CN212778058U - Gas-liquid two-phase refrigerant distributor and heat pump system - Google Patents
Gas-liquid two-phase refrigerant distributor and heat pump system Download PDFInfo
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- CN212778058U CN212778058U CN202020634412.1U CN202020634412U CN212778058U CN 212778058 U CN212778058 U CN 212778058U CN 202020634412 U CN202020634412 U CN 202020634412U CN 212778058 U CN212778058 U CN 212778058U
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 183
- 239000007788 liquid Substances 0.000 title claims abstract description 60
- 239000012530 fluid Substances 0.000 claims abstract description 42
- 238000001816 cooling Methods 0.000 claims description 36
- 239000012071 phase Substances 0.000 description 39
- 230000002349 favourable effect Effects 0.000 description 17
- 230000009286 beneficial effect Effects 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000002826 coolant Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Abstract
The utility model discloses a double-phase refrigerant distributor of gas-liquid and heat pump system, include: a spiral pipe group having a plurality of spiral pipes arranged in a circumferential direction for accelerating a refrigerant; the mixing cavity is used for mixing the refrigerants flowing through the spiral pipe group, and the inlet end of the mixing cavity is communicated with the spiral pipe group; the distribution cavity is communicated with the mixing cavity and is used for distributing the refrigerant; and the plurality of flow path connecting pipes are uniformly distributed at the outlet end of the distribution cavity in the circumferential direction and are used for connecting the distribution cavity with each flow path in the evaporator. Spiral refrigerant fluid flowing out of the spiral pipes is rotationally mixed in the mixing cavity and flows forwards; and then, refrigerant fluid enters the distribution cavity and is uniformly distributed to the flow path connecting pipes, so that the flow and the state of the refrigerant entering each flow path in the evaporator are the same, uniform heat exchange of each flow path is facilitated, the heat exchange efficiency of the evaporator is improved, and a higher energy efficiency ratio is obtained.
Description
Technical Field
The utility model belongs to the technical field of the heat pump, concretely relates to double-phase refrigerant distributor of gas-liquid and have the heat pump system of this double-phase refrigerant distributor of gas-liquid.
Background
The centrifugal water chilling unit of air-cooled heat pump absorbs heat in the environment through the external evaporator in the heating state, and the process is carried out through the evaporation of the liquid refrigerant in the evaporator. In this process, it is desirable that all the refrigerant in the evaporator be liquid and become gas by evaporation and heat absorption, but in the actual operation process, the inside of the evaporator is in a gas-liquid two-phase state.
In order to reduce the evaporation pressure loss of the refrigerant in the evaporator, a multi-flow path design is generally adopted, so that the refrigerant flow in each flow path is different; in order to solve the problem of uneven distribution of the flow of the refrigerant, a distributor is arranged in a pipeline; however, in the distributor, due to uneven mixing of gas phase and liquid phase of the refrigerant, that is, the gaseous and liquid refrigerants are not sufficiently mixed, the change of the two phases often generates bias flow, which causes the distributor to distribute unevenly when equally dividing, causes the refrigerant flow of each branch of the evaporator to be more or less, causes uneven heat exchange of each flow path of the evaporator, causes low utilization rate of the evaporator and insufficient heat exchange, thereby affecting the heat exchange efficiency of the evaporator and causing the energy efficiency ratio of the air conditioning system to be low.
The above information disclosed in this background section is only for enhancement of understanding of the background of the application and therefore it may comprise prior art that does not constitute known to a person of ordinary skill in the art.
Disclosure of Invention
The utility model discloses to foretell problem among the prior art, provide a double-phase refrigerant distributor of gas-liquid for the double-phase refrigerant homogeneous mixing of gas-liquid, and each flow path of evenly distributed evaporimeter improves the heat exchange efficiency of evaporimeter.
