CN106196677B - Refrigerating plant - Google Patents
Refrigerating plant Download PDFInfo
- Publication number
- CN106196677B CN106196677B CN201610613815.6A CN201610613815A CN106196677B CN 106196677 B CN106196677 B CN 106196677B CN 201610613815 A CN201610613815 A CN 201610613815A CN 106196677 B CN106196677 B CN 106196677B
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- Prior art keywords
- gas
- secondary air
- cylinder
- air entry
- heat exchanger
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- 239000007788 liquid Substances 0.000 claims abstract description 143
- 230000006835 compression Effects 0.000 claims abstract description 16
- 238000007906 compression Methods 0.000 claims abstract description 16
- 239000003507 refrigerant Substances 0.000 claims description 31
- 238000000926 separation method Methods 0.000 claims description 7
- 238000005259 measurement Methods 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 10
- 230000007423 decrease Effects 0.000 description 9
- 238000001704 evaporation Methods 0.000 description 8
- 239000000203 mixture Substances 0.000 description 7
- 238000005057 refrigeration Methods 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 5
- 239000002826 coolant Substances 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
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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
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
-
- 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
- F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The present invention discloses a kind of refrigerating plant, comprising: main compressor, main compressor are equipped with main air entry and main vent；Auxiliary compressor, auxiliary compressor include shell and at least one cylinder, and shell, which is equipped at least one secondary air intake duct and secondary exhaust pipe, each cylinder, has at least one secondary air entry and at least one auxiliary exhaust port；Outdoor heat exchanger and indoor heat exchanger；At least one gas-liquid separator, each gas-liquid separator includes two interfaces and gas vent, the gas vent of each gas-liquid separator is connected with a secondary air intake duct, outdoor heat exchanger and indoor heat exchanger pass through the first connecting line respectively and are connected with the interface of corresponding gas-liquid separator, first throttle element is in series on first connecting line, the interface of two adjacent gas-liquid separators is connected by the second connecting line, and the second restricting element is in series on the second connecting line.The refrigerating plant of invention can be effectively reduced compression ratio and compressor horsepower declined, improves system performance.
Description
Technical field
The present invention relates to refrigeration technology fields, more particularly, to a kind of refrigerating plant.
Background technique
Air conditioner refrigerating circulation in the related technology mainly includes an outdoor heat exchanger, an indoor heat exchanger, a section
Device, a common compressor (one exhaust outlet of band and an air entry) are flowed, the gaseous state after throttling in gas-liquid two-phase refrigerant is cold
Matchmaker, which isolates and drains back in compressor, to be compressed, which is simultaneously not involved in heat exchange and gaseous coolant pressure is equal to
Evaporating pressure.With the development of society, people increasingly focus on energy conservation and environmental protection, how to further increase Performance for Air Conditioning Systems is to grind
Study carefully trend.
Summary of the invention
The present invention is directed to solve at least some of the technical problems in related technologies.
For this purpose, the present invention proposes a kind of refrigerating plant, it can effectively reduce compression ratio and compressor horsepower declined, improve system
System performance, reduces the pressure loss that refrigerant flows through evaporator, promotes the heat exchange efficiency of evaporator, further improve systematicness
Energy.
Refrigerating plant according to an embodiment of the present invention, comprising: main compressor, the main compressor are equipped with main air entry and master
Exhaust outlet；Auxiliary compressor, the auxiliary compressor include shell and at least one cylinder, and the shell is equipped at least one pair and inhales
Tracheae and secondary exhaust pipe, each cylinder have at least one secondary air entry and at least one auxiliary exhaust port；Outdoor heat exchanger
And indoor heat exchanger, the main air-breathing of one of them in the indoor heat exchanger and the outdoor heat exchanger with the main compressor
Mouth connection；At least one gas-liquid separator, the quantity of the gas-liquid separator is identical as the secondary quantity of air intake duct, Mei Gesuo
Stating gas-liquid separator includes two interfaces and gas vent, and the gas vent of each gas-liquid separator and a pair are inhaled
Tracheae is connected, and the outdoor heat exchanger and the indoor heat exchanger pass through the first connecting line and the corresponding gas-liquid point respectively
Interface from device is connected, and first throttle element is in series on first connecting line, when the number of the gas-liquid separator is
When multiple, the interface of two adjacent gas-liquid separators is connected by the second connecting line, on second connecting line
It is in series with the second restricting element.
Refrigerating plant according to an embodiment of the present invention passes through setting main compressor, auxiliary compressor and at least one gas-liquid
Separator, and it is identical as the secondary quantity of air intake duct to make the quantity of gas-liquid separator, and makes the gas vent of each gas-liquid separator
It is connected with a secondary air intake duct, while outdoor heat exchanger and indoor heat exchanger is made to pass through the first connecting line and corresponding gas respectively
The interface of liquid/gas separator is connected, and in the first connecting line series connection first throttle element, when the number of gas-liquid separator is multiple
When, so that the interfaces of two adjacent gas-liquid separators is connected by the second connecting line and connects second on the second connecting line
The pressure of restricting element, the refrigerant thus sucked from each secondary air entry is higher than evaporating pressure, so as to which pressure is effectively reduced
Contracting ratio improves system performance, while reducing the indoor heat exchanger as evaporator or room so that compressor horsepower decline
The entrance mass dryness fraction of external heat exchanger reduces the pressure loss that refrigerant flows through evaporator, promotes the heat exchange efficiency of evaporator, further
Improve system performance.
