CN104457032A - Single-cold type refrigeration device and cold-warm type refrigeration device - Google Patents
Single-cold type refrigeration device and cold-warm type refrigeration device Download PDFInfo
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- CN104457032A CN104457032A CN201410797839.2A CN201410797839A CN104457032A CN 104457032 A CN104457032 A CN 104457032A CN 201410797839 A CN201410797839 A CN 201410797839A CN 104457032 A CN104457032 A CN 104457032A
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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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
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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
- F25B2500/00—Problems to be solved
- F25B2500/06—Damage
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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
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
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Abstract
The invention discloses a single-cold type refrigeration device and a cold-warm type refrigeration device. The single-cold type refrigeration device comprises a compressor, an outdoor heat exchanger, an indoor heat exchanger and an oil return device. The compressor is provided with an exhaust port and a gas suction port. The first end of the outdoor heat exchanger is connected with the exhaust port, the first end of the indoor heat exchanger is connected with the gas suction port, and a first throttling element is connected between the second end of the outdoor heat exchanger and the second end of the indoor heat exchanger in series. The oil return device is provided with an inlet, a refrigerant outlet and an oil outlet, the inlet and the refrigerant outlet are connected between the outdoor heat exchanger and the indoor heat exchanger in series, and the oil outlet is connected with the gas suction port. According to the single-cold type refrigeration device, it is guaranteed that cooling oil in the system flows back into the compressor in time, the sealing performance and lubricating performance of the compressor are improved, and therefore the energy efficiency and reliability of the compressor are improved, and the service life of the single-cold type refrigeration device is prolonged; it is avoided that the oil remains in the indoor heat exchanger, and therefore the heat exchange efficiency of the indoor heat exchanger is improved.
Description
Technical field
The present invention relates to refrigerating/heating apparatus field, especially relate to a kind of single cold type refrigerating plant and cold-warm type refrigerating plant.
Background technology
In refrigerating plant during compressor operating, in compressor, be usually sealed with freezing fluid, to seal and to ensure the lubrication that compressor internals runs to compressor.Along with inflow and the discharge of refrigerant, freezing fluid can be blended in cold media gas unavoidably, when compressor operating, freezing fluid can be entered in other components of refrigeration system by exhaust, is distributed in outdoor heat exchanger, indoor heat exchanger, restricting element and connecting line.
When freezing fluid is difficult to be back to compressor inside timely, the operation pasta of compressor can be caused to reduce, thus affect sealing and the lubrication of compressor, compressor efficiency reduces, and even affects compressor reliability time serious.And market also uses the freezing fluid of some special traits, refrigerant intermiscibility in these fluid and refrigerating plant is poor, it is inner that the fluid entering heat exchanger, restricting element and connecting line is difficult to be carried back compressor by refrigerant more, makes the efficiency of compressor more be difficult to ensure.In addition, because freezing fluid is distributed in heat exchanger inside, the heat exchange efficiency of heat exchanger and outdoor environment or indoor environment can be affected, refrigerating plant performance is had a greatly reduced quality.
There is after freezing fluid flows out compressor the problem affecting compressor performance, affect heat exchanger heat exchange efficiency in the refrigerating plant in correlation technique.Inventor finds through research and a large amount of experiments, the reason of the problems referred to above is caused to be to avoid freezing fluid to flow out compressor, therefore, inventor finds, in refrigerating plant, oil return apparatus is set, flow back to compressor inside in time with the freezing fluid in guarantee system, significant impact is existed on raising compressor performance, heat exchanger heat exchange efficiency.
For this reason, the present invention aims to provide a kind of single cold type refrigerating plant, and this single cold type refrigerating plant is provided with oil return apparatus and flows back to compressor inside in time with the freezing fluid in guarantee system.
The present invention also aims to provide a kind of cold-warm type refrigerating plant, and this cold-warm type refrigerating plant is also provided with oil return apparatus and flows back to compressor inside in time with the freezing fluid in guarantee system.
According to the single cold type refrigerating plant of the embodiment of the present invention, comprising: compressor, described compressor has exhaust outlet and air entry; Outdoor heat exchanger and indoor heat exchanger, the first end of described outdoor heat exchanger is connected with described exhaust outlet, the first end of described indoor heat exchanger is connected with described air entry, is in series with first throttle element between the second end of described outdoor heat exchanger and the second end of described indoor heat exchanger; Oil return apparatus, described oil return apparatus has the outlet of entrance, refrigerant exit and fluid, and described entrance and described refrigerant exit are connected between described outdoor heat exchanger and described indoor heat exchanger, and described fluid outlet is connected with described air entry.
According to the single cold type refrigerating plant of the embodiment of the present invention, by arranging oil return apparatus to isolate cooling oil in the refrigerant outdoor between heat exchanger and indoor heat exchanger, in guarantee system, cooling oil flows back to compressor inside in time, improve sealing and the greasy property of compressor, thus improve efficiency and the reliability of compressor, extend the service life of single cold type refrigerating plant.And avoid fluid and be trapped in indoor heat exchanger, improve the heat exchange efficiency of indoor heat exchanger.
In certain embodiments, second section fluid element is in series with between described fluid outlet and described air entry.Thus, can reduce the oil liquid pressure from fluid outlet flow to air entry, when fluid arrives at air entry, pressure can not be too high, thus avoid fluid to enter the quality of the refrigerant of compressor inside to heat exchanger indoor and pressure has an impact.
Particularly, described entrance and described refrigerant exit are connected between described outdoor heat exchanger and described first throttle element.Thus, shorten the path that fluid flows through in refrigerant circulation passage, decrease the time that fluid is back to compressor.And when freezing fluid and refrigerant intermiscibility poor time, effect is also clearly.