In order to realize the purpose of the utility model, the utility model adopts the following technical scheme to realize:
a gas-liquid two-phase refrigerant distributor, comprising:
a spiral pipe group having a plurality of spiral pipes arranged in a circumferential direction for accelerating a refrigerant;
the mixing cavity is used for mixing the refrigerants flowing through the spiral pipe group, and the inlet end of the mixing cavity is communicated with the spiral pipe group;
the distribution cavity is communicated with the mixing cavity and is used for distributing the refrigerant;
and the plurality of flow path connecting pipes are uniformly distributed at the outlet end of the distribution cavity in the circumferential direction and are used for connecting the distribution cavity with each flow path in the evaporator.
Furthermore, the spiral pipes are cylindrical spiral lines, and the spiral pipes are identical in structure and are arranged in a circumferential array.
Furthermore, a limiting block is arranged in the distribution cavity, an annular flow channel is defined between the limiting block and the cavity wall of the distribution cavity, and the flow channel connecting pipe is communicated with the flow channel.
Further, the cavity wall of the distribution cavity is far away from the axis of the distribution cavity in the direction far away from the mixing cavity, the limiting block is provided with a conical outer side face matched with the cavity wall of the distribution cavity, and the flow channel is limited between the cavity wall of the distribution cavity and the conical outer side face.
Furthermore, the limiting block is provided with a first conical outer side surface and a second conical outer side surface which have the same taper with the cavity wall of the distribution cavity, a first flow channel is defined between the first conical outer side surface and the cavity wall of the distribution cavity, a second flow channel is defined between the second conical outer side surface and the cavity wall of the distribution cavity, the width of the first flow channel is larger than that of the second flow channel, and the second flow channel is located at one end far away from the mixing cavity.
Furthermore, a plurality of liquid inlets connected with the spiral pipe are arranged on the front end surface of the mixing cavity.
Furthermore, an impeller which can rotate under the pushing of the refrigerant fluid flowing out of the spiral pipe is arranged in the mixing cavity.
Furthermore, the cooling device also comprises a cooling cavity for cooling the refrigerant, and the cooling cavity is sleeved outside the mixing cavity and/or the shunting cavity.
Based on foretell two-phase refrigerant distributor of gas-liquid, the utility model discloses still provide a heat pump system, be equipped with the two-phase refrigerant distributor of foretell gas-liquid for the two-phase refrigerant homogeneous mixing of gas-liquid, and each flow path to the evaporimeter is evenly distributed, improves the heat exchange efficiency of evaporimeter.
A heat pump system is provided with the gas-liquid two-phase refrigerant distributor.
The heat pump system further comprises a connecting pipeline, the gas-liquid two-phase refrigerant distributor comprises a cooling cavity for cooling the refrigerant, and the heat pump system further comprises a liquid supply pipe for providing the refrigerant for the cooling cavity and a return pipe for returning the refrigerant in the cooling cavity to the connecting pipeline.
Further, the connecting pipeline is provided with a first connecting pipe connected with the spiral pipe group, one end of the liquid supply pipe is communicated with the first connecting pipe, and the other end of the liquid supply pipe is communicated with the cooling cavity.
Furthermore, a capillary tube for cooling the refrigerant is arranged on the liquid supply tube.
Compared with the prior art, the utility model discloses an advantage is with positive effect: the refrigerant enters the plurality of spiral pipes to rotate and accelerate, and the refrigerant fluid has forward moment and rotational torque when entering the mixing cavity, so that the spiral refrigerant fluid flowing out of the plurality of spiral pipes is rotated and mixed in the mixing cavity and flows forward; then the refrigerant fluid enters the distribution cavity and is uniformly distributed to the plurality of flow path connecting pipes, so that the flow and the state of the refrigerant entering each flow path in the evaporator are the same, and the uniform heat exchange of each flow path is facilitated; through setting up spiral tube group and hybrid chamber, be favorable to accelerating and the spiral rotation of refrigerant for the refrigerant can be at the hybrid chamber homogeneous mixing, is favorable to distributing the even stable distribution refrigerant in chamber, is favorable to improving the heat exchange efficiency of evaporimeter, in order to obtain higher energy efficiency ratio.