According to some embodiments of the present invention, each cylinder is equipped with a piston and N number of slide plate, each slide plate
Two sides be equipped with the secondary air entry and the auxiliary exhaust port, each secondary air entry and a pair air intake duct phase
Connect, wherein N >=2.
According to some embodiments of the present invention, N number of slide plate is respectively the first slide plate to N slide plate, and the piston turns
It moves to the i-th secondary air entry corresponding with the i-th slide plate when contacting, in the rotation direction of the piston, the periphery wall of the piston,
The area that the internal perisporium of the cylinder, the i-th secondary air entry, the i+1 slide plate positioned at the described i-th secondary air entry downstream limit
Domain is the i-th region corresponding with the i-th pair air entry, and the i-th auxiliary exhaust port is located in i-th region, i-th region
Volume is Vi, and the compression total measurement (volume) V of the cylinder is total=V1+ ... Vi+ ... VN, the corresponding capacity Qi in i-th region
=(Vi/V is total) × Qf, Qf are the gross exhaust gas of the cylinder, wherein the exhaust of the capacity Qi in the i-th region and i+1 region
Measure the relationship between Qi+1 are as follows: Qi+1=(0.8~1.2) Qi.
According to some embodiments of the present invention, i-th region is correspondingly provided with one i-th secondary air entry and multiple i-th pairs
Exhaust outlet.
According to some embodiments of the present invention, total exhaust of the gross exhaust gas Qz of the main compressor and the auxiliary compressor
Meet following relationship: 5%≤(Qf* auxiliary compressor running frequency)/(Qz* main compressor running frequency)≤30% between amount Qf.
According to some embodiments of the present invention, the auxiliary compressor includes multiple cylinders, and each cylinder is equipped with one
The pair air entry and an auxiliary exhaust port, each secondary air entry are connected with a secondary air intake duct.
According to some embodiments of the present invention, the auxiliary compressor includes the first cylinder and the second cylinder, first gas
Cylinder is equipped with a secondary air entry and an auxiliary exhaust port, and second cylinder is equipped with a piston and N number of slide plate, institute
The two sides for stating each of second cylinder slide plate are equipped with the secondary air entry and the auxiliary exhaust port, second cylinder
Each of the secondary air entry be connected with a secondary air intake duct, the secondary air entry of first cylinder and second gas
Each of cylinder auxiliary exhaust port is connected to, wherein N >=2.
According to some embodiments of the present invention, the auxiliary compressor includes a cylinder, and the cylinder is equipped with an institute
State secondary air entry and an auxiliary exhaust port.
According to some embodiments of the present invention, refrigerating plant further includes oil eliminator, and the oil eliminator includes entrance, cold
Matchmaker outlet and oil export, the entrance and the main vent and the pair exhaust pipe are connected, the oil export respectively with it is described
Main air entry is connected with pair air intake duct described at least one.
According to some embodiments of the present invention, refrigerating plant further includes commutation component, and the commutation component includes the first valve
Mouthful to the 4th valve port, first valve port is connected to one of in the second valve port and third valve port, the 4th valve port and
Second valve port is connected to another in the third valve port, and first valve port and the main vent and the pair are arranged
Tracheae is connected, and the 4th valve port is connected with the main air entry, and second valve port is connected with the outdoor heat exchanger, described
Third valve port is connected with the indoor heat exchanger.
Detailed description of the invention
Fig. 1 is the schematic diagram according to the refrigerating plant of one embodiment of the invention；
Fig. 2 is refrigerant flow schematic diagram when refrigerating plant shown in FIG. 1 freezes；
Fig. 3 is refrigerant flow schematic diagram when refrigerating plant shown in FIG. 1 heats；
Fig. 4 is the schematic diagram according to the refrigerating plant of another embodiment of the present invention；
Fig. 5 is the schematic diagram according to the refrigerating plant of further embodiment of the present invention；
Fig. 6 is the schematic diagram according to the refrigerating plant of another embodiment of the invention；
Fig. 7 is the schematic diagram according to the refrigerating plant of further embodiment of the present invention；
Fig. 8 is the schematic diagram according to the cylinder of the auxiliary compressor of one embodiment of the invention；
Fig. 9 is the schematic diagram according to the cylinder of the auxiliary compressor of another embodiment of the present invention；
Figure 10 is the schematic diagram according to the cylinder of the auxiliary compressor of further embodiment of the present invention.
Appended drawing reference:
Refrigerating plant 1000,
Auxiliary compressor 100, shell 10, cylinder 11, piston 12, slide plate 13, secondary air entry 14, auxiliary exhaust port 15, secondary exhaust
Pipe b, secondary air intake duct 16, oil eliminator 17,
Indoor heat exchanger 200, outdoor heat exchanger 600,
Gas-liquid separator 300,
First throttle element 400a, the second restricting element 400b,
Commutate component 500, the first valve port c, the second valve port d, third valve port e, the 4th valve port f,
First connecting line 2, the second connecting line 3,
Main compressor 700, main air entry a, main vent g.
Specific embodiment
The embodiment of the present invention is described below in detail, examples of the embodiments are shown in the accompanying drawings.Below with reference to
The embodiment of attached drawing description is exemplary, it is intended to is used to explain the present invention, and is not considered as limiting the invention.
In the description of the present invention, it is to be understood that, term " center ", " longitudinal direction ", " transverse direction ", " length ", " width ",
" thickness ", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom" "inner", "outside", " up time
The orientation or positional relationship of the instructions such as needle ", " counterclockwise ", " axial direction ", " radial direction ", " circumferential direction " be orientation based on the figure or
Positional relationship is merely for convenience of description of the present invention and simplification of the description, rather than the device or element of indication or suggestion meaning must
There must be specific orientation, be constructed and operated in a specific orientation, therefore be not considered as limiting the invention.