According to the cold-warm type refrigerating plant of the embodiment of the present invention, comprising: compressor, described compressor has exhaust outlet and air entry; Commutation assembly, described commutation assembly comprises the first port to the 4th port, described first port is communicated with one of them in described 3rd port with described second port, described 4th port and described second port are communicated with another in described 3rd port, described first port is connected with described exhaust outlet, and described 4th port is connected with described air entry; Outdoor heat exchanger and indoor heat exchanger, the first end of described outdoor heat exchanger is connected with described second port, the first end of described indoor heat exchanger is connected with described 3rd port, is in series with first throttle element between the second end of described outdoor heat exchanger and the second end of described indoor heat exchanger; First oil return apparatus, described first oil return apparatus comprises the outlet of the first entrance, the first refrigerant exit and the first fluid, described first entrance and described first refrigerant exit are connected between described outdoor heat exchanger and described indoor heat exchanger, and described first fluid outlet is connected with described air entry.
According to the cold-warm type refrigerating plant of the embodiment of the present invention, by arranging the first oil return apparatus to isolate fluid in the refrigerant outdoor between heat exchanger and indoor heat exchanger, in guarantee system, fluid flows back to compressor inside in time, improve sealing and the greasy property of compressor, thus improve efficiency and the reliability of compressor, extend the service life of cold-warm type refrigerating plant.And avoid fluid and be trapped in indoor heat exchanger or outdoor heat exchanger, improve the heat exchange efficiency of indoor heat exchanger or outdoor heat exchanger.
In certain embodiments, second section fluid element is in series with between described first fluid outlet and described air entry.Thus, can reduce the pressure from the first fluid outlet flow to the fluid of air entry, when fluid arrives at air entry, pressure can not be too high, thus avoid fluid to have an impact to the quality of refrigerant and pressure that enter compressor inside from refrigerant circulation passage.
Particularly, described first entrance and described first refrigerant exit are connected between described outdoor heat exchanger and described first throttle element, and described second section fluid element is configured for the flow of the pipeline regulated between described first fluid outlet and described air entry; Described first oil return apparatus also comprises the second fluid outlet, described second fluid outlet is connected with described air entry by the 3rd restricting element, and described 3rd restricting element is configured for the flow of the pipeline regulated between described second fluid outlet and described air entry.Thus, can ensure no matter cold-warm type refrigerating plant is in refrigerating state or is in the state of heating, by controlling the flow of second section fluid element and the 3rd restricting element, pressure drop can be realized and be suitable for, thus ensure that fluid can together enter into compressor inside along with cold media gas.
Alternatively, described second section fluid element is the combination of capillary and control valve or described second section fluid element is electric expansion valve.
Alternatively, described 3rd restricting element is the combination of capillary and control valve or described 3rd restricting element is electric expansion valve.
In certain embodiments, described first entrance and described first refrigerant exit are connected between described outdoor heat exchanger and described first throttle element; Described cold-warm type refrigerating plant also comprises the second oil return apparatus, described second oil return apparatus comprises the outlet of the second entrance, the second refrigerant exit and the 3rd fluid, described second entrance and described second refrigerant exit are connected between described indoor heat exchanger and first throttle element, and described 3rd fluid outlet is connected with described air entry.Thus, cold-warm type refrigerating plant according to its refrigeration or can heat state, realizes best reflowing result.
Particularly, the 4th restricting element is in series with between described 3rd fluid outlet and described air entry.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Summary of the invention
The application makes the discovery of the following fact and problem and understanding based on inventor:
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present invention and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is the structural representation of single cold type refrigerating plant according to an embodiment of the invention;
Fig. 2 is the structural representation of single cold type refrigerating plant in accordance with another embodiment of the present invention;
Fig. 3 is the structural representation of cold-warm type refrigerating plant according to an embodiment of the invention;
Fig. 4 is the structural representation of cold-warm type refrigerating plant in accordance with another embodiment of the present invention;
Fig. 5 is the structural representation of the cold-warm type refrigerating plant according to another embodiment of the present invention.
Reference numeral:
Single cold type refrigerating plant 100A, cold-warm type refrigerating plant 100B,
Compressor 1, exhaust outlet a, air entry b,
The first end c of outdoor heat exchanger 2, outdoor heat exchanger, the second end d of outdoor heat exchanger,
The first end e of indoor heat exchanger 3, indoor heat exchanger, the second end f of indoor heat exchanger,
First throttle element 41, second section fluid element 42, the 3rd restricting element 43, the 4th restricting element 44,
Capillary 401, electric expansion valve 402, control valve 403,
Oil return apparatus 5, first oil return apparatus 5F, the second oil return apparatus 5S,
Entrance g, the first entrance g1, the second entrance g2,
Refrigerant exit h, the first refrigerant exit h1, the second refrigerant exit h2,
Fluid outlet i, the first fluid outlet i1, the second fluid outlet i2, the 3rd fluid outlet i3,
Knockout 51, first knockout 511, second knockout 512,
Oil return pipe 52, first oil return pipe 521, second oil return pipe 522, the 3rd oil return pipe 523,
Point sap cavity V, first point of sap cavity V1, second point of sap cavity V2,
Commutation assembly 6, first port A, the second port B, the 3rd port C, the 4th port D,
Refrigerant circulation passage T, kind of refrigeration cycle passage t1, heat circulation canal t2,
Fluid flow channel R, the first fluid flow channel r1, the second fluid flow channel r2, the 3rd fluid flow channel r3.
Detailed description of the invention
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristic.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, except as otherwise noted, the implication of " multiple " is two or more.
In describing the invention, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, concrete condition above-mentioned term concrete meaning in the present invention can be understood.
Below with reference to Fig. 1-Fig. 2, the single cold type refrigerating plant 100A according to the embodiment of the present invention is described.
According to the single cold type refrigerating plant 100A of the embodiment of the present invention, as depicted in figs. 1 and 2, comprising: compressor 1, outdoor heat exchanger 2, indoor heat exchanger 3 and oil return apparatus 5.
