CN206648347U - A kind of two-stage superposition type absorption/compression composite refrigeration cycle system - Google Patents
A kind of two-stage superposition type absorption/compression composite refrigeration cycle system Download PDFInfo
- Publication number
- CN206648347U CN206648347U CN201720300361.7U CN201720300361U CN206648347U CN 206648347 U CN206648347 U CN 206648347U CN 201720300361 U CN201720300361 U CN 201720300361U CN 206648347 U CN206648347 U CN 206648347U
- Authority
- CN
- China
- Prior art keywords
- temperature level
- low
- temperature
- compressor
- refrigeration cycle
- 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.)
- Expired - Fee Related
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
Landscapes
- Sorption Type Refrigeration Machines (AREA)
Abstract
The utility model belongs to ship machinery refrigerating field, there is provided a kind of two-stage superposition type absorption/compression composite refrigeration cycle system.The circulation includes：1) high-temperature level absorption/compression combined kind of refrigeration cycle；2) low-temperature level absorption/compression combined kind of refrigeration cycle；3) engine waste heat removes defrosting system.This circulation can be realized in the case of the used heat abundance that fishing boat engines are discharged and provide fish freezing room and refrigerating chamber institute chilling requirement with the waste heat driven two-stage superposition type absorption refrigeration cycle；In the case of the used heat is insufficient, corresponding high and low temperature level compressor is driven by fishing boat engines to be compressed formula refrigeration, so as to supplement fish freezing/jelly room residue institute chilling requirement.And it can come to carry out hot defrosting to refrigeration/jelly room by using partial engine used heat, can both save the consumption of other energy, and can enough ensures that the refrigeration of the refrigeration system is excellent.
Description
Technical field
The utility model is related to it is a kind of can realize energy-saving and emission-reduction with fishing boat engines used heat and power link driving
Two-stage overlapping absorbs/compressed hybrid refrigeration cycle system, belongs to ship machinery refrigerating field.
Background technology
Long range fishing fishing boat due to riding the sea, it is necessary to carry out low temperature cold storage to the seafood of capture for a long time.It is big-and-middle-sized
Dredger be usually mounted with refrigerating plant.The compression-type refrigeration device typically used at present needs to export by fishing boat engines
Shaft work ensure normal operation.And as the reduction of cryogenic temperature, the coefficient of performance of refrigerating plant are gradually reduced, this just anticipates
Taste, which, to be needed more fuel next while ensures the normal/cruise of fishing boat and the normal work of refrigerating plant.This not only adds fishing
The operating cost of ship, and limit fishing boat and go to sea the time, while fishing boat engines can also discharge more pollutants, to environment
Cause bigger influence.On the other hand, as the improvement of people's living standards, increasing people starts to pay attention to the new of marine product
Fresh degree.In general, cryogenic temperature is lower, and the freezing speed of marine product is faster, so that the ice that its intracellular freezing is formed
Brilliant smaller, the denaturation of protein is also smaller, so as to ensure the freshness of marine product to a greater extent.But conventional suction formula refrigeration machine
Evaporating temperature it is not low be absorption refrigeration a prominent defect.More than 0 DEG C of temperature can only be made in lithium bromide-water absorption refrigeration
Degree.And although ammonia-water absorption refrigeration can be run below 0 DEG C, it is extremely difficult that -30 DEG C of temperature below, which are made,.Though
Right auto-cascade absorption type kind of refrigeration cycle can obtain much lower evaporating temperature of freezing than conventional suction formula, but cycle performance coefficient compared with
It is low.
Utility model content
The purpose of this utility model is above mentioned problem be present for prior art, proposes one kind with engine waste heat and power
Combine two-stage superposition type absorption/compression composite refrigeration cycle system of driving, marine product in fishing boat is freezed and refrigerated.
To achieve the above object, the technical solution of the utility model is：
A kind of two-stage superposition type absorption/compression composite refrigeration cycle system bag driven with engine waste heat and power link
Include high-temperature level absorption/compression composite refrigeration cycle system, low-temperature level absorption/compression composite refrigeration cycle system and engine waste heat
Except defrosting system.
