CN217464934U - Refrigerating system and refrigerating equipment - Google Patents
Refrigerating system and refrigerating equipment Download PDFInfo
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- CN217464934U CN217464934U CN202221389824.9U CN202221389824U CN217464934U CN 217464934 U CN217464934 U CN 217464934U CN 202221389824 U CN202221389824 U CN 202221389824U CN 217464934 U CN217464934 U CN 217464934U
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- defrosting
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Abstract
The utility model discloses a refrigerating system and refrigeration plant, refrigerating system includes: the refrigeration cycle loop is formed by connecting a compressor unit, a condenser and an evaporator unit, the compressor unit comprises a first compressor and a second compressor which are arranged in series, and a refrigerant discharged by the first compressor is sent to an air suction port of the second compressor; the heat recovery defrosting circuit is formed by connecting a compressor unit, an evaporator group, an auxiliary heat exchanger and a heat regenerator, a refrigerant flowing out of a condenser is sent to the evaporator group for refrigeration through a first heat exchange pipeline of the heat regenerator, the refrigerant flowing out of the evaporator group is sent back to an air suction port of the first compressor through a second heat exchange pipeline of the auxiliary heat exchanger and the heat regenerator, and the auxiliary heat exchanger is used for cooling the refrigerant discharged by the first compressor. The utility model discloses take place leading-in supplementary heat exchanger of liquid refrigerant and regenerator of phase transition behind the defrosting, reduce compressor unit's exhaust temperature when eliminating liquid and hit the hidden danger, reduce the compressor acting, improve refrigeration efficiency.
Description
Technical Field
The utility model relates to a refrigeration technology field especially relates to refrigerating system and refrigeration plant.
Background
In large industrial freezer refrigeration systems, frosting is a very common phenomenon. It is believed that when air flows over the evaporator surface and the evaporator surface temperature is below 0 c, surface frosting occurs. Because the frost layer formed has low heat conductivity, the heat exchange performance of the evaporator is reduced, the energy consumption is increased, and the air absorption and liquid entrainment can be caused to a certain degree. In general, hot fluorine defrosting is adopted as a defrosting mode of a low-temperature refrigerator in the industry, sufficient heat source, namely gaseous high-pressure high-temperature refrigerant, is needed for hot fluorine defrosting, high-temperature gas generated when a compressor unit works is guided into an evaporator in a defrosting working condition in an evaporator set through shunting, and a frost layer on the surface of the evaporator is melted by using heat of the high-temperature gas.
The defrosting mode has the great advantage in defrosting speed, high-temperature gas can absorb cold of a frost layer and condense into liquid while defrosting an evaporator, a liquid refrigerant treatment scheme generated by defrosting in the prior art is to introduce the liquid refrigerant into a heat regenerator, the liquid refrigerant absorbs heat of refrigerant flowing out of a condenser through the heat regenerator and then is sent to an air suction port of a compressor unit, but due to the factors of low temperature, incomplete heat exchange and the like of the refrigerant flowing out of the condenser, the liquid refrigerant cannot be completely converted into a gaseous refrigerant after absorbing heat, and liquid impact hidden danger still exists.
Therefore, how to overcome the shortcomings of the existing hot fluorine defrosting scheme is a technical problem to be solved in the industry.
SUMMERY OF THE UTILITY MODEL
In order to solve the defect that there is liquid impact hidden danger in current hot fluorine defrosting technique, the utility model provides a refrigerating system and refrigeration plant, this refrigerating system take place leading-in auxiliary heat exchanger of liquid refrigerant and regenerator of phase transition after will defrosting, liquid refrigerant carries out the heat exchange through auxiliary heat exchanger with first compressor combustion gas state refrigerant, reduces the exhaust temperature of second compressor when eliminating liquid impact hidden danger, has reduced compressor acting under the equal pressure ratio, improves refrigeration efficiency.
