CN102648383A - Refrigeration system and heat pump unit including such a system - Google Patents
Refrigeration system and heat pump unit including such a system Download PDFInfo
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- CN102648383A CN102648383A CN2010800565276A CN201080056527A CN102648383A CN 102648383 A CN102648383 A CN 102648383A CN 2010800565276 A CN2010800565276 A CN 2010800565276A CN 201080056527 A CN201080056527 A CN 201080056527A CN 102648383 A CN102648383 A CN 102648383A
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- cold
- producing medium
- compressor reducer
- injection
- condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The invention relates to a cooling system and a heat pump unit including such a system. Said refrigeration system includes a main circuit (2) for circulating a refrigerant, comprising a condenser (4), an expansion valve (5), an evaporator (6) and a compressor (3) connected in series, a refrigerant injection circuit (7) designed to enable the refrigerant taken from the main circuit to be injected into at least one compression chamber of the compressor, a means (8, 9) for measuring the temperature and delivery pressure of the compressor, and a regulation means (11) coupled with the injection circuit and designed such as to regulate the amount of refrigerant injected into the compressor, the regulation means including a blocking means movable between open and closed positions of the injection circuit, and a control means (12); designed for controlling the movements of the blocking means between the open and closed positions thereof according to the temperatures and pressures measured by the measurement means.
Description
Technical field
The present invention relates to a kind of refrigeration system, more particularly, relate to the heat pump unit that is used to produce hot water especially.
Background technology
Known, heat pump unit comprises: be used for the major loop of circulating refrigerant, this major loop comprises condenser, expansion valve, evaporimeter and the compressor reducer that is connected in series.
The air heat pump is used to produce hot water and finishing heating system (for example, changing the boiler supplying high temperature heat sink) more and more, and therefore they need supply the fan loop unit or heat the higher condensation temperature in floor than being used to.During operation, at low environment temperature place, high compression rate is endowed compressor reducer, and it has caused high release temperature.At the condenser place, when cold-producing medium can not be by superheated, the high-temperature gradient that cold-producing medium bears caused through before the condensation heat exchange, and in condenser, the ratio of the heat exchange through convection current is dominant, has then reduced efficient.The reduction of the ratio of the energy that exchanges through condensation has caused increasing the exchange surface of condenser on the one hand, defines once more on the other hand that be used for can not superheated and the relevant zone of condenser condensing.When use had the condensing agent of gentle key temperatures, such as R410A, this effect was amplified through the minimizing of the obtainable potential condensation heat at the high temperature place.Be provided with special specific condenser that can not superheated zone by then necessarily to guarantee that it causes excessive cost for facility towards the heat exchange of the satisfaction of hot-water return.
Another defective intrinsic with the air heat pump is during operation; At above-mentioned low ambient temperature place; The reduction of the heating efficiency of this unit; It has caused or has selected bigger compressor reducer size with during year, satisfies the demand on the run duration of reduction, perhaps uses auxiliary resistor (resistance).
Document JP 2006234363 has been explained a kind of refrigeration system, comprising:
-being used for the major loop of circulating refrigerant continuously, it comprises condenser, expansion valve, evaporimeter and the compressor reducer that is connected in series,
-cold-producing medium injection loop, it has the first that is connected with major loop in the condenser downstream, and the second portion that is connected with compressor reducer is so that allow to be injected into from the cold-producing medium that major loop obtains at least one compression chamber of compressor reducer,
-temperature and pressure measurement mechanism, it is designed to discharging place at compressor reducer, measures the temperature and pressure of cold-producing medium.And
-adjusting device; Itself and injection loop are coupled and are designed to regulate the quantity that injection gets into the cold-producing medium of compressor reducer; Adjusting device comprises the cladding system that can between the open and close position of injection loop, move; And be designed to relevant the control device that the control cladding system moves between their open and close position by the temperature and pressure of measurement mechanism measurement.
The open and close of regulating cladding system as the function of exhaust temperature of being measured by measurement mechanism and pressure makes that can regulate the cold-producing medium injection gets into the function of compressor reducer conduct at the thermodynamic behaviour of the cold-producing medium of discharging place of compressor reducer; It makes can control the characteristic that cold-producing medium infiltrates condenser, therefore to improve its efficient.
Though the refrigeration system of explanation has been improved the performance of condenser in document JP 2006234363, yet it has defective.
