CN107120916A - Superposition type dual temperature drying system - Google Patents
Superposition type dual temperature drying system Download PDFInfo
- Publication number
- CN107120916A CN107120916A CN201710315541.7A CN201710315541A CN107120916A CN 107120916 A CN107120916 A CN 107120916A CN 201710315541 A CN201710315541 A CN 201710315541A CN 107120916 A CN107120916 A CN 107120916A
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- Prior art keywords
- condenser
- evaporator
- superposition type
- compressor
- drying system
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B5/00—Drying solid materials or objects by processes not involving the application of heat
- F26B5/04—Drying solid materials or objects by processes not involving the application of heat by evaporation or sublimation of moisture under reduced pressure, e.g. in a vacuum
- F26B5/06—Drying solid materials or objects by processes not involving the application of heat by evaporation or sublimation of moisture under reduced pressure, e.g. in a vacuum the process involving freezing
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- 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
-
- 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Health & Medical Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Molecular Biology (AREA)
- Drying Of Solid Materials (AREA)
Abstract
The invention provides a kind of superposition type dual temperature drying system, have the feature that, including：Low-pressure stage compressor, cryogenic vaporizer, the first condenser/evaporator, medium pressure grade compressor, the second condenser/evaporator, high pressure stage compressor and warm condenser, wherein, low-pressure stage compressor is connected with cryogenic vaporizer, and be connected by the first condenser/evaporator with medium pressure grade compressor, medium pressure grade compressor is connected by the second condenser/evaporator with high pressure stage compressor, and high pressure stage compressor is connected with warm condenser.The high temperature heat source that the superposition type dual temperature drying system of the present invention takes full advantage of superposition type system produced by chilling process is produced, reduce the operating cost of equipment, heat energy quality can also be improved simultaneously to be used to dry dry, defrosting and heat pump heating, so the energy is fully utilized, reduces energy waste.
Description
Technical field
The present invention relates to freeze-drying field, and in particular to a kind of superposition type dual temperature drying system.
Background technology
Vacuum freeze drying is widely used in industry-by-industry field due to its excellent drying effect.But cold
In lyophilized dry practical application, investment cost is high and operating cost is higher, is air-dry drying cost 3~4 times, and in freezing
In drying, pre-freeze energy consumption only accounts for 4%~14% that freeze-drying produces energy, but drying process intermediate pump, heating plate, cold
Trap work total energy consumption accounts for 86%~96% so that the effective utility of laser power of freeze-drying is greatly reduced.Although dropping in recent years
Low freeze-drying energy consuming process also has a lot, for example, accelerate to rise with procedure parameter optimization shortening drying time, improvement heat transfer
China, avoid using cold-trap, but the effect of this several method reduction energy consumption is all unsatisfactory.
The content of the invention
The present invention is carried out to solve the above problems, it is therefore intended that provide a kind of superposition type dual temperature drying system.
The invention provides a kind of superposition type dual temperature drying system, have the feature that, including：Low-pressure stage compressor,
Cryogenic vaporizer, the first condenser/evaporator, medium pressure grade compressor, the second condenser/evaporator, high pressure stage compressor and high temperature are cold
Condenser, wherein, low-pressure stage compressor is connected with cryogenic vaporizer, and is connected by the first condenser/evaporator and medium pressure grade compressor
Connect, medium pressure grade compressor is connected by the second condenser/evaporator with high pressure stage compressor, high pressure stage compressor and warm condenser
Connection.
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, low-temperature evaporation
The temperature of device is -60~-50 DEG C.
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, high temperature is condensed
The temperature of device is 100~110 DEG C.
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, low-pressure stage pressure
The refrigerant that contracting machine is used is ethane (R170).
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, medium pressure grade pressure
The refrigerant that contracting machine is used is 1,1,1,2- HFC-134as (R134A).
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, hiigh pressure stage pressure
The refrigerant that contracting machine is used is freon (R123).
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, the first condensation
Evaporator is shell and tube exchanger, and the shell and tube exchanger has condensation end and evaporation ends, and condensation end connects with low-pressure stage compressor
Connect, evaporation ends are connected with medium pressure grade compressor.
In the superposition type dual temperature drying system that the present invention is provided, it can also have the feature that：Wherein, the second condensation
Evaporator is shell and tube exchanger, and the shell and tube exchanger has condensation end and evaporation ends, and condensation end connects with medium pressure grade compressor
Connect, evaporation ends are connected with high pressure stage compressor.
