CN102538269B - Compression refrigerating machine - Google Patents
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- CN102538269B CN102538269B CN201110449013.3A CN201110449013A CN102538269B CN 102538269 B CN102538269 B CN 102538269B CN 201110449013 A CN201110449013 A CN 201110449013A CN 102538269 B CN102538269 B CN 102538269B
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- 230000006835 compression Effects 0.000 title claims abstract description 103
- 238000007906 compression Methods 0.000 title claims abstract description 103
- 239000003507 refrigerant Substances 0.000 claims abstract description 104
- 239000007788 liquid Substances 0.000 claims abstract description 82
- 238000005057 refrigeration Methods 0.000 claims abstract description 51
- 238000001816 cooling Methods 0.000 claims description 9
- 239000003795 chemical substances by application Substances 0.000 claims description 7
- 238000001704 evaporation Methods 0.000 claims description 5
- 238000009833 condensation Methods 0.000 description 35
- 230000005494 condensation Effects 0.000 description 35
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 11
- 239000000498 cooling water Substances 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 238000002309 gasification Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 230000002411 adverse Effects 0.000 description 4
- 239000007791 liquid phase Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000012544 monitoring process Methods 0.000 description 2
- OHMHBGPWCHTMQE-UHFFFAOYSA-N 2,2-dichloro-1,1,1-trifluoroethane Chemical compound FC(F)(F)C(Cl)Cl OHMHBGPWCHTMQE-UHFFFAOYSA-N 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
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Abstract
The invention provides a kind of and compression refrigerating machine of cheapness higher than existing two-stage refrigeration circulation compression-type refrigeration engine efficiency.This compression refrigerating machine has two-stage refrigeration circulation, comprise high pressure condenser (22), low-pressure condenser (20), high pressure evaporator (14), low pressure evaporator (12), the compressor (18) be connected with high pressure condenser (22), and the compressor (16) to be connected with low-pressure condenser (20), low-pressure condenser (20) will be imported by the condensed refrigerant liquid of high pressure condenser (22), and between the compressor (18) be connected with high pressure condenser (22) and high pressure condenser (22), between the compressor (16) be connected with low-pressure condenser (20) and low-pressure condenser (20), or between high pressure condenser (22) and low-pressure condenser (20) at least any one is provided with control valve (V1, V2).
Description
Technical field
The present invention relates to compression refrigerating machine, particularly relate to the high performance compression formula refrigeration machine with two-stage refrigeration circulation.
Background technology
Fig. 8 is this figure with the schematic configuration example of the compression refrigerating machine of two-stage refrigeration circulation represented in the past.As shown in the drawing, this compression refrigerating machine 100 comprises low side evaporator 101, high-pressure side evaporimeter 102, low-pressure side compressor 103, high side compressors 104, low-pressure side condenser 105, high-pressure side condenser 106, low-pressure side expansion valve 107 and high-pressure side expansion valve 108.
The refrigerant vapour evaporated by low side evaporator 101 is sent to low-pressure side compressor 103 and is compressed, this is become condensation of refrigerant liquid at low-pressure side condenser 105 by compressing by the refrigerant vapour compressed, this condensation of refrigerant liquid is sent to low side evaporator 101 via low-pressure side expansion valve 107, forms low-pressure side kind of refrigeration cycle.In addition, the refrigerant vapour evaporated by high-pressure side evaporimeter 102 is sent to high side compressors 104 and is compressed, this is become condensation of refrigerant liquid at high-pressure side condenser 106 by compressing by the refrigerant vapour compressed, this condensation of refrigerant liquid is sent to high-pressure side evaporimeter 102 via high-pressure side expansion valve 108, forms high-pressure side kind of refrigeration cycle.
The pipe arrangement that low-pressure side condenser 105 and high-pressure side condenser 106 utilize Cooling Water 110 to pass through and being communicated with, low side evaporator 101 is communicated with by the pipe arrangement passed through for cold water 120 with high-pressure side evaporimeter 102, cooling water 110 flows to high-pressure side condenser 106 from low-pressure side condenser 105, and cold water 120 flows to low side evaporator 101 from high-pressure side evaporimeter 102.At low side evaporator 101 and high-pressure side evaporimeter 102, obtain heat from cold water 120 and cold-producing medium is evaporated, cold water 120 is cooled.In addition, at low-pressure side condenser 105 and high-pressure side condenser 106, the compressed refrigerant water 110 that is cooled cools and becomes condensation of refrigerant liquid.
The compression refrigerating machine of two-stage refrigeration circulation is normally communicated with high-pressure side kind of refrigeration cycle and these 2 kind of refrigeration cycle of low-pressure side kind of refrigeration cycle by cold water and cooling water, and reduce the compression lift of the wherein kind of refrigeration cycle of one or both, thus seek energy-conservation refrigeration machine.Have several pattern according to its method of attachment etc., but the component equipment such as condenser, evaporimeter, compressor, intercooler, expansion valve, subcooler respectively needs 2 substantially.These cause very large burden to cost.
And, when the equipment such as kind of refrigeration cycle and motor are communicated with, need to detect being biased and revising of cold-producing medium.And, although two-stage refrigeration circulation itself is the kind of refrigeration cycle that efficiency is very high, but still wish high efficiency more.