Compressor 1 has exhaust outlet a and air entry b, and compressor 1 compresses for the refrigerant flowed into by air entry b, forms HTHP cold media gas and discharge from exhaust outlet a after refrigerant compression.The first end c of outdoor heat exchanger 2 is connected with exhaust outlet a, and the first end e of indoor heat exchanger 3 is connected with air entry b, is in series with first throttle element 41 between the second end d of outdoor heat exchanger 2 and the second end f of indoor heat exchanger 3.
Particularly, as depicted in figs. 1 and 2, compressor 1, outdoor heat exchanger 2, indoor heat exchanger 3 and first throttle element 41 limit the refrigerant circulation passage T for the refrigerant that circulates, and single cold type refrigerating plant 100A has refrigerating function.Alternatively, first throttle element 41 is capillary or electric expansion valve.
When indoor environment needs cooling, single cold type refrigerating plant 100A opens.Refrigerant flows to as shown in arrow T in Fig. 1 and Fig. 2, refrigerant is discharged from exhaust outlet a after being compressed into HTHP cold media gas by compressor 1, the refrigerant of discharging flows to outdoor heat exchanger 2, the condensation heat release in outdoor heat exchanger 2 of HTHP cold media gas forms cryogenic high pressure refrigerant liquid, refrigerant in outdoor heat exchanger 2 flows to first throttle element 41 by its second end d again and forms Low temperature low pressure liquid with reducing pressure by regulating flow, the refrigerant flowed out from first throttle element 41 flows to indoor heat exchanger 3 again, the cold media gas of low-temp low-pressure is formed with evaporation endothermic, thus indoor environment is lowered the temperature, refrigerant in last indoor heat exchanger 3 is flowed back to the air entry b of compressor 1 again by its first end e.
See figures.1.and.2, oil return apparatus 5 has the outlet of entrance g, refrigerant exit h and fluid i, entrance g and refrigerant exit h and is connected between outdoor heat exchanger 2 and indoor heat exchanger 3, and fluid outlet i is connected with air entry b.That is, oil return apparatus 5 is by introducing refrigerant in the pipeline of entrance g outdoor between heat exchanger 2 and indoor heat exchanger 3, then from the refrigerant introduced, cold oil fluid is isolated, isolated fluid exports i by fluid and flows to air entry b, and remaining refrigerant is flowed back in the pipeline between outdoor heat exchanger 2 and indoor heat exchanger 3 by refrigerant exit h again.
It should be noted that, HTHP cold media gas is mixed with freezing fluid when the exhaust outlet a of compressor 1 discharges, and that is, the refrigerant of discharging compressor 1 is in fact refrigerant-cooling oil mixture.When refrigerant-cooling oil mixture flows between outdoor heat exchanger 2 and indoor heat exchanger 3 along refrigerant circulation passage T, mixture can flow into oil return apparatus 5 from entrance g, mixture isolates refrigerant and fluid in oil return apparatus 5, refrigerant flows back between outdoor heat exchanger 2 and indoor heat exchanger 3 from refrigerant exit h, and continues flowing along refrigerant circulation passage T.Isolated fluid then flows to air entry b from fluid outlet i, then along with the refrigerant in refrigerant circulation passage T flows into compressor 1 inside together.
Thus, can to improve in indoor heat exchanger 3 and the purity of refrigerant in adjacent conduit, avoid freezing fluid to be trapped in indoor heat exchanger 3, thus improve the heat exchange efficiency of indoor heat exchanger 3, improve the performance of single cold type refrigerating plant 100A.In addition, oil return apparatus 5 to be arranged so that freezing fluid can flow back to compressor 1 in time inner, ensure that sealing and the lubrication of compressor 1, improve efficiency and the reliability of compressor 1, thus extend the service life of single cold type refrigerating plant 100A.
And when compressor 1 use freezing fluid and refrigerant intermiscibility poor time, the setting of oil return apparatus 5 can avoid freezing fluid to be trapped in indoor heat exchanger 3 and connecting line more.
Particularly, as Figure 1-Figure 2, oil return apparatus 5 comprises knockout 51 and oil return pipe 52, and knockout 51 is for isolating refrigerant and fluid by the refrigerant of introducing-cooling oil mixture.The refrigerant that entrance g and refrigerant exit h forms knockout 51 is imported and exported, knockout 51 is connected between outdoor heat exchanger 2 and indoor heat exchanger 3, to form fluid outlet i in one end access knockout 51 of oil return pipe 52, the other end of oil return pipe 52 connects air entry b, thus isolated for knockout 51 fluid is directed to air entry b, and flow in compressor 1 with the refrigerant in refrigerant circulation passage T, knockout 51 and oil return pipe 52 form fluid flow channel R, and the flow direction of fluid is as shown in arrow R in Fig. 1 and Fig. 2.
More specifically, as depicted in figs. 1 and 2, limit a point sap cavity V in knockout 51, refrigerant-cooling oil mixture carries out the separation of refrigerant and fluid in point sap cavity V.
Alternatively, a point sap cavity V-arrangement becomes cup-shaped space structure, thus is more beneficial to refrigerant and is separated with freezing fluid, improves separation purity.
According to the single cold type refrigerating plant 100A of the embodiment of the present invention, by arranging oil return apparatus 5 to isolate cooling oil in the refrigerant outdoor between heat exchanger 2 and indoor heat exchanger 3, in guarantee system, cooling oil flows back to compressor 1 inside in time, improve sealing and the greasy property of compressor 1, thus improve efficiency and the reliability of compressor 1, extend the service life of single cold type refrigerating plant 100A.And avoid fluid and be trapped in indoor heat exchanger 3, improve the heat exchange efficiency of indoor heat exchanger 3.
Below with reference to the different specific embodiment of two shown in Fig. 1 and Fig. 2, describe the structure of the single cold type refrigerating plant 100A of the embodiment of the present invention in detail.It should be noted that, in different embodiment, label identical from start to finish represents identical element or has the element of identical function.
