CN118189428A - Self-overlapping high-temperature heat pump system - Google Patents
Self-overlapping high-temperature heat pump system Download PDFInfo
- Publication number
- CN118189428A CN118189428A CN202410456776.8A CN202410456776A CN118189428A CN 118189428 A CN118189428 A CN 118189428A CN 202410456776 A CN202410456776 A CN 202410456776A CN 118189428 A CN118189428 A CN 118189428A
- Authority
- CN
- China
- Prior art keywords
- pipeline
- branch pipe
- refrigerant
- communicated
- self
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 57
- MSSNHSVIGIHOJA-UHFFFAOYSA-N pentafluoropropane Chemical group FC(F)CC(F)(F)F MSSNHSVIGIHOJA-UHFFFAOYSA-N 0.000 claims abstract description 17
- 238000009833 condensation Methods 0.000 claims abstract description 7
- 230000005494 condensation Effects 0.000 claims abstract description 7
- 239000007788 liquid Substances 0.000 claims description 39
- 238000005507 spraying Methods 0.000 claims description 11
- 238000000034 method Methods 0.000 claims 1
- 238000001035 drying Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Landscapes
- Other Air-Conditioning Systems (AREA)
Abstract
The invention relates to the technical field of high-temperature heat pumps, in particular to a self-cascade high-temperature heat pump system, which comprises a system main body, wherein heat energy is transferred in the system main body through a mixed refrigerant, the mixed refrigerant consists of a first refrigerant and a second refrigerant, and the condensation temperature of the second refrigerant is lower than that of the first refrigerant; the first refrigerant is R245fa, and the second refrigerant is R134a. The invention adopts R245fa+R134a mixed refrigerant, R245fa has higher condensing temperature, and the gas with high condensing temperature and higher temperature can be prepared by a self-cascade compressor refrigerating system, and the gas temperature can reach 120 ℃.
Description
Technical Field
The invention relates to the technical field of high-temperature heat pumps, in particular to a self-cascade high-temperature heat pump system.
Background
The air source high-temperature heat pump technology is adopted to extract heat from the air, and then a higher-quality heat source is prepared through the self-cascade system, so that the heat source is widely applied to food processing, chemical fiber and chemical industry.
The highest condensing temperature of the traditional compressor is generally less than or equal to 85 ℃, so the temperature for preparing steam by adopting an air source heat pump unit is generally lower than 80 ℃.
The patent with publication number CN108204690B discloses a single-compressor quasi-cascade air source heat pump system, wherein a single-component (approximate) high-temperature refrigerant heating circulation path is that a compressor exhaust port enters a condenser refrigerant inlet through a four-way valve branch pipe and an electromagnetic valve, after condensation, a condenser refrigerant outlet enters an evaporator inlet through the electromagnetic valve and an electronic expansion valve, and saturated steam after evaporation enters a compressor air suction port through an evaporator outlet through a two-way electromagnetic valve and a four-way valve branch pipe and then enters the four-way valve branch pipe, so that one single-component heating circulation is completed.
With the above system, the maximum temperature of the gas can only reach 70 ℃.
Therefore, the condensation temperature and the output gas temperature of the existing self-cascade high-temperature heat pump system have a certain lifting space.
Disclosure of Invention
In order to solve the technical problems, the invention aims to: a self-cascade high temperature heat pump system is provided to increase the temperature of the output gas.
The invention adopts the technical scheme that:
The self-overlapping high-temperature heat pump system comprises a system main body, wherein heat energy is transferred in the system main body through a mixed refrigerant, the mixed refrigerant consists of a first refrigerant and a second refrigerant, and the condensation temperature of the second refrigerant is lower than that of the first refrigerant; the first refrigerant is R245fa, and the second refrigerant is R134a.
As a further improvement of the above technical solution, the system main body includes a compressor, a gas-liquid separator, an intermediate heat exchanger, a first heat exchanger and a second heat exchanger; the intermediate heat exchanger is provided with a first channel and a second channel, and the gas-liquid separator is provided with a gaseous refrigerant outlet and a liquid refrigerant outlet; the input end of the first channel is communicated with the gaseous refrigerant outlet, the input end of the second channel is communicated with the liquid refrigerant outlet through a first pipeline, and the output end of the second channel is communicated with the input end of the compressor through a second pipeline; the first pipeline is provided with a first expansion valve.