In addition, term " first ", " second " are used for descriptive purposes only and cannot be understood as indicating or suggesting relative importance
Or implicitly indicate the quantity of indicated technical characteristic.Define " first " as a result, the feature of " second " can be expressed or
Implicitly include at least one this feature.In the description of the present invention, the meaning of " plurality " is at least two, such as two, three
It is a etc., unless otherwise specifically defined.
In the present invention unless specifically defined or limited otherwise, term " installation ", " connected ", " connection ", " fixation " etc.
Term shall be understood in a broad sense, for example, it may be being fixedly connected, may be a detachable connection, or integral；It can be mechanical connect
It connects, is also possible to be electrically connected or can communicate each other；It can be directly connected, can also indirectly connected through an intermediary, it can be with
It is the interaction relationship of the connection or two elements inside two elements, unless otherwise restricted clearly.For this field
For those of ordinary skill, the specific meanings of the above terms in the present invention can be understood according to specific conditions.
Refrigerating plant 1000 according to an embodiment of the present invention is described below with reference to Fig. 1-Figure 10, wherein refrigerating plant 1000 can
Think cold-warm type refrigerating plant 1000 (as shown in Fig. 1-Fig. 3, Fig. 5-Fig. 7), can be used for freezing or heating, refrigerating plant 1000 is also
It can be single cold type refrigerating plant 1000 (as shown in Figure 4), can be used for freezing.
As shown in Fig. 1-Fig. 7, refrigerating plant 1000 according to an embodiment of the present invention may include main compressor 700, secondary pressure
Contracting machine 100, outdoor heat exchanger 600, indoor heat exchanger 200 and at least one gas-liquid separator 300.
Specifically, main compressor 700 is equipped with main air entry a and main vent g, and refrigerant can return to master from main air entry a
Compressor 700 is formed as the refrigerant of high temperature and pressure after the compression of main compressor 700, is discharged from main vent g.Main compressor 700
It can be existing compressor, such as piston compressor, scroll compressor or screw compressor etc..
Auxiliary compressor 100 includes shell 10 and at least one cylinder 11, at least one cylinder 11 is located in shell 10, shell
10 are equipped at least one secondary air intake duct 16 and secondary exhaust pipe b, and each cylinder 11 is at least one secondary air entry 14 and at least
One auxiliary exhaust port 15, the secondary air intake duct 16 of shell 10 are connected with the secondary air entry 14 of cylinder 11, and at least one of cylinder 11 is secondary
Exhaust outlet 15 is connected with the secondary exhaust pipe b of shell 10, and refrigerant can be returned from secondary air intake duct 16 and by corresponding secondary air entry 14
To cylinder 11 corresponding with secondary air entry 14, secondary exhaust pipe b is discharged to from corresponding auxiliary exhaust port 15 after the compression of cylinder 11.
For example, the quantity of secondary air intake duct 16 is identical as the secondary quantity of air entry 14, each as shown in Fig. 1-Fig. 5 and Fig. 7
Secondary air intake duct 16 is corresponding with each secondary air entry 14 to be connected.Certainly, in further embodiments, the quantity of secondary air intake duct 16 and pair
The quantity of air entry 14 can not also be identical, such as there are two cylinder 11, one of gas as shown in fig. 6, auxiliary compressor 100 has
The quantity of the secondary air entry 14 of cylinder 11 is identical as the secondary quantity of air intake duct 16, or in other embodiments, secondary exhaust pipe 16
Quantity be it is multiple, the quantity of the secondary air entry 14 of auxiliary compressor 100 is one, and multiple pair exhaust pipes 16 can be connected to one simultaneously
Secondary air entry 14.
Herein it should be noted that main compressor 700, auxiliary compressor 100 are only intended to two compressors of difference, it is not used in
Indicate the importance degree of two compressors with opening sequence.
One of them in indoor heat exchanger 200 and outdoor heat exchanger 600 is connected to the main air entry a of main compressor 700.
Specifically, when refrigerating plant 1000 is single cold type refrigerating plant 1000, as shown in figure 4, the first end of outdoor heat exchanger 600
It is connected simultaneously with main vent g and pair exhaust pipe b, the first end of indoor heat exchanger 200 is connected with main air entry a.When refrigeration fills
When setting 1000 as cold-warm type refrigerating plant 1000, as shown in Fig. 1-Fig. 3, Fig. 5-Fig. 7, refrigerating plant 1000 further includes commutation component
500, commutation component 500 includes the first valve port c to the 4th valve port f, its in the first valve port c and the second valve port d and third valve port e
In a connection, the 4th valve port f is connected to another in the second valve port d and third valve port e, that is to say, that as the first valve port c
When being connected to the second valve port d, third valve port e is connected to the 4th valve port f, when the first valve port c is connected to third valve port e, second
Valve port d is connected to the 4th valve port f；First valve port c is connected with main vent g and pair exhaust pipe b, the 4th valve port f and main air entry a
It is connected, the second valve port d is connected with outdoor heat exchanger 600, and third valve port e is connected with indoor heat exchanger 200, when refrigerating plant 1000
The first valve port c is connected to the second valve port d when refrigeration and third valve port e is connected to the 4th valve port f, when refrigerating plant 1000 heats
First valve port c is connected to third valve port e and the second valve port d is connected to the 4th valve port f.