First embodiment
In this embodiment, as shown in Figure 1, second section fluid element 42 is in series with between fluid outlet i and air entry b, namely second section fluid element 42 is connected on oil return pipe 52, thus, can reduce and flow to the oil liquid pressure of air entry b from fluid outlet i, when fluid arrives at air entry b, pressure can not be too high, thus avoid fluid to enter the quality of the refrigerant of compressor 1 inside to heat exchanger 3 indoor and pressure has an impact.
Specifically, on refrigerant circulation passage T, the refrigerant flowed out from refrigerant exit h flows to the process of air entry b through indoor heat exchanger 3, refrigerant has certain pressure loss, the internal pressure supposing point sap cavity V of oil return apparatus 5 is P2, the pressure at the air entry b place of compressor 1 is P1, then P2 > P1.For ensureing that freezing fluid can be smoothly through oil return pipe 52 and flow to air entry b place, and it is inner together to enter into compressor 1 with cold media gas, therefore be necessary to connect second section fluid element 42 between fluid outlet i and air entry b, make fluid also be depressurized to P1 value, ensure that the pasta of compressor 1 meets instructions for use.
Wherein, second section fluid element 42 is capillary 401, and thus, second section fluid element 42 cost is lower.
In a first embodiment, entrance g and refrigerant exit h is connected between outdoor heat exchanger 2 and first throttle element 41.Namely in FIG, knockout 51 is connected between outdoor heat exchanger 2 and first throttle element 41.
Here it should be noted that, in the refrigerant circulation passage T of single cold type refrigerating plant 100A, when pipeline is longer, heat exchanger is comparatively large, especially under the installation situation of Super long tube, high drop, freezing fluid is difficult to inner to compressor 1 with refrigerant return in time more.
Therefore in single cold type refrigerating plant 100A, the entrance g of oil return apparatus 5 and refrigerant exit h is connected between outdoor heat exchanger 2 and first throttle element 41, make the freezing fluid of discharging compressor 1 need not flow through whole refrigerant circulation passage T, compressor 1 can be got back to inner after only needing it to flow through outdoor heat exchanger 2, greatly shorten the path that it flows through in refrigerant circulation passage T, decrease the time that fluid is back to compressor 1.And when freezing fluid and refrigerant intermiscibility poor time, the entrance g of oil return apparatus 5 and refrigerant exit h is connected on effect between outdoor heat exchanger 2 and first throttle element 41 also clearly.
Such as, single cold type refrigerating plant 100A is air-conditioner, and single cold type refrigerating plant 100A is detachable air conditioner.In detachable air conditioner, in compressor 1, first throttle element 41 machine disposed in the outdoor, off-premises station is connected by pipe arrangement with indoor set, and the length of pipe arrangement, the height fall of off-premises station indoor set are determined by actual installation situation.Therefore in detachable air conditioner, the entrance g of oil return apparatus 5 and refrigerant exit h is preferably connected between outdoor heat exchanger 2 and first throttle element 41, to adapt to the change of various mounting condition, especially under the installation environment of Super long tube, high drop, this set of oil return apparatus 5 substantially reduces the path that fluid flows through in refrigerant circulation passage T, decreases the time that fluid is back to compressor 1.And when single cold type refrigerating plant 100A is detachable air conditioner, oil return apparatus 5 is positioned at off-premises station, the assembling of oil return apparatus 5 is also very convenient.
In a first embodiment, fluid outlet i is arranged on a point bottom of sap cavity V, and entrance g and refrigerant exit h is arranged on a point top of sap cavity V.
Particularly, the fluid density of the refrigerant medium adopted in single cold type refrigerating plant 100A is less than the density of freezing fluid, after freezing fluid and refrigerant layering, freezing fluid is deposited on a point bottom of sap cavity V, refrigerant swims in a point top of sap cavity V, therefore, fluid outlet i is arranged on a point bottom of sap cavity V, and entrance g and refrigerant exit h is arranged on a point top of sap cavity V.
Second embodiment
In a second embodiment, as shown in Figure 2, the structure of single cold type refrigerating plant 100A is substantially identical with the structure of single cold type refrigerating plant 100A in the first embodiment, repeats no more here.
Difference is, in a second embodiment, second section fluid element 42 is electric expansion valve 402.Namely oil return apparatus 5 carries out oil return and pressure drop by electric expansion valve 402.Certainly, second section fluid element 42 also can adopt other voltage drop elements, does not do concrete restriction here.
From the second embodiment, the setting of entrance g and refrigerant exit h is not limited to be connected between outdoor heat exchanger 2 and first throttle element 41, and entrance g and refrigerant exit h also can be connected between indoor heat exchanger 3 and first throttle element 41.
In addition, when the fluid density of the refrigerant medium adopted in single cold type refrigerating plant 100A is greater than the density of freezing fluid, after freezing fluid and refrigerant layering, refrigerant soak is in the bottom of point sap cavity V, freezing fluid swims in a point top of sap cavity V, therefore, fluid outlet i is arranged on a point top of sap cavity V, and entrance g and refrigerant exit h is arranged on a point bottom of sap cavity V.
The scheme drawn by the combination of the first embodiment and the second embodiment, also within the scope of the protection scheme of the single cold type refrigerating plant 100A of the embodiment of the present invention.
Specifically, single cold type refrigerating plant 100A can comprise two oil return apparatus 5, the entrance g of one of them oil return apparatus 5 and refrigerant exit h is connected between outdoor heat exchanger 2 and first throttle element 41, the entrance g of another oil return apparatus 5 and refrigerant exit h is connected between indoor heat exchanger 3 and first throttle element 41, thus in further guarantee system, fluid flow back into compressor 1 inside in time, improves the purity of refrigerant in the refrigerant circulation passage T except compressor 1, outdoor heat exchanger 2.
