CN103836858B - refrigerating and air conditioning system - Google Patents
refrigerating and air conditioning system Download PDFInfo
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- CN103836858B CN103836858B CN201210567937.8A CN201210567937A CN103836858B CN 103836858 B CN103836858 B CN 103836858B CN 201210567937 A CN201210567937 A CN 201210567937A CN 103836858 B CN103836858 B CN 103836858B
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 68
- 238000010257 thawing Methods 0.000 claims abstract description 52
- 239000003507 refrigerant Substances 0.000 claims abstract description 40
- 239000007788 liquid Substances 0.000 claims description 50
- 238000011084 recovery Methods 0.000 claims description 20
- 238000005057 refrigeration Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 13
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 8
- 230000035939 shock Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 5
- 230000008014 freezing Effects 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
- 235000013305 food Nutrition 0.000 description 2
- 235000013372 meat Nutrition 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
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- Air Conditioning Control Device (AREA)
- Defrosting Systems (AREA)
Abstract
The invention provides a refrigeration air-conditioning system, which comprises a refrigerant circulating module and a defrosting control valve. The refrigerant circulation module comprises a compressor, a condenser, an expansion device and an evaporator, wherein the compressor, the condenser, the expansion device and the evaporator are sequentially connected through a pipeline to form a circulation loop. The defrost control valve is connected between the evaporator and the condenser in a parallel configuration with the expansion device.
Description
Technical field
The present invention relates to a kind of refrigerating and air conditioning system, particularly relate to the refrigerating and air conditioning system of the defrosting of a kind of tool or hot-swap feature.
Background technology
The mode of what the defrosting means of current most refrigerating and air conditioning system (such as refrigerator or air-conditioning equipment) were taked is electric defrosting, but with the problem that the mode of electric defrosting will easily cause power consumption higher.Deposit the reach in freezer of quality goods for sales field, if reach in freezer uses the mode of electric defrosting, will easily cause the phenomenon that the temperature of reach in freezer is too high.So often cause the problem such as qualitative variability, variation, blackening of food in reach in freezer or meat.Therefore, time will defrost to reach in freezer in general sales field, often need the food in reach in freezer or meat to carry down just can defrost.So, defrost process will be made too tediously long and inconvenient.
In addition, the defrosting means of refrigerating and air conditioning system are separately had to take the mode of hot gas defrosting or hot liquid defrosting, but will easily cause the negative effect of thermal shock in the mode of hot gas defrosting, and the shortcoming that defrosting temperature is too low will be caused because environment temperature is lower in the mode of hot liquid defrosting.And, above-mentionedly produce the problem of hydraulic compression with also must the arrange in pairs or groups electric heating means of the intrasystem liquid-gas separator of refrigerating and air conditioning of hot gas defrosting or the mode of hot liquid defrosting to prevent compressor, therefore still need to consume extra electric power with hot gas defrosting or the mode of hot liquid defrosting.
In addition, current refrigerating and air conditioning system often has the generation of used heat, and the waste that this used heat also will cause in the using energy source of refrigerating and air conditioning system.
Summary of the invention
The invention reside in and a kind of refrigerating and air conditioning system is provided, so as to solving the problem of existing defrosting means and improving energy utilization rate.
Disclosed refrigerating and air conditioning system, comprises a refrigerant circulation module, a defrost control valve and a heat recovery module.Refrigerant circulation module comprises a compressor, a condenser, an expansion gear and an evaporimeter, and compressor, condenser, expansion gear and evaporimeter are formed a closed circuit by a pipeline to be sequentially connected.Defrost control valve and expansion gear are that the relation configured in parallel is connected between evaporimeter and condenser.Heat recovery module comprises a flow direction controller and a heat regenerator, this flow direction controller is connected between this compressor and this condenser, one end of this heat regenerator connects this flow direction controller, and the other end of this heat regenerator is connected to this pipeline between this condenser and this expansion gear.
Disclosed refrigerating and air conditioning system, comprises a refrigerant circulation module and a heat recovery module.Refrigerant circulation module comprises a compressor, a condenser, an expansion gear and an evaporimeter, and compressor, condenser, expansion gear and evaporimeter are formed a closed circuit by a pipeline to be sequentially connected.Heat recovery module comprises a flow direction controller and a heat regenerator.Flow direction controller is connected between compressor and condenser.One end of heat regenerator connects flow direction controller, and the other end of heat regenerator is connected to the pipeline between condenser and expansion valve.