As a further improvement of the technical scheme, a first branch pipe is arranged on the first pipeline, a liquid spraying pipe is arranged on the compressor, one end of the first branch pipe is communicated with the first pipeline, and the other end of the first branch pipe is communicated with the liquid spraying pipe; the first branch pipe is provided with a liquid spraying capillary and a first valve.
As a further improvement of the technical scheme, a second branch pipe is arranged on the first pipeline, one end of the second branch pipe is communicated with the first pipeline, and the other end of the second branch pipe is communicated with the second pipeline; and the second branch pipe is provided with a capillary pipe and a second valve.
As a further improvement of the above technical solution, the output end of the compressor is communicated with the input end of the first heat exchanger through a third pipeline; a third branch pipe is arranged on the third pipeline, one end of the third branch pipe is communicated with the third pipeline, and the other end of the third branch pipe is communicated with the second pipeline; and a hot gas bypass valve is arranged on the third branch pipe.
As a further improvement of the above technical solution, the output end of the first channel is communicated with the input end of the second heat exchanger through a fourth pipeline; and a thermal expansion valve is arranged on the fourth pipeline.
As a further improvement of the above technical solution, the second pipeline is provided with a gas mixer, and the output end of the second heat exchanger is communicated with the gas mixer through a fifth pipeline.
As a further improvement of the technical scheme, a fourth branch pipe is communicated with the first pipeline, and two sides of the fourth branch pipe are respectively connected with two sides of the first expansion valve; and a second expansion valve is arranged on the fourth branch pipe.
The beneficial effects of the invention are as follows: the invention adopts R245fa+R134a mixed refrigerant, R245fa has higher condensing temperature, and the gas with high condensing temperature and higher temperature can be prepared by a self-cascade compressor refrigerating system, and the gas temperature can reach 120 ℃.
Drawings
The invention is further illustrated by the following description and examples of the embodiments in conjunction with the accompanying drawings.
FIG. 1 is a schematic view of a preferred embodiment of the present invention;
In the figure: 1-compressor, 11-spray pipe, 2-gas-liquid separator, 21-gaseous refrigerant outlet, 22-liquid refrigerant outlet, 3-intermediate heat exchanger, 31-first channel, 32-second channel, 4-first heat exchanger, 5-second heat exchanger, 61-first pipe, 611-reservoir, 612-first dry filter, 613-liquid mirror, 614-first expansion valve, 615-first solenoid valve, 616-first branch pipe, 6161-spray capillary, 6162-first valve, 617-second branch pipe, 6171-capillary, 6172-second valve, 618-fourth branch pipe, 6181-second expansion valve, 6182-second solenoid valve, 62-second pipe, 621-gas mixer, 622-first check valve, 63-third pipe, 631-oil separator, 632-third branch pipe, 6321-hot gas bypass valve, 64-fourth pipe, 651-thermal expansion valve, 642-second dry filter, 643-second liquid mirror, 65-third pipe, 65-fifth check valve.
Detailed Description
Reference will now be made in detail to the present embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein the accompanying drawings are used to supplement the description of the written description so that one can intuitively and intuitively understand each technical feature and overall technical scheme of the present invention, but not to limit the scope of the present invention.
In the description of the present invention, it should be understood that references to orientation descriptions such as upper, lower, front, rear, left, right, etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience of description of the present invention and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present invention.
In the description of the present invention, a number means one or more, a number means two or more, and greater than, less than, exceeding, etc. are understood to not include the present number, and above, below, within, etc. are understood to include the present number. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.
In the description of the present invention, unless explicitly defined otherwise, terms such as arrangement, installation, connection, etc. should be construed broadly and the specific meaning of the terms in the present invention can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical scheme.