The quantity of gas-liquid separator 300 is identical as the secondary quantity of air intake duct 16, and each gas-liquid separator 300 includes two and connects
Mouth and gas vent, the gas vent of each gas-liquid separator 300 are connected with a secondary air intake duct 16, as a result, each gas-liquid point
From the gaseous coolant that device 300 is isolated secondary compression can be flowed to by corresponding secondary air intake duct 16 and by corresponding secondary air entry 14
The cylinder 11 of machine 100.
Outdoor heat exchanger 600 and indoor heat exchanger 200 pass through the first connecting line 2 and corresponding gas-liquid separator respectively
300 interface is connected, and first throttle element 400a is in series on the first connecting line 2, when the number of gas-liquid separator 300 is more
When a, the interface of two adjacent gas-liquid separators 300 is connected by the second connecting line 3, is in series on the second connecting line 3
Second restricting element 400b.
It is understood that the quantity of gas-liquid separator 300 can be selected according to the actual situation, such as such as Fig. 1-figure
Shown in 4, gas-liquid separator 300 is two；In the example of hgure 5, gas-liquid separator 300 is three；In the example of fig. 6, gas
Liquid/gas separator 300 is four, and in the example shown in Fig. 7, gas-liquid separator 300 is one.
As shown in fig. 7, gas-liquid separator 300 is one, two interfaces are respectively first interface and second interface, pair compression
The secondary air entry 14 and auxiliary exhaust port 15 of machine 100 are respectively one, the first interface and outdoor heat exchanger 600 of gas-liquid separator 300
Second end between and gas-liquid separator 300 second interface and indoor heat exchanger 200 second end between be connected with respectively
The gas vent of first throttle element 400a, gas-liquid separator 300 are connected by corresponding secondary air intake duct 16 with secondary air entry 14.
As Figure 1-Figure 4, gas-liquid separator 300 is two and respectively the first gas-liquid separator 300 and the second gas-liquid
Separator 300, two interfaces are respectively first interface and second interface, and the tool of auxiliary compressor 100 is there are two secondary air entry 14 and divides
Not Wei the first secondary air entry 14 and the second secondary air entry 14, the first interface and outdoor heat exchanger 600 of the first gas-liquid separator 300
First throttle element 400a, the gas vent of the first gas-liquid separator 300 are in series on the first connecting line 2 between second end
It is connected to the first secondary air entry 14 by the first secondary air intake duct 16, the second interface and the second gas-liquid of the first gas-liquid separator 300
The second restricting element 400b, the second gas-liquid separator are in series on the second connecting line 3 between the first interface of separator 300
300 gas vent is connected to the second secondary air entry 14 by the second secondary air intake duct 16, and the second of the second gas-liquid separator 300 connects
First throttle element 400a is in series on the first connecting line 2 between mouth and the second end of indoor heat exchanger 200.
As shown in figure 5, gas-liquid separator 300 is three and respectively the first gas-liquid separator 300, the second gas-liquid separator
300 and third gas-liquid separator 300, the secondary air entry 14 of auxiliary compressor 100 is three and the respectively first secondary air entry 14, the
Second mate's air entry 14 and third pair air entry 14, the first interface of the first gas-liquid separator 300 and the second of outdoor heat exchanger 600
The first connecting line 2 between end is in series with first throttle element 400a, the gas vent and first of the first gas-liquid separator 300
It is connected between secondary air entry 14 by the first secondary air intake duct 16, the second interface and the second gas-liquid point of the first gas-liquid separator 300
The second restricting element 400b, the second gas-liquid separator are in series on the second connecting line 3 between first interface from device 300
300 gas vent is connected to the second secondary air entry 14 by the second secondary air intake duct 16, and the second of the second gas-liquid separator 300 connects
It is in series with the second restricting element 400b on the second connecting line 3 between mouth and the first interface of third gas-liquid separator 300, the
Is in series on the first connecting line 2 between the second interface of three gas-liquid separators 300 and the second end of indoor heat exchanger 200
One restricting element 400a, the gas vent and third pair air entry 14 of third gas-liquid separator 300 pass through third pair air intake duct 16
Connection.
As shown in fig. 6, gas-liquid separator 300 is four and respectively the first gas-liquid separator 300, the second gas-liquid separator
300, third gas-liquid separator 300 and the 4th gas-liquid separator 300, there are two cylinder 11, one of gas for the tool of auxiliary compressor 100
There are four secondary air entry 14 and the respectively first secondary air entry 14, second secondary air entries 14, third pair air entry 14 for tool on cylinder 11
With fourth officer air entry 14, between the first interface of the first gas-liquid separator 300 and the second end of outdoor heat exchanger 600 first
Connecting line 2 is in series with first throttle element 400a, and the gas vent of the first gas-liquid separator 300 and the first secondary air entry 14 are logical
It crosses the first secondary air intake duct 16 to be connected to, the first interface of the second interface of the first gas-liquid separator 300 and the second gas-liquid separator 300
Between the second connecting line 3 on be in series with the second restricting element 400b, the gas vent and second of the second gas-liquid separator 300
Secondary air entry 14 is connected to by the second secondary air intake duct 16, the second interface and third gas-liquid separator of the second gas-liquid separator 300
It is in series with the second restricting element 400b on the second connecting line 3 between 300 first interface, third gas-liquid separator 300
The second restricting element is in series on the second connecting line 3 between second interface and the first interface of the 4th gas-liquid separator 300
The gas vent of 400b, third gas-liquid separator 300 are connected to third pair air entry 14 by third pair air intake duct 16, the 4th gas
First segment is in series on the first connecting line 2 between the second interface of liquid/gas separator 300 and the second end of indoor heat exchanger 200
The gas vent of fluid element 400a, the 4th gas-liquid separator 300 are connected to fourth officer air entry 14 by fourth officer air intake duct 16.
