CN109350983B

CN109350983B - Double-stage compression type heat pump double-effect evaporation concentration system

Info

Publication number: CN109350983B
Application number: CN201811544907.9A
Authority: CN
Inventors: 张承虎; 陈�峰; 陈长建; 赵娟
Original assignee: Shanghai Enn New Energy Technology Co ltd
Current assignee: Shanghai Enn New Energy Technology Co ltd
Priority date: 2018-12-17
Filing date: 2018-12-17
Publication date: 2024-03-19
Anticipated expiration: 2038-12-17
Also published as: CN109350983A

Abstract

A double-stage compression type heat pump double-effect evaporation concentration system relates to a double-effect evaporation concentration circulation system. The invention aims to solve the problems of higher energy consumption and lower vacuum degree of the conventional double-effect evaporation concentration system. The invention comprises a first compressor, a heat pump condenser, a heat pump first evaporator, a heat pump second evaporator, a second compressor, a first intermediate water circulation pipeline, a second intermediate water circulation pipeline, a first-effect evaporation tank, a second-effect evaporation tank, a starter, a condensate collection tank, a first starting steam generating pipeline, a first-effect juice steam pipeline, a second-effect juice steam pipeline, a starting secondary steam pipeline, a total condensate pipeline, a second first-effect juice steam pipeline and a second starting steam generating pipeline. The invention can be applied to the evaporation concentration process of industrial production such as pharmacy, milk powder, amino acid, environmental protection water treatment and the like, and can recover the waste heat of the two-effect juice steam, thereby realizing the purpose of energy-saving production.

Description

Double-stage compression type heat pump double-effect evaporation concentration system

Technical Field

The invention relates to a system for double-effect evaporation concentration by utilizing a heat pump technology, in particular to a double-stage compression type heat pump double-effect evaporation concentration system.

Background

In the evaporation concentration process of industrial production such as pharmacy, milk powder, amino acid, environmental protection water treatment, many factories adopt a conventional double-effect evaporation concentration system. The conventional double-effect evaporation concentration system uses a boiler to provide raw steam as a heat source for one-effect evaporation, utilizes cooling water to condense two-effect juice steam through a water-steam condenser, and discharges waste heat of the two-effect juice steam out of the system. Through analysis and balance calculation of energy conservation of the system, waste heat discharged by the water-steam condenser is easy to find to be almost equal to the supply heat of raw steam provided by the boiler, that is, the heat of the raw steam is wasted, so that the energy consumption of the double-effect evaporation system is higher, and the operation economic cost is higher.

In addition, the double-effect evaporation system needs a higher vacuum degree in order to ensure the heat transfer effect and the operation stability of the double-effect evaporation system. The double-effect evaporation system can maintain higher vacuum degree only when the two-effect condensed juice is cooled to lower temperature, but the traditional method generally adopts a cooling tower to provide cooling water, the temperature of the cooling water is higher and unstable (influenced by climate conditions), so that the cooling effect of the water-steam condenser is poor, the outlet temperature of the two-effect condensed juice is generally higher, and the temperature is generally about 40 ℃, so that the double-effect evaporation system is difficult to maintain higher vacuum degree.

As described above, the waste heat of the two-effect juice vapor is wasted, and the waste heat is not recycled, so that the system has higher energy consumption, and the outlet temperature of the condensed water of the two-effect juice vapor is generally higher because the water temperature of natural cooling water is generally higher, so that the vacuum degree of the conventional double-effect evaporation concentration system is difficult to maintain at a higher level, and a novel evaporation concentration system with higher energy utilization efficiency and higher system vacuum degree is required to be provided.

Disclosure of Invention

The invention aims to solve the problems that the existing conventional double-effect evaporation concentration system does not recycle the waste heat of the double-effect juice steam, so that the energy consumption of the system is higher, and the temperature of the condensed water outlet of the double-effect juice steam is generally higher due to generally higher water temperature of natural cooling water, so that the vacuum degree of the conventional double-effect evaporation concentration system is difficult to maintain at a higher level, and further provides a double-stage compression type heat pump double-effect evaporation concentration system and a double-stage compression type heat pump double-effect evaporation concentration device.

The technical scheme adopted for solving the technical problems is as follows:

scheme one: a double-effect evaporation concentration system of a double-stage compression type heat pump comprises a first compressor, a heat pump condenser, a second throttle expansion valve, a heat pump first evaporator, a third throttle expansion valve, a heat pump second evaporator, a second compressor, a first intermediate water circulation pipeline, a second intermediate water circulation pipeline, a first total exhaust steam pipeline, a second total exhaust steam pipeline, a third total exhaust steam pipeline, a first refrigerant pipeline, a sixth refrigerant pipeline, a seventh refrigerant pipeline, an eighth refrigerant pipeline, a ninth refrigerant pipeline, a tenth refrigerant pipeline, a one-effect evaporation tank, a two-effect evaporation tank, a vacuumizing control valve, a vacuum pump, a condensed water collection tank and a condensed water discharge pump a condensed water check valve, a first feed valve, a second feed valve, a third feed valve, a first discharge valve, a second discharge valve, a third discharge valve, a discharge pump, a starter, a steam generation regulating valve, a steam generation condensed water valve, a start water inlet valve, a start water supplementing pipeline, a first start steam generation pipeline, a first one-effect juice steam pipeline, a second one-effect juice steam pipeline, a start secondary steam pipeline, a total condensed water pipeline, a vacuumizing pipeline, a condensed water discharge pipeline, a first feed pipeline, a second feed pipeline, a third feed pipeline, a first discharge pipeline, a second discharge pipeline, a third discharge pipeline, a second one-effect juice steam pipeline and a second start steam generation pipeline,

The outlet end of the first intermediate water circulation pipeline is connected with the heat medium inlet end of the heat pump condenser, the heat medium outlet end of the heat pump condenser is connected with the inlet end of the second intermediate water circulation pipeline, the outlet end of the second intermediate water circulation pipeline is connected with the heat medium inlet end of the first effect evaporation tank, the heat medium outlet end of the first effect evaporation tank is connected with the inlet end of the first intermediate water circulation pipeline,

the inlet end of the first refrigerant pipeline is connected with the refrigerant outlet end of the heat pump condenser, the outlet end of the first refrigerant pipeline is respectively connected with the inlet end of the sixth refrigerant pipeline and the inlet end of the seventh refrigerant pipeline, the sixth refrigerant pipeline is provided with a second throttling expansion valve, the outlet end of the sixth refrigerant pipeline is connected with the refrigerant inlet end of the first evaporator of the heat pump, the refrigerant outlet end of the heat pump evaporator is connected with the inlet end of the eighth refrigerant pipeline, the seventh refrigerant pipeline is provided with a third throttling expansion valve, the outlet end of the seventh refrigerant pipeline is connected with the refrigerant inlet end of the second evaporator of the heat pump, the refrigerant outlet end of the second evaporator of the heat pump is connected with the inlet end of the ninth refrigerant pipeline, the ninth refrigerant pipeline is provided with a second compressor, the outlet end of the ninth refrigerant pipeline is connected with the middle part of the eighth refrigerant pipeline, the outlet end of the eighth refrigerant pipeline is connected with the main air inlet end of the first compressor, the air outlet end of the first compressor is connected with the inlet end of the tenth refrigerant pipeline, the outlet end of the tenth refrigerant pipeline is connected with the refrigerant inlet end of the heat pump condenser,

The inlet end of the first one-effect juice steam pipeline is connected with the air outlet end of the upper part of the first one-effect evaporation tank, the outlet end of the first one-effect juice steam pipeline is connected with the heat medium inlet end of the second one-effect evaporation tank, the heat medium outlet end of the second one-effect evaporation tank is connected with the inlet end of the second one-effect juice steam pipeline, the inlet end of the second one-effect juice steam pipeline is connected with the air outlet end of the upper part of the second one-effect evaporation tank, the outlet end of the first one-effect juice steam pipeline is connected with the raw steam inlet end of the starter, the raw steam outlet end of the starter is connected with the inlet end of the second one-effect steam pipeline, the first one-way steam pipeline is provided with a raw steam regulating valve, the second one-way is provided with a raw steam condensation valve, the inlet end of the second one-way steam pipeline is connected with the air outlet end of the upper part of the starter, the outlet end of the second one-way juice steam pipeline and the outlet end of the second one-way juice pipeline are respectively connected with the inlet end of the first one-way exhaust steam pipeline, the outlet end of the first one-way steam pipeline is connected with the heat pump inlet end of the first one-way exhaust steam pipeline,

the outlet end of the second total exhaust steam pipeline and the outlet end of the second starting steam generating pipeline are respectively connected with the inlet end of a third total exhaust steam pipeline, the outlet end of the third total exhaust steam pipeline is connected with the heat release inlet end of the heat pump second evaporator, the heat release outlet end of the heat pump second evaporator is connected with the inlet end of the total condensation water pipeline, the outlet end of the total condensation water pipeline is connected with the water inlet end of the condensation water collecting tank, the inlet end of the vacuumizing pipeline is connected with the extraction opening end at the upper part of the condensation water collecting tank, the vacuumizing pipeline is sequentially provided with a vacuumizing control valve and a vacuum pump along the medium flow direction, the outlet end of the vacuumizing pipeline is emptied, the inlet end of the condensation water discharging pipeline is connected with the liquid outlet end at the lower part of the condensation water collecting tank, the condensation water discharging pipeline is sequentially provided with a condensation water discharging pump and a condensation water check valve along the medium flow direction, the outlet end of the condensation water discharging pipeline is discharged,

The starting water supplementing pipeline is provided with a starting water inlet valve, the outlet end of the starting water supplementing pipeline is connected with the water inlet end of the lower part of the starter,

a first feeding valve is arranged on the first feeding pipeline, the outlet end of the first feeding pipeline is respectively connected with the inlet end of the second feeding pipeline and the inlet end of the third feeding pipeline, the second feeding pipeline is provided with a second feeding valve, the outlet end of the second feeding pipeline is connected with the feed inlet end of the first-effect evaporation tank, the third feeding pipeline is provided with a third feeding valve, the outlet end of the third feeding pipeline is connected with the feed inlet end of the second-effect evaporation tank,

the inlet end of the first discharging pipeline is connected with the discharge port end of the bottom of the first-effect evaporation tank, the first discharging pipeline is provided with a first discharging valve, the inlet end of the second discharging pipeline is connected with the discharge port end of the bottom of the second-effect evaporation tank, the second discharging pipeline is provided with a second discharging valve, the outlet end of the first discharging pipeline and the outlet end of the second discharging pipeline are respectively connected with the inlet end of a third discharging pipeline, the third discharging pipeline is sequentially provided with a third discharging valve and a discharging pump along the medium flowing direction, and the outlet end of the third discharging pipeline is discharged from the system.