According to the refrigerating and air conditioning system that the invention described above discloses, be that the relation configured in parallel introduces high temperature refrigerant to evaporimeter, to reach defrosting effect by defrost control valve and expansion gear.In addition, by the setting of defrosting supplementary module, to strengthen defrosting effect.Therefore the refrigerating and air conditioning system of the present embodiment can complete rapidly defrosting action and can avoid the problem of thermal shock and extra power consumption.In addition, by the setting of heat recovery module, fully can reclaim used heat that refrigerating and air conditioning system produces and improve reusing of energy source rate.
Feature for the present invention, implementation and effect, now coordinate accompanying drawing to be described in detail as follows as most preferred embodiment.
Accompanying drawing explanation
Fig. 1 is the structure configuration map of refrigerating and air conditioning system according to an embodiment of the invention;
Fig. 2 is the structural representation of the degree of superheat adjustment module of refrigerating and air conditioning system according to Fig. 1;
Fig. 3 is the structure configuration map of refrigerating and air conditioning system according to another embodiment of the present invention;
Fig. 4 is the structure configuration map of refrigerating and air conditioning system according to yet another embodiment of the invention.
Reference numeral
10: refrigerating and air conditioning system 10a: refrigerating and air conditioning system
11: refrigerant circulation module 111: compressor
112: condenser 113: expansion gear
114: evaporimeter 115: pipeline
116: defrost control valve 117: secondary unit
118: distribution pipeline 119: current divider
12: defrosting supplementary module 12a: defrosting supplementary module
121: the first valve body 122: the second valve bodies
123: the three valve bodies 124: first-class pipe
125: second pipe 126: bypass pipe
127: the first temperature sensors 128: heat exchanger
13: heat recovery module 131: flow direction controller
132: heat regenerator 133: pressure-relief valve
134: device for storing liquid 135: the second temperature sensor
14: degree of superheat adjustment module 141: outer chamber
1411: outer chamber 1412: bottom
142: inner chamber body 1421: inner cavity chamber
1422: bottom 143: the first body
1431: opening 144: the second body
1441: opening 145: the three body
1451: opening 146: the four body
1461: opening 20: liquid refrigerant
20 ': liquid refrigerant
Detailed description of the invention
Please refer to Fig. 1 and Fig. 2, Fig. 1 is the structure configuration map of refrigerating and air conditioning system according to an embodiment of the invention, and Fig. 2 is the structural representation of the degree of superheat adjustment module of refrigerating and air conditioning system according to Fig. 1.
The refrigerating and air conditioning system 10 of the present embodiment can apply to refrigerator or air-conditioning equipment, but not as limit.
Refrigerating and air conditioning system 10 comprises refrigerant circulation module 11 and a defrost control valve 116.
Refrigerant circulation module 11 comprises compressor 111, condenser 112, expansion gear 113 and an evaporimeter 114.Compressor 111, condenser 112, expansion gear 113 and evaporimeter 114 are formed a closed circuit by a pipeline 115 to be sequentially connected.Furthermore, cold-producing medium in refrigerant circulation module 11 sequentially flows through condenser 112, expansion gear 113 and evaporimeter 114 by pipeline 115 by compressor 111, then cold-producing medium be back to compressor 111 by evaporimeter 114 by pipeline 115, to complete the refrigerant circulation of single time.Wherein, above-mentioned expansion gear 113 can be but be not limited to expansion valve or capillary.
Defrost control valve 116 is connected between evaporimeter 114 and condenser 112, and defrost control valve 116 and expansion gear 113 are the relation configured in parallel.When defrosting to evaporimeter 114, defrost control valve 116 can be opened.The part high-temperature liquid state cold-producing medium so making condenser 112 discharge, under the state without expansion gear 113, can flow directly into evaporimeter 114 via defrost control valve 116, defrost to make high-temperature liquid state cold-producing medium heat evaporimeter 114.
In addition, if the temperature of the high-temperature liquid state cold-producing medium that environment temperature is too low or the load of refrigerating and air conditioning system is lower and make condenser 112 discharge is not high enough, then the high-temperature liquid state cold-producing medium causing condenser 112 to discharge fully cannot be carried out heating defrosting to evaporimeter 114, and then affect defrosting efficiency.To this, refrigerating and air conditioning system 10 of the present invention also comprises a defrosting supplementary module 12, to strengthen defrosting effect.