Described high-temperature level absorption/compression composite refrigeration cycle system includes high-temperature level generator 1, check-valves 2 and 12, height
Warm level condenser 3, high-temperature level electric expansion valve 4, flow control valve 5 and 7, high-temperature level evaporator 6, low pressure oil eliminator 8, high temperature
Level compressor 10, high pressure oil separator 11, high-temperature level bubble absorption device 13, high-temperature level solution circulation pump 14, high-temperature level solution heat
Exchanger 15, evaporative condenser 19.Described low-temperature level absorption/compression composite refrigeration cycle system includes low-temperature level generator
16th, check-valves 17 and 27, low-temperature level condenser 18, evaporative condenser 19, low-temperature level electric expansion valve 20, low-temperature level evaporator
21st, low pressure oil eliminator 24, compressor 25, high pressure oil separator 26, low-temperature level bubble absorption device 28, low-temperature level solution circulation pump
29th, low-temperature level solution heat exchanger 31.Described engine waste heat includes engine 9, stop valve 30, Flow-rate adjustment except defrosting system
Valve 22 and 23.
Due to when fishing boat across the sea when, influenceed by wind and wave, hull can produce lasting jolt.In such case
Under, falling-film absorber is poor to the assimilation effect of refrigerant in pipe, and bubble absorption device can not be jolted by hull influence keep compared with
Good assimilation effect.Therefore, the refrigerant of the mixed refrigeration systems is absorbed in the utility model using bubble absorption device.
The running situation of two-stage superposition type absorption/compression composite refrigeration cycle system provided by the utility model is：
When engine 9 can produce the refrigeration requirement that enough used heat meets refrigeration/jelly room, engine 9 does not drive high and low temperature pressure
Contracting machine 10 and 25 operates.Now compound-refrigerating circulation is the twin-stage superposition type absorption refrigeration cycle driven with engine waste heat,
And high-temperature level absorb/cold caused by compression combined kind of refrigeration cycle can be entered by flow control valve 5 and 7 come reasonable distribution it is cold
Hide the amount of room and evaporative condenser 19.When the engine waste heat that any one-level is inputted in high and low temperature level kind of refrigeration cycle is not enough to
When meeting corresponding refrigeration requirement, engine 9 starts to drive the compressor of this grade absorb/compression combined kind of refrigeration cycle, so as to
To meet fishing boat institute chilling requirement.When refrigeration or refrigerating chamber need defrosting when, except defrosting system can using partial engine used heat come
Hot defrosting is carried out, so as to ensure that the refrigeration of the hybrid refrigeration cycle is good.
Compared with prior art, had the beneficial effect that possessed by the utility model：1) hybrid refrigeration cycle can use
Environmental protection and the refrigerant and absorbent of function admirable；2) two-stage overlapping Absorption Cooling System is used, the height that engine is discharged
Warm used heat successively passes through low and high temperature level generator 16 and 1.It so not only can more fully utilize the heat of engine waste heat
(marine engine delivery temperature belongs to medium temperature level thermal source typically at 250-500 DEG C), so as to save fishing boat fuel and reduce harmful
The discharge of flue gas, and compared to auto-cascade absorption type refrigeration for, the COP values of the system greatly improve (such as：In document with
R32+R134a/DMF be working medium pair auto-cascade absorption type kind of refrigeration cycle occur temperature be 157 DEG C, evaporating temperature is -34.5
DEG C when, system COP values be only 0.018)；3) when the used heat of engine discharge is not enough to drive the absorption in the hybrid refrigeration cycle
During formula kind of refrigeration cycle, it can be freezed by high and low temperature compressor to be compressed formula, it is cold needed for refrigeration/jelly room residue to supplement
Amount.4) come to carry out hot defrosting to refrigeration/jelly room by using partial engine used heat, can both save the consumption of other energy,
And can enough ensures that the refrigeration of the kind of refrigeration cycle is excellent.
Brief description of the drawings
Fig. 1 is a kind of with engine waste heat and two-stage superposition type absorption/compression combined kind of refrigeration cycle of power link driving
Systematic schematic diagram.
