CN1580671A - Vapor compression type refrigerating machine - Google Patents
Vapor compression type refrigerating machine Download PDFInfo
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- CN1580671A CN1580671A CNA2004100558620A CN200410055862A CN1580671A CN 1580671 A CN1580671 A CN 1580671A CN A2004100558620 A CNA2004100558620 A CN A2004100558620A CN 200410055862 A CN200410055862 A CN 200410055862A CN 1580671 A CN1580671 A CN 1580671A
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- compressor
- refrigerant
- pressure
- cold
- heat exchanger
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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
- F25B41/00—Fluid-circulation 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
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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
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the compressor
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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
- 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
- F25B2400/075—Details of compressors or related parts with parallel compressors
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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
- 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
- F25B2400/23—Separators
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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
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
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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
- F25B2500/27—Problems to be solved characterised by the stop of the refrigeration cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/17—Speeds
- F25B2700/171—Speeds of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
Abstract
A bypass valve 81 is opened until a predetermined period of time elapses after compressors 10a, 10b are stopped so as to equalize the pressure of a refrigerant circuit on a condenser 20 side with the pressure of a refrigerant circuit on an evaporator 30 side and, after the bypass valve 81 is closed, at least either of a refrigerant circuit 91 connecting to the compressor 10aand a refrigerant circuit 92 connecting to the compressor 10b is opened by opening a three-way valve 90 so that the refrigerant circuit on the condenser 20 side is made to communicate with the refrigerant circuit on the evaporator 30 side via the compressor 10 whereby, as the pressure equalized state can be maintained, it is possible to prevent the accumulation of a large amount of refrigerating machine oil on suction sides of the compressors 10 while the compressors 10 are stopped, thereby making it possible to prevent damage to the compressors 10 due to excessive compression when activated.
Description
Technical field
The present invention relates to transfer of heat on low temperature side in the refrigeration machine of high temperature side, have the vapour compression refrigerator of a plurality of compressors, very efficient when being applied to the injector circulation time.
Background technology
The injector circulation is a kind of circulation of using in vapour compression refrigerator, wherein, reduce the pressure of cold-producing medium by injector, thereby cold-producing medium is expanded, the vapor phase refrigerant of vaporizing by evaporimeter is drawn into injector, and by expansion energy be converted to pressure energy increase the suction pressure of compressor (for example, with reference to the open NO.6-11197 of Japanese unexamined patent publication No.).
By way of parenthesis, therein according to the constant enthalpy method, pressure by reducing cold-producing medium such as decompressing unit such as expansion valves (below, be called as expansion valve circulation) vapour compression refrigerator in, the cold-producing medium inflow evaporator that from expansion valve, flows out, but, in the injector circulation, the cold-producing medium that flows out from injector flows into steam-liquid separator, the liquid phase refrigerant that will produce by the separation of steam-liquid separator offers evaporimeter, simultaneously, the vapor phase refrigerant that will produce by the separation of steam-liquid separator is drawn in the compressor.
Just, the expansion valve circulation provides the flow process of cold-producing medium, and wherein, cold-producing medium is according to circulating via the sequence ground that condenser, expansion valve and evaporimeter turn back to compressor from compressor, and still, the injector circulation provides two flow processs of cold-producing medium; A flow process of cold-producing medium is: cold-producing medium is according to circulating via the sequence ground that condenser (high-pressure side heat exchanger), injector and steam-liquid separator turn back to compressor from compressor; Another flow process of cold-producing medium is: cold-producing medium is according to circulating via the sequence ground that evaporimeter and injector turn back to steam-liquid separator from steam-liquid separator.
Yet, in the injector circulation, flow into the low-pressure side heat exchanger owing to be in the cold-producing medium of saturation state, if in the injector circulation, use low-pressure side heat exchanger with the same size of the low-pressure side heat exchanger of use in the expansion valve circulation, the amount of the vapor phase refrigerant of the low-pressure side of then flowing through heat exchanger can become greater than the situation in the expansion valve circulation, therefore, compare, must increase will be enclosed in the amount of the cold-producing medium in the circulation with expansion valve circulation.
Yet, need increase the amount of the refrigerating machine oil of sneaking into cold-producing medium in conjunction with the increase on the amount of cold-producing medium, if increased the amount of the refrigerating machine oil of sneaking into cold-producing medium, also increased the amount of sneaking into the refrigerating machine oil that is mixed in the cold-producing medium of from compressor, discharging inevitably.
By way of parenthesis, refrigerating machine oil is a kind of lubricating oil, and it is used for slipper and bearing in the lubricate compressors.