The utility model discloses a technical scheme be, design refrigerating system, include:
the refrigeration cycle loop is formed by connecting a compressor unit, a condenser and an evaporator unit, the compressor unit comprises a first compressor and a second compressor which are arranged in series, and a refrigerant discharged by the first compressor is sent to an air suction port of the second compressor;
the heat recovery defrosting circuit is formed by connecting a compressor unit, an evaporator group, an auxiliary heat exchanger and a heat regenerator, a refrigerant flowing out of a condenser is sent to the evaporator group for refrigeration through a first heat exchange pipeline of the heat regenerator, the refrigerant flowing out of the evaporator group is sent back to an air suction port of the first compressor through a second heat exchange pipeline of the auxiliary heat exchanger and the heat regenerator, and the auxiliary heat exchanger is used for cooling the refrigerant discharged by the first compressor.
Furthermore, a bypass branch is arranged on the outlet side of the first heat exchange pipeline of the heat regenerator and used for returning part of the refrigerant flowing out of the first heat exchange pipeline to the inlet of the condenser, and a bypass valve for adjusting the flow of the refrigerant is arranged on the bypass branch.
Furthermore, the evaporator group is composed of at least two evaporators arranged in parallel;
the first heat exchange pipeline of the heat regenerator is connected with the refrigerating inlet end of the evaporator group through a liquid supply header, and the refrigerating outlet end of the evaporator group is connected with the exhaust port of the second compressor through a defrosting header;
a second heat exchange pipeline of the heat regenerator is connected with a refrigeration inlet end of the evaporator group through a liquid return header, and a refrigeration outlet end of the evaporator group is connected with an air suction port of the first compressor through an air return header;
the liquid supply collecting pipe, the liquid return collecting pipe, the defrosting collecting pipe and the air return collecting pipe are respectively provided with liquid distributing openings which are connected with the evaporators in a one-to-one correspondence mode, and each liquid distributing opening is provided with an independently working valve.
Further, when the evaporator is in a refrigerating working condition, the valve elements on the liquid supply collecting pipe and the air return collecting pipe corresponding to the evaporator are opened, and the valve elements on the defrosting collecting pipe and the liquid return collecting pipe corresponding to the evaporator are closed;
when the evaporator is in a defrosting working condition, the valve elements on the liquid supply collecting pipe and the air return collecting pipe corresponding to the evaporator are closed, and the valve elements on the defrosting collecting pipe and the liquid return collecting pipe corresponding to the evaporator are opened.
Furthermore, the refrigeration inlet end of each evaporator is connected with the liquid supply header and the liquid return header through two parallel branches, a throttle valve and a switching valve are installed on one branch, a one-way valve is installed on the other branch, the switching valve is opened only when the evaporator is in a refrigeration working condition, and the one-way valve only allows refrigerant to flow out of the refrigeration inlet end of the evaporator.
Furthermore, a backheating control valve is installed at the inlet side of the second heat exchange pipeline of the backheating device, the backheating control valve is kept closed when all the evaporators of the evaporator group are in a refrigeration working condition, and the backheating control valve is kept open when one evaporator is in a defrosting working condition.
The utility model discloses refrigeration plant has still been provided, include: the refrigerating system comprises the refrigerating system and a controller for controlling the running state of the refrigerating system.
In some embodiments, the refrigeration appliance is a freezer.
Compared with the prior art, the utility model discloses following beneficial effect has:
1. an auxiliary heat exchanger is added in a heat regeneration and defrosting loop, liquid refrigerant which is subjected to phase change after defrosting flows through the auxiliary heat exchanger and the heat regenerator in sequence, the liquid refrigerant and the gaseous refrigerant exhausted by the first compressor exchange heat through the auxiliary heat exchanger, the exhaust temperature of the second compressor is reduced while the liquid impact hidden danger is eliminated, the liquid supply supercooling degree is increased, the compressor work under the same pressure ratio is reduced, and the energy consumption of a refrigerating system is reduced;
2. a bypass branch is arranged between the outlet side of the first heat exchange tube of the heat regenerator and the inlet of the condenser, when the heat load of the refrigeration system is not large, a bypass valve of the bypass branch is opened, part of the refrigerant flowing out of the first heat exchange tube is sent back to the inlet of the condenser, the redundant cold energy is utilized to reduce the load of the condenser, and the refrigeration efficiency is improved.