The defrosting supplementary module 12 of the present embodiment comprises first-class pipe 124, the second pipe 125 of one first valve body 121,1 second valve body 122, the 3rd valve body 123, bypass line 126,1 first temperature sensor 127 and a heat exchanger 128.
One end of first valve body 121 connects compressor 111 by first-class pipe 124, and the other end of the first valve body 121 connects defrost control valve 116 by second pipe 125.So, the high temperature liquid refrigerant making compressor 111 discharge directly can arrive defrost control valve 116 by the first valve body 121.
First temperature sensor 127 is positioned at pipeline 115 and contiguous defrost control valve 116, first temperature sensor 127 is electrically connected the first valve body 121.
Heat exchanger 128 is positioned at second pipe 125, and heat exchanger 128 is between the first valve body 121 and defrost control valve 116.Bypass pipe 126 connects between this first valve body 121 and defrost control valve 116, and bypass pipe 126 and second pipe 125 are the relation configured in parallel.Second valve body 122 is at second pipe 125 and between heat exchanger 128 and the first valve body 121, the 3rd valve body 123 is arranged at bypass pipe 126.In addition, an another frame or the water pond being connected to the equipment that refrigerating and air conditioning system 10 is used by a heat pipe of heat exchanger 128.Further, the first above-mentioned valve body 121 and the first temperature sensor 127 form a temperature control valve module jointly, and the second valve body 122 and the 3rd valve body 123 can be itself be a temperature control valve, but not as limit.
Therefore, when the first temperature sensor 127 sense by condenser 112 be expelled to the temperature of the high-temperature liquid state cold-producing medium of defrost control valve 116 not high enough time, the first valve body 121 just can be opened automatically.So, the high temperature liquid refrigerant that compressor 111 is discharged will arrive second pipe 125 and bypass pipe 126 by the first valve body 121.Now, the second valve body 122 and the 3rd valve body 123 can be opened according to the temperature of high temperature liquid refrigerant or close.
Specifically, if the temperature of high temperature liquid refrigerant is too high and may cause the doubt of thermal shock to evaporimeter, then the second valve body 122 can be opened the 3rd valve body 123 and then closes.So, high temperature liquid refrigerant first will carry out heating defrosting, dehumidifying or anti-condensation through over-heat-exchanger 128 to the frame of the equipment that refrigerating and air conditioning system 10 is used or water pond, just enter evaporimeter 114 by defrost control valve 116 after the temperature of high temperature liquid refrigerant can first be reduced and carry out auxiliary heating defrosting, to avoid negative effect evaporimeter 114 being produced to thermal shock.
If the temperature of high temperature liquid refrigerant suitably can not cause the doubt of thermal shock to evaporimeter 114, then the second valve body 122 can be closed the 3rd valve body 123 and then opened.So, high temperature liquid refrigerant directly can enter evaporimeter 114 by defrost control valve 116 and carries out auxiliary heating defrosting, to strengthen defrosting effect.
And, adopt the arrange in pairs or groups design of defrosting supplementary module 12 of defrost control valve 116 to carry out defrosting to actual reach in freezer and test with refrigerating and air conditioning system 10 of the present invention, can measure reach in freezer a whole day and only need spend 11.34 minutes and carry out defrosting and can satisfy the demands by actual amount.Compared to existing in the mode of electric defrosting, need every defrosting action carrying out 30 minutes for 4 hours, the defrosting means of refrigerating and air conditioning system 10 of the present invention significantly can reduce defrosting time really.In addition, the defrosting means of refrigerating and air conditioning system 10 of the present invention do not need to spend extra electric power, therefore can reach energy-conservation effect yet.
In addition, the part high-temperature liquid state cold-producing medium introducing evaporimeter 114 of being discharged by condenser 112 due to the present embodiment defrosts, if liquid refrigerant is not completely vaporised after evaporator 114, then compressor 111 may be caused to produce the problem of hydraulic compression and the connecting rod of compressor 111 inside or valve block are ruptured.To this, refrigerating and air conditioning system 10 of the present invention also comprises a degree of superheat adjustment module 14, with the problem preventing compressor 111 from producing hydraulic compression.
