CN108626118B - Compressor and heat exchange system with same - Google Patents
Compressor and heat exchange system with same Download PDFInfo
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- CN108626118B CN108626118B CN201810517124.5A CN201810517124A CN108626118B CN 108626118 B CN108626118 B CN 108626118B CN 201810517124 A CN201810517124 A CN 201810517124A CN 108626118 B CN108626118 B CN 108626118B
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- compressor
- heat exchange
- exchange system
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- 239000003507 refrigerant Substances 0.000 claims abstract description 156
- 230000006835 compression Effects 0.000 claims abstract description 85
- 238000007906 compression Methods 0.000 claims abstract description 85
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 37
- 238000005192 partition Methods 0.000 claims description 36
- 238000004891 communication Methods 0.000 claims description 28
- 239000007788 liquid Substances 0.000 claims description 28
- 230000005540 biological transmission Effects 0.000 claims description 18
- 230000001502 supplementing effect Effects 0.000 claims description 14
- 238000005057 refrigeration Methods 0.000 claims 1
- 238000012546 transfer Methods 0.000 description 10
- 238000001704 evaporation Methods 0.000 description 9
- 230000008020 evaporation Effects 0.000 description 9
- 238000000034 method Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000012545 processing Methods 0.000 description 5
- 238000009434 installation Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 239000011555 saturated liquid Substances 0.000 description 2
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000008595 infiltration Effects 0.000 description 1
- 238000001764 infiltration Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a compressor and a heat exchange system with the same. Wherein, the compressor includes: the plurality of cylinders form at least two mutually independent refrigerant compression channels; multiple refrigerants flow through different refrigerant compression channels. The invention effectively solves the problems of poor reliability and lower energy efficiency of the compressor in the low-temperature working condition in the prior art.
Description
Technical Field
The invention relates to the technical field of heat exchange, in particular to a compressor and a heat exchange system with the same.
Background
Currently, only one refrigerant can be used for heat exchange in a compressor on the market. If only R134a refrigerant is adopted for heat exchange, the heat exchange system can prepare hot water with higher temperature (more than 75 ℃), however, the evaporation pressure of the heat exchange system is extremely low under the low-temperature working condition, the possibility of air infiltration into the system is increased, and the normal operation of the heat exchange system is affected; if only the R410A refrigerant or the R32 refrigerant is adopted for heat exchange, the outlet water temperature of the heat exchange system is lower (generally lower than 65 ℃), and the use requirements of partial users cannot be met.
In order to solve the above problems, in the prior art, at least two compressors are used in a heat exchange system to exchange heat, and different refrigerants are used in the two compressors to exchange heat respectively. However, the above arrangement not only results in a larger occupied space of the heat exchange system, but also increases the manufacturing cost of the heat exchange system.
Disclosure of Invention
The invention mainly aims to provide a compressor and a heat exchange system with the same, so as to solve the problems of poor reliability and low energy efficiency of the compressor under a low-temperature working condition in the prior art.
In order to achieve the above object, according to one aspect of the present invention, there is provided a compressor comprising: the plurality of cylinders form at least two mutually independent refrigerant compression channels; multiple refrigerants flow through different refrigerant compression channels.
Further, the at least two refrigerant compression passages include a first compression passage and a second compression passage, the compressor includes at least three cylinders, at least one cylinder forming the first compression passage, and at least two cylinders forming the second compression passage.
Further, the plurality of refrigerants includes a first refrigerant flowing through the first compression passage and a second refrigerant flowing through the second compression passage, and the critical temperature of the first refrigerant is less than the critical temperature of the second refrigerant.
Further, the refrigerating capacity per unit volume of the first refrigerant is greater than a preset value.
Further, the critical temperature of the second refrigerant is greater than the preset temperature.
Further, the compressor comprises three cylinders, namely a first cylinder, a second cylinder and a third cylinder, wherein the first cylinder, the second cylinder and the third cylinder are sequentially arranged along the axial direction of a crankshaft of the compressor, the first cylinder is positioned above the second cylinder and the third cylinder, the first cylinder forms a first compression channel, and the second cylinder and the third cylinder form a second compression channel.
Further, a first partition plate is arranged between the second cylinder and the third cylinder, the first partition plate is provided with an intermediate channel, and gas in the third cylinder can enter the second cylinder through the intermediate channel.
Further, a second partition plate is arranged between the first cylinder and the second cylinder, an exhaust groove communicated with an exhaust port of the second cylinder is formed in the second partition plate, and the second partition plate is provided with a first exhaust channel communicated with the exhaust groove.
Further, a third partition plate is arranged between the first cylinder and the second partition plate, the notch of the exhaust groove faces the third partition plate, the third partition plate is covered on the exhaust groove, and the bottom of the exhaust groove is communicated with the exhaust port of the second cylinder through the first communication hole.