Patent document 1: Japanese Unexamined Patent Publication 2009-236428 publication
Summary of the invention
But in the prior art, as mentioned above, the component equipments such as condenser, evaporimeter, compressor, intercooler, expansion valve, subcooler respectively need 2, there is problem cost being caused to very large burden, can not tackle high efficiency more.And, when only making 1 compressor running, need many control valves, and the next door that there is condenser needs the higher problem such as withstand voltage.In addition, as correct cold-producing medium biased, can at the compression refrigerating machine carrying out high efficiency running in a big way of (low loading condition) from nominal load to fractional load, have the refrigeration machine introduced in patent document 1, but the cost that this refrigeration machine can not seek two-stage refrigeration circulation compression refrigerating machine reduces and improved efficiency.
The present invention puts in view of the above problems and makes, and its object is to provide a kind of and existing two-stage refrigeration circulation compression refrigerating machine phase specific efficiency high and the compression refrigerating machine of cheapness.The present invention also aims to the compression refrigerating machine of the efficiency of refrigeration machine when the low load of a kind of energy raising is provided.
In order to solve above-mentioned problem, the invention provides a kind of compression refrigerating machine with two-stage refrigeration circulation, comprise high pressure condenser, low-pressure condenser, at least more than one evaporimeter, the compressor be connected with high pressure condenser, and the compressor to be connected with low-pressure condenser, wherein, low-pressure condenser will be imported by the condensed refrigerant liquid of high pressure condenser, and between the compressor be connected with high pressure condenser and high pressure condenser, between the compressor be connected with low-pressure condenser and low-pressure condenser, and between high pressure condenser and low-pressure condenser at least any one is provided with control valve.
The present invention also provides a kind of compression refrigerating machine with two-stage refrigeration circulation, it comprises high pressure condenser, low-pressure condenser, high pressure evaporator, low pressure evaporator, the high pressure compressor be connected with above-mentioned high pressure condenser, and the low pressure compressor to be connected with above-mentioned low-pressure condenser, wherein, refrigerant liquid from above-mentioned high pressure evaporator is sent to above-mentioned low pressure evaporator via throttle orifice or valve, refrigerant liquid from above-mentioned low-pressure condenser is sent to above-mentioned high pressure evaporator via valve, refrigerant liquid by above-mentioned high pressure condenser condensation is imported above-mentioned low-pressure condenser via throttle orifice or valve, and between the compressor be connected with above-mentioned high pressure condenser and above-mentioned high pressure condenser, between the compressor be connected with above-mentioned low-pressure condenser and above-mentioned low-pressure condenser, and between above-mentioned high pressure condenser and above-mentioned low-pressure condenser at least any one is provided with control valve.
The present invention is in above-mentioned compression refrigerating machine, and evaporimeter is made up of high pressure evaporator and low pressure evaporator.
The present invention, in above-mentioned compression refrigerating machine, arranges the intercooler of cooling refrigeration agent in the outlet of low-pressure condenser.
Refrigerant vapour from intercooler, in above-mentioned compression refrigerating machine, is imported the middle suction inlet of the compressor be connected with low-pressure condenser by the present invention.
The present invention is in above-mentioned compression refrigerating machine, the compressor be connected with low-pressure condenser is the low lift compressor refrigerant vapor compression of high pressure evaporator being sent to low-pressure condenser, the compressor be connected with high pressure condenser is the high-lift compressor refrigerant vapor compression of low pressure evaporator being sent to high pressure condenser, the intercooler of cooling refrigeration agent is set in the outlet of low-pressure condenser, the refrigerant vapour of this intercooler is imported the middle suction inlet of low lift compressor.
The present invention is in above-mentioned compression refrigerating machine, with next door, single tank body separated up and down and be configured to upper chambers and bottom compartment, at upper chambers configuration high pressure condenser, and at bottom compartment configuration low-pressure condenser, next door providing holes, carries out from high pressure condenser to the hole being directed through next door setting of the cold-producing medium of low-pressure condenser.
The present invention is in above-mentioned compression refrigerating machine, and the cold-producing medium being supplied to low pressure evaporator is the cold-producing medium being cooled to the evaporating temperature of this high pressure evaporator at high pressure evaporator.
The present invention, in above-mentioned compression refrigerating machine, arranges the intercooler of cooling refrigeration agent at the entrance of high pressure evaporator.
The present invention is in above-mentioned compression refrigerating machine, and high pressure evaporator and low pressure evaporator are configured on single tank body.
The present invention, in above-mentioned compression refrigerating machine, arranges overflow dike at high pressure evaporator, and the cold-producing medium being configured to cross overflow dike flows into low pressure evaporator.
In the present invention, refrigerant liquid by high pressure condenser condensation is imported low-pressure condenser, and between the compressor be connected with high pressure condenser and high pressure condenser, between the compressor be connected with low-pressure condenser and low-pressure condenser, or between high pressure condenser and low-pressure condenser at least any one arranges control valve, or, the compressor be connected with low-pressure condenser is the low lift compressor refrigerant vapor compression of high pressure evaporator being sent to low-pressure condenser, the compressor be connected with high pressure condenser is the high-lift compressor refrigerant vapor compression of low pressure evaporator being sent to high pressure condenser, the intercooler of cooling refrigeration agent is set in the outlet of low-pressure condenser, the refrigerant vapour of this intercooler is imported the middle suction inlet of low lift compressor, refrigerant liquid by high pressure condenser condensation is imported low-pressure condenser, therefore on high-tension side condensation of refrigerant liquid is by partial gasification, be cooled to the temperature same with the condensation of refrigerant liquid phase of low-pressure side, because the refrigerant vapour after gasification is in low-pressure condenser condensation, therefore the burden of refrigeration machine can not in fact be increased.