The degree of superheat adjustment module 14 of the present embodiment comprises outer chamber 141, inner chamber body 142,1 first body 143,1 second body 144, the 3rd body 145 and one the 4th body 146.Outer chamber 141 has an outer chamber 1411, and inner chamber body 142 is positioned at the outer chamber 1411 of outer chamber 141, and inner chamber body 142 has an inner cavity chamber 1421.Outer chamber 1411 is communicated with the pipeline 115 between condenser 112 and expansion gear 113, and inner cavity chamber 1421 is communicated with the pipeline 115 between compressor 111 and evaporimeter 114.
Specifically, first body 143 is connected outer chamber 141 with the second body 144 and is communicated with outer chamber 1411, and the first body 143 connects condenser 112 away from one end of outer chamber 141 by pipeline 115, the second body 144 connects expansion gear 113 away from one end of outer chamber 141 by pipeline 115.Whereby, the cold-producing medium making condenser 112 discharge first just can arrive expansion gear 113 after outer chamber 1411.Inner chamber body 142 is connected and communication with cavity room 1421 with the 4th body 146 as the 3rd body 145, and the 3rd body 145 connects compressor 111 away from one end of inner chamber body 142 by pipeline 115, the 4th body 146 connects evaporimeter 114 away from one end of inner chamber body 142 by pipeline 115.Whereby, the cold-producing medium making evaporimeter 114 discharge first just can arrive compressor 111 after inner cavity chamber 1421.
In addition, the relative altitude that the first body 143 is positioned at the opening 1431 of outer chamber 1411 is greater than the relative altitude that the second body 144 is positioned at the opening 1441 of outer chamber 1411.Specifically, the distance of the bottom 1412 of opening 1431 to the outer chamber 1411 of the first body 143 is greater than the distance of the bottom 1412 of the second body 144 opening 1441 to outer chamber 1411.
Further, the 3rd body 145 is a U-shaped pipe, and its relative altitude being positioned at the opening 1451 of inner cavity chamber 1421 is greater than the relative altitude that the 4th body 146 is positioned at the opening 1461 of inner cavity chamber 1421.Specifically, the distance of the bottom 1422 of opening 1451 to the inner cavity chamber 1421 of the 3rd body 145 is greater than the distance of the bottom 1422 of opening 1461 to the inner cavity chamber 1421 of the 4th body 146.
When cold-producing medium carries out circulation time, the liquid refrigerant 20 that condenser 112 is discharged can be hoarded in outer chamber 1411, the liquid refrigerant 20 ' that evaporimeter 114 is discharged then is hoarded in inner cavity chamber 1421, and the temperature of liquid refrigerant 20 in outer chamber 1411 can higher than the temperature of the liquid refrigerant 20 ' in inner cavity chamber 1421.So, the liquid refrigerant 20 ' in inner cavity chamber 1421 is made to carry out heat exchange with the liquid refrigerant 20 in outer chamber 1411 and after being evaporated to gaseous refrigerant, to be just expelled to compressor 111 via the 3rd body 145.Further, the relative altitude because of the opening 1451 of the 3rd body 145 is greater than the relative altitude of the opening 1461 of the 4th body 146, therefore can guarantee that the cold-producing medium being expelled to compressor 111 by inner cavity chamber 1421 is all gaseous refrigerant.Whereby, can prevent compressor 111 from producing the problem of hydraulic compression.Relative altitude as the opening 1431 of the first body 143 is greater than the relative altitude of the opening 1441 of the second body 144, then can guarantee that the cold-producing medium flowing out to expansion gear 113 is all liquid refrigerant.
In addition, the refrigerating and air conditioning system 10 of the present embodiment also can comprise a heat recovery module 13, to reclaim used heat that refrigerating and air conditioning system 10 produces and to improve reusing of energy source rate.
Heat recovery module 13 comprises flow direction controller 131, heat regenerator 132, device for storing liquid 134 and one second temperature sensor 135.Flow direction controller 131 is connected between compressor 111 and condenser 112.One end of heat regenerator 132 connects flow direction controller 131, and the other end of heat regenerator 132 is connected to the pipeline 115 between condenser 112 and expansion gear 113.Device for storing liquid 134 connects heat regenerator 132, and device for storing liquid 134 can be but be not limited to a water butt or a water storage tower.Second temperature sensor 135 is positioned at device for storing liquid 134, and the second temperature sensor 135 is in order to detect the temperature of the liquid (such as water) in device for storing liquid 134.Further, the second temperature sensor 135 is electrically connected flow direction controller 131.
