CN104075477A - Cascade high-temperature heat pump - Google Patents
Cascade high-temperature heat pump Download PDFInfo
- Publication number
- CN104075477A CN104075477A CN201410274382.7A CN201410274382A CN104075477A CN 104075477 A CN104075477 A CN 104075477A CN 201410274382 A CN201410274382 A CN 201410274382A CN 104075477 A CN104075477 A CN 104075477A
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- communicated
- compressor
- low
- mouth
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention discloses a cascade high-temperature heat pump. The cascade high-temperature heat pump comprises a low-pressure system, a high-pressure system and a third heat exchanger. The low-pressure system comprises a first compressor and a first four-way valve, and the C port, the S port and the E port of the first four-way valve are communicated with the third heat exchanger, the air return port of the first compressor and a first heat exchanger respectively; the first heat exchanger and the third heat exchanger are sequentially communicated with a separating pipe, a first throttle device, a subcooling copper pipe and a high-pressure liquid storage tank, wherein the subcooling copper pipe is arranged at the bottom of the first heat exchanger. When a unit works in a low-ambient-temperature heating mode, the first heat exchanger is prone to frosting, by the time, after refrigerant passes through the subcooling copper pipe, the subcooling copper pipe can dissipate heat into the first heat exchanger to heat the first heat exchanger; meanwhile, during the working process of the unit, the subcooling pipe continuously dissipates heat to the first heat exchanger, so that the first heat exchanger can avoid frosting, high system evaporation capacity can be increased, and the system low-temperature heating capacity can be effectively improved.
Description
Technical field
The present invention relates to a kind of cascade high-temperature heat pump, particularly relate to a kind of cascade high-temperature heat pump of evaporimeter frosting while preventing low-pressure system heating operation.
Background technology
Traditional air source heat pump system heating capacity under low temperature environment can progressively reduce, and cannot guarantee to stablize comfortable winter heating, and this just makes air source heat pump to apply at cold district, has limited the range of application of air source heat pump.
In order to solve the problem that heats under low ring temperature, some producer has released cascade type heat pump, although further improved the heating efficiency of air source heat pump, guaranteed the effect of its low-temperature heating, but, it is faced with the problem of frosting, defrosting too, when environment temperature is very low, evaporimeter in low-pressure system will be easy to frosting, and this just need to do defrosting and process, at present, common cascade type heat pump adopts the mode of hot-gas bypass to defrost conventionally, but through actual verification, this way still exists defrosting effect not obvious, halfway defect.
Summary of the invention
Object of the present invention, is to provide a kind of evaporimeter frosting can effectively prevent low-pressure system heating operation time, the thorough cascade high-temperature heat pump of quickly defrosting.
The solution that the present invention solves its technical problem is: a kind of cascade high-temperature heat pump, it comprises low-pressure system, high-pressure system and connection low-pressure system, the 3rd heat exchanger between high-pressure system, described low-pressure system comprises having the first compressor of gas returning port and exhaust outlet and the first cross valve being communicated with the exhaust outlet of the first compressor, the C mouth of described the first cross valve is communicated with the 3rd heat exchanger, the S mouth of the first cross valve is communicated with the gas returning port of the first compressor after by the first gas-liquid separator, the E mouth of the first cross valve is communicated with First Heat Exchanger, between described First Heat Exchanger and the 3rd heat exchanger, by pipeline, be communicated with successively separating tube, first throttle device, cross cold copper pipe and high pressure fluid reservoir, the cold copper pipe of described mistake is positioned at the bottom of First Heat Exchanger, described high-pressure system comprises having the second compressor of gas returning port and exhaust outlet and the second cross valve being communicated with the exhaust outlet of the second compressor, the C mouth of described the second cross valve is communicated with the second heat exchanger, the S mouth of the second cross valve is communicated with the gas returning port of the second compressor after by the second gas-liquid separator, the E mouth of the second cross valve is communicated with the 3rd heat exchanger, between described the second heat exchanger and the 3rd heat exchanger, by pipeline, is communicated with successively the second throttling arrangement and high pressure fluid reservoir.