Drawings
The invention is explained in more detail below with reference to exemplary embodiments and the accompanying drawings, in which:
fig. 1 is a schematic connection diagram of the refrigeration system of the present invention.
Detailed Description
In order to make the technical problem, technical solution and advantageous effects to be solved by the present invention more clearly understood, the following description is given in conjunction with the accompanying drawings and embodiments to illustrate the present invention in further detail. It should be understood that the specific embodiments described herein are merely illustrative of the present patent and are not limiting upon the present patent.
As shown in fig. 1, the utility model provides a refrigerating system is applicable to refrigeration plant, especially freezer etc.. The refrigeration system includes: the system comprises a compressor set, a condenser 5, an evaporator group 6, a heat regenerator 11, an auxiliary heat exchanger 12 and the like, wherein the compressor set, the condenser 5 and the evaporator group 6 are connected to form a refrigeration cycle loop, and the compressor set, the evaporator group 6, the auxiliary heat exchanger 12 and the heat regenerator 11 are connected to form a heat regeneration defrosting loop.
The compressor unit comprises a first compressor 1 and a second compressor 2 which are arranged in series, wherein the first compressor 1 is a low-pressure compressor, the second compressor 1 is a high-pressure compressor, a refrigerant discharged from the first compressor 1 is sent to an air suction port of the second compressor 2, an exhaust port of the first compressor 1 is connected with a first oil separator 3, an exhaust port of the second compressor 2 is connected with a second oil separator 4, the refrigerant discharged from the exhaust port of the first compressor 1 is separated and sent to the air suction port of the second compressor 2 through the first oil separator 3, and the refrigerant discharged from the exhaust port of the second compressor 2 is separated and sent to a condenser 5 through the second oil separator 4.
The heat regenerator 11 and the auxiliary heat exchanger 12 both have two sets of heat exchange pipelines, a first heat exchange pipeline of the heat regenerator 11 is connected between an outlet of the condenser and a refrigeration inlet end of the evaporator group 6, the first heat exchange pipeline of the heat regenerator 11 belongs to a part of a refrigeration cycle loop, a second heat exchange pipeline of the heat regenerator 11 is connected between an outlet of the second heat exchange pipeline of the auxiliary heat exchanger 12 and an air suction port of the first compressor 1, and the second heat exchange pipeline of the heat regenerator 11 belongs to a part of a heat regeneration defrosting loop. The first heat exchange pipeline of the auxiliary heat exchanger 12 is connected between the exhaust port of the first compressor 1 and the suction port of the second compressor 2, more precisely, between the air outlet of the first oil separator 3 and the suction port of the second compressor 2, the first heat exchange pipeline of the auxiliary heat exchanger 12 belongs to a part of the refrigeration cycle loop, the second heat exchange pipeline of the auxiliary heat exchanger 12 is connected between the refrigeration inlet end of the evaporator group and the second heat exchange pipeline inlet of the heat regenerator 11, and the second heat exchange pipeline of the auxiliary heat exchanger 12 belongs to a part of the regenerative defrosting loop.
The refrigerant flowing out of the condenser 5 is sent to the evaporator in the evaporator group 6 under the refrigeration condition through the first heat exchange pipeline of the heat regenerator 11 for refrigeration, and the refrigerant flowing out after the evaporator in the defrosting condition in the evaporator group 6 is defrosted sequentially passes through the second heat exchange pipeline of the auxiliary heat exchanger 12 and the second heat exchange pipeline of the heat regenerator 11 and is sent back to the suction port of the first compressor 1. That is, the liquid refrigerant undergoing phase change after defrosting exchanges heat with the gaseous refrigerant discharged from the first compressor 1 through the auxiliary heat exchanger 12 to complete the first heat absorption, and the refrigerant flowing out of the auxiliary heat exchanger 12 exchanges heat with the refrigerant flowing out of the condenser 5 through the heat regenerator 11 to complete the second heat absorption. The design has the advantages that firstly, the liquid refrigerant generated by defrosting realizes twice heat absorption through the auxiliary heat exchanger 12 and the heat regenerator 11, the liquid refrigerant is gasified and enters the air suction port of the compressor unit, the normal operation of the system is ensured, and the liquid impact phenomenon is avoided; secondly, the gaseous refrigerant discharged by the first compressor 1 is cooled through the auxiliary heat exchanger 12, the exhaust temperature of the compressor unit and the heat load of the condenser 5 are reduced, the work of the compressor unit under the same pressure ratio is reduced, the energy consumption of the system is reduced, and the refrigeration efficiency is improved; thirdly, the refrigerant of the second heat exchange pipeline absorbs the heat of the refrigerant of the first heat exchange pipeline, the supercooling degree of the refrigerant flowing out of the first heat exchange pipeline is improved, and the refrigeration effect is optimized; and fourthly, the temperature of lubricating oil of the compressor unit is reduced, and oil return of the compressor unit is facilitated.