The high temperature refrigerant that compressor 111 is discharged can flow to heat regenerator 132 via the guiding of flow direction controller 131, and heat regenerator 132 absorbs the heat energy of high temperature liquid refrigerant and heats the liquid in device for storing liquid 134.And, all high temperature refrigerants that compressor 111 is discharged generally all are guided to heat regenerator 132 by flow direction controller 131 as much as possible, avoid the waste of used heat to make heat regenerator 132 fully absorb the heat energy of the high temperature liquid refrigerant that compressor 111 is discharged.When the temperature that the second temperature sensor 135 detects the liquid (such as water) in device for storing liquid 134 arrives setting demand, the flow direction of cold-producing medium just can be switched to condenser 112 by heat regenerator 132 by flow direction controller 131.So, the organic efficiency of heat regenerator 132 can be improved, and can guarantee that the temperature of the high-temp liquid (as hot water) that device for storing liquid 134 provides can maintain optimum temperature.
In addition, in the present embodiment, heat recovery module 13 also can comprise a pressure-relief valve 133, and one end of pressure-relief valve 133 is connected to flow direction controller 131, and the other end of pressure-relief valve 133 is connected to the pipeline 115 between compressor 111 and evaporimeter 114.Whereby, when flow direction controller 131 switches flowing to of cold-producing medium, the cold-producing medium of part can be back to compressor 111, flow direction controller 131 so can be avoided in handoff procedure cause the flow of the cold-producing medium flowing to heat regenerator 132 or condenser 112 to uprush caused negative effect.
Please then with reference to the structure configuration map that Fig. 3, Fig. 3 are refrigerating and air conditioning system according to another embodiment of the present invention.Because the present embodiment is similar to Fig. 1 embodiment, be therefore only illustrated for deviation.
The difference of the present embodiment and Fig. 1 embodiment is only that the defrosting supplementary module 12a of the refrigerating and air conditioning system 10 of the present embodiment does not have one second valve body 122, the 3rd valve body 123 and bypass line 126.
Therefore, the high temperature liquid refrigerant that compressor 111 is discharged will sequentially after the first valve body 121 and heat exchanger 128, and just entering evaporimeter 114 by defrost control valve 116 carries out auxiliary heating defrosting, to strengthen defrosting effect.The refrigerating and air conditioning system 10 of the above embodiments also still can reach the effect of defrosting rapidly.
Please then with reference to the structure configuration map that Fig. 4, Fig. 4 are refrigerating and air conditioning system according to yet another embodiment of the invention.Because the present embodiment is similar to Fig. 1 embodiment, be therefore only illustrated for deviation.
The refrigerating and air conditioning system 10b of the present embodiment also comprises current divider 119, secondary unit 117 and a distribution pipeline 118.The pipeline 115 of current divider 119 between expansion gear 113 and evaporimeter 114.Current divider 119 can be but be not limited to a control valve, a choke valve or the combination of control valve and choke valve.
One end of distribution pipeline 118 connects current divider 119, and the other end of distribution pipeline 118 is connected to the pipeline 115 (can be the pipeline 115 be connected between evaporimeter 114 and degree of superheat adjustment module 14 especially) between evaporimeter 114 and compressor 111.Secondary unit 117 is positioned on distribution pipeline 118, and secondary unit 117 can be arranged at outdoor, but not as limit.
When refrigerating and air conditioning system 10b need not provide freezing or the load of cold air time, evaporimeter 114 can cut out, and make cold-producing medium all flow to secondary unit 117 by current divider 119 to carry out heat exchange, to maintain the continued operation of compressor 111.So, with the heat energy making heat recovery module 13 can reclaim cold-producing medium constantly, to guarantee that the temperature of the high-temp liquid (as hot water) that device for storing liquid 134 provides can maintain optimum temperature.
When refrigerating and air conditioning system 10b is full load for load that is freezing or cold air, then closes secondary unit 117 and make cold-producing medium all flow to evaporimeter 114 by current divider 119.
When refrigerating and air conditioning system 10b is low load for load that is freezing or cold air, then suitably allocate the flow proportional of the cold-producing medium flowing to evaporimeter 114 and secondary unit 117 by current divider 119, with the continued operation of the demand and heat recovery module 13 that meet freezing or cold air simultaneously.