In addition, because the cold-producing medium flowing into low pressure evaporator is cooled to the saturation temperature of high pressure evaporator, therefore the load of low pressure evaporator diminishes.And the equipment such as intercooler, expansion valve, with 1, can obtain following effect thus, that is: can provide a kind of and existing and there is cheapness compared with compression refrigerating machine that two-stage refrigeration circulates and the higher compression refrigerating machine of efficiency.
And, by the control valve of operation setting between compressor and condenser, can only with a certain of 2 compressors, refrigeration machine be operated when low load.Thereby, it is possible to the efficiency of refrigeration machine when improving low load.
Accompanying drawing explanation
Fig. 1 is the figure of the schematic configuration example representing compression refrigerating machine of the present invention.
Fig. 2 represents the figure by the structure of the fit condenser of high pressure condenser and low-pressure condenser.
Fig. 3 represents the figure by the structure of the fit evaporimeter of high pressure evaporator and low pressure evaporator.
Fig. 4 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.
Fig. 5 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.
Fig. 6 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.
Fig. 7 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.
Fig. 8 is the figure with the schematic configuration example of the compression refrigerating machine of two-stage refrigeration circulation represented in the past.
the explanation of Reference numeral
10-1 ~ 4 compression refrigerating machine
12 low pressure evaporators
13 evaporimeters
14 high pressure evaporators
16 low pressure compressors
16 ' low pressure compressor
17 high-lift compressors
18 high pressure compressors
18 ' high pressure compressor
19 low lift compressors
20 low-pressure condensers
22 high pressure condensers
24 throttle orifices
26 expansion valves
28 liquid level detectors
30 liquid level detectors
32 movements of valve
34 condensers
35 tank bodies (shell)
36 next doors
38 subcoolers
40 evaporimeters
41 tank bodies (shell)
42 next doors
44 overflow dikes
46 throttle orifices
48 intercoolers (energy-saving appliance)
50 throttle orifices
V1 ~ V5 control valve
Detailed description of the invention
Below, embodiments of the present invention are described in detail.Fig. 1 is the figure of the schematic configuration example representing compression refrigerating machine of the present invention.As shown in the figure, this compression refrigerating machine 10-1 comprises low pressure evaporator (EL) 12, high pressure evaporator (EH) 14, low pressure compressor 16, high pressure compressor 18, low-pressure condenser (CL) 20 and high pressure condenser (CH) 22.Each equipment is connected by refrigerant piping, and low pressure compressor 16 and high pressure compressor 18 are by drive motor M rotary actuation independently.
The refrigerant vapour evaporated by low pressure evaporator 12 is sent to low pressure compressor 16 and is compressed, this is flowed into low-pressure condenser 20 by the refrigerant vapour compressed by control valve V2 and is condensed, become condensation of refrigerant liquid, this condensation of refrigerant liquid is sent to high pressure evaporator 14 by expansion valve 26.The refrigerant vapour evaporated by this high pressure evaporator 14 is sent to high pressure compressor 18 and is compressed, this is sent to high pressure condenser 22 by the refrigerant vapour compressed by control valve V1 and is condensed, become condensation of refrigerant liquid, this condensation of refrigerant liquid is imported into low-pressure condenser 20 by throttle orifice 24.
In addition, although the diagram of eliminating, same with Fig. 8, the pipe arrangement that high pressure condenser 22 and low-pressure condenser 20 utilize Cooling Water to pass through and being communicated with, low pressure evaporator 12 and high pressure evaporator 14 utilize the pipe arrangement that passes through for cold water and are communicated with, cooling water flows to high pressure condenser 22 from low-pressure condenser 20, and cold water flows to low pressure evaporator 12 from high pressure evaporator 14.In high pressure evaporator 14 and low pressure evaporator 12, obtain heat from cold water and cold-producing medium is evaporated, cold water is cooled.In addition, in low-pressure condenser 20 and high pressure condenser 22, compressed refrigerant is cooled water cooling and become condensation of refrigerant liquid.
In this compression refrigerating machine 10-1, as mentioned above, low-pressure condenser 20 is sent to by the refrigerant liquid of high pressure condenser 22 condensation by throttle orifice 24.Also can arrange overcooled for cold-producing medium subcooler 38 (with reference to Fig. 2) at low-pressure condenser 20.High pressure evaporator 14 is sent to after being expanded by expansion valve 26 by the condensed refrigerant liquid of low-pressure condenser 20.At low pressure evaporator 12 and high pressure evaporator 14, there is liquid level detector (LV) 28, liquid level detector (LV) 30 respectively, control the aperture of expansion valve 26 and movement of valve 32 to make the cold-producing medium liquid level constant height of low pressure evaporator 12 and high pressure evaporator 14.Specifically, the change of the liquid level of low pressure evaporator 12 is detected with liquid level detector 28, by controlling the aperture of movement of valve 32, thus adjustment is from high pressure evaporator 14 to the refrigerant amount of low pressure evaporator 12 movement, the cold-producing medium liquid level of high pressure evaporator 14 is detected with liquid level detector 30, by controlling the aperture of expansion valve 26, thus adjustment is from low-pressure condenser 20 to the condensation of refrigerant liquid measure of high pressure evaporator 14 movement, makes the cold-producing medium liquid level constant height of low pressure evaporator 12 and high pressure evaporator 14.