In some embodiments, a bypass branch is disposed at an outlet side of the first heat exchange pipeline of the heat regenerator 11, the bypass branch is configured to return a portion of the refrigerant flowing out of the first heat exchange pipeline to an inlet of the condenser 5, a bypass valve 13 for adjusting a flow rate of the bypass branch is installed in the bypass branch, the bypass valve 13 of the bypass branch is opened when a thermal load of the refrigeration system is not large, the portion of the refrigerant flowing out of the first heat exchange pipeline is returned to the inlet of the condenser 5, and the redundant cooling capacity is utilized to reduce a load of the condenser 5, thereby improving the refrigeration efficiency. For example, the thermal load condition of the refrigeration system is judged according to the opening degree of the refrigeration evaporator, when the opening degree of the throttle valve exceeding half of the refrigeration evaporators is smaller than the set opening degree, the thermal load of the refrigeration system is not large at present, the cold quantity provided by the first heat exchange pipeline of the heat regenerator is surplus, at the moment, the bypass valve is opened, part of the refrigerant flowing out of the first heat exchange pipeline of the heat regenerator is sent back to the inlet of the condenser, and the part of the refrigerant is mixed with the high-temperature refrigerant discharged by the second compressor for cooling, so that the load of the condenser is reduced.
In some embodiments, the evaporator group 6 is composed of at least two evaporators arranged in parallel, the evaporators can be installed in different rooms, each evaporator can be independently switched into a refrigeration cycle or a regenerative defrosting cycle, two ends of the evaporator group 6 are a refrigeration inlet end and a refrigeration outlet end, respectively, and since the refrigerant flow directions of the evaporators in the regenerative defrosting cycle or the refrigeration cycle are opposite, the refrigeration inlet end of the evaporator group 6 is actually a defrosting outlet end, and the refrigeration outlet end is actually a defrosting inlet end.
The connection structure of the refrigeration system is described in detail below, a first heat exchange pipeline of the heat regenerator 11 is connected to a refrigeration inlet end of the evaporator group 6 through the liquid supply header 7, a refrigeration outlet end of the evaporator group 6 is connected to an exhaust port of the second compressor 2 through the defrosting header 9, a second heat exchange pipeline of the heat regenerator 11 is connected to the refrigeration inlet end of the evaporator group 6 through the liquid return header 8, and the refrigeration outlet end of the evaporator group 6 is connected to an air suction port of the first compressor 1 through the air return header 10. The end part of each collecting pipe connected with the evaporator group 6 is provided with a plurality of liquid separating ports with the same number as the evaporators, the liquid separating ports are connected with the evaporators in a one-to-one correspondence mode, and each liquid separating port is provided with an independently working valve. When the evaporator is in a refrigeration working condition, the valve elements on the liquid supply header 7 and the air return header 10 corresponding to the evaporator are opened, and the valve elements on the defrosting header 9 and the liquid return header 8 corresponding to the evaporator are closed; when the evaporator is in a defrosting condition, the valve elements on the liquid supply manifold 7 and the air return manifold 10 corresponding to the evaporator are closed, and the valve elements on the defrosting manifold 9 and the liquid return manifold 8 corresponding to the evaporator are opened.