In addition, if comprise the heat exchanger of cold-producing medium inflow such as the high-pressure side heat exchanger and the low-pressure side heat exchanger of a large amount of refrigerating machine oils, its kinematic viscosity is adhered on the inwall of heat exchanger greater than the refrigerating machine oil of cold-producing medium, thereby reduce the heat exchanger effectiveness of heat exchanger.Therefore, standard practice is on the discharge side of compressor, promptly, the refrigerant inlet side of high-pressure side heat exchanger, be provided for separating the oil eliminator of sneaking into the refrigerating machine oil in the cold-producing medium, thereby make the refrigerating machine oil that separates by oil eliminator via the suction side that is configured to turn back to compressor such as the oil return loop of throttling capillaceous unit.
In addition, in having the vapour compression refrigerator of a plurality of compressors, when switching all compressors wherein all when the high load operation pattern of work and in a plurality of compressor any are being worked, when vapor compression refrigerator is operated, in order to prevent to flow into the compressor of not working from the high-pressure refrigerant that compressor flows out, as shown in Figure 2, the refrigerant loop along the discharge side with each compressor 10a, 10b links to each other is provided with check-valves 10c, 10d.
In refrigeration machine shown in Figure 2, that is, comprise the refrigeration machine of following assembly, described assembly comprises: a plurality of compressor 10a, 10b are provided with respect to being used to suck with the cooling flow of compressed refrigerant is parallel; High-pressure side heat exchanger 20 is used for eliminating the heat of the high-pressure refrigerant of discharging from compressor 10a, 10b; Low-pressure side heat exchanger 30, low pressure refrigerant and absorption heat wherein are used to vaporize; Oil eliminator 70, it is arranged on the refrigerant inlet side of high-pressure side heat exchanger 20, is used for separating and extracting the refrigerating machine oil of sneaking into cold-producing medium; And oil return loop 71, be used to make the suction side that turns back to compressor 10a, 10b by the refrigerating machine oil of oil eliminator 70 separation and extraction.Be right after after stopping all a plurality of compressor 10a, 10b, pressure differential between the remaining pressure of the remaining pressure of high-pressure side heat exchanger 20 sides and low-pressure side heat exchanger 30 sides is bigger, owing on the discharge side of compressor 10a, 10b, be provided with check-valves 10c, 10d, will turn back to the suction side of compressor 10a, 10b via oil return loop 71 by oil eliminator 70 separation and the refrigerating machine oil that extracts.
Thus, because the suction side that the refrigerating machine oil that has separated by oil eliminator 70 and extracted continues to turn back to through oil return loop 71 compressor 10a, 10b, up to become at the pressure on high and the low-pressure side equal till, accumulated a large amount of refrigerating machine oils in the suction side of compressor 10a, 10b.
Then, when utilizing a large amount of refrigerating machine oils that on the suction side of compressor 10a, 10b, accumulate to start compressor 10a, 10b, because compressor 10a, 10b have picked up the refrigerating machine oil of big quantity of fluid, because liquid compression has caused the excess compression state, this probably can damage compressor 10a, 10b.
In contrast, as shown in Figure 3, be provided with here: bypass loop 80 is used in refrigerant loop on high-pressure side heat exchanger 20 sides and foundation connection between the refrigerant loop on low-pressure side heat exchanger 30 sides; And bypass valve 81, be used to open and close bypass loop 80, therefore, when stopping a plurality of compressor 10a, 10b, open bypass valve 81.Yet this structure has caused another problem as described below.
In other words, except that pressure differential, also there is bigger temperature difference at the refrigerant loop on high-pressure side heat exchanger 20 sides with between the kind of refrigeration cycle on low-pressure side heat exchanger 30 sides.
Because this situation has taken place, by opening bypass valve 81, can eliminate in refrigerant loop on high-pressure side heat exchanger 20 sides and the temperature difference between the kind of refrigeration cycle on low-pressure side heat exchanger 30 sides, so that the relatively short time period (for example, 30 seconds the order of magnitude) in, when equal pressure is provided betwixt, because high-pressure side heat exchanger 20 and low-pressure side heat exchanger 30 have relatively large thermal capacity, even under the situation that the pressure of the kind of refrigeration cycle on refrigerant loop on high-pressure side heat exchanger 20 sides and low-pressure side heat exchanger 30 sides becomes equal, can not reduce the temperature difference between the kind of refrigeration cycle on refrigerant loop on high-pressure side heat exchanger 20 sides and low voltage side heat exchanger 30 sides according to the mode identical with reducing pressure differential.
The result, by opening bypass valve 81, after pressure at the pressure of the refrigerant loop on high-pressure side heat exchanger 20 sides and the refrigerant loop on low-pressure side heat exchanger 30 sides being become equate, when closing bypass valve, as shown in Figure 4, because refrigerant loop and the temperature difference between the refrigerant loop of low-pressure side heat exchanger 30 sides on high-pressure side heat exchanger 20 sides have caused in refrigerant loop on high-pressure side heat exchanger 20 sides and the pressure differential between the refrigerant loop on low-pressure side heat exchanger 30 sides.