Fig. 2 represents the figure by the structure of the condenser of high pressure condenser 22 and low-pressure condenser 20 zoarium.As shown in the figure, the structure of condenser 34 is: separated by single tank body (shell) about 35 with next door 36, clip this ground, next door 36 at upper chambers configuration high pressure condenser 22, in bottom compartment configuration low-pressure condenser 20, high pressure condenser 22 and low-pressure condenser about 20 collapsed configuration.Next door 36 is provided with the aperture 36a played a role as throttle orifice 24, and by this aperture 36a, cold-producing medium moves to low-pressure condenser 20 from high pressure condenser 22.The size of aperture 36a designs according to high pressure condenser 22 and the pressure differential of low-pressure condenser 20 and the amount of condensation of refrigerant liquid, even if but it is usually slightly larger, the specific volume of steam is much larger compared with liquid, especially as in HFC245fa, HCFC123 of low pressure refrigerant, the channelling amount of refrigerant vapour is little, therefore little on the impact of performance.And, due to usually when there being pressure differential condensation of refrigerant liquid measure become many, therefore in discharge characteristic, channelling amount is automatically suppressed.
Fig. 3 represents the figure by the structure of the evaporimeter 40 of high pressure evaporator 14 and low pressure evaporator 12 zoarium.
As shown in Figure 3, evaporimeter 40 next door 42 is separated in single tank body (shell) 41, clips this ground, next door 42 by high pressure evaporator 14 and low pressure evaporator 12 horizontal arrangement.High pressure evaporator 14 is adjacent across overflow dike 44 with low pressure evaporator 12, from high pressure evaporator 14 cross overflow dike 44 and overflow refrigerant liquid move to low pressure evaporator 12 by being located at the aperture 42a in next door 42.Now, the cold-producing medium channelling from aperture 42a is automatically suppressed.
Fig. 4 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.As shown in the figure, to comprise low pressure evaporator 12, high pressure evaporator 14, low pressure compressor 16, high pressure compressor 18, low-pressure condenser 20 and high pressure condenser 22 this point same with compression refrigerating machine 10-1 for this compression refrigerating machine 10-2.But, replace throttle orifice 24 and control valve V3 be set between high pressure condenser 22 and low-pressure condenser 20.This control valve V3 is except carrying out except opening and closing operations, identical with throttle orifice 24.
In the compression refrigerating machine 10-1 shown in Fig. 1, monitor the cold-producing medium liquid level of high pressure evaporator 14 and low pressure evaporator 12 both sides with liquid level detector 30, liquid level detector 28, utilize the change of its cold-producing medium liquid level to control the aperture of movement of valve 32 and expansion valve 26.In the compression refrigerating machine 10-2 shown in Fig. 4, as shown in Figure 3, between high pressure evaporator 14 and low pressure evaporator 12, arrange overflow dike 44, the refrigerant liquid overflowing across this overflow dike 44 is sent to low pressure evaporator 12 via the aperture 42a as throttle orifice 46 be arranged on next door 42.At this, monitor the liquid level of low pressure evaporator 12 with liquid level detector 28, control the aperture of expansion valve 26 according to the change of its liquid level.
So, utilize overflow dike 44 to keep the liquid level of high pressure evaporator 14 to be constant, by the opening and closing of expansion valve 26, the cold-producing medium liquid measure supplied from low-pressure condenser 20 to high pressure evaporator 14 is changed, spill-out increases and decreases.Therefore, by detecting the cold-producing medium liquid level of low pressure evaporator 12 with liquid level detector 28, and control the aperture of expansion valve 26 according to this cold-producing medium liquid level height detection value, thus suitably can control refrigerant amount and the circulating mass of refrigerant of low pressure evaporator 12.
Fig. 5 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.As shown in the figure, this compression refrigerating machine 10-3 comprises low pressure evaporator 12, high pressure evaporator 14, the two-stage type low pressure compressor 16 ' with low pressure compressor 16-1 and 16-2, the two-stage type high pressure compressor 18 ' with high pressure compressor 18-1 and 18-2, low-pressure condenser 20, high pressure condenser 22 and intercooler (economizer: energy-saving appliance) 48.
Intercooler 48 is located between low-pressure condenser 20 and high pressure evaporator 14.The middle suction inlet of two-stage type low pressure compressor 16 ' is returned by the refrigerant vapour after intercooler 48 gasifies.The condensation of refrigerant liquid of intercooler 48 is delivered to by monitoring the cold-producing medium liquid level of low pressure evaporator 12 with liquid level detector 28 and controlling the aperture of expansion valve 52 and control from low-pressure condenser 20.In addition, the refrigerant liquid from intercooler 48 is sent to high pressure evaporator 14 by throttle orifice 50.
Fig. 6 is the figure of other schematic configuration examples representing compression refrigerating machine of the present invention.As shown in the figure, this compression refrigerating machine 10-4 comprises low pressure evaporator 12, high pressure evaporator 14, the high-lift compressor 17 ' of two-stage type with compressor 17-1 and 17-2, the two-stage type low lift compressor 19 ' with compressor 19-1 and 19-2, low-pressure condenser 20, high pressure condenser 22 and intercooler (energy-saving appliance) 48.