The refrigeration system of explanation comprises screw compression device and the control device that is designed to control cladding system in document JP 2006234363; So that under blowdown presssure; Difference between the exhaust temperature of compressor reducer and the saturation temperature of cold-producing medium is lower than 10 ° of C, more particularly, approaches 0 ° of C.It should be noted that under the blowdown presssure of compressor reducer the difference between the exhaust temperature of compressor reducer and the saturation temperature of cold-producing medium is also referred to as " in the superheated of discharging place of compressor reducer ".
When the cold-producing medium that is intended to pass the screw compression device was the R134A type, this crossed approximate 20% injection flow rate of mass flowrate (flowrate) that thermal valve can easily obtain to be sucked by compressor reducer.
Yet, for cold-producing medium such as R410A, approximate 70% or more injection flow rate of so mass flowrate that can only obtain by compressor reducer suck overheated at this of discharging place of compressor reducer.
Yet, make injection loop use big conduit in order to guarantee this flow rate, to be known that.
This conduit can make that the installation at the scene of installation refrigeration system is complicated, and when injection is stopped, has increased the influence of the wasted space that is formed by the conduit that constitutes injection loop considerably, and it has damaged the performance of compressor reducer.
Summary of the invention
The present invention is devoted to solve the whole of these defectives or some.
Advantageously comprising based on technical problem of the present invention provides the refrigeration system with simple and economical structure; It is suitable for operation under the high temperature deviation between evaporation and the condensation; And irrespectively carry out the condenser that maintains the standard simultaneously well with employed cold-producing medium.
For this purpose; The present invention relates to the refrigeration system of aforementioned type; Wherein injection loop is included in one or more injection openings that forms in one or more compression chamber of compressor reducer; Each injection openings is configured to and made before the volume that the part refrigerant compressed stands to be substantially equal to 2.5 the factor reduces, the refrigerant mixed of the cold-producing medium of injection loop and compressed in the middle part of corresponding compression chamber.
The configuration of this injection openings makes and can obtain in the pressure of injection cold-producing medium and the high pressure differential between the main average pressure in the compression chamber in correspondence; It makes can maximize maximum flow rate; For given condensing pressure; This maximum flow rate can be injected into said chamber potentially, uses ductule to process injection loop simultaneously.This has caused minimizing the influence of the wasted space that when injection stops, being made up of the conduit that forms injection loop, and it has improved the performance of compressor reducer, and has therefore improved the performance of refrigeration system.
In addition; Make with the adjusting of the opening and closing of the cladding system of the configuration association of this injection openings; If hope; The injection that can regulate cold-producing medium is so that on the mass flowrate that obtains on the extreme operating position to be sucked by compressor to 60% to 80% or bigger injection flow rate, and when injection stops, not damaging the performance of compressor reducer.This flow rate value in discharging place of compressor reducer converts endergonic increase (in the major part in compression process, mass flowrate increases by 60% to 80%) into.Have extra energy at the condenser place, near 10%, it is favourable especially at the operating position place that is considered, because heat demand is maximum usually for the thermal capacity that can be considered to increase with respect to traditional solution.As a result, for the mass flowrate at 100 evaporimeter place of evaporimeter, condenser can be passed with 160 to 180 mass flowrate.
Advantageously, infusion line is designed to make the injection of the cold-producing medium in the compression chamber of compressor reducer just after the termination with respect to the suction process in said chamber, to begin.
According to an embodiment, control device is designed under the blowdown presssure of compressor reducer, and the control cladding system is as the function of the difference between the saturation temperature of the exhaust temperature of compressor reducer and cold-producing medium.The exhaust temperature of compressor reducer and the blowdown presssure of compressor reducer correspond respectively to the value of being measured by measurement mechanism, and under the blowdown presssure of compressor reducer, the saturation temperature of the cold-producing medium advantageously chart from be stored in control device is inferred.
Therefore, aforesaid embodiment makes can be between compression period, the cold-producing medium of the variable number that injection obtains from the condenser downstream, and the overheated standard that is based on discharging place of compressor reducer, the quantity of regulating injection.These are arranged so that can monitor the overheated of compressor reducer discharging place, and keeps the latter to be in the scope of the value of expectation.Therefore can be controlled at the ratio of the heat that exchanges through condensation in the condenser, therefore improve the efficient of condenser.Therefore can obtain to allow the refrigeration system of high condensation temperature, the condenser that maintains the standard simultaneously.
Advantageously, injection loop is designed to make the cold-producing medium that obtains in the condenser downstream to be transferred to compressor reducer roughly adiabaticly.Adopt this layout, the enthalpy of the cold-producing medium of injection (enthalpy) minimum, and, for given injection flow rate, be minimized the overheated of compressor reducer discharging place.This has caused the improved validity of condenser.
