CN204648752U - The heat pump of a kind of drying medium step heating and exhaust heat stepped recovery - Google Patents
The heat pump of a kind of drying medium step heating and exhaust heat stepped recovery Download PDFInfo
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- CN204648752U CN204648752U CN201420833495.1U CN201420833495U CN204648752U CN 204648752 U CN204648752 U CN 204648752U CN 201420833495 U CN201420833495 U CN 201420833495U CN 204648752 U CN204648752 U CN 204648752U
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Abstract
The utility model provides the heat pump of the heating of a kind of drying medium step and exhaust heat stepped recovery, comprise drying room and be attached thereto logical drying medium flow channel and flow pass, heat pump at least includes two cover source pump, often overlaps source pump and has included compressor, condenser, choke valve and evaporimeter; Condenser is all arranged in drying medium flow channel, and at least one evaporimeter is arranged in drying medium flow pass; Condenser in each cover source pump starts to drying room order spread configuration from import in drying medium flow channel, and it often overlaps the corresponding and evaporimeter self-desiccation medium flow export being arranged in drying medium flow pass and starts to drying room order spread configuration.The utility model reduces the temperature difference, pressure reduction and compression ratio between the condenser of each cover source pump self and evaporimeter, improves the Energy Efficiency Ratio of each cover source pump, improves the Energy Efficiency Ratio of whole heat pump, improve the operating mode of compressor bank.
Description
Technical field
The utility model relates to xeothermic pump design field, particularly relates to the heat pump of the heating of a kind of drying medium step and exhaust heat stepped recovery.
Background technology
Heat pump is a kind of is power with compressor, by the evaporation of refrigeration working medium at low-temperature heat source and the condensation at high temperature heat source, by the thermal apparatus of the transfer of heat of low-temperature heat source to high temperature heat source.
Be generally used for the low-temperature heat source of the evaporimeter heat absorption of heat pump assembly, being the medium around us, as air, river, lake water, underground water etc., also can be the waste gas waste water and waste liquid that the band produced in industrial processes has surplus heat.
Usually, heat pump is used for the heating to air, water, wet goods medium, these media are exactly the high temperature heat source of heat pump.
But, in existing heat pump, if low-temperature heat source temperature is low, heated medium temperature is high, then the evaporating pressure of heat pump evaporimeter is low, the condensing pressure of condenser is high, cause suction pressure of compressor and pressure at expulsion " pressure reduction " between the two to expand, compression ratio increases, and compressor exhaust temperature raises, working conditions of compressor worsens, refrigerating capacity declines, and heating capacity declines, and systematic energy efficiency ratio declines.Current heat pump, under cryogenic, cannot meet the Production requirement of high temperature drying, air heat and health hot water.
Now with air source hot pump water heater, it is discussed.
In air source heat pump hot water production device, main employing single stage compress system at present, its groundwork process is, cold-producing medium absorbs air heat energy and becomes low-pressure steam in evaporimeter, shortened into the steam of HTHP by compressor suction pressure, the condenser entered in water tank is condensed into refrigerant liquid after heat released by running water in water tank, reduce pressure through throttling arrangement again, again flow into evaporimeter, thus enter new round circulation, so move in circles, constantly using as the heat energy in the air of low-temperature heat source, pump into the health hot water as high temperature heat source.
The single-stage compression heat-pump hot-water process units of operation like this, its heating efficiency (Energy Efficiency Ratio) determines primarily of the condensing pressure of heat pump and evaporating pressure.
Because the evaporating temperature of heat pump must lower than the temperature of surrounding air, the liquid refrigerant in evaporimeter could absorb heat, carburation by evaporation from the air evaporimeter; So the evaporating pressure of heat pump is mainly determined by the temperature of surrounding air, the low then evaporating pressure of environment temperature is low, and the density of the refrigerant gas that compressor sucks is low, and circulating mass of refrigerant is little, and heating capacity is poor; Environment temperature height then evaporating pressure is high, and the density of the refrigerant gas that compressor sucks is large, and circulating mass of refrigerant is large, and heating capacity is strong.The condensation temperature of heat pump hot-water system again must higher than hot water temperature, and the refrigerant gas in condenser could liquefy by exothermic condensation, heat is put the hot water in feed-tank outside condenser; So the condensing pressure of heat-pump hot-water unit is mainly determined by the temperature of hot water in water tank, hot water temperature is low, and then condensing pressure is low, and working conditions of compressor is good, and heat pump Energy Efficiency Ratio is high; Hot water temperature raises then condensing pressure and raises, and working conditions of compressor is deteriorated, and heat pump Energy Efficiency Ratio reduces.
For heat-pump hot-water unit, if environment (low-temperature heat source) temperature high (such as 15 DEG C), hot water (high temperature heat source) temperature low (such as 25 DEG C), evaporating pressure then in heat pump evaporimeter higher (using R22 to reach more than 6atm), condensing pressure in condenser lower (about 12atm), suction pressure of compressor and pressure at expulsion " pressure reduction " are between the two less, compression ratio is little, compressor exhaust temperature is lower, working conditions of compressor is good, refrigerating capacity is extremely strong, heating capacity is extremely strong, Energy Efficiency Ratio (heating the ratio of power and institute's power consumption) reaches more than 10 times.