Below with reference to Fig. 3-Fig. 5, the cold-warm type refrigerating plant 100B according to the embodiment of the present invention is described.
According to the cold-warm type refrigerating plant 100B of the embodiment of the present invention, as shown in Figure 3-Figure 5, comprising: compressor 1, commutation assembly 6, outdoor heat exchanger 2, indoor heat exchanger 3, first oil return apparatus 5F.
Compressor 1 has exhaust outlet a and air entry b, and compressor 1 compresses for the refrigerant flowed into by air entry b.Commutation assembly 6 comprises the first port A to the 4th port D, first port A is communicated with one of them in the 3rd port C with the second port B, 4th port D and the second port B are communicated with another in the 3rd port C, and the first port A is connected with exhaust outlet a, and the 4th port D is connected with air entry b.That is, commutation assembly 6 has two kinds of conducting states, a kind of conducting state is the first port A and the second port B conducting and the 3rd port C and the 4th port D conducting, and another kind of conducting state is the first port A and the 3rd port C conducting and the second port B and the 4th port D conducting.The first end c of outdoor heat exchanger 2 is connected with the second port B, and the first end e of indoor heat exchanger 3 is connected with the 3rd port C, is in series with first throttle element 41 between the second end d of outdoor heat exchanger 2 and the second end f of indoor heat exchanger 3.
Particularly, compressor 1, commutation assembly 6, outdoor heat exchanger 2, indoor heat exchanger 3 and first throttle element 41 limit the refrigerant circulation passage T for the refrigerant that circulates, according to the conducting state of commutation assembly 6, refrigerant circulation passage T comprises again kind of refrigeration cycle passage t1 and heats circulation canal t2, and namely cold-warm type refrigerating plant 100B has the function freezed and heat.
When indoor environment needs cooling, commutation assembly 6 controls the first port A and the second port B conducting, and the 3rd port C and the 4th port D conducting, compressor 1, commutation assembly 6, outdoor heat exchanger 2, indoor heat exchanger 3 and first throttle element 41 form the kind of refrigeration cycle passage t1 of refrigerant.In kind of refrigeration cycle passage t1, refrigerant flows to as shown in arrow t1 in Fig. 3-Fig. 5, refrigerant is discharged from exhaust outlet a after being compressed into HTHP cold media gas by compressor 1, the refrigerant of discharging flows to outdoor heat exchanger 2 from commutation assembly 6, the condensation heat release in outdoor heat exchanger 2 of HTHP cold media gas forms cryogenic high pressure liquid, refrigerant in outdoor heat exchanger 2 flows to first throttle element 41 by its second end d again and forms Low temperature low pressure liquid with reducing pressure by regulating flow, the refrigerant flowed out from first throttle element 41 flows to indoor heat exchanger 3 again, the cold media gas of low-temp low-pressure is formed with evaporation endothermic, thus indoor environment is lowered the temperature, refrigerant in last indoor heat exchanger 3 flows back to the air entry b of compressor 1 again by commutation assembly 6.
When indoor environment needs to heat up, commutation assembly 6 controls the first port A and the 3rd port C conducting, and the second port B and the 4th port D conducting, what compressor 1, commutation assembly 6, outdoor heat exchanger 2, indoor heat exchanger 3 and first throttle element 41 formed refrigerant heats circulation canal t2.Heating in circulation canal t2, refrigerant flows to as shown in arrow t2 in Fig. 3-Fig. 5, refrigerant is discharged from exhaust outlet a after being compressed into HTHP cold media gas by compressor 1, the refrigerant of discharging flows to indoor heat exchanger 3 from commutation assembly 6, the condensation heat release in indoor heat exchanger 3 of HTHP cold media gas forms cryogenic high pressure liquid, thus indoor environment is heated up, refrigerant in indoor heat exchanger 3 flows to first throttle element 41 with reducing pressure by regulating flow again by its second end f, the refrigerant flowed out from first throttle element 41 flows to outdoor heat exchanger 2 again with the cold media gas of evaporation endothermic formation low-temp low-pressure, refrigerant in outdoor heat exchanger 2 flows back to the air entry b of compressor 1 again by commutation assembly 6.
Preferably, because the application technology of cross valve in heating-cooling equipment is comparatively ripe, and cross valve volume is little, cost is lower, and commutation function is stable, reliable, and cross valve selected by the assembly 6 that therefore commutates.Certainly, the present invention is not limited thereto, such as, commutation assembly 6 also to can be disclosed in prior art by multiple valve also, valve member in series, do not do concrete restriction here.
With reference to Fig. 3-Fig. 5, first oil return apparatus 5F comprises the first entrance g1, the first refrigerant exit h1 and the first fluid outlet i1, first entrance g1 and the first refrigerant exit h1 is connected between outdoor heat exchanger 2 and indoor heat exchanger 3, and the first fluid outlet i1 is connected with air entry b.That is, first oil return apparatus 5F is by introducing refrigerant-cooling oil mixture in the pipeline of the first entrance g1 outdoor between heat exchanger 2 and indoor heat exchanger 3, then from the refrigerant-cooling oil mixture introduced, cooling oil is isolated, isolated fluid exports i1 by the first fluid and flows to air entry b, and remaining refrigerant is flowed back in the pipeline between outdoor heat exchanger 2 and indoor heat exchanger 3 by the first refrigerant exit h1 again.
Thus, the purity of refrigerant in the refrigerant circulation passage T between outdoor heat exchanger 2 and indoor heat exchanger 3 can be improved, freezing fluid is avoided to be trapped in indoor heat exchanger 3 or outdoor heat exchanger 2, thus improve the heat exchange efficiency of indoor heat exchanger 3 or outdoor heat exchanger 2, improve the performance of cold-warm type refrigerating plant 100B.In addition, the first oil return apparatus 5F is arranged so that freezing fluid can flow back to compressor 1 inside in time, ensure that sealing and the lubrication of compressor 1, improves efficiency and the reliability of compressor 1, thus extend the service life of cold-warm type refrigerating plant 100B.