Thus, fully consistent in order to make as far as possible at the pressure of the pressure of the refrigerant loop on high-pressure side heat exchanger 20 sides and refrigerant loop on low-pressure side heat exchanger 30 sides, need to keep bypass valve 81 to open, up to after stopping refrigeration machine, compressor 10a, 10b have been restarted, that is, till the vapour compression refrigerator.
On the other hand, in order to prevent the operation generation problem of vapour compression refrigerator,, preferably,, adopt the normally closed type valve at bypass valve 81 even under the situation that bypass valve 81 breaks down.
Notice that in magnetic valve etc., the normally closed type valve is illustrated in the valve of cutting out and opening when powering up when not powering up.
Yet, when adopting the normally closed type valve as bypass valve 81, owing to need to give bypass valve 81 to power up, till after stopping it, having restarted this vapor compression refrigerator, dark current, promptly institute's consumed current can increase in arrestment.
Summary of the invention
Consider above-mentioned situation, the present invention has been proposed, first purpose of the present invention provides a kind of new vapour compression refrigerator that is different from traditional vapor compression formula refrigeration machine, and second purpose of the present invention is when refrigeration machine starts, and prevents owing to excess compression is damaged compressor.
In order to achieve the above object, according to an aspect of the present invention, providing a kind of is used for the vapour compression refrigerator of the transfer of heat on the low temperature side to high temperature side, this refrigeration machine comprises: with respect to a plurality of compressors (10a, 10b) that the flow process of cold-producing medium is arranged in parallel, it is used for sucking and compressed refrigerant; High-pressure side heat exchanger (20) is used for eliminating the heat from the high pressurize refrigerant that compressor (10a, 10b) is discharged; Low-pressure side heat exchanger (30) is used for absorbing heat by the evaporation low pressure refrigerant; Oil eliminator (70) is arranged on the refrigerant inlet side of high-pressure side heat exchanger (20), and this oil eliminator is used to separate and extract the refrigerating machine oil of sneaking into cold-producing medium; Oil return loop (71) is used for the cold-producing medium that separates by oil eliminator (70) and extract is sent back to the suction side of compressor (10a, 10b); Bypass loop (80) is used in refrigerant loop on high-pressure side heat exchanger (20) side and foundation connection between the refrigerant loop on low-pressure side heat exchanger (30) side; Bypass valve (81) is used to open and close bypass loop (80); Compressor valve (90) is used for opening and closing respectively the refrigerant loop (91,92) that links to each other with compressor (10a, 10b); And control module (100), be used for controlling in such a way two valves (81,90), described mode is: bypass valve (81) is stayed open, up to having passed through predetermined amount of time afterwards stopping a plurality of compressors (10a, 10b), after passing through predetermined amount of time, close bypass valve (81), open compressor valve (90) simultaneously.
Then, according to the present invention, bypass valve (81) stays open, up to having passed through predetermined amount of time afterwards stopping compressor (10a, 10b), so that equate at the pressure of the refrigerant loop on high-pressure side heat exchanger (20) side and the pressure of the refrigerant loop on low-pressure side heat exchanger (30) side, closing bypass valve (81) afterwards, open compressor valve (90), so that communicate with each other by compressor (10a, 10b) at refrigerant loop on high-pressure side heat exchanger (20) side and the refrigerant loop on low-pressure side heat exchanger (30) side.Therefore, if even between high-pressure side heat exchanger (20) side and low-pressure side heat exchanger (30) side, there is bigger temperature difference, also can prevent because temperature difference, produced pressure differential, and made refrigerating machine oil at the refrigerant loop on high-pressure side heat exchanger (20) side with mobile between the refrigerant loop on low-pressure side heat exchanger (30) side.
As a result, owing to can prevent to stop compressor (10a, 10b) simultaneously, the accumulation of a large amount of refrigerating machine oils in the time of also can preventing to start refrigeration machine, damages the danger of compressor (10a, 10b) owing to excess compression on the suction side of compressor (10a, 10b).