Further, an effective condensate throttling device is arranged on the second effective juice vapor pipeline.

Further, a first condensate U-shaped bend is arranged on the second total exhaust steam pipeline, and a second condensate U-shaped bend is arranged on the second starting steam generating pipeline.

Scheme II: a double-effect evaporation concentration system of a double-stage compression type heat pump comprises a first compressor, a heat pump condenser, a second throttle expansion valve, a heat pump first evaporator, a third throttle expansion valve, a heat pump second evaporator, a second compressor, a first intermediate water circulation pipeline, a second intermediate water circulation pipeline, a first total exhaust steam pipeline, a second total exhaust steam pipeline, a third total exhaust steam pipeline, a first refrigerant pipeline, a sixth refrigerant pipeline, a seventh refrigerant pipeline, an eighth refrigerant pipeline, a ninth refrigerant pipeline, a tenth refrigerant pipeline, a one-effect evaporation tank, a two-effect evaporation tank, a vacuumizing control valve, a vacuum pump, a condensed water collection tank and a condensed water discharge pump a condensed water check valve, a first feed valve, a second feed valve, a third feed valve, a first discharge valve, a second discharge valve, a third discharge valve, a discharge pump, a starter, a steam generation regulating valve, a steam generation condensed water valve, a start water inlet valve, a start water supplementing pipeline, a first start steam generation pipeline, a first one-effect juice steam pipeline, a second one-effect juice steam pipeline, a start secondary steam pipeline, a total condensed water pipeline, a vacuumizing pipeline, a condensed water discharge pipeline, a first feed pipeline, a second feed pipeline, a third feed pipeline, a first discharge pipeline, a second discharge pipeline, a third discharge pipeline, a second one-effect juice steam pipeline and a second start steam generation pipeline,

the inlet end of the first refrigerant pipeline is connected with the refrigerant outlet end of the heat pump condenser, the first refrigerant pipeline is provided with a second throttling expansion valve, the outlet end of the first refrigerant pipeline is respectively connected with the inlet end of the sixth refrigerant pipeline and the inlet end of the seventh refrigerant pipeline, the outlet end of the sixth refrigerant pipeline is connected with the refrigerant inlet end of the first evaporator of the heat pump, the refrigerant outlet end of the heat pump evaporator is connected with the inlet end of the eighth refrigerant pipeline, the seventh refrigerant pipeline is provided with a third throttling expansion valve, the outlet end of the seventh refrigerant pipeline is connected with the refrigerant inlet end of the second evaporator of the heat pump, the refrigerant outlet end of the second evaporator of the heat pump is connected with the inlet end of the ninth refrigerant pipeline, the ninth refrigerant pipeline is provided with a second compressor, the outlet end of the ninth refrigerant pipeline is connected with the middle part of the eighth refrigerant pipeline, the outlet end of the eighth refrigerant pipeline is connected with the main air inlet end of the first compressor, the air outlet end of the first compressor is connected with the inlet end of the tenth refrigerant pipeline, the outlet end of the tenth refrigerant pipeline is connected with the refrigerant inlet end of the heat pump condenser,

Scheme III: a double-stage compression type heat pump double-effect evaporation concentration system comprises a first compressor, a heat pump condenser, a first throttle expansion valve, a supercooling heat exchanger, a second throttle expansion valve, a heat pump first evaporator, a third throttle expansion valve, a heat pump second evaporator, a second compressor, a first intermediate water circulation pipeline, a second intermediate water circulation pipeline, a first total exhaust steam pipeline, a second total exhaust steam pipeline, a third total exhaust steam pipeline, a first refrigerant pipeline, a second refrigerant pipeline, a third refrigerant pipeline, a fourth refrigerant pipeline, a fifth refrigerant pipeline, a sixth refrigerant pipeline, a seventh refrigerant pipeline, an eighth refrigerant pipeline, a ninth refrigerant pipeline, a tenth refrigerant pipeline, a first-effect evaporation tank, a second-effect evaporation tank the vacuum pumping control valve, the vacuum pump, the condensate collecting tank, the condensate discharging pump, the condensate check valve, the first feeding valve, the second feeding valve, the third feeding valve, the first discharging valve, the second discharging valve, the third discharging valve, the discharging pump, the starter, the raw steam adjusting valve, the raw steam condensing water valve, the starting water inlet valve, the starting water supplementing pipe, the first starting raw steam pipe, the first one-effect juice steam pipe, the second one-effect juice steam pipe, the starting secondary steam pipe, the total condensate pipe, the vacuum pumping pipe, the condensate discharging pipe, the first feeding pipe, the second feeding pipe, the third feeding pipe, the first discharging pipe, the second discharging pipe, the third discharging pipe, the second one-effect juice steam pipe and the second starting raw steam pipe,

the inlet end of the first refrigerant pipeline is connected with the refrigerant outlet end of the heat pump condenser, the outlet end of the first refrigerant pipeline is respectively connected with the inlet end of the second refrigerant pipeline and the inlet end of the third refrigerant pipeline, the outlet end of the second refrigerant pipeline is connected with the first inlet end of the supercooling heat exchanger, the first outlet end of the supercooling heat exchanger is connected with the inlet end of the fourth refrigerant pipeline, the third refrigerant pipeline is provided with a first throttling expansion valve, the outlet end of the third refrigerant pipeline is connected with the second inlet end of the supercooling heat exchanger, the second outlet end of the supercooling heat exchanger is connected with the inlet end of the fifth refrigerant pipeline, the outlet end of the fifth refrigerant pipeline is connected with the middle air supplementing end of the first compressor, the outlet end of the fourth refrigerant pipeline is respectively connected with the inlet end of the sixth refrigerant pipeline and the inlet end of the seventh refrigerant pipeline, a second throttling expansion valve is arranged on a sixth refrigerant pipeline, the outlet end of the sixth refrigerant pipeline is connected with the refrigerant inlet end of a first evaporator of the heat pump, the refrigerant outlet end of the heat pump evaporator is connected with the inlet end of an eighth refrigerant pipeline, a third throttling expansion valve is arranged on a seventh refrigerant pipeline, the outlet end of the seventh refrigerant pipeline is connected with the refrigerant inlet end of a second evaporator of the heat pump, the refrigerant outlet end of the second evaporator of the heat pump is connected with the inlet end of a ninth refrigerant pipeline, a second compressor is arranged on the ninth refrigerant pipeline, the outlet end of the ninth refrigerant pipeline is connected with the middle part of the eighth refrigerant pipeline, the outlet end of the eighth refrigerant pipeline is connected with the main air inlet end of the first compressor, the air outlet end of the first compressor is connected with the inlet end of the tenth refrigerant pipeline, the outlet end of the tenth refrigerant pipeline is connected with the refrigerant inlet end of the heat pump condenser,

Scheme IV: a double-stage compression type heat pump double-effect evaporation concentration system comprises a first compressor, a heat pump condenser, a first throttle expansion valve, a supercooling heat exchanger, a second throttle expansion valve, a heat pump first evaporator, a third throttle expansion valve, a heat pump second evaporator, a second compressor, a first intermediate water circulation pipeline, a second intermediate water circulation pipeline, a first total exhaust steam pipeline, a second total exhaust steam pipeline, a third total exhaust steam pipeline, a first refrigerant pipeline, a second refrigerant pipeline, a third refrigerant pipeline, a fourth refrigerant pipeline, a fifth refrigerant pipeline, a sixth refrigerant pipeline, a seventh refrigerant pipeline, an eighth refrigerant pipeline, a ninth refrigerant pipeline, a tenth refrigerant pipeline, a first-effect evaporation tank, a second-effect evaporation tank the vacuum pumping control valve, the vacuum pump, the condensate collecting tank, the condensate discharging pump, the condensate check valve, the first feeding valve, the second feeding valve, the third feeding valve, the first discharging valve, the second discharging valve, the third discharging valve, the discharging pump, the starter, the raw steam adjusting valve, the raw steam condensing water valve, the starting water inlet valve, the starting water supplementing pipe, the first starting raw steam pipe, the first one-effect juice steam pipe, the second one-effect juice steam pipe, the starting secondary steam pipe, the total condensate pipe, the vacuum pumping pipe, the condensate discharging pipe, the first feeding pipe, the second feeding pipe, the third feeding pipe, the first discharging pipe, the second discharging pipe, the third discharging pipe, the second one-effect juice steam pipe and the second starting raw steam pipe,

the inlet end of the first refrigerant pipeline is connected with the refrigerant outlet end of the heat pump condenser, the outlet end of the first refrigerant pipeline is respectively connected with the inlet end of the second refrigerant pipeline and the inlet end of the third refrigerant pipeline, the outlet end of the second refrigerant pipeline is connected with the first inlet end of the supercooling heat exchanger, the first outlet end of the supercooling heat exchanger is connected with the inlet end of the fourth refrigerant pipeline, the fourth refrigerant pipeline is provided with a second throttling expansion valve, the third refrigerant pipeline is provided with a first throttling expansion valve, the outlet end of the third refrigerant pipeline is connected with the second inlet end of the supercooling heat exchanger, the second outlet end of the supercooling heat exchanger is connected with the inlet end of the fifth refrigerant pipeline, the outlet end of the fifth refrigerant pipeline is connected with the middle air supplementing port of the first compressor, the outlet end of the fourth refrigerant pipeline is respectively connected with the inlet end of the sixth refrigerant pipeline and the inlet end of the seventh refrigerant pipeline, the outlet end of the sixth refrigerant pipeline is connected with the refrigerant inlet end of the first evaporator of the heat pump, the refrigerant outlet end of the heat pump evaporator is connected with the inlet end of the eighth refrigerant pipeline, the seventh refrigerant pipeline is provided with a third throttling expansion valve, the outlet end of the seventh refrigerant pipeline is connected with the refrigerant inlet end of the second evaporator of the heat pump, the refrigerant outlet end of the second evaporator of the heat pump is connected with the inlet end of the ninth refrigerant pipeline, the ninth refrigerant pipeline is provided with a second compressor, the outlet end of the ninth refrigerant pipeline is connected with the middle part of the eighth refrigerant pipeline, the outlet end of the eighth refrigerant pipeline is connected with the main air inlet end of the first compressor, the air outlet end of the first compressor is connected with the inlet end of the tenth refrigerant pipeline, the outlet end of the tenth refrigerant pipeline is connected with the refrigerant inlet end of the heat pump condenser,