In this compression refrigerating machine 10-4, intercooler 48 is located between low-pressure condenser 20 and high pressure evaporator 14.Be provided with for the refrigerant vapor compression by delivering to high pressure condenser 22 from low pressure evaporator 12 high-lift compressor 17 and be used for the low lift compressor 19 of the refrigerant vapor compression by delivering to low-pressure condenser 20 from high pressure evaporator 14.The middle suction inlet of low lift compressor 19 ' is returned by the refrigerant vapour after intercooler 48 gasifies.The condensation of refrigerant liquid of intercooler 48 is delivered to by monitoring the cold-producing medium liquid level of low pressure evaporator 12 with liquid level detector 28 and controlling the aperture of expansion valve 52 and control from low-pressure condenser 20.In addition, the refrigerant liquid from intercooler 48 is sent to high pressure evaporator 14 by throttle orifice 50.
Above-mentioned compression refrigerating machine 10-1 ~ 10-4 will be by guiding to low-pressure condenser 20 by throttle orifice 24 (with reference to Fig. 1, Fig. 5) or control valve V3, V5 (with reference to Fig. 4, Fig. 6) at the condensed refrigerant liquid of high pressure condenser 22, thus on high-tension side condensation of refrigerant liquid is by partial gasification, be cooled to the temperature same with the condensation of refrigerant liquid phase of low-pressure side.Because the refrigerant vapour gasified at this is by low-pressure condenser 20 condensation immediately, therefore, the steam flow of compressor does not increase, and in fact can not increase the burden of refrigeration machine.Thus, high-pressure side refrigerant liquid does not use subcooler, just reaches the state identical with being cooled to the temperature of low-pressure condenser 20.In addition, as shown in Figure 2, if arrange subcooler 38 by the refrigerant liquid supercooling of low-pressure side, then efficiency of refrigerator improves further.
In addition, owing to not being directly refrigerant liquid is guided low pressure evaporator 12 from high pressure condenser 22 or intercooler 48, but condensate liquid is temporarily directed to high pressure evaporator 14, and in high pressure evaporator 14, be cooled to the evaporating temperature of this high pressure evaporator 14, cooled refrigerant liquid is directed to low pressure evaporator 12, even if thus expansion valve (expansion valve 26,52) is 1, also to low pressure evaporator 12, these 2 evaporimeter the supply system cryogens of high pressure evaporator 14, can control to wait also becoming easy.When arranging intercooler 48, also can with 1 intercooler 48 by whole refrigerant cools.
In addition, high pressure evaporator 14 will be equivalent to the refrigerant vapor with the temperature difference of condenser (high pressure condenser 22, low-pressure condenser 20) or intercooler 48, but the refrigerant vapour of this part correspondingly reduces in low pressure evaporator 12.At this, arrange from low pressure evaporator 12 to the high-lift compressor 17 of the refrigerant vapor compression of high pressure condenser 22 with by during from high pressure evaporator 14 to the low lift compressor 19 of the refrigerant vapor compression of low-pressure condenser 20 in compression refrigerating machine 10-4, the refrigerant vapour flow of low lift compressor 19 side increases, but the refrigerant vapour amount of high-lift compressor 17 side reduces.Therefore, can required drive be reduced, save necessary power.In addition, be two-stage type compressor in Fig. 6, but also can obtain same effect during employing single-stage compressor.
In addition, arrange as compression refrigerating machine 10-3 the refrigerant vapor compression by being sent to low-pressure condenser 20 from low pressure evaporator 12 two-stage type low pressure compressor 16 ' and by when being sent to the high pressure compressor 18 ' of the two-layer configuration of the refrigerant vapor compression of high pressure condenser 22 from high pressure evaporator 14, the middle suction inlet of low pressure compressor 16 ' is returned by the refrigerant vapour of intercooler 48 gasification separation, condenser (high pressure condenser 22, low-pressure condenser 20) is little with the lift difference of intercooler 48, is therefore favourable.
In addition, also can consider arbitrary group of high pressure evaporator 14 and low pressure evaporator 12 or high pressure condenser 22 and low-pressure condenser 20 as single evaporimeter or condenser.Fig. 7 is the figure representing schematic configuration example high pressure evaporator and low pressure evaporator being made the compression refrigerating machine of single evaporimeter.As shown in Figure 7, this compression refrigerating machine 10-5 comprises the evaporimeter 13 high pressure evaporator and low pressure evaporator being made single evaporimeter, the refrigerant vapour of flash-pot 13 delivers to high pressure compressor 18 and low pressure compressor 16 in the future, the refrigerant vapour compressed by high pressure compressor 18 is delivered to high pressure condenser 22 and makes condensation of refrigerant liquid, the refrigerant vapour compressed is delivered to low-pressure condenser 20 make condensation of refrigerant liquid by low pressure compressor 16.
The condensation of refrigerant liquid of high pressure condenser 22 is imported to low-pressure condenser 20 by throttle orifice 24, the cold-producing medium liquid level of evaporimeter 13 is monitored with liquid level detector 30, control the aperture of expansion valve 26, control from low-pressure condenser 20 to the condensation of refrigerant liquid measure of evaporimeter 13 movement, to make the cold-producing medium liquid level constant height of evaporimeter 13.