According to the refrigerating and air conditioning system of above-described embodiment, be that the relation configured in parallel introduces high temperature refrigerant to evaporimeter, to reach defrosting effect by defrost control valve and expansion gear.Further, the refrigerating and air conditioning system of the present embodiment can complete rapidly defrosting action and can avoid the problem of thermal shock and extra power consumption.In addition, by the setting of defrosting supplementary module, to strengthen defrosting effect.By the setting of degree of superheat adjustment module, with the problem preventing compressor from producing hydraulic compression.By the setting of heat recovery module, fully to reclaim used heat that refrigerating and air conditioning system produces and to improve reusing of energy source rate.
Claims (19)
1. a refrigerating and air conditioning system, is characterized in that, comprises:
One refrigerant circulation module, comprises a compressor, a condenser, an expansion gear and an evaporimeter, and this compressor, this condenser, this expansion gear and this evaporimeter are formed a closed circuit by a pipeline to be sequentially connected;
One defrost control valve is that the relation configured in parallel is connected between this evaporimeter and this condenser with this expansion gear; And
One heat recovery module, comprise a flow direction controller and a heat regenerator, this flow direction controller is connected between this compressor and this condenser, and one end of this heat regenerator connects this flow direction controller, and the other end of this heat regenerator is connected to this pipeline between this condenser and this expansion gear.
2. refrigerating and air conditioning system according to claim 1, it is characterized in that, also comprise a defrosting supplementary module, comprise one first valve body and one first temperature sensor, the opposite end of this first valve body connects this compressor and this defrost control valve respectively, this first temperature sensor is positioned at this pipeline and this defrost control valve contiguous, and this first temperature sensor is electrically connected this first valve body.
3. refrigerating and air conditioning system according to claim 2, it is characterized in that, this defrosting supplementary module also comprises a first-class pipe, a second pipe and a heat exchanger, this first valve body connects this compressor by this first-class pipe, this first valve body connects this defrost control valve by this second pipe, and this heat exchanger is at this second pipe and between this first valve body and this defrost control valve.
4. refrigerating and air conditioning system according to claim 3, it is characterized in that, this defrosting supplementary module also comprises bypass line, one second valve body and one the 3rd valve body, this bypass pipe and this second pipe are that the relation configured in parallel is connected between this first valve body and this defrost control valve, this second valve body is between this heat exchanger and this first valve body, and the 3rd valve body is positioned at this bypass pipe.
5. refrigerating and air conditioning system according to claim 1, is characterized in that, this heat recovery module also comprises a device for storing liquid, connects this heat regenerator.
6. refrigerating and air conditioning system according to claim 5, is characterized in that, this heat recovery module also comprises one second temperature sensor, is positioned at this device for storing liquid, and this second temperature sensor is electrically connected this flow direction controller.
7. refrigerating and air conditioning system according to claim 1, is characterized in that, this heat recovery module also comprises a pressure-relief valve, and one end of this pressure-relief valve is connected to this flow direction controller, and the other end of this pressure-relief valve is connected to this pipeline between this compressor and this evaporimeter.
8. refrigerating and air conditioning system according to claim 1, it is characterized in that, also comprise a degree of superheat adjustment module, comprise an outer chamber and be positioned at an inner chamber body of this outer chamber, this outer chamber has an outer chamber, this inner chamber body has an inner cavity chamber, and this outer chamber is communicated with this pipeline between this condenser and this expansion gear, and this inner cavity chamber is communicated with this pipeline between this compressor and this evaporimeter.
9. refrigerating and air conditioning system according to claim 8, it is characterized in that, this degree of superheat adjustment module also comprises one first body and one second body and one the 3rd body and one the 4th body that are connected this inner chamber body that connect this outer chamber, this first body connects this condenser, this second body connects this expansion gear, 3rd body connects this compressor, 4th body connects this evaporimeter, the cold-producing medium that this evaporimeter is discharged first just can arrive this compressor after this inner chamber body, the relative altitude that this first body is positioned at the opening of this outer chamber is greater than the relative altitude that this second body is positioned at the opening of this outer chamber, 3rd body is a U-shaped pipe, the relative altitude being positioned at the opening of this inner cavity chamber is greater than the relative altitude that the 4th body is positioned at the opening of this inner cavity chamber.
10. refrigerating and air conditioning system according to claim 1, it is characterized in that, also comprise a current divider, a secondary unit and a distribution pipeline, this current divider this pipeline between this expansion gear and this evaporimeter, one end of this distribution pipeline connects this current divider, the other end of this distribution pipeline is connected to this pipeline between this evaporimeter and this compressor, and this secondary unit is positioned on this distribution pipeline.