In figure：- solution line --- used heat pipeline-refrigerant line -- refrigeration/jelly room border
1 high-temperature level generator；2nd, 12,17,27 check-valves；3 high-temperature level condensers；4 high-temperature level electric expansion valves；5、7、
22nd, 23 flow control valve；6 high-temperature level evaporators；8th, 24 low pressure oil eliminator；9 engines；10 high-temperature level compressors；11st, 26 is high
Press oil separator；13 high-temperature level bubble absorption devices；14th, 29 solution circulation pump；15 high-temperature level solution heat exchangers；16 low-temperature levels are sent out
Raw device；18 low-temperature level condensers；19 evaporative condensers；20 low-temperature level electric expansion valves；21 low-temperature level evaporators；25 low-temperature level pressures
Contracting machine；28 low-temperature level bubble absorption devices；30 stop valves；31 low-temperature level solution heat exchangers.
Embodiment
Embodiment of the present utility model is described further below in conjunction with the accompanying drawings.
As shown in Figure 1 is a kind of with engine waste heat and two-stage superposition type absorption/compression combined system of power link driving
SAPMAC method system, structure are as follows.
Described high-temperature level absorption/compression composite refrigeration cycle system includes high-temperature level generator 1, check-valves 2 and 12, height
Warm level condenser 3, high-temperature level electric expansion valve 4, flow control valve 5 and 7, high-temperature level evaporator 6, low pressure oil eliminator 8, high temperature
Level compressor 10, high pressure oil separator 11, high-temperature level bubble absorption device 13, high-temperature level solution circulation pump 14, high-temperature level solution heat
Exchanger 15, evaporative condenser 19.
Described high-temperature level generator 1 is connected in warm condenser 3, high-temperature level generator 1 with high-temperature level compressor 10
Stop valve 2 is installed, in the branch road that high-temperature level compressor 10 is connected with warm condenser 3 in the branch road being connected with warm condenser 3
Stop valve 12 is installed, and the outlet of high-temperature level compressor 10 is connected with high pressure oil separator 11, for separating refrigerant and compressor
Machine oil；Described stop valve 2 and 12 is used for preventing refrigerant adverse current, and high-temperature level compressor 10 is driven by engine 9, and the two passes through
Shaft coupling connects.After the described export pipeline of warm condenser 3 is connected with high-temperature level electric expansion valve 4, it is divided into two branch roads, two
A flow control valve 5,7 is respectively mounted on individual branch road, the place branch road of flow control valve 5 is connected with high-temperature level evaporator 6, and flow is adjusted
The section place branch road of valve 7 evaporates end entrance with evaporative condenser 19 and is connected；Two branch roads are in the evaporation ends exit of evaporative condenser 19
After pooling all the way, it is connected with the entrance of low pressure oil eliminator 8；The pipeline of outflow low pressure oil eliminator 8 is divided into two branch roads, one
Branch road is connected with high-temperature level compressor 10, and another branch road is connected with the entrance of high-temperature level bubble absorption device 13；Described high-temperature level drum
The outlet of bubble absorber 13 is connected with the entrance of solution circulation pump 14, and the outlet of solution circulation pump 14 is low with high-temperature level solution heat exchanger 15
Warm end entrance connection, the outlet of the low-temperature end of high-temperature level solution heat exchanger 15 are connected with the entrance of high-temperature level generator 1；At the same time,
The described taphole end of high-temperature level generator 1 is connected with the high temperature end entrance of high-temperature level solution heat exchanger 15, and its high temperature is brought out
Mouth is connected with the solution inlet of high-temperature level bubble absorption device 13.Described high-temperature level evaporator 6 is located in refrigerating chamber.
Described low-temperature level absorption/compression composite refrigeration cycle system include low-temperature level generator 16, check-valves 17 and 27,
Low-temperature level condenser 18, evaporative condenser 19, low-temperature level electric expansion valve 20, low-temperature level evaporator 21, low pressure oil eliminator 24,
Compressor 25, high pressure oil separator 26, low-temperature level bubble absorption device 28, low-temperature level solution circulation pump 29, low-temperature level solution heat are handed over
Parallel operation 31.