According to an alternative embodiment, control device is designed to control cladding system so that under blowdown presssure, the poor constant between the saturation temperature of the exhaust temperature of compressor reducer and cold-producing medium or be lower than predetermined value.These means make and can guarantee that in condenser the ratio by the heat of condensation exchange is maintained on the predetermined value, and are irrelevant with the operating condition of system.
According to first embodiment, control device is designed to control cladding system, and is so that the ratio of the heat through convective exchange in condenser and the total heat that in condenser, exchanges is no more than 35%, irrelevant with the operating position of system.Use the opereating specification of the system of R410A cold-producing medium advantageously comprise-30 and+evaporating temperature between 20 ° of C, and be included in+20 and+condensation temperature between 70 ° of C.This adjusting has the advantage of condenser with following physical region work that make; Wherein, Carry out non-superheated and condensation, it remains unchanged and irrelevant with the variation in evaporation and condensation, and therefore it make and can use the condenser of standard to be used for according to system of the present invention.
Advantageously, the cold-producing medium that in major loop, circulates is R410A.
According to second embodiment; Refrigeration system comprises the recovery interchanger; It is designed to make and can be delivered in the some place that is positioned at the condenser downstream, the cold-producing medium that circulates in the major loop and in the some place in the downstream that are positioned at adjusting device, the heat between the cold-producing medium that circulates in the injection loop.
This existence of reclaiming interchanger makes can increase the enthalpy of cold-producing medium before the cold-producing medium injection gets into compressor reducer, it has caused increasing capacity and its efficient of system.In addition; Because the adjusting of the quantity of the cold-producing medium of injection is carried out according to the dynamic thermodynamic parameter in discharging place of compressor reducer, so can control the opening of cladding system so that in cold-producing medium or the dry saturated steam or the moist steam in the exit of reclaiming interchanger.Control device can advantageously be designed to control cladding system; So that under blowdown presssure; Difference between the saturation temperature of the exhaust temperature of compressor reducer and cold-producing medium is maintained at predetermined value or is lower than predetermined value; Predetermined value is defined so that the cold-producing medium in the exit of reclaiming interchanger is a wet-steam phase, for example has 95% or steam titer (titer) still less.
According to one embodiment of present invention, compressor reducer is the roll-type compressor reducer.
Preferably, adjusting device comprises electromagnetism (solenoid) valve and the electronic controller of arranging with the control magnetic valve, preferably through electric pulse control.These devices make can regulate the wide region of injection flow rate through the simple modulation of impulse duration.Preferably, close usually during the adjusting magnetic valve of the type.These devices make can eliminate the extra isolating valve that is positioned at the control valve upper reaches, has therefore limited the cost of system.Another solution comprises: use gradually the open form control valve and arrange to control the gradually electronic controller of open form control valve.Advantageously, control valve be motorized and allow to control gradually flow rate.
According to one embodiment of present invention; Refrigeration system can be reversible so that operate according to demand; Perhaps, therefore can comprise four road control valves that are positioned between compressor reducer and the major loop in heat manufacturing (heat pump) or cold manufacturing (at the antifreeze circulation or the air regulator of heat pump mode).Under the sort of situation, injection loop advantageously comprises three-way control valve, and it arranges to allow it to be supplied to the cold-producing medium with two kinds of configuration-independents, especially during antifreeze to carry out function of injection.The alternative embodiment of three-way control valve comprises that use is arranged in the control valve upper reaches, at the check valve of supplying with in the branch.
The present invention also relates to heat pump unit, be used to make the heat pump unit of hot water especially, comprise according to refrigeration system of the present invention.Use the air heat pump unit of R410A cold-producing medium that the enforcement that has benefited from according to refrigeration system of the present invention is arranged especially.
The present invention also relates to control the method for refrigeration system, comprise following step:
Be provided for the main circulation loop of circulating refrigerant continuously, this main circulation loop comprises condenser, expansion valve, evaporimeter and the compressor reducer that is connected in series,
The cold-producing medium injection loop is set, and it has the second portion that is connected to the first of major loop in the condenser downstream and is connected to compressor reducer so that allow to be injected into from the cold-producing medium that major loop obtains at least one compression chamber of compressor reducer,
The temperature and pressure measurement mechanism is set, and it designs with the temperature and pressure of measurement at the cold-producing medium of compressor reducer discharging place, and
Setting is coupled to the adjusting device of injection loop, and adjusting device comprises the cladding system that can between the opening and closing position of injection loop, move, and
The mobile conduct of control cladding system between their opening and closing position is by the function of the temperature and pressure of measurement mechanism measurement, so that adjusting is injected into the quantity of the cold-producing medium of compressor reducer,
It is characterized in that: refrigerant compressed stands to be substantially equal to before 2.5 factor volume reduces before in compression chamber, carries out the cold-producing medium that obtains from major loop is injected into the compression chamber of compressor reducer.