Compared with the prior art, the invention has the following beneficial effects:

1. the invention utilizes the heat pump principle, consumes less electric quantity and realizes heat recycling. The raw steam consumption of the one-effect evaporation tank in the conventional double-effect evaporation concentration system is completely canceled, the part of energy is saved, the cooling water consumption of the conventional double-effect evaporation concentration system is canceled, and the water resource is saved.

2. The invention realizes the cascade evaporation of the refrigerant through the heat pump first evaporator 6 and the heat pump second evaporator 8, realizes the cascade compression of the refrigerant steam through the first compressor 1 and the second compressor 9, avoids the deep compression of all the refrigerant steam, and finally realizes the improvement of the performance coefficient of the heat pump circulation system through the cascade recovery of exhaust steam waste heat and the cascade improvement of energy quality, and the practice shows that the performance coefficient can reach 4.8-5.3.

3. The sensible heat and the waste heat of the condensed water of the first-effect juice vapor and the second-effect juice vapor are deeply recovered, the sensible heat and the waste heat of the condensed water of the starting raw vapor are recovered for cyclic heat utilization, the heat waste of the system is reduced to the greatest extent, the outlet temperature of the condensed water is deeply reduced, the evaporation system is maintained at an extremely high vacuum degree level, and the vacuum degree of the system can reach-0.97 bar.

Drawings

FIG. 1 is a schematic view of the overall structure of a first embodiment of the present invention;

FIG. 2 is a schematic overall structure of a second embodiment of the present invention;

FIG. 3 is a schematic overall structure of a third embodiment of the present invention;

FIG. 4 is a schematic overall structure of a fourth embodiment of the present invention;

wherein the arrow direction indicates the direction of the medium flow.

Detailed Description

The first embodiment is as follows: the present embodiment will be described with reference to figure 1, the dual-stage compression heat pump double-effect evaporation concentration system according to the present embodiment includes a first compressor 1, a heat pump condenser 2, a second throttle expansion valve 5, a heat pump first evaporator 6, a third throttle expansion valve 7, a heat pump second evaporator 8, a second compressor 9, a first intermediate water circulation line 31, a second intermediate water circulation line 32, a first total exhaust line 33, a second total exhaust line 34, a third total exhaust line 35, a first refrigerant line 41, a sixth refrigerant line 46, a seventh refrigerant line 47, an eighth refrigerant line 48, a ninth refrigerant line 49, a tenth refrigerant line 50, a first-effect evaporation tank 61, a second-effect evaporation tank 62, a vacuum pump control valve 64, a vacuum pump 65, a condensate collection tank 66, a condensate discharge pump 67 condensate check valve 68, first feed valve 71, second feed valve 72, third feed valve 73, first discharge valve 74, second discharge valve 75, third discharge valve 76, discharge pump 77, starter 81, raw steam regulating valve 82, raw steam condensate valve 83, start water inlet valve 84, start water make-up line 91, first start raw steam line 92, first one-effect juice steam line 93, second one-effect juice steam line 94, start secondary steam line 95, total condensate line 96, evacuation line 97, condensate drain line 98, first feed line 99, second feed line 100, third feed line 101, first discharge line 102, second discharge line 103, third discharge line 104, second one-effect juice steam line 105, and second start raw steam line 106,

The outlet end of the first intermediate water circulation pipeline 31 is connected with the heat medium inlet end of the heat pump condenser 2, the heat medium outlet end of the heat pump condenser 2 is connected with the inlet end of the second intermediate water circulation pipeline 32, the outlet end of the second intermediate water circulation pipeline 32 is connected with the heat medium inlet end of the first effective evaporation tank 61, the heat medium outlet end of the first effective evaporation tank 61 is connected with the inlet end of the first intermediate water circulation pipeline 31,

the inlet end of the first refrigerant line 41 is connected with the refrigerant outlet end of the heat pump condenser 2, the outlet end of the first refrigerant line 41 is connected with the inlet end of the sixth refrigerant line 46 and the inlet end of the seventh refrigerant line 47, the sixth refrigerant line 46 is provided with the second throttle expansion valve 5, the outlet end of the sixth refrigerant line 46 is connected with the refrigerant inlet end of the heat pump first evaporator 6, the refrigerant outlet end of the heat pump evaporator 6 is connected with the inlet end of the eighth refrigerant line 48, the seventh refrigerant line 47 is provided with the third throttle expansion valve 7, the outlet end of the seventh refrigerant line 47 is connected with the refrigerant inlet end of the heat pump second evaporator 8, the refrigerant outlet end of the heat pump second evaporator 8 is connected with the inlet end of the ninth refrigerant line 49, the ninth refrigerant line 49 is provided with the second compressor 9, the outlet end of the ninth refrigerant line 49 is connected with the middle part of the eighth refrigerant line 48, the outlet end of the eighth refrigerant line 48 is connected with the main end of the first compressor 1, the outlet end of the first refrigerant line 1 is connected with the inlet end of the tenth refrigerant line 50, the outlet end of the tenth refrigerant line 50 is connected with the refrigerant inlet end of the tenth refrigerant line 50,

The inlet end of the first one-effect juice steam pipeline 93 is connected with the air outlet end of the upper part of the one-effect evaporation tank 61, the outlet end of the first one-effect juice steam pipeline 93 is connected with the heat medium inlet end of the second one-effect evaporation tank 62, the heat medium outlet end of the second one-effect evaporation tank 62 is connected with the inlet end of the second one-effect juice steam pipeline 105, the inlet end of the second one-effect juice steam pipeline 94 is connected with the air outlet end of the upper part of the second one-effect evaporation tank 62, the outlet end of the first one-effect juice steam pipeline 92 is connected with the raw steam inlet end of the starter 81, the raw steam outlet end of the starter 81 is connected with the inlet end of the second one-effect steam pipeline 106, the first one-effect steam pipeline 92 is provided with a raw steam regulating valve 82, the second one-effect steam pipeline 106 is provided with a raw steam condensing valve 83, the inlet end of the second one-effect steam pipeline 95 is connected with the air outlet end of the upper part of the starter 81, the outlet end of the second one-effect juice steam pipeline 105, the outlet end of the second one-effect steam pipeline 94 and the outlet end of the second one-effect steam pipeline 95 are respectively connected with the inlet end of the first one-way exhaust steam pipeline 33, the first one-way exhaust steam pipeline 33 is connected with the heat pump 34 of the first one-way exhaust steam pipeline 6, the first one-way exhaust steam pipeline 6 is connected with the first one-way exhaust steam pipeline 6,

The outlet end of the second total exhaust steam pipeline 34 and the outlet end of the second starting raw steam pipeline 106 are respectively connected with the inlet end of the third total exhaust steam pipeline 35, the outlet end of the third total exhaust steam pipeline 35 is connected with the heat release inlet end of the heat pump second evaporator 8, the heat release outlet end of the heat pump second evaporator 8 is connected with the inlet end of the total condensation water pipeline 96, the outlet end of the total condensation water pipeline 96 is connected with the water inlet end of the condensation water collecting tank 66, the inlet end of the vacuumizing pipeline 97 is connected with the extraction opening end at the upper part of the condensation water collecting tank 66, the vacuumizing pipeline 97 is sequentially provided with a vacuumizing control valve 64 and a vacuum pump 65 along the medium flow direction, the outlet end of the vacuumizing pipeline 97 is emptied, the inlet end of the condensation water discharging pipeline 98 is connected with the liquid outlet end at the lower part of the condensation water collecting tank 66, the condensation water discharging pipeline 98 is sequentially provided with a condensation water discharging pump 67 and a condensation water check valve 68 along the medium flow direction, the outlet end of the condensation water discharging pipeline 98 is discharged,

the starting water supplementing pipeline 91 is provided with a starting water inlet valve 84, the outlet end of the starting water supplementing pipeline 91 is connected with the water inlet end of the lower part of the starter 81,

the first feeding pipeline 99 is provided with a first feeding valve 71, the outlet end of the first feeding pipeline 99 is respectively connected with the inlet end of a second feeding pipeline 100 and the inlet end of a third feeding pipeline 101, the second feeding pipeline 100 is provided with a second feeding valve 72, the outlet end of the second feeding pipeline 100 is connected with the inlet end of a first-effect evaporation tank 61, the third feeding pipeline 101 is provided with a third feeding valve 73, the outlet end of the third feeding pipeline 101 is connected with the inlet end of a second-effect evaporation tank 62,

The inlet end of the first discharging pipeline 102 is connected with the discharge port end at the bottom of the first-effect evaporation tank 61, the first discharging pipeline 102 is provided with a first discharging valve 74, the inlet end of the second discharging pipeline 103 is connected with the discharge port end at the bottom of the second-effect evaporation tank 62, the second discharging pipeline 103 is provided with a second discharging valve 75, the outlet end of the first discharging pipeline 102 and the outlet end of the second discharging pipeline 103 are respectively connected with the inlet end of a third discharging pipeline 104, the third discharging pipeline 104 is sequentially provided with a third discharging valve 76 and a discharging pump 77 along the medium flowing direction, and the outlet end of the third discharging pipeline 104 is discharged.