As the further improvement of technique scheme, between described First Heat Exchanger and first throttle device, be parallel with discharge, between described discharge and first throttle device, check valve is installed.
As the further improvement of technique scheme, described the 3rd heat exchanger is refrigerant-refrigerant heat exchanger, and described First Heat Exchanger is air-refrigerant heat exchanger, and described the second heat exchanger is water-refrigerant heat exchanger.
The invention has the beneficial effects as follows: the present invention was provided with cold copper pipe by the bottom at First Heat Exchanger, when the low ring temperature of unit heating operation, First Heat Exchanger is easy to frosting, now cold-producing medium is after cold copper pipe, cross cold copper pipe and will give out heat in First Heat Exchanger, to First Heat Exchanger, heat, simultaneously in the running of unit, because cross cold copper pipe, constantly distributing heat to First Heat Exchanger, so, make First Heat Exchanger be not easy frosting, system evaporation quantitative change is large, has effectively improved system hypothermia heating capacity.
Accompanying drawing explanation
In order to be illustrated more clearly in the technical scheme in the embodiment of the present invention, below the accompanying drawing of required use during embodiment is described is briefly described.Obviously, described accompanying drawing is a part of embodiment of the present invention, rather than whole embodiment, and those skilled in the art is not paying under the prerequisite of creative work, can also obtain other designs and accompanying drawing according to these accompanying drawings.
Fig. 1 is structural representation of the present invention.
The specific embodiment
Below with reference to embodiment and accompanying drawing, the technique effect of design of the present invention, concrete structure and generation is clearly and completely described, to understand fully object of the present invention, feature and effect.Obviously; described embodiment is a part of embodiment of the present invention, rather than whole embodiment, based on embodiments of the invention; other embodiment that those skilled in the art obtains under the prerequisite of not paying creative work, all belong to the scope of protection of the invention.In addition, all connection/annexations of mentioning in literary composition, not singly refer to that member directly joins, and refer to and can by adding or reducing, connect auxiliary according to concrete performance, form more excellent draw bail.
With reference to Fig. 1, a kind of cascade high-temperature heat pump, it comprises low-pressure system 6, high-pressure system 15 and connection low-pressure system 6, the 3rd heat exchanger 19 between high-pressure system 15, described low-pressure system 6 comprises having the first compressor 1 of gas returning port and exhaust outlet and the first cross valve 2 being communicated with the exhaust outlet of the first compressor 1, the C mouth of described the first cross valve 2 is communicated with the 3rd heat exchanger 19, the S mouth of the first cross valve 2 is communicated with the gas returning port of the first compressor 1 afterwards by the first gas-liquid separator 7, the E mouth of the first cross valve 2 is communicated with First Heat Exchanger 4, between described First Heat Exchanger 4 and the 3rd heat exchanger 19, by pipeline, be communicated with successively separating tube 10, first throttle device 8, cross cold copper pipe 5 and high pressure fluid reservoir 11, the cold copper pipe 5 of described mistake is positioned at the bottom of First Heat Exchanger 4, described high-pressure system 15 comprises having the second compressor 17 of gas returning port and exhaust outlet and the second cross valve 18 being communicated with the exhaust outlet of the second compressor 17, the C mouth of described the second cross valve 18 is communicated with the second heat exchanger 16, the S mouth of the second cross valve 18 is communicated with the gas returning port of the second compressor 17 afterwards by the second gas-liquid separator 13, the E mouth of the second cross valve 18 is communicated with the 3rd heat exchanger 19, between described the second heat exchanger 16 and the 3rd heat exchanger 19, by pipeline, is communicated with successively the second throttling arrangement 12 and high pressure fluid reservoir 11.Certainly, also comprise the water pump 14 being connected with the second heat exchanger 16.