If but environment temperature is low, hot water temperature is high, then the evaporating pressure of heat pump evaporimeter is low, the condensing pressure of condenser is high, suction pressure of compressor and pressure at expulsion " pressure reduction " is between the two caused to increase, compression ratio increases, compressor exhaust temperature raises, " three high and one low " phenomenon that heating capacity declines, and working conditions of compressor worsens.
Please refer to following table, according to the data that American blend compressor " paddy wheel " manufacturer issues for 2011, different evaporating temperature, condensation temperature and the motor of a ZW108KS three-phase screw compressor suck power P and heat the relation between power (heating capacity) H, wherein, this compressor adopts R22 cold-producing medium.
Different evaporating temperature, condensation temperature and the motor of ZW108KS three-phase screw compressor suck power P and heat the relation between power (heating capacity) H
Can find out from upper table, under evaporating temperature 15 DEG C of condensation temperatures 25 DEG C of conditions, compressor sucks electrical power 4435W, heating capacity 47595W, and its heating efficiency is up to 10.7; But this ZW108KS compressor, under the condition of evaporating temperature-25 DEG C, condensation temperature+65 DEG C, suck electrical power 9825W, heating capacity 15858W, its heating efficiency is down to 1.61; Compare with previous operating mode, compressor sucks electrical power increases by 121%, heating capacity reduces by 66.7%, has occurred the phenomenon of " three high and one low " that condensing pressure rising, compression ratio rising, compressor exhaust temperature rising, heating efficiency reduce, working conditions of compressor severe exacerbation.And, this or laboratory data, in the heating of reality, because repeatedly carry out power consumption etc. the factor of the reversion defrost on evaporimeter, water Pumps & Fans in the on-way resistance of evaporimeter, condenser " two devices ", system operation, the heating efficiency of system is by < 1.5, close to the efficiency of resistor-type electrical appliance direct electro heating, high energy efficiency ratio and the high economy of " heat pump " exhaust.
The inevitable outcome of the heat pump that Here it is carries out the large temperature difference, greatly pressure reduction between condenser and evaporimeter, high compression ratio is run.
Therefore, improve the Energy Efficiency Ratio of heat pump and improve the operating mode of heat pump, fundamental solution is to improve evaporating pressure, reduce condensing pressure, namely requires the temperature improving low-temperature heat source as much as possible, turns down high temperature heat source (heated medium) temperature as much as possible.
The waste gas waste water and waste liquid of waste heat will be loaded with, as the low-temperature heat source of heat pump, although easily cause that evaporator with heat pump is contaminated even to be scrapped, but the low-temperature heat source of potential temperature can improve evaporating temperature, the evaporating pressure of heat pump like this, thus improve load and the efficiency of whole heat pump, thus for heat pump application, still there is very large temptation.
In much industry and civilian closing with thermal field, flow out the air being loaded with waste heat, flue gas, the waste water of the heat power engineering systems such as drying, heating, the ratio that its contained waste heat accounts for total heat is very high, if will the low-temperature heat source of medium (air, water etc.) as heat pump of waste heat be loaded with, then the evaporating pressure of heat pump, evaporating temperature can significantly improve, the density of the refrigerant gas that compressor sucks improves, circulating mass of refrigerant improves, heating capacity strengthens, and therefore waste heat recovery has high technical meaning and economic worth.
Such as grain dry run, huge with heat, day dry 2000 tons of damp grains the grain depot of moderate processing power, in summer harvest season, autumn harvest season, every day, needs removed moisture about 140 tons in (evaporation) damp grain, and institute's calorific requirement is up to 8 × 10
9kcal, calculate according to overall thermal efficiency 60%, standard coal 20 tons amounted to by the fuel such as required coal, natural gas, stalk.Grain dry, need air heat to more than 60 DEG C (if dry object is cereal seed, then be heated to about 45 DEG C), then carry out heat exchange with the dry air more than these 60 DEG C (or 45 DEG C) and damp grain, absorb the moisture of cereal.In Grain Drying Process, drying air temperature decline, relative humidity and absolute moisture content increase, but dry air does " constant enthalpy " change, namely the enthalpy (energy density) of air remains unchanged, and the gross energy of air does not reduce (ignoring dry air in dry run hot to the leakage of environment); Dry air is lowered the temperature the part sensible heat discharged, and be transformed to the latent heat that damp grain moisture flashes to water vapour, the humidity load of air increases fast.Humid air after dried grain is at about 40 DEG C, and the waste heat entrained by it, comprises the sensible heat of air and the latent heat of water vapour, caloric receptivity when being heated with air before drying is substantially equal, quantity is very huge, as the low-temperature heat source of heat pump, has high recovery value.
But current heat pump application still faces efficiency partially than low problem.Drying waits operation, and usually need the drying mediums such as air, the temperature rise had by a relatively large margin obtains stronger wettability power with the relative humidity significantly reducing air, and this just requires that the condenser of the heat pump used at present has higher condensation temperature; But as previously mentioned, higher condensation temperature and condensing pressure, must reduce the Energy Efficiency Ratio of heat pump.And if there is no sufficiently high Energy Efficiency Ratio, the costs such as the installation cost of digestive fever pumping system, the electricity charge must be difficult to, cause heat pump to be difficult to actual operation.