The operation principle of the present embodiment:

before the system is started, all communication valves of the system and the outside are closed, including a first feed valve 71, a third discharge valve 76 and a start water inlet valve 84, the vacuumizing control valve 64 is opened, the vacuumizing pump 65 is started, the system is vacuumized through a vacuumizing pipeline 97, and when the vacuum degree of the system meets the requirement, the vacuumizing control valve 64 is closed, and the vacuumizing pump 65 is stopped.

At system start-up, the first feed valve 71, the second feed valve 72 and the third feed valve 73 are opened and adjusted to inject the raw material liquid into the first-effect evaporation tank 61 and the second-effect evaporation tank 62. The start water inlet valve 84 is opened and adjusted and raw water enters the starter 81 from the start water replenishment line 91. The steam generation regulating valve 82 is opened, and steam enters the system from the first start steam generation pipeline 92, and the steam generation regulating valve 82 plays a role in regulating the steam generation flow rate and pressure. In the starter 81, raw water is heated by raw steam, and low-pressure secondary steam (for example, saturated temperature thereof is 60 ℃) is generated, and enters the heat pump first evaporator 6 through the starting secondary steam line 95 and the first total exhaust steam line 33. The low-pressure secondary steam generated by the starter and the secondary juice steam generated by the first-effect evaporation tank 61 and the second-effect evaporation tank 62 are collectively referred to as exhaust steam.

Taking the exhaust steam with the saturation temperature of 60 ℃ as an example, the exhaust steam firstly enters the first heat pump evaporator 6 to carry out condensation heat release, the exhaust steam condensation is a phase change process, the temperature is kept unchanged at 60 ℃, and the evaporation temperature of the refrigerant of the first heat pump evaporator 6 is generally designed to be 55 ℃. After the exhaust steam is condensed into water, the exhaust steam is combined with the raw steam condensed water obtained by heat release condensation in the starter 81, and the raw steam condensed water continuously enters the second heat pump evaporator 8 to cool and release heat, which is a single-phase heat exchange process, the temperature of the exhaust steam condensed water is continuously reduced, for example, the outlet temperature is reduced to 25 ℃, and at the moment, the evaporation temperature of the refrigerant of the second heat pump evaporator 8 is generally designed to be 20 ℃. In the heat pump first evaporator 6 and the heat pump second evaporator 8, the exhaust steam transfers all latent heat of condensation and part of temperature difference sensible heat of all condensation water to the refrigerant of the heat pump, so that the recovery of exhaust steam and waste heat of condensation water is realized.

Thermodynamic cycle process of refrigerant: the evaporating temperature of the refrigerant in the heat pump first evaporator 6 reaches 55 c, so that the generated refrigerant vapor pressure is relatively high. Because the evaporation temperature of the refrigerant in the heat pump second evaporator 8 is only 20 ℃, the pressure of the generated refrigerant vapor is relatively low, the second compressor 9 is arranged to compress and boost the pressure of the refrigerant vapor generated by the heat pump second evaporator 8, after the pressure of the refrigerant vapor generated by the heat pump first evaporator 6 is reached, the two refrigerant vapors are converged and enter the first compressor 1 to compress and boost, for example, the exhaust pressure after the compression of the first compressor 1 can be increased to the corresponding refrigerant saturation pressure of 90 ℃, then the exhaust gas of the first compressor 1 enters the heat pump condenser 2 to condense and release heat (release heat to intermediate water), and the condensed liquid refrigerant flows out of the heat pump condenser 2 through the first refrigerant pipeline 41 and is divided into two paths, wherein one path with larger flow rate enters the heat pump first evaporator 6 after being throttled and cooled by the second throttle expansion valve 5 through the sixth refrigerant pipeline 46, and the exhaust gas is absorbed in the heat pump first evaporator 6 to condense and evaporate latent heat into a gaseous state;

The other path with smaller flow rate is throttled, depressurized and cooled by the third throttle expansion valve 7 through the seventh refrigerant pipeline 47, then enters the heat pump second evaporator 8, absorbs sensible heat of exhaust steam condensation water in the heat pump second evaporator 8, evaporates into a gas state, then enters the second compressor 9 for compression and pressure boosting, reaches the pressure of refrigerant steam generated by the heat pump first evaporator 6, the exhaust gas of the second compressor 9 is converged with the refrigerant steam generated by the heat pump first evaporator 6, and then enters the first compressor 1 for compression and pressure boosting, thus a complete refrigerant thermodynamic cycle process is completed, and the process is also an atypical vapor compression heat pump cycle process.

Intermediate water thermodynamic cycle process: the first intermediate water circulation pipe 31 is internally packaged with a certain amount of intermediate water (pure water), the intermediate water is heated and boiled in the heat pump condenser 2 by the high-temperature refrigerant discharged by the first compressor 1 to generate intermediate water vapor with higher temperature (for example, 85 ℃), then the intermediate water vapor enters the first effect evaporation tank 61 from the second intermediate water circulation pipe 32 and heats the raw material liquid in the first effect evaporation tank 61 to make the raw material liquid be boiled and concentrated, and meanwhile, the intermediate water vapor is condensed into a liquid state and flows back to the heat pump condenser 2 to absorb heat again by gravity, so that the complete intermediate water thermodynamic cycle process is completed.

The double-effect evaporation concentration process comprises the following steps: the double-effect evaporation concentration process in the invention is similar to the conventional double-effect evaporation concentration process, and is briefly described as follows: the raw material liquid in the first-effect evaporation tank 61 is heated by the medium steam to be evaporated and concentrated, for example, to have a boiling point of 75 ℃, to generate a first-effect juice steam at 75 ℃. The first-effect juice vapor enters the second-effect evaporation tank 62 through the first-effect juice vapor pipeline 93, and raw material liquid in the first-effect juice vapor pipeline is heated to evaporate and concentrate, for example, the boiling point is 60 ℃, so that the second-effect juice vapor with the temperature of 60 ℃ is generated, and meanwhile, the first-effect juice vapor is condensed into a liquid state.

After the raw material liquid in the first-effect evaporation tank 61 or the second-effect evaporation tank 62 is evaporated and concentrated to reach the target concentration, the first discharge valve 74 or the second discharge valve 75 and the third discharge valve 76 are opened, and the discharge pump 77 is started to discharge the concentrated liquid reaching the standard out of the system.

When the system gradually reaches normal and steady operation, the raw steam regulating valve 82 is closed, the raw steam supply is cut off, the start-up water inlet valve 84 is closed, and the raw water supply is cut off. After the start-up is completed, the system and the device can realize the cyclic utilization of heat under the driving action of the first compressor 1 and the second compressor 9, thereby achieving the aim of saving energy.

The invention analyzes the energy-saving reason:

The invention can realize energy saving mainly for two reasons, which are as follows:

firstly, the heat pump principle is utilized, less electric quantity is consumed, and heat recycling is realized. The cooling water is not utilized to condense the two-effect juice vapor like the conventional double-effect evaporation concentration system, but the heat pump first evaporator 6 is utilized to recycle the condensation latent heat of the two-effect juice vapor and part of sensible heat of the condensed water of the one-effect juice vapor, the heat pump second evaporator 8 is utilized to deeply recycle all sensible heat of the condensed water, the first compressor 1 and the second compressor 9 are utilized to upgrade the recovered heat by utilizing the vapor compression heat pump principle, the medium vapor with higher temperature is produced, the medium vapor is used for heating the one-effect evaporation tank 61, the raw vapor consumption of the one-effect evaporation tank in the conventional double-effect evaporation concentration system is completely canceled, the part of energy is saved, the cooling water consumption of the conventional double-effect evaporation concentration system is canceled, and the water resource is saved. In the practical process, the invention can reach the extremely low energy consumption level that 50kWh of electric quantity is consumed, namely one ton of water can be evaporated.

Secondly, less electric quantity is consumed, and higher vacuum degree is realized. Because the multi-effect evaporation system requires a high vacuum level, the temperature of the exhaust steam condensate needs to be reduced to a low temperature, such as 25 ℃. If the conventional heat pump cycle is adopted, the evaporation temperature of the heat pump must be designed according to the outlet temperature of the exhaust steam condensate water of 25 ℃, and is generally 20 ℃; the condensation temperature of the heat pump must be designed according to the outlet temperature of the heat transfer medium of 85 ℃, generally 90 ℃, the difference between the condensation temperature and the evaporation temperature of the heat pump is as high as 90-20=70 ℃, the coefficient of performance of the heat pump system is very low according to the common sense of refrigeration, the coefficient of performance calculated theoretically is only about 2.8, and the energy conservation and economy of waste steam heat recovery by adopting the heat pump system are hardly reflected.

The basic reason that the conventional heat pump cycle is uneconomical is that only one-stage evaporation is adopted, so that the evaporation temperature is too low, and the advantages of high saturation temperature and constant temperature during the phase transition of the dead steam are not fully utilized. It can be found by calculation that the heat pump first evaporator 6 takes on most of the latent heat of condensation in the exhaust steam heat recovery, the unit mass of exhaust steam is about 2360kJ/kg, while the heat pump second evaporator 8 takes on only a small part of the sensible heat in the exhaust steam heat recovery, the unit mass of exhaust steam is about 4.18× (60-25) =146.3 kJ/kg. That is, most of the waste heat of the exhaust steam is released at a higher temperature of 60 ℃, and most of the evaporation temperature of the refrigerant is reasonable to be set at 55 ℃. Only a small part of the refrigerant can be set at 20 ℃ through the evaporation temperature after deep throttling, so as to recover the sensible heat of the exhaust steam condensation water which only occupies a small part. This small portion of the refrigerant vapor can be compressed separately by a second, lower-power compressor 9, and after reaching a corresponding refrigerant saturation pressure of 55 c, mixed with the vast majority of the refrigerant vapor, and fed into the first compressor 1 for compression. It can be found that the difference between the discharge saturation temperature and the suction saturation temperature of the first compressor 1 is only 90-55=35 ℃, and the difference between the discharge saturation temperature and the suction saturation temperature of the second compressor 9 is also only 55-20=35 ℃. The cascade recovery and the cascade lifting of the energy quality of exhaust steam waste heat are realized through cascade evaporation and cascade compression, and deep compression of all refrigerant steam is avoided, so that the performance coefficient of a heat pump circulation system is improved, and the practice shows that the performance coefficient of the invention can be up to more than 4.8.