According to a further aspect in the invention, provide a kind of vapour compression refrigerator, this refrigeration machine comprises: with respect to a plurality of compressors (10) that the flow process of cold-producing medium is arranged in parallel, it is used for sucking and compressed refrigerant; High-pressure side heat exchanger (20) is used for eliminating the heat from the high pressurize refrigerant that compressor (10a, 10b) is discharged; Low-pressure side heat exchanger (30) is used for absorbing heat by the evaporation low pressure refrigerant; Injector (40), it has: nozzle (41), the pressure energy that is used for the high pressurize refrigerant that will flow out from high-pressure side heat exchanger (20) is converted to the speed energy, so that reduce the pressure of cold-producing medium, so that its expansion; And supercharging part (42,43), be used for locating to suck the vapor phase refrigerant of vaporizing by the high speed cold-producing medium stream that sprays from nozzle (41) at low-pressure side heat exchanger (30), and the cold-producing medium that will spray from nozzle (41) mixes mutually with the cold-producing medium that sucks from low-pressure side heat exchanger (30), so that speed can be converted to pressure energy, thereby the pressure of cold-producing medium is increased; Steam-liquid separator (50), the cold-producing medium that is used for having flowed out from injector (40) is separated into vapor phase refrigerant and liquid phase refrigerant, wherein the outlet of vapor phase refrigerant links to each other with the suction side of compressor (10a, 10b), and the outlet of liquid phase refrigerant links to each other with low-pressure side heat exchanger (30); Oil eliminator (70) is arranged on the refrigerant inlet side of high-pressure side heat exchanger (20), and this oil eliminator is used for separating and extracting the refrigerating machine oil of sneaking into cold-producing medium; Oil return loop (71) is used to make the suction side that turns back to compressor (10a, 10b) by the cold-producing medium of oil eliminator (70) separation and extraction; Bypass loop (80) is used in refrigerant loop on high-pressure side heat exchanger (20) side and foundation connection between the refrigerant loop on low-pressure side heat exchanger (30) side; Bypass valve (81) is used to open and close bypass loop (80); Compressor valve (90) is used for opening and closing respectively the refrigerant loop (91,92) that links to each other with compressor (10a, 10b); And control module (100), be used for controlling in the following manner two valves (81,90), described mode is: bypass valve (81) is stayed open, till stopping a plurality of compressors (10a, 10b) and having passed through predetermined amount of time afterwards, and after passing through predetermined amount of time, close bypass valve (81), open compressor valve (90) simultaneously.
Then, according to the present invention, bypass valve (81) stays open up to having passed through predetermined amount of time afterwards stopping compressor (10a, 10b), so that equate at the pressure of the refrigerant loop on high-pressure side heat exchanger (20) side and the pressure of the refrigerant loop on low-pressure side heat exchanger (30) side, closing bypass valve (81) afterwards, open compressor valve (90), so that communicate with each other by compressor (10a, 10b) at refrigerant loop on high-pressure side heat exchanger (20) side and the refrigerant loop on low-pressure side heat exchanger (30) side.Therefore, if even between high-pressure side heat exchanger (20) side and low-pressure side heat exchanger (30) side, there is bigger temperature difference, also can prevent because temperature difference, produce pressure differential, make refrigerating machine oil at the refrigerant loop on high-pressure side heat exchanger (20) side with mobile between the refrigerant loop on low-pressure side heat exchanger (30) side.
Therefore, because can prevent to stop compressor (10a, 10b) time, the accumulation of a large amount of refrigerating machine oils in the time of also can preventing to start refrigeration machine, damages the danger of compressor (10a, 10b) owing to excess compression on the suction side of compressor (10a, 10b).
According to the present invention, compressor valve (90) opens and closes the refrigerant loop (91,92) that links to each other with the discharge side of compressor (10a, 10b).
By way of parenthesis, the parenthesized reference number of giving above-mentioned each unit is corresponding to after a while with the particular instance of the unit described in the embodiments of the invention of describing.
With reference to the accompanying drawings and the preferred embodiments of the present invention, the present invention will more completely be understood.
Description of drawings
Fig. 1 shows the instance graph of injector circulation according to an embodiment of the invention;
Fig. 2 shows the instance graph according to the injector circulation of prior art;
Fig. 3 shows the instance graph according to the injector circulation of another prior art; And
Fig. 4 shows the curve map according to the pressure characteristic of the injector circulation of prior art.
The specific embodiment
In an embodiment of the present invention, will injector cycle applications according to the present invention in vapour compression refrigerator, described refrigeration machine need be reduced in and be used at the cabinet of preservation Food ﹠ Drink under refrigeration and the freezing condition or be used for transporting temperature with the refrigerating box of the refrigeration instrument of the Food ﹠ Drink preserved under the refrigeration of the temperature that is lower than air conditioner and the freezing condition.
In addition, injector 40 comprises: nozzle 41, be used for according to the constant enthalpy method, and the pressure energy that flows into high-pressure refrigerant wherein is converted to the speed energy, so that reduce the pressure of cold-producing medium; Standing part 42 is used for the cold-producing medium stream by the high speed of injecting from nozzle 41, through the effect of entrainmenting (entrainment action), sucks the cold-producing medium of having vaporized at evaporimeter 30 places, so that mix with the cold-producing medium stream that injects from nozzle 41; Diffuser 43 is used for and will mixes from the cold-producing medium of nozzle 41 injections and the cold-producing medium that sucks from evaporimeter 30, so that speed can be converted to pressure energy, thus the pressure of increase cold-producing medium.
Because this situation has taken place, at mixing portion 42 places, owing to drive stream and inlet flow is mixed with each other, thereby kept driving the summation of the momentum of the summation of the momentum that flows and inlet flow, at mixing portion 42 places, also increased the pressure (static pressure) of cold-producing medium.
On the other hand, at diffuser 43 places, owing to, make the speed of cold-producing medium (dynamic pressure) be converted to pressure energy (static pressure), increased the pressure of the cold-producing medium at mixing portion 42 in injector 40 and diffuser 43 places by the cross-sectional area of extended channel gradually.Therefore, hereinafter, mixing portion 42 and diffuser 43 common names are made the supercharging part.
By way of parenthesis, in this example, for accelerating to, the speed of falling from nozzle 41 cold-producing medium that injects equals or faster than the speed of velocity of sound, although adopted a position that has along passage length, aisle spare is decreased to Laval (Laval) nozzle (reference fluid engineering (Tokyo University publishes association)) of the throat portion of minimum of a value, but, needless to say, can adopt conical nozzle.
In addition, steam-liquid separator 50 is steam-fluid separation applications unit, the cold-producing medium that flows out from injector 40 flows in this steam-fluid separation applications unit, and this steam-liquid separator 50 is applicable to by cold-producing medium being separated into the cold-producing medium that vapor phase refrigerant and liquid phase refrigerant are stored such inflow, and the outlet at the vapor phase refrigerant of steam-liquid separator 50 links to each other with the suction side of compressor 10, but, link to each other with evaporimeter 30 sides at the outlet of the liquid phase refrigerant of steam-liquid separator 50.
Specifically, this variable restrictor unit 60 can comprise: valve element 61 is used to change the opening of throttling; Membranaceous dividing plate 63 has constituted between back pressure 62, presses in wherein to change by the refrigerant temperature of perception on the refrigerant outlet side of evaporimeter 30; Connecting rod 64 is used for valve element 61 is linked to each other with dividing plate 63, so that transmit the displacement of dividing plate 63; Spring 65 is suitable for reducing between back pressure to apply spring pressure on the direction of 62 capacity; And outer balance pipe 67, be used for the pressure at the cold-producing medium on the refrigerant outlet side of evaporimeter 30 is incorporated into and be positioned at and pass between dividing plate 63 and back pressure between 62 opposite pressure 66.
Notice that 62 are connected with the temperature-sensitive pipe that is used for the refrigerant temperature of perception on the refrigerant outlet side of evaporimeter 30 between back pressure, thus, will be delivered between back pressure 62 via the temperature-sensitive pipe in the temperature of the cold-producing medium on the refrigerant outlet side of evaporimeter 30.
Thus, reduce the opening of the throttling of variable restrictor unit 60, to improve the speed of the driving stream that from nozzle 41, injects, thereby the pressure in evaporimeter 30, when being the thermic load generation increase in the evaporimeter 30, increase inlet flow or in evaporimeter 30 amount of the cold-producing medium of circulation, thus, the degree of superheat of the cold-producing medium on the outlet side of evaporimeter 30 is increased.Otherwise, when the pressure in the evaporimeter 30 reduces, thus, the degree of superheat of the cold-producing medium on the outlet side of evaporimeter 30 reduces, variable restrictor unit 60 increases the opening of its throttling, lowering the speed of the driving stream that from nozzle 41, injects, thereby reduced the amount of the cold-producing medium of circulation in evaporimeter 30.
Note,, have a kind of centrifugal separation,, from cold-producing medium, separate refrigerating machine oil by rotating the cold-producing medium of wherein having sneaked into refrigerating machine oil at high speed as oil eliminator; And there is a kind of collision partition method,, from cold-producing medium, separates refrigerating machine oil by making the cold-producing medium of wherein having sneaked into refrigerating machine oil with respect to the wall surface high velocity impact.In the present embodiment, adopted centrifugal separation system.
Note, this oil return loop 71 is provided with, thereby produced the pressure loss of summation of the decompression amount of the decompression amount that equals nozzle 41 in fact and variable restrictor unit 60.
Note, in the present embodiment, the high-pressure side of bypass loop 80 links to each other with refrigerant loop on condenser 20 sides of the position between condenser 20 and the oil eliminator 70, and the low-pressure side of bypass loop 80 links to each other with refrigerant loop on evaporimeter 30 sides of the position between steam-liquid separator 50 and the evaporimeter 30.