Other features and advantages of the present invention will become more apparent from the following detailed description of the invention when read in conjunction with the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
Fig. 1 is a schematic structural diagram of an embodiment of a gas-liquid two-phase refrigerant distributor according to the present invention;
FIG. 2 is a schematic top view of the structure of FIG. 1;
FIG. 3 is a schematic axial cross-sectional view of the mixing and distribution chambers of FIG. 1;
FIG. 4 is a heat pump system having the gas-liquid two-phase refrigerant distributor of FIG. 1;
fig. 5 is a schematic structural view of a second embodiment of the gas-liquid two-phase refrigerant distributor according to the present invention;
fig. 6 is a schematic structural view of a third embodiment of the gas-liquid two-phase refrigerant distributor according to the present invention;
fig. 7 is a schematic structural view of a fourth embodiment of the gas-liquid two-phase refrigerant distributor according to the present invention;
FIG. 8 is a heat pump system with the gas-liquid two-phase refrigerant distributor of FIG. 7;
fig. 9 is an enlarged schematic structural view of a part of the structure in fig. 8.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the drawings in the embodiments of the present invention are combined below to clearly and completely describe the technical solutions in the embodiments of the present invention.
In the description of the present invention, it should be noted that the terms "upper", "lower", "left", "right", and the like indicate directions or positional relationships based on the positional relationships shown in the drawings, and the direction close to the axis of the inner tube is "inner", whereas "outer" is used. The terminology is for the purpose of describing the invention only and is not intended to be limiting of the invention since it is not intended to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation. Moreover, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "a plurality" means two or more unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.
Example one
Referring to fig. 1-4, an embodiment of the gas-liquid two-phase refrigerant distributor provided in the present invention is a gas-liquid two-phase refrigerant distributor 100, which includes: the spiral pipe group 10 is provided with a plurality of spiral pipes 11 which are circumferentially arranged and used for accelerating a refrigerant, the refrigerant forms a fluid which spirally moves after passing through the spiral pipes 11, and a plurality of fluids which spirally move are formed by arranging the plurality of spiral pipes 11, so that the uniformity of mixing is facilitated; the mixing cavity 20 is used for mixing the refrigerant flowing through the spiral tube group 10, and the inlet end of the mixing cavity 20 is communicated with the spiral tube group 10; the distribution cavity 30 is communicated with the mixing cavity 20 and is used for distributing the refrigerant; the plurality of flow path connection pipes 41 are circumferentially and uniformly distributed at the outlet end of the distribution chamber, which is advantageous for uniformly distributing the refrigerant fluid reaching the distribution chamber 30 to the flow path connection pipes 41, and the flow path connection pipes 41 are used for connecting the distribution chamber 30 and the flow paths in the evaporator 200.
The refrigerant enters the plurality of spiral pipes 11 to rotate and accelerate, and when the refrigerant enters the mixing cavity 20, the refrigerant has forward moment and rotational torque, so that spiral refrigerant fluid flowing out of the plurality of spiral pipes 11 rotates and mixes in the mixing cavity 20 and flows forwards; then, the refrigerant fluid enters the distribution cavity 30 and is uniformly distributed to the flow path connecting pipes 41, so that the flow rate and the state of the refrigerant entering each flow path in the evaporator 200 are the same, and uniform heat exchange of each flow path is facilitated; through setting up spiral tube group and hybrid chamber, be favorable to accelerating and the spiral rotation of refrigerant for the refrigerant can be in hybrid chamber 20 homogeneous mixing, is favorable to distributing the even stable distribution refrigerant in chamber 30, is favorable to improving evaporator 200's heat exchange efficiency, in order to obtain higher energy efficiency ratio.
In this embodiment, the spiral tubes 11 are cylindrical spiral lines, three spiral tubes 11 are uniformly arranged in the circumferential direction, that is, arranged in a circumferential array of 120 degrees, and the three spiral tubes 11 have the same structure; the refrigerant is ensured to uniformly enter the three spiral pipes 11 and is subjected to the same rotation acceleration in the three spiral pipes 11, so that the refrigerant fluid flowing through the three spiral pipes 11 has the same flow rate and speed after entering the mixing cavity 20, and is spirally sprayed out in three directions at an angle of 120 degrees to enter the mixing cavity 20 to be collided and uniformly mixed with each other. The sum of the flow rates of the three spiral pipes 11 is the same as the flow rate of the inlet end of the mixing cavity 20, or the sum of the sectional areas of the three spiral pipes 11 is the same as the sectional area of the inlet end of the mixing cavity 20, so that the refrigerant is prevented from entering the mixing cavity 20 to generate phase change, the spiral rotation of the refrigerant fluid is ensured, and the uniform mixing is facilitated.