Below be cold-warm type refrigerating plant 1000 with refrigerating plant 1000, secondary air entry 14 is two, gas-liquid separator 300
It is illustrated for being two.
As denoted by the arrows in fig. 2, when 1000 refrigerating operaton of refrigerating plant, the compressed refrigerant of main compressor 700 is from master
Exhaust outlet g discharge, the compressed refrigerant of auxiliary compressor 100 is discharged to secondary exhaust pipe b from auxiliary exhaust port 15, from main vent g and
The high pressure gaseous refrigerant being discharged from secondary exhaust pipe b enters outdoor heat exchanger 600 and is cooled into high pressure low temperature liquid, then passes through
It is mixed after crossing the first throttle element 400a decrease temperature and pressure between outdoor heat exchanger 600 and the first gas-liquid separator 300 as gas-liquid
Object is closed, gas-liquid mixture is imported into the first gas-liquid separator 300, wherein the gas separated by the first gas-liquid separator 300
The cylinder 11 that auxiliary compressor 100 is entered by the first secondary air entry 14, is then compressed into height by the cylinder 11 of auxiliary compressor 100
Warm high pressure gas；In addition the liquid separated by the first gas-liquid separator 300 passes through the second restricting element 400b decrease temperature and pressure
Become gas-liquid mixture afterwards, gas-liquid mixture is imported into the second gas-liquid separator 300, wherein being divided by the second gas-liquid separator 300
The cylinder 11 that the gas come enters auxiliary compressor 100 by the second secondary air entry 14 is separated out, then by the gas of auxiliary compressor 100
Cylinder 11 is compressed into high temperature and high pressure gas, and the liquid in addition separated by the second gas-liquid separator 300 passes through indoor heat exchanger 200
The evaporation of heat exchanger 200 is entered the room after first throttle element 400a decrease temperature and pressure between the second gas-liquid separator 300 to become
Overheated gas, these overheated gas are compressed into high temperature and high pressure gas by main compressor 700；High temperature is compressed by main compressor 700
The gas of high pressure and outdoor heat exchanger 600 is entered by the gas that auxiliary compressor 100 is compressed into high temperature and pressure together, repeatedly.
As indicated by the arrows in fig. 3, when 1000 heating operation of refrigerating plant, the compressed refrigerant of main compressor 700 is from master
Exhaust outlet g discharge, the compressed refrigerant of auxiliary compressor 100 is discharged to secondary exhaust pipe b from auxiliary exhaust port 15, from main vent g and
The refrigerant being discharged from secondary exhaust pipe b enters the room heat exchanger 200 and is cooled into high pressure low temperature liquid, is then passed through first throttle member
Become gas-liquid mixture after part 400a decrease temperature and pressure, gas-liquid mixture is imported into the second gas-liquid separator 300, wherein by the second gas
The gas that liquid/gas separator 300 is separated enters auxiliary compressor 100 by the second secondary air entry 14, then by auxiliary compressor
100 cylinder 11 is compressed into high temperature and high pressure gas；In addition the liquid separated by the second gas-liquid separator 300 passes through the second section
Become gas-liquid mixture after fluid element 400b decrease temperature and pressure, gas-liquid mixture is imported into the first gas-liquid separator 300, wherein by the
The gas that one gas-liquid separator 300 is separated enters the cylinder 11 of auxiliary compressor 100 by the first secondary air entry 14, then
High temperature and high pressure gas is compressed by the cylinder 11 of auxiliary compressor 100, the liquid in addition separated by the first gas-liquid separator 300
Enter outdoor after the first throttle element 400a decrease temperature and pressure between outdoor heat exchanger 600 and the first gas-liquid separator 300
The evaporation of heat exchanger 600 becomes overheated gas, these overheated gas are compressed into high temperature and high pressure gas by main compressor 700；By main pressure
Contracting machine 700 be compressed into high temperature and pressure gas and by the cylinder 11 of auxiliary compressor 100 be compressed into the gas of high temperature and pressure together into
Enter indoor heat exchanger 200, repeatedly.
It follows that in refrigeration and heating, refrigerant by the gas-liquid separation twice that throttles three times, by secondary air entry 14 into
The pressure entered to the refrigerant in the cylinder 11 of auxiliary compressor 100 is greater than evaporating pressure, presses winner so as to reduce compression ratio
The decline of the power of contracting machine 700 and auxiliary compressor 100, improves system performance.Gas-liquid separator more than 300, when refrigeration with it is outdoor
The refrigerant pressure of the gas vent discharge of the connected gas-liquid separator 300 of heat exchanger 600 is more higher than evaporating pressure, when heating and room
The refrigerant pressure of the gas vent discharge of the connected gas-liquid separator 300 of interior heat exchanger 200 is more higher than evaporating pressure, thus more
Compression ratio can be reduced.Simultaneously can largely reduce flow into evaporator (when refrigeration indoor heat exchanger 200 be evaporator,
Outdoor heat exchanger 600 is evaporator when heating) refrigerant mass dryness fraction, reduce pressure loss when refrigerant flows through evaporator, promoted
The heat exchange efficiency of evaporator.