Triple valve 90 is a kind of compressor valves that are used for opening and closing respectively the refrigerant loop 91,92 that links to each other with compressor 10a, 10b.This triple valve 90 is a kind of electric valves that switch between following situation, and described situation is: the refrigerant loop 91 that links to each other with compressor 10a is opened and the refrigerant loop 92 that links to each other with compressor 10b is closed situation; The refrigerant loop 91 that links to each other with compressor 10a is closed and the refrigerant loop 92 that links to each other with compressor 10b is opened situation; And refrigerant loop 91,92 situation about all opening.
Note, in the present embodiment, although triple valve 90 is arranged in the side of converging of refrigerant loop 91,92, that is, the discharge side of compressor 10a, 10b, still, triple valve 90 also can be arranged in branch's side of refrigerant loop 91,92, the i.e. suction side of compressor 10a, 10b.
Then, control the operation of bypass valve 81 and triple valve 90, and will be input to electronic control unit 100 from the signal of the speed probe 101,102 of the rotating speed that is used to detect compressor 10a, 10b by electronic control unit 100.
Notice that this electronic control unit 100 detects compressor 10a, 10b and whether stops according to the rotating speed by speed probe 101,102 detected compressor 10a, 10b.
Next, will the operation of injector circulation be described briefly.
1. basic operation
This operation is a kind of operator scheme that is used for producing at evaporimeter 30 places refrigeration capacity.
Specifically, make the cold-producing medium of discharging be recycled to condenser 20 sides, thus,,, make the pressure of the high pressurize refrigerant of cooling off at condenser 20 places be reduced to steam-liquid two-phase zone by variable restrictor unit 60 according to the constant enthalpy method from compressor 10.Afterwards,,, the above-mentioned pressure that has reduced the cold-producing medium of pressure is reduced, thus, cold-producing medium is expanded, thereby cold-producing medium is flowed in the mixing portion 42 with ultrasonic speed by the nozzle 41 of injector 40 according to the constant enthalpy method.
In the present embodiment, when this happens, cold-producing medium once seethed with excitement at 60 places, variable restrictor unit, and cold-producing medium expands in the inlet portion office of nozzle 41, so that pressure recovers, thus, cold-producing medium can be seethed with excitement at second level nozzle place, continue to produce boiling atomic nucleus (boilng nucleus) simultaneously.Therefore, can be lifted at the boiling point of the cold-producing medium at nozzle 41 places, so that improve ejector efficiency η e by cold-producing medium being dripped become particulate.
By way of parenthesis, the product that flows through the mass flowrate Gn of cold-producing medium of condenser 20 and the enthalpy difference Δ ie between the outlet of nozzle 41 and inlet by utilization is as denominator, utilize expression since 10 works of compressor recover the degree of energy refrigerant flow rate Gn, flow through evaporimeter 30 cold-producing medium mass flowrate Ge and in the summation of the pressure recovery Δ P at injector 40 places as molecule, define ejector efficiency η e.
Notice that in the present embodiment, used chlorofluorocarbon as cold-producing medium, and made the high-pressure side refrigerant pressure, promptly the pressure of the cold-producing medium of flow nozzle is equal to or less than the critical pressure of cold-producing medium.
On the other hand, owing to produced swabbing action explicitly (with reference to the Z of Japanese Industrial Standards (JIS) 8126 by the effect of entrainmenting with the high speed cold-producing medium that flows into mixing portion 42,2.1.2.3 etc.), make the cold-producing medium of the vaporization in evaporimeter 30 be inhaled into mixing portion 42, make cold-producing medium on low-pressure side according to circulating via the sequence ground that evaporimeter 30 and injector 40 (supercharging part) turn back to steam-liquid separator 50 from steam-liquid separator 50.
Then, when the cold-producing medium (driving stream) of cold-producing medium (inlet flow) that sucks from evaporimeter 30 and ejection from nozzle 41 mixes in mixing portion 42, make the dynamic pressure of the cold-producing medium that has mixed convert static pressure to by diffuser 43, and then, make cold-producing medium turn back to steam-liquid separator 50.
Notice that when cooling load was big, as the situation that shows bigger refrigeration capacity at evaporimeter 30 places, perhaps the external temperature condition with higher was operated two compressor 10a, 10b simultaneously; And when cooling load hour, only one of operate compressor 10a, 10b (for example, compressor 10a).
2. refrigeration machine stop mode
This operator scheme is used for carrying out under the situation that compressor 10a, 10b stop.
Specifically, electronic control unit 100 continues to power up to bypass valve 81, up to after compressor 10a, 10b stop, (for example having passed through predetermined amount of time, 30 seconds) so that till bypass loop 80 opens, and, when passing through predetermined amount of time, electronic control unit 100 cuts off powering up of bypass valve 81, so that bypass loop 80 is closed, and open triple valve 90, thus, opened the refrigerant loop 91 that links to each other with compressor 10a with refrigerant loop 92 that compressor 10b links to each other at least one.
Next, the function and the advantage of present embodiment below will be described.
In the present embodiment, bypass valve is opened, up to from compressor 10a, after stopping, having passed through 10b predetermined amount of time, so that at the pressure of the refrigerant loop on condenser 20 sides with till the pressure of the refrigerant loop on evaporimeter 30 sides equates, and, after closing bypass valve 81, open triple valve 90, thereby open at least the refrigerant loop 91 that links to each other with compressor 10a with refrigerant loop 92 that compressor 10b links to each other in any, be communicated with thereby set up via compressor 10 at the refrigerant loop on condenser 20 sides with between the refrigerant loop on evaporimeter 30 sides.Thus, if even under the bigger situation of the temperature difference between condenser 20 sides and evaporimeter 30 sides, also can prevent because temperature difference has produced pressure differential, and refrigerating machine oil is flowed at the refrigerant loop on condenser 20 sides with between the refrigerant loop on evaporimeter 30 sides.
Just, present embodiment has following mode: when stopping compressor 10a, 10b, at first, bypass valve 81 is opened, so that equate with the pressure of refrigerant loop on evaporimeter 30 sides, afterwards, make at the refrigerant loop on condenser 20 sides to communicate with each other by the refrigerant loop 91,92 that links to each other with compressor 10 with refrigerant loop on evaporimeter 30 sides at the pressure of the refrigerant loop on condenser 20 sides, thus, the pressure state that keeps balance.
As a result, owing to can when stopping compressor, prevent the accumulation of a large amount of refrigerating machine oils on the suction side of compressor 10, therefore, when starting, can prevent that the danger that damages compressor 10 owing to excess compression from occurring.
In the present embodiment, although compressor 10a, 10b utilize the energy that obtains from motor to suck and compressed refrigerant, but, the invention is not restricted to this, compressor 10a, 10b also can suck by the energy that obtains from the engine such as internal combustion engine and compressed refrigerant.
In addition, in the present embodiment, although the present invention is applied to the cabinet of maintenance Food ﹠ Drink under refrigeration and freezing condition etc., application of the present invention is not limited to this, and for example, the present invention also can be applied to be used for the vapour compression refrigerator of air-conditioning.
In addition, in the present embodiment,, press balanced type temperature expansion valve in also can adopting as variable restrictor unit 60 although adopted external pressure balanced type temperature expansion valve as the variable restrictor unit.
In addition, in the present embodiment,, the invention is not restricted to this, for example, variable restrictor unit 60 and nozzle 41 are integrated in the individual unit although be provided with variable restrictor unit 60 and nozzle 41 discretely.
In addition, in the description of prior art, though be to be described by comparing expansion valve circulation and spraying cycle, also more or less foregoing problems can occur in the expansion valve circulation, therefore, the present invention can be applied to the expansion valve circulation.
In addition, in the present embodiment, although compressor valve is made up of triple valve 90, but the present invention is not limited to this, for example, also can by along the refrigerant loop 91 that links to each other with compressor 10a with refrigerant loop 92 that compressor 10b links to each other in each length the electronic switch valve is set, form compressor valve.
Although in order to illustrate, the present invention has been described by the selected specific embodiment of reference,, what it should be obvious that is that those skilled in the art can carry out various modifications to it under the situation that does not break away from basic conception of the present invention and scope.
Claims (4)
1. one kind is used for the vapour compression refrigerator of the transfer of heat on the low temperature side to high temperature side comprised:
With respect to a plurality of compressors that the flow process of cold-producing medium is arranged in parallel, be used for sucking and compressed refrigerant;
The high-pressure side heat exchanger is used for eliminating the heat of the high pressurize refrigerant of discharging from compressor;
The low-pressure side heat exchanger is used for absorbing heat by the evaporation low pressure refrigerant;
Oil eliminator is arranged on the refrigerant inlet side of high-pressure side heat exchanger, is used for separating and extracting the refrigerating machine oil of sneaking into cold-producing medium;
The oil return loop is used to make the suction side that is turned back to compressor by the cold-producing medium of oil eliminator separation and extraction;
Bypass loop is used in refrigerant loop on the heat exchanger side of high-pressure side and foundation connection between the refrigerant loop on the low-pressure side heat exchanger side;
Bypass valve is used to open and close bypass loop;
Compressor valve is used for opening and closing respectively the refrigerant loop that links to each other with compressor; And
Control module is used for controlling in such a way two valves, and described mode is: bypass valve is stayed open, after stopping a plurality of compressors, pass through till the predetermined amount of time, and after passing through predetermined amount of time, close bypass valve, open compressor valve simultaneously.
2. vapour compression refrigerator according to claim 1 is characterized in that, described compressor valve opens and closes the refrigerant loop that links to each other with the discharge side of described compressor.