A limiting block 32 is arranged in the distribution cavity 30, an annular flow channel 33 is defined between the limiting block 32 and the cavity wall 31 of the distribution cavity 30, the flow channel connecting pipe 41 is communicated with the flow channel 33, and the flow channel 33 and the distribution cavity 30 are coaxially arranged; the refrigerant fluid in the distribution cavity 30 is beneficial to be divided in the circumferential direction by defining the annular flow passage 33, and flows into a plurality of flow passage connecting pipes 41 which are uniformly distributed in the circumferential direction at the outlet end of the distribution cavity 30; the flow channel 33 is arranged in the distribution cavity 30, so that the refrigerant fluid is primarily distributed in the distribution cavity 30, the refrigerant is guaranteed to be distributed to the same circumferential direction with the plurality of flow path connecting pipes 41, and the refrigerant is uniformly distributed to the plurality of flow path connecting pipes 41.
The cavity wall 31 of the distribution cavity 30 is tapered, that is, the cavity wall 31 is far away from the axis of the distribution cavity 30 in the direction far away from the mixing cavity 20, the limiting block 32 has a tapered outer side surface matched with the cavity wall of the distribution cavity 31, and a flow passage 33 is defined between the cavity wall 31 and the tapered outer side surface. Preferably, the delimiting block 32 has a first tapered outer side 321 and a second tapered outer side 322 having the same taper as the chamber wall 31 of the dispensing chamber, the taper being the ratio of the diameter of the bottom face of the taper to the height of the taper; the first conical outer side 321 and the second conical outer side 322 are connected by a radial surface 323 along the radial direction; a first flow passage 331 is defined between the first tapered outer side surface 321 and the cavity wall 31 of the distribution cavity 30, a second flow passage 332 is defined between the second tapered outer side surface 322 and the cavity wall 31 of the distribution cavity 30, the width of the first flow passage 331 is greater than that of the second flow passage 332, the width of the first flow passage 331 is the distance between the first tapered outer side surface 311 and the cavity wall 31, the second flow passage 332 is located at one end far away from the mixing cavity 20, that is, the refrigerant firstly flows through the first flow passage 331 and enters the second flow passage 332, and the second flow passage 332 is connected with the plurality of flow passage connecting pipes 41. The flow passage 33 includes a first flow passage 331 and a second flow passage 332 provided in the refrigerant flow direction.
The cavity wall 31 is a cone extending radially outward in the refrigerant flowing direction, that is, the outer side of the flow channel 30 extends radially in the refrigerant flowing direction; the first flow channel 331 is a conical ring structure extending outward in the radial direction in the refrigerant flowing direction, the second flow channel 332 is a conical ring structure extending outward in the radial direction in the refrigerant flowing direction, the width of the first flow channel 331 is set to be larger than that of the second flow channel 332, which is beneficial to realizing the fluid supply to the second flow channel 332, and the radial surface 313 is set to be beneficial to forming the turbulent flow of the fluid, so that the fluid is remixed, and the uniformity of the refrigerant fluid mixing is increased.
The gas-liquid two-phase refrigerant distributor in this embodiment may be used in all apparatuses that employ a heat pump, and fig. 4 illustrates a heat pump system that employs the gas-liquid two-phase refrigerant distributor. A heat pump system comprising: the air conditioner comprises a compressor 300, an evaporator 200, a condenser 400, a four-way valve 500, an expansion valve 700, a connecting pipeline 600 for connecting all the parts, and a gas-liquid two-phase refrigerant distributor 100 for distributing refrigerants for all the flow paths of the evaporator 200; the gas-liquid two-phase refrigerant distributor is arranged, so that gas-liquid two-phase refrigerants are uniformly mixed and uniformly distributed to each flow path of the evaporator, and the heat exchange efficiency of the evaporator is improved.
