CN211345914U - Wide-ring-temperature CO2 air source heat pump system - Google Patents
Wide-ring-temperature CO2 air source heat pump system Download PDFInfo
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- CN211345914U CN211345914U CN201922446023.6U CN201922446023U CN211345914U CN 211345914 U CN211345914 U CN 211345914U CN 201922446023 U CN201922446023 U CN 201922446023U CN 211345914 U CN211345914 U CN 211345914U
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Abstract
The utility model provides a wide ring temperature type CO2 air source heat pump system, include: the system comprises a low-pressure section CO2 compressor, a high-pressure section exhaust electronic three-way valve, a high-pressure section CO2 compressor, a heat recovery plate type heat exchanger, a regenerative cycle plate type heat exchanger, a high-pressure electronic pressure regulating valve, an evaporator, a de-superheater, a gas-liquid separator, a steam distribution electronic pressure regulating valve, a low-pressure section air suction electronic three-way valve and a de-superheater check valve; the evaporator and the superheater are integrally designed, so that pre-heat dissipation is given to the subcritical compressor, heat is absorbed by evaporation of the whole system, heat compensation is given to evaporation heat absorption by the pre-heat dissipation, and the maximum recycling of a heat source is realized. The outdoor temperature change process carries out data acquisition through the controller, and the switching of heating cycle can be realized to the control electron three-way valve to the controller procedure accessible, and this switching guarantees that the system realizes the two-stage compression process under the low ring temperature condition, realizes the one-level compression process under the high ring temperature condition, can guarantee the safe and reliable operation of system.
Description
Technical Field
The utility model relates to a heat pump system technical field particularly, especially relates to a wide ring temperature type CO2 air source heat pump system.
Background
With the increase of the national requirement for environmental protection, the winter heating equipment is changed from the traditional coal-fired heat pump system using electric power. The heat pump system needs to use a refrigerant working medium, and the natural refrigerant CO2 is favored in a novel heat pump system due to its excellent environmental protection characteristic (ODP is 0, GWP is 1) and excellent heating capacity. The latitude north and south of our country is very large in span, the environmental temperature in the northern area can be as low as-40 ℃ in winter, the temperature span is very large, and the common heat pump system is difficult to adapt to the use of the low environmental temperature in the northern area.
Disclosure of Invention
According to the technical problem provided by the invention, the wide-loop-temperature CO2 air source heat pump system is provided.
The utility model discloses a technical means as follows:
a wide-loop-temperature CO2 air-source heat pump system, comprising:
the system comprises a low-pressure section CO2 compressor, an exhaust check valve, a high-pressure section exhaust electronic three-way valve, a high-pressure section CO2 compressor, a heat recovery plate heat exchanger, a regenerative cycle plate heat exchanger, a high-pressure electronic pressure regulating valve, an evaporator, a de-superheater, a gas-liquid separator, a steam distribution electronic pressure regulating valve, a low-pressure section air suction electronic three-way valve, an electric ball valve and a de-superheater check valve;
one end of the low-pressure section CO2 compressor is communicated with an air inlet pipeline of the high-pressure section CO2 compressor through an evaporator and a de-superheater through a pipeline with an exhaust one-way valve, and the de-superheater one-way valve is arranged at the outlet positions of the evaporator and the de-superheater;
the other end is communicated with one port of the low-pressure section air suction electronic three-way valve through a pipeline; the other pipeline of the low-pressure section air suction electronic three-way valve is communicated with the high-pressure section CO2 compressor, the last pipeline of the low-pressure section air suction electronic three-way valve is communicated with the gas circuit of the gas-liquid separator, and the low-pressure section air suction electronic three-way valve and the gas circuit of the gas-liquid separator are communicated through a regenerative circulating plate heat exchanger;
the output end of the high-pressure section CO2 compressor is communicated with one path of the high-pressure section exhaust electronic three-way valve, the other path of the high-pressure section exhaust electronic three-way valve is communicated with the heat recovery plate type heat exchanger, the output pipeline of the heat recovery plate type heat exchanger is communicated with the regenerative cycle plate type heat exchanger, and the output pipeline communicated with the regenerative cycle plate type heat exchanger is finally communicated with the inlet of the gas-liquid separator through the evaporator and the desuperheater; the last path of the high-pressure section exhaust electronic three-way valve is communicated with pipelines of the regenerative cycle plate heat exchanger positioned at the front ends of the evaporator and the superheater, and the pipelines are converged together and then pass through the evaporator and the superheater; the high-pressure electronic pressure regulating valve is arranged on a pipeline between the regenerative cycle plate heat exchanger and the evaporator and between the regenerative cycle plate heat exchanger and the de-superheater;
and a steam distribution electronic pressure regulating valve is arranged on the other output pipeline of the gas-liquid separator and is finally communicated with the gas circuit of the gas-liquid separator, and an electric ball valve is arranged between the outlet of the gas circuit of the gas-liquid separator and the communicated position.