Advantageously, the control step comprises the control cladding system so that the ratio of the heat through convective exchange in condenser and the total heat that in condenser, exchanges is no more than 35%, and is irrelevant with the operating position of system.
According to one embodiment of the method for the invention; This method also comprises step; It also comprises: design is set allowing the being positioned at location downstream of condenser, the cold-producing medium that in major loop, circulates and be positioned at the adjusting device location downstream, the heat exchange between the cold-producing medium that in injection loop, circulates; And the control cladding system is so that under blowdown presssure; Difference between the saturation temperature of the exhaust temperature of compressor reducer and cold-producing medium keeps predetermined value or under predetermined value, predetermined value is defined so that the cold-producing medium in the exit of reclaiming interchanger is a wet-steam phase, for example has 95% or steam titer still less.
Description of drawings
Under any circumstance, use the explanation of the subsidiary explanatory view of next reference, the present invention will understand better, and said accompanying drawing has been explained an embodiment of this system as non-limitative example.
Fig. 1 is the explanatory view according to the heat pump unit of the first embodiment of the present invention.
Fig. 2 is the figure of the several kind of refrigeration cycle of explanation, comprises according to the kind of refrigeration cycle of the heat pump unit of Fig. 1 and the saturation curve of cold-producing medium.
Fig. 3 is the figure of the Temperature Distribution of the cold-producing medium in the condenser of the unit of Fig. 1.
Fig. 4 is the explanatory view of heat pump unit according to a second embodiment of the present invention.
Fig. 5 is the figure of the several kind of refrigeration cycle of explanation, comprises according to the kind of refrigeration cycle of the heat pump unit of Fig. 4 and the saturation curve of cryogenic fluid.
Fig. 6 is the explanatory view of the heat pump unit of a third embodiment in accordance with the invention.
The specific embodiment
Fig. 1 schematically illustrates the critical piece of heat pump unit 1.
This heat pump unit 1 comprises the major loop 2 that is used for circulating refrigerant, and it comprises compressor reducer 3, condenser 4, expansion valve 5 and the evaporimeter 6 that is connected in series.
Though in Fig. 1, do not illustrate, heat pump unit 1 can comprise the fluid reservoir that is inserted between condenser and the expansion valve extraly, and in this case, injection loop 7 can advantageously have the first that is connected to major loop in the downstream of fluid reservoir.
Advantageously, control valve 11 is impulse solenoid valves and is closed usually type.Replacedly, control valve 11 can be equipped with gradually open form control valve, and it can advantageously closed usually type.
The open and close of cladding system can be used as by the function of the exhaust temperature of measurement mechanism measurement and pressure and regulates in a different manner.
According to first method of handling control valve 11; Electronic controller 12 is designed to control cladding system so that under the blowdown presssure of compressor reducer; Poor constant between the saturation temperature Td of the exhaust temperature Tr of compressor reducer and condensing agent; That is, so that in discharging place of compressor reducer, overheated (Δ Ts) is constant.
For example, when refrigerant fluid is R410A, can select the adjustment criteria of general Δ Ts=30k.The value of this Δ Ts make can with at the condenser place through the proportional limit of the energy of convective exchange be made as the exchange of condenser place gross energy 40%.Under blowdown presssure, the saturation temperature of known fluid, the quantity of injection cold-producing medium can be followed by adjustment until acquisition value Tr-Td=Δ Ts.
For condenser 4 is optimized more subtly; Can use the more exquisite method of handling control valve 11; It no longer regulates its opening; So that keep overheated constant, but so that remain in the condenser ratios constant by the total energy that exchanges in the energy of convective exchange and the condenser in compressor reducer discharging place (perhaps overheated) in the porch of condenser.For this purpose, must understand the function of the enthalpy curve of bubble (Hb (P)) and condensate (Hd (P)) as pressure, and the steam enthalpy (Hv (P, T)) is as the function of pressure and temperature.Then for example select fixed ratio k=0.2 to 0.25 (energy through convective exchange 20 to 25%), the size value of typical standard condenser, the quantity of the cold-producing medium of injection can be followed by adjustment with the acquisition value
Hv=（Hd-k*Hb）/（1-k）
(perhaps, with reference to the point among Fig. 2 of following explanation, H
D=(H
E-k*H
F)/(1-k) is if by the energy Hb-H of the sub-cooled of fluid exchange
FBe left in the basket).