Example two
Referring to fig. 1 and 5, a second embodiment of the gas-liquid two-phase refrigerant distributor according to the present invention is provided, and the main difference between the present embodiment and the first embodiment is: the same structure as that of the first embodiment may be adopted for the difference in the block structure, that is, the difference in the flow path structure.
A gas-liquid two-phase refrigerant distributor 100, comprising: the spiral pipe group 10 is provided with a plurality of spiral pipes 11 which are circumferentially arranged and used for accelerating a refrigerant, the refrigerant forms a fluid which spirally moves after passing through the spiral pipes 11, and a plurality of fluids which spirally move are formed by arranging the plurality of spiral pipes 11, so that the uniformity of mixing is facilitated; the mixing cavity 20 is used for mixing the refrigerant flowing through the spiral tube group 10, and the inlet end of the mixing cavity 20 is communicated with the spiral tube group 10; the distribution cavity 30 is communicated with the mixing cavity 20 and is used for distributing the refrigerant; the plurality of flow path connecting pipes 41 are circumferentially and uniformly distributed at the outlet end of the distribution chamber, which is beneficial to uniformly distributing the refrigerant fluid reaching the distribution chamber 30 to each flow path connecting pipe 41, and the flow path connecting pipes 41 are used for connecting each flow path in the distribution chamber 30 and the evaporator.
The refrigerant enters the plurality of spiral pipes 11 to rotate and accelerate, and when the refrigerant enters the mixing cavity 20, the refrigerant has forward moment and rotational torque, so that spiral refrigerant fluid flowing out of the plurality of spiral pipes 11 rotates and mixes in the mixing cavity 20 and flows forwards; then, the refrigerant fluid enters the distribution cavity 30 and is uniformly distributed to the flow path connecting pipes 41, so that the flow rate and the state of the refrigerant entering each flow path in the evaporator 200 are the same, and uniform heat exchange of each flow path is facilitated; through setting up spiral tube group and hybrid chamber, be favorable to accelerating and the spiral rotation of refrigerant for the refrigerant can be in hybrid chamber 20 homogeneous mixing, is favorable to distributing the even stable distribution refrigerant in chamber 30, is favorable to improving the heat exchange efficiency of evaporimeter, in order to obtain higher energy efficiency ratio.
A limiting block 34 is arranged in the distribution cavity 30, an annular flow passage 35 is defined between the limiting block 34 and the cavity wall 31 of the distribution cavity 30, a flow passage connecting pipe 41 is communicated with the flow passage 35, and the flow passage 35 and the distribution cavity 30 are coaxially arranged; by defining the annular flow passage 35, the refrigerant fluid in the distribution chamber 30 is favorably divided in the circumferential direction and flows into a plurality of flow path connecting pipes 41 which are uniformly distributed in the circumferential direction at the outlet end of the distribution chamber 30; the flow channel 35 is arranged in the distribution cavity 30, so that the refrigerant fluid is primarily distributed in the distribution cavity 30, the refrigerant is guaranteed to be distributed to the same circumferential direction with the plurality of flow path connecting pipes 41, and the refrigerant is uniformly distributed to the plurality of flow path connecting pipes 41.
The cavity wall 31 is a cone extending outward in the radial direction in the refrigerant flowing direction, the limiting block 34 is a cone extending outward in the radial direction in the refrigerant flowing direction, the taper of the limiting block 34 is greater than that of the cavity wall 31, that is, the distance between the outer side surface of the limiting block 34 and the cavity wall 31 is gradually reduced in the refrigerant flowing direction, that is, the flow channel 35 extends outward in the radial direction in the refrigerant flowing direction and has a reduced width, and the flow channel 35 extends outward in the radial direction in the refrigerant flowing direction, so that the section radius of the flow channel 35 is increased, and the section area of the flow channel 35 is increased; by reducing the width, the cross-sectional area of the flow passage 35 is reduced, so that the change of the cross-sectional area of the flow passage 35 in the refrigerant flowing direction is reduced, and the refrigerant fluid is uniformly distributed to the flow passage connecting pipes 41.