Further, the compressor further comprises a first flange and a cover plate which are sleeved on the crankshaft, a transmission groove is formed in one side, facing the cover plate, of the first flange, the cover plate is located below the first flange and covers the transmission groove, the exhaust hole of the third cylinder is communicated with the transmission groove through a second communication hole in the bottom of the transmission groove, the third cylinder is provided with a communication channel, the communication channel is communicated with the transmission groove through a third communication hole in the bottom of the transmission groove, and the communication channel is communicated with the middle channel.
Further, the compressor further comprises a first liquid dispenser and an air supplementing enthalpy increasing pipeline, wherein the first liquid dispenser is communicated with the air suction port of the third cylinder, and the air supplementing enthalpy increasing pipeline is communicated with the transmission groove.
Further, the compressor further comprises a second flange positioned above the first cylinder, and a second exhaust passage communicated with the exhaust port of the first cylinder is arranged on the second flange.
Further, the compressor further comprises a second liquid separator, and the second liquid separator is communicated with the air suction port of the first cylinder.
According to another aspect of the present invention, there is provided a heat exchange system comprising a compressor, the compressor being the compressor described above.
Further, the heat exchange system also comprises an outdoor heat exchanger, a first throttling element and an intermediate heat exchanger, wherein the outdoor heat exchanger, the first throttling element and the intermediate heat exchanger are connected with a first compression channel of the compressor through pipelines to form a first refrigerant circulation loop; the heat exchange system further comprises an indoor heat exchanger and a second throttling piece, and the indoor heat exchanger, the second throttling piece, the intermediate heat exchanger and a second compression channel of the compressor are connected through pipelines to form a second refrigerant circulation loop.
Further, the intermediate heat exchanger comprises a first pipeline and a second pipeline which are mutually independent, the first pipeline is communicated with the first compression channel, the second pipeline is communicated with the second compression channel, and the flow directions of refrigerants in the first pipeline and the second pipeline are opposite.
Further, the heat exchange system further includes: the third throttling element is arranged between the flash evaporator and the intermediate heat exchanger, and one port of the flash evaporator is connected with the air supplementing enthalpy increasing pipeline of the compressor.
Further, the heat exchange system further includes: and the control valve is arranged on the air supplementing and enthalpy increasing pipeline and used for controlling the on-off of the air supplementing and enthalpy increasing pipeline of the compressor and the flash evaporator.
Further, the heat exchange system further includes: one end of the drainage main pipe is communicated with the water outlet of the middle heat exchanger, and the other end of the drainage main pipe is communicated with the water inlet of the indoor heat exchanger; at least one drainage branch pipe is connected with the drainage main pipe and is arranged at an included angle with the drainage main pipe.
By applying the technical scheme of the invention, the compressor comprises a plurality of cylinders and a plurality of refrigerants. Wherein, a plurality of cylinders form two at least mutually independent refrigerant compression passageway. Multiple refrigerants flow through different refrigerant compression channels. Therefore, in order to meet different use demands of users, different refrigerant compression channels can be adopted for heat exchange, and the refrigerant flows through the same compressor. Specifically, one type of refrigerant is used in one refrigerant compression channel, another refrigerant of a different type from the refrigerant is used in the other refrigerant compression channel, and different refrigerant compression channels are adopted according to different use requirements (such as different temperatures) so as to solve the problems of poor reliability and low energy efficiency of the compressor under the low-temperature working condition. Meanwhile, the arrangement can reduce the occupied space of the heat exchange system and reduce the processing cost of the heat exchange system.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
fig. 1 shows a cross-sectional view of an embodiment one of a compressor according to the present invention;
FIG. 2 shows a cross-sectional view of the pump body of the compressor of FIG. 1;
FIG. 3 is a schematic diagram showing the connection relationship and the refrigerant flow direction of the first embodiment of the heat exchange system according to the present invention;
fig. 4 is a schematic diagram showing a connection relationship and a refrigerant flow direction of a second embodiment of the heat exchange system according to the present invention; and
fig. 5 shows a pressure enthalpy diagram of the compressor of the invention.
Wherein the above figures include the following reference numerals:
10. a crankshaft; 21. a first cylinder; 22. a second cylinder; 23. a third cylinder; 31. a first separator; 32. a second separator; 321. an exhaust groove; 33. a third separator; 41. a first flange; 411. a transmission groove; 42. a second flange; 50. a cover plate; 61. a first knockout; 62. a second knockout; 70. air supplementing and enthalpy increasing pipeline; 80. an outdoor heat exchanger; 90. a first throttle member; 100. an intermediate heat exchanger; 101. a first pipeline; 102. a second pipeline; 110. a compressor; 120. an indoor heat exchanger; 130. a second throttle member; 140. a third throttling element; 150. a flash evaporator; 160. a control valve; 171. a water drain header; 172. a water discharge branch pipe; 180. a housing; 181. a first exhaust pipe; 182. a second exhaust pipe; 190. and a motor.
