CN210004618U

CN210004618U - evaporative cold space energy double-source heat pump heat recovery unit

Info

Publication number: CN210004618U
Application number: CN201920338583.7U
Authority: CN
Inventors: 李国斌
Original assignee: Hanrun United High-Tech Development (beijing) Co Ltd
Current assignee: Hanrun United High-Tech Development (beijing) Co Ltd
Priority date: 2019-03-11
Filing date: 2019-03-11
Publication date: 2020-01-31
Anticipated expiration: 2029-03-11

Abstract

The utility model discloses an cold space of evaporation can dual-source heat pump heat recovery unit, including compressor, cross valve, second cross valve, third cross valve, vapour and liquid separator, outdoor side heat transfer portion, functional module, indoor side heat exchanger, multi-functional heat exchanger, solar heat exchanger and a plurality of solenoid valve, check valve, the utility model discloses add positive displacement solar heat exchanger in the cold and hot pump of evaporation, provide the second heat source for heating and reach energy-conserving purpose, through addding the hot water storage tank, realize energy regulation general use, add multi-functional heat exchanger, realized the total heat recovery of air conditioner, satisfied the hot water demand of supplying life, the pipeline design of optimization has realized ten kinds of mode, realizes three big functions of refrigeration, heating, hot water, the multi-functional heat exchanger of extensible, except can realizing the heat recovery function, can also introduce third cold, heat source such as water, ground source, municipal sewage, industrial waste water etc. realize water source refrigeration, heat, hot water and defrosting demand, realized the pluralism of the energy.

Description

evaporative cold space energy double-source heat pump heat recovery unit

Technical Field

The utility model relates to an air conditioning equipment field especially relates to kinds of evaporation cold space energy double-source heat pump heat recovery unit who combines together solar energy technique and heat recovery technique and evaporation cold heat pump unit, solves under the different operating modes to refrigeration, heat, hot water demand, greatly improves evaporation cold heat pump refrigeration efficiency/heat efficiency and comprehensive efficiency.

Background

At present, the air-conditioning heat pump unit mainly comprises the following four types: (1) air-cooled heat pump-air conditioner using outdoor ambient air as cold and heat source; (2) water (ground) source heat pump-air conditioner using underground water, sewage, river, lake or soil as cold and heat source; (3) evaporative cooling heat pump-air conditioner using water as cold source and air as heat source; (4) solar heat pump-air conditioner using solar energy as heat source.

The evaporation cold and hot pump unit improves the refrigeration efficiency of the heat pump, and although the problem of low refrigeration efficiency of the air-cooled heat pump under the refrigeration working condition is solved, the following defects still exist:

1. the problem that the heating capacity of a unit using air as a heat source is seriously attenuated under a low-temperature working condition, particularly at the temperature of minus 35 ℃ or even lower, cannot be broken through, the efficiency is low, and the energy consumption is high.

2. The problem that the comfort degree is affected by the reduction of the indoor environment temperature caused by the adoption of refrigeration defrosting under the refrigeration working condition cannot be solved, the defrosting frequency of the air-cooled heat exchanger is high, the unit heating time is shortened, the defrosting time is long, and extra electric energy is consumed for defrosting.

3. The frosting phenomenon caused by the evaporation of the air-cooled heat exchanger cannot be solved, the indoor temperature is reduced, the use effect is influenced, and the unit efficiency is sacrificed due to the extra work of the defrosting compressor.

4. The condensation heat discharge under the refrigeration working condition of the evaporation cooling unit causes energy waste and environmental heat pollution, and increases the urban heat island phenomenon.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is to provide kinds of cold space of evaporation can dual-source heat pump heat recovery units, use solar energy to supply heat energy for the heat pump as the second heat source, realize high-efficient heating under the prerequisite that need not to change the frost, change the frost with solar energy heating heat accumulation mode, furthest reduces refrigeration and changes the frost and lead to indoor temperature fluctuation, realize that condensation heat recovery reaches energy reutilization, effectively reduce the energy waste, provide the third kind and heat the heat source, greatly expand unit service function.

In order to solve the technical problem, the utility model adopts the technical proposal that kinds of evaporative cold space energy double-source heat pump heat recovery units comprise:

the compressor is an enhanced vapor injection compressor and is provided with a flow outlet, a return port and an EVI injection port;

an th four-way valve, wherein the th four-way valve is provided with four interfaces a, b, c and d, and the interface d is connected with the outlet of the compressor;

the second four-way valve is provided with four interfaces of e, f, g and h, and the interface c of the th four-way valve is connected with the interface e of the second four-way valve;

the interface g of the second four-way valve is respectively connected with the interface j of the third four-way valve and the interface b of the th four-way valve;

the b interface of the th four-way valve, the g interface of the second four-way valve and the j interface of the third four-way valve are connected in parallel and are respectively connected with the return port of the compressor through the gas-liquid separator;

the outdoor heat exchange part is provided with an R, S interface, and an R interface of the outdoor heat exchange part is connected with a k interface of the third four-way valve;

the system comprises a functional module, a P interface of the functional module, an EVI injection port of a compressor, a P interface of the functional module, a fifth electromagnetic valve, a sixth electromagnetic valve, a seventh electromagnetic valve, a sixth;

the indoor side heat exchanger is provided with an M, N interface, the U interface of the functional module is connected with the N interface of the indoor side heat exchanger through a second one-way valve and a second electromagnetic valve, and the V interface of the functional module is connected with the N interface of the indoor side heat exchanger through a fourth one-way valve and a second electromagnetic valve; the M interface of the indoor side heat exchanger is connected with the f interface of the second four-way valve;

the multifunctional heat exchanger is provided with an O, T interface, a water inlet and a water outlet, a T interface of the multifunctional heat exchanger is connected with a fourth electromagnetic valve through a fifth one-way valve or a sixth one-way valve and then connected with a U interface of the functional module through a second one-way valve, or connected with a V interface of the functional module through a fourth one-way valve;

the solar heat exchanger comprises a water replenishing port, a refrigerant coil pipe, a water temperature sensor, a refrigerant inlet, a refrigerant outlet, an overflow port, a solar upper circulation port and a solar lower circulation port, wherein the solar upper circulation port is respectively connected with an th water replenishing electromagnetic valve and a end of a solar heat collecting vacuum pipe, the solar lower circulation port is connected with the other end of the solar heat collecting vacuum pipe through a solar circulating pump, the other end of the solar heat collecting vacuum pipe is connected with a water filling port of a heat storage water tank through a second water replenishing electromagnetic valve, a hot water lower circulation port of the heat storage water tank is connected with a water inlet of the multifunctional heat exchanger, a water outlet of the multifunctional heat exchanger is connected with a hot water upper circulation port of the heat storage water tank, the refrigerant outlet of the solar heat exchanger is connected with an i interface of a third four-way valve, the refrigerant inlet of the solar heat exchanger is connected with a U interface of the functional module through a fifth electromagnetic valve, a ninth electromagnetic valve and a second one-way valve, and the refrigerant inlet of the solar heat exchanger.

, replacing the heat storage water tank with an external heat source, wherein the external heat source is a third cold or heat source such as water, a ground source, municipal sewage, industrial wastewater and the like, the end of the external heat source is connected with the water inlet of the multifunctional heat exchanger, and the other end of the external heat source is connected with the water outlet of the multifunctional heat exchanger.

, the function module comprises a liquid storage tank, a drying filter, a electronic expansion valve, an economizer, a second electronic expansion valve and a sixth electromagnetic valve, a U interface of the function module is sequentially connected with the liquid storage tank, the drying filter, the economizer, a electronic expansion valve and a V interface, the drying filter is sequentially connected with the sixth electromagnetic valve, the second electronic expansion valve, the economizer and a Q interface, the drying filter is further connected with a P interface, and when the function module is used in combination with the enhanced vapor injection compressor, the evaporative cold space energy double-source heat pump heat recovery unit can be used for efficient refrigeration in a high-temperature high-humidity environment and efficient heating in a low-temperature environment.

, the outdoor heat exchange part comprises a fan, an air cooling heat exchanger, an evaporation cooling heat exchanger, a sprayer, a spray pump, a water collecting tank, a th functional electromagnetic valve A and a second functional electromagnetic valve B, the spray pump is arranged in the water collecting tank, the fan enables air to flow through the surface of the air cooling heat exchanger, the sprayer sprays cooling water to the surface of the evaporation cooling heat exchanger, an R interface of the outdoor heat exchange part is sequentially connected with an inlet end of the evaporation cooling heat exchanger, an outlet end of the evaporation cooling heat exchanger, an inlet end of the air cooling heat exchanger and an outlet end of the air cooling heat exchanger, an outlet end of the evaporation cooling heat exchanger is further connected with an inlet end of the second functional electromagnetic valve B, an outlet end of the air cooling heat exchanger is further connected with an inlet end of the th functional electromagnetic valve A, and an outlet end of the second functional electromagnetic valve B and an outlet end of the th functional electromagnetic valve A.