EXAMPLE III
Referring to fig. 1 and fig. 6, a third embodiment of the gas-liquid two-phase refrigerant distributor according to the present invention is provided, and the main difference between the present embodiment and the first embodiment is: an impeller is provided in the mixing chamber, and the structure may be the same as that of the first embodiment.
A gas-liquid two-phase refrigerant distributor 100, comprising: the spiral pipe group 10 is provided with a plurality of spiral pipes 11 which are circumferentially arranged and used for accelerating a refrigerant, the refrigerant forms a fluid which spirally moves after passing through the spiral pipes 11, and a plurality of fluids which spirally move are formed by arranging the plurality of spiral pipes 11, so that the uniformity of mixing is facilitated; the mixing cavity 20 is used for mixing the refrigerant flowing through the spiral tube group 10, and the inlet end of the mixing cavity 20 is communicated with the spiral tube group 10; the distribution cavity 30 is communicated with the mixing cavity 20 and is used for distributing the refrigerant; the plurality of flow path connecting pipes 41 are circumferentially and uniformly distributed at the outlet end of the distribution chamber, which is beneficial to uniformly distributing the refrigerant fluid reaching the distribution chamber 30 to each flow path connecting pipe 41, and the flow path connecting pipes 41 are used for connecting each flow path in the distribution chamber 30 and the evaporator.
The refrigerant enters the plurality of spiral pipes 11 to rotate and accelerate, and when the refrigerant enters the mixing cavity 20, the refrigerant has forward moment and rotational torque, so that spiral refrigerant fluid flowing out of the plurality of spiral pipes 11 rotates and mixes in the mixing cavity 20 and flows forwards; then, the refrigerant fluid enters the distribution cavity 30 and is uniformly distributed to the flow path connecting pipes 41, so that the flow rate and the state of the refrigerant entering each flow path in the evaporator 200 are the same, and uniform heat exchange of each flow path is facilitated; through setting up spiral tube group and hybrid chamber, be favorable to accelerating and the spiral rotation of refrigerant for the refrigerant can be in hybrid chamber 20 homogeneous mixing, is favorable to distributing the even stable distribution refrigerant in chamber 30, is favorable to improving the heat exchange efficiency of evaporimeter, in order to obtain higher energy efficiency ratio.
An impeller 50 which can rotate under the pushing of the refrigerant fluid flowing out of the spiral pipe 11 is arranged in the mixing cavity 20, and the impeller 50 rotates under the pushing of the spiral refrigerant fluid to further stir the fluid and increase the uniformity of the fluid mixing.
Example four
Referring to fig. 1, 7-9, a fourth embodiment of the gas-liquid two-phase refrigerant distributor according to the present invention is provided, and the main difference between the present embodiment and the first embodiment is: a cooling chamber is provided, and the same structure as that of the first embodiment may be adopted.
A gas-liquid two-phase refrigerant distributor 100, comprising: the spiral pipe group 10 is provided with a plurality of spiral pipes 11 which are circumferentially arranged and used for accelerating a refrigerant, the refrigerant forms a fluid which spirally moves after passing through the spiral pipes 11, and a plurality of fluids which spirally move are formed by arranging the plurality of spiral pipes 11, so that the uniformity of mixing is facilitated; the mixing cavity 20 is used for mixing the refrigerant flowing through the spiral tube group 10, and the inlet end of the mixing cavity 20 is communicated with the spiral tube group 10; the distribution cavity 30 is communicated with the mixing cavity 20 and is used for distributing the refrigerant; the plurality of flow path connection pipes 41 are circumferentially and uniformly distributed at the outlet end of the distribution chamber, which is advantageous for uniformly distributing the refrigerant fluid reaching the distribution chamber 30 to the flow path connection pipes 41, and the flow path connection pipes 41 are used for connecting the distribution chamber 30 and the flow paths in the evaporator 200.