The effect of invention and effect
According to superposition type dual temperature drying system involved in the present invention because take full advantage of superposition type system produce it is low
High temperature heat source produced by during temperature, reduces the operating cost of equipment, while can also improve heat energy quality to be used for
Drying is dried, thawed and heat pump heating, so that the energy is fully utilized, and reduces energy waste.In addition.The present invention
Superposition type dual temperature drying system, compared with single stage compress is circulated, be capable of the pressure of rational compressors at different levels of control system
Than so that whole superposition type dual temperature drying system is run under reasonable normal operating mode, obtains optimal Energy Efficiency Ratio.
Brief description of the drawings
Fig. 1 is the structural representation of superposition type dual temperature drying system in embodiments of the invention；
Fig. 2 is the thermodynamic cycle pressure-enthalpy chart of superposition type dual temperature drying system in embodiments of the invention.
Embodiment
In order that the technical means, the inventive features, the objects and the advantages of the present invention are easy to understand, it is real below
Example combination accompanying drawing is applied to be specifically addressed superposition type dual temperature drying system of the present invention.
Fig. 1 is the structural representation of superposition type dual temperature drying system in embodiments of the invention.
As shown in figure 1, superposition type dual temperature drying system 100 includes low-pressure stage compressor 11, the first condenser/evaporator 12, the
One choke valve 13, cryogenic vaporizer 14, medium pressure grade compressor 15, the second condenser/evaporator 16, second throttle 17, hiigh pressure stage pressure
Contracting machine 18, the 3rd choke valve 20 and warm condenser 19.
Low-pressure stage compressor 11 is used for compression refrigerant, in the present embodiment, the refrigerant that low-pressure stage compressor 11 is used
For ethane (R170).
First condenser/evaporator 12 is shell and tube exchanger, and the shell and tube exchanger has condensation end and evaporation ends, is condensed
It is 5 DEG C to hold temperature, and evaporation ends temperature is -2 DEG C.
First throttle valve 13 is connected by the condensation end of the first condenser/evaporator 12 with low-pressure stage compressor 11, first throttle
Valve 13 is used for the flow for controlling fluid.
The one end of cryogenic vaporizer 14 is connected with first throttle valve 13, and the other end is connected with low-pressure stage compressor 11.Low temperature steams
The temperature for sending out device 14 is -60~-50 DEG C, in the present embodiment, and the temperature of cryogenic vaporizer 14 is -55 DEG C.
Medium pressure grade compressor 15 is connected with the evaporation ends of the first condenser/evaporator 12, for compression refrigerant.In this implementation
In example, the refrigerant that medium pressure grade compressor 15 is used is HFA 134a (R134A).
Second condenser/evaporator 16 is shell and tube exchanger, and the shell and tube exchanger has condensation end and evaporation ends, is condensed
It is 40 DEG C to hold temperature, and evaporation ends temperature is 33 DEG C.
The one end of second throttle 17 is connected by the condensation end of the second condenser/evaporator 16 with medium pressure grade compressor 16, another
End is connected with the evaporation ends of the first condenser/evaporator 12.Second throttle 17 is used for the flow for controlling fluid.
High pressure stage compressor 18 is connected with the evaporation ends of the second condenser/evaporator 16, for compression refrigerant.In this implementation
In example, the refrigerant that high pressure stage compressor 18 is used is freon (R123).
Warm condenser 19 is connected with high pressure stage compressor 18, and for providing thermal source, temperature is 100~110 DEG C.In this reality
Apply in example, the temperature of warm condenser 19 is 100 DEG C.
The one end of 3rd choke valve 20 is connected with warm condenser 19, and the evaporation ends of the other end and the second condenser/evaporator 16 connect
Connect.3rd choke valve 20 is used for the flow for controlling fluid.
Condensation end, first throttle valve 13 and the cryogenic compressor 14 of the condenser/evaporator 12 of low-pressure stage compressor 11 and first
Constitute the first loop.
Condensation end, the condensation evaporation of second throttle 17 and first of the condenser/evaporator 16 of medium pressure grade compressor 15 and second
The evaporation ends of device 12 constitute second servo loop.
The evaporation ends of high pressure stage compressor 18 and warm condenser 19, the 3rd choke valve 20 and the second condenser/evaporator 16
Constitute tertiary circuit.