Utility model content
In order to solve the problem, the utility model provides the heat pump of the heating of a kind of drying medium step and exhaust heat stepped recovery, the drying medium flow channel comprising drying room and be connected with drying room and drying medium flow pass, described heat pump at least includes two cover source pump, often overlaps source pump and includes connected compressor, condenser, choke valve and evaporimeter; Described condenser is all arranged in described drying medium flow channel, and at least one evaporimeter is arranged in described drying medium flow pass,
Wherein, condenser in all source pump starts to described drying room order spread configuration from the import of described drying medium flow channel, and it often overlaps the corresponding and evaporimeter being positioned at described drying medium flow pass and starts to described drying room order spread configuration from the outlet of described drying medium flow pass.
Preferably, the described evaporimeter in the described source pump of at least two covers is all positioned at described drying medium flow pass.
Preferably, described heat pump at least includes three cover source pump, wherein the evaporimeter of the described source pump of at least two covers is positioned at described drying medium flow pass, and the evaporimeter of at least a set of described source pump is positioned at drying medium flow pass atmosphere outside.
Preferably, the evaporimeter being positioned at drying medium flow pass atmosphere outside is arranged on the import side of described drying medium flow channel with the condenser that group is corresponding.
Preferably, the far and near order in position between each described condenser to described drying room, the evaporimeter of corresponding with it group is to the position distance sequence consensus of drying room.
Preferably, described evaporimeter, described choke valve and the pipeline in described condenser are connected and form with described compressor the circulation canal that supplies flow of refrigerant warp; Described cold-producing medium flows through the pipeline in described condenser, choke valve and described evaporimeter successively from described compressor starts.
Preferably, described drying medium for carrying heat and transferring heat directly can heat and promote to dry containing moisture evaporation in wet stock containing wet stock, or promote to evaporate containing moisture in wet stock the medium dried by the wet stock that contains in dividing wall type heat exchanger indirect heat exchanger, comprise air, nitrogen, carbon dioxide, water vapour, conduction oil, water.
Preferably, the import of described drying medium flow channel, the outlet of described drying medium flow pass, is provided with fluid delivery system, and described fluid delivery system adopts blower fan or oil pump or water pump.
The heat pump of the heating of a kind of drying medium of the utility model step and exhaust heat stepped recovery, owing to adopting above technical scheme, makes it compared with prior art, has following advantage and good effect:
The source pump that a kind of exhaust heat stepped recovery of the utility model and drying medium step heat, take the small temperature difference thermal pump type waste heat recovery of step multiple stage rank, in the fluid passage of the fluid media (medium) making to be loaded with the waste heats such as water vapour outside evaporimeter by continuously slightly cool-down dehumidification heat release realize exhaust heat stepped recycling; Containing the water vapour being loaded with a large amount of high enthalpy in humid air, its enthalpy is obviously higher, makes this unit have higher energy regenerating value;
The source pump that a kind of exhaust heat stepped recovery of the utility model and drying medium step heat, take the little temp. difference condenser heat release in step multiple stage rank, make drying medium (such as air) in the fluid passage of outside condenser by continuous heat temperature raising by a small margin;
The utility model is compared with single step of the prior art high-power single-stage heat pump drying unit, significantly reduce the temperature difference, pressure reduction and the compression ratio between the condenser of each cover heat pump self and evaporimeter, increase substantially the Energy Efficiency Ratio of each cover heat pump, thus significantly improve by the Energy Efficiency Ratio of overlapping the whole source pump that heat pump forms, and significantly improve the operating mode of compressor bank more.
Accompanying drawing explanation
By reference to the accompanying drawings, by hereafter state detailed description, more clearly can understand above-mentioned and other feature and advantage of the present utility model, wherein:
Fig. 1 is the structural representation of the heat pump of the heating of drying medium step and exhaust heat stepped recovery in the utility model embodiment one;
Fig. 2 is air step temp. rising and exhaust heat stepped recovery temperature difference schematic diagram in the utility model embodiment one;
Fig. 3 is that in the utility model embodiment one, heat pump heats circular chart;
The grain drying system figure of the heat pump that Fig. 4 provides for employing the utility model;
Fig. 5 is air condition variation diagram in the utility model embodiment one;
Fig. 6 is the structural representation of the heat pump of the heating of drying medium step and exhaust heat stepped recovery in the utility model embodiment two;
Fig. 7 is air condition variation diagram in the utility model embodiment two;
Symbol description:
1-blower fan
2-drying medium flow channel
201-import
3-drying room
4-drying medium flow pass
401-exports
5a, 6a, 7a, 10a, 11a-condenser
5b, 6b, 7b, 10b, 11b-compressor
5c, 6c, 7c, 10c, 11c-choke valve
5d, 6d, 7d, 10d, 11d-evaporimeter
5e, 6e, 7e, 10e, 11e-tank
8-filter screen
9-device for recovering powder
10-drying tower
11-grain hoisting system
12-dedusting dust collecting system
13-air-introduced machine
14-main air blower
15-condenser passages
The cylindrical silo of 16-
17-boiler channel
1001-stores section
1002-drying section
1003-cooling section temperature descending section
1004-recycling cavity
Detailed description of the invention
See the accompanying drawing that the utility model embodiment is shown, hereafter in more detail the utility model will be described.But the utility model can realize in many different forms, and should not be construed as by the restriction in the embodiment of this proposition.On the contrary, it is abundant and complete open in order to reach for proposing these embodiments, and makes those skilled in the art understand scope of the present utility model completely.In these accompanying drawings, for clarity sake, may be exaggerated size and the relative size in layer and region.