Detailed Description
It should be noted that, in the case of no conflict, the embodiments and features in the embodiments may be combined with each other. The invention will be described in detail below with reference to the drawings in connection with embodiments.
It is noted that all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs unless otherwise indicated.
In the present invention, unless otherwise indicated, terms of orientation such as "upper" and "lower" are used generally with respect to the orientation shown in the drawings or to the vertical, vertical or gravitational orientation; also, for ease of understanding and description, "left, right" is generally directed to the left, right as shown in the drawings; "inner and outer" refer to inner and outer relative to the outline of the components themselves, but the above-described orientation terms are not intended to limit the present invention.
In order to solve the problems of poor reliability and low energy efficiency of a compressor in the prior art under a low-temperature working condition, the application provides a compressor and a heat exchange system with the compressor.
Example 1
As shown in fig. 1 and 2, the compressor includes three cylinders forming two mutually independent refrigerant compression passages. Two refrigerants flow through the two refrigerant compression passages, respectively.
By applying the technical scheme of the embodiment, different refrigerant compression channels can be adopted for heat exchange in order to meet different use demands of users, and the refrigerant flows through the same compressor. Specifically, one type of refrigerant is used in one refrigerant compression channel, another refrigerant of a different type from the refrigerant is used in the other refrigerant compression channel, and different refrigerant compression channels are adopted according to different use requirements (such as different temperatures) so as to solve the problems of poor reliability and low energy efficiency of the compressor under the low-temperature working condition. Meanwhile, the arrangement can reduce the occupied space of the heat exchange system and reduce the processing cost of the heat exchange system.
In this embodiment, the two refrigerant compression channels are a first compression channel and a second compression channel, respectively. Wherein one cylinder forms a first compression channel and two cylinders form a second compression channel. The structure is simple and easy to realize.
The number of cylinders is not limited to this. Optionally, the compressor comprises four, five or more cylinders.
In other embodiments not shown in the drawings, the compressor includes four cylinders, two of which form a first compression passage and the other two of which form a second compression passage. The structure is simple and easy to process and realize.
In this embodiment, the plurality of refrigerants includes a first refrigerant flowing through the first compression passage and a second refrigerant flowing through the second compression passage, and the critical temperature of the first refrigerant is less than the critical temperature of the second refrigerant. Specifically, the first compression channel can compress the first refrigerant into a refrigerant with relatively low temperature, the second compression channel can compress the second refrigerant into a refrigerant with relatively high temperature, and the refrigerant exchanges heat with air or liquid to enable the air or liquid to have a certain temperature so as to meet different use requirements of users. Such as in summer, the user needs air or liquid (water) at a lower temperature; in winter, the user needs air or liquid (water) with a relatively high temperature. Like this, above-mentioned setting can satisfy user's different user demands to promote user's use experience.
Alternatively, the refrigerating capacity per unit volume of the first refrigerant is greater than a preset value. Wherein the preset value is equal to 3500KJ/m 3 。
In the present embodiment, the first refrigerant is an R32 refrigerant. The R32 refrigerant is environment-friendly, and is converted into gas with lower temperature (lower than 65 ℃) after being compressed by the compressor, so as to meet the use requirements of users at medium and low temperatures.
The type of the first refrigerant is not limited to this. Alternatively, the first refrigerant is an R410A refrigerant or other high unit volume refrigerant environment friendly refrigerant.
Optionally, the critical temperature of the second refrigerant is greater than the preset temperature. Wherein the preset temperature is equal to 75 ℃.
In the present embodiment, the second refrigerant is R134a refrigerant. Wherein, R134a refrigerant can be compressed into higher temperature gas by the compressor to satisfy user's high temperature operation requirement.
The type of the second refrigerant is not limited to this. Optionally, the second refrigerant is another high critical temperature refrigerant.
As shown in fig. 1 and 2, the compressor includes three cylinders, namely, a first cylinder 21, a second cylinder 22 and a third cylinder 23, the first cylinder 21, the second cylinder 22 and the third cylinder 23 being sequentially disposed along an axial direction of a crankshaft 10 of the compressor, wherein the first cylinder 21 is located above the second cylinder 22 and the third cylinder 23, the first cylinder 21 forms a first compression passage, and the second cylinder 22 and the third cylinder 23 form a second compression passage. The structure is simple and easy to realize and process.