The operation principle of superposition type dual temperature drying system 100 is：The compression refrigerant ethane of low-pressure stage compressor 11, and pass through
Cryogenic vaporizer 14 is evaporated offer cold, and the temperature of cryogenic vaporizer 14 is -55 DEG C, the condensation of the first condenser/evaporator 12
It is 5 DEG C to hold temperature, and evaporation ends temperature is -2 DEG C.Heat in first loop is transmitted into second servo loop so that the first loop
In temperature it is lower.The compression refrigerant freon of high pressure stage compressor 18, and condensation offer heat is carried out by warm condenser 19
Source, the temperature of high-temperature evaporator is 100 DEG C, and the condensation end temperature of the second condenser/evaporator 16 is 40 DEG C, and evaporation ends temperature is 33
DEG C, heat in second servo loop is transmitted into tertiary circuit so that the temperature in tertiary circuit is higher.
Fig. 2 is the thermodynamic cycle pressure-enthalpy chart of superposition type dual temperature drying system in embodiments of the invention.
As shown in Fig. 2 A-B-C-D-E-F circulates for the first circuit refrigeration, G-H-I-J-K-L is that second servo loop refrigeration is followed
Ring, M-N-O-P-Q-R is tertiary circuit kind of refrigeration cycle.
Condensation segment C-E in second servo loop kind of refrigeration cycle with evaporating during first condenser/evaporator 12 circulates the first circuit refrigeration
L-H sections of connections of section.First condenser/evaporator 12 is shell and tube exchanger, and the condensation temperature of the shell and tube exchanger is 5 DEG C, evaporation
Temperature is -2 DEG C, and condensation segment C-E heat is transmitted to evaporator section L-H so that the temperature of the first circuit cycle refrigeration is lower.
Second condenser/evaporator 16 will evaporate in condensation segment I-K in second servo loop kind of refrigeration cycle and tertiary circuit kind of refrigeration cycle
R-M sections of connections of section.Second condenser/evaporator 16 is shell and tube exchanger, and the condensation temperature of the shell and tube exchanger is 40 DEG C, is steamed
It is 33 DEG C to send out temperature.Condensation segment I-K heat is transmitted to evaporator section R-M so that the temperature of tertiary circuit circulation is higher.
In the present embodiment, the first condenser/evaporator 12 and the second condenser/evaporator 16 are shell and tube exchanger, right
It is general by the high heat exchange of pressure for the sake of security because the pressure-bearing in pipe is outer than pipe high in the use of shell and tube exchanger
Fluid is walked in pipe.It is independent that superposition type dual temperature drying system 100, which is used between three compression circuits and three compression circuits,
Operation, connected between the first loop and second servo loop by the first condenser/evaporator 12, so low-pressure stage compressor 11 is with
The refrigerant that compressor 15 of arbitrarily downgrading is used is different, so the pressure of two kinds of refrigerants is also different, in the present embodiment, takes
Refrigerant pressure is higher to be walked in pipe, refrigerant pressure it is less walk pipe outside.Similarly, the second condenser/evaporator 16 is with the first condensation
The operation principle of evaporator 12 is also identical, medium pressure grade compressor 15 and high pressure in second servo loop and tertiary circuit
The pressure of refrigerant in level compressor 18 is different and selects that pressure is higher to be walked in pipe, and pressure is relatively low to be walked outside pipe.
The effect of embodiment and effect
Superposition type dual temperature drying system in the present embodiment, because taking full advantage of superposition type system is producing low temperature
During produced by high temperature heat source, the operating cost of equipment is reduced, while heat energy quality can also be improved to be used to dry
Dry, thaw and heat pump heating, so that the energy is fully utilized, and reduces energy waste.In addition.The present invention's
Superposition type dual temperature drying system, compared with single stage compress is circulated, is capable of the pressure ratio of rational compressors at different levels of control system,
So that whole superposition type dual temperature drying system is run under reasonable normal operating mode, optimal Energy Efficiency Ratio is obtained.
In addition, the superposition type dual temperature drying system in the present embodiment, will be originally during using each system isolated operation
The Btu utilization for being discharged to air gets up there is provided the heat source temperature of whole system, reaches the efficient utilization of the energy, can also realize one
The multi-purpose effect of machine, in the case of -55 DEG C of unit cold is produced, can obtain 2.2 times of 100 DEG C of heat of high temperature, simultaneously
Meet frozen drying and high temperature drying drying.
In addition, in the present embodiment, the refrigerant that low-pressure stage compressor is used is ethane, the system that medium pressure grade compressor is used
Cryogen is HFA 134a, and the refrigerant that high pressure stage compressor is used is freon, in actual applications, can basis
Actual conditions are using other refrigerants.
Above-mentioned embodiment is the preferred case of the present invention, is not intended to limit protection scope of the present invention.