Specifically, a liquid supply electromagnetic valve is installed at each liquid distribution port of the liquid supply header 7, a liquid return electromagnetic valve is installed at each liquid distribution port of the liquid return header 8, a defrosting electromagnetic valve is installed at each liquid distribution port of the defrosting header 9, and a gas return electromagnetic valve is installed at each liquid distribution port of the gas return header 10, so that independent control of each evaporator is realized through a valve and the liquid distribution ports, and the refrigerant can be uniformly distributed.
In some embodiments, the refrigeration inlet end of each evaporator is connected to the liquid supply header 7 and the liquid return header 8 by two parallel branches, one branch is provided with a throttle valve and a switching valve, the other branch is provided with a check valve, the switching valve is opened only when the evaporator is in a refrigeration condition, and the check valve only allows refrigerant to flow out of the refrigeration inlet end of the evaporator. The inlet of the second heat exchange pipeline of the regenerator 11 is provided with a regenerative control valve 14, and the regenerative control valve 14 is kept closed when all the evaporators of the evaporator group 6 are in the refrigeration working condition.
As shown in FIG. 1, for example, an evaporator group comprises four evaporators 6-1 to 6-4, liquid supply electromagnetic valves of the four evaporators are 7-1 to 7-4 from left to right, liquid return electromagnetic valves are 8-1 to 8-4 from left to right, defrosting electromagnetic valves are 9-1 to 9-4 from left to right, and air return electromagnetic valves are 10-1 to 10-4 from right to left, and the working flow of the refrigeration system is as follows.
All evaporators are in a refrigeration mode, liquid supply electromagnetic valves 7-1-7-4 are opened, liquid return electromagnetic valves 8-1-8-4 are closed, defrosting electromagnetic valves 9-1-9-4 are closed, air return electromagnetic valves 10-1-10-4 are opened, and heat return control valves and bypass valves are closed. The refrigerant flow direction is as follows: high-temperature and high-pressure gaseous refrigerant discharged from the second compressor 2 → the second oil separator 4 → the condenser 5 → the regenerator 11 → the liquid supply solenoid valve → the throttle valve → the evaporator → the air return solenoid valve → the suction port of the first compressor 1 → the first oil separator 3 → the suction port of the second compressor 2.
Part of evaporators enter a defrosting working condition, and the other part of evaporators are in a refrigeration mode, taking the evaporator 5-1 for defrosting and the evaporators 5-2, 5-3 and 5-4 for refrigeration as an example: the defrosting electromagnetic valve 9-1 is opened, and the defrosting electromagnetic valves 9-2, 9-3 and 9-4 are closed; the liquid supply electromagnetic valve 7-1 is closed, and the liquid supply electromagnetic valves 7-2, 7-3 and 7-4 are opened; the liquid return electromagnetic valve 8-1 is opened, the liquid return electromagnetic valves 8-2, 8-3 and 8-4 are closed, the heat return control valve 14 is opened, and the bypass valve 13 is opened when the heat load of the refrigeration system is not large. The refrigerant flow direction in the refrigeration mode is as follows: high-temperature and high-pressure gaseous refrigerant discharged from the second compressor 2 → the second oil separator 4 → the condenser 5 → the regenerator 11 → the liquid supply solenoid valve → the throttle valve → the evaporator → the air return solenoid valve → the suction port of the first compressor 1 → the first oil separator 3 → the suction port of the second compressor 2; the refrigerant flow direction of the defrosting working condition is as follows: high-temperature and high-pressure gaseous refrigerant discharged from the second compressor 2 → the second oil separator 4 → the defrosting solenoid valve → the evaporator → the check valve → the liquid return solenoid valve → the regenerative control valve → the auxiliary heat exchanger 12 → the regenerator 11 → the suction port of the first compressor 1 → the first oil separator 3 → the suction port of the second compressor 2.
The utility model also provides a refrigeration plant, include: the refrigerating system and the controller for controlling the running state of the refrigerating system, and the refrigerating equipment can be a refrigeration house and the like.
The above description is only exemplary of the present invention and should not be taken as limiting the scope of the present invention, as any modifications, equivalents, improvements and the like made within the spirit and principles of the present invention are intended to be included within the scope of the present invention.