11. refrigerating and air conditioning systems according to claim 10, it is characterized in that, this secondary unit is arranged at outdoor.
12. 1 kinds of refrigerating and air conditioning systems, is characterized in that, comprise:
One refrigerant circulation module, comprises a compressor, a condenser, an expansion gear and an evaporimeter, and this compressor, this condenser, this expansion gear and this evaporimeter are formed a closed circuit by a pipeline to be sequentially connected; And
One heat recovery module, comprise a flow direction controller and a heat regenerator, this flow direction controller is connected between this compressor and this condenser, and one end of this heat regenerator connects this flow direction controller, and the other end of this heat regenerator is connected to this pipeline between this condenser and this expansion gear.
13. refrigerating and air conditioning systems according to claim 12, it is characterized in that, this heat recovery module also comprises a device for storing liquid, connects this heat regenerator.
14. refrigerating and air conditioning systems according to claim 13, it is characterized in that, this heat recovery module also comprises one second temperature sensor, is positioned at this device for storing liquid, and this second temperature sensor are electrically connected this flow direction controller.
15. refrigerating and air conditioning systems according to claim 12, it is characterized in that, this heat recovery module also comprises a pressure-relief valve, and one end of this pressure-relief valve is connected to this flow direction controller, and the other end of this pressure-relief valve is connected to this pipeline between this compressor and this evaporimeter.
16. refrigerating and air conditioning systems according to claim 12, it is characterized in that, also comprise a degree of superheat adjustment module, comprise an outer chamber and be positioned at an inner chamber body of this outer chamber, this outer chamber has an outer chamber, this inner chamber body has an inner cavity chamber, and this outer chamber is communicated with this pipeline between this condenser and this expansion gear, and this inner cavity chamber is communicated with this pipeline between this compressor and this evaporimeter.
17. refrigerating and air conditioning systems according to claim 16, it is characterized in that, this degree of superheat adjustment module also comprises one first body and one second body and one the 3rd body and one the 4th body that are connected this inner chamber body that connect this outer chamber, this first body connects this condenser, this second body connects this expansion gear, 3rd body connects this compressor, 4th body connects this evaporimeter, the cold-producing medium that this evaporimeter is discharged first just can arrive this compressor after this inner chamber body, the relative altitude that this first body is positioned at the opening of this outer chamber is greater than the relative altitude that this second body is positioned at the opening of this outer chamber, 3rd body is a U-shaped pipe, and the relative altitude being positioned at the opening of this inner cavity chamber is greater than the relative altitude that the 4th body is positioned at the opening of this inner cavity chamber.
18. refrigerating and air conditioning systems according to claim 12, it is characterized in that, also comprise a current divider, a secondary unit and a distribution pipeline, this current divider this pipeline between this expansion gear and this evaporimeter, one end of this distribution pipeline connects this current divider, the other end of this distribution pipeline is connected to this pipeline between this evaporimeter and this compressor, and this secondary unit is positioned on this distribution pipeline.
19. refrigerating and air conditioning systems according to claim 18, it is characterized in that, this secondary unit is arranged at outdoor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TW101144036A TWI506237B (en) | 2012-11-23 | 2012-11-23 | Refrigeration and air condition system |
| TW101144036 | 2012-11-23 |
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| CN103836858A CN103836858A (en) | 2014-06-04 |
| CN103836858B true CN103836858B (en) | 2015-12-09 |
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| CN201210567937.8A Active CN103836858B (en) | 2012-11-23 | 2012-12-25 | refrigerating and air conditioning system |
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| CN (1) | CN103836858B (en) |
| TW (1) | TWI506237B (en) |
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| JP6929318B2 (en) * | 2019-03-28 | 2021-09-01 | 東プレ株式会社 | Refrigeration equipment and operation method of refrigeration equipment |
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| TWM405555U (en) * | 2010-08-10 | 2011-06-11 | Tenzon Co Ltd | Defrosting structure for low-temperature or rapid refrigerator |
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- 2012-12-25 CN CN201210567937.8A patent/CN103836858B/en active Active
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| JPH07324849A (en) * | 1994-05-30 | 1995-12-12 | Nippondenso Co Ltd | Refrigerator |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN103836858A (en) | 2014-06-04 |
| TWI506237B (en) | 2015-11-01 |
| TW201420980A (en) | 2014-06-01 |
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