When high-ring-temperature heating is carried out, a high-pressure-section CO2 compressor compresses a CO2 refrigerant, the compressed high-temperature high-pressure refrigerant gas enters a heat recovery plate type heat exchanger through a high-pressure-section exhaust electronic three-way valve, hot water is heated in the heat recovery plate type heat exchanger and the CO2 refrigerant is cooled at the same time, a high-pressure transcritical state refrigerant is formed after cooling, the transcritical refrigerant is further cooled in a regenerative cycle plate type heat exchanger and enters an evaporator after being throttled by a high-pressure electronic pressure regulating valve, a low-pressure refrigerant is evaporated and absorbs heat in the evaporator, the formed low-pressure gas refrigerant enters a regenerative cycle plate type heat exchanger through an electric ball valve, an overheated-state CO2 refrigerant is formed after passing through the plate type heat exchanger, and the overheated-state refrigerant returns to the high-pressure-section compressor after passing through a low. During the operation of the compressor, the steam distribution electronic pressure regulating valve is opened to ensure that oil in the steam can return to the compressor along with the refrigerant.
When heating at low ring temperature, a low-pressure section CO2 compressor compresses CO2 refrigerant, the refrigerant gas compressed into high temperature and medium pressure enters an evaporator and a superheater, CO2 refrigerant is cooled in the evaporator and the superheater to form medium pressure refrigerant after cooling, the medium pressure refrigerant enters a high-pressure section CO2 compressor to be continuously compressed, the refrigerant gas compressed into high temperature and high pressure enters a heat recovery plate type heat exchanger, hot water is heated in the heat recovery plate type heat exchanger and simultaneously cools CO2 refrigerant, high pressure transcritical state refrigerant is formed after cooling, the transcritical refrigerant is further cooled in a regenerative cycle plate type heat exchanger, the refrigerant enters an evaporator after being throttled by a high-pressure electronic pressure regulating valve, the low pressure refrigerant is evaporated and absorbs heat in the evaporator to form low pressure gas refrigerant, the low pressure gas refrigerant enters a regenerative cycle plate type heat exchanger after passing through an electric ball valve, and the superheated state CO2 refrigerant is formed after passing through the plate type heat exchanger, the superheated refrigerant returns to the low-pressure compressor after passing through the low-pressure suction electronic three-way valve, and the heating cycle is completed. During the operation of the compressor, the steam distribution electronic pressure regulating valve is opened to ensure that oil in the steam can return to the compressor along with the refrigerant.
During defrosting, a high-pressure section CO2 compressor compresses CO2 refrigerant, high-temperature and high-pressure refrigerant gas compressed into high-temperature and high-pressure refrigerant gas enters an evaporator after passing through a high-pressure section exhaust electronic three-way valve, the high-temperature gas is used for defrosting for the evaporator, the defrosted high-pressure refrigerant enters a regenerative cycle plate heat exchanger after being throttled and depressurized by a steam distribution electronic pressure regulating valve, and returns to the high-pressure section compressor through a low-pressure section air suction electronic three-way valve after absorbing part of heat, so that defrosting cycle is completed.
The utility model discloses a patent advantage: the wide-environment-temperature CO2 air source heat pump system can realize the heating process of high environment temperature and low environment temperature, and can well meet the application requirements in winter in northern areas of China. The hot water prepared by the heat pump system can be used for household hot water, heating and the like. The electronic three-way valve is controlled by the controller, so that intelligent conversion can be realized, and good matching performance of system operation and environmental working conditions can be realized. The system has strong practicability and universality, accords with the current energy-saving and environment-friendly design concept, and necessarily provides a good system design for the application of a future heat pump system.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required to be used in the description of the embodiments or the prior art are briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive labor.
FIG. 1 is a schematic view of a high-loop temperature heating cycle of the present invention.
FIG. 2 is a schematic view of a low-loop temperature heating cycle of the present invention.
FIG. 3-schematic view of the defrost cycle of the present invention.