Specifically, the second cylinder 22 and the third cylinder 23 form a two-stage compression channel, the first cylinder 21 forms a single-stage compression channel, in the process of actual use, the first compression channel and the second compression channel are respectively connected with two side-by-side heat exchangers, the heat exchanger connected with the two-stage compression channel is positioned on the windward side of the heat exchanger connected with the single-stage compression channel, and the two independent refrigerant circulation loops can conveniently adjust the condensation temperature and the evaporation temperature of the windward side and the leeward side of the heat exchanger, so that the heat exchange effect of the windward side and the leeward side of the heat exchanger can be fully utilized, the refrigerating capacity and the heating capacity are improved, and the energy efficiency of the heat exchange system is further improved.
As shown in fig. 2, a first partition 31 is provided between the second cylinder 22 and the third cylinder 23, the first partition 31 having an intermediate passage (not shown) through which the gas in the third cylinder 23 can enter into the second cylinder 22. In this way, the exhaust port of the third cylinder 23 is communicated with the air inlet of the second cylinder 22 through the middle channel, so that the communication between the second cylinder 22 and the third cylinder 23 is easier and simpler, and the processing cost of the compressor is further reduced.
As shown in fig. 2, a second partition plate 32 is provided between the first cylinder 21 and the second cylinder 22, an exhaust groove 321 for communicating with an exhaust port of the second cylinder 22 is provided on the second partition plate 32, and the second partition plate 32 has a first exhaust passage communicating with the exhaust groove 321. The structure is simple and easy to realize.
Specifically, the gas entering the third cylinder 23 is compressed in the third cylinder 23, enters the second cylinder 22 through the middle channel on the first partition 31 after the compression is completed, is compressed in the second cylinder 22 for the second time, enters the exhaust groove 321 through the exhaust port of the second cylinder 22 after the compression is completed, and is finally discharged to the outside of the compressor through the first exhaust channel.
As shown in fig. 2, a third partition plate 33 is provided between the first cylinder 21 and the second partition plate 32, the notch of the exhaust groove 321 is provided toward the third partition plate 33, the third partition plate 33 is provided to cover the exhaust groove 321, and the bottom of the exhaust groove 321 communicates with the exhaust port of the second cylinder 22 through the first communication hole. Specifically, the exhaust port of the second cylinder 22 is communicated with the exhaust groove 321 through the first communication hole in the third partition 33, and the gas discharged from the exhaust port of the second cylinder 22 enters into the exhaust groove 321 through the first communication hole and is finally discharged from the first exhaust passage. The structure is simple and easy to process and realize.
In other embodiments not shown in the drawings, the notch of the exhaust recess on the second partition faces the second cylinder, and the exhaust port of the second cylinder communicates with the exhaust recess, and the second partition has a first exhaust passage communicating with the exhaust recess. Specifically, the gas discharged from the exhaust port of the second cylinder is discharged from the first exhaust passage through the exhaust groove. The structure is simple and easy to process and realize.
As shown in fig. 1 and 2, the compressor further includes a first flange 41 and a cover plate 50 which are sleeved on the crankshaft 10, the first flange 41 having a transfer groove 411 on a side facing the cover plate 50, the cover plate 50 being positioned under the first flange 41 and covering the transfer groove 411, the exhaust hole of the third cylinder 23 being communicated with the transfer groove 411 through a second communication hole at a bottom of the transfer groove 411, the third cylinder 23 having a communication passage which is communicated with the transfer groove 411 through a third communication hole at a bottom of the transfer groove 411, the communication passage being communicated with the intermediate passage. The structure is simple and easy to process and realize.
Specifically, the gas compressed in the third cylinder 23 is introduced into the transfer groove 411 through the exhaust hole of the third cylinder 23 and the second communication hole of the first flange 41, and then introduced into the communication passage of the third cylinder 23 through the third communication hole of the first flange 41 into the intermediate passage of the first separator 31, and then introduced into the second cylinder 22 through the intermediate passage. After the second compression in the second cylinder 22, the gas enters the exhaust groove 321 of the second partition plate 32 through the exhaust port of the second cylinder 22 and the first communication hole of the second partition plate 32, and finally is discharged from the first exhaust passage.
As shown in fig. 1, the compressor further includes a first knockout 61 and a gas-supplementing enthalpy-increasing pipe 70, the first knockout 61 is communicated with the intake port of the third cylinder 23, and the gas-supplementing enthalpy-increasing pipe 70 is communicated with the conveying groove 411. In this way, the air supply enthalpy increasing pipe 70 can supply air in the second cylinder 22 and the third cylinder 23 to increase the compression amount of the compressor.
