation when nonuniformity occurs in the refrigerant distribution will be described with reference to FIGS.

  When the refrigerant jet is deflected toward the outflow side flow path 2C and nonuniformity occurs in the refrigerant distribution, the flow rate of the refrigerant flow flowing in from the inlet portions 11D and 12E of the return flow path 10 increases. Thereby, the refrigerant | coolant flow volume which flows out out of the exit part 13B connected with inlet part 11D, 12E of the return flow path 10 increases. The refrigerant flow that flows out from the outlet portion 13B of the return flow path 10 pushes the refrigerant jet, and the refrigerant jet receives a force that bends toward the outflow side refrigerant flow path 2A. With the above mechanism, the refrigerant jet is deflected so as to rotate the three outflow side refrigerant passages, so that the time average flow rates of the three outflow side refrigerant passages become equal, and as a result, equal distribution is achieved.

  As described above, according to the present embodiment, the refrigerant flow flowing out from the nozzle portion is unintentionally deflected toward the inner wall surface on the downstream side of the nozzle portion. As a result, when non-uniformity occurs in the flow rate of the refrigerant flowing out from the plurality of outflow side refrigerant channels, the flow rate ratio of the return channel changes corresponding to the flow rate ratio of each outflow side refrigerant channel. When the flow rate ratio of each return flow path changes, the refrigerant flow from the exit of the return flow path with a large refrigerant flow pushes the refrigerant flow at the outlet of the nozzle, so the direction of the refrigerant flow flowing out from the nozzle is corrected. The By this operation, the refrigerant flow flowing out from the nozzle is always evenly distributed to each outflow side refrigerant flow path. In addition, since the portion where the cross-sectional area of the flow path becomes smaller than the conventional one is short, the pressure loss can be minimized and the energy loss can be reduced.

  As described above, according to the present embodiment, it is possible to provide a refrigerant distributor that maximizes the effects of fluidics (fluid elements).

  DESCRIPTION OF SYMBOLS 1 ... Inflow side refrigerant | coolant flow path, 2 ... Outflow side refrigerant | coolant flow path, 3 ... Refrigerant distributor main body, 4 ... Condensation part, 5 ... Channel expansion part, 6 ... Channel cross-sectional area minimum part, 7 ... Nozzle part, DESCRIPTION OF SYMBOLS 8 ... Projection part, 9 ... Flow path branching part, 10 ... Return flow path, 11 ... Outer entrance part of return flow path, 12 ... Inner entrance part of return flow path, 13 ... Outlet part of return flow path, 14 ... Refrigerant Soryu, 15 ... main body member, 16 ... upper lid member, 17 ... outer member.

Claims (6)

An inflow side refrigerant flow path is connected to the upstream side of the flow path branching section, a plurality of outflow side refrigerant flow paths are connected to the downstream side of the flow path branching section, and the refrigerant flow flowing in from the inflow side refrigerant flow path is In the refrigerant distributor for distributing to the plurality of outflow side refrigerant flow paths,
A nozzle portion having a flow path cross-sectional area minimum portion on the downstream side of the inflow side refrigerant flow path and on the upstream side of the flow path branching section; in addition, a peripheral portion of each outflow side refrigerant flow path and the flow path cross-sectional area A refrigerant distributor comprising a return flow path connecting the downstream side of the minimum part. The refrigerant distributor according to claim 1, wherein
A refrigerant distributor comprising an inlet portion of the return flow passage connected to a periphery of an inlet portion of the outflow side refrigerant passage on both an outer side and an inner side of the inlet portion of the outflow side refrigerant passage. . The refrigerant distributor according to claim 1, wherein
A refrigerant distributor comprising an outlet portion of the return flow path connected to a downstream side of the flow path cross-sectional area minimum portion, which is equal to or more than the number of the outflow side refrigerant flow paths. The refrigerant distributor according to claim 1, wherein
A refrigerant distributor comprising an outlet part of the return flow path and an inlet part of the return flow path in the same direction with respect to the central axis of the nozzle part. The refrigerant distributor according to claim 1, wherein
A refrigerant distributor comprising an outlet part of the return flow path and an inlet part of the outflow side refrigerant flow path in different directions with respect to the central axis of the nozzle part.   A refrigeration cycle apparatus comprising the refrigerant distributor according to any one of claims 1 to 5.

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