In above-mentioned compression refrigerating machine 10-5, its effect reduces certainly, but compared with the refrigeration machine of unitary system SAPMAC method in the past, is high performance refrigeration machine.In addition, can be same with refrigeration machine in the past, the throttle orifice 24 that high pressure condenser exports is made automatic valve to control aperture, for expansion valve 26, also can be same, utilize the liquid level etc. of low-pressure condenser 20 to control.Certainly, so-called float valve etc. also can be utilized to control.
Then, to the compression refrigerating machine of the invention described above, the situation only making a side of compressor stop is described.The on-stream cold-producing medium of compressor only flows to a direction, if but stop, then cold-producing medium adverse current, therefore needs special consideration.In addition, as everyone knows, owing to being made tank body pressure equalization each other by refrigerant piping, the situation that therefore on-stream tank body is adjacent with the tank body in stopping is inferior, produces and diverse pressure differential in running, there is the problems such as the withstand voltage deficiency in common next door.And according to the connection status of each heat exchanger, the movement producing undesirable cold-producing medium and the heat brought move thereupon, also there is the problem making the deterioration of efficiency of refrigeration machine.
Such as, in the compression refrigerating machine 100 of the structure in the past shown in Fig. 8, if stop high side compressors 104, then by high side compressors 104, high-pressure side condenser 106 and high-pressure side evaporimeter 102 pressure equalization, therefore the pressure of high-pressure side condenser 106 becomes the pressure roughly the same with high-pressure side evaporimeter 102.On the other hand, the pressure of high-pressure side evaporimeter 102 cools because of the cooling water 110 of circulation, and roughly equal with low side evaporator 101.Therefore, between high-pressure side condenser 106 and low-pressure side condenser 105, the pressure differential roughly equal with the discrepancy pressure differential of low-pressure side compressor 103 is produced.Preferably high-pressure side condenser 106 and low-pressure side condenser 105 separate a tank body with next door as described above, and when producing large pressure differential (when adopting the cold-producing medium of HFC245fa, being about 0.2MPa) like this, the design in next door is more difficult.And condenser each other or evaporimeter each other by pipe arrangement, compressor sealed tube etc. and when being communicated with etc., producing undesirable cold-producing medium and move and cause efficiency to reduce.Therefore, adopt with the following method in compression refrigerating machine of the present invention.
First, in the compression refrigerating machine 10-1 of Fig. 1, control valve V1 being set between high pressure condenser 22 and high pressure compressor 18, when stopping high pressure compressor 18, closing this control valve V1.So, then in high pressure evaporator 14, the evaporation of cold-producing medium stops, and is inflated that valve 26 reduces pressure and the cold-producing medium of partial gasification to be condensed liquefaction at high pressure evaporator 14 on the contrary.On the other hand, low pressure evaporator 12 is in running due to low pressure compressor 16 low pressure become lower than high pressure evaporator 14, drives by this pressure differential, and cold-producing medium moves from high pressure evaporator 14 to low pressure evaporator 12.Therefore, it is possible to carry out the running of refrigeration machine without barrier.
In above-mentioned compression refrigerating machine 10-1, also control valve V2 being set between low-pressure condenser 20 and low pressure compressor 16, when stopping low pressure compressor 16, closing this control valve V2.So, due to the running of high pressure compressor 18, flow to low-pressure condenser 20 by throttle orifice 24 by the refrigerant liquid of high pressure condenser 22 condensation together with uncooled refrigerant vapour.Because the temperature of the cooling water in low-pressure condenser 20 is lower than the temperature of the cooling water in high pressure condenser 22, therefore a part for refrigerant liquid temporarily gasifies, but at low-pressure condenser 20 by its cooling condensation together with uncooled steam.At this, because low pressure compressor 16 does not operate, therefore the heat load of low-pressure condenser 20 is very little, and refrigerant liquid is cooled to and the cooling water inlet temperature of refrigeration machine temperature closely.Therefore, the efficiency of refrigeration machine improves further.But in this case, the high pressure evaporator 14 in running is than low pressure evaporator 12 low pressure, and therefore cold-producing medium may adverse current.Now, movement of valve 32 can be closed.
In these cases, no matter which kind of situation, high pressure condenser 22 is roughly equal owing to being communicated with by throttle orifice 24 with the pressure of low-pressure condenser 20.Therefore, the pressure putting on next door for usually operate in same degree or its below, do not need to make next door withstand voltage especially.In addition, above-mentioned compression refrigerating machine 10-1 has 2 control valves V1, V2, if but the compressor always stopped is defined as side's compressor (low pressure compressor 16 or high pressure compressor 18), can certainly be only a side.