Can be pointed out that,, can periodically advantageously inject a large amount of condensing agents as function for the integrated value of the size of condenser 4, the perhaps quantity of restriction injection as much as possible on the contrary, this situation is corresponding to the heat demand of maximum.
Therefore, third party's method of handling control valve 11 comprises increases injecting fluid stream, until reaching capacity in discharging place of compressor reducer at the most.Adjustment criteria Tr-Td=Δ Ts then remains valid, but near 5K, has the value of Δ Ts.Transfer to the energy therefore maximum (cause obtaining the loss of energy efficiency, but at low environment temperature place, in view of short cumulative operational time, this being not obvious) of condenser.
On the contrary, it can help limiting as much as possible the quantity (situation corresponding with the interim demand of maximum heat coolant-temperature gage) of injection cold-producing medium, for example carries out from the interim temperature rising of the local provisioning water loop demand of heat, so that avoid the breeding of bacterium.With this relevant method of operating of compressor reducer that can operate maximum discharge temperature (normally greater than 140 ° of C), make and can reduce auxiliary stabilizer, therefore reduced unit cost.Therefore, the cubic method that is used to handle control valve 11 comprises and reduces the injecting fluid flow rate up to the overheated Δ T that obtains at the target discharge place in advance by the characteristic decision of this unit
O, so that can obtain the coolant-temperature gage grade of needs.
Certain specific physical points of major loop 2 is cited in Fig. 1; At the some A of compressor reducer 3 suctions place (the perhaps outlet of evaporimeter 6); Some D (the perhaps inlet of condenser 4) in discharging place of compressor reducer 3; Some F (the perhaps inlet of expansion valve 5) in the exit of condenser 4, the some G in the exit of control valve 11, some H (the perhaps inlet of evaporimeter 6) in the exit of expansion valve 5.
Fig. 2 shows several kind of refrigeration cycle, and the logarithm of the absolute pressure of cold-producing medium is shown as the function of its enthalpy.Curve S shown in figure 2 shows the saturation curve of cold-producing medium.Point Cr, key point, the separation saturation curve is two parts; First has minimum enthalpy, the conversion (be positioned at bubble curve below) of indication between liquid and moist steam, and second portion is corresponding to the conversion between dry saturated steam and moist steam (being positioned at condensate curve below).By some A, D, F, G and the H of the circulation of cold-producing medium explanation corresponding to the physical points of mentioning among Fig. 1, the particular state of the cold-producing medium that some B, C and E obtain corresponding to the part interior at heat pump unit 2, and therefore they can not be clearly shown that in Fig. 1.
Next; With providing brief explanation with respect to first illustrated example; About traditional fluid infusion cycles (that is, use to comprise injection loop, comprise the circulation of the unit acquisition that only relevant with the exhaust temperature of compressor reducer control valve is handled); And not injection, the conversion that relatively during kind of refrigeration cycle 20, stands by cold-producing medium.
According to first embodiment, the cold-producing medium in state A is allowed to get into compressor reducer 3, and constitutes main fluid.The first that compresses is until state B, and the injection of cold-producing medium begins there.For that purpose, expand (state G) through control valve 11 by the fluid of condenser 4 sub-cooled (state F), then mix with the main fluid of compressor reducer 3.The cold-producing medium that comes from mixed process is in state C; Its pressure and enthalpy depend on that the quantity of the cold-producing medium of actual injection is (in the example shown in Fig. 2; The mass flowrate of the cold-producing medium of injection is corresponding to approximate 30% to 40% of the principal mass flow rate; Mixing point C then is positioned at the below of saturation curve, that is, it is made up of the moist steam with titer of approximate 90%; But injection flow rate can use control valve 11 to adjust on wide scope with respect to the value of main fluid, so state C can freely select the function as the target of seeking).Corresponding to the discharging of compressor reducer 3, cold-producing medium then is compressed from state C to state D, under condensing pressure, roughly is positioned at the situation shown in Fig. 2.Cold-producing medium then leaves compressor reducer 3 to condenser 4, and standing there can not the superheated stage from first of D to E, then is condensed to the bubble curve from E, and last sub-cooled is to state F.Through the expansion valve 5 of major loop 2, main fluid is expanded to evaporating pressure (some H) at last, is allowed to get into evaporimeter 6, then is evaporated to the condensate curve, heats at last until it and gets back to state A, is allowed to get into compressor reducer 3 there again.