The low-temperature level generator 16 is connected in low-temperature condenser 18, low-temperature level generator 16 with low-temperature level compressor 25
Stop valve 17, the branch road that low-temperature level compressor 25 is connected with low-temperature condenser 18 are installed in the branch road being connected with low-temperature condenser 18
It is middle installation stop valve 27, low-temperature level compressor 25 outlet where pipeline connection high pressure oil separator 26, for separate refrigerant with
Compressor oil；Described stop valve 17,27 is used to prevent refrigerant adverse current, and low-temperature level compressor 25 is driven by engine 9, and two
Person is connected by shaft coupling, and the engine being connected with high-temperature level compressor 10 and low-temperature level compressor 25 belongs to same engine system
System.After the described export pipeline of low-temperature condenser 18 connects with evaporative condenser 19, it is connected with low-temperature level electric expansion valve 20, it is low
Warm level electric expansion valve 20 is connected with low-temperature level evaporator 21；The described refrigerant outlet of low-temperature level evaporator 21 and low pressure oil
Connected from device 24；The pipeline of outflow low pressure oil eliminator 24 is divided into two branch roads；One branch road is connected with low-temperature level compressor 25,
Another branch road is connected with low-temperature level bubble absorption device 28；The described outlet of low-temperature level bubble absorption device 28 enters with solution circulation pump 29
Mouth is connected；The outlet of solution circulation pump 29 is connected with the low temperature end entrance of low-temperature level solution heat exchanger 31, low-temperature level solution heat exchange
The outlet of the low-temperature end of device 31 is connected with the entrance of low-temperature level generator 16；At the same time, the taphole end of low-temperature level generator 16 with it is low
The warm high temperature end entrance of level solution heat exchanger 31 connection, the outlet of its temperature end and the solution inlet phase of low-temperature level bubble absorption device 28
Even.Described low-temperature level evaporator 21 is located in refrigerating chamber.
Described engine waste heat includes engine 9, stop valve 30, flow control valve 22 and 23 except defrosting system.
The exhaust waste heat of engine 9 is divided to two pipelines, and a part of exhaust waste heat passes sequentially through low-temperature level by pipeline all the way
Generator 16, high-temperature level generator 1, driving high-temperature level absorption/compression composite refrigeration cycle system, low-temperature level absorption/compression are multiple
Close cooling cycle system；Another part exhaust waste heat is divided into two by another way pipeline, the pipeline after being connected with stop valve 30
Branch road, there is a flow control valve 22,23 on each branch road, the branch road and low-temperature level evaporator of flow control valve 22 are installed
21 connections, the branch road of installation flow control valve 23 connects with high-temperature level evaporator 6, for being removed to refrigerating chamber and refrigerating chamber
Frost.
Use as described in Figure 1 a kind of multiple with engine waste heat and two-stage superposition type absorption/compression that power link drives
Closing kind of refrigeration cycle has following four running situation：
1) when the used heat that engine is discharged is enough to drive high-temperature level absorption/compression composite refrigeration cycle system, low-temperature level
Absorption/compression composite refrigeration cycle system, when producing refrigerating chamber, refrigerating chamber jelly room institute's chilling requirement, high and low temperature compressor 10,25
In stopped status.Now, high-temperature flue gas caused by engine occurs successively by cryogenerator 16 and high-temperature generator 1
In device concentrated solution (such as：Low-temperature level Absorption Cooling System uses R23+NMP working medium pair, and refrigerant R23 is in absorbent NMP
Middle dissolving it is more, then solution concentration is bigger；High-temperature level Absorption Cooling System uses R134a+NMP working medium pair, refrigerant
R134a dissolves more in absorbent NMP, then solution concentration is bigger) be heated after isolate refrigerant R23 and R134a.System
Cryogen R134a and R23 respectively enter high and low temperature condenser 3 and 18.The cooled seawater of refrigerant R134a is cold in warm condenser 3
Congeal into liquid；The cooled seawater coolings of the refrigerant R23 of low-temperature condenser 18, but still be gaseous refrigerant.