Refrigerating plant 1000 according to an embodiment of the present invention passes through setting main compressor 700, auxiliary compressor 100 and extremely
A few gas-liquid separator 300, and it is identical as the secondary quantity of air intake duct 16 to make the quantity of gas-liquid separator 300, and makes each gas
The gas vent of liquid/gas separator 300 is connected with a secondary air intake duct 16, while making outdoor heat exchanger 600 and indoor heat exchanger 200
It is connected respectively by the first connecting line 2 and the interface of corresponding gas-liquid separator 300, and connects the in the first connecting line 2
One restricting element 400a makes the interface of two adjacent gas-liquid separators 300 when the number of gas-liquid separator 300 is multiple
And on second connecting line 3 connect second restricting element 400b connected by the second connecting line 3, thus from each secondary air-breathing
The pressure of the refrigerants of 14 sucking of mouth is all higher than evaporating pressure, so as to which compression ratio is effectively reduced compressor horsepower is declined,
System performance is improved, while reducing and entering dry as the indoor heat exchanger 200 or outdoor heat exchanger 600 of evaporator
Degree, reduces the pressure loss that refrigerant flows through evaporator, promotes the heat exchange efficiency of evaporator, further increase system performance.
Inventor under the conditions of international standard operating condition ARI and uses refrigerating plant 1000 according to an embodiment of the present invention
Performance when R410A refrigerant is calculated, and compared with existing refrigerating plant 1000, inventor's discovery is primary using second throttle
Gas-liquid separation can use the gas-liquid separation twice that throttles three times can be with improving energy efficiency 12.8%, using four times with improving energy efficiency 9.6%
Gas-liquid separation can use five throttlings, four gas-liquid separations can be with improving energy efficiency three times with improving energy efficiency 14.3% for throttling
15.2%, use ten throttlings, nine gas-liquid separations can be with improving energy efficiency 17%.
According to some embodiments of the present invention, each cylinder 11 is equipped with a piston 12 and N number of slide plate 13, each slide plate 13
Two sides be equipped with secondary air entry 14 and auxiliary exhaust port 15, the apex of each slide plate 13 is contacted with the periphery wall of piston 12, wherein N
≥2.Specifically, the two sides of each slide plate 13 are equipped with a secondary air entry 14 and at least one auxiliary exhaust port 15, as a result, each
The quantity of secondary air entry 14 is identical as the quantity of slide plate 13 on cylinder 11.For example, as shown in figure 8, each cylinder 11 is equipped with one
Piston 12 and two slide plates 13, the two sides of each slide plate 13 are equipped with a secondary air entry 14 and an auxiliary exhaust port 15；In Fig. 9
In the example shown, each cylinder 11 is equipped with a piston 12 and three slide plates 13, and the two sides of each slide plate 13 are equipped with one
Secondary air entry 14 and an auxiliary exhaust port 15；In the example shown in Figure 10, each cylinder 11 is equipped with a piston 12 and four
Slide plate 13, the two sides of each slide plate 13 are equipped with a secondary air entry 14 and an auxiliary exhaust port 15.
Each pair air entry 14 is connected with a secondary air intake duct 16.For example, as Figure 1-Figure 4, auxiliary compressor 100 has
One cylinder 11, and slide plate 13, two secondary air entries 14, two gas-liquid separators 300 pass through respectively there are two tools on cylinder 11
Two secondary air intake ducts 16 are connected to two secondary air entries 14；In the specific example shown in Fig. 5, auxiliary compressor 100 has one
Cylinder 11, and there are three slide plates 13 for tool on cylinder 11, three secondary air entries 14, three gas-liquid separators 300 are respectively by three
Secondary air intake duct 16 is connected with three secondary air entries 14；Alternatively, in further embodiments, auxiliary compressor 100 has multiple cylinders
11, each cylinder 11 is equipped with a piston 12 and N number of slide plate 13, and the two sides of each slide plate 13 are equipped with secondary air entry 14 and secondary row
Port 15, for example, it is twin-tub rotation-type compressor that the tool of auxiliary compressor 100, which is auxiliary compressor 100 there are two cylinder 11,.
Preferably, in the circumferential direction of cylinder 11, N number of slide plate 13 is evenly spaced on.
Specifically, N number of slide plate 13 is respectively the first slide plate 13 to N slide plate 13, and piston 12 turns to right with the i-th slide plate 13
When the secondary air entry 14 of i-th answered contacts, in the rotation direction of piston 12, the periphery wall of piston 12, the internal perisporium of cylinder 11, the
The region that i pair air entry 14, the i+1 slide plate 13 positioned at the i-th 14 downstream of secondary air entry limit is right with the i-th secondary air entry 14
The i-th region answered, the i-th auxiliary exhaust port 15 are located in the i-th region, and the volume in the i-th region is Vi, the compression total measurement (volume) V of cylinder 11
Always=V1+ ... Vi+ ... VN, corresponding capacity Qi=(Vi/V the is total) × Qf in the i-th region, Qf are total exhaust of cylinder 11
Amount, wherein the relationship between the capacity Qi in the i-th region and the capacity Qi+1 in i+1 region are as follows: Qi+1=(0.8~1.2)
Qi.Such as Q2=(0.8~1.2) * Q1, Q3=(0.8~1.2) * Q2 ... ..., QN=(0.8~1.2) * QN-1.
Optionally, the i-th region is correspondingly provided with one i-th secondary air entry 14 and multiple i-th auxiliary exhaust ports 15.For example, the i-thth area
Domain is correspondingly provided with one i-th secondary air entry 14 and two the i-th auxiliary exhaust ports 15.Pressure between multiple i-th auxiliary exhaust ports 15 as a result,
Power is identical.