Overlapping in above-mentioned circulation, show not traditional kind of refrigeration cycle 21 of injection, disclosed the compressor reducer emission point, replace D, identify by D '.Can find out that the cold-producing medium in the porch of condenser is in state D ', with the enthalpy of the very big increase relevant with higher exhaust temperature, and is different from state D.As a result, in traditional situation, through condenser carry out can not superheated part (being identified as DS ') greater than the part that is used for the first embodiment of the present invention (being identified as DS).
Be stacked in the above-mentioned circulation, the kind of refrigeration cycle 22 with traditional fluid injection also is shown.Overheated in view of in compressor reducer discharging place, the circulation with traditional fluid injection mediates, at the cold-producing medium of the porch of condenser at state D.According to the overwhelming majority's embodiment (not shown in FIG.), traditional fluid infusion cycles is different from the first embodiment of the present invention and is to be injected in the compression process and carries out after a while, and therefore is in higher pressure rating.In addition, the quantity of the cold-producing medium of injection is lower, and mixing point C ' remains on the superheated steam stage usually, and is as shown in Figure 2, and one of characteristics of the present invention are the feasible mixing points that can obtain to be positioned at the saturation curve below.
Fig. 3 shows the distribution map of temperature of the water of cold-producing medium and hot-water return, and for example, in the condenser of the brazed plates of operation, the parts of the type are used to have the air heat pump unit of R410A traditionally in adverse current (counter-current).When it passed through condenser, the temperature profile of cold-producing medium was shown as the function of the thermal energy of the accumulation that is received by water.Corresponding to constant water grade (identical flow rate, grade and thermograde); At the operating point place corresponding to the ambient temperature of-15 ° of C, traditional situation (1) of injection is not carried out with the comparison according to the situation with fluid injection of the first embodiment of the present invention.Should be noted that curve 3 shows the temperature profile through the water of condenser.
Under traditional situation, exhaust temperature is higher than 140 ° of C, between the water in the exit of the fluid of the porch of condenser and condenser, has temperature deviation Δ T>80k.In addition, before by condensation exchanged heat (from 1b to 1c), have superiority by the heat of convective exchange (from 1a to 1b, what come from cold-producing medium can not superheated).According to the first embodiment of the present invention, under the situation of cold-producing medium injection, the inlet temperature of cold-producing medium has greatly been reduced, and simultaneously, increases in the mass flowrate of the cold-producing medium at condenser place.The result is that < 30k and by the ratio (from 2b to 2c) of the energy of condensation exchange becomes majority again for the refrigerant/water temperature spread Δ T2 that greatly reduces.Because main temperature spread, thermodynamic (al) irreversibility is greatly reduced, because the present invention, the efficient of condenser is modified.In addition, with the condensation of passing through with respect to convection current, the increase of the flow velocity degree of the cold-producing medium of best exchange efficiency coupling, the feasible exchange surface that can optimize condenser with respect to traditional condenser.
Fig. 4 shows heat pump unit according to a second embodiment of the present invention; It is different from the injection loop that mainly is shown in Fig. 1 and comprises the isolating valve 13 that is positioned at control valve 11 upper reaches; Be positioned at the recovery interchanger 14 in control valve downstream; Reclaim interchanger 14 be designed to allow in major loop the cold-producing medium of the some place circulation in the downstream of condenser 4 and in injection loop 7 at heat exchange between the cold-producing medium in the some place circulation in the downstream of control valve 11 (that is, extract and fluid-vapour mixture of expanding between) at the sub-cooled fluid of major loop with from injection loop.
Fig. 5 shows kind of refrigeration cycle 20 (corresponding to coming from the moist steam injection of reclaiming interchanger 14) according to a second embodiment of the present invention with the mode that is similar to Fig. 2; There is not the circulation 21 of injection; And the tradition of comparing circulation 22 with the injection of superheated steam (use comprises the circulation that the unit of injection loop obtains, injection loop comprise reclaim interchanger with only as control valve in the overheated function manipulation in the exit of reclaiming interchanger).Corresponding to the physical points of mentioning among Fig. 4, therefore some B, C and E do not indicate in Fig. 4 corresponding to the special state of the fluid that in parts, obtains by some A, D, F, G, G ', H and the I of the circulation of fluid explanation.
Fig. 6 has schematically explained the critical piece of the exemplary embodiment of heat pump unit 1bis, is different from heat pump unit 1 and is that it comprises the additional parts that makes it possible to inverse operation.