Then, the compression refrigerating machine 10-2 of key diagram 4.In this compression refrigerating machine 10-2, be substituted between the compressor (low pressure compressor 16, high pressure compressor 18) of Fig. 1 and condenser (low-pressure condenser 20, high pressure condenser 22) and control valve V1, V2 are set, but control valve V3 is set between high pressure condenser 22 and low-pressure condenser 20, when stopping high pressure compressor 18, close this control valve V3.Like this, then, during refrigerant vapor in high pressure condenser 22, flow to high pressure evaporator 14 by high pressure compressor 18, but due to the cold-producing medium recoverable amount in high pressure condenser 22 extremely few, after there is no cold-producing medium, then can not produce adverse current.Now, high pressure condenser 22 and high pressure evaporator 14 uniform pressure, therefore when high pressure condenser 22 is adjacent with low-pressure condenser 20, next door needs withstand voltage, usually at the control valve of refrigerant vapour and the control valve of refrigerant liquid, specific volume difference is comparatively large, and the control valve V3 therefore as refrigerant liquid control valve is little.Therefore, compared with there is the compression refrigerating machine 10-1 of larger 2 control valves V1, V2, can manufacture at an easy rate.In addition, about the circulation of cold-producing medium, same with compression refrigerating machine 10-1.
Then, the compression refrigerating machine 10-3 of key diagram 5.In this compression refrigerating machine 10-3, control valve V4 being set between high pressure compressor 18-1 and high pressure condenser 22, closing this control valve V4 when stopping high pressure compressor 18 '.Functions and effects are now identical with the compression refrigerating machine 10-1 of Fig. 1.But, in this compression refrigerating machine 10-3, between low pressure compressor 16-1 and low-pressure condenser 20, control valve is not set.Even if this is because, arrange control valve at this, when stopping low pressure compressor 16 ', cold-producing medium, from intercooler 48 to low pressure compressor 16 ' adverse current, therefore also needs to arrange control valve at this.That is, in this compression refrigerating machine 10-3, only operate a control valve V4,1 compressor can not be made to stop.
Then, the compression refrigerating machine 10-4 of key diagram 6.In this compression refrigerating machine 10-4, control valve V5 being set between high pressure condenser 22 and low-pressure condenser 20, when stopping high-lift compressor 17, closing this control valve V5.Now, also the action effect same with the compression refrigerating machine 10-2 of Fig. 4 can be obtained.
Then, the compression refrigerating machine 10-5 of key diagram 7.In this compression refrigerating machine 10-5, control valve V6 is set between high pressure compressor 18 and high pressure condenser 22.Now, also the action effect same with the compression refrigerating machine 10-1 of Fig. 1 can be obtained.
Above, describe embodiments of the present invention, but the invention is not restricted to above-mentioned embodiment, can various distortion be carried out in the scope of the technical conceive described in claims and description and accompanying drawing.In addition, any shape, the structure directly do not recorded in description and accompanying drawing, as long as play action effect of the present invention, then also in protection scope of the present invention.
The present invention is the compression refrigerating machine of two-stage refrigeration circulation, cold-producing medium in high pressure condenser condensation is imported low-pressure condenser, low pressure evaporator is imported by being cooled to the cold-producing medium of evaporating temperature at high pressure evaporator, therefore on high-tension side condensation of refrigerant liquid is by partial gasification, be cooled to the temperature same with the condensation of refrigerant liquid phase of low-pressure side, in fact refrigerant vapour after gasification, in low-pressure condenser condensation, therefore can not increase the burden of refrigeration machine.In addition, because the cold-producing medium flowing into low pressure evaporator is cooled to the saturation temperature of high pressure evaporator, therefore the load of low pressure evaporator diminishes.And the equipment such as intercooler, expansion valve, with 1, thus, can be used as more cheap, more high efficiency compression refrigerating machine compared with existing two-stage refrigeration circulation compression refrigerating machine and is used.In addition, due to 1 compressor can be made stoppingly to operate, therefore, it is possible to be used as the performance that can not reduce refrigeration machine when low load especially, the compression refrigerating machine that can adapt to load.
Claims (9)
1. a compression refrigerating machine, there is two-stage refrigeration circulation, the compressor that described compression refrigerating machine comprises high pressure condenser, low-pressure condenser, high pressure evaporator and low pressure evaporator, the compressor be connected with described high pressure condenser and is connected with described low-pressure condenser, is characterized in that
Described low-pressure condenser will be imported by the condensed refrigerant liquid of described high pressure condenser, and between the compressor be connected with described low-pressure condenser between the compressor be connected with described high pressure condenser and described high pressure condenser and described low-pressure condenser and between described high pressure condenser and described low-pressure condenser at least any one is provided with control valve
The compressor be connected with described low-pressure condenser is the low lift compressor refrigerant vapor compression of described high pressure evaporator being sent to described low-pressure condenser,
The compressor be connected with described high pressure condenser is the high-lift compressor refrigerant vapor compression of described low pressure evaporator being sent to described high pressure condenser,
The intercooler of cooling refrigeration agent is set in the outlet of described low-pressure condenser, the refrigerant vapour of this intercooler is imported the middle suction inlet of described low lift compressor.
2. a compression refrigerating machine, there is two-stage refrigeration circulation, the compressor that described compression refrigerating machine comprises high pressure condenser, low-pressure condenser, high pressure evaporator and low pressure evaporator, the compressor be connected with described high pressure condenser and is connected with described low-pressure condenser, is characterized in that
Described low-pressure condenser will be imported by the condensed refrigerant liquid of described high pressure condenser, and between the compressor be connected with described low-pressure condenser between the compressor be connected with described high pressure condenser and described high pressure condenser and described low-pressure condenser and between described high pressure condenser and described low-pressure condenser at least any one is provided with control valve
With next door, single tank body separated up and down and be configured to upper chambers and bottom compartment,
Configure described high pressure condenser in described upper chambers, and configure described low-pressure condenser in described bottom compartment, in described next door providing holes, being directed through the hole that arranges in described next door and carrying out from described high pressure condenser to the cold-producing medium of described low-pressure condenser.