The refrigerant enters the plurality of spiral pipes 11 to rotate and accelerate, and when the refrigerant enters the mixing cavity 20, the refrigerant has forward moment and rotational torque, so that spiral refrigerant fluid flowing out of the plurality of spiral pipes 11 rotates and mixes in the mixing cavity 20 and flows forwards; then, the refrigerant fluid enters the distribution cavity 30 and is uniformly distributed to the flow path connecting pipes 41, so that the flow rate and the state of the refrigerant entering each flow path in the evaporator 200 are the same, and uniform heat exchange of each flow path is facilitated; through setting up spiral tube group and hybrid chamber, be favorable to accelerating and the spiral rotation of refrigerant for the refrigerant can be in hybrid chamber 20 homogeneous mixing, is favorable to distributing the even stable distribution refrigerant in chamber 30, is favorable to improving evaporator 200's heat exchange efficiency, in order to obtain higher energy efficiency ratio.
The gas-liquid two-phase refrigerant distributor 100 further comprises a cooling cavity 60 for cooling the refrigerant, and the cooling cavity 60 is sleeved on the outer sides of the mixing cavity 20 and the flow dividing cavity 30, and the cooling cavity 60 is sleeved on the outer sides of the mixing cavity 60 and the flow dividing cavity 30; through setting up cooling chamber 60 for the further cooling of cooling medium in mixing chamber 20 and the reposition of redundant personnel chamber 30, reduce the temperature of cooling medium, be favorable to providing more heat transfer energy in evaporimeter 200, be favorable to improving the heat exchange efficiency of evaporimeter 200, improve the heating performance.
In other embodiments, cooling chambers may be provided only outside the mixing chamber 20, or only outside the flow splitting chamber 30.
Referring to fig. 8 and 9, a heat pump system using the gas-liquid two-phase refrigerant distributor is shown. A heat pump system comprising: the air conditioner comprises a compressor 300, an evaporator 200, a condenser 400, a four-way valve 500, connecting pipelines for connecting all parts, and a gas-liquid two-phase refrigerant distributor 100 for distributing refrigerants for all flow paths of the evaporator 200; the gas-liquid two-phase refrigerant distributor is arranged, so that gas-liquid two-phase refrigerants are uniformly mixed and uniformly distributed to each flow path of the evaporator, and the heat exchange efficiency of the evaporator is improved.
The heat pump system further includes a liquid supply pipe 71 for supplying the cooling chamber 60 with a refrigerant, and a return pipe 72 for returning the refrigerant in the cooling chamber 60 to the connection pipe 600. Specifically, the connection pipe 600 has a first connection pipe 601 connected to the coil group 10, the other end of the first connection pipe 601 is connected to the expansion valve 700, one end of the liquid supply pipe 71 is communicated with the first connection pipe 601, the other end is communicated with the cooling chamber 60, and the first connection pipe 601; the refrigerant cooling device is used for cooling the refrigerant in the mixing cavity 20 and the flow dividing cavity 30 by allowing the low-temperature and low-pressure refrigerant passing through the expansion valve 700 to flow into the cooling cavity 60 in the heat pump system.
In order to further reduce the temperature of the refrigerant flowing into the cooling chamber 60, the capillary tube 73 for cooling the refrigerant is disposed on the liquid supply tube 71, the refrigerant is cooled again through the capillary tube 73, and the temperature of the refrigerant entering the cooling chamber 60 is lower than that of the refrigerant in the first connection tube 601, which is beneficial to improving the cooling effect on the refrigerant in the mixing chamber 20 and the branch chamber 30, and further improving the heat exchange efficiency of the evaporator. A check valve 74 is also provided on the supply pipe 71.
The above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described in the foregoing embodiments, or that equivalents may be substituted for elements thereof; such modifications and substitutions do not depart from the spirit and scope of the present invention, which is claimed.
Claims (10)
1. A gas-liquid two-phase refrigerant distributor, comprising:
a spiral pipe group having a plurality of spiral pipes arranged in a circumferential direction for accelerating a refrigerant;
the mixing cavity is used for mixing the refrigerants flowing through the spiral pipe group, and the inlet end of the mixing cavity is communicated with the spiral pipe group;
the distribution cavity is communicated with the mixing cavity and is used for distributing the refrigerant;
and the plurality of flow path connecting pipes are uniformly distributed at the outlet end of the distribution cavity in the circumferential direction and are used for connecting the distribution cavity with each flow path in the evaporator.