By the bottom at First Heat Exchanger 4, be provided with cold copper pipe 5, when the low ring temperature of unit heating operation, First Heat Exchanger 4 is easy to frosting, now cold-producing medium is after cold copper pipe 5, cross cold copper pipe 5 and will give out heat in First Heat Exchanger 4, give First Heat Exchanger 4 heating, simultaneously in the running of unit, because cross cold copper pipe 5, constantly distributing heat to First Heat Exchanger 4, so, make First Heat Exchanger 4 be not easy frosting, system evaporation quantitative change is large, has effectively improved system hypothermia heating capacity.
Be further used as preferred embodiment, between described First Heat Exchanger 4 and first throttle device 8, be parallel with discharge 3, between described discharge 3 and first throttle device 8, check valve 9 is installed.
During unit Defrost operation, from the first compressor 1 high temperature refrigerant out, by discharge 3, pass in and out First Heat Exchangers 4, because discharge 3 inner spaces are large, reduced the resistance of the turnover First Heat Exchanger 4 of high temperature refrigerant, accelerate the flow velocity of high temperature refrigerant in First Heat Exchanger 4 inside, effectively shortened unit defrosting time.Guaranteed the low-temperature heating efficiency of unit.
Be further used as preferred embodiment, described the 3rd heat exchanger 19 is refrigerant-refrigerant heat exchanger, and described First Heat Exchanger 4 is air-refrigerant heat exchanger, and described the second heat exchanger 16 is water-refrigerant heat exchanger.
Below the preferred embodiment of the invention.
One, heating operation: the second compressor 17 is first opened, the rear unlatching of the first compressor 1.
High-pressure system: the second compressor 17 is discharged the refrigerant gas of HTHP, high-temperature high-pressure refrigerant gas flows to from the D mouth of the second cross valve 18, from the C mouth of the second cross valve 18, flow out, enter in the second heat exchanger 16, carry out becoming cryogenic high pressure refrigerant liquid after heat exchange with the cold water entering in the second heat exchanger 16 simultaneously, cryogenic high pressure refrigerant liquid, after reducing pressure by regulating flow in the second throttling arrangement 12, flows in the 3rd heat exchanger 19 by high pressure fluid reservoir 11.The refrigerant liquid of low-temp low-pressure has absorbed the 3rd heat exchanger 19 heat that condensation discharges in low-pressure system for evaporation in the 3rd heat exchanger 19, complete low-temperature low-pressure refrigerant gas after evaporation successively through E mouth, the S mouth of the second cross valve 18, enter the second gas-liquid separator 13, from the second gas-liquid separator 13, flow out again, from the gas returning port of the second compressor 17, get back to the second compressor 17.
Low-pressure system: the first compressor 1 is discharged the refrigerant gas of HTHP, high-temperature high-pressure refrigerant gas flows to from the D mouth of the first cross valve 2, from the C mouth of the first cross valve 2, flow out, enter in the 3rd heat exchanger 19 with high-pressure system in the refrigerant liquid of low-temp low-pressure carry out becoming after heat exchange the refrigerant liquid of cryogenic high pressure, cryogenic high pressure refrigerant liquid was flowed in cold copper pipe 5 and was carried out cold treatment by high pressure fluid reservoir 11, then after reducing pressure by regulating flow in first throttle device 8, by separating tube 10, flow in First Heat Exchanger 4 and evaporate.Complete evaporation low-temperature low-pressure refrigerant gas afterwards successively through E mouth, the S mouth of the first cross valve 2, enter the first gas-liquid separator 7, then flow out from the first gas-liquid separator 7, from the gas returning port of the first compressor 1, get back to the first compressor 1.
Two, Defrost operation: the first compressor 1 is first opened, the rear unlatching of the second compressor 17.