The second embodiment is as follows: referring to fig. 1, a first condensate throttling device 63 is disposed on the second first condensate pipeline 105 according to the present embodiment. The technical features not disclosed in this embodiment are the same as those of the first embodiment.

In order to fully recycle the waste heat of the condensed water of the first effect juice vapor, the condensed water of the first effect juice vapor and the second effect juice vapor are combined and integrated into the first evaporator 6 of the heat pump for heat recovery. Since the pressure of the first-effect evaporation tank 61 is higher than that of the second-effect evaporation tank 62, a first-effect condensate throttling device 63 is disposed on the second first-effect condensate pipeline 105 to control the pressure difference between the first-effect evaporation tank 61 and the second-effect evaporation tank 62 (and also control the boiling point difference therebetween).

And a third specific embodiment: referring to fig. 1, a first condensate U-shaped bend 10 is disposed on a second total exhaust steam pipeline 34 according to the present embodiment, and a second condensate U-shaped bend 85 is disposed on a second starting steam pipeline 106. The technical features not disclosed in this embodiment are the same as those of the first or second embodiment.

The purpose of providing the first condensate U-bend 10 and the second condensate U-bend 85 is to block exhaust steam which cannot be completely condensed in the heat pump first evaporator 6 or raw steam which cannot be completely condensed in the starter 81 from entering the heat pump second evaporator 8, so as to avoid the rapid increase of the evaporation amount of the refrigerant of the heat pump second evaporator 8, thereby avoiding the rapid increase of the load of the second compressor 9 and avoiding unstable system operation.

The specific embodiment IV is as follows: the present embodiment will be described with reference to figure 2, the dual-stage compression heat pump double-effect evaporation concentration system according to the present embodiment includes a first compressor 1, a heat pump condenser 2, a second throttle expansion valve 5, a heat pump first evaporator 6, a third throttle expansion valve 7, a heat pump second evaporator 8, a second compressor 9, a first intermediate water circulation line 31, a second intermediate water circulation line 32, a first total exhaust line 33, a second total exhaust line 34, a third total exhaust line 35, a first refrigerant line 41, a sixth refrigerant line 46, a seventh refrigerant line 47, an eighth refrigerant line 48, a ninth refrigerant line 49, a tenth refrigerant line 50, a first-effect evaporation tank 61, a second-effect evaporation tank 62, a vacuum pump control valve 64, a vacuum pump 65, a condensate collection tank 66, a condensate discharge pump 67 condensate check valve 68, first feed valve 71, second feed valve 72, third feed valve 73, first discharge valve 74, second discharge valve 75, third discharge valve 76, discharge pump 77, starter 81, raw steam regulating valve 82, raw steam condensate valve 83, start water inlet valve 84, start water make-up line 91, first start raw steam line 92, first one-effect juice steam line 93, second one-effect juice steam line 94, start secondary steam line 95, total condensate line 96, evacuation line 97, condensate drain line 98, first feed line 99, second feed line 100, third feed line 101, first discharge line 102, second discharge line 103, third discharge line 104, second one-effect juice steam line 105, and second start raw steam line 106,

the inlet end of the first refrigerant line 41 is connected with the refrigerant outlet end of the heat pump condenser 2, the second throttle expansion valve 5 is arranged on the first refrigerant line 41, the outlet end of the first refrigerant line 41 is respectively connected with the inlet end of the sixth refrigerant line 46 and the inlet end of the seventh refrigerant line 47, the outlet end of the sixth refrigerant line 46 is connected with the refrigerant inlet end of the heat pump first evaporator 6, the refrigerant outlet end of the heat pump evaporator 6 is connected with the inlet end of the eighth refrigerant line 48, the seventh refrigerant line 47 is provided with the third throttle expansion valve 7, the outlet end of the seventh refrigerant line 47 is connected with the refrigerant inlet end of the heat pump second evaporator 8, the refrigerant outlet end of the heat pump second evaporator 8 is connected with the inlet end of the ninth refrigerant line 49, the ninth refrigerant line 49 is provided with the second compressor 9, the outlet end of the ninth refrigerant line 49 is connected with the middle part of the eighth refrigerant line 48, the outlet end of the eighth refrigerant line 48 is connected with the main end of the first compressor 1, the outlet end of the first refrigerant line 1 is connected with the inlet end of the tenth refrigerant line 50, the outlet end of the tenth refrigerant line 50 is connected with the refrigerant inlet end of the tenth refrigerant line 50,

The operation principle of the present embodiment: the difference between this embodiment and the first embodiment is that the refrigerant entering the second evaporator 8 of the heat pump is throttled in two stages by the second throttle expansion valve 5 and the third throttle expansion valve 7 in sequence, so that the step throttle is realized. When the temperature of the heat transfer medium outlet is required to be much higher than that of the exhaust steam condensate outlet, the step throttling is adopted, so that the operation stability and the performance coefficient of the heat pump circulation system can be ensured. Other operating principles, operation modes and the like of the system are the same as those of the first embodiment.

Fifth embodiment: referring to fig. 2, a first condensate throttling device 63 is disposed on the second first condensate pipeline 105 according to the present embodiment. The technical features not disclosed in this embodiment are the same as those of the fourth embodiment.

Specific embodiment six: referring to fig. 2, a first condensate U-shaped bend 10 is disposed on the second total exhaust steam pipeline 34, and a second condensate U-shaped bend 85 is disposed on the second starting steam pipeline 106. The technical features not disclosed in this embodiment are the same as those of the fourth or fifth embodiment.

Seventh embodiment: the present embodiment will be described with reference to figure 3, the two-stage compression type heat pump double-effect evaporation concentration system according to the present embodiment includes a first compressor 1, a heat pump condenser 2, a first throttle expansion valve 3, a supercooling heat exchanger 4, a second throttle expansion valve 5, a heat pump first evaporator 6, a third throttle expansion valve 7, a heat pump second evaporator 8, a second compressor 9, a first intermediate water circulation line 31, a second intermediate water circulation line 32, a first total exhaust steam line 33, a second total exhaust steam line 34, a third total exhaust steam line 35, a first refrigerant line 41, a second refrigerant line 42, a third refrigerant line 43, a fourth refrigerant line 44, a fifth refrigerant line 45, a sixth refrigerant line 46, a seventh refrigerant line 47, an eighth refrigerant line 48, a ninth refrigerant line 49, a tenth refrigerant line 50, a first-effect evaporation tank 61, a second-effect evaporation tank 62 the vacuum pump 65, the condensate collection tank 66, the condensate discharge pump 67, the condensate check valve 68, the first feed valve 71, the second feed valve 72, the third feed valve 73, the first discharge valve 74, the second discharge valve 75, the third discharge valve 76, the discharge pump 77, the starter 81, the steam generation adjusting valve 82, the steam condensate 83, the start water inlet valve 84, the start water supplementing pipe 91, the first start steam generating pipe 92, the first one-effect juice steam pipe 93, the second one-effect juice steam pipe 94, the start secondary steam pipe 95, the total condensate pipe 96, the vacuum pump 97, the condensate discharge pipe 98, the first feed pipe 99, the second feed pipe 100, the third feed pipe 101, the first discharge pipe 102, the second discharge pipe 103, the third discharge pipe 104, the second one-effect juice steam pipe 105 and the second start steam generating pipe 106,

the inlet end of the first refrigerant line 41 is connected with the refrigerant outlet end of the heat pump condenser 2, the outlet end of the first refrigerant line 41 is connected with the inlet end of the second refrigerant line 42 and the inlet end of the third refrigerant line 43, the outlet end of the second refrigerant line 42 is connected with the first inlet end of the supercooling heat exchanger 4, the first outlet end of the supercooling heat exchanger 4 is connected with the inlet end of the fourth refrigerant line 44, the third refrigerant line 43 is provided with the first throttling expansion valve 3, the outlet end of the third refrigerant line 43 is connected with the second inlet end of the supercooling heat exchanger 4, the second outlet end of the supercooling heat exchanger 4 is connected with the inlet end of the fifth refrigerant line 45, the outlet end of the fifth refrigerant line 45 is connected with the intermediate air-supplementing end of the first compressor 1, the outlet end of the fourth refrigerant line 44 is connected with the inlet end of the sixth refrigerant line 46 and the inlet end of the seventh refrigerant line 47, the sixth refrigerant line 46 is provided with the second throttling valve 5, the outlet end of the sixth refrigerant line 46 is connected with the evaporator 6, the outlet end of the eighth refrigerant line 49 is connected with the inlet end of the eighth refrigerant line 8, the eighth refrigerant line 48 is connected with the eighth outlet end of the eighth refrigerant line 48, the eighth refrigerant line is connected with the eighth outlet end of the eighth refrigerant line 8 is provided with the eighth outlet end of the eighth refrigerant line 8, the eighth refrigerant line is connected with the eighth outlet end of the eighth refrigerant line 8 is provided with the eighth outlet end of the eighth refrigerant line 47, the air outlet end of the first compressor 1 is connected with the inlet end of a tenth refrigerant line 50, the outlet end of the tenth refrigerant line 50 is connected with the refrigerant inlet end of the heat pump condenser 2,

The operation principle of the present embodiment: the difference between this embodiment and the first embodiment is that the first throttle expansion valve 3 and the supercooling heat exchanger 4 are added, which causes the difference in the "thermodynamic cycle process of the refrigerant" between them, and the thermodynamic cycle process of the refrigerant in this embodiment is as follows:

the evaporating temperature of the refrigerant in the heat pump first evaporator 6 reaches 55 c, so that the generated refrigerant vapor pressure is relatively high. Since the evaporating temperature of the refrigerant in the heat pump second evaporator 8 is only 20 c, the resulting refrigerant vapor pressure is relatively low. The second compressor 9 is arranged to compress and boost the refrigerant vapor generated by the second evaporator 8 of the heat pump, so that after the refrigerant vapor reaches the pressure of the refrigerant vapor generated by the first evaporator 6 of the heat pump, the two refrigerant vapors are converged and enter the first compressor 1 to compress and boost, for example, the exhaust pressure compressed by the first compressor 1 can be increased to the corresponding refrigerant saturation pressure at 90 ℃, then the exhaust gas of the first compressor 1 enters the heat pump condenser 2 to carry out condensation heat release (release heat to a heat carrier medium) and condense into liquid refrigerant to flow out of the heat pump condenser 2,

The liquid refrigerant flows out of the heat pump condenser 2 through the first refrigerant pipeline 41 and then is divided into two paths, wherein one path with smaller flow rate is throttled, depressurized and cooled by the first throttling expansion valve 3 through the third refrigerant pipeline 43 and then enters the supercooling heat exchanger 4, the other path with larger flow rate is directly enters the supercooling heat exchanger 4 through the second refrigerant pipeline 42,

in the supercooling heat exchanger 4, the temperature of the refrigerant in the third refrigerant line 43 is lower than the temperature of the refrigerant in the second refrigerant line 42 after the throttling and cooling effects of the first throttling expansion valve 3, the refrigerant in the third refrigerant line 43 absorbs heat and evaporates into a gas state through heat transfer, and enters the first compressor 1 from the middle air supplementing port of the first compressor 1 to be compressed, the refrigerant in the second refrigerant line 42 obtains larger supercooling degree due to heat release, the larger supercooling degree can improve the coefficient of performance of the whole heat pump circulation system, and practice shows that the coefficient of performance can be improved by about 10 percent, which is the aim of arranging the supercooling heat exchanger 4.

The refrigerant in the fourth refrigerant pipeline 44 after being supercooled by the supercooling heat exchanger 4 is divided into two paths, wherein the path with larger flow rate enters the heat pump first evaporator 6 after being throttled, depressurized and cooled by the second throttle expansion valve 5 through the sixth refrigerant pipeline 46, absorbs the condensation latent heat of the dead steam in the heat pump first evaporator 6, evaporates into a gaseous state,

Other operating principles, operation modes and the like of the system are the same as those of the first embodiment.

Eighth embodiment: referring to fig. 3, an effective condensate throttling device 63 is disposed on the second effective juice vapor pipeline 105 according to the present embodiment. The technical features not disclosed in this embodiment are the same as those of the seventh embodiment.

Detailed description nine: referring to fig. 3, a first condensate U-shaped bend 10 is disposed on the second total exhaust steam pipeline 34, and a second condensate U-shaped bend 85 is disposed on the second starting steam pipeline 106. The technical features not disclosed in this embodiment are the same as those of the seventh or eighth embodiment.

Detailed description ten: the present embodiment will be described with reference to figure 4, the two-stage compression type heat pump double-effect evaporation concentration system according to the present embodiment includes a first compressor 1, a heat pump condenser 2, a first throttle expansion valve 3, a supercooling heat exchanger 4, a second throttle expansion valve 5, a heat pump first evaporator 6, a third throttle expansion valve 7, a heat pump second evaporator 8, a second compressor 9, a first intermediate water circulation line 31, a second intermediate water circulation line 32, a first total exhaust steam line 33, a second total exhaust steam line 34, a third total exhaust steam line 35, a first refrigerant line 41, a second refrigerant line 42, a third refrigerant line 43, a fourth refrigerant line 44, a fifth refrigerant line 45, a sixth refrigerant line 46, a seventh refrigerant line 47, an eighth refrigerant line 48, a ninth refrigerant line 49, a tenth refrigerant line 50, a first-effect evaporation tank 61, a second-effect evaporation tank 62 the vacuum pump 65, the condensate collection tank 66, the condensate discharge pump 67, the condensate check valve 68, the first feed valve 71, the second feed valve 72, the third feed valve 73, the first discharge valve 74, the second discharge valve 75, the third discharge valve 76, the discharge pump 77, the starter 81, the steam generation adjusting valve 82, the steam condensate 83, the start water inlet valve 84, the start water supplementing pipe 91, the first start steam generating pipe 92, the first one-effect juice steam pipe 93, the second one-effect juice steam pipe 94, the start secondary steam pipe 95, the total condensate pipe 96, the vacuum pump 97, the condensate discharge pipe 98, the first feed pipe 99, the second feed pipe 100, the third feed pipe 101, the first discharge pipe 102, the second discharge pipe 103, the third discharge pipe 104, the second one-effect juice steam pipe 105 and the second start steam generating pipe 106,

the inlet end of the first refrigerant pipeline 41 is connected with the refrigerant outlet end of the heat pump condenser 2, the outlet end of the first refrigerant pipeline 41 is respectively connected with the inlet end of the second refrigerant pipeline 42 and the inlet end of the third refrigerant pipeline 43, the outlet end of the second refrigerant pipeline 42 is connected with the first inlet end of the supercooling heat exchanger 4, the first outlet end of the supercooling heat exchanger 4 is connected with the inlet end of the fourth refrigerant pipeline 44, the fourth refrigerant pipeline 44 is provided with the second throttling expansion valve 5, the third refrigerant pipeline 43 is provided with the first throttling expansion valve 3, the outlet end of the third refrigerant pipeline 43 is connected with the second inlet end of the supercooling heat exchanger 4, the second outlet end of the supercooling heat exchanger 4 is connected with the inlet end of the fifth refrigerant pipeline 45, the outlet end of the fifth refrigerant pipeline 45 is connected with the middle air supplementing end of the first compressor 1, the outlet end of the fourth refrigerant line 44 is connected with the inlet end of the sixth refrigerant line 46 and the inlet end of the seventh refrigerant line 47, respectively, the outlet end of the sixth refrigerant line 46 is connected with the refrigerant inlet end of the first evaporator 6 of the heat pump, the refrigerant outlet end of the first evaporator 6 of the heat pump is connected with the inlet end of the eighth refrigerant line 48, the seventh refrigerant line 47 is provided with the third throttle expansion valve 7, the outlet end of the seventh refrigerant line 47 is connected with the refrigerant inlet end of the second evaporator 8 of the heat pump, the refrigerant outlet end of the second evaporator 8 of the heat pump is connected with the inlet end of the ninth refrigerant line 49, the ninth refrigerant line 49 is provided with the second compressor 9, the outlet end of the ninth refrigerant line 49 is connected with the middle part of the eighth refrigerant line 48, the outlet end of the eighth refrigerant line 48 is connected with the main inlet end of the first compressor 1, the air outlet end of the first compressor 1 is connected with the inlet end of a tenth refrigerant line 50, the outlet end of the tenth refrigerant line 50 is connected with the refrigerant inlet end of the heat pump condenser 2,

The operation principle of the present embodiment: the difference between the present embodiment and the seventh embodiment is that the refrigerant entering the second evaporator 8 of the heat pump is throttled in two stages by the second throttle expansion valve 5 and the third throttle expansion valve 7 in sequence, so that the step throttle is realized. When the temperature of the heat transfer medium outlet is required to be much higher than that of the exhaust steam condensate outlet, the step throttling is adopted, so that the operation stability and the performance coefficient of the heat pump circulation system can be ensured.

The other operating principle, operation mode and the like of the system are the same as those of the seventh embodiment.

In this embodiment, an effective condensate throttling device 63 may also be disposed on the second effective juice vapor pipeline 105. In order to fully recycle the waste heat of the condensed water of the first effect juice vapor, the condensed water of the first effect juice vapor and the second effect juice vapor are combined and integrated into the first evaporator 6 of the heat pump for heat recovery. Since the pressure of the first-effect evaporation tank 61 is higher than that of the second-effect evaporation tank 62, a first-effect condensate throttling device 63 is disposed on the second first-effect condensate pipeline 105 to control the pressure difference between the first-effect evaporation tank 61 and the second-effect evaporation tank 62 (and also control the boiling point difference therebetween).

The first condensate U-shaped bend 10 can also be arranged on the second total exhaust steam pipeline 34, and the second condensate U-shaped bend 85 can be arranged on the second starting steam pipeline 106. The purpose of providing the first condensate U-bend 10 and the second condensate U-bend 85 is to block exhaust steam which cannot be completely condensed in the heat pump first evaporator 6 or raw steam which cannot be completely condensed in the starter 81 from entering the heat pump second evaporator 8, so as to avoid the rapid increase of the evaporation amount of the refrigerant of the heat pump second evaporator 8, thereby avoiding the rapid increase of the load of the second compressor 9 and avoiding unstable system operation.

The main body of each specific embodiment in the invention belongs to a general inventive concept, is related to each other in technology, and comprises a plurality of identical or similar specific technical characteristics, so that the requirement of singleness is met, and the main body is proposed as a piece of application.