Claims (8)
1. a kind of superposition type dual temperature drying system, it is characterised in that including：
Low-pressure stage compressor, cryogenic vaporizer, the first condenser/evaporator, medium pressure grade compressor, the second condenser/evaporator, hiigh pressure stage
Compressor and warm condenser,
Wherein, the low-pressure stage compressor is connected with the cryogenic vaporizer, and by first condenser/evaporator with it is described
Medium pressure grade compressor is connected,
Medium pressure level compressor is connected by second condenser/evaporator with the high pressure stage compressor,
The high pressure stage compressor is connected with the warm condenser.
2. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, the temperature of the cryogenic vaporizer is -60~-50 DEG C.
3. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, the temperature of the warm condenser is 100~110 DEG C.
4. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, the refrigerant that the low-pressure stage compressor is used is ethane (R170).
5. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, the refrigerant that medium pressure level compressor is used is HFA 134a (R134A).
6. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, the refrigerant that the high pressure stage compressor is used is freon (R123).
7. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, first condenser/evaporator is shell and tube exchanger, and the shell and tube exchanger has condensation end and evaporation ends,
The condensation end is connected with the low-pressure stage compressor,
The evaporation ends are connected with medium pressure level compressor.
8. superposition type dual temperature drying system according to claim 1, it is characterised in that：
Wherein, second condenser/evaporator is shell and tube exchanger, and the shell and tube exchanger has condensation end and evaporation ends,
The condensation end is connected with medium pressure level compressor,
The evaporation ends are connected with the high pressure stage compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710315541.7A CN107120916A (en) | 2017-05-08 | 2017-05-08 | Superposition type dual temperature drying system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710315541.7A CN107120916A (en) | 2017-05-08 | 2017-05-08 | Superposition type dual temperature drying system |
Publications (1)
| Publication Number | Publication Date |
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| CN107120916A true CN107120916A (en) | 2017-09-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710315541.7A Pending CN107120916A (en) | 2017-05-08 | 2017-05-08 | Superposition type dual temperature drying system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109506383A (en) * | 2018-12-25 | 2019-03-22 | 天津商业大学 | The direct condensation by contact cooling cycle system of three-level overlapping |
| CN109682102A (en) * | 2019-01-28 | 2019-04-26 | 天津商业大学 | Direct condensation by contact cryogenic refrigerating system with injection injection |
| CN112033038A (en) * | 2020-08-31 | 2020-12-04 | 青岛海尔空调电子有限公司 | Air source heat pump drying system |
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| CN101825364A (en) * | 2010-05-13 | 2010-09-08 | 中原工学院 | Cascade high-temperature heat pump with gaseous intermediate-temperature heat source and double low-temperature heat sources |
| CN101865589A (en) * | 2010-07-14 | 2010-10-20 | 天津商业大学 | Environment-friendly and freon-free ultralow cold storage |
| CN204141879U (en) * | 2014-10-16 | 2015-02-04 | 珠海格力电器股份有限公司 | Heat pump system |
| CN205641652U (en) * | 2016-04-06 | 2016-10-12 | 广东美的制冷设备有限公司 | Cooling systems |
| CN205784049U (en) * | 2016-05-20 | 2016-12-07 | 南京天源冷冻设备有限公司 | A kind of Liquid refrigerant by-pass cold recovery refrigeration system for two-stage cascade refrigeration |
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2017
- 2017-05-08 CN CN201710315541.7A patent/CN107120916A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101825364A (en) * | 2010-05-13 | 2010-09-08 | 中原工学院 | Cascade high-temperature heat pump with gaseous intermediate-temperature heat source and double low-temperature heat sources |
| CN101865589A (en) * | 2010-07-14 | 2010-10-20 | 天津商业大学 | Environment-friendly and freon-free ultralow cold storage |
| CN204141879U (en) * | 2014-10-16 | 2015-02-04 | 珠海格力电器股份有限公司 | Heat pump system |
| CN205641652U (en) * | 2016-04-06 | 2016-10-12 | 广东美的制冷设备有限公司 | Cooling systems |
| CN205784049U (en) * | 2016-05-20 | 2016-12-07 | 南京天源冷冻设备有限公司 | A kind of Liquid refrigerant by-pass cold recovery refrigeration system for two-stage cascade refrigeration |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109506383A (en) * | 2018-12-25 | 2019-03-22 | 天津商业大学 | The direct condensation by contact cooling cycle system of three-level overlapping |
| CN109682102A (en) * | 2019-01-28 | 2019-04-26 | 天津商业大学 | Direct condensation by contact cryogenic refrigerating system with injection injection |
| CN112033038A (en) * | 2020-08-31 | 2020-12-04 | 青岛海尔空调电子有限公司 | Air source heat pump drying system |
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