After liquid refrigerant R134a is throttled by high-temperature level electric expansion valve 4, two-way is divided to flow：High-temperature level is reached all the way
Evaporator 6 absorbs heat in refrigerating chamber；Another way reaches the evaporation ends of evaporative condenser 19 to flowing into the condensation end of evaporative condenser 19
Gaseous refrigerant R23 cooled down, refrigerant R23 is changed into liquid, and flowed out from the condensation end of evaporative condenser 19；Above-mentioned two
The mass flow of road refrigerant determines according to refrigerating chamber and cooling gaseous refrigerant institute chilling requirement, and passes through flow control valve 5,7
It is adjusted.
The refrigerant convergence of two-way outflow high-temperature level evaporator 6 and the evaporation ends of evaporative condenser 19 is to flow into high temperature afterwards all the way
Level bubble absorption device 13, is absorbed by weak solution therein.Lead to from the liquid refrigerant R23 of the condensation end of evaporative condenser 19 outflow
Cross after low-temperature level electric expansion valve 20 throttles and enter low-temperature level evaporator 21, absorption refrigerating heat, flow out low-temperature level evaporator
21 refrigerant R23 flows into low-temperature level bubble absorption device 28, is absorbed by weak solution therein.In high and low temperature level bubble absorption device
The solution concentration increase of refrigerant was absorbed, high and low temperature level solution heat exchanger 15 is pumped into by solution circulation pump 14 and 29 respectively
In 31, the weak solution with being flowed out out of high and low temperature level generator is exchanged heat in solution heat exchanger respectively；Afterwards, quilt
The concentrated solution of heating respectively enters again to be occurred in high and low temperature level generator 1 and 16；At the same time, cooled weak solution
Respectively enter in high and low temperature level bubble absorption device 13 and 28 to absorb corresponding refrigerant.When freezing/Tibetan room needs defrosting,
Stop valve 30 is opened, and adjusts the aperture of flow control valve 22 and 23, high-temperature flue gas caused by engine respectively enter freezing/
Room is hidden to be defrosted.
2) when the used heat that engine is discharged can only drive low-temperature level Absorption Cooling System to produce needed for refrigerating chamber
During cold, low-temperature level compressor 25 is in stopped status, and high temperature compressor 10 drives start-up operation by engine 9.The situation
Under, refrigeration system with 1) described in running situation difference be by high-temperature level evaporator 6 and the evaporation ends of evaporative condenser 19
After two strands of refrigerant R134as convergence out, it is partly into high-temperature level bubble absorption device 13 and is absorbed by weak solution；Another portion
Divide and enter high-temperature level compressor 10.After refrigerant R134a after being compressed by high-temperature level compressor 10 is by high pressure oil separator 11
Condensed after being converged with the refrigerant R134a gone out in high-temperature level generator 1 into high-temperature level condenser 3.Remaining with 1) in feelings
The method of operation is consistent under condition.
3) when the used heat that engine is discharged can only drive high-temperature level Absorption Cooling System to produce refrigerating chamber and steaming
Feel cold 19 chilling requirements of condenser when, high-temperature level compressor 10 is in stopped status, and cryogenic compressor 25 is driven by engine 9 and opened
Beginning work.In this case, refrigeration system with 1) described in running situation difference be by low-temperature level evaporator 21 come out
Refrigerant R23 is partly into low-temperature level bubble absorption device 28 to be absorbed by weak solution；Another part enters low-temperature level compressor
25.Refrigerant R134a after being compressed by low-temperature level compressor 25 by after high pressure oil separator 26 with low-temperature level generator 16
Condensed after the refrigerant R134a convergence gone out into low-temperature level condenser 18.Remaining with 1) in the case of the method for operation one
Cause.