Low-pressure system: the first compressor 1 is discharged the refrigerant gas of HTHP, high-temperature high-pressure refrigerant gas flows to from the D mouth of the first cross valve 2, from the E mouth of the first cross valve 2, flow out, enter in First Heat Exchanger 4 and carry out becoming cryogenic high pressure refrigerant liquid after condensation, cryogenic high pressure refrigerant liquid flows in first throttle devices 8 after reducing pressure by regulating flow by discharge 3, check valve 9, then is flow in the 3rd heat exchanger 19 and evaporated by high pressure fluid reservoir 11.Complete evaporation low-temperature low-pressure refrigerant gas afterwards successively through C mouth, the S mouth of the first cross valve 2, enter the first gas-liquid separator 7, then flow out from the first gas-liquid separator 7, from the gas returning port of the first compressor 1, get back to the first compressor 1.
High-pressure system: the second compressor 17 is discharged the refrigerant gas of HTHP, high-temperature high-pressure refrigerant gas flows to from the D mouth of the second cross valve 18, from the E mouth of the second cross valve 18, flow out, enter in the 3rd heat exchanger 19 and carry out becoming cryogenic high pressure refrigerant liquid after condensation, cryogenic high pressure refrigerant liquid enters in the second throttling arrangement 12 after reducing pressure by regulating flow by high pressure fluid reservoir 11 again, flow in the second heat exchanger 16 and evaporate, complete low-temperature low-pressure refrigerant gas after evaporation successively through the C mouth of the second cross valve 18, S mouth, enter the second gas-liquid separator 13, from the second gas-liquid separator 13, flow out again, from the gas returning port of the second compressor 17, get back to the second compressor 17.
More than that better embodiment of the present invention is illustrated, but the invention is not limited to described embodiment, those of ordinary skill in the art also can make all equivalent modifications or replacement under the prerequisite without prejudice to spirit of the present invention, and the modification that these are equal to or replacement are all included in the application's claim limited range.
Claims (3)
1. a cascade high-temperature heat pump, it comprises low-pressure system, high-pressure system and connection low-pressure system, the 3rd heat exchanger between high-pressure system, it is characterized in that: described low-pressure system comprises having the first compressor of gas returning port and exhaust outlet and the first cross valve being communicated with the exhaust outlet of the first compressor, the C mouth of described the first cross valve is communicated with the 3rd heat exchanger, the S mouth of the first cross valve is communicated with the gas returning port of the first compressor after by the first gas-liquid separator, the E mouth of the first cross valve is communicated with First Heat Exchanger, between described First Heat Exchanger and the 3rd heat exchanger, by pipeline, be communicated with successively separating tube, first throttle device, cross cold copper pipe and high pressure fluid reservoir, the cold copper pipe of described mistake is positioned at the bottom of First Heat Exchanger, described high-pressure system comprises having the second compressor of gas returning port and exhaust outlet and the second cross valve being communicated with the exhaust outlet of the second compressor, the C mouth of described the second cross valve is communicated with the second heat exchanger, the S mouth of the second cross valve is communicated with the gas returning port of the second compressor after by the second gas-liquid separator, the E mouth of the second cross valve is communicated with the 3rd heat exchanger, between described the second heat exchanger and the 3rd heat exchanger, by pipeline, is communicated with successively the second throttling arrangement and high pressure fluid reservoir.
2. cascade high-temperature heat pump according to claim 1, is characterized in that: between described First Heat Exchanger and first throttle device, be parallel with discharge, between described discharge and first throttle device, check valve be installed.