Specifically, the gas, which has completed compression in the third cylinder 23, enters into the transfer groove 411 through the exhaust port thereof. Meanwhile, the gas in the gas-supplementing enthalpy-increasing pipe 70 enters into the transmission groove 411, is mixed with the compressed gas, enters into the intermediate passage of the first partition plate 31 through the communication passage of the third communication hole of the first flange 41 into the third cylinder 23 after the mixing is completed, and then enters into the second cylinder 22 through the intermediate passage, and is secondarily compressed in the second cylinder 22.
As shown in fig. 1 and 2, the compressor further includes a second flange 42 above the first cylinder 21, and a second exhaust passage (not shown) for communicating with the exhaust port of the first cylinder 21 is provided on the second flange 42. In this way, the gas discharged from the second exhaust passage of the second flange 42 is discharged to the outside through the first exhaust pipe 181 provided on the housing 180.
As shown in fig. 2, the compressor further includes a second liquid separator 62, and the second liquid separator 62 communicates with the suction port of the first cylinder 21 to facilitate the delivery of the refrigerant into the first cylinder 21.
As shown in fig. 3, the present application further provides a heat exchange system, which includes a compressor, and the compressor is the compressor 110.
As shown in fig. 3, the heat exchange system further includes an outdoor heat exchanger 80, a first throttling element 90, and an intermediate heat exchanger 100, where the outdoor heat exchanger 80, the first throttling element 90, the intermediate heat exchanger 100, and a first compression channel of the compressor 110 are connected by a pipe to form a first refrigerant circulation loop. The heat exchange system further comprises an indoor heat exchanger 120 and a second throttling element 130, wherein the indoor heat exchanger 120, the second throttling element 130, the intermediate heat exchanger 100 and a second compression channel of the compressor 110 are connected through pipelines to form a second refrigerant circulation loop. Like this, above-mentioned setting can realize the heat transfer of two kinds of different temperatures of heat transfer system to satisfy the different operation requirement of user, promote user's use experience.
In this embodiment, the heat exchange system is a hot water system. The intermediate heat exchanger 100 is disposed in the water tank, and the refrigerant flowing through the intermediate heat exchanger 100 exchanges heat with water in the water tank to realize heating. Therefore, high-temperature hot water can be prepared by adopting the overlapping type hot water system, the volume of a water tank of the water heater is reduced, the installation space is reduced, and the material cost and the transportation cost are reduced. Meanwhile, the heat exchange system in the embodiment can solve the reliability problem and the energy efficiency problem caused by the low pressure ratio and the low pressure difference of the low-temperature working condition. In addition, the hot water system adopts a compressor, so that the processing and manufacturing cost of the compressor is reduced.
Specifically, the first refrigerant circulation loop is a low-temperature refrigerant circulation loop, the second refrigerant circulation loop is a high-temperature refrigerant circulation loop, and the low-temperature refrigerant circulation loop and the high-temperature refrigerant circulation loop are overlapped in the same heat exchange system, so that not only can high-temperature water be prepared, but also the volume of a water tank of a hot water system can be reduced, and the installation space is reduced. The low-temperature refrigerant circulation loop adopts R32 refrigerant to heat cold water to medium-temperature hot water, so that the problems of low-temperature evaporation pressure and small pressure ratio can be solved, and the reliability of the compressor 110 is improved; the high-temperature refrigerant circulation loop adopts R134a refrigerant to prepare high-temperature hot water. Therefore, high-temperature hot water can be prepared, the pressure ratio can be reduced, and the reliability of the compressor and the energy efficiency of the hot water system can be improved.
As shown in fig. 3, the intermediate heat exchanger 100 includes two independent first and second pipelines 101 and 102, the first pipeline 101 is communicated with the first compression channel, the second pipeline 102 is communicated with the second compression channel, and the flow directions of the refrigerants in the first pipeline 101 and the second pipeline 102 are opposite. Thus, the intermediate heat exchanger 100 can participate in both the low-temperature refrigerant circulation loop and the high-temperature refrigerant circulation loop, and can promote the heat exchange between the low-temperature refrigerant circulation loop and the high-temperature refrigerant circulation loop, so as to raise the evaporation temperature of the high-temperature refrigerant circulation loop and prevent the leakage problem caused by too low evaporation pressure (for example, the pressure of R134a refrigerant is only 0.106MPa at the evaporation temperature of-25 ℃, which is equivalent to the atmospheric pressure, and the leakage accident is easy to occur). Meanwhile, the above arrangement can reduce the compression ratio, i.e., reduce the load of the compressor 110, and improve the operational reliability of the compressor 110. In addition, since the intermediate heat exchanger 100 is not only a condenser of the low-temperature refrigerant circulation loop but also an evaporator of the high-temperature refrigerant circulation loop, and only one fan is used for providing air quantity, the installation space is saved, the cost is reduced, and the power consumption can be reduced.