, the function module can be replaced by a second function module, the second function module is provided with a U, V interface, the second function module comprises a liquid storage tank, a drying filter and a electronic expansion valve, and a U interface is sequentially connected with the liquid storage tank, the drying filter, a electronic expansion valve and a V interface.

And , replacing the indoor heat exchanger with a multi-connected indoor unit, wherein the multi-connected indoor unit comprises a refrigerant fin heat exchanger and an indoor fan, and the indoor fan enables air to flow through the surface of the refrigerant fin heat exchanger for refrigerating and heating of the unit.

, the outdoor heat exchange part can be replaced by a second outdoor heat exchange part, the second outdoor heat exchange part is provided with a R, S interface, the second outdoor heat exchange part comprises a fan, an air cooling heat exchanger, an evaporative cooling heat exchanger, a sprayer, a spray pump, a water collecting tank, a third function electromagnetic valve C and a fourth function electromagnetic valve D, an inlet end of the third function electromagnetic valve C and an inlet end of the fourth function electromagnetic valve D are connected in parallel and then connected with an R interface of the second outdoor heat exchange part, an outlet end of the third function electromagnetic valve C is connected with an inlet end of the air cooling heat exchanger, an outlet end of the fourth function electromagnetic valve D is connected with an inlet end of the evaporative cooling heat exchanger, and an outlet end of the air cooling heat exchanger and an outlet end of the evaporative cooling heat exchanger are connected in parallel and then connected with an S interface of the second outdoor heat exchange part.

And , replacing the outdoor heat exchange part with a third chamber outer heat exchange part, wherein the third chamber outer heat exchange part is provided with a R, S interface, the third chamber outer heat exchange part comprises a fan, an air-cooled heat exchanger, an evaporative cooling heat exchanger, a sprayer, a spray pump, a water collection tank, a fifth function electromagnetic valve E and a sixth function electromagnetic valve F, the R interface of the third chamber outer heat exchange part is connected with the inlet end of the air-cooled heat exchanger, the outlet end of the air-cooled heat exchanger is connected with the inlet end of the evaporative cooling heat exchanger, the outlet end of the evaporative cooling heat exchanger is connected with the inlet end of the sixth function electromagnetic valve, the outlet end of the air-cooled heat exchanger is further connected with the inlet end of the fifth function electromagnetic valve E, and the outlet end of the fifth function electromagnetic valve E is connected with the S interface of the third chamber outer heat exchange part after.

The solar water heater has the beneficial effects that the solar water heater can realize cooling by multiple cold sources, heat supply by multiple heat sources, a preferred selection mode enables a unit to have more than ten functions of being in the most efficient working state, multiple functions of collecting to realize multiple functions of cooling, heating and hot water, the solar water heater is characterized in that a volumetric solar heat exchanger is additionally arranged in an evaporation cold source heat pump to provide a second heat source for heating so as to achieve the purpose of saving energy, a heat storage water tank is additionally arranged so as to realize energy regulation total use, a multifunctional heat exchanger (a cold-heat exchanger) is additionally arranged so as to realize air conditioning cooling/heat and total heat recovery and meet the requirements of heating/domestic hot water supply, an optimized pipeline design realizes three functions of refrigerating, heating and hot water by connecting various components, and an expandable multifunctional heat recovery function can be realized, and a third cold-source heat pump, a third heat source, a solar energy hot water pump, a solar defrosting heat pump, a hot water defrosting heat pump, a hot water source, a municipal wastewater heating heat exchanger and the like can be introduced so as to realize the requirements of water source and the water source.

Drawings

Fig. 1 is a schematic structural view of an embodiment of the double-source heat pump heat recovery unit for evaporative cooling space energy of the present invention.

Fig. 2 is an enlarged schematic view of a four-way valve 131 included in an embodiment of the present invention.

Fig. 3 is an enlarged schematic view of the second four-way valve 132 according to embodiment of the present invention.

Fig. 4 is an enlarged schematic view of the third four-way valve 133 according to embodiment of the present invention.

Fig. 5 is an enlarged schematic view of the compressor 1 according to the embodiment of the present invention.

Fig. 6 is an enlarged schematic view of the multifunctional heat exchanger 3 according to embodiment of the present invention.

Fig. 7 is an enlarged schematic view of the outdoor heat exchanging unit 4 according to embodiment of the present invention.

Fig. 8 is an enlarged schematic view of the indoor-side heat exchanger 5 according to embodiment of the present invention.

Fig. 9 is an enlarged schematic view of a solar heat exchanger 6 according to an embodiment of the present invention.

Fig. 10 is an enlarged schematic view of the hot water storage tank 15 according to embodiment of the present invention.

Fig. 11 is an enlarged schematic view of the functional module 10 included in the embodiment of the present invention.

Fig. 12 is a flow chart of an evaporative cooling refrigeration mode of embodiment of the present invention.

Fig. 13 is a flow chart of the combined evaporative cooling and air cooling refrigeration mode of embodiment of the present invention.

Fig. 14 is a flow chart of an air source heating mode according to embodiment of the present invention.

Fig. 15 is a flow chart of a solar heating mode according to embodiment of the present invention.

Fig. 16 is a flow chart of a solar heat storage and supply mode (external heat source heating mode) according to embodiment of the present invention.

Fig. 17 is a flow chart of an air source hot water mode of an embodiment of the present invention.

Fig. 18 is a flow chart of a solar heat pump hot water mode of embodiment of the present invention.

Fig. 19 is a flow chart of the cooling and domestic hot water simultaneous supply mode according to embodiment of the present invention.

Fig. 20 is a flow chart of a solar hot water supply mode according to embodiment of the present invention.

Fig. 21 is a flow chart of the refrigeration and defrosting mode of the embodiment of the present invention.

Fig. 22 is a flow chart of a solar defrosting mode according to the embodiment of the present invention.

Fig. 23 is a flow chart of a hot water defrosting mode (external heat source defrosting mode) according to embodiment of the present invention.

FIG. 24 is a schematic structural view of a second embodiment of the evaporative cooling multi-source heat pump unit of the present invention.

FIG. 25 is a schematic diagram of the third structure of the embodiment of the evaporation-cooling multi-source heat pump unit of the present invention.

FIG. 26 is a schematic diagram of the fourth embodiment of the evaporative cooling multi-source heat pump unit of the present invention.

FIG. 27 is a schematic diagram of the fifth embodiment of the evaporative cooling multi-source heat pump unit of the present invention.

FIG. 28 is a schematic diagram of a sixth embodiment of the evaporative cooling multi-source heat pump unit of the present invention.

Fig. 29 is a partially enlarged view of the second functional module 10a included in the second and fourth embodiments of the present invention.

Fig. 30 is a partially enlarged view of the multiple indoor units 5a according to the third and fourth embodiments of the present invention.

Fig. 31 is a partially enlarged view of the second outdoor heat exchanging portion 4a according to the fifth embodiment of the present invention.

Fig. 32 is a partially enlarged view of the third chamber outer heat exchanging portion 4b according to the sixth embodiment of the present invention.

The solar energy water heater comprises a compressor 1, a compressor 11, an outlet port 12, a return port 13, an EVI injection port 2, a gas-liquid separator 131, a fourth four-way valve 132, a second four-way valve 133, a third four-way valve 3, a multifunctional heat exchanger 31, a water inlet 32, a water outlet 4, an outdoor heat exchange part 41, a fan 42, an air-cooled heat exchanger 43, a sprayer 44, a spray pump 45, an evaporative cooling heat exchanger 46, a water collecting tank 4a, a second outdoor heat exchange part 4B, a third outdoor heat exchange part , a second functional solenoid valve B, a third functional solenoid valve C, a fourth functional solenoid valve D, a fifth functional solenoid valve E, a sixth functional solenoid valve F, a sixth functional solenoid valve 5, an indoor heat exchanger 5a, an indoor multi-unit 539, a 6, a solar heat exchanger 61, a water replenishing port 62, a coil pipe 63, a water temperature sensor 64, a water outlet 65, a refrigerant inlet 66, a refrigerant inlet 67, a solar energy upper circulation valve 68, a solar energy upper circulation unit 120, a solar energy water circulation unit 120, a solar energy upper circulation unit 120, a solar energy water heater 120, a lower circulation valve 121, a solar energy heat exchange module 117, a fifth heat exchange solenoid valve 120, a heat exchange solenoid valve 121, a fifth heat exchange solenoid valve 120, a fifth function solenoid valve 120, a 3615, a heat recovery solenoid valve 120, a 3615, a heat exchange solenoid valve 120, a heat pump 15, a fifth function solenoid valve 120, a fifth function solenoid valve 65, a fifth function solenoid valve 15, a heat pump 15, a warm water inlet 120, a warm water inlet 103, a warm water inlet 120, a warm water inlet, a warm water heater.

Detailed Description

The present invention will be described in further detail in with reference to specific embodiments.

Example

Fig. 1-11, the structure schematic diagram and each partial enlarged view of the embodiment of the heat recovery unit of the evaporative cold space energy dual-source heat pump of the present invention.

A double-source heat pump heat recovery unit for evaporative cold space energy, comprising:

the compressor 1 is an enhanced vapor injection compressor and is provided with an outlet 11, a return port 12 and an EVI injection port 13;

an -th four-way valve 131, wherein the -th four-way valve 131 has four ports a, b, c and d, and the port d is connected with the outflow port 11 of the compressor 1;

a second four-way valve 132, wherein the second four-way valve 132 has four interfaces of e, f, g and h, and an interface c of the -th four-way valve 131 is connected with an interface e of the second four-way valve 132;

a third four-way valve 133, wherein the third four-way valve 133 is provided with four interfaces of i, j, k and l, and an interface h of the second four-way valve 132 is connected with an interface l of the third four-way valve 133;

a gas-liquid separator 2, wherein a b interface of the th four-way valve 131, a g interface of the second four-way valve 132 and a j interface of the third four-way valve 133 are connected in parallel and are respectively connected with a return opening of the compressor 1 through the gas-liquid separator 2;

an outdoor heat exchanging portion 4, the outdoor heat exchanging portion 4 having an R, S interface, an R interface of the outdoor heat exchanging portion 4 being connected to a k interface of the third four-way valve 133;

the functional module 10 is provided with an U, V, P, Q interface, an S interface of the outdoor heat exchanging part 4 is connected with a U interface of the functional module 10 through a electromagnetic valve 111 and a one-way valve 120 and is connected with a V interface of the functional module 10 through a electromagnetic valve 111 and a third one-way valve 122, the S interface of the outdoor heat exchanging part 4 is connected with the V interface of the functional module 10 through a electromagnetic valve 111, an eighth electromagnetic valve 118 and a ninth electromagnetic valve 119 and is connected with the V interface of the functional module 10 through a fourth one-way valve 123, a Q interface of the functional module 10 is connected with an EVI injection port 13 of the compressor 1, and a P interface of the functional module 10 is connected with the EVI injection port 13 of the compressor 1 through a seventh electromagnetic valve 117 and a thermal;

the indoor heat exchanger 5, the indoor heat exchanger 5 has an M, N interface, the U interface of the functional module 10 is connected to the N interface of the indoor heat exchanger 5 through the second check valve 121 and the second electromagnetic valve 112, and the V interface of the functional module 10 is connected to the N interface of the indoor heat exchanger 5 through the fourth check valve 123 and the second electromagnetic valve 112; an M port of the indoor-side heat exchanger 5 is connected to an f port of the second four-way valve 132;

the multifunctional heat exchanger 3 is provided with an O, T interface, a water inlet 31 and a water outlet 32, a T interface of the multifunctional heat exchanger 3 is connected with a fourth electromagnetic valve 114 through a fifth one-way valve 124 or a sixth one-way valve 125, then is connected with a U interface of the functional module 10 through a second one-way valve 121, and is connected with a V interface of the functional module 10 through a fourth one-way valve 123, the T interface of the multifunctional heat exchanger 3 is also connected with a one-way valve 120 and a third one-way valve 122 respectively after passing through the sixth one-way valve 125 and a third electromagnetic valve 113, and an O interface of the multifunctional heat exchanger 3 is connected with an a interface of a four-way valve 131;

the solar heat exchanger 6 comprises a water replenishing port 61, a refrigerant coil 62, a water temperature sensor 63, a refrigerant inlet 65, a refrigerant outlet 64, an overflow port 66, a solar upper circulation port 67 and a solar lower circulation port 68, wherein the solar upper circulation port 67 is respectively connected with a water replenishing electromagnetic valve 162 and a end of a solar heat collecting vacuum tube 16, the solar lower circulation port 68 is connected with the other end of the solar heat collecting vacuum tube 16 through a solar circulating pump 161, the other end of the solar heat collecting vacuum tube 16 is also connected with a water filling port 15a of a heat storage water tank 15 through a second water replenishing electromagnetic valve 163, a hot water lower circulation port 15d of the heat storage water tank 15 is connected with a water inlet 31 of the multifunctional heat exchanger 3, a water outlet 32 of the multifunctional heat exchanger 3 is connected with a hot water upper circulation port 15c of the heat storage water tank 15, the i interface of the outlet 64 of the solar heat exchanger 6 is connected with a third check valve 133, the inlet 65 of the solar heat exchanger 6 is connected with a U interface of the functional module 10 through a fifth electromagnetic valve 115, a ninth electromagnetic valve 119 and a fourth check valve 123;

, the heat storage water tank 15 can be replaced by an external heat source, the external heat source is a third cold or heat source such as water, a ground source, municipal sewage, industrial wastewater and the like, the end of the external heat source is connected with the water inlet 31 of the multifunctional heat exchanger 3, and the other end of the external heat source is connected with the water outlet 32 of the multifunctional heat exchanger 3.

, the function module 10 comprises a liquid storage tank 7, a drying filter 8, a electronic expansion valve 101, an economizer 9, a second electronic expansion valve 102 and a sixth electromagnetic valve 116, a U interface of the function module 10 is sequentially connected with the liquid storage tank 7, the drying filter 8, the economizer 9, a electronic expansion valve 101 and a V interface, the drying filter 8 is sequentially connected with the sixth electromagnetic valve 116, the second electronic expansion valve 102, the economizer 9 and a Q interface, the drying filter 8 is further connected with a P interface, and when the function module 10 is used in combination with the air injection enthalpy increasing compressor, the evaporative cold space energy double-source heat pump heat recovery unit can be used for refrigerating and heating in a low-temperature environment.

, the outdoor heat exchanging part 4 comprises a fan 41, an air-cooled heat exchanger 42, an evaporative cooling heat exchanger 45, a sprayer 43, a spray pump 44, a water collecting tank 46, a functional electromagnetic valve A and a second functional electromagnetic valve B, the spray pump 44 is arranged in the water collecting tank 46, the fan 41 makes air flow through the surface of the air-cooled heat exchanger 42, the sprayer 43 sprays cooling water to the surface of the evaporative cooling heat exchanger 45, the R interface of the outdoor heat exchanging part 4 is sequentially connected with the inlet end 451 of the evaporative cooling heat exchanger 45, the outlet end 452 of the evaporative cooling heat exchanger 45, the inlet end 421 of the air-cooled heat exchanger 42 and the outlet end 422 of the air-cooled heat exchanger 42, the outlet end 452 of the evaporative cooling heat exchanger 45 is further connected with the inlet end B1 of the second functional electromagnetic valve B, the outlet end 422 of the air-cooled heat exchanger 42 is further connected with the inlet end A1 of the functional electromagnetic valve A, and the outlet ends B2 and A2 of the second functional electromagnetic valve B and are connected in parallel and then.

The evaporative cooling multi-source heat pump unit of the embodiment has the following working modes:

() evaporative cooling refrigeration mode

As shown in FIG. 12, in this mode, the a-B ends and the c-d ends of the fourth valve 131 of are communicated, the e-h ends and the f-g ends of the second four valve 132 are communicated, the j-i ends and the l-k ends of the third four valve 133 are communicated, the spray pump 44 is turned on, the blower 41 is turned on, the sprayer 43 is in a spray state, the second functional solenoid valve B is turned on, the functional solenoid valve A is turned off, the compressor 1 is in a working state, the seventh solenoid valve 117 is turned on or off at a set temperature, for example, when the temperature of the compressor is higher than a certain set value (for example, 95 ℃).

In the refrigerant circuit, the second, th, 112 th, and sixth solenoid valves are opened, and the th, 113 th, 114 th, 115 th, 118 eighth, and 119 ninth solenoid valves are closed.

The liquid injection enthalpy-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from the outlet 11 of the compressor 1, enters the d end inlet and the c end outlet of the four-way valve 131, enters the e end inlet and the h end outlet of the second four-way valve 132, enters the l end inlet and the k end outlet of the third four-way valve 133, enters the evaporative cooling heat exchanger 45, enters the liquid storage tank 7 and the drying filter 8 through the second functional electromagnetic valve B, the electromagnetic valve 111 and the one-way valve 120, and is divided into two paths:

(1) in the main loop, after the economizer 9 exchanges heat with refrigerant on the other side of the economizer in the secondary loop to be condensed and cooled by , the refrigerant is cooled to low-temperature and low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, the refrigerant is discharged through a fourth one-way valve 123 and enters the indoor heat exchanger 5 through a second electromagnetic valve 112, the liquid refrigerant exchanges heat with indoor circulating water at a lower temperature flowing through the indoor heat exchanger 5, the refrigerant is vaporized and heated to absorb heat, and the indoor circulating water at the lower temperature is cooled to obtain chilled water so as to achieve the refrigeration purpose.

(2) And in the auxiliary EVI loop, after the pressure of the second electronic expansion valve 102 is reduced by throttling through a sixth electromagnetic valve 116, the refrigerant is subjected to heat exchange and preliminary vaporization and temperature rise through another side of the economizer 9 and a refrigerant at the main loop side, the refrigerant is changed into medium-temperature medium-pressure steam, the medium-temperature medium-pressure steam returns to the EVI injection port 13 of the compressor and enters the compressor 1, and cycles are completed.

When the temperature of the compressor 1 is high, in order to prevent the compressor 1 from being broken down by high temperature, the seventh electromagnetic valve 117 is opened, the sixth electromagnetic valve 116 is closed, the secondary evaporation amount of the refrigerant entering the economizer 9 is reduced, the refrigerant returns to the EVI injection port 13 of the compressor after being throttled and depressurized by the seventh electromagnetic valve 117 and the thermal expansion valve, and the secondary refrigerant backflow amount is increased, so that the temperature of the compressor 1 is reduced, and the compressor is prevented from being burnt.

Evaporative cooling and air cooling combined refrigeration mode

As shown in FIG. 13, in this mode, the a-B ends and the c-d ends of the fourth valve 131 of are communicated, the e-h ends and the f-g ends of the second four valve 132 are communicated, the j-i ends and the l-k ends of the third four valve 133 are communicated, the spray pump 44 is turned on, the blower 41 is turned on, the spray 43 is in a spray state, the second functional solenoid valve B is closed, the functional solenoid valve A is opened, the compressor 1 is in a working state, the seventh solenoid valve 117 is opened or closed at a set temperature, such as when the temperature of the compressor is higher than a certain set value (e.g., 95 ℃).

In the refrigerant circuit, the th function solenoid valve A, the th solenoid valve 111, the second solenoid valve 112, and the sixth solenoid valve 116 are opened, and the second function solenoid valve B, the third solenoid valve 113, the eighth solenoid valve 118, the fourth solenoid valve 114, the fifth solenoid valve 115, and the ninth solenoid valve 119 are closed.

The liquid injection enthalpy-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant sprayed from the outflow port 11 of the compressor 1 enters the end inlet of the fourth valve 131d of the , enters the end inlet of the second four-way valve 132 after the end outlet of the c, enters the end inlet of the e and the end outlet of the h, enters the end inlet of the third four-way valve 133 and the end outlet of the k, enters the evaporative cooling heat exchanger 45 and the air cooling heat exchanger 42, enters the liquid storage tank 7 and the drying filter 8 through the functional electromagnetic valve A, the electromagnetic valve 111 and the one-way valve 120, and is divided into two paths:

(1) in the main loop, after the economizer 9 exchanges heat with refrigerant on the other side of the economizer in the secondary loop to be condensed and cooled in , the refrigerant is cooled to low-temperature low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, the low-temperature low-pressure refrigerant liquid refrigerant is discharged through a fourth one-way valve 123 and enters the indoor heat exchanger 5 through a second electromagnetic valve 112, the liquid refrigerant exchanges heat with indoor low-temperature circulating water flowing through the indoor heat exchanger 5, the refrigerant is vaporized and heated to absorb heat, and the indoor circulating water with low temperature is cooled to obtain chilled water so as to achieve the refrigeration purpose.

(2) And in the auxiliary EVI loop, after the pressure of the second electronic expansion valve 102 is reduced by throttling through a sixth electromagnetic valve 116, the refrigerant is subjected to heat exchange and preliminary vaporization and temperature rise through another side of the economizer 9 and a refrigerant at the main loop side, the refrigerant is changed into medium-temperature medium-pressure steam, the medium-temperature medium-pressure steam returns to the EVI injection port 13 of the compressor, and the medium-temperature medium-pressure steam enters the compressor to finish cycles.

When the temperature of the compressor 1 is high, in order to prevent the compressor from high-temperature breakdown, the seventh electromagnetic valve 117 is opened, the sixth electromagnetic valve 116 is closed, the secondary evaporation amount of the refrigerant entering the economizer 9 is reduced, and the return flow amount of the secondary refrigerant is increased, so that the temperature of the compressor is reduced, and the compressor is prevented from being burnt.

(III) air source heating mode

As shown in FIG. 14, in this mode, the a-B ends and the c-d ends of the four-way valve 131 of are communicated, the e-f ends and the h-g ends of the second four-way valve 132 are communicated, the j-i ends and the l-k ends of the third four-way valve 133 are communicated, the spray pump 44 is closed, the fan 41 is started, the spray 43 is in a closed state, the second functional solenoid valve B is closed, the functional solenoid valve A is opened, the evaporative cooling heat exchanger 45 functions as an evaporator, the compressor 1 is in a working state, the seventh solenoid valve 117 is opened or closed at a set temperature, and is opened (e.g., 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the second solenoid valve 112, the sixth solenoid valve 116, and the solenoid valve 111 are open, and the fourth solenoid valve 114, the fifth solenoid valve 115, the eighth solenoid valve 118, the third solenoid valve 113, and the ninth solenoid valve 119 are closed.

The spray enthalpy-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is sprayed from an outflow port 11 of the compressor 1, enters a d end inlet and a c end outlet of a fourth valve 131 of , enters an indoor side heat exchanger 5 after entering an e end inlet and an f end outlet of a second four-way valve 132, a spray pump 44 is closed, a fan 41 is started, a spray device 43 stops spraying, a second functional electromagnetic valve B is closed, a functional electromagnetic valve A is opened, an evaporative cooling heat exchanger 45 plays the role of an evaporator at the moment, refrigerant steam exchanges heat with secondary refrigerant (water) flowing through the indoor side heat exchanger 5 in the indoor side heat exchanger 5, heated hot water is conveyed to an indoor fan coil pipe under the action of a refrigeration pump, indoor air exchanges heat under the action of the fan, the secondary refrigerant (water) heats the indoor air to achieve the purpose of air conditioning and heating, the refrigerant is liquefied after being cooled in the indoor side heat exchanger 5, the high-temperature and high-pressure refrigerant steam is changed into high-temperature and high-pressure liquid refrigerant at the moment, and the refrigerant sequentially passes through a:

(1) in the main loop, refrigerant enters for condensation and temperature reduction through heat exchange between the economizer 9 and refrigerant at the other side of the economizer in the secondary loop, is reduced to low-temperature low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, passes through a third one-way valve 122 and a electromagnetic valve 111, then sequentially enters the air-cooled heat exchanger 42 and the evaporative cooling heat exchanger 45, is gasified, evaporated and absorbs heat in air under the combined action of the evaporative cooling heat exchanger 45 and the air-cooled heat exchanger 42 under the forced convection action of a fan 41, the low-temperature low-pressure liquid refrigerant is changed into low-temperature low-pressure refrigerant steam, passes through a k end inlet and an l end outlet of a third four-way valve 133, passes through an h end inlet and a g end outlet of a second four-way valve 132, passes through a gas-liquid separator 2 and then returns to a return port 12.

(2) And in the auxiliary EVI circuit, after the pressure is reduced by throttling through the sixth electromagnetic valve 116 and the second electronic expansion valve 102, the refrigerant on the side of the economizer 9 and the refrigerant on the main circuit side are subjected to heat exchange, vaporization and temperature rise to become medium-temperature and medium-pressure steam, the medium-temperature and medium-pressure steam returns to the EVI injection port 13 of the compressor 1, and the medium-temperature and medium-pressure steam enters the compressor to finish cycles.

When the temperature of the compressor 1 is high, in order to prevent the compressor from high-temperature breakdown, the seventh electromagnetic valve 117 is opened, the sixth electromagnetic valve 116 is closed, the secondary evaporation amount of the refrigerant entering the economizer 9 is reduced, and the return flow amount of the secondary refrigerant is increased, so that the temperature of the compressor is reduced.

The solar heat collection circulation heats according to the temperature difference method. When the solar heat supply or the solar heat storage heat supply is finished, the mode is started to supply heat.

(IV) solar heating mode

As shown in FIG. 15, the mode is that the solar heat exchanger is started when the temperature of the solar heat exchanger reaches the set temperature during the full day, in this mode, the a-B ends and the c-d ends of the fourth valve 131 of the are communicated, the e-f ends and the h-g ends of the second four valve 132 are communicated, the l-i ends and the j-k ends of the third four valve 133 are communicated, the spray pump 44 is closed, the fan 41 is closed, the spray 43 is in the closed state, the second functional solenoid valve B is closed, the functional solenoid valve A is closed, the compressor 1 is in the working state, the seventh solenoid valve 117 is opened or closed at the set temperature, and is opened (for example, 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the second solenoid valve 112, the sixth solenoid valve 116, the eighth solenoid valve 118, and the fifth solenoid valve 115 are opened, and the fourth solenoid valve 114, the ninth solenoid valve 119, the solenoid valve 111, and the third solenoid valve 113 are closed.

The steam-injection and augmentation-contained compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from an outflow port 11 of the compressor 1, enters a d end inlet and a c end outlet of a fourth valve 131 of , enters an indoor side heat exchanger 5 after entering an e end inlet and an f end outlet of a second four-way valve 132, a spray pump 44 is closed, a fan 41 is closed, a spray device 43 stops spraying, a second functional solenoid valve B is closed, a functional solenoid valve A is closed, refrigerant steam exchanges heat with secondary refrigerant (water or antifreeze) in the indoor side heat exchanger 5, the heated secondary refrigerant (water or antifreeze) conveys hot water to an indoor fan coil under the action of a refrigeration pump, indoor air exchanges heat with the secondary refrigerant under the action of the fan, the indoor air is heated to achieve the purpose of air conditioning and heating, the refrigerant is liquefied after being cooled in the indoor side heat exchanger 5, at the moment, the high-temperature and high-pressure steam is changed into high-temperature and high-pressure liquid refrigerant, and the high-temperature and high-pressure liquid refrigerant sequentially:

(1) in the main loop, after the refrigerant is subjected to heat exchange with another refrigerant at side of the economizer in the secondary loop through the economizer 9 and is condensed and cooled in , the refrigerant is cooled to be low-temperature low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, and the low-temperature low-pressure refrigerant liquid refrigerant enters the solar heat exchanger 6 after passing through a third one-way valve 122, an eighth electromagnetic valve 118 and a fifth electromagnetic valve 115, the low-temperature low-pressure liquid refrigerant is vaporized and evaporated to absorb heat in the sun, the low-temperature low-pressure liquid refrigerant is changed into low-temperature low-pressure refrigerant steam, the low-temperature low-pressure refrigerant steam sequentially enters and exits through an i end and an l end of a third four-way valve 133, and enters and exits through a g end of a second four-way valve 132.

The solar heat collection cycle is circulated according to a temperature difference method, and a mode is set.

(V) solar heat storage and supply mode (external heat source heat supply mode)

As shown in FIG. 16, the two modes are respectively started when the temperature of the solar heat exchanger is higher or an external heat source is sufficient when the sunshine is sufficient, ends a-B and c-d of a four-way valve 131 of the are communicated, ends e-f and h-g of a second four-way valve 132 are communicated, ends l-i and j-k of a third four-way valve 133 are communicated, a spray pump 44 is closed, a fan 41 is closed, a spray device 43 is in a closed state, a second functional electromagnetic valve B is closed, a functional electromagnetic valve A is closed, the compressor 1 is in a working state, a seventh electromagnetic valve 117 is opened or closed at a set temperature, and is opened (such as 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the second solenoid valve 112, the sixth solenoid valve 116, and the third solenoid valve 113 are opened, and the fourth solenoid valve 114, the ninth solenoid valve 119, the solenoid valve 111, the fifth solenoid valve 115, and the eighth solenoid valve 118 are closed.

(1) in the main loop, refrigerant on the other side of an economizer in a secondary loop exchanges heat through an economizer 9 and is condensed and cooled in a step, the refrigerant is cooled to be low-temperature low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, the low-temperature low-pressure refrigerant liquid refrigerant enters the multifunctional heat exchanger 3 after passing through a third one-way valve 122, a third electromagnetic valve 113 and a fifth one-way valve 124, the low-temperature low-pressure liquid refrigerant exchanges heat with circulating water with higher temperature flowing in from a water inlet 31, the heat in the sun stored in the heat storage water tank 15 or the heat of an external heat source is absorbed and vaporized and evaporated, the circulating water with higher temperature is cooled and then is conveyed back to the heat storage water tank 15 or the external heat source from a water outlet 32 under the action of a heat recovery pump 151, at the moment, the low-temperature low-pressure liquid refrigerant is changed into low-temperature low-pressure refrigerant steam, the low-temperature low-pressure refrigerant steam sequentially passes through an.

(2) And in the auxiliary EVI circuit, after being throttled and depressurized by the sixth electromagnetic valve 116 and the second electronic expansion valve 102, the refrigerant on the side of the economizer 9 and the refrigerant on the main circuit side are subjected to heat exchange, vaporization and temperature rise, then the refrigerant is changed into medium-temperature medium-pressure steam, the medium-temperature medium-pressure steam returns to the EVI injection port 13 of the compressor, and the medium-temperature medium-pressure steam enters the compressor to finish cycles.

(VI) air source hot water mode

As shown in FIG. 17, in this mode, the a-d terminals and the c-B terminals of the fourth valve 131 of are connected, the e-f terminals and the h-g terminals of the second four valve 132 are connected, the j-i terminals and the l-k terminals of the third four valve 133 are connected, the spray pump 44 is turned off, the blower fan 41 is turned on, the spray unit 43 is in a turned-off state, the second functional solenoid valve B is turned off, the functional solenoid valve A is turned on, the compressor 1 is in an operating state, the seventh solenoid valve 117 is turned on or off at a set temperature, and is turned on (e.g., 95 ℃) when the temperature of the compressor is higher than a certain set.

In each refrigerant circuit, the fourth solenoid valve 114, the sixth solenoid valve 116, and the solenoid valve 111 are open, and the second solenoid valve 112, the third solenoid valve 113, the fifth solenoid valve 115, the eighth solenoid valve 118, and the ninth solenoid valve 119 are closed.

The steam-injection enthalpy-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from an outflow port 11 of the compressor 1, enters a d end and an a end of a four-way valve 131 of a , enters the multifunctional heat exchanger 3 after entering and exiting from a d end, a spray pump 44 is turned off, a fan 41 is started, a spray thrower 43 stops spraying, a second functional electromagnetic valve B is turned off, a functional electromagnetic valve A is turned on, a high-temperature and high-pressure steam refrigerant and circulating water with lower temperature are subjected to heat exchange in the multifunctional heat exchanger 3, then are condensed, cooled and liquefied, at the moment, high-temperature and high-pressure refrigerant steam is changed into high-temperature and high-pressure liquid refrigerant, and enters a liquid storage tank 7:

(1) in the main loop, refrigerant on the other side of the economizer in the secondary loop exchanges heat through the economizer 9 and is condensed and cooled in , the refrigerant is cooled to low-temperature low-pressure refrigerant liquid refrigerant through a th electronic expansion valve 101, the low-temperature low-pressure refrigerant liquid refrigerant sequentially enters the air-cooled heat exchanger 42 and the evaporative cooling heat exchanger 45 through a third one-way valve 122 and a th electromagnetic valve 111, the heat in outdoor air is absorbed under the forced action of a fan 41, the refrigerant is vaporized and evaporated and heated, a function electromagnetic valve A is opened, a second function electromagnetic valve B is closed, the evaporative cooling heat exchanger plays the role of an evaporator, the low-temperature low-pressure liquid refrigerant is changed into low-temperature low-pressure refrigerant steam under the combined action of the evaporative cooling heat exchanger 45 and the air-cooled heat exchanger 42, the low-temperature low-pressure refrigerant steam passes through a k end and an l end of a third four-way valve 133 and passes through an h end inlet and a g end of a second.

When the temperature of the compressor 1 is high, in order to prevent the compressor from high-temperature breakdown, the seventh electromagnetic valve 117 is opened while the sixth electromagnetic valve 116 is closed, the secondary evaporation amount of the refrigerant entering the economizer 9 is reduced, and the return flow amount of the secondary refrigerant is increased, so that the temperature of the compressor is reduced.

The mode is a solar hot water mode which is started preferentially after a cooling and heat recovery mode in summer, and is started when the temperature of the heat storage water tank does not reach a set value (55 ℃) after the solar hot water mode is ended. The solar heat collection cycle is cycled according to a temperature difference method.

(VII) solar heat pump hot water mode

As shown in FIG. 18, in this mode, the a-d terminals and the c-B terminals of the fourth valve 131 of are communicated, the e-f terminals and the h-g terminals of the second four valve 132 are communicated, the l-i terminals and the j-k terminals of the third four valve 133 are communicated, the spray pump 44 is closed, the blower fan 41 is closed, the spray device 43 is in a closed state, the second functional solenoid valve B is closed, the functional solenoid valve A is closed, the compressor 1 is in a working state, the seventh solenoid valve 117 is opened or closed at a set temperature, and is opened (e.g., 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the third solenoid valve 113, the fifth solenoid valve 115, the sixth solenoid valve 116, and the ninth solenoid valve 119 are opened, and the -th solenoid valve 111, the second solenoid valve 112, the fourth solenoid valve 114, and the eighth solenoid valve 118 are closed.

The steam-injection culvert-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from an outflow port 11 of the compressor 1, enters a port d of a four-way valve 131 and enters a multifunctional heat exchanger 3 after exiting a port a, a spray pump 44 is closed, a fan 41 is stopped, a spray device 43 stops spraying, a second functional electromagnetic valve B is closed, a functional electromagnetic valve A is closed, high-temperature and high-pressure steam refrigerant and circulating water with lower temperature flowing in from a water inlet 31 are subjected to heat exchange in the multifunctional heat exchanger 3 and then are condensed, cooled and liquefied, the circulating water with lower temperature is heated and then flows out of the multifunctional heat exchanger 3 from a water outlet 32 to achieve the purpose of heat recovery, at the moment, high-temperature and high-pressure refrigerant steam is changed into high-temperature and high-pressure liquid refrigerant and flows out of the multifunctional heat exchanger 3, and then enters:

(1) in the main loop, after the refrigerant is subjected to heat exchange with another side refrigerant of an economizer in a secondary loop through an economizer 9 and is condensed and cooled in a step, the refrigerant is cooled to be low-temperature and low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, the low-temperature and low-pressure refrigerant liquid refrigerant enters the solar heat exchanger 6 through a fourth one-way valve 123, a ninth electromagnetic valve 119 and a fifth electromagnetic valve 115 to absorb solar heat for vaporization and evaporation, the low-temperature and low-pressure liquid refrigerant is changed into low-temperature and low-pressure refrigerant steam, the low-temperature and low-pressure refrigerant steam enters an i end and an l end of a third four-way valve 133 and enters an h end and a g end of a second four-way valve 132 and returns to a return port 12 of.

(2) And in the auxiliary EVI loop, after being throttled and depressurized by the electromagnetic valve 115 and the electronic expansion valve 102, the refrigerant on the side of the economizer 9 and the refrigerant on the main loop side are subjected to heat exchange, vaporization and temperature rise, then the refrigerant is changed into medium-temperature medium-pressure steam, returns to the EVI injection port 13 of the compressor 1, and enters the compressor to finish cycles.

The mode is the end of the cooling and heat recovery mode, and when the temperature of the hot water storage tank 15 is lower than the set value (for example, 55 ℃), the mode is preferentially started.

(eight) mode for refrigerating and supplying domestic hot water simultaneously

In this mode, the a-d ends and the c-B ends of the fourth valve 131 of are communicated, the e-f ends and the h-g ends of the second four valve 132 are communicated, the j-i ends and the l-k ends of the third four valve 133 are communicated, the spray pump 44 is turned off, the fan 41 is stopped, the spray device 43 is in a spray stop state, the second functional solenoid valve B is turned off, the functional solenoid valve A is turned off, the compressor 1 is in a working state, the seventh solenoid valve 117 is turned on or off at a set temperature, and is turned on (for example, 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the third solenoid valve 113, the sixth solenoid valve 116, and the second solenoid valve 112 are opened, and the th solenoid valve 111, the fourth solenoid valve 114, the fifth solenoid valve 115, the ninth solenoid valve 119, and the eighth solenoid valve 118 are closed.

The steam-injection culvert-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from an outflow port 11 of the compressor 1, enters a d end and exits from an a end of a four-way valve 131 and then enters the multifunctional heat exchanger 3, the spray pump 44 is closed, the fan 41 is stopped, the spray device 43 stops spraying, the second functional electromagnetic valve B is closed, the functional electromagnetic valve A is closed, high-temperature and high-pressure steam refrigerant and circulating water with lower temperature are subjected to heat exchange in the multifunctional heat exchanger 3, then are condensed, cooled and liquefied, the circulating water with lower temperature absorbs heat of the refrigerant, then are heated and flow out of the multifunctional heat exchanger 3, the purpose of heat recovery is achieved, at the moment, the high-temperature and high-pressure refrigerant steam is changed into high-temperature and high-pressure liquid refrigerant, and the high-:

(1) in the main loop, the refrigerant is condensed and cooled in step by heat exchange between the economizer 9 and another refrigerant at side of the economizer in the secondary loop, and then is cooled to be low-temperature and low-pressure refrigerant liquid refrigerant, the refrigerant is discharged through a fourth one-way valve 123 and a second electromagnetic valve 112 and then enters the indoor side heat exchanger 5, the low-temperature and low-pressure liquid refrigerant exchanges heat with indoor higher-temperature water flowing through another side of the indoor side heat exchanger 5 to prepare chilled water, the chilled water is conveyed to the indoor through a refrigeration pump to achieve the purpose of refrigeration, the low-temperature refrigerant is vaporized, evaporated and absorbed to be changed into higher-temperature refrigerant steam, the refrigerant steam enters through an f end and an e end of a second four-way valve 132, enters through a c end and a b end of a four-way valve 131, passes through a gas-liquid separator 2 and then returns to a return port 12.

(2) And in the auxiliary EVI circuit, after being throttled and depressurized by the sixth electromagnetic valve 116 and the second electronic expansion valve 102, the refrigerant on the side of the economizer 9 and the refrigerant on the main circuit side are subjected to heat exchange, vaporization and temperature rise, then the refrigerant is changed into medium-temperature medium-pressure steam, returns to the EVI injection port 13 of the compressor 1, and enters the compressor to finish cycles.

The mode is started preferentially under the refrigeration working condition until the heat storage water tank reaches the set temperature (45 ℃), and the mode is switched to other modes.

(nine) solar domestic hot water supply mode

In this mode, the refrigerant circuit is fully closed.

As shown in fig. 20, when the temperature of the circulating water in the tank of the solar heat exchanger 6 is 5 ℃ lower than the temperature of the solar heat collecting vacuum tube 16, the solar circulating pump 161 starts circulating heating, when the temperature of the solar heat exchanger 6 reaches a set temperature such as 60 ℃, the th water replenishing electromagnetic valve 162 and the second water replenishing electromagnetic valve 163 are simultaneously opened, hot water is fed into the hot water storage tank 15 through the water inlet 15a until the water level of the hot water storage tank 15 reaches a set height, water is stopped being supplied to the equipment requiring domestic hot water when the water outlet 15 is opened, and when the temperature of the solar heat exchanger 6 is lower than 45 ℃, the th water replenishing electromagnetic valve 162 and the second water replenishing electromagnetic valve 163 are simultaneously closed, and water supply to the hot water storage tank 15 is stopped.

(Ten) refrigeration defrosting mode

As shown in FIG. 21, in this mode, the a-B ends and the c-d ends of the fourth valve 131 of are communicated, the e-h ends and the f-g ends of the second four valve 132 are communicated, the j-i ends and the l-k ends of the third four valve 133 are communicated, the spray pump 44 and the fan 41 are closed, the spray 43 is in a spray stop state, the second functional solenoid valve B is closed, the functional solenoid valve A is opened, the compressor 1 is in a working state, the seventh solenoid valve 117 is opened or closed at a set temperature, such as when the temperature of the compressor is higher than a certain set value (e.g., 95 ℃).

The liquid injection enthalpy-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant sprayed from the outflow port 11 of the compressor 1 enters the d end of the four-way valve 131, enters the e end of the second four-way valve 132 after the c end of the refrigerant exits, enters the l end of the third four-way valve 133 after the h end of the refrigerant exits, and exits the k end of the refrigerant after entering the evaporative cooling heat exchanger 45 and the air cooling heat exchanger 42, and enters the liquid storage tank 7 and the drying filter 8 through the functional electromagnetic valve A, the electromagnetic valve 111 and the one-way valve 120, and then is divided into two paths:

(1) in the main loop, after the economizer 9 exchanges heat with refrigerant on the other side of the economizer in the secondary loop to be condensed and cooled in , the refrigerant is cooled to be low-temperature low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, the low-temperature low-pressure refrigerant liquid refrigerant is discharged through a fourth one-way valve 123 and then enters the indoor heat exchanger 5 through a second electromagnetic valve 112, the liquid refrigerant exchanges heat with indoor low-temperature circulating water flowing through the indoor heat exchanger 5, the refrigerant is vaporized and heated to absorb indoor heat, and the indoor circulating water with higher temperature is cooled to provide a heat source for the compressor so as to achieve the defrosting purpose.

(2) And in the auxiliary EVI loop, after the pressure of the second electronic expansion valve 102 is reduced by throttling through a sixth electromagnetic valve 116, the refrigerant is subjected to heat exchange and preliminary vaporization and temperature rise through another side of the economizer 9 and a refrigerant at the main loop side, the refrigerant is changed into medium-temperature medium-pressure steam, the medium-temperature medium-pressure steam returns to the EVI injection port 13 of the compressor 1, and the medium-temperature medium-pressure steam enters the compressor to finish cycles.

The mode is an emergency defrosting mode: this mode is activated when the hot water defrost mode, the solar defrost mode, or the conditions are not satisfied. The frequency of using the mode is reduced to the maximum extent, and the influence on the indoor temperature caused by defrosting is avoided.

(ten ) solar defrosting mode

As shown in FIG. 22, in this mode, the a-B ends and the c-d ends of the fourth valve 131 of are communicated, the e-h ends and the f-g ends of the second four valve 132 are communicated, the j-i ends and the l-k ends of the third four valve 133 are communicated, the spray pump 44 is closed, the fan 41 is closed, the spray device 43 is in a spray stop state, the second functional solenoid valve B is closed, the functional solenoid valve A is opened, the compressor 1 is in a working state, the seventh solenoid valve 117 is opened or closed at a set temperature, and is opened (for example, 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the th, sixth, ninth, and

fifth solenoid valves

111, 116, 119, and 115 are open, and the second, third, fourth, and

eighth solenoid valves

112, 113, 114, and 118 are closed.

The steam-injection increase culvert compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from an outflow port 11 of the compressor 1, enters a d end inlet and a c end outlet of a four-way valve 131, enters an e end inlet and an h end outlet of a second four-way valve 132, enters an l end inlet and a k end outlet of a third four-way valve 133, enters an evaporative cooling heat exchanger 45 and an air cooling heat exchanger 42, a spray pump 44 is closed, a fan 41 stops starting, a spray device 43 stops spraying, a second functional electromagnetic valve B is closed, a functional electromagnetic valve A is opened, high-temperature and high-pressure refrigerant steam enters the evaporative cooling heat exchanger 45 and the air cooling heat exchanger 42 to absorb surface heat so as to achieve the purpose of defrosting, at the moment, the high-temperature and high-pressure refrigerant steam is changed into high-temperature and high-pressure liquid refrigerant, and the high-temperature and high:

(1) in the main loop, refrigerant enters steps of condensation and temperature reduction through heat exchange between the economizer 9 and refrigerant at the other side of the economizer in the secondary loop, is reduced to low-temperature and low-pressure refrigerant liquid refrigerant through the electronic expansion valve 101, enters the solar heat exchanger 6 after passing through the fourth one-way valve 123, the ninth electromagnetic valve 119 and the fifth electromagnetic valve 115, is evaporated, evaporated and absorbed heat in the solar heat exchanger 6, and is evaporated and heated to low-temperature and low-pressure refrigerant steam after absorbing solar heat, and the low-temperature and low-pressure refrigerant steam passes through the inlet end and the outlet end of the third four-way valve 133, returns to the return port 12 of the compressor 1 through the gas-liquid separator 2, and finishes the main refrigerant cycle and enters the lower cycle.

The mode is a second priority defrosting mode, and is started when the water temperature sensor 63 arranged in the solar heat exchanger 6 senses that the water temperature in the water tank is higher than a certain set value (such as 15 ℃) in the defrosting mode, and is switched into a refrigeration defrosting mode when the water temperature is lower than a certain set value (such as 5 ℃).

(twelve) Hot Water defrosting mode (external heat source defrosting mode)

As shown in FIG. 23, in this mode, the a-B ends and the c-d ends of the fourth valve 131 of are communicated, the e-h ends and the f-g ends of the second four valve 132 are communicated, the j-i ends and the l-k ends of the third four valve 133 are communicated, the spray pump 44 is closed, the fan 41 is closed, the spray device 43 is in a spray stop state, the second functional solenoid valve B is closed, the functional solenoid valve A is opened, the compressor 1 is in a working state, the seventh solenoid valve 117 is opened or closed at a set temperature, and is opened (e.g., 95 ℃) when the temperature of the compressor is higher than a certain set value.

In each refrigerant circuit, the -th solenoid valve 111, the fourth solenoid valve 114, and the sixth solenoid valve 116 are open, and the second solenoid valve 112, the third solenoid valve 113, the fifth solenoid valve 115, the eighth solenoid valve 118, and the ninth solenoid valve 119 are closed.

The steam-injection culvert-increasing compressor 1 is electrified to work, high-temperature and high-pressure gaseous refrigerant is injected from the outflow port 11 of the compressor 1, enters the end d of the four-way valve 131, enters the end e of the second four-way valve 132 after the end c of the second four-way valve is discharged, enters the end e of the second four-way valve 132 and is discharged from the end h of the second four-way valve 133, enters the evaporative cooling heat exchanger 45 and the air cooling heat exchanger 42 after the end l and the end k of the third four-way valve 133, is sprayed, the spray pump 44 is turned off, the fan 41 is stopped to be started, the spray 43 is stopped to spray, the second functional electromagnetic valve B is turned off, the functional electromagnetic valve A is turned on, high-temperature and high-pressure refrigerant steam enters the evaporative cooling heat exchanger 45 and the air cooling heat exchanger 42 to absorb surface heat to achieve the defrosting purpose:

(1) in the main loop, refrigerant enters for condensation and temperature reduction through heat exchange between the economizer 9 and refrigerant on the other side of the economizer in the secondary loop, is reduced to low-temperature and low-pressure refrigerant liquid refrigerant through a electronic expansion valve 101, and enters the multifunctional heat exchanger 3 after passing through a fourth check valve 123, a fourth electromagnetic valve 114 and a fifth check valve 124, the low-temperature and low-pressure refrigerant liquid exchanges heat with hot water flowing into the heat storage water tank 15 or an external heat source through a water inlet 31, the refrigerant absorbs the heat of the hot water to be vaporized and heated to low-temperature and low-pressure refrigerant steam, the hot water flows back to the heat storage water tank 15 or the external heat source from a water outlet 32 after being reduced in temperature, the refrigerant steam enters and exits through an end a and an end b of a four-way valve 131, passes through a gas-liquid separator 2 and then returns to a.

(2) And in the auxiliary EVI circuit, after throttling and pressure reduction are carried out through the sixth electromagnetic valve 116 and the second electronic expansion valve 102, the refrigerant on the side of the economizer 9 and the refrigerant on the side are subjected to heat exchange, vaporization and temperature rise, the refrigerant is changed into medium-temperature medium-pressure steam, the medium-temperature medium-pressure steam returns to the EVI injection port 13 of the compressor 1, and the medium-temperature medium-pressure steam enters the compressor to finish cycles.

The mode is priority defrosting mode, which is preferably started after the unit receives defrosting signal, and is switched to the second defrosting mode, i.e. solar defrosting mode, when the temperature of the water in the heat storage water tank is lower than deg.C (such as 5 deg.C).

In the second embodiment, on the basis of the structure of the second embodiment , the evaporative cold space energy dual-source heat pump heat recovery unit is characterized in that the function module 10 is replaced by a second function module 10a, namely, the structure of the second embodiment is shown in fig. 24, the second function module is provided with a U, V interface, the second function module 10a comprises a liquid storage tank 7, a drying filter 8 and a electronic expansion valve 101, a U interface is sequentially connected with the liquid storage tank 7, the drying filter 8, the electronic expansion valve 101 and a V interface, when the function module 10 is replaced by the second function module 10a, the compressor is a common compressor which is only provided with a flow outlet 111 and a return outlet 112, and the evaporative cold space energy dual-source heat pump heat recovery unit can only be used for cooling and heating in a non-cold environment (above-10 ℃).

In a third embodiment, on the basis of the structure of the third embodiment , the evaporative cold space energy dual-source heat pump heat recovery unit is a structure in which the indoor heat exchanger 5 is replaced by a multi-connected indoor unit 5a, as shown in fig. 25, the multi-connected indoor unit 5a includes a refrigerant fin heat exchanger and an indoor fan, and the indoor fan causes air to flow through the surface of the refrigerant fin heat exchanger, so as to cool and heat the units.

In a fourth embodiment, on the basis of the structure of the embodiment , types of evaporative cold space energy dual-source heat pump heat recovery units are configured such that the function module 10 is replaced with a second function module 10a, and the indoor-side heat exchanger 5 is replaced with a multi-connected indoor unit 5a, which is a structure implementing the fourth embodiment, as shown in fig. 26.

In the fifth embodiment, evaporative cooling space energy dual-source heat pump heat recovery units are characterized in that on the basis of the structure of the embodiment , the outdoor heat exchange part 4 is replaced by a second outdoor heat exchange part 4a, as shown in fig. 27 and 31, the second outdoor heat exchange part 4a is provided with a R, S interface, the second outdoor heat exchange part 4a comprises a fan 41, an air cooling heat exchanger 42, an evaporative cooling heat exchanger 45, a sprayer 43, a spray pump 44, a water collecting tank 46, a third functional solenoid valve C and a fourth functional solenoid valve D, an inlet end C1 of the third functional solenoid valve C and an inlet end D1 of the fourth functional solenoid valve D are connected in parallel and then connected with an R interface of the second outdoor heat exchange part 4a, an outlet end C2 of the third functional solenoid valve C is connected with an inlet end 421 of the air cooling heat exchanger 42, an outlet end D2 of the fourth functional solenoid valve D is connected with an inlet end 451 of the evaporative cooling heat exchanger 45, and an outlet end 422 of the air cooling heat exchanger 42 and an outlet end 452 of the evaporative cooling heat exchanger 45 are connected in parallel and then connected with an outdoor interface S of.

In a sixth embodiment, evaporative cooling space energy dual-source heat pump heat recovery units are characterized in that on the basis of the structure of the embodiment , the outdoor heat exchange portion 4 is replaced by a third chamber outer heat exchange portion 4b, as shown in fig. 28 and 32, the third chamber outer heat exchange portion 4b is provided with a R, S interface, the third chamber outer heat exchange portion 4b comprises a fan 41, an air-cooled heat exchanger 42, an evaporative cooling heat exchanger 45, a sprayer 43, a spray pump 44, a water collection tank 46, a fifth function electromagnetic valve E and a sixth function electromagnetic valve F, an R interface of the third chamber outer heat exchange portion 4b is connected with an inlet end 421 of the air-cooled heat exchanger 42, an outlet end 422 of the air-cooled heat exchanger 42 is connected with an inlet end 451 of the evaporative cooling heat exchanger 45, an outlet end 452 of the evaporative cooling heat exchanger 45 is connected with an inlet end F1 of the sixth function electromagnetic valve F, an outlet end 422 of the air-cooled heat exchanger 42 is further connected with an inlet end E1 of the fifth function electromagnetic valve E, and an outlet end E2 of the fifth function electromagnetic valve E is connected with an outlet end F2 of.

Although the embodiments of the present invention have been described in the specification, these embodiments are only for the purpose of presentation and should not be construed as limiting the scope of the present invention. Various omissions, substitutions, and changes may be made without departing from the spirit and scope of the invention.

Claims

1, kinds of evaporation cold space can double source heat pump heat recovery unit, its characterized in that includes:

2. The evaporative cold space energy dual-source heat pump heat recovery unit as claimed in claim 1, wherein the thermal storage water tank is replaced by an external heat source, the end of the external heat source is connected with the water inlet of the multifunctional heat exchanger, and the other end of the external heat source is connected with the water outlet of the multifunctional heat exchanger.

3. The evaporative cold space energy dual-source heat pump heat recovery unit as claimed in claim 1 or 2, wherein the functional module comprises a liquid storage tank, a drying filter, an th electronic expansion valve, an economizer, a second electronic expansion valve and a sixth electromagnetic valve, a U interface of the functional module is sequentially connected with the liquid storage tank, the drying filter, the economizer, a th electronic expansion valve and a V interface, the drying filter is sequentially connected with the sixth electromagnetic valve, the second electronic expansion valve, the economizer and a Q interface, and the drying filter is further connected with a P interface.

4. The evaporative cold space energy double-source heat pump heat recovery unit as claimed in claim 1 or 2, wherein the outdoor heat exchange portion comprises a fan, an air-cooled heat exchanger, an evaporative cold heat exchanger, a sprayer, a spray pump, a water collection tank, a function solenoid valve A and a second function solenoid valve B, the spray pump is arranged in the water collection tank, the fan enables air to flow through the surface of the air-cooled heat exchanger, the sprayer sprays cooling water on the surface of the evaporative cold heat exchanger, an R interface of the outdoor heat exchange portion is sequentially connected with an inlet end of the evaporative cold heat exchanger, an outlet end of the evaporative cold heat exchanger, an inlet end of the air-cooled heat exchanger and an outlet end of the air-cooled heat exchanger, an outlet end of the evaporative cold heat exchanger is further connected with an inlet end of the second function solenoid valve B, an outlet end of the air-cooled heat exchanger is further connected with an inlet end of the function solenoid valve A, and an outlet end of the second function solenoid valve B and an outlet end of the .

5. The evaporative cold space energy dual-source heat pump heat recovery unit as claimed in claim 1 or 2, wherein the indoor heat exchanger is replaced by a multi-connected indoor unit, the multi-connected indoor unit comprises a refrigerant fin heat exchanger and an indoor fan, and the indoor fan enables air to flow through the surface of the refrigerant fin heat exchanger for refrigerating and heating of the unit.

6. The evaporative cold space energy dual-source heat pump heat recovery unit as claimed in claim 3, wherein the function module is replaceable with a second function module, the second function module has U, V interface, the second function module comprises a liquid storage tank, a dry filter and a electronic expansion valve, and a U interface is connected with the liquid storage tank, the dry filter, a electronic expansion valve and a V interface in sequence.

7. The evaporative cold space energy dual-source heat pump heat recovery unit as claimed in claim 4, wherein the outdoor heat exchange section is replaced with a second outdoor heat exchange section, the second outdoor heat exchange section having an R, S interface; the second outdoor heat exchanging part comprises a fan, an air cooling heat exchanger, an evaporative cooling heat exchanger, a sprayer, a spray pump, a water collecting tank, a third functional electromagnetic valve C and a fourth functional electromagnetic valve D; the inlet end of the third functional electromagnetic valve C and the inlet end of the fourth functional electromagnetic valve D are connected in parallel and then are connected with the R interface of the second outdoor side heat exchanging part, the outlet end of the third functional electromagnetic valve C is connected with the inlet end of the air cooling heat exchanger, the outlet end of the fourth functional electromagnetic valve D is connected with the inlet end of the evaporative cooling heat exchanger, and the outlet end of the air cooling heat exchanger and the outlet end of the evaporative cooling heat exchanger are connected in parallel and then are connected with the S interface of the second outdoor side heat exchanging part.

8. The evaporative cold space energy dual source heat pump heat recovery unit as defined in claim 4 wherein said outdoor heat exchange section is replaced with a third outdoor heat exchange section having an R, S interface; the third chamber outer side heat exchange part comprises a fan, an air cooling heat exchanger, an evaporative cooling heat exchanger, a sprayer, a spray pump, a water collecting tank, a fifth function electromagnetic valve E and a sixth function electromagnetic valve F; the R interface of the third chamber outer side heat exchange part is connected with the inlet end of the air-cooled heat exchanger, the outlet end of the air-cooled heat exchanger is connected with the inlet end of the evaporative cooling heat exchanger, the outlet end of the evaporative cooling heat exchanger is connected with the inlet end of the sixth functional electromagnetic valve, the outlet end of the air-cooled heat exchanger is also connected with the inlet end of the fifth functional electromagnetic valve E, and the outlet end of the fifth functional electromagnetic valve E is connected with the outlet end of the sixth functional electromagnetic valve in parallel and then is connected with the S interface of the third chamber outer side heat.