And when compressor 1 use freezing fluid and refrigerant intermiscibility poor time, the setting of oil return apparatus 5 can avoid freezing fluid to be trapped in indoor heat exchanger 3, outdoor heat exchanger 2, first throttle element 41 and connecting line more.
Particularly, as shown in Figure 3-Figure 5, the first oil return apparatus 5F comprises the first knockout 511 and the first oil return pipe 521, first knockout 511 for the refrigerant of introducing-cooling oil mixture is isolated refrigerant and fluid.The refrigerant that first entrance g1 and the first refrigerant exit h1 forms the first knockout 511 is imported and exported, namely the first knockout 511 is connected between outdoor heat exchanger 2 and indoor heat exchanger 3, one end of first oil return pipe 521 is accessed in the first knockout 511 to form the first fluid outlet i1, the other end of the first oil return pipe 521 connects air entry b, thus the isolated fluid of the first knockout 511 is directed to air entry b, and flow in compressor 1 with the refrigerant in refrigerant circulation passage T, first knockout 511 and the first oil return pipe 521 form the first fluid flow channel r1, the flow direction of fluid is as shown in arrow r1 in Fig. 3-Fig. 5.
More specifically, as shown in Figure 3-Figure 5, limit first point of sap cavity V1 in the first knockout 511, refrigerant-cooling oil mixture carries out the separation of refrigerant-fluid in first point of sap cavity V1.
According to the cold-warm type refrigerating plant 100B of the embodiment of the present invention, by arranging the first oil return apparatus 5F to isolate fluid in the refrigerant outdoor between heat exchanger 2 and indoor heat exchanger 3, in guarantee system, fluid flows back to compressor 1 inside in time, improve sealing and the greasy property of compressor 1, thus improve efficiency and the reliability of compressor 1, extend the service life of cold-warm type refrigerating plant 100B.And avoid fluid and be trapped in indoor heat exchanger 3 or outdoor heat exchanger 2, improve the heat exchange efficiency of indoor heat exchanger 3 or outdoor heat exchanger 2.
Below with reference to three different specific embodiments shown in Fig. 3-Fig. 5, describe the structure of the cold-warm type refrigerating plant 100B of the embodiment of the present invention in detail.It should be noted that, in different embodiment, label identical from start to finish represents identical element or has the element of identical function.
3rd embodiment
In this embodiment, as shown in Figure 3, second section fluid element 42 is in series with between the first fluid outlet i1 and air entry b.Thus, can reduce and flow to the pressure of the fluid of air entry b from the first fluid outlet i1, when fluid arrives at air entry b, pressure can not be too high, thus avoid fluid to have an impact to the quality of refrigerant and pressure that enter compressor 1 inside from refrigerant circulation passage T.
In the third embodiment, the first entrance g1 and the first refrigerant exit h1 is connected between outdoor heat exchanger 2 and first throttle element 41, and namely in FIG, the first knockout 511 is connected between outdoor heat exchanger 2 and first throttle element 41.
Advantageously, second section fluid element 42 is configured to the adjustable fluid step-down amount from the first fluid outlet i1 to air entry b.
Here it should be noted that, in cold-warm type refrigerating plant 100B, refrigerant is carrying out kind of refrigeration cycle and is heating circulation time, and the component order that refrigerant flows through is different.Suppose, compressor 1 is P1 at the pressure at air entry b place, and refrigerant is in kind of refrigeration cycle passage t1, and refrigerant flows into the first oil return apparatus 5F after being discharged by compressor 1 after commutation assembly 6, outdoor heat exchanger 2, and the internal pressure of first point of sap cavity V1 is P2.Refrigerant is heating in circulation canal t2, and refrigerant flows into the first oil return apparatus 5F after being discharged by compressor 1 after commutation assembly 6, indoor heat exchanger 3, first throttle element 41, and first point of sap cavity V1 internal pressure is P3.Owing to heating circulation canal t2 for kind of refrigeration cycle passage t1, the refrigerant path flowing into the first oil return apparatus 5F adds first throttle element 41, therefore P2 > P3 under normal circumstances.
For ensureing no matter cold-warm type refrigerating plant 100B is in refrigerating state or is in the state of heating, freezing fluid is all depressured to P1 value by the first oil return apparatus 5F, inner to ensure that fluid can together enter compressor 1 in company with cold media gas, be therefore necessary the second section fluid element 42 being in series with adjustable fluid step-down amount between the first fluid outlet i1 and air entry b.
Alternatively, as in Fig. 3, second section fluid element 42 is electric expansion valve 402.
Certainly, in the third embodiment, second section fluid element 42 also can be the combination of capillary 401 and control valve 403.
4th embodiment
In the fourth embodiment, as shown in Figure 4, the structure of cold-warm type refrigerating plant 100B is substantially identical with the structure of the cold-warm type refrigerating plant 100B of the 3rd embodiment, repeats no more here.
Difference is, in the fourth embodiment, fluid flow channel R can be arranged to many, and the pressure drop of every bar fluid flow channel R is different, every bar fluid flow channel R is also provided with the valve controlling its flow simultaneously.
By arranging valve on every bar fluid flow channel R, cold-warm type refrigerating plant 100B can select wherein one or more fluid flow channel R to work when freezing as required, and other fluid flow channels R closes.In like manner, cold-warm type refrigerating plant 100B also can select wherein another or fluid flow channel R that separately several pressure drops are suitable works as required when heating, other fluid flow channels R closes, the reflowing result of final realization the best.
In the fourth embodiment, cold-warm type refrigerating plant 100B comprises an oil return apparatus 5 (i.e. the first oil return apparatus 5F), limits many fluid flow channel R in an oil return apparatus 5.