As shown in fig. 3, the heat exchange system further includes a third throttling element 140 and a flash vessel 150. Wherein the third throttling element 140 and the flash vessel 150 are arranged between the second throttling element 130 and the intermediate heat exchanger 100. The third throttling element 140 is disposed between the flash evaporator 150 and the intermediate heat exchanger 100, and one port of the flash evaporator 150 is connected to the air-supplementing enthalpy-increasing pipe 70 of the compressor 110. In this way, the refrigerant is further compressed in the third throttling element 140 so that the refrigerant is in a low-temperature low-pressure gas-liquid mixture state.
As shown in fig. 3, the heat exchange system further includes a control valve 160. The control valve 160 is disposed on the air-supplementing and enthalpy-increasing pipeline 70, and is used for controlling on-off of the air-supplementing and enthalpy-increasing pipeline 70 of the compressor 110 and the flash evaporator 150. Thus, the control valve 160 controls the on-off of the air supplementing enthalpy increasing pipeline 70 and the flash evaporator 150, and air supplementing is performed when the air supplementing is needed by the compressor, so that the energy utilization rate is improved.
In this embodiment, the working principle of the heat exchange system is as follows:
a first refrigerant circulation circuit: the first refrigerant absorbs heat in the outdoor heat exchanger 80 (evaporator), changes from a low-temperature low-pressure gas-liquid mixed state to a low-temperature low-pressure gas state, and the gas refrigerant enters the first cylinder 21 through the second liquid separator 62, is compressed to form a high-temperature high-pressure gas refrigerant, and is discharged from the first exhaust pipe 181. Then, the high-temperature and high-pressure gaseous refrigerant enters the intermediate heat exchanger 100 and is condensed into a high-temperature and high-pressure liquid refrigerant, the high-temperature and high-pressure liquid refrigerant is reduced in pressure through the first throttling element 90 to become a low-temperature and low-pressure gas-liquid mixed state refrigerant, and then the low-temperature and low-pressure gas-liquid mixed state refrigerant enters the outdoor heat exchanger 80 (evaporator) to absorb heat and returns to the first cylinder 21 through the second liquid separator 62, so that a low-temperature refrigerant circulation loop is formed. The exhaust temperature of the low-temperature refrigerant circulation loop is relatively low, so that the motor 190 of the compressor can be effectively cooled, the power of the motor 190 can be reduced, the energy efficiency of the compressor can be improved, and the operation reliability of the compressor can be improved. In addition, since the evaporation pressure of the first refrigerant is high, the problem of leakage of the first refrigerant due to low evaporation pressure can be solved.
A second refrigerant circulation circuit: the second refrigerant absorbs heat in the intermediate heat exchanger 100, the low-temperature low-pressure gas-liquid mixed state is changed into low-temperature low-pressure gas state, the gas refrigerant enters the third cylinder 23 through the first liquid separator 61 for primary compression, the gas refrigerant with medium temperature and medium pressure is formed through compression, and the gas refrigerant is discharged into the transmission groove 411 of the first flange 41. Meanwhile, part of the refrigerant flashed by the flash evaporator 150 enters the transmission groove 411 through the air supplementing enthalpy increasing pipeline 70, is mixed with the refrigerant discharged from the air outlet of the third air cylinder 23, enters the second air cylinder 22 for secondary compression, forms high-temperature and high-pressure gaseous refrigerant after secondary compression, and is discharged into a cavity surrounded by the second partition plate 32 and the third partition plate 33 and is discharged from the second exhaust pipe 182. Then, the high-temperature and high-pressure gaseous refrigerant enters the indoor heat exchanger 120 (condenser) and is condensed into a high-temperature and high-pressure saturated liquid refrigerant, the high-temperature and high-pressure saturated liquid refrigerant is reduced in pressure through the second throttling element 130 to become a medium-temperature and medium-pressure gas-liquid mixed state refrigerant, and the gas-liquid mixed state refrigerant enters the flash evaporator 150 and is split into two paths.
The first path is liquid refrigerant without flash. The liquid refrigerant without flash evaporation is further reduced in pressure to a low-temperature low-pressure gas-liquid mixed state through the third throttling element 140, then enters the intermediate heat exchanger 100 again to absorb heat, returns to the third cylinder 23 through the first liquid separator 61, and is compressed and exhausted:
the second path is the saturated gaseous refrigerant flashed from flash vessel 150. The saturated gaseous refrigerant flashed from the flash evaporator 150 enters the first flange 41 through the air supplementing enthalpy increasing pipeline 70, is mixed with the primary compression exhaust gas of the third cylinder 23, and enters the second cylinder 22 for secondary compression after being mixed, so that the high-temperature refrigerant circulation loop is completed. Wherein the second path is called the air-supplementing loop.