Claims

1. A double-stage compression type heat pump double-effect evaporation concentration system is characterized in that: the double-stage compression type heat pump double-effect evaporation concentration system comprises a first compressor (1), a heat pump condenser (2), a second throttling expansion valve (5), a heat pump first evaporator (6), a third throttling expansion valve (7), a heat pump second evaporator (8), a second compressor (9), a first intermediate water circulation pipeline (31), a second intermediate water circulation pipeline (32), a first total exhaust steam pipeline (33), a second total exhaust steam pipeline (34), a third total exhaust steam pipeline (35), a first refrigerant pipeline (41), a sixth refrigerant pipeline (46), a seventh refrigerant pipeline (47), an eighth refrigerant pipeline (48), a ninth refrigerant pipeline (49), a tenth refrigerant pipeline (50), a first-effect evaporation tank (61), a second-effect evaporation tank (62), a vacuumizing control valve (64), a vacuum pump (65), a condensate collection tank (66), a condensate water discharge pump (67), a condensate water check valve (68), a first feed valve (71), a second feed valve (72), a third feed valve (73), a first discharge valve (74), a second discharge valve (82), a third discharge valve (82), a raw steam generation valve (77), a start-up steam valve (81), a raw steam generation valve (77) and a water valve (81) A starting water supplementing pipeline (91), a first starting steam generating pipeline (92), a first one-effect juice steam pipeline (93), a second one-effect juice steam pipeline (94), a starting secondary steam pipeline (95), a total condensed water pipeline (96), a vacuumizing pipeline (97), a condensed water discharging pipeline (98), a first feeding pipeline (99), a second feeding pipeline (100), a third feeding pipeline (101), a first discharging pipeline (102), a second discharging pipeline (103), a third discharging pipeline (104), a second one-effect juice steam pipeline (105) and a second starting steam generating pipeline (106),

The outlet end of the first intermediate water circulation pipeline (31) is connected with the heat medium inlet end of the heat pump condenser (2), the heat medium outlet end of the heat pump condenser (2) is connected with the inlet end of the second intermediate water circulation pipeline (32), the outlet end of the second intermediate water circulation pipeline (32) is connected with the heat medium inlet end of the first effective evaporation tank (61), the heat medium outlet end of the first effective evaporation tank (61) is connected with the inlet end of the first intermediate water circulation pipeline (31),

the inlet end of the first refrigerant pipeline (41) is connected with the refrigerant outlet end of the heat pump condenser (2), the outlet end of the first refrigerant pipeline (41) is respectively connected with the inlet end of the sixth refrigerant pipeline (46) and the inlet end of the seventh refrigerant pipeline (47), the sixth refrigerant pipeline (46) is provided with a second throttling expansion valve (5), the outlet end of the sixth refrigerant pipeline (46) is connected with the refrigerant inlet end of the heat pump first evaporator (6), the refrigerant outlet end of the heat pump first evaporator (6) is connected with the inlet end of the eighth refrigerant pipeline (48), the seventh refrigerant pipeline (47) is provided with a third throttling expansion valve (7), the outlet end of the seventh refrigerant pipeline (47) is connected with the refrigerant inlet end of the heat pump second evaporator (8), the refrigerant outlet end of the heat pump second evaporator (8) is connected with the inlet end of the ninth refrigerant pipeline (49), the ninth refrigerant pipeline (49) is provided with a second compressor (9), the refrigerant outlet end of the ninth refrigerant pipeline (49) is connected with the inlet end of the eighth refrigerant pipeline (48), the outlet end of the eighth refrigerant pipeline (48) is connected with the inlet end of the first compressor (1), the outlet end of the tenth refrigerant pipeline (50) is connected with the refrigerant inlet end of the heat pump condenser (2),

The inlet end of the first one-effect juice vapor pipeline (93) is connected with the air outlet end of the upper part of the one-effect evaporation tank (61), the outlet end of the first one-effect juice vapor pipeline (93) is connected with the heat medium inlet end of the second one-effect evaporation tank (62), the heat medium outlet end of the second one-effect evaporation tank (62) is connected with the inlet end of the second one-effect juice vapor pipeline (105), the inlet end of the second one-effect juice vapor pipeline (94) is connected with the air outlet end of the upper part of the second one-effect evaporation tank (62), the outlet end of the first one-effect steam pipeline (92) is connected with the raw steam inlet end of the starter (81), the raw steam outlet end of the starter (81) is connected with the inlet end of the second one-effect steam pipeline (106), a raw steam regulating valve (82) is arranged on a first starting raw steam pipeline (92), a raw steam condensation valve (83) is arranged on a second starting raw steam pipeline (106), the inlet end of a starting secondary steam pipeline (95) is connected with the air outlet end at the upper part of the starter (81), the outlet end of a second first effective juice steam pipeline (105), the outlet end of a second effective juice steam pipeline (94) and the outlet end of the starting secondary steam pipeline (95) are respectively connected with the inlet end of a first total exhaust steam pipeline (33), the outlet end of the first total exhaust steam pipeline (33) is connected with the heat release inlet end of a first evaporator (6) of a heat pump, the heat release outlet end of the first evaporator (6) of the heat pump is connected with the inlet end of a second total exhaust steam pipeline (34),

The outlet end of the second total exhaust steam pipeline (34) and the outlet end of the second starting steam generating pipeline (106) are respectively connected with the inlet end of the third total exhaust steam pipeline (35), the outlet end of the third total exhaust steam pipeline (35) is connected with the heat release inlet end of the heat pump second evaporator (8), the heat release outlet end of the heat pump second evaporator (8) is connected with the inlet end of the total condensation water pipeline (96), the outlet end of the total condensation water pipeline (96) is connected with the water inlet end of the condensation water collecting tank (66), the inlet end of the vacuumizing pipeline (97) is connected with the extraction opening end at the upper part of the condensation water collecting tank (66), the vacuumizing control valve (64) and the vacuum pump (65) are sequentially arranged on the vacuumizing pipeline (97) along the medium flow direction, the outlet end of the vacuumizing pipeline (97) is emptied, the inlet end of the condensation water discharging pipeline (98) is connected with the liquid outlet end at the lower part of the condensation water collecting tank (66), the condensation water discharging pipeline (98) is sequentially provided with the condensation water discharging pump (67) and the condensation water discharging valve (68) in the medium flow direction,

a starting water inlet valve (84) is arranged on the starting water supplementing pipeline (91), the outlet end of the starting water supplementing pipeline (91) is connected with the water inlet end at the lower part of the starter (81),

a first feeding valve (71) is arranged on the first feeding pipeline (99), the outlet end of the first feeding pipeline (99) is respectively connected with the inlet end of a second feeding pipeline (100) and the inlet end of a third feeding pipeline (101), a second feeding valve (72) is arranged on the second feeding pipeline (100), the outlet end of the second feeding pipeline (100) is connected with the inlet end of a first-effect evaporation tank (61), a third feeding valve (73) is arranged on the third feeding pipeline (101), the outlet end of the third feeding pipeline (101) is connected with the inlet end of a second-effect evaporation tank (62),

The inlet end of a first discharging pipeline (102) is connected with the discharge port end at the bottom of an effective evaporation tank (61), a first discharging valve (74) is arranged on the first discharging pipeline (102), the inlet end of a second discharging pipeline (103) is connected with the discharge port end at the bottom of a second effective evaporation tank (62), a second discharging valve (75) is arranged on the second discharging pipeline (103), the outlet end of the first discharging pipeline (102) and the outlet end of the second discharging pipeline (103) are respectively connected with the inlet end of a third discharging pipeline (104), and a third discharging valve (76) and a discharging pump (77) are sequentially arranged on the third discharging pipeline (104) along the medium flowing direction, and the outlet end of the third discharging pipeline (104) is discharged.

2. The dual stage compression heat pump dual effect evaporative concentration system as defined in claim 1 wherein: an effective condensate throttling device (63) is arranged on the second effective juice vapor pipeline (105).

3. A dual stage compression heat pump dual effect evaporative concentration system as claimed in claim 1 or 2 wherein: the second total exhaust steam pipeline (34) is provided with a first condensate U-shaped bend (10), and the second starting steam generating pipeline (106) is provided with a second condensate U-shaped bend (85).

4. A double-stage compression type heat pump double-effect evaporation concentration system is characterized in that: the double-stage compression type heat pump double-effect evaporation concentration system comprises a first compressor (1), a heat pump condenser (2), a second throttling expansion valve (5), a heat pump first evaporator (6), a third throttling expansion valve (7), a heat pump second evaporator (8), a second compressor (9), a first intermediate water circulation pipeline (31), a second intermediate water circulation pipeline (32), a first total exhaust steam pipeline (33), a second total exhaust steam pipeline (34), a third total exhaust steam pipeline (35), a first refrigerant pipeline (41), a sixth refrigerant pipeline (46), a seventh refrigerant pipeline (47), an eighth refrigerant pipeline (48), a ninth refrigerant pipeline (49), a tenth refrigerant pipeline (50), a first-effect evaporation tank (61), a second-effect evaporation tank (62), a vacuumizing control valve (64), a vacuum pump (65), a condensate collection tank (66), a condensate water discharge pump (67), a condensate water check valve (68), a first feed valve (71), a second feed valve (72), a third feed valve (73), a first discharge valve (74), a second discharge valve (82), a third discharge valve (82), a raw steam generation valve (77), a start-up steam valve (81), a raw steam generation valve (77) and a water valve (81) A starting water supplementing pipeline (91), a first starting steam generating pipeline (92), a first one-effect juice steam pipeline (93), a second one-effect juice steam pipeline (94), a starting secondary steam pipeline (95), a total condensed water pipeline (96), a vacuumizing pipeline (97), a condensed water discharging pipeline (98), a first feeding pipeline (99), a second feeding pipeline (100), a third feeding pipeline (101), a first discharging pipeline (102), a second discharging pipeline (103), a third discharging pipeline (104), a second one-effect juice steam pipeline (105) and a second starting steam generating pipeline (106),

the inlet end of the first refrigerant pipeline (41) is connected with the refrigerant outlet end of the heat pump condenser (2), a second throttling expansion valve (5) is arranged on the first refrigerant pipeline (41), the outlet end of the first refrigerant pipeline (41) is respectively connected with the inlet end of a sixth refrigerant pipeline (46) and the inlet end of a seventh refrigerant pipeline (47), the outlet end of the sixth refrigerant pipeline (46) is connected with the refrigerant inlet end of the heat pump first evaporator (6), the refrigerant outlet end of the heat pump first evaporator (6) is connected with the inlet end of an eighth refrigerant pipeline (48), a third throttling expansion valve (7) is arranged on the seventh refrigerant pipeline (47), the outlet end of the seventh refrigerant pipeline (47) is connected with the refrigerant inlet end of the heat pump second evaporator (8), the refrigerant outlet end of the heat pump second evaporator (8) is connected with the inlet end of a ninth refrigerant pipeline (49), the ninth refrigerant pipeline (49) is provided with a second compressor (9), the refrigerant outlet end of the ninth refrigerant pipeline (49) is connected with the inlet end of the eighth refrigerant pipeline (48), the outlet end of the eighth refrigerant pipeline (48) is connected with the first compressor (1) at the middle part of the inlet end of the eighth refrigerant pipeline (48), the outlet end of the tenth refrigerant pipeline (50) is connected with the refrigerant inlet end of the heat pump condenser (2),

5. The dual stage compression heat pump dual effect evaporative concentration system as defined in claim 4 wherein: an effective condensate throttling device (63) is arranged on the second effective juice vapor pipeline (105).