Heat pump unit 1bis comprises the major loop 2 that is used for circulating refrigerant, and major loop 2 comprises compressor reducer 3, water condenser 4, two-way expansion valve 5, and air evaporator 6, four road control valves 16 and three-way control valve 17.Four tunnel 16 and three tunnel 17 control valves make and can reconfigure the loop from " heat " pattern shown in the solid line to " cold " pattern shown in the dotted line (cold manufacturing, perhaps carrying out the antifreezing agent circulation of evaporimeter).In that " in the cold pattern, compressor reducer 3 discharging gets into air evaporators 6 and no longer gets into water condenser 4, and water condenser 4 is supplied with by two-way expansion valve 5; During heat pump operation, this operator scheme is corresponding to the water cooler with aerial condenser, perhaps through the inverted antifreezing agent stage of circulation.Irrelevant with operator scheme, three-way valve 17 makes can supply flow cryogen to control valve 11.As the replacement of three-way valve, the check valve (not shown in Fig. 6) that is positioned in the supply branch of control valve can be carried out identical functions.
Under the situation of first embodiment, as beginning, the conversion operations that stops mutually during and before the antifreeze work and during circulation afterwards is inverted, injection loop 7 should advantageously be closed.This is closed and comprises and little by little reduce opening stage until for good and all closing, and then closes unique control valve.
Under the situation of second embodiment, during identical conversion mutually be used for all of reversible unit antifreeze mutually during, injection loop can be closed; This process is included in after the flow rate of using control valve 11 injections reduces gradually, closes isolating valve 13.
Under the situation according to the reversible unit of first embodiment, at cold manufacturing mode, injection loop can advantageously be closed, so that do not hinder energy efficiency.
For these identical unit; During antifreeze (outside mutually) in above-mentioned conversion; The 3rd above-mentioned operating pattern can be used to limit duration (because the injection of antifreeze circulation; The available energy that increases with because the mass flowrate that increases, better distributed combination in the passage of evaporimeter), and therefore improved energy efficiency and users'comfort.
Certainly the present invention is not the embodiment that is only limited to above-mentioned this refrigeration system as an example, but comprises the alternative embodiment that they are all on the contrary.
Claims (9)
1. refrigeration system comprises:
Be used for the major loop of circulating refrigerant (2) continuously, it comprises condenser (4), expansion valve (5), evaporimeter (6) and the compressor reducer (7) that is connected in series,
Cold-producing medium injection loop (7); It has the first that is connected with said major loop (2) in said condenser downstream; And the second portion that is connected with said compressor reducer (3) is so that allow to be injected into from the cold-producing medium that major loop obtains at least one compression chamber of said compressor reducer
Temperature and pressure measurement mechanism (8,9), it is designed to discharging place at said compressor reducer, measures the temperature and pressure of cold-producing medium, and
Adjusting device (11); Itself and said injection loop are coupled and are designed to regulate the amount that injection gets into the cold-producing medium of said compressor reducer; Said adjusting device comprises the cladding system that can between the open and close position of said injection loop, move; And be designed to function as the temperature and pressure of measuring by said measurement mechanism, control the control device (12) that said cladding system moves between their open and close position
It is characterized in that: said injection loop (7) is included in one or more injection openings that forms in one or more compression chamber of said compressor reducer; Each injection openings is configured to and made before the volume that the part refrigerant compressed stands to be substantially equal to 2.5 the factor reduces, the refrigerant mixed of the cold-producing medium of said injection loop (7) and compressed in the middle part of corresponding compression chamber.
2. refrigeration system according to claim 1; It is characterized in that: said control device (12) is designed under the blowdown presssure of said compressor reducer, and the control cladding system is as the function of the difference between the saturation temperature of the exhaust temperature of said compressor reducer and said cold-producing medium.
3. refrigeration system according to claim 2; It is characterized in that: said control device (12) is designed to control said cladding system so that under blowdown presssure, the poor constant between the saturation temperature of the exhaust temperature of said compressor reducer and cold-producing medium or be lower than predetermined value.
4. refrigeration system according to claim 1; It is characterized in that: said control device (12) is designed to control said cladding system; So that it is the ratio through the heat of convective exchange and total heat of in said condenser, exchanging is no more than 35% in said condenser, irrelevant with the operating point of system.
5. according to one of them described refrigeration system of claim 1 to 4; It is characterized in that: it comprises reclaims interchanger (14); It is designed to make and can be positioned at said condenser (4) location downstream; The cold-producing medium of circulation and in the location downstream that is positioned at said adjusting device (11) in said major loop (2) transmits hot in said injection loop (7) between the cold-producing medium of circulation.
6. according to one of them described refrigeration system of claim 1 to 5, it is characterized in that: said compressor reducer is the roll type compressor reducer.
7. according to one of them described refrigeration system of claim 1 to 6, it is characterized in that: said adjusting device comprise the solenoid valve or gradually open form control valve (11) with arrange to control the perhaps electronic controller (12) of said gradually open form control valve of said solenoid valve.