4) when the used heat that engine is discharged both be not enough to drive high-temperature level Absorption Cooling System come produce refrigerating chamber and
19 chilling requirements of evaporative condenser, when being not enough to drive low-temperature level Absorption Cooling System to produce refrigerating chamber institute chilling requirement again,
High and low temperature compressor 10/25 drives by engine 9 and started working.In such cases, from 1) described in running situation it is different it
Be in：After the two strands of refrigerant R134as convergence come out by high-temperature level evaporator 6 and the evaporation ends of evaporative condenser 19, a part
Absorbed into high-temperature level bubble absorption device 13 by weak solution；Another part enters high-temperature level compressor 10；Meanwhile by low-temperature level
The refrigerant R23 that evaporator 21 comes out is partly into low-temperature level bubble absorption device 28 to be absorbed by weak solution；Another part enters
Enter low-temperature level compressor 25.Refrigerant R134a and R23 enter high pressure oil separator after being compressed respectively in high and low temperature compressor
11 and 26, the R134a and R23 for then occurring out with high and low temperature level generator enter in high and low temperature condenser after converging respectively
Condensation.Remaining with 1) described in running situation it is consistent.
Finally, using ammonia-water as working medium pair is absorbed in the case of, after rectifier (tower) is set, remained to using the utility model
Realize last purpose.
Claims (1)
1. a kind of two-stage superposition type absorption/compression composite refrigeration cycle system, it is characterised in that described two-stage superposition type is inhaled
Receipts/compression composite refrigeration cycle system is multiple including high-temperature level absorption/compression composite refrigeration cycle system, low-temperature level absorption/compression
Close cooling cycle system and engine waste heat removes defrosting system；
Described high-temperature level absorption/compression composite refrigeration cycle system includes high-temperature level generator (1), check-valves (2,12), height
Warm level condenser (3), high-temperature level electric expansion valve (4), flow control valve (5,7), high-temperature level evaporator (6), low pressure oil separation
Device (8), high-temperature level compressor (10), high pressure oil separator (11), high-temperature level bubble absorption device (13), high-temperature level solution circulation pump
(14), high-temperature level solution heat exchanger (15), evaporative condenser (19)；
Described high-temperature level generator (1) is connected in warm condenser (3) with high-temperature level compressor (10), divides in two branch roads
It An Zhuan not be used for preventing the stop valve (2,12) of refrigerant adverse current, and high-temperature level compressor (10) outlet and high pressure oil separator
(11) it is connected, for separating refrigerant and compressor oil, high-temperature level compressor (10) is driven by engine (9)；Described height
After warm condenser (3) export pipeline is connected with high-temperature level electric expansion valve (4), it is divided into two branch roads, is respectively mounted on two branch roads
One flow control valve (5,7), branch road where flow control valve (5) are connected with high-temperature level evaporator (6), flow control valve (7)
Place branch road is connected with evaporative condenser (19) evaporation end entrance；Two branch roads converge in evaporative condenser (19) evaporation ends exit
After being polymerized to all the way, it is connected with low pressure oil eliminator (8) entrance；The pipeline of outflow low pressure oil eliminator (8) is divided into two branch roads, and one
Individual branch road is connected with high-temperature level compressor (10), and another branch road is connected with high-temperature level bubble absorption device (13) entrance；Described height
Warm level bubble absorption device (13) outlet is connected with solution circulation pump (14) entrance, solution circulation pump (14) outlet and high-temperature level solution
Heat exchanger (15) low temperature end entrance connects, the outlet of high-temperature level solution heat exchanger (15) low-temperature end and high-temperature level generator (1)
Entrance connects；Described high-temperature level generator (1) taphole end connects with high-temperature level solution heat exchanger (15) high temperature end entrance
Connect, the outlet of its temperature end is connected with high-temperature level bubble absorption device (13) solution inlet；Described high-temperature level evaporator (6) is positioned at cold