In the figure: the system comprises a 1-low-pressure section CO2 compressor, a 2-exhaust one-way valve, a 3-high-pressure section exhaust electronic three-way valve, a 4-high-pressure section CO2 compressor, a 5-heat recovery plate type heat exchanger, a 6-regenerative cycle plate type heat exchanger, a 7-high-pressure electronic pressure regulating valve, an 8-evaporator and desuperheater, a 9-gas-liquid separator, a 10-steam distribution electronic pressure regulating valve, an 11-low-pressure section air suction electronic three-way valve, a 12-electric ball valve and a 13-desuperheater one-way valve.
Detailed Description
It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the invention. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
Unless specifically stated otherwise, the relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present invention. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. Any specific values in all examples shown and discussed herein are to be construed as exemplary only and not as limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the orientation words such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom", etc. are usually based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplicity of description, and in the case of not making a contrary explanation, these orientation words do not indicate and imply that the device or element in question must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the scope of the present invention: the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.
Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
It should be noted that the terms "first", "second", and the like are used to define the components, and are only used for convenience of distinguishing the corresponding components, and if not stated otherwise, the terms have no special meaning, and therefore, the scope of the present invention should not be construed as being limited.
As shown in fig. 1, the utility model provides a wide ring temperature type CO2 air source heat pump system, include:
the system comprises a low-pressure section CO2 compressor 1, an exhaust one-way valve 2, a high-pressure section exhaust electronic three-way valve 3, a high-pressure section CO2 compressor 4, a heat recovery plate type heat exchanger 5, a regenerative cycle plate type heat exchanger 6, a high-pressure electronic pressure regulating valve 7, an evaporator and a superheater removal 8, a gas-liquid separator 9, a steam distribution electronic pressure regulating valve 10, a low-pressure section air suction electronic three-way valve 11, an electric ball valve 12 and a superheater removal one-way valve 13;
one end of the low-pressure section CO2 compressor 1 is communicated with an air inlet pipeline of the high-pressure section CO2 compressor 4 through an evaporator and a de-superheater 8 through a pipeline with an exhaust one-way valve 2, and a de-superheater one-way valve 13 is arranged at the outlet positions of the evaporator and the de-superheater 8;
the other end is communicated with one port of the low-pressure section air suction electronic three-way valve 11 through a pipeline; the other pipeline of the low-pressure section air suction electronic three-way valve 11 is communicated with the high-pressure section CO2 compressor 4, the last pipeline of the low-pressure section air suction electronic three-way valve 11 is communicated with the gas circuit of the gas-liquid separator 9, and the low-pressure section air suction electronic three-way valve 11 and the gas circuit of the gas-liquid separator 9 pass through the regenerative circulating plate heat exchanger 6;
the output end of the high-pressure section CO2 compressor 4 is communicated with one path of the high-pressure section exhaust electronic three-way valve 3, the other path of the high-pressure section exhaust electronic three-way valve 3 is communicated with the heat recovery plate type heat exchanger 5, the output pipeline of the heat recovery plate type heat exchanger 5 is communicated with the regenerative cycle plate type heat exchanger 6, and the output pipeline communicated with the regenerative cycle plate type heat exchanger 6 is finally communicated with the inlet of the gas-liquid separator 9 through the evaporator and the de-superheater 8; the last path of the high-pressure section exhaust electronic three-way valve 3 is communicated with pipelines of the regenerative cycle plate heat exchanger 6 positioned at the front ends of the evaporator and the superheater 8, and the pipelines are converged together and then pass through the evaporator and the superheater 8;
the high-pressure electronic pressure regulating valve 7 is arranged on a pipeline between the regenerative cycle plate heat exchanger 6 and the evaporator and between the regenerative cycle plate heat exchanger and the de-superheater 8;
and a steam distribution electronic pressure regulating valve 10 is arranged on the other output pipeline of the gas-liquid separator 9 and is finally communicated with the gas circuit of the gas-liquid separator 9, and an electric ball valve 12 is arranged between the outlet of the gas circuit of the gas-liquid separator 9 and the communication position.
During actual use, a low-pressure section CO2 compressor 1, an exhaust check valve 2, a high-pressure section exhaust electronic three-way valve 3, a high-pressure section CO2 compressor 4, a heat recovery plate type heat exchanger 5, a regenerative cycle plate type heat exchanger 6, a high-pressure electronic pressure regulating valve 7, an evaporator, a de-superheater 8, a gas-liquid separator 9, a steam distribution electronic pressure regulating valve 10, a low-pressure section air suction electronic three-way valve 11, an electric ball valve 12 and a de-superheater check valve 13 are integrated into a whole outdoor heat pump unit, and the unit is installed outdoors to ensure good heat dissipation of a condenser and stable operation of the system.