8. a heat pump unit is used to make hot water especially, comprises according to one of them described refrigeration system of claim 1 to 7.
9. a method that is used to control refrigeration system comprises the steps:
Be provided for the main circulation loop of circulating refrigerant (2) continuously, this main circulation loop comprises condenser (4), expansion valve (5), evaporimeter (6) and the compressor reducer (3) that is connected in series,
Cold-producing medium injection loop (7) is set; It has the second portion that is connected to the first of said major loop (2) in said condenser (4) downstream and is connected to said compressor reducer (3) so that allow to be injected into from the cold-producing medium that said major loop obtains at least one compression chamber of said compressor reducer
Temperature and pressure measurement mechanism (8,9) is set, and it designs with the temperature and pressure of measurement at the cold-producing medium of said compressor reducer discharging place, and
Setting is coupled to the adjusting device (11) of said injection loop (7), and said adjusting device comprises the cladding system that can between the opening and closing position of said injection loop, move, and
Control the function of the temperature and pressure that the mobile conduct of said cladding system between their opening and closing position measured by said measurement mechanism, be injected into the quantity of the cold-producing medium of said compressor reducer (3) with adjusting,
It is characterized in that: refrigerant compressed stands to be substantially equal to before 2.5 factor volume reduces before in said compression chamber, carries out the cold-producing medium that obtains from said major loop is injected into the compression chamber of said compressor reducer.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR09/57138 | 2009-10-13 | ||
| FR0957138A FR2951250B1 (en) | 2009-10-13 | 2009-10-13 | REFRIGERATION SYSTEM AND HEAT PUMP UNIT COMPRISING SUCH A SYSTEM |
| PCT/FR2010/052153 WO2011045522A1 (en) | 2009-10-13 | 2010-10-12 | Refrigeration system and heat pump unit including such a system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102648383A true CN102648383A (en) | 2012-08-22 |
| CN102648383B CN102648383B (en) | 2015-09-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080056527.6A Expired - Fee Related CN102648383B (en) | 2009-10-13 | 2010-10-12 | Refrigeration system and the heat pump unit comprising this system |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2488803A1 (en) |
| CN (1) | CN102648383B (en) |
| FR (1) | FR2951250B1 (en) |
| WO (1) | WO2011045522A1 (en) |
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| CN104296435A (en) * | 2013-07-19 | 2015-01-21 | 艾默生环境优化技术(苏州)有限公司 | Refrigeration system and method for controlling the same |
| CN104567157A (en) * | 2013-10-18 | 2015-04-29 | 卡雷尔工业股份公司 | Actuation method of a refrigerating machine provided with an economizer apparatus |
| CN104697387A (en) * | 2015-03-10 | 2015-06-10 | 芜湖美的厨卫电器制造有限公司 | Control method and control device of water mixer |
| CN109900003A (en) * | 2017-12-08 | 2019-06-18 | 丹佛斯（天津）有限公司 | Fluid injection control system and fluid circulating system |
| WO2021022766A1 (en) * | 2019-08-07 | 2021-02-11 | 青岛海尔空调电子有限公司 | Compressor cooling control method for air conditioning unit |
| WO2024102371A1 (en) * | 2022-11-07 | 2024-05-16 | Johnson Controls Tyco IP Holdings LLP | Energy efficient heat pump systems and methods |
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| JP5995990B2 (en) * | 2012-11-20 | 2016-09-21 | 三菱電機株式会社 | Refrigeration equipment |
| JP2017166709A (en) * | 2016-03-14 | 2017-09-21 | パナソニックＩｐマネジメント株式会社 | Refrigeration cycle device and hot water heating device including the same |
| FR3051509B1 (en) * | 2016-05-20 | 2018-06-15 | Safran | REVERSIBLE SYSTEM FOR DISSIPATING THERMAL POWER GENERATED IN A GAS TURBINE ENGINE |
| NL1042999B9 (en) * | 2018-09-14 | 2020-07-23 | 7Innovations B V | Installation, intended and equipped as a heat pump system with booster circuit as a heat source for, for example, a central heating or other installation |
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| WO2024102371A1 (en) * | 2022-11-07 | 2024-05-16 | Johnson Controls Tyco IP Holdings LLP | Energy efficient heat pump systems and methods |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2951250B1 (en) | 2012-11-02 |
| CN102648383B (en) | 2015-09-09 |
| EP2488803A1 (en) | 2012-08-22 |
| FR2951250A1 (en) | 2011-04-15 |
| WO2011045522A1 (en) | 2011-04-21 |
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