In this embodiment, the second refrigerant circulation loop adopts a quasi-secondary circulation loop, so that the problem of high exhaust temperature can be effectively improved through two-stage compression, and meanwhile, as can be found through fig. 5 (the solid line is the pressure enthalpy diagram of the quasi-secondary circulation loop, and the dotted line is the pressure enthalpy diagram of the single-stage pressure circulation loop), the adoption of the quasi-secondary circulation loop is superior to the single-stage circulation loop in energy efficiency, so that the reliability and energy efficiency of the whole heat exchange system can be effectively improved by adopting two independent refrigerant circulation loops and the innovative adoption of the quasi-secondary circulation loop.
Example two
The heat exchange system of the second embodiment is different from the first embodiment in that: the connection relationship between the intermediate heat exchanger 100 and the indoor heat exchanger 120 is different.
Optionally, the heat exchange system further comprises a drain header 171 and at least one drain branch 172. Wherein one end of the drain header 171 is communicated with the water outlet of the intermediate heat exchanger 100, and the other end of the drain header 171 is communicated with the water inlet of the indoor heat exchanger 120. At least one drain branch 172 is connected to the drain header 171 and is disposed at an angle to the drain header 171. As shown in fig. 4, the heat exchange system further includes a drain branch 172. Specifically, cold water enters the intermediate heat exchanger 100 and is discharged into the drain branch pipe 172 through the drain header 171, so that the inside of the drain branch pipe 172 is medium-temperature water, and a user can use the medium-temperature water to wash dishes or laundry.
In the present embodiment, the water introduced into the indoor heat exchanger 120 from the drain header 171 is discharged from the indoor heat exchanger 120, and is high-temperature water, which can be used by a user to sterilize food or small-sized facilities.
From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:
in order to meet different use demands of users, different refrigerant compression channels can be adopted for heat exchange, and the refrigerant flows through the same compressor. Specifically, one type of refrigerant is used in one refrigerant compression channel, another refrigerant of a different type from the refrigerant is used in the other refrigerant compression channel, and different refrigerant compression channels are adopted according to different use requirements (such as different temperatures) so as to solve the problems of poor reliability and low energy efficiency of the compressor under the low-temperature working condition. Meanwhile, the arrangement can reduce the occupied space of the heat exchange system and reduce the processing cost of the heat exchange system.
It will be apparent that the embodiments described above are merely some, but not all, embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, shall fall within the scope of the present invention.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the present application described herein may be implemented in sequences other than those illustrated or described herein.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (14)
1. A heat exchange system comprises a compressor, and is characterized in that,
the heat exchange system further comprises an outdoor heat exchanger (80), a first throttling element (90) and an intermediate heat exchanger (100), wherein the outdoor heat exchanger (80), the first throttling element (90), the intermediate heat exchanger (100) and a first compression channel of the compressor (110) are connected through pipelines to form a first refrigerant circulation loop;
the heat exchange system further comprises an indoor heat exchanger (120) and a second throttling element (130), wherein the indoor heat exchanger (120), the second throttling element (130), the intermediate heat exchanger (100) and a second compression channel of the compressor (110) are connected through a pipeline to form a second refrigerant circulation loop;
the intermediate heat exchanger (100) comprises two mutually independent first pipelines (101) and second pipelines (102), the first pipelines (101) are communicated with the first compression channels, the second pipelines (102) are communicated with the second compression channels, and the flow directions of refrigerants in the first pipelines (101) and the second pipelines (102) are opposite;
wherein the compressor comprises:
the plurality of cylinders form at least two mutually independent refrigerant compression channels;
a plurality of refrigerants flowing through different ones of the refrigerant compression passages; different refrigerant compression channels are adopted according to different use requirements;
the at least two refrigerant compression channels comprise a first compression channel and a second compression channel, the compressor comprises at least three air cylinders, at least one air cylinder forms the first compression channel, and at least two air cylinders form the second compression channel;
the plurality of refrigerants includes a first refrigerant flowing through the first compression passage and a second refrigerant flowing through the second compression passage, and a critical temperature of the first refrigerant is less than a critical temperature of the second refrigerant.
2. The heat exchange system of claim 1, wherein the first refrigerant has a refrigeration per unit volume greater than a preset value.
3. The heat exchange system of claim 1, wherein the critical temperature of the second refrigerant is greater than a preset temperature.