Referring to fig. 1, a self-cascade high-temperature heat pump system comprises a system main body, wherein the system main body comprises a compressor 1, a gas-liquid separator 2, an intermediate heat exchanger 3, a first heat exchanger 4 and a second heat exchanger 5, the intermediate heat exchanger 3 is provided with a first channel 31 and a second channel 32, the gas-liquid separator 2 is provided with a gaseous refrigerant outlet 21 and a liquid refrigerant outlet 22, the input end of the first channel 31 is communicated with the gaseous refrigerant outlet 21, the input end of the second channel 32 is communicated with the liquid refrigerant outlet 22 through a first pipeline 61, a liquid reservoir 611, a first drying filter 612 and a first liquid-viewing mirror 613 are arranged on the first pipeline 61, the output end of the second channel 32 is communicated with the input end of the compressor 1 through a second pipeline 62, the output end of the compressor 1 is communicated with the input end of the first heat exchanger 4 through a third pipeline 63, an oil separator 631 is arranged on the third pipeline 63, and the system main body is internally communicated with the first refrigerant and the second refrigerant at a lower temperature than the first refrigerant; the first refrigerant is R245fa, and the second refrigerant is R134a. The invention adopts R245fa+R134a mixed refrigerant, R245fa has higher condensing temperature, and the gas with high condensing temperature and higher temperature can be prepared by a refrigerating system of the self-cascade compressor 1, and the gas temperature can reach 120 ℃.
In some embodiments, the first conduit 61 has a first expansion valve 614 and a first solenoid valve 615 mounted thereon. The R245fa liquid refrigerant is throttled by the first expansion valve 614.
In some embodiments, a first branch pipe 616 is disposed on the first pipeline 61, a liquid spraying pipe 11 is disposed on the compressor 1, one end of the first branch pipe 616 is communicated with the first pipeline 61, the other end of the first branch pipe 616 is communicated with the liquid spraying pipe 11, and a liquid spraying capillary 6161 and a first valve 6162 (using a hand valve) are mounted on the first branch pipe 616. The R245fa liquid refrigerant from the liquid reservoir 611 flows into the liquid spraying pipe 11 of the compressor 1 through the liquid spraying adjusting capillary tube 6161 and the first valve 6162 to cool the compressor 1.
In some embodiments, a second branch 617 is disposed on the first pipeline 61, one end of the second branch 617 is communicated with the first pipeline 61, and the other end of the second branch 617 is communicated with the second pipeline 62; the second branch pipe 617 is provided with a capillary tube 6171 and a second valve 6172. Heat entering the return air end of the compressor 1 can be neutralized by adjusting the capillary tube 6171 and the second valve 6172 to prevent the return air of the compressor 1 from being overheated.
In some embodiments, a third branch pipe 632 is disposed on the third pipe 63, one end of the third branch pipe 632 communicates with the third pipe 63 (communicates on the output end side of the oil separator 631), and the other end of the third branch pipe 632 communicates with the second pipe 62; the third branch pipe 632 is provided with a hot gas bypass valve 6321. By means of the hot gas bypass valve 6321, the compressor 1 can be adjusted, further preventing the compressor 1 from overheating.
In some embodiments, the output end of the first channel 31 is communicated with the input end of the second heat exchanger 5 through a fourth pipeline 64, and a second drying filter 642, a second liquid-viewing mirror 643613 and a third electromagnetic valve 644 are installed on the fourth pipeline 64; the fourth pipeline 64 is provided with a thermal expansion valve 641. The R134a liquid refrigerant enters the second heat exchanger 5 after being throttled and depressurized by the thermal expansion valve 641, absorbs heat in the air and evaporates into a gaseous R134a refrigerant.
In some embodiments, the second pipeline 62 is provided with a gas mixer 621, a pipeline between the intermediate heat exchanger 3 and the gas mixer 621 is provided with a first check valve 622, the output end of the second heat exchanger 5 is communicated with the gas mixer 621 through a fifth pipeline 65, and the fifth pipeline 65 is provided with a second check valve 651. The gaseous R134a refrigerant and the gaseous R245fa refrigerant enter the gas mixer 621 and are fully mixed, enter the suction end of the compressor 1, and are further boosted and heated to be discharged from the exhaust port of the compressor 1.