The utility model provides the heat pump of the heating of a kind of drying medium step and exhaust heat stepped recovery, comprise drying room, drying medium flow channel and drying medium flow pass, drying medium flow channel is all connected with drying room with drying medium flow channel passage; This heat pump at least includes two cover source pump, often overlaps source pump and includes connected compressor, condenser, choke valve and evaporimeter; All condensers are all arranged in drying medium flow channel, and at least one evaporimeter is arranged in drying medium flow pass; Wherein, the import side of the condenser self-desiccation medium flow channel in all source pump starts to drying room order spread configuration, and it often overlaps the corresponding and outlet side being positioned at the evaporimeter self-desiccation medium flow pass of drying medium flow pass and starts to drying room order spread configuration.
The utility model is by high-power for large for traditional single step temperature difference heat pump waste heat recovery, transform the small temperature difference thermal pump type waste heat recovery of many steps multiple stage rank as, in the fluid passage of the fluid media (medium) making to be loaded with the waste heats such as water vapour outside evaporimeter by continuously slightly cooling heat release namely realize exhaust heat stepped recycling; Drying medium (such as air) is heated by the step that namely continuous heat temperature raising by a small margin realizes drying medium in the fluid passage of outside condenser.The utility model significantly reduces the temperature difference, pressure reduction and compression ratio between the condenser of each cover heat pump self and evaporimeter, increase substantially the Energy Efficiency Ratio of each cover heat pump, thus significantly improve by the Energy Efficiency Ratio of overlapping the whole source pump that heat pump forms, and significantly improve the operating mode of compressor bank more.
Be described in detail with regard to specific embodiment below:
Embodiment one
With reference to figure 1-4, the utility model provides the heat pump that a kind of exhaust heat stepped recovery and drying medium step heat, include drying room 3, drying medium flow channel 2 and drying medium flow pass 4, drying medium flow channel 2 is all connected with drying room 3 with drying medium flow pass 4.
Wherein, drying medium is carrying heat and transferring heat can heat the medium promoting to contain moisture evaporation in wet stock containing wet stock, and concrete which kind of drying medium that adopts is not restricted herein, can adopt air, nitrogen, carbon dioxide etc.
If drying medium is heated indirectly by dividing wall type heat exchanger be positioned over evaporating containing moisture in wet stock containing wet stock promotion in heat exchanger, then drying medium also can adopt water vapour, conduction oil, water etc., in this condition, the passage at evaporimeter place is no longer " drying medium flow pass ", but is indirectly heated by dividing wall type heat exchanger " the water vapour passing away " that produce containing wet stock that be positioned in dividing wall type heat exchanger by the drying medium such as water vapour, conduction oil, water being loaded with heat.
Be described using air as drying medium below.The import 201 of drying medium self-desiccation medium flow channel 2 enters, and after drying room 3, flows through drying medium flow pass 4, is discharged by outlet 401.In the present embodiment, this heat pump also at least includes two groups of source pump, and the group number of source pump does not limit herein, can be three groups, four groups etc., be described below for three groups of source pump.
Concrete, as shown in fig. 1, this heat pump includes three groups of source pump, often organize source pump and include condenser (5a, 6a, 7a), evaporimeter (5d, 6d, 7d), compressor (5b, 6b, 7b) and choke valve (5c, 6c, 7c), condenser is connected with the pipeline in evaporimeter and forms with compressor the circulation canal that supplies flow of refrigerant warp, cold-producing medium flows through the pipeline in condenser and evaporimeter successively from compressor starts, and choke valve is arranged on the pipeline between condenser and evaporimeter.High temperature refrigerant gas after compressor out pressurized, flow through the pipeline of condenser, realize heat release cooling, the liquefaction of high temperature refrigerant condensation of gas becomes the refrigerant liquid of low pressure to be input in the pipeline of evaporimeter through choke valve step-down, and absorbing heat of vaporization becomes low pressure refrigerant gas; Compressor flows to condenser after pressurizeing to the low pressure refrigerant gas of being come by evaporimeter again, thus forms a complete refrigerant circulation.
In the present embodiment, condenser 5a, 6a, 7a of three groups of source pump are all arranged in drying medium flow channel 2, and evaporimeter 5d, 6d, 7d are all arranged in drying medium flow pass 4.Wherein, import 201 side of condenser 5a, 6a, 7a self-desiccation medium flow channel 2 in three groups of source pump starts side order spread configuration (i.e. 5a → 6a → 7a) to drying room 3, and outlet 401 side simultaneously often organizing corresponding evaporimeter 5d, 6d, 7d self-desiccation medium flow pass 4 starts the side sequentially spread configuration (i.e. 5d → 6d → 7d) to drying room 3.Spaced apart certain distance between condenser 5a, 6a, 7a, also spaced apart certain distance between evaporimeter 5d, 6d, 7d; Preferably, the far and near order in position between each described condenser to described drying room, the evaporimeter of corresponding with it group is to the position distance sequence consensus of drying room.