Claims (8)
1. A refrigeration system, comprising:
the refrigeration cycle loop is formed by connecting a compressor unit, a condenser and an evaporator unit, wherein the compressor unit comprises a first compressor and a second compressor which are arranged in series, and a refrigerant discharged by the first compressor is sent to a suction port of the second compressor;
the heat recovery defrosting circuit is formed by connecting the compressor unit, the evaporator group, the auxiliary heat exchanger and the heat regenerator, a refrigerant flowing out of the condenser is sent to the evaporator group for refrigeration through a first heat exchange pipeline of the heat regenerator, the refrigerant flowing out of the evaporator group defrosting sequentially passes through the auxiliary heat exchanger and a second heat exchange pipeline of the heat regenerator and is sent back to an air suction port of the first compressor, and the auxiliary heat exchanger is used for cooling the refrigerant discharged by the first compressor.
2. The refrigerating system of claim 1, wherein a bypass branch is disposed at an outlet side of the first heat exchange line of the heat regenerator, the bypass branch is configured to return a portion of the refrigerant flowing out of the first heat exchange line to an inlet of the condenser, and the bypass branch is provided with a bypass valve for adjusting a flow rate of the bypass branch.
3. The refrigeration system according to claim 1, wherein the evaporator group is composed of at least two evaporators arranged in parallel;
the first heat exchange pipeline of the heat regenerator is connected with the refrigerating inlet end of the evaporator group through a liquid supply header, and the refrigerating outlet end of the evaporator group is connected with the exhaust port of the second compressor through a defrosting header;
a second heat exchange pipeline of the heat regenerator is connected with a refrigeration inlet end of the evaporator group through a liquid return header, and a refrigeration outlet end of the evaporator group is connected with an air suction port of the first compressor through an air return header;
the liquid supply collecting pipe, the liquid return collecting pipe, the defrosting collecting pipe and the air return collecting pipe are respectively provided with liquid distributing openings which are connected with the evaporators in a one-to-one correspondence mode, and each liquid distributing opening is provided with an independently working valve.
4. The refrigerant system as set forth in claim 3, wherein when said evaporator is in a cooling condition, valves on said supply header and said return header corresponding to said evaporator are open and valves on said defrost header and said return header corresponding to said evaporator are closed;
when the evaporator is in a defrosting condition, the valve elements on the liquid supply header and the air return header corresponding to the evaporator are closed, and the valve elements on the defrosting header and the liquid return header corresponding to the evaporator are opened.
5. A refrigeration system as recited in claim 3 wherein the refrigerant inlet end of each of said evaporators is connected to said supply header and said return header by two parallel branches, one branch being fitted with a throttle valve and a switching valve, the other branch being fitted with a check valve, said switching valve being opened only when said evaporator is in a refrigeration mode, said check valve allowing refrigerant to flow only out of the refrigerant inlet end of said evaporator.
6. The refrigeration system according to claim 1, wherein a regenerative control valve is installed on an inlet side of the second heat exchange line of the regenerator, the regenerative control valve is kept closed when all evaporators of the evaporator group are in a cooling condition, and the regenerative control valve is kept open when any evaporator is in a defrosting condition.
7. A refrigeration appliance comprising: a refrigeration system and a controller for controlling an operation state of the refrigeration system, wherein the refrigeration system employs the refrigeration system according to any one of claims 1 to 6.
8. The refrigeration appliance of claim 7 wherein the refrigeration appliance is a freezer.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202221389824.9U CN217464934U (en) | 2022-06-06 | 2022-06-06 | Refrigerating system and refrigerating equipment |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202221389824.9U CN217464934U (en) | 2022-06-06 | 2022-06-06 | Refrigerating system and refrigerating equipment |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114811986A (en) * | 2022-06-06 | 2022-07-29 | 珠海格力电器股份有限公司 | Refrigeration system, defrosting control method and refrigeration equipment |
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- 2022-06-06 CN CN202221389824.9U patent/CN217464934U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114811986A (en) * | 2022-06-06 | 2022-07-29 | 珠海格力电器股份有限公司 | Refrigeration system, defrosting control method and refrigeration equipment |
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