In some embodiments of the invention, the gross exhaust gas of the gross exhaust gas Qz of main compressor 700 and auxiliary compressor 100
Meet following relationship between Qf: 5%≤(100 running frequency of Qf* auxiliary compressor)/(700 running frequency of Qz* main compressor)≤
30%.To be conducive to further decrease compression ratio compressor horsepower is declined, improves system performance.
In other embodiments of the invention, auxiliary compressor 100 includes multiple cylinders 11, and each cylinder 11 is equipped with one
Secondary air entry 14 and an auxiliary exhaust port 15, each pair air entry 14 are connected with a secondary air intake duct 16.For example, in refrigerating plant
For tool there are two gas-liquid separator 300, auxiliary compressor 100 includes two cylinders 11 on 1000, and each cylinder 11 is equipped with a pair and inhales
Port 14 and an auxiliary exhaust port 15, each pair air entry 14 is connected with corresponding each secondary air intake duct 16, consequently facilitating from two
The gaseous coolant that a gas-liquid separator 300 is isolated can divide by two secondary air intake ducts 16 and corresponding secondary air entry 14 respectively
Two cylinders 11 are not flowed to.
According to some embodiments of the present invention, as shown in fig. 6, auxiliary compressor 100 includes the first cylinder 11 and the second cylinder
11, the first cylinder 11 is equipped with a secondary air entry 14 and an auxiliary exhaust port 15, and the second cylinder 11 is equipped with a piston 12 and N number of
The two sides of slide plate 13, each slide plate 13 in the second cylinder 11 are equipped with secondary air entry 14 and auxiliary exhaust port 15, the second cylinder 11
Each of secondary air entry 14 be connected with a pair air intake duct 16, the secondary air entry 14 of the first cylinder 11 is every with the second cylinder 11
A auxiliary exhaust port 15 is connected to, wherein N >=2.The gaseous coolant isolated as a result, through gas-liquid separator 300 can pass through corresponding pair
Air intake duct 16 and secondary air entry 14 flow to the second cylinder, and refrigerant is after the second cylinder compression from 15 row of auxiliary exhaust port of the second cylinder
Out, and by the secondary air entry 14 of the first cylinder the first cylinder is flowed to, so that refrigerant is made to continue to compress in the first cylinder, it is real
The function of the two stages of compression of existing auxiliary compressor, further increases the compression ratio of auxiliary compressor.
In some embodiments of the invention, it as shown in fig. 7, auxiliary compressor 100 includes a cylinder 11, is set on cylinder 11
Have a secondary air entry 14 and an auxiliary exhaust port 15, for example, auxiliary compressor 100 be plug compressor, scroll compressor or
Screw compressor.At this point, the quantity of gas-liquid separator 300 can be one, the quantity of certain gas-liquid separator 300 can be with
To be multiple, when gas-liquid separator 300 is multiple, the gas vent of multiple gas-liquid separators 300 passes through corresponding secondary suction respectively
Tracheae 16 is connected to secondary air entry 14 simultaneously.
According to some embodiments of the present invention, refrigerating plant 1000 further includes oil eliminator 17, oil eliminator 17 include into
Mouth, refrigerant exit and oil export.Entrance is connected with main vent g and pair exhaust pipe b, oil export respectively with main air entry a and extremely
A few secondary air intake duct 16 is connected, when refrigerating plant 1000 is single cold type refrigerating plant 1000, refrigerant exit and outdoor heat exchange
Device 600 is connected, and when refrigerating plant 1000 is cold-warm type refrigerating plant 1000, refrigerant exit is connected with above-mentioned first valve port c.When
So, in further embodiments, as shown in Fig. 1-Fig. 4 and Fig. 6-Fig. 7, entrance be only connected with main vent g.
In some embodiments of the invention, as shown in fig. 7, main compressor 700 further includes liquid storage device, the outlet of liquid storage device
It is connected to main air entry a, wherein liquid storage device plays gas liquid separating function, is drawn into main pressure so as to reduce from main air entry a
The content liquid of refrigerant in contracting machine 700 avoids the occurrence of liquid hit phenomenon, improves the service life of main compressor 700.
In the present invention unless specifically defined or limited otherwise, fisrt feature in the second feature " on " or " down " can be with
It is that the first and second features directly contact or the first and second features pass through intermediary mediate contact.Moreover, fisrt feature exists
Second feature " on ", " top " and " above " but fisrt feature be directly above or diagonally above the second feature, or be merely representative of
First feature horizontal height is higher than second feature.Fisrt feature can be under the second feature " below ", " below " and " below "
One feature is directly under or diagonally below the second feature, or is merely representative of first feature horizontal height less than second feature.
In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show
The description of example " or " some examples " etc. means specific features, structure, material or spy described in conjunction with this embodiment or example
Point is included at least one embodiment or example of the invention.In the present specification, schematic expression of the above terms are not
It must be directed to identical embodiment or example.Moreover, particular features, structures, materials, or characteristics described can be in office
It can be combined in any suitable manner in one or more embodiment or examples.In addition, without conflicting with each other, the skill of this field
Art personnel can tie the feature of different embodiments or examples described in this specification and different embodiments or examples
It closes and combines.
Although the embodiments of the present invention has been shown and described above, it is to be understood that above-described embodiment is example
Property, it is not considered as limiting the invention, those skilled in the art within the scope of the invention can be to above-mentioned
Embodiment is changed, modifies, replacement and variant.