Hide in room；
Described low-temperature level absorption/compression composite refrigeration cycle system include low-temperature level generator (16), check-valves (17,27),
Low-temperature level condenser (18), evaporative condenser (19), low-temperature level electric expansion valve (20), low-temperature level evaporator (21), low pressure oil
Separator (24), compressor (25), high pressure oil separator (26), low-temperature level bubble absorption device (28), low-temperature level solution circulation pump
(29), low-temperature level solution heat exchanger (31)；
The low-temperature level generator (16) is connected in low-temperature condenser (18) with low-temperature level compressor (25), and two branch roads are pacified respectively
The stop valve (17,27) for preventing refrigerant adverse current is filled, pipeline connection high pressure oil where low-temperature level compressor (25) outlet
From device (26), for separating refrigerant and compressor oil；Low-temperature level compressor (25) is driven by engine (9), with high-temperature level
The engine that compressor (10) is connected with low-temperature level compressor (25) belongs to same engine system；Described low-temperature condenser
(18) after export pipeline connects with evaporative condenser (19), it is connected with low-temperature level electric expansion valve (20), low-temperature level electronic expansion
Valve (20) is connected with low-temperature level evaporator (21)；Described low-temperature level evaporator (21) refrigerant outlet and low pressure oil eliminator
(24) connect；The pipeline of outflow low pressure oil eliminator (24) is divided into two branch roads；One branch road and low-temperature level compressor (25) phase
Even, another branch road is connected with low-temperature level bubble absorption device (28)；Described low-temperature level bubble absorption device (28) outlet follows with solution
Ring pump (29) entrance is connected；Solution circulation pump (29) outlet is connected with low-temperature level solution heat exchanger (31) low temperature end entrance, low
Warm level solution heat exchanger (31) low-temperature end outlet is connected with low-temperature level generator (16) entrance；Low-temperature level generator (16) solution
The port of export is connected with low-temperature level solution heat exchanger (31) high temperature end entrance, the outlet of its temperature end and low-temperature level bubble absorption device
(28) solution inlet is connected；Described low-temperature level evaporator (21) is located in refrigerating chamber；
Described engine waste heat includes engine (9), stop valve (30), flow control valve (22,23) except defrosting system；
The exhaust waste heat of engine (9) is divided to two pipelines, and a part of exhaust waste heat passes sequentially through low-temperature level by pipeline all the way and sent out
Raw device (16), high-temperature level generator (1), driving high-temperature level absorption/compression composite refrigeration cycle system, low-temperature level absorption/compression
The compound-refrigerating circulatory system；Another part exhaust waste heat is divided into by another way pipeline, the pipeline after being connected with stop valve (30)
Two branch roads, a flow control valve is respectively mounted on each branch road, and branch road and the low-temperature level of installation flow control valve (22) are steamed
Device (21) connection is sent out, the branch road of installation flow control valve (23) connects with high-temperature level evaporator (6), refrigerating chamber and refrigerating chamber are entered
Row defrosting.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720300361.7U CN206648347U (en) | 2017-03-27 | 2017-03-27 | A kind of two-stage superposition type absorption/compression composite refrigeration cycle system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720300361.7U CN206648347U (en) | 2017-03-27 | 2017-03-27 | A kind of two-stage superposition type absorption/compression composite refrigeration cycle system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206648347U true CN206648347U (en) | 2017-11-17 |
Family
ID=60280179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201720300361.7U Expired - Fee Related CN206648347U (en) | 2017-03-27 | 2017-03-27 | A kind of two-stage superposition type absorption/compression composite refrigeration cycle system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206648347U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108674126A (en) * | 2018-05-04 | 2018-10-19 | 山东科技大学 | A kind of half effect absorption system using automobile engine residual heat driving |
| CN108709333A (en) * | 2018-07-20 | 2018-10-26 | 天津商业大学 | The operation method and system of refrigeration system completely cooling among second throttle |