Particularly, second section fluid element 42 is configured for the flow of the pipeline between adjustment first fluid outlet i1 and air entry b, that is, second section fluid element 42 is for regulating the fluid flow in the first oil return pipe 521, and the first knockout 511, first oil return pipe 521 and second section fluid element 42 form the first fluid flow channel r1.
First oil return apparatus 5F also comprises the second fluid outlet i2, and the second fluid outlet i2 is connected with air entry b by the 3rd restricting element 43, and the 3rd restricting element 43 is configured for the flow of the pipeline between adjustment second fluid outlet i2 and air entry b.
Wherein, first oil return apparatus 5F also comprises the second oil return pipe 522, one end of second oil return pipe 522 is accessed in the first knockout 511 to form the second fluid outlet i2, the other end of the second oil return pipe 522 connects air entry b, thus the isolated fluid of the first knockout 511 is directed to air entry b, and together flow in compressor 1 with the refrigerant in refrigerant circulation passage T, first knockout 511, second oil return pipe 522 and the 3rd restricting element 43 form the second fluid flow channel r2, and the flow direction of fluid is as shown in arrow r2 in Fig. 4.
For ensureing no matter cold-warm type refrigerating plant 100B is in refrigerating state or is in the state of heating, can by controlling the flow of second section fluid element 42 and the 3rd restricting element 43, realize pressure drop suitable (namely ensureing that freezing fluid is all depressured to P1 by the first oil return apparatus 5F), to ensure that fluid can together enter into compressor 1 inside along with cold media gas, therefore in the fourth embodiment, be provided with two fluid flow channel R, the pressure drop of two fluid flow channel R is different.
Wherein, when cold-warm type refrigerating plant 100B is in refrigerating state, when first point of sap cavity V1 internal pressure is P2, second section fluid element 42 is opened and the 3rd restricting element 43 is closed, and fluid flows back into air entry b by the first fluid flow channel r1.And when cold-warm type refrigerating plant 100B be in heat state time, when first point of sap cavity V1 internal pressure is P3, second section fluid element 42 is closed and the 3rd restricting element 43 is opened, and fluid flows back into air entry b by the second fluid flow channel r2.
In the fourth embodiment, second section fluid element 42 is the combination of capillary 401 and control valve 403, and the 3rd restricting element 43 is also the combination of capillary 401 and control valve 403.
Certainly, in the fourth embodiment, second section fluid element 42 also can be electric expansion valve 402, and the 3rd restricting element 43 also can be electric expansion valve 402, does not do concrete restriction here.
5th embodiment
In the 5th embodiment, as shown in Figure 5, the structure of cold-warm type refrigerating plant 100B is substantially identical with the structure of the cold-warm type refrigerating plant 100B of the 4th embodiment.In the 5th embodiment, fluid flow channel R is also arranged to many, and the pressure drop of every bar fluid flow channel R is different, every bar fluid flow channel R is also provided with the valve controlling its flow simultaneously.Cold-warm type refrigerating plant 100B according to its refrigeration or can heat state, selects wherein one or more fluid flow channel R to work, the final reflowing result realizing the best.
Difference is, the 5th embodiment is provided with multiple oil return apparatus 5, and each oil return apparatus 5 has limited out a fluid flow channel R.
Particularly, the first entrance g1 and the first refrigerant exit h1 is connected between outdoor heat exchanger 2 and first throttle element 41, and the first knockout 511, first oil return pipe 521 forms the first fluid flow channel r1.
Cold-warm type refrigerating plant 100B also comprises the second oil return apparatus 5S, second oil return apparatus 5S comprises the second entrance g2, the second refrigerant exit h2 and the 3rd fluid outlet i3, second entrance g2 and the second refrigerant exit h2 is connected between indoor heat exchanger 3 and first throttle element 41, and the 3rd fluid outlet i3 is connected with air entry b.
More specifically, as shown in Figure 5, the second oil return apparatus 5S comprises the second knockout 512 and the 3rd oil return pipe 523, second knockout 512 for the refrigerant of introducing-cooling oil mixture is isolated refrigerant and fluid.The refrigerant that second entrance g2 and the second refrigerant exit h2 forms the second knockout 512 is imported and exported, namely the second knockout 512 is connected between indoor heat exchanger 3 and first throttle element 41, one end of 3rd oil return pipe 523 is accessed in the second knockout 512 to form the 3rd fluid outlet i3, the other end of the 3rd oil return pipe 523 connects air entry b, thus the isolated fluid of the second knockout 512 is directed to air entry b, and flow in compressor 1 with the refrigerant in refrigerant circulation passage T, second knockout 512 and the 3rd oil return pipe 523 form the 3rd fluid flow channel r3, the flow direction of fluid is as shown in arrow r3 in Fig. 5.
Wherein, as shown in Figure 5, limit second point of sap cavity V2 in the second knockout 512, refrigerant-cooling oil mixture carries out the separation of refrigerant, fluid in second point of sap cavity V2.
In the 5th embodiment, be in series with between the first fluid outlet i1 and air entry b between second section fluid element the 42, three fluid outlet i3 and air entry b and be in series with the 4th restricting element 44.
In the 5th embodiment, second section fluid element 42 is the combination of capillary 401 and control valve 403, and the 4th restricting element 44 is also the combination of capillary 401 and control valve 403.
Certainly, in the 5th embodiment, second section fluid element 42 also can be electric expansion valve 402, and the 4th restricting element 44 also can be electric expansion valve 402, does not do concrete restriction here.
It should be noted that, the structure, principle etc. of compressor 1, cross valve, outdoor heat exchanger 2, indoor heat exchanger 3 and first throttle element 41 are prior art, are just not described in detail here.