6. The dual stage compression heat pump dual effect evaporative concentration system as defined in claim 4 or 5 wherein: the second total exhaust steam pipeline (34) is provided with a first condensate U-shaped bend (10), and the second starting steam generating pipeline (106) is provided with a second condensate U-shaped bend (85).

7. A double-stage compression type heat pump double-effect evaporation concentration system is characterized in that: the double-effect evaporation concentration system of the double-effect compression type heat pump comprises a first compressor (1), a heat pump condenser (2), a first throttling expansion valve (3), a supercooling heat exchanger (4), a second throttling expansion valve (5), a heat pump first evaporator (6), a third throttling expansion valve (7), a heat pump second evaporator (8), a second compressor (9), a first medium water circulation pipeline (31), a second medium water circulation pipeline (32), a first total exhaust steam pipeline (33), a second total exhaust steam pipeline (34), a third total exhaust steam pipeline (35), a first refrigerant pipeline (41), a second refrigerant pipeline (42), a third refrigerant pipeline (43), a fourth refrigerant pipeline (44), a fifth refrigerant pipeline (45), a sixth refrigerant pipeline (46), a seventh refrigerant pipeline (47), an eighth refrigerant pipeline (48), a ninth refrigerant pipeline (49), a tenth refrigerant pipeline (50), a first-effect evaporation tank (61), a second-effect evaporation tank (62), a vacuum control valve (64), a vacuum pump (65), a condensation pump (66), a collection tank (67), a first discharge valve (73), a third feed valve (72), a condensation valve (72) and a discharge valve (72) A second discharge valve (75), a third discharge valve (76), a discharge pump (77), a starter (81), a raw steam regulating valve (82), a raw steam condensation valve (83), a starting water inlet valve (84), a starting water supplementing pipeline (91), a first starting raw steam pipeline (92), a first one-effect juice steam pipeline (93), a second one-effect juice steam pipeline (94), a starting secondary steam pipeline (95), a total condensation pipeline (96), a vacuumizing pipeline (97), a condensation water discharge pipeline (98), a first feeding pipeline (99), a second feeding pipeline (100), a third feeding pipeline (101), a first discharge pipeline (102), a second discharge pipeline (103), a third discharge pipeline (104), a second one-effect juice steam pipeline (105) and a second starting raw steam pipeline (106),

the inlet end of the first refrigerant pipeline (41) is connected with the refrigerant outlet end of the heat pump condenser (2), the outlet end of the first refrigerant pipeline (41) is respectively connected with the inlet end of the second refrigerant pipeline (42) and the inlet end of the third refrigerant pipeline (43), the outlet end of the second refrigerant pipeline (42) is connected with the first inlet end of the supercooling heat exchanger (4), the first outlet end of the supercooling heat exchanger (4) is connected with the inlet end of the fourth refrigerant pipeline (44), the third refrigerant pipeline (43) is provided with a first throttling expansion valve (3), the outlet end of the third refrigerant pipeline (43) is connected with the second inlet end of the heat pump (4), the second outlet end of the supercooling heat exchanger (4) is connected with the inlet end of the fifth refrigerant pipeline (45), the outlet end of the fifth refrigerant pipeline (45) is connected with the middle air supplementing end of the first compressor (1), the outlet end of the fourth refrigerant pipeline (44) is respectively connected with the inlet end of the sixth refrigerant pipeline (46) and the seventh refrigerant pipeline (46), the outlet end of the seventh refrigerant pipeline (46) is connected with the inlet end of the eighth refrigerant pipeline (46), the outlet end of the eighth refrigerant pipeline (46) is connected with the first refrigerant pipeline (6) of the eighth refrigerant pipeline (46), a third throttling expansion valve (7) is arranged on a seventh refrigerant pipeline (47), the outlet end of the seventh refrigerant pipeline (47) is connected with the refrigerant inlet end of a second evaporator (8) of the heat pump, the refrigerant outlet end of the second evaporator (8) of the heat pump is connected with the inlet end of a ninth refrigerant pipeline (49), a second compressor (9) is arranged on the ninth refrigerant pipeline (49), the outlet end of the ninth refrigerant pipeline (49) is connected with the middle part of an eighth refrigerant pipeline (48), the outlet end of the eighth refrigerant pipeline (48) is connected with the main air inlet end of the first compressor (1), the air outlet end of the first compressor (1) is connected with the inlet end of a tenth refrigerant pipeline (50), the outlet end of the tenth refrigerant pipeline (50) is connected with the refrigerant inlet end of the heat pump condenser (2),

8. The dual stage compression heat pump dual effect evaporative concentration system as defined in claim 7 wherein: an effective condensate throttling device (63) is arranged on the second effective juice vapor pipeline (105).

9. The dual stage compression heat pump dual effect evaporative concentration system as defined in claim 7 or 8 wherein: the second total exhaust steam pipeline (34) is provided with a first condensate U-shaped bend (10), and the second starting steam generating pipeline (106) is provided with a second condensate U-shaped bend (85).

10. A double-stage compression type heat pump double-effect evaporation concentration system is characterized in that: the double-effect evaporation concentration system of the double-effect compression type heat pump comprises a first compressor (1), a heat pump condenser (2), a first throttling expansion valve (3), a supercooling heat exchanger (4), a second throttling expansion valve (5), a heat pump first evaporator (6), a third throttling expansion valve (7), a heat pump second evaporator (8), a second compressor (9), a first medium water circulation pipeline (31), a second medium water circulation pipeline (32), a first total exhaust steam pipeline (33), a second total exhaust steam pipeline (34), a third total exhaust steam pipeline (35), a first refrigerant pipeline (41), a second refrigerant pipeline (42), a third refrigerant pipeline (43), a fourth refrigerant pipeline (44), a fifth refrigerant pipeline (45), a sixth refrigerant pipeline (46), a seventh refrigerant pipeline (47), an eighth refrigerant pipeline (48), a ninth refrigerant pipeline (49), a tenth refrigerant pipeline (50), a first-effect evaporation tank (61), a second-effect evaporation tank (62), a vacuum control valve (64), a vacuum pump (65), a condensation pump (66), a collection tank (67), a first discharge valve (73), a third feed valve (72), a condensation valve (72) and a discharge valve (72) A second discharge valve (75), a third discharge valve (76), a discharge pump (77), a starter (81), a raw steam regulating valve (82), a raw steam condensation valve (83), a starting water inlet valve (84), a starting water supplementing pipeline (91), a first starting raw steam pipeline (92), a first one-effect juice steam pipeline (93), a second one-effect juice steam pipeline (94), a starting secondary steam pipeline (95), a total condensation pipeline (96), a vacuumizing pipeline (97), a condensation water discharge pipeline (98), a first feeding pipeline (99), a second feeding pipeline (100), a third feeding pipeline (101), a first discharge pipeline (102), a second discharge pipeline (103), a third discharge pipeline (104), a second one-effect juice steam pipeline (105) and a second starting raw steam pipeline (106),

the inlet end of the first refrigerant pipeline (41) is connected with the refrigerant outlet end of the heat pump condenser (2), the outlet end of the first refrigerant pipeline (41) is respectively connected with the inlet end of the second refrigerant pipeline (42) and the inlet end of the third refrigerant pipeline (43), the outlet end of the second refrigerant pipeline (42) is connected with the first inlet end of the supercooling heat exchanger (4), the first outlet end of the supercooling heat exchanger (4) is connected with the inlet end of the fourth refrigerant pipeline (44), the fourth refrigerant pipeline (44) is provided with a second throttling expansion valve (5), the third refrigerant pipeline (43) is provided with a first throttling expansion valve (3), the outlet end of the third refrigerant pipeline (43) is connected with the second inlet end of the supercooling heat exchanger (4), the outlet end of the supercooling heat exchanger (4) is connected with the inlet end of the fifth refrigerant pipeline (45), the outlet end of the fifth refrigerant pipeline (45) is connected with the middle air supplementing end of the first compressor (1), the outlet end of the fourth refrigerant pipeline (44) is connected with the outlet end of the eighth refrigerant pipeline (46) and the outlet end of the eighth refrigerant pipeline (46) is connected with the inlet end of the eighth refrigerant pipeline (6), a third throttling expansion valve (7) is arranged on a seventh refrigerant pipeline (47), the outlet end of the seventh refrigerant pipeline (47) is connected with the refrigerant inlet end of a second evaporator (8) of the heat pump, the refrigerant outlet end of the second evaporator (8) of the heat pump is connected with the inlet end of a ninth refrigerant pipeline (49), a second compressor (9) is arranged on the ninth refrigerant pipeline (49), the outlet end of the ninth refrigerant pipeline (49) is connected with the middle part of an eighth refrigerant pipeline (48), the outlet end of the eighth refrigerant pipeline (48) is connected with the main air inlet end of the first compressor (1), the air outlet end of the first compressor (1) is connected with the inlet end of a tenth refrigerant pipeline (50), the outlet end of the tenth refrigerant pipeline (50) is connected with the refrigerant inlet end of the heat pump condenser (2),