As shown in fig. 1, the evaporator and the desuperheater 8 adopt an integrated design form, and simultaneously give the pre-heat radiation of the subcritical compressor and the evaporation absorption heat of the whole system, the pre-heat radiation can give the heat compensation of the evaporation absorption heat, and the maximum recycling of the heat source is realized.
As shown in fig. 1 and 2, the change process of the outdoor temperature is data-collected by the controller, the controller program can control the electronic three-way valves (the high-pressure exhaust electronic three-way valve 3 and the low-pressure suction electronic three-way valve 11) to realize the switching of the heating cycle, and the system can realize the two-stage compression process under the low ring temperature condition and the one-stage compression process under the high ring temperature condition through the switching, thereby ensuring the safe and reliable operation of the system and the high efficiency of the system operation.
As shown in fig. 1, during high-loop heating, a high-pressure-stage CO2 compressor compresses CO2 refrigerant, the compressed high-temperature and high-pressure refrigerant gas enters a heat recovery plate heat exchanger through a high-pressure-stage exhaust electronic three-way valve, hot water is heated in the heat recovery plate heat exchanger and the CO2 refrigerant is cooled at the same time, a high-pressure transcritical refrigerant is formed after cooling, the transcritical refrigerant is further cooled in a regenerative cycle plate heat exchanger, the refrigerant enters an evaporator after being throttled by a high-pressure electronic pressure regulating valve, low-pressure refrigerant is evaporated and absorbed in the evaporator, the formed low-pressure gas refrigerant enters a regenerative cycle plate heat exchanger through an electric ball valve, a superheated CO2 refrigerant is formed after passing through the plate heat exchanger, and the superheated refrigerant returns to the high-pressure-stage compressor after passing through a low-pressure-stage suction electronic three-way valve, so. During the operation of the compressor, the steam distribution electronic pressure regulating valve is opened to ensure that oil in the steam can return to the compressor along with the refrigerant.
As shown in fig. 2, during low-cycle-temperature heating, a low-pressure-stage CO2 compressor compresses CO2 refrigerant, the compressed high-temperature and medium-pressure refrigerant gas enters an evaporator and a superheater, CO2 refrigerant is cooled in the evaporator and the superheater to form medium-pressure refrigerant after cooling, the medium-pressure refrigerant enters a high-pressure-stage CO2 compressor to be continuously compressed, the compressed high-temperature and high-pressure refrigerant gas enters a heat recovery plate heat exchanger, hot water is heated in the heat recovery plate heat exchanger and simultaneously cools CO2 refrigerant to form high-pressure transcritical refrigerant after cooling, the transcritical refrigerant is further cooled in a regenerative cycle plate heat exchanger, the refrigerant enters the evaporator after throttling by a high-pressure electronic pressure regulating valve, the low-pressure refrigerant is evaporated in the evaporator to absorb heat, the formed low-pressure gas refrigerant enters the regenerative cycle plate heat exchanger through an electric ball valve, and the superheated CO2 refrigerant is formed after passing through the plate heat exchanger, and returns to the low-pressure section compressor after passing through the low-pressure section suction electronic three-way valve, so that the heating cycle is completed. During the operation of the compressor, the steam distribution electronic pressure regulating valve is opened to ensure that oil in the steam can return to the compressor along with the refrigerant.
As shown in fig. 3, during defrosting, a high-pressure stage CO2 compressor compresses CO2 refrigerant, the high-temperature and high-pressure refrigerant gas compressed by the high-pressure stage CO2 compressor enters an evaporator after passing through a high-pressure stage exhaust electronic three-way valve, the high-temperature gas is used for defrosting of the evaporator, the high-pressure refrigerant after defrosting enters a regenerative cycle plate heat exchanger after being throttled and depressurized by a distribution electronic pressure regulating valve, and the refrigerant returns to the high-pressure stage compressor through a low-pressure stage suction electronic three-way valve after absorbing part of heat, so that a defrosting cycle is completed.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention.
Claims (1)
1. A wide-loop-temperature CO2 air source heat pump system is characterized by comprising:
the system comprises a low-pressure section CO2 compressor (1), an exhaust check valve (2), a high-pressure section exhaust electronic three-way valve (3), a high-pressure section CO2 compressor (4), a heat recovery plate type heat exchanger (5), a regenerative cycle plate type heat exchanger (6), a high-pressure electronic pressure regulating valve (7), an evaporator, a superheater (8), a gas-liquid separator (9), a steam distribution electronic pressure regulating valve (10), a low-pressure section air suction electronic three-way valve (11), an electric ball valve (12) and a superheater removing check valve (13);
one end of the low-pressure section CO2 compressor (1) is communicated with an air inlet pipeline of the high-pressure section CO2 compressor (4) through an evaporator and a de-superheater (8) through a pipeline with an exhaust check valve (2), and a de-superheater check valve (13) is arranged at the outlet positions of the evaporator and the de-superheater (8);
the other end is communicated with one port of a low-pressure section air suction electronic three-way valve (11) through a pipeline; the other pipeline of the low-pressure section air suction electronic three-way valve (11) is communicated with the high-pressure section CO2 compressor (4), the last pipeline of the low-pressure section air suction electronic three-way valve (11) is communicated with the gas circuit of the gas-liquid separator (9), and the gas circuits of the low-pressure section air suction electronic three-way valve (11) and the gas-liquid separator (9) pass through the regenerative circulating plate heat exchanger (6);
the output end of a high-pressure section CO2 compressor (4) is communicated with one path of a high-pressure section exhaust electronic three-way valve (3), the other path of the high-pressure section exhaust electronic three-way valve (3) is communicated with a heat recovery plate type heat exchanger (5), an output pipeline of the heat recovery plate type heat exchanger (5) is communicated with a regenerative cycle plate type heat exchanger (6), and the output pipeline communicated with the regenerative cycle plate type heat exchanger (6) is finally communicated with the inlet of a gas-liquid separator (9) through an evaporator and a de-superheater (8); the last path of the high-pressure section exhaust electronic three-way valve (3) is communicated with pipelines of the regenerative cycle plate heat exchanger (6) at the front ends of the evaporator and the desuperheater (8), and the pipelines are converged together and then pass through the evaporator and the desuperheater (8);
the high-pressure electronic pressure regulating valve (7) is arranged on a pipeline between the regenerative cycle plate heat exchanger (6) and the evaporator and between the regenerative cycle plate heat exchanger and the desuperheater (8);
and a steam distribution electronic pressure regulating valve (10) is arranged on the other output pipeline of the gas-liquid separator (9), and is finally communicated with the gas circuit of the gas-liquid separator (9), and an electric ball valve (12) is arranged between the outlet of the gas circuit of the gas-liquid separator (9) and the communication position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922446023.6U CN211345914U (en) | 2019-12-30 | 2019-12-30 | Wide-ring-temperature CO2 air source heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922446023.6U CN211345914U (en) | 2019-12-30 | 2019-12-30 | Wide-ring-temperature CO2 air source heat pump system |
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| CN211345914U true CN211345914U (en) | 2020-08-25 |
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| CN201922446023.6U Withdrawn - After Issue CN211345914U (en) | 2019-12-30 | 2019-12-30 | Wide-ring-temperature CO2 air source heat pump system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111306827A (en) * | 2019-12-30 | 2020-06-19 | 松下冷机系统（大连）有限公司 | Wide-ring-temperature CO2Air source heat pump system |
-
2019
- 2019-12-30 CN CN201922446023.6U patent/CN211345914U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111306827A (en) * | 2019-12-30 | 2020-06-19 | 松下冷机系统（大连）有限公司 | Wide-ring-temperature CO2Air source heat pump system |
| CN111306827B (en) * | 2019-12-30 | 2023-08-29 | 冰山冷热科技股份有限公司 | Wide-ring temperature type CO 2 Air source heat pump system |
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Address after: 116600 No. 8 Songlan Street, Dalian Economic and Technological Development Zone, Liaoning Province Patentee after: Bingshan Songyang Refrigerator System (Dalian) Co.,Ltd. Address before: 116000 No.8 Songlan street, Jinzhou new district, Dalian City, Liaoning Province Patentee before: PANASONIC REFRIGERATOR SYSTEM (DALIAN) CO.,LTD. |
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Effective date of registration: 20230530 Address after: No. 106 Liaohe East Road, Dalian Economic and Technological Development Zone, Liaoning Province, 116600 Patentee after: Iceberg cold and hot technology Co.,Ltd. Address before: 116600 No. 8 Songlan Street, Dalian Economic and Technological Development Zone, Liaoning Province Patentee before: Bingshan Songyang Refrigerator System (Dalian) Co.,Ltd. |
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Granted publication date: 20200825 Effective date of abandoning: 20230829 |
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