3. a compression refrigerating machine, there is two-stage refrigeration circulation, the low pressure compressor that described compression refrigerating machine comprises high pressure condenser, low-pressure condenser, high pressure evaporator, low pressure evaporator, the high pressure compressor be connected with described high pressure condenser and is connected with described low-pressure condenser, it is characterized in that
Refrigerant liquid from described high pressure evaporator is sent to described low pressure evaporator via throttle orifice or valve, refrigerant liquid from described low-pressure condenser is sent to described high pressure evaporator via valve, described low-pressure condenser will be imported via throttle orifice or valve by the condensed refrigerant liquid of described high pressure condenser, and between the compressor be connected with described high pressure condenser and described high pressure condenser, between the compressor be connected with described low-pressure condenser and described low-pressure condenser, and between described high pressure condenser and described low-pressure condenser at least any one is provided with control valve,
With next door, single tank body separated up and down and be configured to upper chambers and bottom compartment,
Configure described high pressure condenser in described upper chambers, and configure described low-pressure condenser in described bottom compartment, in described next door providing holes, being directed through the hole that arranges in described next door and carrying out from described high pressure condenser to the cold-producing medium of described low-pressure condenser.
4. the compression refrigerating machine according to Claims 2 or 3, is characterized in that,
The intercooler of cooling refrigeration agent is provided with in the outlet of described low-pressure condenser.
5. compression refrigerating machine according to claim 4, is characterized in that,
Refrigerant vapour from described intercooler is imported the middle suction inlet of the compressor be connected with described low-pressure condenser.
6. the compression refrigerating machine according to Claims 2 or 3, is characterized in that,
The cold-producing medium being supplied to described low pressure evaporator is the cold-producing medium of the evaporating temperature being cooled to this high pressure evaporator by described high pressure evaporator.
7. compression refrigerating machine according to claim 6, is characterized in that,
The intercooler of cooling refrigeration agent is provided with at the entrance of described high pressure evaporator.
8. compression refrigerating machine according to claim 3, is characterized in that,
Described high pressure evaporator and described low pressure evaporator are configured on single tank body.
9. the compression refrigerating machine according to Claims 2 or 3, is characterized in that,
Overflow dike is provided with at described high pressure evaporator,
The cold-producing medium being configured to cross described overflow dike flows into described low pressure evaporator.
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| CN104329821A (en) * | 2013-07-22 | 2015-02-04 | 刘雄 | Air conditioning refrigeration equipment and control method thereof |
| KR101440858B1 (en) * | 2014-02-13 | 2014-09-17 | 주식회사 아이셈 | System for controlling compressor pressure in Human Machine Interface system and method thereof |
| WO2018068431A1 (en) * | 2016-10-12 | 2018-04-19 | 李华玉 | Combined cycle steam power device having evaporation stages |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101093116A (en) * | 2007-05-25 | 2007-12-26 | 清华大学 | Multistage-cascaded compression type heat pump set under large temperature difference |
| CN101617181A (en) * | 2006-10-10 | 2009-12-30 | 开利公司 | Double loop cooler with the binary channel heat exchanger that is series-counterflow arrangement |
| CN101619904A (en) * | 2009-08-02 | 2010-01-06 | 山东美琳达再生能源开发有限公司 | Two-stage heating high temperature heat pump device |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60126549A (en) * | 1983-12-12 | 1985-07-06 | 株式会社荏原製作所 | Energy conservation type refrigerator |
| US5137082A (en) * | 1989-10-31 | 1992-08-11 | Nippondenso Co., Ltd. | Plate-type refrigerant evaporator |
| US5875637A (en) * | 1997-07-25 | 1999-03-02 | York International Corporation | Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit |
| JP3821286B2 (en) * | 2002-06-21 | 2006-09-13 | 株式会社荏原製作所 | Refrigeration system combining absorption type and compression type and its operating method |
| JP4283633B2 (en) * | 2003-10-20 | 2009-06-24 | 川重冷熱工業株式会社 | Double-effect absorption chiller / heater with exhaust heat recovery unit |
| JP5096678B2 (en) * | 2006-01-10 | 2012-12-12 | 株式会社荏原製作所 | Refrigeration equipment |
| CN101265188A (en) * | 2008-04-21 | 2008-09-17 | 太仓市浦源化工有限公司 | Method for preparing ethyl 2-oxy-4-phenylbutyrate |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101617181A (en) * | 2006-10-10 | 2009-12-30 | 开利公司 | Double loop cooler with the binary channel heat exchanger that is series-counterflow arrangement |
| CN101093116A (en) * | 2007-05-25 | 2007-12-26 | 清华大学 | Multistage-cascaded compression type heat pump set under large temperature difference |
| CN101619904A (en) * | 2009-08-02 | 2010-01-06 | 山东美琳达再生能源开发有限公司 | Two-stage heating high temperature heat pump device |
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| JP5754935B2 (en) | 2015-07-29 |
| CN105066495A (en) | 2015-11-18 |
| JP2012137202A (en) | 2012-07-19 |
| CN105066495B (en) | 2017-11-17 |
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