According to single cold type refrigerating plant 100A and the cold-warm type refrigerating plant 100B of the embodiment of the present invention, by arranging oil return apparatus 5 in systems in which, inner to ensure that cooling oil flows back to compressor 1 in time, thus avoid cooling oil to be distributed in outdoor heat exchanger 2, indoor heat exchanger 3, first throttle element 41 and connecting line, ensure that compressor 1 inner fluid runs liquid level and is suitable for, improve sealing and the greasy property of compressor 1, and then improve the performance of single cold type refrigerating plant 100A and cold-warm type refrigerating plant 100B.
In the description of this description, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and describe embodiments of the invention, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present invention and aim, scope of the present invention is by claim and equivalents thereof.
Claims (10)
1. a single cold type refrigerating plant, is characterized in that, comprising:
Compressor, described compressor has exhaust outlet and air entry;
Outdoor heat exchanger and indoor heat exchanger, the first end of described outdoor heat exchanger is connected with described exhaust outlet, the first end of described indoor heat exchanger is connected with described air entry, is in series with first throttle element between the second end of described outdoor heat exchanger and the second end of described indoor heat exchanger;
Oil return apparatus, described oil return apparatus has the outlet of entrance, refrigerant exit and fluid, and described entrance and described refrigerant exit are connected between described outdoor heat exchanger and described indoor heat exchanger, and described fluid outlet is connected with described air entry.
2. single cold type refrigerating plant according to claim 1, is characterized in that, is in series with second section fluid element between described fluid outlet and described air entry.
3. single cold type refrigerating plant according to claim 1, is characterized in that, described entrance and described refrigerant exit are connected between described outdoor heat exchanger and described first throttle element.
4. a cold-warm type refrigerating plant, is characterized in that, comprising:
Compressor, described compressor has exhaust outlet and air entry;
Commutation assembly, described commutation assembly comprises the first port to the 4th port, described first port is communicated with one of them in described 3rd port with described second port, described 4th port and described second port are communicated with another in described 3rd port, described first port is connected with described exhaust outlet, and described 4th port is connected with described air entry;
Outdoor heat exchanger and indoor heat exchanger, the first end of described outdoor heat exchanger is connected with described second port, the first end of described indoor heat exchanger is connected with described 3rd port, is in series with first throttle element between the second end of described outdoor heat exchanger and the second end of described indoor heat exchanger;
First oil return apparatus, described first oil return apparatus comprises the outlet of the first entrance, the first refrigerant exit and the first fluid, described first entrance and described first refrigerant exit are connected between described outdoor heat exchanger and described indoor heat exchanger, and described first fluid outlet is connected with described air entry.
5. cold-warm type refrigerating plant according to claim 4, is characterized in that, is in series with second section fluid element between described first fluid outlet and described air entry.
6. cold-warm type refrigerating plant according to claim 5, it is characterized in that, described first entrance and described first refrigerant exit are connected between described outdoor heat exchanger and described first throttle element, and described second section fluid element is configured for the flow of the pipeline regulated between described first fluid outlet and described air entry;
Described first oil return apparatus also comprises the second fluid outlet, described second fluid outlet is connected with described air entry by the 3rd restricting element, and described 3rd restricting element is configured for the flow of the pipeline regulated between described second fluid outlet and described air entry.
7. cold-warm type refrigerating plant according to claim 6, is characterized in that, described second section fluid element is the combination of capillary and control valve or described second section fluid element is electric expansion valve.
8. cold-warm type refrigerating plant according to claim 6, is characterized in that, described 3rd restricting element is the combination of capillary and control valve or described 3rd restricting element is electric expansion valve.
9. the cold-warm type refrigerating plant according to claim 4 or 5, is characterized in that, described first entrance and described first refrigerant exit are connected between described outdoor heat exchanger and described first throttle element;
Described cold-warm type refrigerating plant also comprises the second oil return apparatus, described second oil return apparatus comprises the outlet of the second entrance, the second refrigerant exit and the 3rd fluid, described second entrance and described second refrigerant exit are connected between described indoor heat exchanger and first throttle element, and described 3rd fluid outlet is connected with described air entry.
10. cold-warm type refrigerating plant according to claim 9, is characterized in that, is in series with the 4th restricting element between described 3rd fluid outlet and described air entry.
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| CN201410797839.2A CN104457032B (en) | 2014-12-17 | 2014-12-17 | Single-cold type refrigeration device and cold-warm type refrigeration device |
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| CN201410797839.2A CN104457032B (en) | 2014-12-17 | 2014-12-17 | Single-cold type refrigeration device and cold-warm type refrigeration device |
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| CN104457032B CN104457032B (en) | 2017-02-22 |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3238737A (en) * | 1964-03-31 | 1966-03-08 | Larkin Coils Inc | Heated receiver winter control for refrigeration systems |
| CN1865815A (en) * | 2006-05-16 | 2006-11-22 | 东南大学 | Double-compressor hybrid-power combustion-gas thermal pump air-conditioning system |
| CN101949621A (en) * | 2010-09-30 | 2011-01-19 | 广东志高空调有限公司 | Energy-saving air conditioner with refrigerant adjusting function |
| CN202216445U (en) * | 2011-08-23 | 2012-05-09 | 安徽美芝精密制造有限公司 | Refrigeration device |
-
2014
- 2014-12-17 CN CN201410797839.2A patent/CN104457032B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3238737A (en) * | 1964-03-31 | 1966-03-08 | Larkin Coils Inc | Heated receiver winter control for refrigeration systems |
| CN1865815A (en) * | 2006-05-16 | 2006-11-22 | 东南大学 | Double-compressor hybrid-power combustion-gas thermal pump air-conditioning system |
| CN101949621A (en) * | 2010-09-30 | 2011-01-19 | 广东志高空调有限公司 | Energy-saving air conditioner with refrigerant adjusting function |
| CN202216445U (en) * | 2011-08-23 | 2012-05-09 | 安徽美芝精密制造有限公司 | Refrigeration device |
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