3. vapour compression refrigerator comprises:
With respect to a plurality of compressors (10) that the flow process of cold-producing medium is arranged in parallel, be used for sucking and compressed refrigerant;
The high-pressure side heat exchanger is used for eliminating the heat of the high pressurize refrigerant of discharging from compressor;
The low-pressure side heat exchanger is used for absorbing heat by the evaporation low pressure refrigerant;
Injector has: nozzle, and the pressure energy that is used for the high pressurize refrigerant that will flow out from the high-pressure side heat exchanger is converted to the speed energy, to reduce the pressure of cold-producing medium, so that its expansion; And supercharging part, be used in the vapor phase refrigerant of low-pressure side heat exchanger place suction by the high speed cold-producing medium stream vaporization of injecting from nozzle, and the cold-producing medium that will inject from nozzle mixes mutually with the cold-producing medium that sucks from the low-pressure side heat exchanger, so that speed can be converted to pressure energy, thereby the pressure of cold-producing medium is increased;
Steam-liquid separator, the cold-producing medium that is used for flowing out from injector is separated into vapor phase refrigerant and liquid phase refrigerant, and wherein, the outlet of vapor phase refrigerant links to each other with the suction side of compressor, and the outlet of liquid phase refrigerant links to each other with the low-pressure side heat exchanger;
Oil eliminator is arranged on the refrigerant inlet side of high-pressure side heat exchanger, is used for separating and extracting the refrigerating machine oil of sneaking into cold-producing medium;
The oil return loop is used to make the suction side that is turned back to compressor by the cold-producing medium of oil eliminator separation and extraction;
Bypass loop is used in refrigerant loop on the heat exchanger side of high-pressure side and foundation connection between the refrigerant loop on the low-pressure side heat exchanger side;
Bypass valve is used to open and close bypass loop;
Compressor valve is used for opening and closing respectively the refrigerant loop that links to each other with compressor; And
Control module is used for controlling in such a way two valves, and described mode is: bypass valve is stayed open, after stopping a plurality of compressors, pass through till the predetermined amount of time, and after passing through predetermined amount of time, close bypass valve, open compressor valve simultaneously.
4. vapour compression refrigerator according to claim 3 is characterized in that, described compressor valve opens and closes the refrigerant loop that links to each other with the discharge side of described compressor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003287719A JP4023415B2 (en) | 2003-08-06 | 2003-08-06 | Vapor compression refrigerator |
| JP2003287719 | 2003-08-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1580671A true CN1580671A (en) | 2005-02-16 |
| CN100498138C CN100498138C (en) | 2009-06-10 |
Family
ID=34114023
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100558620A Expired - Fee Related CN100498138C (en) | 2003-08-06 | 2004-08-04 | Vapor compression type refrigerating machine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20050028552A1 (en) |
| JP (1) | JP4023415B2 (en) |
| CN (1) | CN100498138C (en) |
| DE (1) | DE102004036718B4 (en) |
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| CN101400952B (en) * | 2006-02-07 | 2011-06-15 | 布鲁克斯自动化有限公司 | Methods of freezeout prevention for very low temperature mixed refrigerant systems |
| CN105716324A (en) * | 2016-03-16 | 2016-06-29 | 北京建筑大学 | Double-heat-source efficient air conditioner system based on compression-injection combination and application |
| CN106969558A (en) * | 2017-04-21 | 2017-07-21 | 美的集团股份有限公司 | The heat-exchange method of refrigeration system and refrigeration system |
| WO2018082347A1 (en) * | 2016-11-02 | 2018-05-11 | 重庆美的通用制冷设备有限公司 | Water chilling unit |
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| JP4631721B2 (en) * | 2005-08-04 | 2011-02-16 | 株式会社デンソー | Vapor compression refrigeration cycle |
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-
2004
- 2004-07-29 DE DE102004036718A patent/DE102004036718B4/en not_active Expired - Fee Related
- 2004-08-03 US US10/909,547 patent/US20050028552A1/en not_active Abandoned
- 2004-08-04 CN CNB2004100558620A patent/CN100498138C/en not_active Expired - Fee Related
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| CN106969558A (en) * | 2017-04-21 | 2017-07-21 | 美的集团股份有限公司 | The heat-exchange method of refrigeration system and refrigeration system |
| CN113310243A (en) * | 2021-05-21 | 2021-08-27 | 西安交通大学 | Mixed working medium low-temperature refrigeration cycle system adopting ejector and control method |
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Also Published As
| Publication number | Publication date |
|---|---|
| US20050028552A1 (en) | 2005-02-10 |
| JP2005055113A (en) | 2005-03-03 |
| DE102004036718A1 (en) | 2005-05-25 |
| JP4023415B2 (en) | 2007-12-19 |
| DE102004036718B4 (en) | 2010-12-16 |
| CN100498138C (en) | 2009-06-10 |
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