4. The heat exchange system according to claim 1, wherein the compressor includes three cylinders, which are a first cylinder (21), a second cylinder (22) and a third cylinder (23), respectively, the first cylinder (21), the second cylinder (22) and the third cylinder (23) being sequentially disposed along an axial direction of a crankshaft (10) of the compressor, wherein the first cylinder (21) is located above the second cylinder (22) and the third cylinder (23), the first cylinder (21) forms the first compression passage, and the second cylinder (22) and the third cylinder (23) form the second compression passage.
5. The heat exchange system according to claim 4, wherein a first partition (31) is provided between the second cylinder (22) and the third cylinder (23), the first partition (31) having an intermediate passage through which gas in the third cylinder (23) can enter into the second cylinder (22).
6. The heat exchange system according to claim 4 or 5, wherein a second partition plate (32) is provided between the first cylinder (21) and the second cylinder (22), an exhaust groove (321) for communicating with an exhaust port of the second cylinder (22) is provided on the second partition plate (32), and the second partition plate (32) has a first exhaust passage communicating with the exhaust groove (321).
7. The heat exchange system according to claim 6, wherein a third partition plate (33) is provided between the first cylinder (21) and the second partition plate (32), a notch of the exhaust groove (321) is provided toward the third partition plate (33), the third partition plate (33) is covered on the exhaust groove (321), and a bottom of the exhaust groove (321) is communicated with an exhaust port of the second cylinder (22) through a first communication hole.
8. The heat exchange system according to claim 5, wherein the compressor further comprises a first flange (41) and a cover plate (50) which are sleeved on the crankshaft (10), wherein a transmission groove (411) is formed in one side of the first flange (41) facing the cover plate (50), the cover plate (50) is positioned below the first flange (41) and covers the transmission groove (411), the exhaust hole of the third cylinder (23) is communicated with the transmission groove (411) through a second communication hole at the bottom of the transmission groove (411), and the third cylinder (23) is provided with a communication channel which is communicated with the transmission groove (411) through a third communication hole at the bottom of the transmission groove (411), and the communication channel is communicated with the intermediate channel.
9. The heat exchange system according to claim 8, wherein the compressor further comprises a first liquid separator (61) and a gas-supplementing enthalpy-increasing pipe (70), the first liquid separator (61) is in communication with the suction port of the third cylinder (23), and the gas-supplementing enthalpy-increasing pipe (70) is in communication with the transmission groove (411).
10. The heat exchange system according to claim 4, wherein the compressor further comprises a second flange (42) located above the first cylinder (21), the second flange (42) being provided with a second exhaust passage for communicating with an exhaust port of the first cylinder (21).
11. The heat exchange system according to claim 4, wherein the compressor further comprises a second dispenser (62), the second dispenser (62) being in communication with the suction port of the first cylinder (21).
12. The heat exchange system of claim 1, further comprising:
the device comprises a third throttling element (140) and a flash evaporator (150) which are arranged between the second throttling element (130) and the intermediate heat exchanger (100), wherein the third throttling element (140) is arranged between the flash evaporator (150) and the intermediate heat exchanger (100), and one port of the flash evaporator (150) is connected with a gas supplementing enthalpy increasing pipeline (70) of the compressor (110).
13. The heat exchange system of claim 12, further comprising:
and the control valve (160) is arranged on the air supplementing and enthalpy increasing pipeline (70) and is used for controlling the on-off of the air supplementing and enthalpy increasing pipeline (70) of the compressor (110) and the flash evaporator (150).
14. The heat exchange system of claim 1, further comprising:
a water draining main pipe (171), wherein one end of the water draining main pipe (171) is communicated with a water outlet of the intermediate heat exchanger (100), and the other end of the water draining main pipe (171) is communicated with a water inlet of the indoor heat exchanger (120);
and at least one drainage branch pipe (172) connected with the drainage main pipe (171) and arranged at an included angle with the drainage main pipe (171).
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| CN109340113A (en) * | 2018-11-19 | 2019-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly and compressor |
| CN109751795B (en) * | 2018-12-20 | 2020-02-07 | 珠海格力电器股份有限公司 | Heat pump system and control method thereof |
| WO2020132894A1 (en) * | 2018-12-25 | 2020-07-02 | 广东美的白色家电技术创新中心有限公司 | Compressor, heat pump system, water heater and clothes drying machine |
| CN112746963B (en) * | 2019-10-31 | 2022-06-14 | 广东美的白色家电技术创新中心有限公司 | Compressor, compressor assembly, heat exchange system and electrical equipment |
| CN112594952A (en) * | 2020-12-16 | 2021-04-02 | 宁波爱握乐热能科技有限公司 | Ultra-low temperature frequency conversion cascade air source heat pump unit |
| CN113776863B (en) * | 2021-07-19 | 2024-03-19 | 威凯检测技术有限公司 | Comprehensive test device and method for remote refrigeration appliance |
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