Claims (10)
1. a kind of refrigerating plant characterized by comprising
Main compressor, the main compressor are equipped with main air entry and main vent；
Auxiliary compressor, the auxiliary compressor include shell and at least one cylinder, and the shell is equipped at least one secondary air-breathing
Pipe and secondary exhaust pipe, each cylinder have at least one secondary air entry and at least one auxiliary exhaust port；
Outdoor heat exchanger and indoor heat exchanger, one of them in the indoor heat exchanger and the outdoor heat exchanger and the master
The main air entry of compressor is connected to, another in the indoor heat exchanger and the outdoor heat exchanger with the main vent and
The auxiliary exhaust port connection；
At least one gas-liquid separator, the quantity of the gas-liquid separator is identical as the secondary quantity of air intake duct, each described
Gas-liquid separator includes two interfaces and gas vent, the gas vent of each gas-liquid separator and a secondary air-breathing
Pipe is connected, and the outdoor heat exchanger and the indoor heat exchanger pass through the first connecting line and the corresponding gas-liquid separation respectively
The interface of device is connected, and first throttle element is in series on first connecting line, when the number of the gas-liquid separator is more
When a, the interface of two adjacent gas-liquid separators is connected by the second connecting line, is gone here and there on second connecting line
It is associated with the second restricting element.
2. refrigerating plant according to claim 1, which is characterized in that each cylinder is equipped with a piston and N number of cunning
Piece, the two sides of each slide plate are equipped with the secondary air entry and the auxiliary exhaust port, each secondary air entry and one
The pair air intake duct is connected, wherein N >=2.
3. refrigerating plant according to claim 2, which is characterized in that N number of slide plate is respectively that the first slide plate is sliding to N
Piece, it is described in the rotation direction of the piston when piston rotation to the corresponding with the i-th slide plate i-th secondary air entry contacts
The periphery wall of piston, the internal perisporium of the cylinder, the i-th secondary air entry, the i+1 positioned at the described i-th secondary air entry downstream
The region that slide plate limits is the i-th region corresponding with the i-th pair air entry, and the i-th auxiliary exhaust port is located at i-th region
Interior, the volume in i-th region is Vi, the compression total measurement (volume) V of the cylinder is total=V1+ ... Vi+ ... VN, and i-thth area
Corresponding capacity Qi=(Vi/V the is total) × Qf in domain, Qf be the cylinder gross exhaust gas, wherein the capacity Qi in the i-th region with
Relationship between the capacity Qi+1 in i+1 region are as follows: Qi+1=(0.8~1.2) Qi.
4. refrigerating plant according to claim 3, which is characterized in that i-th region is correspondingly provided with one i-th secondary air-breathing
Mouth and multiple i-th auxiliary exhaust ports.
5. refrigerating plant described in any one of -4 according to claim 1, which is characterized in that the gross exhaust gas of the main compressor
Meet following relationship: 5%≤(Qf* auxiliary compressor running frequency)/(Qz* between Qz and the gross exhaust gas Qf of the auxiliary compressor
Main compressor running frequency)≤30%.
6. refrigerating plant according to claim 1, which is characterized in that the auxiliary compressor includes multiple cylinders, Mei Gesuo
It states cylinder and is equipped with a secondary air entry and an auxiliary exhaust port, each secondary air entry and a secondary air-breathing
Pipe is connected.
7. refrigerating plant according to claim 1, which is characterized in that the auxiliary compressor includes the first cylinder and the second gas
Cylinder, first cylinder are equipped with a secondary air entry and an auxiliary exhaust port, and second cylinder is equipped with a work
Plug and N number of slide plate, the two sides of each of described second cylinder slide plate are equipped with the secondary air entry and the secondary exhaust
Mouthful, each of described second cylinder secondary air entry is connected with a secondary air intake duct, and the secondary of first cylinder inhales
Port is connected to each of second cylinder auxiliary exhaust port, wherein N >=2.
8. refrigerating plant according to claim 1, which is characterized in that the auxiliary compressor includes a cylinder, the gas
Cylinder is equipped with a secondary air entry and an auxiliary exhaust port.
9. refrigerating plant according to claim 1, which is characterized in that further include oil eliminator, the oil eliminator includes
Entrance, refrigerant exit and oil export, the entrance are connected with the main vent and the secondary exhaust pipe, the oil export difference
It is connected with the main air entry and at least one described secondary air intake duct.
10. refrigerating plant according to claim 1, which is characterized in that further include commutation component, the commutation component includes
First valve port to the 4th valve port, first valve port are connected to one of in the second valve port and third valve port, and the described 4th
Valve port is connected to another in second valve port and the third valve port, first valve port and the main vent and institute
It states secondary exhaust pipe to be connected, the 4th valve port is connected with the main air entry, second valve port and the outdoor heat exchanger phase
Even, the third valve port is connected with the indoor heat exchanger.
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| CN201610613815.6A CN106196677B (en) | 2016-07-28 | 2016-07-28 | Refrigerating plant |
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| CN1138109C (en) * | 2001-12-28 | 2004-02-11 | 西安交通大学 | Two-stage carbon dioxide cryogenic refrigeration device |
| CN103380337B (en) * | 2011-02-14 | 2016-09-21 | 开利公司 | Liquid vapor phase separation equipment |
| TWI499750B (en) * | 2014-06-10 | 2015-09-11 | Round Shine Industrail Co Ltd | A multi-blade rotary compressor and a mathod for multiple cycle |
| CN105066493A (en) * | 2015-08-31 | 2015-11-18 | 广东美的暖通设备有限公司 | Air conditioning system |
| CN205102448U (en) * | 2015-11-06 | 2016-03-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and refrigerating system |
| CN205349730U (en) * | 2016-02-18 | 2016-06-29 | 广东美芝制冷设备有限公司 | Cylinder, rotary compressor , single cold system and heat pump system |
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