| CN108759138A (en) * | 2018-07-20 | 2018-11-06 | 天津商业大学 | The operation method and system of not exclusively cooling refrigeration system among second throttle |
| CN108974315A (en) * | 2018-08-01 | 2018-12-11 | 广州中臣碧阳船舶科技有限公司 | A kind of seawater defrosting system peculiar to vessel |
| CN113587471A (en) * | 2021-06-21 | 2021-11-02 | 东南大学 | Cold and hot confession system that allies oneself with of doublestage compression and absorption formula high temperature heat pump complex |
-
2017
- 2017-03-27 CN CN201720300361.7U patent/CN206648347U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108674126A (en) * | 2018-05-04 | 2018-10-19 | 山东科技大学 | A kind of half effect absorption system using automobile engine residual heat driving |
| CN108674126B (en) * | 2018-05-04 | 2020-03-06 | 山东科技大学 | Semi-effective absorption type refrigerating system driven by waste heat of automobile engine |
| CN108709333A (en) * | 2018-07-20 | 2018-10-26 | 天津商业大学 | The operation method and system of refrigeration system completely cooling among second throttle |
| CN108759138A (en) * | 2018-07-20 | 2018-11-06 | 天津商业大学 | The operation method and system of not exclusively cooling refrigeration system among second throttle |
| CN108709333B (en) * | 2018-07-20 | 2023-04-25 | 天津商业大学 | Operation method and system of secondary throttling middle complete cooling refrigerating system |
| CN108759138B (en) * | 2018-07-20 | 2023-04-28 | 天津商业大学 | Operation method and system of secondary throttling middle incomplete cooling refrigerating system |
| CN108974315A (en) * | 2018-08-01 | 2018-12-11 | 广州中臣碧阳船舶科技有限公司 | A kind of seawater defrosting system peculiar to vessel |
| CN113587471A (en) * | 2021-06-21 | 2021-11-02 | 东南大学 | Cold and hot confession system that allies oneself with of doublestage compression and absorption formula high temperature heat pump complex |
| CN113587471B (en) * | 2021-06-21 | 2022-06-28 | 东南大学 | Double-stage compression and absorption type high-temperature heat pump combined cold and heat combined supply system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN206648347U (en) | A kind of two-stage superposition type absorption/compression composite refrigeration cycle system | |
| EP3299747B1 (en) | Switchable two-stage cascade energy-saving ultralow-temperature refrigeration system for ships | |
| CN108662808A (en) | A kind of two-stage superposition type absorption/compression composite refrigeration cycle system with engine waste heat and power link driving | |
| CN105299987B (en) | Air source heat pump spray defroster based on super-hydrophobic finned tube exchanger | |
| CN204373252U (en) | Change type CO2 trans critical cycle refrigeration system | |
| CN109203912B (en) | Air conditioning system, control method thereof and pure electric cold-chain logistics vehicle | |
| CN208458298U (en) | A kind of heat siphon type defrosting binary channels petroleum vapor recovery condensation unit | |
| CN102032705A (en) | Two-stage compression heat pump system | |
| CN105627622A (en) | Jetting type auto-cascade refrigeration system for waste heat recovery of tuna clipper | |
| CN106368775A (en) | Power turbine compression refrigerating device for recovering exhaust waste heat of diesel main engine for fishing boat | |
| CN107120831A (en) | A kind of continuous heating air friction drag | |
| CN201926222U (en) | Air conditioner and low-pressure oil storage and refrigerant circulation accelerating device thereof | |
| CN208832629U (en) | A kind of low-temperature cold water unit | |
| CN106705494A (en) | Air source heat pump energy conservation system with function of preventing air side heat exchanger from freezing | |
| CN206160542U (en) | Overlapping formula refrigerating units | |
| CN107024048A (en) | Variable disengagement area fluidised form ice-making system | |
| CN206113384U (en) | Refrigeration or heat pump system | |
| CN215571358U (en) | Compound refrigerating system with natural cooling function | |
| CN206637882U (en) | Switchable type double evaporators CO2 trans critical cycle refrigeration systems | |
| CN215113319U (en) | Air supplement unit under partial load of single-screw refrigeration compressor coupled with composite slide valve | |
| CN110145914A (en) | A kind of domestic refrigerator introducing natural cooling source | |
| CN205980563U (en) | Plasma quick -frozen machine refrigerating system | |
| CN205980423U (en) | A heat exchanger and heat pump system for heat pump system | |
| CN105972933A (en) | Refrigerating system of blood plasma rapid freezer | |
| CN210832351U (en) | Multifunctional combined type air conditioner heat pump system for refrigeration and heat supply |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20171117 Termination date: 20200327 |