3. cascade high-temperature heat pump according to claim 1 and 2, is characterized in that: described the 3rd heat exchanger is refrigerant-refrigerant heat exchanger, and described First Heat Exchanger is air-refrigerant heat exchanger, and described the second heat exchanger is water-refrigerant heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410274382.7A CN104075477B (en) | 2014-06-18 | 2014-06-18 | Cascade high-temperature heat pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410274382.7A CN104075477B (en) | 2014-06-18 | 2014-06-18 | Cascade high-temperature heat pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104075477A true CN104075477A (en) | 2014-10-01 |
| CN104075477B CN104075477B (en) | 2017-02-22 |
Family
ID=51596925
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410274382.7A Active CN104075477B (en) | 2014-06-18 | 2014-06-18 | Cascade high-temperature heat pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104075477B (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104406340A (en) * | 2014-10-28 | 2015-03-11 | 广东芬尼克兹节能设备有限公司 | Overlapping type heat pump compressor control method and system |
| CN105865083A (en) * | 2016-04-29 | 2016-08-17 | 广东高而美制冷设备有限公司 | Trigeneration system capable of recovering heat |
| CN105937822A (en) * | 2016-06-21 | 2016-09-14 | 广东芬尼克兹节能设备有限公司 | Cascade type high-temperature heat pump with high defrosting performance and control method of cascade type high-temperature heat pump |
| CN106766413A (en) * | 2016-11-28 | 2017-05-31 | 镇江恒安防爆电器有限公司 | A kind of energy-conservation, rapid frost melting heater |
| CN107062607A (en) * | 2017-03-23 | 2017-08-18 | 济南明湖制冷空调设备有限公司 | Overlapping air energy liquid heating |
| CN108036557A (en) * | 2017-12-28 | 2018-05-15 | 广东芬尼克兹节能设备有限公司 | A kind of parallel connection Cascade type heat pump system |
| CN108954886A (en) * | 2018-08-21 | 2018-12-07 | 珠海格力电器股份有限公司 | cascade heat pump system and control method thereof |
| CN110285619A (en) * | 2019-06-28 | 2019-09-27 | 中国科学院理化技术研究所 | Cascade type heat pump control method and system |
| 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 |
| WO2021138861A1 (en) * | 2020-01-09 | 2021-07-15 | 创远亿德(天津)集团有限公司 | Multi-cycle system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04263758A (en) * | 1991-02-18 | 1992-09-18 | Kansai Electric Power Co Inc:The | Heat pump hot-water supplier |
| CN101619904A (en) * | 2009-08-02 | 2010-01-06 | 山东美琳达再生能源开发有限公司 | Two-stage heating high temperature heat pump device |
| CN202521952U (en) * | 2011-10-26 | 2012-11-07 | 广东芬尼克兹节能设备有限公司 | Ultralow temperature air source heat pump with double throttling devices |
| CN103047721A (en) * | 2012-12-21 | 2013-04-17 | 美意(浙江)空调设备有限公司 | Air-cooling cascade heat pump |
| CN203024506U (en) * | 2012-12-28 | 2013-06-26 | 广东志高暖通设备股份有限公司 | Indoor heat exchanger of air conditioner |
| CN203940648U (en) * | 2014-06-18 | 2014-11-12 | 广东芬尼克兹节能设备有限公司 | A kind of cascade high-temperature heat pump |
-
2014
- 2014-06-18 CN CN201410274382.7A patent/CN104075477B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04263758A (en) * | 1991-02-18 | 1992-09-18 | Kansai Electric Power Co Inc:The | Heat pump hot-water supplier |
| CN101619904A (en) * | 2009-08-02 | 2010-01-06 | 山东美琳达再生能源开发有限公司 | Two-stage heating high temperature heat pump device |
| CN202521952U (en) * | 2011-10-26 | 2012-11-07 | 广东芬尼克兹节能设备有限公司 | Ultralow temperature air source heat pump with double throttling devices |
| CN103047721A (en) * | 2012-12-21 | 2013-04-17 | 美意(浙江)空调设备有限公司 | Air-cooling cascade heat pump |
| CN203024506U (en) * | 2012-12-28 | 2013-06-26 | 广东志高暖通设备股份有限公司 | Indoor heat exchanger of air conditioner |