Dried is placed in drying room 3 containing wet stock, drying medium air enters in drying medium flow channel 2 from import 201 under the effect of blower fan 1, the import of drying medium flow channel 2 is provided with filter screen 8, prevents extraneous dust, impurity etc. from entering in drying machine with air; Drying medium is fed in drying medium flow channel 2 by fluid delivery system, be sucked in drying medium flow channel 2 by blower fan 1 when drying medium is gas time, then can be transfused to by oil pump or water pump when drying medium is oil, water time, not be restricted herein.After drying medium air enters into drying medium flow channel 2, successively through condenser 5a, 6a, 7a, absorptive condenser inner refrigerant condensation of gas liberated heat, drying medium air is heated into high temperature air by step; High temperature air is imported in drying room 3, carries out drying to the wet stock that contains in drying room 3; Enter in drying medium flow pass 4 to carrying out dried to export containing wet high temperature air containing wet stock, wherein can be provided with device for recovering powder 9 in the exit of drying room 3, enter in drying medium flow pass 4 to prevent the dust in drying room with air; Enter after in drying medium flow pass 4 containing wet high temperature air, flow through evaporimeter 5d, 6d, 7d successively, carry out heat exchange with the refrigerant liquid in evaporimeter, release heat containing wet high temperature air, evaporimeter 5d, 6d, 7d realize exhaust heat stepped recovery; Containing wet high temperature air when evaporator 5d, 6d, 7d, condensation moisture, reclaims condensed water by arranging tank 5e, 6e, 7e in the below of evaporimeter 5d, 6d, 7d.
With reference to Fig. 2, be the utility model air step temp. rising and exhaust heat stepped recovery temperature difference schematic diagram:
By evaporimeter 7d by the part atmospheric heat being in temperature step extreme higher position (>=t3) in the drying medium flow channel 2 outside it, condenser 7a is flowed to compressor 7b, for the heating being in the part air of temperature step extreme higher position T2 in the drying medium flow pass 4 outside condenser 7a, make it temperature and rise to T3;
The part atmospheric heat being in temperature step time high position (t3 → t2) in the drying medium flow channel 2 outside it is made by evaporimeter 6d, condenser 6a is flowed to compressor 6b, for the heating being in the part air of temperature step time high position T1 in the drying medium flow pass 4 outside condenser 6a, make it temperature and rise to T2;
The part atmospheric heat being in temperature step extreme lower position (t2 → t1) in the drying medium flow channel 2 outside it is made by evaporimeter 5d, condenser 5a is flowed to compressor 5b, for the heating being in the part air of temperature step extreme lower position (≤T1) in the drying medium flow pass 4 outside condenser 5a, make it temperature and rise to T1;
The main body of the condenser-reboiler operational difference of above-mentioned this exhaust heat stepped recovery drying medium step temp. rising source pump is T3-t3, T2-t2, T1-t1, is significantly less than the respective value of the high-power heat pump waste heat recovery of the large temperature difference of single step; And the condensation temperature > T3 of the high-power heat pump of the large temperature difference of single step, evaporating temperature < t1, the main body=T3-t1 of condenser-reboiler operational difference.
If the medium (such as air) being loaded with waste heat with certain flow, necessarily specific heat capacity, uniform temperature flowed out by the thermal apparatus such as self-desiccation device is as low-temperature heat source, high-power single cover heat pump is adopted to be transported to by waste heat to have and to determine that the high temperature heat source of temperature requirement goes, the evaporating temperature of this high-power single cover heat pump must lower than the minimum temperature of medium being loaded with waste heat, only in this way, liquid refrigerant in evaporimeter could absorb heat, carburation by evaporation from being loaded with in the medium of waste heat evaporimeter; The evaporating pressure singly overlapping heat pump so high-power is mainly determined by the minimum temperature of the medium being loaded with waste heat, the low then evaporating pressure of minimum temperature being loaded with the medium of waste heat is low, the density of the refrigerant gas that compressor sucks is low, and circulating mass of refrigerant is little, and heating capacity is poor; Then evaporating pressure is high to be loaded with the minimum temperature height of the medium of waste heat, and the density of the refrigerant gas that compressor sucks is large, and circulating mass of refrigerant is large, and heating capacity is strong; The condensation temperature of this high-power single cover heat pump again must higher than the maximum temperature with the drying medium (high temperature heat source) determining temperature requirement, only in this way, refrigerant gas in condenser could liquefy by exothermic condensation, is put by heat to having the drying medium determining temperature requirement; So the condensing pressure of high-power single cover source pump is mainly by having, the drying medium of determining temperature requirement determines, have and determine that the low then condensing pressure of the drying medium temperature of temperature requirement is low, working conditions of compressor is good, and heat pump Energy Efficiency Ratio is high; Have and determine that the drying medium temperature of temperature requirement raises then condensing pressure and raises, working conditions of compressor is deteriorated, and heat pump Energy Efficiency Ratio reduces.
And the heat pump of the drying medium step heating that the utility model provides and exhaust heat stepped recovery, take the small temperature difference thermal pump type waste heat recovery of many steps multiple stage rank, in the drying medium flow pass 4 of the fluid media (medium) making to be loaded with the waste heats such as water vapour outside evaporimeter by continuously slightly cool-down dehumidification heat release realize exhaust heat stepped recycling; Drying medium (such as air) is heated by the step that continuous heat temperature raising by a small margin realizes drying medium in the fluid passage of outside condenser; Compared with the utility model and single step high-power single-stage heat pump drying unit, significantly reduce the temperature difference, pressure reduction and the compression ratio between the condenser of each cover heat pump self and evaporimeter, increase substantially the Energy Efficiency Ratio of each cover heat pump, thus significantly improve by the Energy Efficiency Ratio of overlapping the whole source pump that heat pump forms more, and significantly improve the operating mode of compressor bank, as shown in 3.
Applying in grain dry with regard to the utility model is below example (wherein adopting 3 groups of source pump), is further detailed:
The grain depot of the moderate processing power of day dry 2000 tons of damp grains, in summer harvest season, autumn harvest season, every day, needs removed moisture about 140 tons in (evaporation) damp grain, and institute's calorific requirement is up to 8 × 10
9kcal, calculate according to overall thermal efficiency 60%, standard coal 20 tons amounted to by the fuel such as required coal, natural gas, stalk.
With reference to Fig. 4, the grain drying system of the heat pump provided for adopting the utility model, it comprises drying tower 10, grain hoisting system 11, dedusting dust collecting system 12; Its method of operation is: the surrounding air outside source pump, under the effect of the air powered equipment such as air-introduced machine 13, main air blower 14, flow into the condenser passages 15 of " heat pump of the heating of drying medium step and exhaust heat stepped recovery ", overlapped after heat pump condenser step heat temperature raising becomes high temperature dry air more in condenser passages 15, entered grain column 10; Damp grain, under the effect of drying tower 10 elevator, is transported to drying tower 10 top bottom cylindrical silo 16, falls into the storage section 1001 of drying tower, then sequentially passes through each drying section 1002 of drying tower downwards; In each drying section of drying tower 10, enter the dry air of discharging from right side again on the left of the damp grain flowed downward and self-desiccation tower and carry out cross-flow hot and humid area, damp grain dries out, and dry air moisture absorption is lowered the temperature; After damp grain drying, enter the section of cooling 1003; Through the dried grain of cooling section cooling, be transported to grain depot again after falling into recycling cavity 1004 and deposit; The dry air cooling moisture absorption that drying tower is 10 li becomes containing after humid air, under the effect of the air-supply such as air-introduced machine 13, main air blower 14 power-equipment, flow into the boiler channel 17 of " heat pump of the heating of drying medium step and exhaust heat stepped recovery ", after sensible heat in the many covers evaporimeter step cool-down dehumidification in boiler channel deflates and the latent heat of water vapor in air, then enter air.
Grain dry, need temperature, humidity, enthalpy respectively 25 DEG C, 50%RH, 51kJ/ (kg dry air) left and right surrounding air, be heated to temperature, humidity, enthalpy are respectively 65 DEG C, 4.9%RH, 92kJ/ (kg dry air) left and right is (if dry object is cereal seed, then can only be heated to about 45 DEG C), again with this temperature, humidity, enthalpy be respectively 65 DEG C, the dry air of 4.9%RH, 92kJ/ (kg dry air) left and right and damp grain carry out heat exchange, absorbs the moisture of cereal.
In Grain Drying Process, dry air does " constant enthalpy " change, namely enthalpy (energy density) 92kJ/ (kg dry air) of air remains unchanged, and the gross energy of air does not reduce (ignoring dry air in dry run hot to the leakage of environment); Dry air is lowered the temperature the part sensible heat discharged, and be transformed to the latent heat that damp grain moisture flashes to water vapour, the humidity load of air increases fast.With carry out the temperature of the humid air after hot and humid area, humidity, enthalpy containing wet cereal respectively 41 DEG C, 40%RH, 92kJ/ (kg dry air) left and right, waste heat entrained by it, comprise the sensible heat of air and the latent heat of water vapour, caloric receptivity when being heated with air before drying is in theory equal, as the low-temperature heat source of heat pump, there is high recovery value.
The source pump that a kind of exhaust heat stepped recovery of the utility model and drying medium step heat, be loaded with medium (the such as air of waste heat, water etc.) heat release cooling passage in realize reclaiming the step of waste heat, such as, in the drying medium flow channel got up at the air side Tandem of 3 evaporimeters by 3 cover heat pumps, by temperature after aforementioned grain dry, humidity, enthalpy is respectively 41 DEG C, 40%RH, the humid air of 92kJ/ (kg dry air) reduces to 20 DEG C, 100%RH, the exothermic process of the cool-down dehumidification of 58kJ/ (kg dry air) saturated air, 11 DEG C are divided into by runner order, 7 DEG C, the step of 3 DEG C of totally 3 small size cool-down dehumidifications, the step realizing waste heat (comprising air sensible and vapour latent heat) reclaims, although the temperature difference of each step is little, minimum only has 3 DEG C, but because containing the water vapour being loaded with a large amount of high enthalpy in humid air, its enthalpy is obviously higher, there is higher energy value, even if close to 20 DEG C of boiler channel outlet, the saturated air of 100%RH, its enthalpy still has 58kJ/ (kg dry air), apparently higher than temperature, humidity, enthalpy respectively 25 DEG C, 50%RH, 51kJ/ (kg dry air) left and right surrounding air, this for improve in source pump evaporimeter refrigerant evaporating temperature, evaporating pressure, significant.
In the present embodiment, surrounding air is as drying medium, be inhaled into → condenser 5a, condenser 6a, condenser 7a step heating → drying room drying operation → evaporimeter 7d, evaporimeter 6d, evaporimeter 5d step cool-down dehumidification → enter the process of air from the outlet 401 of drying medium flow pass 4 from the import 201 of drying medium flow channel 2, the state parameter of each point is with reference to shown in following table.
Three condensers by the air heat of 25 DEG C in aforementioned grain dry environment to the heat absorption temperature-rise period of 65 DEG C, be divided into rising 13.3 DEG C (25 DEG C → 38.3 DEG C), rising 13.3 DEG C (38.3 DEG C → 41.6 DEG C) by runner order, rise 13.3 DEG C (41.6 DEG C → 65 DEG C) totally 3 steps slightly heated up, the waste heat that realization is reclaimed with step, to the air as drying medium, carry out step heating.
With reference to Fig. 5, in the present embodiment:
Unit one: the air outside evaporimeter 5d in drying medium flow pass 4, from b2 → b3, release heat Q1, the evaporating temperature t1 of cold-producing medium in evaporimeter 5d, absorbs heat Q1, adds the work done during compression Aa of compressor 5b, the condensation temperature T1 of cold-producing medium in condenser 5a, release heat Q1+Aa, the air condition entering condenser a5 is risen to a1 point from a point, and air themperature is from 25 DEG C → 38.3 DEG C;
Unit two: the air outside evaporimeter 6d in drying medium flow pass 4, from b1 → b2, release heat Q2, the evaporating temperature t2 of cold-producing medium in evaporimeter 6d, absorbs heat Q2, adds the work done during compression Ab of compressor 6b, the condensation temperature T2 of cold-producing medium in condenser 6a, release heat Q2+Ab, the air condition entering condenser 6a is risen to a2 point from a1 point, and air themperature is from 38.3 DEG C → 41.6 DEG C;
Unit three: the air outside evaporimeter 6d in side drying medium flow pass 4, from b → b1, release heat Q3, the evaporating temperature t3 of cold-producing medium in evaporimeter 7d, absorbs heat Q3, adds the work done during compression Ac of compressor 7b, refrigerant condensing temperature T3 in condenser 7a, release heat Q3+Ac, the air condition entering condenser 7a is risen to a3 point from a2 point, and air themperature is from 41.6 DEG C → 65.
Embodiment two
With reference to Fig. 6-7, this heat pump includes some source pump, often organizes source pump and has included condenser, evaporimeter, compressor and choke valve, in the present embodiment, condenser in all source pump is all arranged in drying medium flow channel 2, the evaporimeter in one group of source pump is wherein had at least to be positioned at drying medium flow pass 4, the evaporimeter in one group of source pump is had at least to be arranged in (i.e. external environment) outside drying medium flow pass 4, and evaporimeter is arranged in the condenser of the corresponding source pump of external environment, between condenser in drying medium flow channel 2 in corresponding source pump of import 201 and the evaporimeter of drying medium flow channel 2, remainder is with reference to the description in embodiment one, be not restricted herein.
Below with 5 groups of source pump in order to be described in detail, the evaporimeter that wherein evaporimeter of three groups of source pump is positioned at drying medium flow pass 4, two groups of source pump is arranged in external environment, with reference to shown in Fig. 6.
In the present embodiment, be arranged in the source pump of external environment by increasing evaporimeter, mainly higher for the operating temperature of drying device and flow process is longer, leak the situation that heat is more, heat loss is larger.When the operating temperature of drying device is higher and flow process is longer, leak that heat is more, heat loss is larger time, easily cause return air temperature on the low side, in the drying medium flow pass 4 of the return air being loaded with the waste heats such as water vapour outside evaporimeter by continuously slightly after cool-down dehumidification heat release enthalpy lower than surrounding air; The utility model increases the step levels quantity of drying medium step heating, the basis of 3 described in embodiment one grade is increased to 5 grades, and evaporimeter 10d, the 11d corresponding to the front 2 grades of condensers in drying medium heat tunnel is arranged in outside ambient air, directly extract the air energy in ambient air.Technique scheme, reduce further the temperature difference, pressure reduction and the compression ratio between the condenser of each cover heat pump self and evaporimeter, improves the Energy Efficiency Ratio of each cover heat pump.
With reference to Fig. 7, be the air condition variation diagram of heat pump in the present embodiment, upper as can be seen from figure, the surrounding air of suction is from a point → c point in condenser air passage, and air divides 5 sections of intensifications; Wherein:
The main body of ac1, c1c2 two sections of intensification institute calorific requirements, derive from the evaporimeter in surrounding air, corresponding evaporating temperature is ta, tb, and corresponding condensation temperature is Ta, Tb, and corresponding thermal discharge is respectively Qa+Aa, Qb+Ab;
The main body of c2c3, c3c4, c4c tri-sections of intensification institute calorific requirements, derive from the evaporimeter be loaded with in the return air of waste heat, corresponding evaporating temperature is tc, td, te; Corresponding condensation temperature is respectively Tc, Td, Te; Corresponding thermal discharge is respectively Qc+Ac, Qd+Ad, Qe+Ae.
In sum, the source pump that a kind of exhaust heat stepped recovery of the utility model and drying medium step heat, take the small temperature difference thermal pump type waste heat recovery of step multiple stage rank, in the fluid passage of the fluid media (medium) (such as air) making to be loaded with the waste heats such as water vapour outside evaporimeter by continuously slightly cool-down dehumidification heat release realize exhaust heat stepped recycling; Containing the water vapour being loaded with a large amount of high enthalpy in humid air, its enthalpy is obviously higher, has higher energy regenerating value; Take the little temp. difference condenser heat release in step multiple stage rank, make drying medium (such as air) in the fluid passage of outside condenser by continuous heat temperature raising by a small margin.The utility model is compared with the high-power single-stage heat pump drying of single step in prior art unit, significantly reduce the temperature difference, pressure reduction and the compression ratio between the condenser of each cover heat pump self and evaporimeter, increase substantially the Energy Efficiency Ratio of each cover heat pump, thus significantly improve by the Energy Efficiency Ratio of overlapping the whole source pump that heat pump forms, and significantly improve the operating mode of compressor bank more.
Those skilled in the art should be understood that the utility model can realize with other concrete forms many and not depart from spirit or scope of the present utility model.Although described embodiment of the present utility model, the utility model should be understood and should not be restricted to these embodiments, within the utility model spirit and scope that those skilled in the art can define as appended claims, make change and amendment.
Claims (8)
1. the heat pump of a drying medium step heating and exhaust heat stepped recovery, it is characterized in that, the drying medium flow channel comprising drying room and be connected with drying room and drying medium flow pass, described heat pump at least includes two cover source pump, often overlaps source pump and includes connected compressor, condenser, choke valve and evaporimeter; Described condenser is all arranged in described drying medium flow channel, and at least one evaporimeter is arranged in described drying medium flow pass;
Wherein, condenser in all source pump starts to described drying room order spread configuration from the import of described drying medium flow channel, and it often overlaps the corresponding and evaporimeter being positioned at described drying medium flow pass and starts to described drying room order spread configuration from the outlet of described drying medium flow pass.
2. according to drying medium step heating according to claim 1 and the heat pump of exhaust heat stepped recovery, it is characterized in that, the described evaporimeter in the described source pump of at least two covers is all positioned at described drying medium flow pass.
3. according to the heat pump of drying medium step heating according to claim 1 with exhaust heat stepped recovery, it is characterized in that, described heat pump at least includes three cover source pump, wherein the evaporimeter of the described source pump of at least two covers is positioned at described drying medium flow pass, and the evaporimeter of at least a set of described source pump is positioned at drying medium flow pass atmosphere outside.
4. the drying medium step stated according to claim 3 heats the heat pump with exhaust heat stepped recovery, it is characterized in that, the evaporimeter being positioned at drying medium flow pass atmosphere outside is arranged on the import side of described drying medium flow channel with the condenser that group is corresponding.
5. according to the heat pump of the drying medium step heating described in claim 1 or 2 or 4 with exhaust heat stepped recovery, it is characterized in that, the far and near order in position between each described condenser to described drying room, the evaporimeter of corresponding with it group is to the position distance sequence consensus of drying room.
6. according to the heat pump of drying medium step heating according to claim 1 with exhaust heat stepped recovery, it is characterized in that, described evaporimeter, described choke valve are connected with the pipeline in described condenser and form with described compressor the circulation canal that supplies flow of refrigerant warp; Described cold-producing medium flows through the pipeline in described condenser, choke valve and described evaporimeter successively from described compressor starts.
7. according to the heat pump of drying medium step heating according to claim 1 with exhaust heat stepped recovery, it is characterized in that, described drying medium is carrying heat and transferring heat directly or indirectly can heat the medium promoting containing moisture evaporation in wet stock containing wet stock, and described drying medium adopts air or nitrogen or carbon dioxide or water vapour or conduction oil or water.
8. according to the heat pump of drying medium step heating according to claim 1 with exhaust heat stepped recovery, it is characterized in that, the import of described drying medium flow channel, the outlet of described drying medium flow pass, be provided with fluid delivery system, described fluid delivery system adopts blower fan or oil pump or water pump.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420833495.1U CN204648752U (en) | 2014-12-19 | 2014-12-19 | The heat pump of a kind of drying medium step heating and exhaust heat stepped recovery |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420833495.1U CN204648752U (en) | 2014-12-19 | 2014-12-19 | The heat pump of a kind of drying medium step heating and exhaust heat stepped recovery |
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| CN204648752U true CN204648752U (en) | 2015-09-16 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104792065A (en) * | 2014-12-19 | 2015-07-22 | 上海伯涵热能科技有限公司 | Heat pump system for heating drying medium and recovering waste heat in stepped mode |
| CN109405524A (en) * | 2018-11-23 | 2019-03-01 | 黑龙江中科热泵科技有限公司 | A kind of heat pump continous way grain dryer |
| CN110678248A (en) * | 2017-03-24 | 2020-01-10 | 马西莫·维琴蒂尼 | Apparatus and method for producing water |
-
2014
- 2014-12-19 CN CN201420833495.1U patent/CN204648752U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104792065A (en) * | 2014-12-19 | 2015-07-22 | 上海伯涵热能科技有限公司 | Heat pump system for heating drying medium and recovering waste heat in stepped mode |
| CN104792065B (en) * | 2014-12-19 | 2017-06-20 | 浙江普林艾尔电器工业有限公司 | A kind of dried medium step heats the heat pump with exhaust heat stepped recovery |
| CN110678248A (en) * | 2017-03-24 | 2020-01-10 | 马西莫·维琴蒂尼 | Apparatus and method for producing water |
| CN110678248B (en) * | 2017-03-24 | 2022-05-13 | 荣达高科技有限公司 | Apparatus and method for producing water |
| CN109405524A (en) * | 2018-11-23 | 2019-03-01 | 黑龙江中科热泵科技有限公司 | A kind of heat pump continous way grain dryer |
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Effective date of registration: 20160330 Address after: Hangzhou City, Zhejiang province 311612 large hangtou town in the city of Jiande Industrial Zone Patentee after: Zhejiang Preair Electrical Appliance Industry Co., Ltd. Address before: 200237 Shanghai, Hongmei South Road, No. 777, the bottom floor, room 53, 2101 Patentee before: Shanghai Bohan Thermal Energy Technology Co., Ltd. |
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