2. The gas-liquid two-phase refrigerant distributor according to claim 1, wherein the spiral tubes are cylindrical spiral lines, and a plurality of the spiral tubes have the same structure and are arranged in a circumferential array.
3. The gas-liquid two-phase refrigerant distributor according to claim 2, wherein a limiting block is disposed in the distribution chamber, an annular flow passage is defined between the limiting block and a wall of the distribution chamber, and the flow passage connecting pipe is communicated with the flow passage.
4. The gas-liquid two-phase refrigerant distributor according to claim 3, wherein the wall of the distribution chamber is away from the axis of the distribution chamber in the direction away from the mixing chamber, the limiting block has a tapered outer side surface matched with the wall of the distribution chamber, and the flow passage is defined between the wall of the distribution chamber and the tapered outer side surface.
5. The gas-liquid two-phase refrigerant distributor according to claim 4, wherein the limiting block has a first tapered outer side surface and a second tapered outer side surface having the same taper as the cavity wall of the distribution cavity, a first flow channel is defined between the first tapered outer side surface and the cavity wall of the distribution cavity, a second flow channel is defined between the second tapered outer side surface and the cavity wall of the distribution cavity, the width of the first flow channel is greater than that of the second flow channel, and the second flow channel is located at one end far away from the mixing cavity.
6. The gas-liquid two-phase refrigerant distributor according to any one of claims 1 to 5, wherein an impeller rotatable by the refrigerant fluid flowing out of the spiral pipe is provided in the mixing chamber.
7. The gas-liquid two-phase refrigerant distributor according to any one of claims 1 to 5, further comprising a cooling chamber for cooling the refrigerant, the cooling chamber being provided outside the mixing chamber and/or outside the flow dividing chamber.
8. A heat pump system characterized by having the gas-liquid two-phase refrigerant distributor according to any one of claims 1 to 7.
9. The heat pump system according to claim 8, further comprising a connection line, wherein the gas-liquid two-phase refrigerant distributor comprises a cooling chamber for cooling a refrigerant, and the heat pump system further comprises a liquid supply pipe for supplying the refrigerant to the cooling chamber, and a return pipe for returning the refrigerant in the cooling chamber to the connection line.
10. The heat pump system according to claim 9, wherein said connection pipe has a first connection pipe connected to said coil group, and said liquid supply pipe has one end communicating with said first connection pipe and the other end communicating with said cooling chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202020634412.1U CN212778058U (en) | 2020-04-23 | 2020-04-23 | Gas-liquid two-phase refrigerant distributor and heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202020634412.1U CN212778058U (en) | 2020-04-23 | 2020-04-23 | Gas-liquid two-phase refrigerant distributor and heat pump system |
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| CN212778058U true CN212778058U (en) | 2021-03-23 |
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| CN202020634412.1U Active CN212778058U (en) | 2020-04-23 | 2020-04-23 | Gas-liquid two-phase refrigerant distributor and heat pump system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111503947A (en) * | 2020-04-23 | 2020-08-07 | 青岛海尔空调电子有限公司 | Gas-liquid two-phase refrigerant distributor and heat pump system |
| CN113465237A (en) * | 2021-05-26 | 2021-10-01 | 珠海格力电器股份有限公司 | Shunt, heat exchange device and air conditioner |
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2020
- 2020-04-23 CN CN202020634412.1U patent/CN212778058U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111503947A (en) * | 2020-04-23 | 2020-08-07 | 青岛海尔空调电子有限公司 | Gas-liquid two-phase refrigerant distributor and heat pump system |
| CN111503947B (en) * | 2020-04-23 | 2024-09-13 | 青岛海尔空调电子有限公司 | Gas-liquid two-phase refrigerant distributor and heat pump system |
| CN113465237A (en) * | 2021-05-26 | 2021-10-01 | 珠海格力电器股份有限公司 | Shunt, heat exchange device and air conditioner |
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