| CN203940648U (en) * | 2014-06-18 | 2014-11-12 | 广东芬尼克兹节能设备有限公司 | A kind of cascade high-temperature heat pump |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104406340A (en) * | 2014-10-28 | 2015-03-11 | 广东芬尼克兹节能设备有限公司 | Overlapping type heat pump compressor control method and system |
| CN104406340B (en) * | 2014-10-28 | 2017-01-11 | 广东芬尼克兹节能设备有限公司 | Overlapping type heat pump compressor control method and system |
| CN105865083A (en) * | 2016-04-29 | 2016-08-17 | 广东高而美制冷设备有限公司 | Trigeneration system capable of recovering heat |
| CN105937822A (en) * | 2016-06-21 | 2016-09-14 | 广东芬尼克兹节能设备有限公司 | Cascade type high-temperature heat pump with high defrosting performance and control method of cascade type high-temperature heat pump |
| CN106766413A (en) * | 2016-11-28 | 2017-05-31 | 镇江恒安防爆电器有限公司 | A kind of energy-conservation, rapid frost melting heater |
| CN107062607A (en) * | 2017-03-23 | 2017-08-18 | 济南明湖制冷空调设备有限公司 | Overlapping air energy liquid heating |
| CN108036557A (en) * | 2017-12-28 | 2018-05-15 | 广东芬尼克兹节能设备有限公司 | A kind of parallel connection Cascade type heat pump system |
| CN108036557B (en) * | 2017-12-28 | 2023-11-14 | 广东芬尼克兹节能设备有限公司 | Parallel cascade heat pump system |
| CN108954886A (en) * | 2018-08-21 | 2018-12-07 | 珠海格力电器股份有限公司 | cascade heat pump system and control method thereof |
| CN110285619A (en) * | 2019-06-28 | 2019-09-27 | 中国科学院理化技术研究所 | Cascade type heat pump control method and system |
| 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 |
| WO2021138861A1 (en) * | 2020-01-09 | 2021-07-15 | 创远亿德(天津)集团有限公司 | Multi-cycle system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104075477B (en) | 2017-02-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104075477A (en) | Cascade high-temperature heat pump | |
| CN201652663U (en) | Heat recovery heat pump air conditioning system | |
| CN104236164B (en) | Ultra-high temperature cascade water source heat pump system | |
| CN203940649U (en) | The cascade high-temperature heat pump that a kind of high efficiency heats | |
| CN104896794A (en) | Heat recovery system of air source heat pump cold and hot water unit | |
| CN203771771U (en) | Air-conditioning unit and air heat exchanger | |
| CN203964449U (en) | The switchable heat pump of a kind of single twin-stage | |
| CN104121721B (en) | Single-and-double-stage switchable heat pump | |
| CN204987596U (en) | Air source heat pump air conditioning system that defrosts | |
| CN201876033U (en) | Heat-regeneration refrigerating system with check bridge | |
| CN202382470U (en) | R32 air-cooled water chiller heat pump unit with EVI (enhanced vapor injection) compressor | |
| CN104534722A (en) | Air conditioning refrigeration equipment | |
| CN203940648U (en) | A kind of cascade high-temperature heat pump | |
| CN201866995U (en) | Hot water air-conditioning system | |
| CN204128238U (en) | A kind of can the cascade high-temperature heat pump of quickly defrosting | |
| CN203629140U (en) | Heat pump device for providing hot water with large temperature difference through gradient utilization of ventilation air methane heat energy | |
| CN105865083A (en) | Trigeneration system capable of recovering heat | |
| CN206488407U (en) | A kind of water source heat pump units device | |
| CN201652987U (en) | Novel air conditioning system with cold and hot drinking water supply functions | |
| CN204345974U (en) | Shell and tube exchanger and multifunction water-heating system | |
| CN104676964A (en) | Coal mine methane heat energy gradient utilization large-temperature difference hot water supply heat pump device | |
| CN210320592U (en) | Heat exchanger assembly and air conditioner | |
| CN204115287U (en) | With the cascade high-temperature heat pump of phase change heat accumulator | |
| CN101706186A (en) | Defrosting device of air heat energy heat pump water heater | |
| CN202501654U (en) | Air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |