CN115264983A

CN115264983A - Double-effect injection type heat pump circulating system with special-shaped continuous-injection structure injector

Info

Publication number: CN115264983A
Application number: CN202210899649.6A
Authority: CN
Inventors: 张承虎; 林子琛; 朱添奇; 杨海滨
Original assignee: Harbin Institute of Technology
Current assignee: Harbin Institute of Technology
Priority date: 2022-07-28
Filing date: 2022-07-28
Publication date: 2022-11-01
Anticipated expiration: 2042-07-28
Also published as: CN115264983B

Abstract

The invention provides a double-effect injection type heat pump circulating system with an abnormal-shaped continuous-injection structure injector, and belongs to the technical field of refrigeration and heat pump systems. The system aims to solve the problems that in a traditional series injection type refrigeration/heat pump system, a working medium generates irreversible loss and the overall efficiency of the system is reduced through two complete decompression acceleration, mixing and pressurization deceleration processes. The boiling device is connected with a working fluid inlet of the special-shaped continuous spraying structure ejector, an outlet of the special-shaped continuous spraying structure ejector is sequentially connected with inlets of the condenser and the liquid collector, an outlet of the liquid collector is respectively connected with the first evaporator, the second evaporator and the boiling device, and the first evaporator and the second evaporator are respectively connected with the first injection fluid inlet and the second injection fluid inlet of the special-shaped continuous spraying structure ejector. Compared with the traditional series type ejector heat pump system, the double-effect injection type heat pump circulating system disclosed by the invention has the advantages that the continuous injection process is realized, the system structure is simplified, and the irreversible loss of the system is reduced.

Description

Double-effect injection type heat pump circulating system with special-shaped continuous-injection structure injector

Technical Field

The invention relates to the technical field of refrigeration and heat pump equipment, in particular to a double-effect injection type heat pump circulating system with an abnormal-shaped continuous injection structure injector.

Background

The jet refrigeration/heat pump circulation system is a refrigeration/heat pump circulation system which is driven by heat energy and does not contain a mechanical compression part, and can generate high-pressure working fluid under the driving of a high-temperature heat source, so that low-pressure fluid generated under the action of a low-temperature heat source is jetted in an ejector, is condensed to release heat after being lifted to intermediate pressure, and the heat of the low-level heat source is extracted by adopting the flow, so that the function of the refrigeration/heat pump is realized.

Two ejectors are connected in series, the ejection quality is effectively improved, the application range of the ejectors is expanded, and the traditional series injection type refrigeration/heat pump cycle mainly comprises a boiler, a condenser, an evaporator, the ejectors, a liquid collector and associated pipeline equipment. Under the action of high-temperature primary water, the boiler heats and boils the refrigerant therein to generate high-temperature and high-pressure working steam. The working steam enters the first ejector through the working steam pipeline to inject low-pressure steam, the mixed steam enters the second ejector after the pressure increasing and speed reducing of the pressure expanding section, the pressure reducing and speed increasing are carried out, the low-pressure steam is injected again, the mixed steam is mixed with the low-pressure steam and then completes the injection process through the pressure increasing and speed reducing of the pressure expanding section, the mixed steam enters the condenser through the mixed steam pipeline to be condensed to release heat, and the working steam is changed into liquid.

However, in the above-mentioned conventional series injection type refrigeration/heat pump system, the working medium undergoes two complete decompression acceleration, mixing, pressurization deceleration processes, wherein the pressurization deceleration process of the diffusion section of the first stage of the ejector, the decompression acceleration process of the second stage of the ejector, and the flow through the connecting pipeline between the two ejectors may generate a certain irreversible loss, which increases the complexity of the system structure, resulting in a decrease in the overall efficiency of the system.

Disclosure of Invention

The technical problem to be solved by the invention is as follows:

the system aims to solve the problems that in a traditional series injection type refrigeration/heat pump system, working media generate irreversible loss and the overall efficiency of the system is reduced through two complete decompression acceleration, mixing and pressurization deceleration processes.

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

the invention provides a double-effect injection type heat pump circulating system with a special-shaped continuous-injection structure injector, which comprises a boiling device, a booster pump, the special-shaped continuous-injection structure injector, a first evaporator, a first throttle valve, a second evaporator, a second throttle valve, a condenser, a liquid collector, a first conveying pipeline, a second conveying pipeline, a third conveying pipeline, a fourth conveying pipeline, a fifth conveying pipeline, a sixth conveying pipeline, a seventh conveying pipeline, an eighth conveying pipeline, a ninth conveying pipeline, a heat source pipeline, a first cold source pipeline and a second cold source pipeline, wherein the boiling device is arranged on the boiling device;

a refrigerant outlet of the boiling device is connected with an inlet of a first conveying pipeline, and an outlet of the first conveying pipeline is connected with a working fluid inlet of the special-shaped continuous-spraying structure ejector;

the outlet of the special-shaped continuous spraying structure ejector is connected with the inlet of an eighth conveying pipeline, the outlet of the eighth conveying pipeline is connected with the refrigerant inlet of a condenser, the refrigerant outlet of the condenser is connected with the inlet of a ninth conveying pipeline, the outlet of the ninth conveying pipeline is connected with the inlet of a liquid collector, the outlet of the liquid collector is connected with the inlet of a seventh conveying pipeline, the outlet of the seventh conveying pipeline is respectively connected with the inlets of a fourth conveying pipeline and a sixth conveying pipeline, the outlet of the fourth conveying pipeline is connected with the refrigerant inlet of a first evaporator, a first throttling valve is arranged on the fourth conveying pipeline, and the refrigerant outlet of the first evaporator is connected with the inlet of a third conveying pipeline; an outlet of the sixth conveying pipeline is connected with a refrigerant inlet of the second evaporator, a second throttling valve is arranged on the sixth conveying pipeline, a refrigerant outlet of the second evaporator is connected with an inlet of the fifth conveying pipeline, an outlet of the third conveying pipeline is connected with a first injection fluid inlet of the special-shaped continuous-spraying structure ejector, and an outlet of the fifth conveying pipeline is connected with a second injection fluid inlet of the special-shaped continuous-spraying structure ejector;

a second outlet of the liquid collector is connected with an inlet of a second conveying pipeline, a booster pump is arranged on the second conveying pipeline, and an outlet of the second conveying pipeline is connected with a refrigerant inlet of the boiler;

the heat source pipeline flows through the boiling device, and the first cold source pipeline flows through the condenser;

the first evaporator and the second evaporator are connected in parallel through a second cold source pipeline, the second cold source pipeline is divided into two paths from the incoming flow direction, and the two paths of cold source pipeline are converged into one path and discharged after respectively flowing through the first evaporator and the second evaporator;

the special-shaped continuous-spraying structure ejector comprises a first spray pipe, a first suction chamber, a first injection section, a first mixing section, a second spray pipe, a second suction chamber, a second injection section, a second mixing section, a diffusion section, a first injection fluid inlet and a second injection fluid inlet;

the inlet end of the first spray pipe is a working fluid inlet, the first suction chamber comprises a first injection fluid inlet and a first injection section inlet, the first injection section is an arc transition of the outer wall of the first spray pipe, a cavity is defined between the horizontal part of the first spray pipe and the arc transition of the inlet of the first mixing section, the outlet end of the first spray pipe is connected with the outlet end of the first injection section after being converged with the outlet end of the first mixing section, the first injection fluid is converged with the working fluid after passing through the first injection section and then enters the first mixing section, the outlet end of the first mixing section is connected with the inlet end of the second spray pipe, the second suction chamber comprises a second injection fluid inlet and an inlet of the second injection section, the second injection section is an arc transition of the outer wall of the second spray pipe, a cavity is defined between the horizontal part of the second spray pipe and the arc transition of the inlet of the second mixing section, the second injection fluid is converged with the working fluid after passing through the second injection section and then enters the second mixing section, and the outlet end of the second mixing section is connected with the diffusion section;

the first nozzle is a first Laval nozzle which comprises a first nozzle front horizontal section, a first nozzle contraction section, a first nozzle expansion section and a first nozzle rear horizontal section;

when the speed of the working medium mixed by the first mixing section is lower than the local sound speed, the second spray pipe is a second Laval spray pipe, and the second Laval spray pipe comprises a second spray pipe contraction section, a second spray pipe expansion section and a second spray pipe rear horizontal section; when the speed of the working medium mixed by the first mixing section is higher than the local sound speed, the second spray pipe is an expansion spray pipe with the diameter gradually increased, and the expansion spray pipe comprises an expansion spray pipe expansion section and an expansion spray pipe horizontal section;

the outlet end of the first spray pipe is flush with the outlet end of the first ejector section, and the outlet end of the second spray pipe is flush with the outlet end of the second ejector section;

the section of the arc transition of one side of the first injection section and one side of the second injection section, which are far away from the spray pipe, is 1/4 arc transition;

the length of the front horizontal section of the first spray pipe is 4 times greater than the radius of the inlet section of the first spray pipe;

when the first spray pipe is a first Laval spray pipe and the second spray pipe is a second Laval spray pipe, the linear type of the first spray pipe and the second spray pipe, namely the section radius d, is determined by the following formula:

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

{d＝d₁₁,0≤x₁₁≤L₁₁；d＝d₁₂,L₁₁≤x₁₂≤L₁₁+L₁₂；d＝d₁₃,L₁₁+L₁₂≤x₁₃≤L₁₁+1.07×L₁₂}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1t-a first or second laval nozzle throat section radius;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or second laval nozzle flare length;

x is the distance from the cross section at x to the inlet cross section of the first or second laval nozzle;

when the second nozzle is a divergent nozzle, the linear form of the divergent nozzle, i.e. the section radius d, is determined by the following formula:

{x＝x₂₁；x＝x₂₂}

{d＝d₂₁,0≤x₂₁≤L₂₂；d＝d₂₂,L₂₂≤x₂₂≤1.07L₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-expanding the nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle extension section;

x is the distance from the section at the x to the inlet section of the expansion nozzle;

the line type of the first injection section and the second injection section is determined by the following method and formula,

the known quantity is the annular area S of the inlet of the first injection section or the second injection section₁The annular area S of the throat part of the first injection section or the second injection section₂The radius R' of a circle formed by the first ejector section outlet and the first spray pipe outlet or the second ejector section outlet and the second spray pipe outlet is R and L as unknown quantity₁、L₂、L₃、L₄The following formula is needed for the solution:

L₂＝R+R'

L₁the distance between the inlet end of the first injection section close to one side of the spray pipe and the central axis of the first spray pipe or the distance between the inlet end of the second injection section and the central axis of the second spray pipe;

L₂the distance between the inlet end of the first injection section far away from one side of the spray pipe and the central axis of the first spray pipe or the distance between the inlet end of the second injection section and the central axis of the second spray pipe;

L₃the distance between the end point of the throat part of the first injection section, which is close to one side of the spray pipe, and the central axis of the first spray pipe or the distance between the throat part of the second injection section and the central axis of the second spray pipe;

L₄the distance between the end point of the throat part of the first injection section, which is far away from one side of the spray pipe, and the central axis of the first spray pipe or the distance between the throat part of the second injection section and the central axis of the second spray pipe;

r' -the distance between the outlet end of the arc transition of the first injection section and the central axis of the first spray pipe or the distance between the outlet end of the arc transition of the second injection section and the central axis of the second spray pipe;

L₆the length of the inlet end of the first ejector section or the length of the inlet end of the second ejector section;

L₇the length of the throat of the first ejector section or the length of the throat of the second ejector section;

r is the radius of a 1/4 circular arc curve on one side, far away from the spray pipe, of the first injection section or the second injection section;

the outlet end tangent line of 1/4 circular arc transition is connected with the first injection section or the second injection section side wall close to the spray pipe, the intersection point is a point D, the curve from the inlet end of the first injection section or the second injection section side wall close to the spray pipe to the point D is symmetrical with the perpendicular line of the 1/4 circular arc transition about the middle point of the throat, the plane where the throat is located on the angular bisector of the central angle corresponding to the 1/4 circular arc, the D point is connected with the tail end of the first spray pipe expansion section or the tail end of the second spray pipe expansion section through a function curve, and the function curve is determined by the following method and formula:

y＝a+bt+ct²+et³

two ends of the function curve are respectively and smoothly connected with the point D and the tail end of the first spray pipe expansion section or the point D and the tail end of the second spray pipe expansion section, so that the positions of end points on two sides of the function curve and the first derivative of the end points are known to form four equations, and four undetermined coefficients of a, b, c and e are calculated;

length L of the first mixing section₅The design is as follows:

when the second lance is a second laval lance,

L₅＝13.23×R″′

when the second nozzle is an expansion nozzle,

L₅＝5.81×R″′

L₅-the length of the first mixing section;

r' -the radius of the first mixing section;

length L of the second mixing section₈The design is as follows:

L₈＝1.51×R″

L₈-the length of the second mixing section;

r' -the radius of the second mixing section;

the linear design of the diffuser section is determined by the following formula:

L₉＝c×R″

s is the horizontal distance from any one position of the diffusion section to the inlet section of the diffusion section;

r is the radius of any section of the diffusion section;

r' -the radius of the second mixing section;

L₉-the length of the diffuser section;

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。

the refrigerant outlet of the boiling device is connected with the inlet of a first conveying pipeline, and the outlet of the first conveying pipeline is connected with the working fluid inlet of the special-shaped continuous spraying structure ejector;

the outlet of the liquid collector is connected with the inlet of a second conveying pipeline, a booster pump is arranged on the second conveying pipeline, and the outlet of the second conveying pipeline is connected with the refrigerant inlet of the boiler;

the first evaporator and the second evaporator are connected in series through a second cold source pipeline, and the second cold source pipeline sequentially flows through the second evaporator and the first evaporator;

the special-shaped continuous jet structure ejector comprises a first spray pipe, a first suction chamber, a first jet section, a first mixing section, a second spray pipe, a second suction chamber, a second jet section, a second mixing section, a diffusion section, a first jet fluid inlet and a second jet fluid inlet;

the inlet end of the first spray pipe is a working fluid inlet, the first suction chamber comprises a first injection fluid inlet and a first injection section inlet, the first injection section is a cavity defined between an arc transition of the outer wall of the first spray pipe and an arc transition of the horizontal part of the first spray pipe and the inlet of the first mixing section, the outlet end of the first spray pipe is connected with the outlet end of the first injection section after being converged, the first injection fluid is used for entering the first mixing section after passing through the first injection section and converging with the working fluid, the outlet end of the first mixing section is connected with the inlet end of the second spray pipe, the second suction chamber comprises a second injection fluid inlet and a second injection section inlet, the second injection section is an arc transition of the outer wall of the second spray pipe, the cavity defined between the horizontal part of the second spray pipe and the arc transition of the inlet of the second mixing section is used for entering the second mixing section after passing through the second injection section, and the outlet end of the second mixing section is connected with the inlet end of the diffusion section;

the length of the front horizontal section 1-1 of the first spray pipe is 4 times greater than the radius of the inlet section of the first spray pipe 1;

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1t-a first or second laval nozzle throat section radius;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or second laval nozzle flare length;

{x＝x₂₁；x＝x₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-expanding the nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle extension section;

x-the distance from the section at the position of x to the section of the inlet of the expansion nozzle;

L₂＝R+R'

r' -the distance between the outlet end of the arc transition of the first injection section and the central axis of the first spray pipe or the distance between the outlet end of the second injection section and the central axis of the second spray pipe;

r is the radius of a 1/4 circular arc curve of one side, far away from the spray pipe, of the first injection section or the second injection section;

the tangent line of an outlet end of the 1/4 circular arc transition is connected with the side wall of the first injection section or the second injection section close to the spray pipe, the intersection point is a point D, a curve from the inlet end of the first injection section or the side wall of the second injection section close to the spray pipe to the point D is symmetrical to a perpendicular line of the 1/4 circular arc transition relative to the midpoint of the throat, the plane where the throat is located on an angle bisector of a central angle corresponding to the 1/4 circular arc, the D point is connected with the tail end of the expansion section of the first spray pipe or the tail end of the expansion section of the second spray pipe through a function curve, and the function curve is determined by the following method and formula:

y＝a+bt+ct²+et³

two ends of the function curve are respectively connected with the point D and the tail end of the first spray pipe expansion section in a smooth mode or the point D and the tail end of the second spray pipe expansion section in a smooth mode, therefore, the positions of end points on two sides of the function curve and the first derivative of the position are known, four equations are formed, and four undetermined coefficients of a, b, c and e are solved;

length L of the first mixing section₅The design is as follows:

when the second lance is a second laval lance,

L₅＝13.23×R″′

when the second nozzle is a divergent nozzle,

L₅＝5.81×R″′

L₅-the length of the first mixing section;

r' -the radius of the first mixing section;

length L of the second mixing section₈The design is as follows:

L₈＝1.51×R″

L₈-the length of the second mixing section;

r' -the radius of the second mixing section;

L₉＝c×R″

r is the radius of any section of the diffusion section;

r' -the radius of the second mixing section;

L₉-the length of the diffuser section;

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。

further, the system also comprises a common ejector, a heat exchanger, a third throttling valve, a tenth conveying pipeline, an eleventh conveying pipeline and a thirteenth conveying pipeline;

an outlet of the first conveying pipeline is connected with an inlet of the special-shaped continuous-spraying structure ejector and an inlet of the common ejector respectively, an outlet of the special-shaped continuous-spraying structure ejector and an outlet of the common ejector are converged and then connected with an inlet of the eighth conveying pipeline, an outlet of the ninth conveying pipeline is connected with an inlet of the liquid collector, an outlet of the liquid collector is connected with an inlet of the eleventh conveying pipeline and an inlet of the thirteenth conveying pipeline respectively, an outlet of the eleventh conveying pipeline is connected with a second inlet of the heat exchanger, a second outlet of the heat exchanger is connected with an inlet of the tenth conveying pipeline, the eleventh conveying pipeline is provided with a third throttle valve, an injection fluid inlet of the common ejector is connected with an outlet of the tenth conveying pipeline, an outlet of the thirteenth conveying pipeline is connected with a first inlet of the heat exchanger, and a first outlet of the heat exchanger is connected with an inlet of the seventh conveying pipeline.

The invention provides a double-effect injection type heat pump circulating system with a special-shaped continuous injection structure ejector, which comprises a boiling device, a booster pump, the special-shaped continuous injection structure ejector, a first evaporator, a first throttle valve, a condenser, a liquid collector, a first conveying pipeline, a second conveying pipeline, a third conveying pipeline, a fourth conveying pipeline, a seventh conveying pipeline, an eighth conveying pipeline, a ninth conveying pipeline, a heat source pipeline, a first cold source pipeline, a heat exchanger, a third throttle valve, a fourteenth conveying pipeline and a fifteenth conveying pipeline, wherein the boiling device is connected with the booster pump through a pipeline;

an outlet of the special-shaped continuous spraying structure ejector is connected with an inlet of an eighth conveying pipeline, an outlet of the eighth conveying pipeline is connected with a refrigerant inlet of a condenser, a refrigerant outlet of the condenser is connected with an inlet of a ninth conveying pipeline, an outlet of the ninth conveying pipeline is connected with an inlet of a liquid collector, an outlet of the liquid collector is respectively connected with an inlet of a fourteenth conveying pipeline, an inlet of a seventh conveying pipeline and an inlet of a second conveying pipeline, an outlet of the fourteenth conveying pipeline is connected with a second inlet of the heat exchanger, a third throttle valve is arranged on the fourteenth conveying pipeline, a second outlet of the heat exchanger is connected with an inlet of a fifteenth conveying pipeline, and an outlet of the fifteenth conveying pipeline is connected with a second injection fluid inlet of the special-shaped continuous spraying structure ejector;

an outlet of the seventh conveying pipeline is connected with a first inlet of the heat exchanger, a first outlet of the heat exchanger is connected with an inlet of a fourth conveying pipeline, an outlet of the fourth conveying pipeline is connected with a refrigerant inlet of the first evaporator, the fourth conveying pipeline is provided with a first throttle valve, a refrigerant outlet of the first evaporator is connected with an inlet of the third conveying pipeline, and an outlet of the third conveying pipeline is connected with a first injection fluid inlet of the special-shaped continuous injection structure injector;

a booster pump is arranged on the second conveying pipeline, and the outlet of the second conveying pipeline is connected with the refrigerant inlet of the boiler;

the special-shaped continuous spraying structure ejector comprises a first spray pipe, a first suction chamber, a first injection section, a first mixing section, a second spray pipe, a second suction chamber, a second injection section, a second mixing section, a diffusion section, a first injection fluid inlet and a second injection fluid inlet;

the length of the front horizontal section 1-1 of the first spray pipe is more than 4 times of the radius of the inlet section of the first spray pipe 1;

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1t-a first or second laval nozzle throat section radius;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or second laval nozzle flare length;

{x＝x₂₁；x＝x₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-expanding the nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle extension section;

L₂＝R+R'

y＝a+bt+ct²+et³

length L of the first mixing section₅The design is as follows:

when the second lance is a second laval lance,

L₅＝13.23×R″′

when the second nozzle expands the nozzle,

L₅＝5.81×R″′

L₅-the length of the first mixing section;

r' -the radius of the first mixing section;

length L of the second mixing section₈The design is as follows:

L₈＝1.51×R″

L₈-the length of the second mixing section;

r' -the radius of the second mixing section;

L₉＝c×R″

r is the radius of any section of the diffusion section;

r' -the radius of the second mixing section;

L₉-the length of the diffuser section;

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。

compared with the prior art, the invention has the beneficial effects that:

the invention provides a double-effect jet type heat pump circulating system with a special-shaped continuous jet structure ejector, wherein a boiling device is connected with a working fluid inlet of the special-shaped continuous jet structure ejector, the special-shaped continuous jet structure ejector is sequentially connected with a condenser and an inlet of a liquid collector, an outlet of the liquid collector is respectively connected with a first evaporator, a second evaporator and the boiling device, and the first evaporator and the second evaporator are respectively connected with a first injection fluid inlet and a second injection fluid inlet of the special-shaped continuous jet structure ejector.

The special-shaped ejector integrates the two ejectors connected in series, a diffusion section of the first ejector and a connecting pipeline of the two ejectors are omitted, the structure of the ejectors connected in series is simplified, and the distance of fluid conveying is reduced.

The different ejector reduces the irreversible loss of three parts of the traditional series ejector, wherein the first part is the irreversible loss of a conveying pipeline connecting two ejectors, the second part is the irreversible loss of a fluid in a process of decelerating and pressurizing through a diffusion section part of the first ejector, and the third part is the irreversible loss of a fluid in a process of accelerating and depressurizing through a nozzle part of the second ejector. Compared with common series-connected ejectors, the ejector device effectively improves the ejection coefficient and the operation effect.

The invention provides a novel design method of a linear type spray pipe, a linear type ejection section, the sectional area and the length of a first mixing section, the sectional area and the length of a second mixing section and a linear type diffusion section. The linear design of the spray pipe enables the working fluid to have more uniform speed, and reduces irreversible loss during mixing.

Compared with the traditional serial ejector heat pump system, the double-effect injection type heat pump circulating system of the special-shaped continuous-injection structure ejector based on the continuous-injection structure is provided with the two evaporators and the two injection fluid inlets, so that the continuous injection process is realized, the system structure is simplified, and the total irreversible loss of the system is reduced.

Drawings

FIG. 1 is a schematic structural diagram of a first dual effect ejector heat pump cycle system according to an embodiment of the present invention;

FIG. 2 is a schematic structural diagram of a second dual effect ejector heat pump cycle system according to an embodiment of the present invention;

FIG. 3 is a third schematic structural diagram of a dual effect ejector heat pump cycle system in an embodiment of the present invention;

FIG. 4 is a schematic structural diagram of a dual effect ejector heat pump cycle system according to an embodiment of the present invention;

FIG. 5 is a schematic structural diagram of a dual effect ejector heat pump cycle system according to an embodiment of the present invention;

FIG. 6 is a sixth schematic structural view of a dual effect ejector heat pump cycle system in an embodiment of the present invention;

FIG. 7 is a first schematic structural diagram of an injector with a special-shaped continuous spraying structure according to an embodiment of the present invention;

FIG. 8 is a second schematic structural diagram of an injector with a special-shaped continuous spraying structure according to an embodiment of the present invention;

FIG. 9 is a third schematic structural diagram of an injector with a special-shaped continuous spraying structure in the embodiment of the invention;

fig. 10 is an enlarged view of a portion a in fig. 9.

Description of reference numerals:

1. a first nozzle; 2. a first suction chamber; 3. a first injection section; 4. a first mixing section; 5. a second nozzle; 6. a second suction chamber; 7. a second injection section; 8. a second mixing section; 9. a diffuser section; 10. a working fluid inlet; 11. a first motive fluid inlet; 12. a second motive fluid inlet; 1-1, a front horizontal section of a first spray pipe; 1-2, a first nozzle contraction section; 1-3, a first nozzle expansion section; 1-4, a rear horizontal section of the first spray pipe; 5-2, a second nozzle contraction section; 5-3, a second nozzle expansion section; 5-4, a rear horizontal section of the second spray pipe; 21. a boiler; 22. a booster pump; 23. an injector with a special-shaped continuous spraying structure; 24. a first evaporator; 25. a first throttle valve; 26. a second evaporator; 27. a second throttle valve; 28. a condenser; 29. a liquid collector; 30. a first delivery line; 31. a second delivery line; 32. a third delivery line; 33. a fourth delivery line; 34. a fifth delivery line; 35. a delivery pipe; 36. a seventh delivery line; 37. an eighth delivery line; 38. a ninth delivery line; 39. a heat source pipeline; 40. a first cold source pipeline; 41. a second cold source pipeline; 51. a common ejector; 52. a heat exchanger; 53. a third throttle valve; 54. a tenth transfer line; 55. an eleventh transfer line; 57. a thirteenth transfer line; 58. a fourteenth transfer line; 59. a fifteenth delivery conduit; 61. and a third cold source pipeline.

Detailed Description

In the description of the present invention, it should be noted that terms such as "upper", "lower", "front", "rear", "left", "right", and the like in the embodiments indicate terms of orientation, and are used only for simplifying the positional relationship based on the drawings of the specification, and do not represent that the elements, devices, and the like indicated in the description must operate according to the specific orientation and the defined operation, method, and configuration, and such terms are not to be construed as limiting the present invention.

In the description of the present invention, it should be noted that the terms "first", "second" and "third" mentioned in the embodiments of the present invention are only used for descriptive purposes and are not to be construed as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Thus, features defined as "first", "second", and "third" may explicitly or implicitly include one or more of the features.

In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.

The first specific embodiment is as follows: referring to fig. 1, the present invention provides a dual-effect injection type heat pump cycle system with a special-shaped continuous injection structure injector, including a boiler 21, a booster pump 22, a special-shaped continuous injection structure injector 23, a first evaporator 24, a first throttle valve 25, a second evaporator 26, a second throttle valve 27, a condenser 28, a liquid collector 29, a first conveying pipeline 30, a second conveying pipeline 31, a third conveying pipeline 32, a fourth conveying pipeline 33, a fifth conveying pipeline 34, a sixth conveying pipeline 35, a seventh conveying pipeline 36, an eighth conveying pipeline 37, a ninth conveying pipeline 38, a heat source pipeline 39 and a first cold source pipeline 40;

the refrigerant outlet of the boiler 21 is connected with the inlet of the first conveying pipeline 30, and the outlet of the first conveying pipeline 30 is connected with the working fluid inlet of the special-shaped continuous spraying structure ejector 23;

the outlet of the special-shaped continuous spraying structure ejector 23 is connected with the inlet of an eighth conveying pipeline 37, the outlet of the eighth conveying pipeline 37 is connected with the refrigerant inlet of the condenser 28, the refrigerant outlet of the condenser 28 is connected with the inlet of a ninth conveying pipeline 38, the outlet of the ninth conveying pipeline 38 is connected with the inlet of the liquid collector 29, the outlet of the liquid collector 29 is connected with the inlet of a seventh conveying pipeline 36, the outlet of the seventh conveying pipeline 36 is respectively connected with the inlets of a fourth conveying pipeline 33 and a sixth conveying pipeline 35, the outlet of the fourth conveying pipeline 33 is connected with the refrigerant inlet of the first evaporator 24, the fourth conveying pipeline 33 is provided with a first throttle valve 25, and the refrigerant outlet of the first evaporator 24 is connected with the inlet of the third conveying pipeline 32; an outlet of the sixth conveying pipeline 35 is connected with a refrigerant inlet of the second evaporator 26, a second throttle valve 27 is arranged on the sixth conveying pipeline 35, a refrigerant outlet of the second evaporator 26 is connected with an inlet of a fifth conveying pipeline 34, an outlet of the third conveying pipeline 32 is connected with a first injection fluid inlet of the special-shaped continuous injection structure ejector 23, and an outlet of the fifth conveying pipeline 34 is connected with a second injection fluid inlet of the special-shaped continuous injection structure ejector 23;

a second outlet of the liquid collector 29 is connected with an inlet of a second conveying pipeline 31, a booster pump 22 is arranged on the second conveying pipeline 31, and an outlet of the second conveying pipeline 31 is connected with a refrigerant inlet of the boiler 21;

the heat source line 39 passes through the boiler 21 and the first cool source line 40 passes through the condenser 28.

Compared with the traditional series type ejector heat pump system, the double-effect injection type heat pump circulating system of the special-shaped continuous injection structure ejector 23 based on the continuous injection structure is provided with the two evaporators and the two injection fluid inlets, so that the continuous injection process is realized, the system structure is simplified, and the total energy loss of the system is reduced.

The second specific embodiment: referring to fig. 2 and 3, the first evaporator 24 and the second evaporator 26 are connected in series or in parallel through the second cold source pipeline 41, and when the first evaporator 24 and the second evaporator 26 are connected in parallel through the second cold source pipeline 41, the second cold source pipeline 41 is divided into two paths from the flow direction, and the two paths respectively flow through the first evaporator 24 and the second evaporator 26 and then are merged into one path to be discharged; when the first and

second evaporators

24 and 26 are connected in series through the second cool source line 41, the second cool source line 41 flows through the second evaporator 26 and the first evaporator 24 in sequence. Other combinations and connections of this embodiment are the same as those of the first embodiment.

The operation principle of the embodiment is as follows:

when the first evaporator 24 and the second evaporator 26 are connected in parallel through the second cold source pipeline 41, the high-temperature high-pressure gaseous working medium generated in the boiler 21 is used as working steam to inject low-pressure gas in the first evaporator 24 and the second evaporator 26, the low-pressure gas is mixed through the special-shaped continuous-injection structure ejector 23, the working medium is changed into liquid after being subjected to heat release and liquefaction through the condenser, the liquid working medium is stored in the liquid collector 29, a part of the liquid working medium in the liquid collector 29 passes through the first throttling valve 25 and the second throttling valve 27 respectively, the pressure is reduced, the part of the liquid working medium enters the first evaporator 24 and the second evaporator 26 respectively, the part of the liquid working medium is changed into the gaseous working medium after absorbing heat and enters the special-shaped continuous-injection structure ejector 23 to complete the circulation of a part of the working medium, the other part of the liquid working medium in the liquid collector 29 enters the boiler 21 after being pressurized through the booster pump 22, and the high-temperature high-pressure gaseous working medium is generated after absorbing heat, so that the circulation of the rest of the working medium is completed. When the cold source fluid is connected in parallel, enough cold source fluid is equivalently provided, so that the refrigerant and the cold source fluid perform sufficient heat exchange, the refrigerant generates great temperature rise, and the injection coefficient is improved.

When the first evaporator 24 and the second evaporator 26 are connected in series through the second cold source pipeline 41, a high-temperature high-pressure gaseous working medium generated in the boiler 21 is used as working steam to inject low-pressure gas in the first evaporator 24 and the second evaporator 26, the low-pressure gas is mixed through the special-shaped continuous injection structure ejector 23, the mixture is subjected to heat release and liquefaction through the condenser 28 and becomes a liquid state, the liquid working medium is stored in the liquid storage device 29, a part of the liquid working medium in the liquid storage device 29 passes through the first throttle valve 25 and the second throttle valve 27 respectively, the pressure is reduced, the liquid working medium enters the first evaporator 24 and the second evaporator 26 respectively, the liquid working medium is changed into a gaseous working medium after heat absorption and enters the special-shaped continuous injection structure ejector 23, circulation of a part of working medium is completed, the other part of the liquid working medium in the liquid storage device 29 enters the boiler 21 after being pressurized through the booster pump 22, and the high-temperature high-pressure gaseous working medium is generated after heat absorption, so that circulation of the residual working medium is completed. Due to the characteristics of the special-shaped continuous spraying structure ejector 23, the evaporation effect of the refrigerant of the first evaporator 24 connected with the first injection fluid inlet 11 is better than that of the refrigerant of the second evaporator 26 connected with the first injection fluid inlet 11, therefore, the two evaporators are connected in series through the cold source pipeline, the cold source passes through the first evaporator 24 after passing through the second evaporator 26, the cold source fluid and the refrigerant perform step heat exchange, and the cold source fluid is subjected to larger temperature drop.

The third concrete implementation scheme is as follows: as shown in fig. 4 and 5, a common injector 51, a heat exchanger 52, a third throttle valve 53, a tenth transfer line 54, an eleventh transfer line 55, and a thirteenth transfer line 57;

an outlet of the first conveying pipeline 30 is connected with an inlet of the special-shaped continuous spraying structure ejector 23 and an inlet of the common ejector 51, an outlet of the special-shaped continuous spraying structure ejector 23 and an outlet of the common ejector 51 are merged and then connected with an inlet of the eighth conveying pipeline 37, an outlet of the ninth conveying pipeline 38 is connected with an inlet of the liquid collector 29, an outlet of the liquid collector 29 is connected with an inlet of the eleventh conveying pipeline 55 and an inlet of the thirteenth conveying pipeline 57, an outlet of the eleventh conveying pipeline 55 is connected with a second inlet of the heat exchanger 52, a second outlet of the heat exchanger 52 is connected with an inlet of the tenth conveying pipeline 54, a third throttle valve 53 is arranged on the eleventh conveying pipeline 55, an injection fluid inlet of the common ejector 51 is connected with an outlet of the tenth conveying pipeline 54, an outlet of the thirteenth conveying pipeline 57 is connected with a first inlet of the heat exchanger 52, and a first outlet of the heat exchanger 52 is connected with an inlet of the seventh conveying pipeline 36. Other combinations and connections of this embodiment are the same as those of the second embodiment.

The operation principle of the embodiment is as follows:

the gaseous working medium which generates high temperature and high pressure in the boiling device 21 respectively enters the common ejector 51 and the special-shaped continuous spraying structure ejector 23, the gaseous working medium which enters the special-shaped continuous spraying structure ejector 23 is used as working steam to eject low-pressure gas in the first evaporator 24 and the second evaporator 26, the low-pressure gas is mixed through the special-shaped continuous spraying structure ejector 23, the gaseous working medium ejected from the common ejector 51 and the special-shaped continuous spraying structure ejector 23 simultaneously enters the condenser 28, the heat is released and liquefied to become liquid working medium, a part of the liquid working medium passes through the third throttle valve 53, the pressure is reduced, the liquid working medium passes through the heat exchanger 52, circulation is completed through the ejection effect of the common ejector 51, the other part of the liquid working medium is stored in the liquid storage device 29, a part of the liquid working medium in the liquid storage device 29 respectively passes through the first throttle valve 25 and the second throttle valve 27, the pressure is reduced, the liquid working medium respectively enters the first evaporator 24 and the second evaporator 26, the gaseous working medium which is changed into the gaseous working medium after the heat is absorbed and enters the special-shaped continuous spraying structure ejector 23, circulation of the gaseous working medium is completed, and the other part of the liquid working medium in the liquid storage device 29, the high temperature and the high-pressure of the high-pressure-generated gaseous working medium is increased by the booster pump 22, thereby completing circulation of the gaseous working medium.

The fourth specific embodiment: with reference to fig. 6, the present invention provides a dual-effect ejector type heat pump cycle system with a special-shaped continuous jet structure ejector, which includes a boiler 21, a booster pump 22, a special-shaped continuous jet structure ejector 23, a first evaporator 24, a first throttle 25, a condenser 28, a liquid collector 29, a first conveying pipeline 30, a second conveying pipeline 31, a third conveying pipeline 32, a fourth conveying pipeline 33, a seventh conveying pipeline 36, an eighth conveying pipeline 37, a ninth conveying pipeline 38, a heat source pipeline 39, a first cold source pipeline 40, a heat exchanger 52, a third throttle 53, a fourteenth conveying pipeline 58, and a fifteenth conveying pipeline 59;

an outlet of the special-shaped continuous-spraying structure ejector 23 is connected with an inlet of an eighth conveying pipeline 37, an outlet of the eighth conveying pipeline 37 is connected with a refrigerant inlet of the condenser 28, a refrigerant outlet of the condenser 28 is connected with an inlet of a ninth conveying pipeline 38, an outlet of the ninth conveying pipeline 38 is connected with an inlet of the liquid collector 29, an outlet of the liquid collector 29 is respectively connected with an inlet of a fourteenth conveying pipeline 58, an inlet of a seventh conveying pipeline 36 and an inlet of a second conveying pipeline 31, an outlet of the fourteenth conveying pipeline 58 is connected with a second inlet of the heat exchanger 52, a third throttle valve 53 is arranged on the fourteenth conveying pipeline 58, a second outlet of the heat exchanger 52 is connected with an inlet of a fifteenth conveying pipeline 59, and an outlet of the fifteenth conveying pipeline 59 is connected with a second injection fluid inlet of the special-shaped continuous-spraying structure ejector 23;

an outlet of the seventh conveying pipeline 36 is connected with a first inlet of the heat exchanger 52, a first outlet of the heat exchanger 52 is connected with an inlet of the fourth conveying pipeline 33, an outlet of the fourth conveying pipeline 33 is connected with a refrigerant inlet of the first evaporator 24, the fourth conveying pipeline 33 is provided with a first throttle valve 25, a refrigerant outlet of the first evaporator 24 is connected with an inlet of the third conveying pipeline 32, and an outlet of the third conveying pipeline 32 is connected with a first injection fluid inlet of the special-shaped continuous injection structure ejector 23;

the second conveying pipeline 31 is provided with a booster pump 22, and the outlet of the second conveying pipeline 31 is connected with the refrigerant inlet of the boiler 21;

the heat source line 39 flows through the boiler 21, the first cool source line 40 flows through the condenser 28, and the third cool source line 61 flows through the evaporator 24.

The working principle is as follows: the high-temperature high-pressure gaseous working medium generated in the boiler 21 enters the special-shaped continuous spraying structure ejector 23 to be used as working fluid to inject low-pressure gas, the fluid mixed by the special-shaped continuous spraying structure ejector 23 passes through the condenser 28, the discharged heat is liquefied and then changed into saturated liquid working medium, the saturated liquid working medium enters the liquid collector 29, a part of liquid in the liquid collector 29 enters the boiler 21 through the booster pump 22 to absorb heat and evaporate, the circulation of a part of working medium is completed, the rest working medium is divided into two paths, one path of working medium is subjected to pressure reduction through the third throttle valve 53 and then enters the heat exchanger 52 from one side to be injected so as to complete the circulation, the other portion of working medium enters the heat exchanger 52 from the other side, the heat is absorbed by the working medium passing through the third throttle valve 53, the temperature is reduced, then the working medium passes through the first throttle valve 25 to be changed into low-temperature low-pressure liquid working medium, the heat is absorbed by the first evaporator 24 and then is injected, and the circulation of the rest working medium is completed.

The fifth concrete embodiment: with reference to fig. 7 to 10, the special-shaped continuous jet structure ejector 23 includes a first nozzle 1, a first suction chamber 2, a first ejector section 3, a first mixing section 4, a second nozzle 5, a second suction chamber 6, a second ejector section 7, a second mixing section 8, a diffusion section 9, a first ejector fluid inlet 11, and a second ejector fluid inlet 12;

the inlet end of the first spray pipe 1 is a working fluid inlet 10, the first suction chamber 2 comprises a first injection fluid inlet 11 and an inlet of the first injection section 3, the first injection section 3 is a cavity defined between an arc transition of the outer wall of the first spray pipe 1 and an arc transition of the inlet of the first mixing section 4, the outlet end of the first spray pipe 1 is connected with the inlet end of the first mixing section 4 after being converged with the outlet end of the first injection section 2, the first injection fluid is converged with the working fluid and then enters the first mixing section 4 after passing through the first injection section 3, the outlet end of the first mixing section 4 is connected with the inlet end of the second spray pipe 2, the second suction chamber 6 comprises a second injection fluid inlet 12 and an inlet of the second injection section 7, the second injection section 7 is a cavity defined between an arc transition of the outer wall of the second spray pipe 5 and an arc transition of the inlet of the second mixing section 8, and is used for the second injection fluid to pass through the second injection section 6 and then enter the second mixing section 8, and then enters the second injection section 8, and the second injection section 6 is connected with the mixing diffusion inlet end of the second injection section 8. Other combinations and connections of this embodiment are the same as those of the fourth embodiment.

The first spray pipe 1 is a first Laval spray pipe which comprises a front horizontal section 1-1 of the first spray pipe, a contracted section 1-2 of the first spray pipe, an expanded section 1-3 of the first spray pipe and a rear horizontal section 1-4 of the first spray pipe.

When the speed of the working medium mixed by the first mixing section 4 is lower than the local sound speed, the second spray pipe 5 is a second Laval spray pipe, and the second Laval spray pipe comprises a second spray pipe contraction section 5-2, a second spray pipe expansion section 5-3 and a second spray pipe rear horizontal section 5-4; when the speed of the working medium mixed by the first mixing section 4 is higher than the local sound speed, the second spray pipe 5 is an expansion spray pipe with the diameter gradually increased, and the expansion spray pipe comprises an expansion spray pipe expansion section 5-5 and an expansion spray pipe horizontal section 5-6.

The outlet end of the first spray pipe 1 is flush with the outlet end of the first injection section 3, and the outlet end of the second spray pipe 5 is flush with the outlet end of the second injection section 7.

The section of the arc transition of one side, far away from the spray pipe, of the first injection section 3 and the second injection section 7 is in 1/4 arc transition.

The length of the front horizontal section 1-1 of the first spray pipe is more than 4 times of the radius of the inlet section of the first spray pipe 1.

The working principle is as follows:

when the second nozzle 5 is a second Laval nozzle, the working fluid passes through the first Laval nozzle, the speed is increased, the pressure is reduced, and the first injection fluid passes through the first injection section 3, the speed is increased, and the pressure is reduced. At the inlet of the first mixing section 4, the working fluid and the first injection fluid have the same pressure, the two fluids are mixed in the first mixing section 4 at a speed lower than the local sonic speed, then enter the second Laval nozzle, and are mixed in the contraction section of the second Laval nozzle, meanwhile, the speed of the mixed fluid is increased, the pressure is reduced, and the speed of the second injection fluid passing through the second injection section 7 is increased, and the pressure is reduced. At the inlet of the second mixing section 7, the mixed fluid and the second injection fluid have the same pressure, the two fluids are fully mixed in the second mixing section, and the speed is reduced and the pressure is increased after passing through the diffusion section 9, so that the injection process is completed.

When the second spray pipe 5 is an expansion spray pipe, the working fluid passes through the first Laval spray pipe, the speed is increased, the pressure is reduced, and the first injection fluid passes through the first injection section 3, the speed is increased, and the pressure is reduced. At the inlet of the first mixing section 4, the working fluid and the first injection fluid have the same pressure, the two fluids are mixed in the first mixing section 4 at a speed higher than the local sonic speed and then enter the expansion nozzle, the mixing is completed in the expansion nozzle expansion section 5-5, meanwhile, the speed of the mixed fluid is increased, the pressure is reduced, and the speed of the second injection fluid passing through the second injection section 7 is increased, and the pressure is reduced. At the inlet of the second mixing section 8, the mixed fluid and the second injection fluid have the same pressure, the two fluids are fully mixed in the second mixing section 8, and the speed is reduced and the pressure is increased through the diffusion section 9, so that the injection process is completed.

Since the fluid has different state parameters at different positions, the sound velocity is also different, and the velocity of the fluid at a certain position is called the local sound velocity.

The special-shaped continuous-spraying structure ejector 23 in the invention integrates two existing ejectors connected in series, thereby omitting a diffusion section of a first ejector and a spray pipe part of a second ejector, simplifying the structure of the ejectors connected in series and reducing the distance of fluid delivery.

The different ejector 23 in the invention reduces the irreversible loss of three parts of the traditional series ejector, wherein the first part is the irreversible loss of a conveying pipeline connecting two ejectors, the second part is the irreversible loss of a fluid in a speed-reducing and pressure-increasing process of a diffusion section part of the first ejector, and the third part is the irreversible loss of a fluid in an accelerating and pressure-reducing process of a nozzle part of the second ejector. Compared with common series-connected ejectors, the ejector device effectively improves the ejection coefficient and the operation effect.

The sixth specific embodiment: as shown in fig. 7 to 10, when the first nozzle 1 is a first laval nozzle and the second nozzle 2 is a second laval nozzle, the linear type of the first nozzle 1 and the second nozzle 2, i.e. the section radius d, is determined by the following formula:

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1t-a first or second laval nozzle throat section radius;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or a second laval nozzle flare length;

x-the distance from the cross-section at x to the inlet cross-section of the first or second laval nozzle.

When the second nozzle 5 is a divergent nozzle, the linear form of the divergent nozzle, i.e. the section radius d, is determined by the following formula:

{x＝x₂₁；x＝x₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-expanding the nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle extension section;

the line type of the first ejector section 3 and the second ejector section 7 is determined by the following method and formula,

the known quantity is the annular area S of the inlet of the first injection section 3 or the second injection section 7₁The annular area S of the throat part of the first injection section 3 or the second injection section 7₂The radius R' of a circle formed by the outlet of the first ejector section 3 and the outlet of the first spray pipe 1 or the outlet of the second ejector section 7 and the outlet of the second spray pipe 5 is unknown R and L₁、L₂、L₃、L₄The following formula is needed for the solution:

L₂＝R+R'

L₁the distance between the inlet end of the first injection section 3 close to one side of the spray pipe and the central axis of the first spray pipe 1 or the distance between the inlet end of the second injection section 7 and the central axis of the second spray pipe 5;

L₂the distance between the inlet end of the first injection section 3 far away from one side of the spray pipe and the central axis of the first spray pipe 1 or the distance between the inlet end of the second injection section 7 and the central axis of the second spray pipe 5;

L₃the distance between the end point of the throat part of the first injection section 3 close to one side of the spray pipe and the central axis of the first spray pipe 1 or the distance between the throat part of the second injection section 7 and the central axis of the second spray pipe 5 is obtained;

L₄the distance between the end point of the throat part of the first injection section 3, which is far away from one side of the spray pipe, and the central axis of the first spray pipe 1 or the distance between the throat part of the second injection section 7 and the central axis of the second spray pipe 5 is short;

r' -the distance between the outlet end of the circular arc transition of the first injection section 3 and the central axis of the first spray pipe 1 or the distance between the outlet end of the circular arc transition of the second injection section 7 and the central axis of the second spray pipe 5;

L₆the length of the inlet end of the first injection section 3 or the length of the inlet end of the second injection section 7;

L₇the length of the throat part of the first injection section 3 or the length of the throat part of the second injection section 7;

r is the radius of a 1/4 circular arc curve of one side, far away from the spray pipe, of the first injection section 3 or the second injection section 7;

the outlet end tangent line of 1/4 circular arc transition is connected with the side wall of the first injection section 3 or the second injection section 7 close to the spray pipe, the intersection point is a point D, a curve from the inlet end of the side wall of the first injection section 3 or the second injection section 7 close to the spray pipe to the point D is symmetrical to a perpendicular line of the 1/4 circular arc transition relative to the midpoint of the throat, the plane of the throat is positioned on an angular bisector of a central angle corresponding to the 1/4 circular arc, the point D is connected with the tail end of the first spray pipe expansion section 1-3 or the tail end of the second spray pipe expansion section 5-3 through a function curve, and the function curve is determined by the following method and formula:

y＝a+bt+ct²+et³

two ends of the function curve are respectively and smoothly connected with the point D and the tail ends of the first nozzle expansion sections 1-3 or the point D and the tail ends of the second nozzle expansion sections 5-3, so that the positions of end points at two sides of the function curve and the first derivative of the end points are known to form four equations, and four undetermined coefficients of a, b, c and e are obtained;

length L of the first mixing section 4₅The design is as follows:

when the second lance 5 is a second laval lance,

L₅＝13.23×R″′

when the second lance 5 is an expanding lance,

L₅＝5.81×R″′

L₅the length of the first mixing section 4;

r' -the radius of the first mixing section 4;

length L of second mixing section 8₈The design is as follows:

L₈＝1.51×R″

L₈the length of the second mixing section 8;

r' -the radius of the second mixing section 8;

the linear design of the diffuser section 9 is determined by the following formula:

L₉＝c×R″

s-horizontal distance from any one of the diffuser sections 9 to the inlet cross-section of the diffuser section 9;

r is the radius of any section of the diffusion section 9;

r' -the radius of the second mixing section 8;

L₉the length of the diffuser section 9;

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。

the linear design of the diffusion section is suitable for working medium R245fa, the temperature of the working fluid is 100-140 ℃, and the superheat degree is 3-5 ℃; the temperature of the first injection fluid is 32-46 ℃, the temperature of the second injection fluid is 40-58 ℃, the superheat degree of the first injection fluid and the second injection fluid is 2-5 ℃, the applicable working medium is not limited to R245fa, and the applicable working condition is not limited to the working conditions.

Other combinations and connections of this embodiment are the same as those of the fourth embodiment.

The invention provides a novel design method for the cross-sectional areas of a spray pipe line type, an ejection section line type and a mixing section, the linear structure of the ejection section enables the velocity of the ejection fluid to exceed the sonic velocity, the velocity difference between the working fluid and the mixed fluid is reduced, the ejection section has the guiding effect on the ejection fluid, the velocity keeps the consistent direction when the working fluid and the ejection fluid are mixed, and the loss of kinetic energy is reduced. The linear design of the spray pipe enables the working fluid to have more uniform speed, and reduces the irreversible loss during mixing.

Although the present disclosure has been described above, the scope of the present disclosure is not limited thereto. Various changes and modifications may be effected therein by one of ordinary skill in the pertinent art without departing from the spirit and scope of the present disclosure, and these changes and modifications are intended to be within the scope of the present disclosure.

Claims

1. The utility model provides a double-effect injection formula heat pump cycle system with abnormal shape is even spouted structure sprayer which characterized in that: the device comprises a boiling device (21), a booster pump (22), a special-shaped continuous spraying structure ejector (23), a first evaporator (24), a first throttle valve (25), a second evaporator (26), a second throttle valve (27), a condenser (28), a liquid collector (29), a first conveying pipeline (30), a second conveying pipeline (31), a third conveying pipeline (32), a fourth conveying pipeline (33), a fifth conveying pipeline (34), a sixth conveying pipeline (35), a seventh conveying pipeline (36), an eighth conveying pipeline (37), a ninth conveying pipeline (38), a heat source pipeline (39), a first cold source pipeline (40) and a second cold source pipeline (41);

a refrigerant outlet of the boiler (21) is connected with an inlet of a first conveying pipeline (30), and an outlet of the first conveying pipeline (30) is connected with a working fluid inlet of the special-shaped continuous spraying structure ejector (23);

an outlet of the special-shaped continuous-spraying structure ejector (23) is connected with an inlet of an eighth conveying pipeline (37), an outlet of the eighth conveying pipeline (37) is connected with a refrigerant inlet of a condenser (28), a refrigerant outlet of the condenser (28) is connected with an inlet of a ninth conveying pipeline (38), an outlet of the ninth conveying pipeline (38) is connected with an inlet of a liquid collector (29), an outlet of the liquid collector (29) is connected with an inlet of a seventh conveying pipeline (36), an outlet of the seventh conveying pipeline (36) is respectively connected with inlets of a fourth conveying pipeline (33) and a sixth conveying pipeline (35), an outlet of the fourth conveying pipeline (33) is connected with a refrigerant inlet of a first evaporator (24), a first throttling valve (25) is arranged on the fourth conveying pipeline (33), and a refrigerant outlet of the first evaporator (24) is connected with an inlet of a third conveying pipeline (32); an outlet of a sixth conveying pipeline (35) is connected with a refrigerant inlet of the second evaporator (26), a second throttle valve (27) is arranged on the sixth conveying pipeline (35), a refrigerant outlet of the second evaporator (26) is connected with an inlet of a fifth conveying pipeline (34), an outlet of a third conveying pipeline (32) is connected with a first injection fluid inlet of the special-shaped continuous spraying structure ejector (23), and an outlet of the fifth conveying pipeline (34) is connected with a second injection fluid inlet of the special-shaped continuous spraying structure ejector (23);

the outlet of the liquid collector (29) is connected with the inlet of a second conveying pipeline (31), a booster pump (22) is arranged on the second conveying pipeline (31), and the outlet of the second conveying pipeline (31) is connected with the refrigerant inlet of the boiler (21);

a heat source pipeline (39) flows through the boiler (21), and a first cold source pipeline (40) flows through the condenser (28);

the first evaporator (24) and the second evaporator (26) are connected in parallel through a second cold source pipeline (41), the second cold source pipeline (41) is divided into two paths from the flow direction, and the two paths of cold source pipeline respectively flow through the first evaporator (24) and the second evaporator (26) and then are converged into one path to be discharged;

the special-shaped continuous-spraying structure ejector (23) comprises a first spray pipe (1), a first suction chamber (2), a first injection section (3), a first mixing section (4), a second spray pipe (5), a second suction chamber (6), a second injection section (7), a second mixing section (8), a diffusion section (9), a first injection fluid inlet (11) and a second injection fluid inlet (12);

the inlet end of the first spray pipe (1) is a working fluid inlet (10), the first suction chamber (2) comprises a first injection fluid inlet (11) and an inlet of a first injection section (3), the first injection section (3) is an arc transition of the outer wall of the first spray pipe (1), a cavity is formed by enclosing the horizontal part of the first spray pipe (1) and an arc transition at the inlet of the first mixing section (4), the outlet end of the first spray pipe (1) is connected with the inlet end of the first mixing section (4) after being converged with the outlet end of the first injection section (2) and is used for leading the first injection fluid to enter the first mixing section (4) after passing through the first injection section (3) and converging with the working fluid, the outlet end of the first mixing section (4) is connected with the inlet end of the second spray pipe (2), the second suction chamber (6) comprises a second injection fluid inlet (12) and an inlet of a second injection section (7), the second injection section (7) is an inlet end of the second injection section (5) and an outlet end of the second injection section (8) after being converged with the outer wall of the second injection section (5), and the second injection section (8) is used for leading the mixing fluid to enter the cavity after passing through the second injection section (8);

the first spray pipe (1) is a first Laval spray pipe, and the first Laval spray pipe comprises a first spray pipe front horizontal section (1-1), a first spray pipe contraction section (1-2), a first spray pipe expansion section (1-3) and a first spray pipe rear horizontal section (1-4);

when the speed of the working medium mixed by the first mixing section (4) is lower than the local sound speed, the second spray pipe (5) is a second Laval spray pipe which comprises a second spray pipe contraction section (5-2), a second spray pipe expansion section (5-3) and a second spray pipe rear horizontal section (5-4); when the speed of the working medium mixed by the first mixing section (4) is higher than the local sound speed, the second spray pipe (5) is an expansion spray pipe with the diameter gradually increased, and the expansion spray pipe comprises an expansion spray pipe expansion section (5-5) and an expansion spray pipe horizontal section (5-6);

the outlet end of the first spray pipe (1) is flush with the outlet end of the first injection section (3), and the outlet end of the second spray pipe (5) is flush with the outlet end of the second injection section (7);

the section of the arc transition of one side of the first injection section (3) and one side of the second injection section (7) far away from the spray pipe is 1/4 arc transition;

the length of the front horizontal section (1-1) of the first spray pipe is more than 4 times of the radius of the inlet section of the first spray pipe (1);

when the first spray pipe (1) is a first Laval spray pipe and the second spray pipe (2) is a second Laval spray pipe, the linear type of the first spray pipe (1) and the second spray pipe (2), namely the section radius d, is determined by the following formula:

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

{d＝d₁₁，0≤x₁₁≤L₁₁；d＝d₁₂，L₁₁≤x₁₂≤L₁₁+L₁₂；d＝d₁₃，L₁₁+L₁₂≤x₁₃≤L₁₁+1.07×L₁₂}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1tthe first or second Laval nozzle throat section radiusThe radius of the section of the throat part of the spray pipe;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or second laval nozzle flare length;

x-the distance from the cross section at x to the inlet cross section of the first or second laval nozzle;

when the second nozzle (5) is a divergent nozzle, the linear form of the divergent nozzle, i.e. the section radius d, is determined by the following formula:

{x＝x₂₁；x＝x₂₂}

{d＝d₂₁，0≤x₂₁≤L₂₂；d＝d₂₂，L₂₂≤x₂₂≤1.07L₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-the divergent nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle extension section;

the line type of the first injection section (3) and the second injection section (7) is determined by the following method and formula,

the known quantity is the annular area S of the inlet of the first injection section (3) or the second injection section (7)₁The annular area S of the throat part of the first injection section (3) or the second injection section (7)₂First introduction ofThe radius R' of a circle formed by the outlet of the injection section (3) and the outlet of the first spray pipe (1) or the outlet of the second injection section (7) and the outlet of the second spray pipe (5) has unknown quantities of R and L₁、L₂、L₃、L₄The following formula is needed for the solution:

L₂＝R+R′

L₁the distance between the inlet end of the first injection section (3) close to one side of the spray pipe and the central axis of the first spray pipe (1) or the distance between the inlet end of the second injection section (7) and the central axis of the second spray pipe (5);

L₂the distance between the inlet end of the first injection section (3) far away from one side of the spray pipe and the central axis of the first spray pipe (1) or the distance between the inlet end of the second injection section (7) and the central axis of the second spray pipe (5);

L₃the distance between the end point of the throat part of the first injection section (3) close to one side of the spray pipe and the central axis of the first spray pipe (1) or the distance between the throat part of the second injection section (7) and the central axis of the second spray pipe (5);

L₄the distance between the end point of the throat part of the first injection section (3) far away from one side of the spray pipe and the central axis of the first spray pipe (1) or the distance between the throat part of the second injection section (7) and the central axis of the second spray pipe (5);

r' -the distance between the outlet end of the circular arc transition of the first injection section (3) and the central axis of the first spray pipe (1) or the distance between the outlet end of the circular arc transition of the second injection section (7) and the central axis of the second spray pipe (5);

L₆-the length of the inlet end of the first ejector section (3) or the length of the inlet end of the second ejector section (7);

L₇-the length of the throat of the first ejector section (3) or the length of the throat of the second ejector section (7);

r is the radius of a 1/4 circular arc curve of one side, far away from the spray pipe, of the first injection section (3) or the second injection section (7);

the exit end tangent line of 1/4 circular arc transition is connected with the side wall of the first injection section (3) or the second injection section (7) close to the spray pipe, the intersection point is a point D, a curve from the entrance end of the side wall of the first injection section (3) or the second injection section (7) close to the spray pipe to the point D is symmetrical to a perpendicular line of the 1/4 circular arc transition relative to the midpoint of the throat, the plane of the throat is positioned on an angular bisector of a central angle corresponding to the 1/4 circular arc, the point D is connected with the tail end of the first spray pipe expansion section (1-3) or the tail end of the second spray pipe expansion section (5-3) through a function curve, and the function curve is determined by the following method and formula:

y＝a+bt+ct²+et³

two ends of the function curve are respectively and smoothly connected with the D point and the tail end of the first spray pipe expansion section (1-3) or the D point and the tail end of the second spray pipe expansion section (5-3), so that the positions of end points on two sides of the function curve and a first derivative thereof are known to form four equations, and four undetermined coefficients of a, b, c and e are obtained;

the length L of the first mixing section (4)₅The design is as follows:

when the second nozzle (5) is a second Laval nozzle,

L₅＝13.23×R″′

when the second nozzle (5) is an expansion nozzle,

L₅＝5.81×R″′

L₅-the length of the first mixing section (4);

r' -the radius of the first mixing section (4);

of the second mixing section (8)Length L₈The design is as follows:

L₈＝1.51×R″

L₈-the length of the second mixing section (8);

r' -the radius of the second mixing section (8);

the linear design of the diffuser section (9) is determined by the following formula:

L₉＝c×R″

s is the horizontal distance from any position of the diffuser section (9) to the inlet section of the diffuser section (9);

r is the radius of any section of the diffusion section (9);

r' -the radius of the second mixing section (8);

L₉-the length of the diffuser section (9);

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。

2. the utility model provides a double-effect injection formula heat pump cycle system with abnormal shape is even spouted structure sprayer which characterized in that: the device comprises a boiling device (21), a booster pump (22), a special-shaped continuous spraying structure ejector (23), a first evaporator (24), a first throttle valve (25), a second evaporator (26), a second throttle valve (27), a condenser (28), a liquid collector (29), a first conveying pipeline (30), a second conveying pipeline (31), a third conveying pipeline (32), a fourth conveying pipeline (33), a fifth conveying pipeline (34), a sixth conveying pipeline (35), a seventh conveying pipeline (36), an eighth conveying pipeline (37), a ninth conveying pipeline (38), a heat source pipeline (39), a first cold source pipeline (40) and a second cold source pipeline (41);

a refrigerant outlet of the boiler (21) is connected with an inlet of a first conveying pipeline (30), and an outlet of the first conveying pipeline (30) is connected with a working fluid inlet of the special-shaped continuous-spraying structure ejector (23);

an outlet of the special-shaped continuous spraying structure ejector (23) is connected with an inlet of an eighth conveying pipeline (37), an outlet of the eighth conveying pipeline (37) is connected with a refrigerant inlet of a condenser (28), a refrigerant outlet of the condenser (28) is connected with an inlet of a ninth conveying pipeline (38), an outlet of the ninth conveying pipeline (38) is connected with an inlet of a liquid collector (29), an outlet of the liquid collector (29) is connected with an inlet of a seventh conveying pipeline (36), an outlet of the seventh conveying pipeline (36) is respectively connected with inlets of a fourth conveying pipeline (33) and a sixth conveying pipeline (35), an outlet of the fourth conveying pipeline (33) is connected with a refrigerant inlet of a first evaporator (24), a first throttling valve (25) is arranged on the fourth conveying pipeline (33), and a refrigerant outlet of the first evaporator (24) is connected with an inlet of the third conveying pipeline (32); an outlet of the sixth conveying pipeline (35) is connected with a refrigerant inlet of the second evaporator (26), a second throttle valve (27) is arranged on the sixth conveying pipeline (35), a refrigerant outlet of the second evaporator (26) is connected with an inlet of the fifth conveying pipeline (34), an outlet of the third conveying pipeline (32) is connected with a first injection fluid inlet of the special-shaped continuous spraying structure ejector (23), and an outlet of the fifth conveying pipeline (34) is connected with a second injection fluid inlet of the special-shaped continuous spraying structure ejector (23);

the first evaporator (24) and the second evaporator (26) are connected in series through a second cold source pipeline (41), and the second cold source pipeline (41) sequentially flows through the second evaporator (26) and the first evaporator (24);

the inlet end of the first spray pipe (1) is a working fluid inlet (10), the first suction chamber (2) comprises a first injection fluid inlet (11) and an inlet of a first injection section (3), the first injection section (3) is a cavity enclosed between an arc transition of the outer wall of the first spray pipe (1) and an arc transition of the inlet of the first mixing section (4), the outlet end of the first spray pipe (1) is connected with the inlet end of the first mixing section (4) after being converged with the outlet end of the first injection section (2) and is used for leading the first injection fluid to pass through the first injection section (3) and then enter the first mixing section (4) after being converged with the working fluid, the outlet end of the first mixing section (4) is connected with the inlet end of the second spray pipe (2), the second suction chamber (6) comprises a second injection fluid inlet (12) and an inlet of a second injection section (7), the outlet end of the second injection section (7) is an inlet of the second injection fluid inlet of the second injection section (5) and an outlet end of the second injection section (8) after being converged with the second injection section, and the second injection section (8) is used for leading the second injection fluid to pass through the arc transition of the second injection section (8) and is arranged after being diffused;

the first spray pipe (1) is a first Laval spray pipe, and the first Laval spray pipe comprises a front horizontal section (1-1) of the first spray pipe, a first spray pipe contraction section (1-2), a first spray pipe expansion section (1-3) and a rear horizontal section (1-4) of the first spray pipe;

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1t-a first or second laval nozzle throat section radius;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or second laval nozzle flare length;

{x＝x₂₁；x＝x₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-the divergent nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle extension section;

the known quantity is the annular area S of the inlet of the first injection section (3) or the second injection section (7)₁The annular area S of the throat part of the first injection section (3) or the second injection section (7)₂The radius R' of a circle formed by the outlet of the first injection section (3) and the outlet of the first spray pipe (1) or the outlet of the second injection section (7) and the outlet of the second spray pipe (5) is unknown R and L₁、L₂、L₃、L₄To solve the needThe following formula is used:

L₂＝R+R′

r' -the distance between the outlet end of the arc transition of the first injection section (3) and the central axis of the first spray pipe (1) or the distance between the outlet end of the second injection section (7) and the central axis of the second spray pipe (5);

the tangent line of an outlet end of a 1/4 circular arc transition is connected with the side wall of a first injection section (3) or a second injection section (7) close to the spray pipe, the intersection point is a point D, a curve from the inlet end of the side wall of the first injection section (3) or the second injection section (7) close to the spray pipe to the point D is symmetrical to a perpendicular line of the 1/4 circular arc transition relative to the midpoint of the throat, the plane of the throat is positioned on an angle bisector of a central angle corresponding to the 1/4 circular arc, the point D is connected with the tail end of a first spray pipe expansion section (1-3) or the tail end of a second spray pipe expansion section (5-3) through a function curve, and the function curve is determined by the following method and formula:

y＝a+bt+ct²+et³

two ends of the function curve are respectively connected with the D point and the tail end of the first spray pipe expansion section (1-3) in a smooth mode or the D point and the tail end of the second spray pipe expansion section (5-3), so that the positions of end points on two sides of the function curve and the first derivative of the end points are known to form four equations, and four undetermined coefficients of a, b, c and e are obtained;

the length L of the first mixing section (4)₅The design is as follows:

when the second nozzle (5) is a second Laval nozzle,

L₅＝13.23×R″′

when the second nozzle (5) is an expansion nozzle,

L₅＝5.81×R″′

L₅-the length of the first mixing section (4);

r' -the radius of the first mixing section (4);

the length L of the second mixing section (8)₈The design is as follows:

L₈＝1.51×R″

L₈-the length of the second mixing section (8);

r' -the radius of the second mixing section (8);

L₉＝c×R″

r is the radius of any section of the diffusion section (9);

r' -the radius of the second mixing section (8);

L₉-the length of the diffuser section (9);

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。

3. the double-effect injection type heat pump circulating system with the special-shaped continuous injection structure ejector as claimed in claim 1 or 2, characterized in that: the system also comprises a common ejector (51), a heat exchanger (52), a third throttle valve (53), a tenth conveying pipeline (54), an eleventh conveying pipeline (55) and a thirteenth conveying pipeline (57);

an outlet of the first conveying pipeline (30) is connected with an inlet of the special-shaped continuous spraying structure ejector (23) and an inlet of the common ejector (51) respectively, an outlet of the special-shaped continuous spraying structure ejector (23) and an outlet of the common ejector (51) are combined and then connected with an inlet of the eighth conveying pipeline (37), an outlet of the ninth conveying pipeline (38) is connected with an inlet of the liquid collector (29), an outlet of the liquid collector (29) is connected with an inlet of the eleventh conveying pipeline (55) and an inlet of the thirteenth conveying pipeline (57) respectively, an outlet of the eleventh conveying pipeline (55) is connected with a second inlet of the heat exchanger (52), a second outlet of the heat exchanger (52) is connected with an inlet of the tenth conveying pipeline (54), a third throttle valve (53) is arranged on the eleventh conveying pipeline (55), an injection fluid inlet of the common ejector (51) is connected with an outlet of the tenth conveying pipeline (54), an outlet of the thirteenth conveying pipeline (57) is connected with a first inlet of the heat exchanger (52), and a first outlet of the heat exchanger (52) is connected with an inlet of the seventh conveying pipeline (36).

4. The utility model provides a double-effect injection formula heat pump cycle system with abnormal shape is even spouted structure sprayer which characterized in that: the device comprises a boiler (21), a booster pump (22), a special-shaped continuous spraying structure ejector (23), a first evaporator (24), a first throttle valve (25), a condenser (28), a liquid collector (29), a first conveying pipeline (30), a second conveying pipeline (31), a third conveying pipeline (32), a fourth conveying pipeline (33), a seventh conveying pipeline (36), an eighth conveying pipeline (37), a ninth conveying pipeline (38), a heat source pipeline (39), a first cold source pipeline (40), a heat exchanger (52), a third throttle valve (53), a fourteenth conveying pipeline (58) and a fifteenth conveying pipeline (59);

an outlet of the special-shaped continuous-spraying structure ejector (23) is connected with an inlet of an eighth conveying pipeline (37), an outlet of the eighth conveying pipeline (37) is connected with a refrigerant inlet of a condenser (28), a refrigerant outlet of the condenser (28) is connected with an inlet of a ninth conveying pipeline (38), an outlet of the ninth conveying pipeline (38) is connected with an inlet of a liquid collector (29), an outlet of the liquid collector (29) is respectively connected with an inlet of a fourteenth conveying pipeline (58), an inlet of a seventh conveying pipeline (36) and an inlet of a second conveying pipeline (31), an outlet of the fourteenth conveying pipeline (58) is connected with a second inlet of the heat exchanger (52), a third throttle valve (53) is arranged on the fourteenth conveying pipeline (58), a second outlet of the heat exchanger (52) is connected with an inlet of a fifteenth conveying pipeline (59), and an outlet of the fifteenth conveying pipeline (59) is connected with a second injection fluid inlet of the special-shaped continuous-spraying structure ejector (23);

an outlet of the seventh conveying pipeline (36) is connected with a first inlet of the heat exchanger (52), a first outlet of the heat exchanger (52) is connected with an inlet of the fourth conveying pipeline (33), an outlet of the fourth conveying pipeline (33) is connected with a refrigerant inlet of the first evaporator (24), the fourth conveying pipeline (33) is provided with a first throttle valve (25), a refrigerant outlet of the first evaporator (24) is connected with an inlet of the third conveying pipeline (32), and an outlet of the third conveying pipeline (32) is connected with a first injection fluid inlet of the special-shaped continuous injection structure ejector (23);

a booster pump (22) is arranged on the second conveying pipeline (31), and the outlet of the second conveying pipeline (31) is connected with the refrigerant inlet of the boiler (21);

a heat source pipeline (39) flows through the boiling device (21), a first cold source pipeline (40) flows through the condenser (28), a third cold source pipeline (61) flows through the evaporator (24), and the special-shaped continuous-spraying structure ejector (23) comprises a first spray pipe (1), a first suction chamber (2), a first injection section (3), a first mixing section (4), a second spray pipe (5), a second suction chamber (6), a second injection section (7), a second mixing section (8), a diffusion section (9), a first injection fluid inlet (11) and a second injection fluid inlet (12);

{x＝x₁₁；x＝x₁₂；x＝x₁₃}

d₁₃＝d_1c

L₁₁＝1.5×d_1i

L₁₂＝4×d_1t

d_1i-a first or second laval nozzle inlet cross-sectional radius;

d_1t-a first or second laval nozzle throat section radius;

d_1c-a first or second laval nozzle outlet cross-sectional radius;

L₁₁-a first or second laval nozzle constriction length;

L₁₂-a first or a second laval nozzle flare length;

{x＝x₂₁；x＝x₂₂}

d₂₂＝d_2c

L₂₂＝4×d_2t

d_2i-expanding the nozzle inlet cross-sectional radius;

d_2c-expanding the nozzle outlet cross-sectional radius;

d_2t-expanding the nozzle throat section radius;

L₂₂-expanding the length of the nozzle flare;

the known quantity is the annular area S of the inlet of the first injection section (3) or the second injection section (7)₁The annular area S of the throat part of the first injection section (3) or the second injection section (7)₂The radius R' of a circle formed by the outlet of the first injection section (3) and the outlet of the first spray pipe (1) or the outlet of the second injection section (7) and the outlet of the second spray pipe (5) is unknown R and L₁、L₂、L₃、L₄The following formula is needed for the solution:

L₂＝R+R′

L₁the distance between the inlet end of the first injection section (3) close to one side of the spray pipe and the central axis of the first spray pipe (1) or the distance between the inlet end of the second injection section (7) and the central axis of the second spray pipe (5)A distance;

y＝a+bt+ct²+et³

two ends of the function curve are respectively and smoothly connected with the D point and the tail end of the first spray pipe expansion section (1-3) or the D point and the tail end of the second spray pipe expansion section (5-3), so that the positions of end points at two sides of the function curve and the first derivative thereof are known to form four equations, and four undetermined coefficients a, b, c and e are calculated;

the length L of the first mixing section (4)₅The design is as follows:

when the second nozzle (5) is a second Laval nozzle,

L₅＝13.23×R″′

when the second nozzle (5) expands the nozzle,

L₅＝5.81×R″′

L₅-the length of the first mixing section (4);

r' -the radius of the first mixing section (4);

the length L of the second mixing section (8)₈The design is as follows:

L₈＝1.51×R″

L₈-the length of the second mixing section (8);

r' -the radius of the second mixing section (8);

L₉＝c×R″

r is the radius of any section of the diffusion section (9);

r' -the radius of the second mixing section (8);

L₉-the length of the diffuser section (9);

a₀＝1；

a₁＝-0.0532；

a₂＝0.0150；

a₃＝-0.0032016；

a₄＝0.00037943；

a₅＝-0.000020884；

a₆＝0.0000004646；

c＝17.55。