In some embodiments, the first pipeline 61 is communicated with a fourth branch pipe 618, two sides of the fourth branch pipe 618 are respectively connected to two sides of the first expansion valve 614, and the fourth branch pipe 618 is provided with a second expansion valve 6181 and a second electromagnetic valve 6182, so that the pressure of the R245fa liquid refrigerant is reduced and throttled.
Specifically, the third pipeline 63 is provided with a first pressure gauge and a high-pressure switch, and the pipeline between the output end of the gas mixer 621 and the input end of the compressor 1 is provided with a second pressure gauge.
Further, the first heat exchanger 4 and the second heat exchanger 5 are fin heat exchangers, and the intermediate heat exchanger 3 is a plate heat exchanger.
Further, the compressor 1 adopts an ultra-high temperature compressor 1 produced by Cope l and company, the return air temperature can reach 55 ℃ at most, and the maximum condensation temperature can reach 135 ℃.
Working principle: after the exhaust gas of the compressor 1 is subjected to heat exchange by the first heat exchanger 4, R245fa is condensed into liquid, R134a is not condensed or is in a gaseous state due to high temperature, the gas is subjected to gas-liquid separation by the gas-liquid separator 2, the gaseous state R134a is discharged from the upper part (gaseous refrigerant outlet 21) and enters the intermediate heat exchanger 3, the R245fa liquid is throttled by the first expansion valve 614 and the second expansion valve 6181 and then flows through the intermediate heat exchanger 3 and the gaseous state R134a to be subjected to heat release and condensation into a liquid state, the liquid state R134a is throttled by the thermal expansion valve 641 and then enters the second heat exchanger 5 to evaporate and absorb heat in the air, the R245fa absorbs the heat of the gaseous state R134a and then evaporates and gasifies and the gaseous state R134a is mixed by the gas mixer 621 and returns to the air return end of the compressor 1, the gaseous state R134a is compressed into the high temperature by the compressor 1 and the high-pressure gas is discharged by the air outlet of the compressor 1, and a complete refrigeration cycle is formed.
The foregoing description of the preferred embodiments of the present invention should not be construed as limiting the scope of the invention, but rather should be understood to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention as defined by the following description and drawings or any application directly or indirectly to other relevant art(s).
Claims (8)
1. The self-overlapping high-temperature heat pump system comprises a system main body, wherein heat energy is transferred in the system main body through a mixed refrigerant, the mixed refrigerant consists of a first refrigerant and a second refrigerant, and the condensation temperature of the second refrigerant is lower than that of the first refrigerant;
The method is characterized in that:
the first refrigerant is R245fa, and the second refrigerant is R134a.
2. A self-cascade high temperature heat pump system as in claim 1, wherein:
The system main body comprises a compressor (1), a gas-liquid separator (2), an intermediate heat exchanger (3), a first heat exchanger (4) and a second heat exchanger (5);
The intermediate heat exchanger (3) is provided with a first channel (31) and a second channel (32), and the gas-liquid separator (2) is provided with a gaseous refrigerant outlet (21) and a liquid refrigerant outlet (22);
The input end of the first channel (31) is communicated with the gaseous refrigerant outlet (21), the input end of the second channel (32) is communicated with the liquid refrigerant outlet (22) through a first pipeline (61), and the output end of the second channel (32) is communicated with the input end of the compressor (1) through a second pipeline (62);
a first expansion valve (614) is mounted on the first pipeline (61).
3. A self-cascade high temperature heat pump system as in claim 2, wherein:
A first branch pipe (616) is arranged on the first pipeline (61), a liquid spraying pipe (11) is arranged on the compressor (1), one end of the first branch pipe (616) is communicated with the first pipeline (61), and the other end of the first branch pipe (616) is communicated with the liquid spraying pipe (11);
The first branch pipe (616) is provided with a liquid spraying capillary (6161) and a first valve (6162).
4. A self-cascade high temperature heat pump system as in claim 2, wherein:
a second branch pipe (617) is arranged on the first pipeline (61), one end of the second branch pipe (617) is communicated with the first pipeline (61), and the other end of the second branch pipe (617) is communicated with the second pipeline (62);
and a capillary (6171) and a second valve (6172) are arranged on the second branch pipe (617).
5. A self-cascade high temperature heat pump system as in claim 2, wherein:
The output end of the compressor (1) is communicated with the input end of the first heat exchanger (4) through a third pipeline (63);
A third branch pipe (632) is arranged on the third pipeline (63), one end of the third branch pipe (632) is communicated with the third pipeline (63), and the other end of the third branch pipe (632) is communicated with the second pipeline (62);
the third branch pipe (632) is provided with a hot gas bypass valve (6321).
6. A self-cascade high temperature heat pump system as in claim 2, wherein:
The output end of the first channel (31) is communicated with the input end of the second heat exchanger (5) through a fourth pipeline (64);
The fourth pipeline (64) is provided with a thermal expansion valve (641).
7. A self-cascade high temperature heat pump system as recited in claim 6, wherein:
The second pipeline (62) is provided with a gas mixer (621), and the output end of the second heat exchanger (5) is communicated with the gas mixer (621) through a fifth pipeline (65).
8. A self-cascade high temperature heat pump system as in claim 2, wherein:
a fourth branch pipe (618) is communicated with the first pipeline (61), and two sides of the fourth branch pipe (618) are respectively connected with two sides of the first expansion valve (614);
the fourth branch pipe (618) is provided with a second expansion valve (6181).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410456776.8A CN118189428A (en) | 2024-04-16 | 2024-04-16 | Self-overlapping high-temperature heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410456776.8A CN118189428A (en) | 2024-04-16 | 2024-04-16 | Self-overlapping high-temperature heat pump system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN118189428A true CN118189428A (en) | 2024-06-14 |
Family
ID=91412192
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410456776.8A Pending CN118189428A (en) | 2024-04-16 | 2024-04-16 | Self-overlapping high-temperature heat pump system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN118189428A (en) |
-
2024
- 2024-04-16 CN CN202410456776.8A patent/CN118189428A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101413707B1 (en) | Waste Recovery Heat Pump System with 2nd Evaporaton | |
| CN107366621B (en) | Rolling rotor compressor with three-stage air supplement and air conditioning system | |
| CN103292523A (en) | Refrigerating-heating air conditioning system with heat regenerator | |
| CN105135729A (en) | Single-refrigerant-loop and multi-exhaust-pressure vapor compression refrigeration/heat pump system | |
| CN109869944A (en) | Absorption supercooling refrigeration system | |
| KR20010107052A (en) | Heat pump system | |
| CN205783983U (en) | The heat high efficiente callback device of air source handpiece Water Chilling Units | |
| CN114909725B (en) | Efficient energy-saving multi-split system | |
| CN109751768A (en) | A kind of second level heat pump system with cooling heat exchange device | |
| CN104236146A (en) | Refrigerating circulation system | |
| CN118189428A (en) | Self-overlapping high-temperature heat pump system | |
| CN105928201A (en) | Air source high-temperature heat pump | |
| CN201225784Y (en) | Heat pump plant unit | |
| CN101660850A (en) | Air conditioning system | |
| CN209622910U (en) | A kind of air source heat pump heating system | |
| CN112710082A (en) | Ultra-low temperature overlapping formula air source heat pump hot water system | |
| CN105783331A (en) | Heat efficient recovery device for air source water chilling unit | |
| CN206247522U (en) | A kind of trilogy supply air source heat pump system | |
| CN217785518U (en) | Air source heat pump unit | |
| CN110173912A (en) | A kind of the mixed working fluid compression circulatory system and working method of the recuperation of heat of band machinery | |
| CN219756547U (en) | Air conditioner system | |
| CN215675892U (en) | Enhanced vapor injection split air conditioning system | |
| CN219103146U (en) | Heat exchange air conditioning system | |
| CN214307710U (en) | Single-system double-temperature secondary throttling technology | |
| CN219140968U (en) | High-temperature-resistant kitchen air conditioner refrigerating system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination |