Double-evaporator non-isothermal water chilling unit and control method thereof

Abstract

The invention relates to the related technical field of water chilling units, and discloses a double-evaporator non-isothermal water chilling unit and a control method thereof.The double-evaporator non-isothermal water chilling unit comprises a box body, a compressor, an oil separator, a flooded evaporator and a dry evaporator are arranged on the lower side in the box body, a condenser is arranged on the upper side in the box body, and two condensation fans are arranged at the upper end of the box body; a liquid inlet cavity, a liquid outlet cavity and a heat exchange cavity are formed in the flooded evaporator, and a heat exchange assembly is arranged in the heat exchange cavity. The multiple pairs of baffles are distributed on the two side walls of the heat exchange cavity in a staggered mode, so that the flowing stroke of refrigerants in the heat exchange cavity is prolonged; chilled water enters the liquid inlet cavity through the water inlet pipe, and the chilled water in the liquid inlet cavity sequentially passes through the interiors of the first S-shaped heat exchange pipe, the second S-shaped heat exchange pipe and the third S-shaped heat exchange pipe, so that the flowing stroke of the chilled water in the heat exchange cavity is prolonged, the chilled water is in full contact with a refrigerant for heat exchange, and the heat exchange efficiency of the flooded evaporator is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field related to chillers, and more specifically, particularly relates to a dual-evaporator non-isothermal chiller and a control method thereof. Background Art

[0002] As people's living standards gradually improve, air conditioning technology has been widely used in modern buildings. In summer, the peak load of air conditioning systems overlaps with the peak load of the power grid. In today's increasingly scarce energy, the peak-to-valley difference in power load has been aggravated, bringing many difficulties to power production and unit operation. Energy conservation has become a hot issue for research in all walks of life throughout society. Therefore, in the development and application of air conditioning technology for energy conservation and carbon reduction, how to efficiently utilize the energy and energy conservation of central air conditioning systems has become an urgent problem to be solved. Improving the cooling efficiency of air conditioning units and reducing the power supply load of the power grid have significant social and economic benefits. However, the chillers in the existing technology have the following defects: In the prior art, when the heat exchange liquid is input into the flooded evaporator in the chiller, the relative flow rate of the heat exchange liquid in the heat exchange tube and the external refrigerant is slow, and poor heat exchange is easily generated, resulting in reduced working efficiency of the flooded evaporator; There is an existing application number of CN202410147326.0 The Chinese patent discloses a high-efficiency heat-exchange flooded evaporator, comprising a shell; a heat exchange chamber is arranged in the shell; the shell is provided with a first inlet and a first outlet; the first inlet and the first outlet are respectively connected to the heat exchange chamber; a heat exchange pipe is arranged in the heat exchange chamber; the shell is provided with a second inlet and a second outlet; the second inlet and the second outlet are respectively connected to the heat exchange pipe; a heat exchange device is arranged in the heat exchange chamber; the heat exchange device comprises a stirring shell; a stirring chamber is arranged in the stirring shell; a spiral fan blade is arranged in the stirring chamber. The present invention arranges a heat exchange device connected to the heat exchange pipe in the heat exchange chamber, so that the heat exchange liquid in the heat exchange pipe enters the stirring shell when passing through the heat exchange device, and the stirring shell is rotated by the spiral fan blade, so that the heat exchange pipe path of the heat exchange liquid in the stirring chamber is increased, thereby improving the heat exchange efficiency of the evaporator; however, simply increasing the flow path of the heat exchange liquid to improve the heat exchange efficiency of the evaporator has limited effect, and the refrigerant in the heat exchange chamber is usually not flowing, which makes it easy for the local temperature of the refrigerant to rise quickly, thereby affecting the effect of cooling the heat exchange liquid.

[0003] Therefore, in view of this, the existing structure and defects are studied and improved, and a dual-evaporator non-isothermal chiller and a control method thereof are provided, in order to achieve a more practical and valuable purpose. Summary of the invention

[0004] The present invention provides a dual-evaporator non-isothermal chiller and a control method thereof, which are used to overcome the above-mentioned defects in the prior art.

[0005] The purpose and effect of the dual-evaporator non-isothermal chiller and the control method thereof of the present invention are achieved by the following specific technical means: A dual-evaporator non-isothermal chiller and a control method thereof, comprising a casing, wherein a compressor, an oil separator, a flooded evaporator, and a dry evaporator are arranged on the lower inner side of the casing, a condenser is arranged on the upper inner side of the casing, two condensing fans are arranged on the upper end of the casing, two partitions are symmetrically arranged inside the flooded evaporator, the interior of the flooded evaporator is divided into a liquid inlet chamber, a liquid outlet chamber, and a heat exchange chamber by the two partitions, and a heat exchange component is arranged inside the heat exchange chamber; the heat exchange component comprises a first S-shaped heat exchange tube, a second S-shaped heat exchange tube, and a third S-shaped heat exchange tube, the first S-shaped heat exchange tube, the second S-shaped heat exchange tube, and the third S-shaped heat exchange tube are vertically spaced and distributed inside the heat exchange chamber, and the middle of the second S-shaped heat exchange tube is rotated at intervals. There are a plurality of wheel tubes, each of which is provided with an axial flow wheel inside, a plurality of first stirring components are respectively provided in a circumferential array at both ends of the outside of each wheel tube, a plurality of second stirring components are respectively provided in a circumferential array on both sides of the outside of each wheel tube near the middle, a hollow elastic member is connected between each of the first stirring components and the second stirring components, a first slider is provided at one end of each of the second stirring components, each of the first sliders slides in the outer wall of the wheel tube, a plurality of pairs of baffles are respectively provided on both sides of the lower part of the heat exchange chamber, an elliptical plate is fixedly provided in the middle of the outside of each wheel tube, two grooves are provided on the side close to each other of each pair of baffles, and the outer side of each elliptical plate is respectively in sliding contact with the inclined surface of one side of each pair of the grooves.

[0006] A further technical solution is that several pairs of baffles are staggered and distributed on both sides of the lower part of the heat exchange chamber, and the lower part of the heat exchange chamber forms an S-shaped channel through the several pairs of baffles, an exhaust pipe is connected between the compressor and the oil separator, an air pipe is connected between the oil separator and the condenser, a first liquid pipe is connected between the condenser and the flooded evaporator, a second liquid pipe is connected between the flooded evaporator and the dry evaporator, a first suction pipe is provided on one side of the dry evaporator, an electric three-way valve is provided at one end of the first suction pipe, a second suction pipe is connected between one end of the electric three-way valve and the compressor, a third suction pipe is connected between the other end of the electric three-way valve and the flooded evaporator, a water inlet pipe is provided on one side of the liquid inlet chamber, a water outlet pipe is provided on one side of the liquid outlet chamber, one end of the S-shaped channel in the lower part of the heat exchange chamber is connected to the first liquid pipe, the other end of the S-shaped channel in the lower part of the heat exchange chamber is connected to the second liquid pipe, and the upper part of the heat exchange chamber is connected to the third suction pipe.

[0007] A further technical solution is that the first stirring assembly includes a first stirring plate, a movable block is slidingly provided inside the first stirring plate, a second stirring plate is fixedly provided at one end of the movable block, two elastic fins are respectively connected to two sides of one end of the second stirring plate, a first spring is connected to one end of the movable block and the inside of the first stirring plate, the interior of the hollow elastic part and the interior of the first stirring plate are interconnected and a connecting channel is provided, the structure of the first stirring assembly is the same as that of the second stirring assembly, the first stirring plate in the first stirring assembly is fixedly connected to the outer wall of the wheel tube, and the first stirring plate in the second stirring assembly is in sliding contact with the outer wall of the wheel tube.

[0008] According to a further technical solution, two second sliders are fixedly provided on one side of each pair of the baffles, each pair of the second sliders slides in the side wall of the heat exchange cavity, and a second spring is connected between each pair of the second sliders.

[0009] According to a further technical solution, one end of the first S-shaped heat exchange tube is connected to the liquid inlet chamber, the other end of the first S-shaped heat exchange tube is connected to one end of the second S-shaped heat exchange tube, the other end of the second S-shaped heat exchange tube is connected to one end of the third S-shaped heat exchange tube, and the other end of the third S-shaped heat exchange tube is connected to the liquid outlet chamber.

[0010] According to a further technical solution, two annular parts are fixedly provided at both ends of each of the runner tubes, and each of the annular parts slides in an annular manner inside the tube wall of the second S-shaped heat exchange tube.

[0011] A further technical solution is that the first liquid pipe is provided with a drying filter, a first throttling device, and a first solenoid valve, the first throttling device is connected in parallel with the first solenoid valve, the second liquid pipe is provided with a second throttling device and a second solenoid valve, the second throttling device is connected in series with the second solenoid valve, the first intake pipe is provided with a first pressure sensor and a first temperature sensor, the first pressure sensor is connected in series with the first temperature sensor, the flooded evaporator is provided with a second pressure sensor and a second temperature sensor, the condenser is provided with a third pressure sensor, and the exhaust pipe is provided with a third temperature sensor.

[0012] A further technical solution is that a jet return oil pipe is provided on one side of the condenser, a jet pump is provided at one end of the jet return oil pipe, a third solenoid valve is provided on the jet return oil pipe, and the other two ends of the jet pump are respectively connected to the flooded evaporator and the second suction pipe. The jet pump uses the Venturi principle to form a negative pressure area inside the jet pump when the high-pressure refrigerant vapor in the flooded evaporator flows through the jet pump at high speed, thereby returning the low-pressure refrigeration oil fluid in the flooded evaporator to the compressor along the second suction pipe, completing the jet return oil.

[0013] A further technical solution is that a motor liquid spray pipe is connected between the first liquid pipe and the second intake pipe, a fourth solenoid valve and an expansion valve are provided on the motor liquid spray pipe, the fourth solenoid valve is connected in series with the expansion valve, an oil return pipe is connected between the oil separator and the second intake pipe, an air supply pipe is connected between the compressor and the full liquid evaporator, a fifth solenoid valve is provided on the air supply pipe, and in the high pressure ratio ice storage refrigeration condition, the fifth solenoid valve is opened to supply air to the compressor, thereby improving the energy efficiency of the compressor.

[0014] A control method for a dual-evaporator non-isothermal chiller comprises the following steps: S1: Mode selection: adjust the conventional cooling mode and ice storage mode of the air conditioner according to the peak and off-peak periods of power supply of the power grid, actively respond to energy-saving and carbon reduction policies, improve the cooling efficiency of the air-conditioning unit, and reduce the power supply load of the power grid; S2: Conventional cooling mode, using the flooded evaporator alone for air conditioning and cooling, giving full play to the high efficiency of the flooded evaporator; S3: Ice storage mode, using a combination of a flooded evaporator and a dry evaporator connected in series. At this time, the flooded evaporator acts as a liquid receiver and economizer to store abundant refrigerant, and compresses the compressor under ice storage and high compression ratio conditions, further improving the efficiency of the dry evaporator.

[0015] Compared with the prior art, the present invention has the following beneficial effects: The dual-evaporator non-isothermal chiller and control method thereof of the present invention can utilize a fully liquid-filled evaporator for efficient conventional air-conditioning refrigeration; and can also combine a fully liquid-filled evaporator and a dry evaporator for ice storage. The fully liquid-filled evaporator can be used as a liquid storage device and an economizer to further improve the efficiency of ice storage under high compression ratio conditions, fully combining the high energy efficiency advantage of the fully liquid-filled evaporator and the oil return advantage of the dry evaporator, thereby significantly saving energy.

[0016] The present invention discloses a dual-evaporator non-isothermal chiller and a control method thereof. Through the arrangement of a first S-shaped heat exchange tube, a second S-shaped heat exchange tube, a third S-shaped heat exchange tube and a baffle, the refrigerant enters one end of the S-shaped channel at the bottom of the heat exchange chamber through a first liquid pipe, and is staggeredly distributed on the two side walls of the heat exchange chamber through a plurality of pairs of baffles, so as to extend the flow distance of the refrigerant in the heat exchange chamber; and the chilled water enters the liquid inlet chamber through a water inlet pipe, and the chilled water in the liquid inlet chamber passes through the first S-shaped heat exchange tube, the second S-shaped heat exchange tube and the third S-shaped heat exchange tube in turn, so as to extend the flow distance of the chilled water in the heat exchange chamber, so that the chilled water and the refrigerant are fully in contact with each other for heat exchange, thereby improving the heat exchange efficiency of the full-liquid evaporator. Through the setting of the axial flow wheel and the wheel tube, the chilled water flows in the first S-shaped heat exchange tube, and the flow of the chilled water generates an impact force on the axial flow wheel, thereby causing the axial flow wheel and the wheel tube to rotate, thereby increasing the stroke of the chilled water in the second S-shaped heat exchange tube, further improving the heat exchange efficiency of the flooded evaporator.

[0017] The present invention discloses a dual-evaporator non-isothermal chiller and a control method thereof. Through the arrangement of the first stirring component and the second stirring component, the rotation of the rotary tube drives the first stirring components and the second stirring components to rotate, thereby stirring and mixing the refrigerant in the heat exchange chamber, avoiding uneven heating of the local refrigerant, and reducing the influence on the heat exchange efficiency of the chilled water. Then, through the arrangement of the elliptical plate, the outer side of the elliptical plate is respectively in sliding contact with the inclined surface of one side of the two grooves and under the elastic force of the second spring, the rotation of the rotary tube drives the rotation of the elliptical plate, so that the two baffles are alternately moved away from and approached to each other, so as to facilitate the refrigerant in the heat exchange chamber to fluctuate and mix back and forth, which is conducive to improving the stirring effect on the refrigerant. Then, through the arrangement of the hollow elastic member, the baffles are alternately moved away from and approached to each other, and the elastic force of the hollow elastic member is coordinated to make the second stirring component move back and forth along the axial direction of the rotary tube, so as to improve the stirring effect of the second stirring component on the refrigerant. Finally, through the arrangement of the second stirring plate, the movable block, the first spring, the first stirring plate, and the elastic fins, the second stirring component moves to squeeze the hollow elastic part, so that the solution in the hollow elastic part enters the first stirring plate through the connecting channel, thereby pushing the movable block and the second stirring plate to move radially outward; the radial outward movement of the second stirring plate cooperates with the radial fixation of the first stirring plate, thereby stretching the two elastic fins to increase the area with the refrigerant, so as to increase the contact area of ​​the first stirring component and the second stirring component for stirring the refrigerant, and improve the stirring effect of the first stirring component and the second stirring component on the refrigerant, which is beneficial to avoid uneven heating of the refrigerant and improve the heat exchange efficiency of the full-liquid evaporator. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0019] The present invention is further described below in conjunction with the accompanying drawings and embodiments.

[0020] Figure 1 It is a structural schematic diagram of the present invention; Figure 2 It is an isometric structural schematic diagram of the present invention; Figure 3 It is a front view structural schematic diagram of the present invention; Figure 4 for Figure 3 Schematic diagram of the cross-sectional structure at AA in the middle; Figure 5 for Figure 4 The structural schematic diagram of the local enlarged view at D in the middle; Figure 6 for Figure 4 The structural schematic diagram of the local enlarged view at E in the middle; Figure 7 It is a left-side structural schematic diagram of the present invention; Figure 8 for Figure 7 Schematic diagram of the cross-sectional structure at the middle BB; Fig. 9 for Figure 8 The structural schematic diagram of the local enlarged view at F in the middle; Fig.10 for Figure 7 Schematic diagram of the cross-sectional structure at CC in the middle.

[0021] Description of reference numerals: Box 10, compressor 11, oil separator 12, condenser 13, flooded evaporator 14, dry evaporator 15, air pipe 16, first liquid pipe 17, second liquid pipe 18, first suction pipe 19, electric three-way valve 20, second suction pipe 21, third suction pipe 22, exhaust pipe 23, dry filter 24, first throttling device 25, first solenoid valve 26, second throttling device 27, second solenoid valve 28, first pressure sensor 29, first temperature sensor 30, second pressure sensor 31, second temperature sensor 32, third temperature sensor 33, third pressure sensor 34, injection oil return pipe 35, third solenoid valve 36, injection pump 37, motor liquid spray pipe 38, fourth Solenoid valve 39, expansion valve 40, oil return pipe 41, air supply pipe 42, fifth solenoid valve 43, water inlet pipe 44, water outlet pipe 45, partition 48, liquid inlet chamber 49, liquid outlet chamber 50, heat exchange chamber 51, first S-type heat exchange tube 52, second S-type heat exchange tube 53, third S-type heat exchange tube 54, baffle 55, second slider 56, second spring 57, runner tube 58, annular member 59, first stirring assembly 60, second stirring assembly 61, hollow elastic member 62, elliptical plate 63, axial flow runner 64, first slider 65, first stirring plate 66, movable block 67, second stirring plate 68, first spring 69, elastic fin 70, connecting channel 71, condensing fan 72, groove 73. DETAILED DESCRIPTION

[0022] The following embodiments of the present invention are described in further detail in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0023] In the description of the present invention, unless otherwise specified, "plurality" means two or more than two; the orientations or positional relationships indicated by the terms "upper", "lower", "left", "right", "inner", "outer", "front end", "rear end", "head", "tail", etc. are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", "third", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0024] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "connected" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0025] As attached Figure 1 To Attachment Fig.10 As shown: The invention provides a dual-evaporator non-isothermal type chiller and a control method thereof.

[0026] See attached Figure 1 To Attachment Fig.10 , including a box body 10, a compressor 11, an oil separator 12, a flooded evaporator 14, and a dry evaporator 15 are arranged on the lower side of the box body 10, a condenser 13 is arranged on the upper side of the box body 10, two condensing fans 72 are arranged on the upper end of the box body 10, two partitions 48 are symmetrically arranged inside the flooded evaporator 14, and the inside of the flooded evaporator 14 is divided into a liquid inlet chamber 49, a liquid outlet chamber 50, and a heat exchange chamber 51 by the two partitions 48, and a heat exchange component is arranged inside the heat exchange chamber 51; the heat exchange component includes a first S-type heat exchange tube 52, a second S-type heat exchange tube 53, and a third S-type heat exchange tube 54, the first S-type heat exchange tube 52, the second S-type heat exchange tube 53, and the third S-type heat exchange tube 54 are vertically spaced and distributed inside the heat exchange chamber 51, and the middle part of the second S-type heat exchange tube 53 is rotated and provided with a plurality of rotating parts. The wheel tube 58 has an axial flow impeller 64 disposed inside each impeller tube 58. A plurality of first stirring assemblies 60 are disposed in a circumferential array at both ends of the outside of each impeller tube 58. A plurality of second stirring assemblies 61 are disposed in a circumferential array on both sides of the outside of each impeller tube 58 near the middle. A hollow elastic member 62 is connected between each first stirring assembly 60 and the second stirring assembly 61. A first slider 65 is disposed at one end of each second stirring assembly 61. Each first slider 65 slides inside the outer wall of the impeller tube 58. A plurality of pairs of baffles 55 are disposed on both sides of the lower part of the heat exchange chamber 51. An elliptical plate 63 is fixedly disposed in the middle of the outside of each impeller tube 58. Two grooves 73 are disposed on the side close to each other of each pair of baffles 55. The outer side of each elliptical plate 63 is in sliding contact with the inclined surface of one side of each pair of grooves 73.

[0027] Preferably, see Attachment Figure 1 , Attachment Figure 4 To Attachment Figure 6 , Attachment Figure 8 , Attachment Fig.10A plurality of pairs of baffles 55 are staggered and distributed on both sides of the lower part of the heat exchange chamber 51. The lower part of the heat exchange chamber 51 forms an S-shaped channel through the plurality of pairs of baffles 55. An exhaust pipe 23 is connected between the compressor 11 and the oil separator 12. An air pipe 16 is connected between the oil separator 12 and the condenser 13. A first liquid pipe 17 is connected between the condenser 13 and the flooded evaporator 14. A second liquid pipe 18 is connected between the flooded evaporator 14 and the dry evaporator 15. A first suction pipe 19 is provided on one side of the dry evaporator 15. The first suction pipe 19 is connected to the first suction pipe 17. 9 is provided with an electric three-way valve 20, a second suction pipe 21 is connected between one end of the electric three-way valve 20 and the compressor 11, a third suction pipe 22 is connected between the other end of the electric three-way valve 20 and the flooded evaporator 14, a water inlet pipe 44 is provided on one side of the liquid inlet chamber 49, a water outlet pipe 45 is provided on one side of the liquid outlet chamber 50, one end of the lower S-shaped channel of the heat exchange chamber 51 is connected to the first liquid pipe 17, the other end of the lower S-shaped channel of the heat exchange chamber 51 is connected to the second liquid pipe 18, and the upper part of the heat exchange chamber 51 is connected to the third suction pipe 22.

[0028] Preferably, see Attachment Figure 4 To Attachment Figure 6 The first stirring component 60 includes a first stirring plate 66, a movable block 67 is slidably provided inside the first stirring plate 66, a second stirring plate 68 is fixedly provided at one end of the movable block 67, two elastic fins 70 are respectively connected to the two sides of one end of the first stirring plate 66 and the two sides of one end of the second stirring plate 68, a first spring 69 is connected to the inside of the first stirring plate 66 at one end of the movable block 67, the interior of the hollow elastic member 62 and the interior of the first stirring plate 66 are interconnected and a connecting channel 71 is provided. The structure of the first stirring component 60 is the same as that of the second stirring component 61. The difference between the first stirring component 60 and the second stirring component 61 is that the first stirring plate 66 in the first stirring component 60 is fixedly connected to the outer wall of the wheel tube 58, and the first stirring plate 66 in the second stirring component 61 is in sliding contact with the outer wall of the wheel tube 58.

[0029] Preferably, see Attachment Figure 6 Two second sliders 56 are fixedly provided on one side of each pair of baffles 55 , and each pair of second sliders 56 slides in the side wall of the heat exchange chamber 51 . A second spring 57 is connected between each pair of second sliders 56 .

[0030] Preferably, see Attachment Figure 8 To Attachment Fig. 9 One end of the first S-type heat exchange tube 52 is connected to the liquid inlet chamber 49, the other end of the first S-type heat exchange tube 52 is connected to one end of the second S-type heat exchange tube 53, the other end of the second S-type heat exchange tube 53 is connected to one end of the third S-type heat exchange tube 54, and the other end of the third S-type heat exchange tube 54 is connected to the liquid outlet chamber 50.

[0031] Preferably, see Attachment Figure 4 Two annular members 59 are fixedly provided at both ends of each runner tube 58 , and each annular member 59 slides in an annular manner inside the tube wall of the second S-shaped heat exchange tube 53 .

[0032] Preferably, see Attachment Figure 1 A drying filter 24, a first throttling device 25 and a first solenoid valve 26 are provided on the first liquid pipe 17, and the first throttling device 25 is connected in parallel with the first solenoid valve 26. A second throttling device 27 and a second solenoid valve 28 are provided on the second liquid pipe 18, and the second throttling device 27 and the second solenoid valve 28 are connected in series. A first pressure sensor 29 and a first temperature sensor 30 are provided on the first intake pipe 19, and the first pressure sensor 29 is connected in series with the first temperature sensor 30. A second pressure sensor 31 and a second temperature sensor 32 are provided on the flooded evaporator 14, a third pressure sensor 34 is provided on the condenser 13, and a third temperature sensor 33 is provided on the exhaust pipe 23.

[0033] Preferably, see Attachment Figure 1 A jet return oil pipe 35 is provided on one side of the condenser 13, a jet pump 37 is provided at one end of the jet return oil pipe 35, a third solenoid valve 36 is provided on the jet return oil pipe 35, and the other two ends of the jet pump 37 are respectively connected to the flooded evaporator 14 and the second suction pipe 21. The jet pump 37 uses the Venturi principle to form a negative pressure area inside the jet pump 37 when the high-pressure refrigerant vapor in the flooded evaporator 14 flows through the jet pump 37 at a high speed, thereby returning the low-pressure refrigeration oil fluid in the flooded evaporator 14 to the compressor 11 along the second suction pipe 21, completing the jet return oil.

[0034] Preferably, see Attachment Figure 1 A motor liquid spray pipe 38 is connected between the first liquid pipe 17 and the second suction pipe 21, and a fourth solenoid valve 39 and an expansion valve 40 are provided on the motor liquid spray pipe 38. The fourth solenoid valve 39 and the expansion valve 40 are connected in series. An oil return pipe 41 is connected between the oil separator 12 and the second suction pipe 21. An air supply pipe 42 is connected between the compressor 11 and the flooded evaporator 14. A fifth solenoid valve 43 is provided on the air supply pipe 42. In the high pressure ratio ice storage refrigeration condition, the fifth solenoid valve 43 is opened to supply air to the compressor 11, thereby improving the energy efficiency of the compressor 11.

[0035] A control method for a dual-evaporator non-isothermal chiller, comprising the following steps: S1: Mode selection: adjust the conventional cooling mode and ice storage mode of the air conditioner according to the peak and off-peak periods of power supply of the power grid, actively respond to energy-saving and carbon reduction policies, improve the cooling efficiency of the air-conditioning unit, and reduce the power supply load of the power grid; S2: Conventional cooling mode, using the flooded evaporator alone for air conditioning and cooling, giving full play to the high efficiency of the flooded evaporator; S3: Ice storage mode, using a combination of a flooded evaporator and a dry evaporator connected in series. At this time, the flooded evaporator acts as a liquid receiver and economizer to store abundant refrigerant, and compresses the compressor under ice storage and high compression ratio conditions, further improving the efficiency of the dry evaporator.

[0036] Specific use of the present invention: When the machine is turned on and the cooling mode is selected, the control system automatically adjusts the opening direction of the electric three-way valve 20, so that the third suction pipe 22 is connected to the second suction pipe 21, and the first suction pipe 19 is disconnected from the second suction pipe 21; the control system closes the first solenoid valve 26 and the second solenoid valve 28, and opens the first throttling device 25 and the third solenoid valve 36, so that the compressor 11 is directly connected to the flooded evaporator 14. The high-temperature and high-pressure refrigeration steam from the compressor 11 enters the oil separator 12 through the exhaust pipe 23, then enters the condenser 13 through the air pipe 16, and then enters the flooded evaporator 14 through the first liquid pipe 17 for heat exchange and cooling, and finally returns to the compressor 11 through the third suction pipe 22 and the second suction pipe 21, realizing the steam compression cycle of normal temperature refrigeration conditions. At the same time, the data detected by the first pressure sensor 29, the first temperature sensor 30, the third temperature sensor 33, and the third pressure sensor 34 are compared and intelligently analyzed, so that the control system controls the first throttling device 25 to adjust the flow of the refrigerant liquid, so as to control the outlet water temperature of the full-liquid evaporator 14. At the same time, the third solenoid valve 36 is opened from time to time to guide the refrigeration oil deposited inside the full-liquid evaporator 14 back to the compressor 11, ensuring the normal oil circulation of the compressor 11, and also reducing the excessive refrigeration oil inside the heat exchanger, which affects the heat exchange efficiency of the heat exchanger. In the cooling mode, the full-liquid evaporator 14 is used alone for air conditioning refrigeration, and the high efficiency of the full-liquid evaporator 14 is brought into play.

[0037] When the ice storage mode is selected, the control system automatically adjusts the opening direction of the electric three-way valve 20, so that the first air intake pipe 19 is connected to the second air intake pipe 21, and the third air intake pipe 22 is disconnected from the second air intake pipe 21; the control system controls the first solenoid valve 26 and the second solenoid valve 28 to open, and the first throttling device 25 and the third solenoid valve 36 to close, that is, the dry evaporator 15 is connected to the compressor 11. The high-temperature and high-pressure refrigeration steam coming out of the compressor 11 enters the oil separator 12 through the exhaust pipe 23, then enters the condenser 13 through the air pipe 16, and then enters the full-liquid evaporator 14 through the first liquid pipe 17, and then enters the dry evaporator 15 through the second liquid pipe 18, and finally returns to the compressor 11 through the first air intake pipe 19 and the second air intake pipe 21, completing the ice storage working condition. At the same time, the second throttling device 27 is intelligently controlled by the data detected by the first temperature sensor 30 and the first pressure sensor 29, and the second throttling device 27 adjusts the flow rate of the refrigerant to control the outlet water temperature of the dry evaporator 15. At the same time, when the evaporation temperature is low, the control system controls the fifth solenoid valve 43 to open, and adjusts the expansion valve 40 according to the exhaust temperature to cool the motor, ensuring that the compressor 11 operates within the normal temperature range. In the ice storage mode, the full liquid evaporator 14 and the dry evaporator 15 are connected in series in sequence. At this time, the full liquid evaporator 14 acts as a liquid storage device and an economizer to store abundant refrigerant, and compresses the compressor 11 under the high compression ratio of ice storage, further improving the efficiency of the dry evaporator 15.

[0038] When the chilled water enters the flooded evaporator 14 through the water inlet pipe 44, the refrigerant enters one end of the S-shaped channel at the bottom of the heat exchange chamber 51 through the first liquid pipe 17, and is staggered and distributed on both side walls of the heat exchange chamber 51 through a plurality of pairs of baffles 55, so as to extend the flow of the refrigerant in the heat exchange chamber 51, and then the refrigerant in the heat exchange chamber 51 enters the dry evaporator 15 through the second liquid pipe 18. The refrigeration steam in the heat exchange chamber 51 returns to the compressor 11 through the third suction pipe 22 and the second suction pipe 21, realizing the steam compression cycle of the normal temperature refrigeration condition.

[0039] At the same time, the chilled water enters the liquid inlet chamber 49 through the water inlet pipe 44, and the chilled water in the liquid inlet chamber 49 passes through the first S-type heat exchange tube 52, the second S-type heat exchange tube 53, and the third S-type heat exchange tube 54 in turn, so as to extend the flow distance of the chilled water in the heat exchange chamber 51, so that the chilled water and the refrigerant are fully in contact for heat exchange, thereby improving the heat exchange efficiency of the full liquid evaporator 14.

[0040] Secondly, when the chilled water flows in the first S-shaped heat exchange tube 52, the flow of the chilled water generates an impact force on the axial flow rotor 64, thereby rotating the axial flow rotor 64 and the rotor tube 58, so that the stroke of the chilled water in the second S-shaped heat exchange tube 53 is increased, further improving the heat exchange efficiency of the flooded evaporator 14. At the same time, the rotation of the rotor tube 58 drives the two annular members 59 to slide in an annular manner in the tube wall of the second S-shaped heat exchange tube 53, so that the rotor tube 58 rotates smoothly. The rotation of the rotor tube 58 drives the first stirring components 60 and the second stirring components 61 to rotate, thereby stirring and mixing the refrigerant in the heat exchange chamber 51, avoiding uneven heating of the local refrigerant, and reducing the impact on the heat exchange efficiency of the chilled water.

[0041] Next, the runner tube 58 rotates to drive the elliptical plate 63 to rotate, and the outer side of the elliptical plate 63 slides in contact with the inclined surfaces of one side of the two grooves 73, and guides the two baffles 55 at the end of the larger diameter of the elliptical plate 63, so that the two baffles 55 move away from each other. The two baffles 55 move away from each other, and the two second sliders 56 move away from each other to stretch the second spring 57 to generate elastic force. When the end of the elliptical plate 63 with a smaller diameter contacts the two grooves 73, the two baffles 55 are brought closer to each other under the elastic force of the two second springs 57, so that the outer side of the elliptical plate 63 slides in contact with the inclined surfaces of one side of the two grooves 73 and the elastic force of the second springs 57, the runner tube 58 rotates to drive the elliptical plate 63 to rotate, so that the two baffles 55 move away from each other and move closer to each other alternately, so that the refrigerant in the heat exchange chamber 51 is mixed back and forth, which is conducive to improving the stirring effect on the refrigerant.

[0042] Then, the baffles 55 move away from each other and approach each other alternately, and the baffles 55 move away from each other to push the pairs of second stirring components 61 away from each other, so that the second stirring components 61 are close to the first stirring components 60, and the second stirring components 61 move to drive the first slider 65 to move to squeeze and compress the hollow elastic member 62, and the hollow elastic member 62 is compressed to generate elastic force. When the baffles 55 approach each other, the second stirring components 61 are moved away from the first stirring components 60 under the elastic force of the hollow elastic member 62, so that the baffles 55 move away from each other and approach each other alternately, and the elastic force of the hollow elastic member 62 is coordinated to make the second stirring components 61 move back and forth along the axial direction of the impeller tube 58, so as to improve the stirring effect of the second stirring components 61 on the refrigerant.

[0043] At the same time, the second stirring component 61 approaches the first stirring component 60, and the second stirring component 61 moves to squeeze the hollow elastic member 62, so that the solution in the hollow elastic member 62 enters the first stirring plate 66 through the connecting channel 71, thereby pushing the movable block 67 and the second stirring plate 68 to move radially outward. The second stirring plate 68 moves radially outward to cooperate with the radial fixation of the first stirring plate 66, so as to stretch the two elastic fins 70 to increase the area with the refrigerant, so as to increase the area of ​​the first stirring component 60 and the second stirring component 61 for stirring the refrigerant, and improve the stirring effect of the first stirring component 60 and the second stirring component 61 on the refrigerant. The movable block 67 moves radially outward to stretch the first spring 69 to generate elastic force. The second stirring component 61 is away from the first stirring component 60, and the hollow elastic member 62 restores its shape under the action of elastic force, thereby sucking the solution in the first stirring plate 66 back into the hollow elastic member 62 through the connecting channel 71, and the movable block 67 and the second stirring plate 68 are driven by the elastic force of the first spring 69 to move radially inward, so that the second stirring component 61 moves back and forth to squeeze or relax the hollow elastic member 62 to cooperate with the elastic force of the first spring 69, so that the second stirring plate 68 moves radially back and forth, thereby improving the stirring effect of the first stirring component 60 and the second stirring component 61 on the refrigerant, which is beneficial to avoid uneven heating of the refrigerant and improve the heat exchange efficiency of the flooded evaporator 14.

[0044] Finally, the chilled water enters the liquid outlet chamber 50 through the third S-shaped heat exchange tube 54 , and the chilled water in the liquid outlet chamber 50 is discharged through the water outlet pipe 45 .

[0045] The dual-evaporator non-isothermal chiller and control method thereof of the present invention can utilize the flooded evaporator 14 to perform efficient conventional air-conditioning refrigeration; and can also combine the flooded evaporator 14 and the dry evaporator 15 to perform ice storage. The flooded evaporator 14 can be used as a liquid storage device and an economizer to further improve the efficiency of ice storage under high compression ratio conditions, and fully combine the high energy efficiency advantage of the flooded evaporator 14 and the oil return advantage of the dry evaporator 15, thereby significantly saving energy.

[0046] The present invention provides a dual-evaporator non-isothermal chiller and a control method thereof. Through the arrangement of a first S-shaped heat exchange tube 52, a second S-shaped heat exchange tube 53, a third S-shaped heat exchange tube 54, and a baffle 55, the refrigerant enters one end of the S-shaped channel at the bottom of a heat exchange chamber 51 through a first liquid pipe 18, and is staggeredly distributed on the two side walls of the heat exchange chamber 51 through a plurality of pairs of baffles 55, so as to extend the flow distance of the refrigerant in the heat exchange chamber 51; and the chilled water enters the liquid inlet chamber 49 through a water inlet pipe 44, and the chilled water in the liquid inlet chamber 49 passes through the first S-shaped heat exchange tube 52, the second S-shaped heat exchange tube 53, and the third S-shaped heat exchange tube 54 in turn, so as to extend the flow distance of the chilled water in the heat exchange chamber 51, so that the chilled water and the refrigerant are fully in contact with each other for heat exchange, thereby improving the heat exchange efficiency of the full-liquid evaporator 14. Through the setting of the axial flow wheel 64 and the wheel tube 58, the chilled water flows in the first S-shaped heat exchange tube 52, and the flow of the chilled water generates an impact force on the axial flow wheel 64, thereby causing the axial flow wheel 64 and the wheel tube 58 to rotate, thereby increasing the stroke of the chilled water in the second S-shaped heat exchange tube 53, further improving the heat exchange efficiency of the full liquid evaporator 14.

[0047] The present invention provides a dual-evaporator non-isothermal chiller and a control method thereof. Through the arrangement of the first stirring assembly 60 and the second stirring assembly 61, the runner tube 58 rotates to drive the first stirring assembly 60 and the second stirring assembly 61 to rotate, thereby stirring and mixing the refrigerant in the heat exchange chamber 51, avoiding uneven heating of the local refrigerant and reducing the influence on the heat exchange efficiency of the chilled water. Then, through the arrangement of the elliptical plate 63, the outer side of the elliptical plate 63 is in sliding contact with the inclined surface of one side of the two grooves 73 respectively and under the elastic force of the second spring 57, the runner tube 58 rotates to drive the elliptical plate 63 to rotate, so that the two baffles 55 are alternately moved away from and close to each other, so as to facilitate the back and forth mixing of the refrigerant in the heat exchange chamber 51, which is beneficial to improve the stirring effect on the refrigerant. Then, by setting the hollow elastic member 62, the baffles 55 move away from and towards each other alternately, and under the elastic force of the hollow elastic member 62, the second stirring component 61 moves back and forth along the axial direction of the impeller tube 58, so as to enhance the stirring effect of the second stirring component 61 on the refrigerant. Finally, through the arrangement of the second stirring plate 68, the movable block 67, the first spring 69, the first stirring plate 66, and the elastic fins 70, the second stirring component 61 moves to squeeze the hollow elastic member 62, so that the solution in the hollow elastic member 62 enters the first stirring plate 66 through the connecting channel 71, thereby pushing the movable block 67 and the second stirring plate 68 to move radially outward; the second stirring plate 68 moves radially outward to cooperate with the radial fixation of the first stirring plate 66, thereby stretching the two elastic fins 70 to increase the area with the refrigerant, so as to increase the area of ​​the first stirring component 60 and the second stirring component 61 contacting with the refrigerant, and improve the stirring effect of the first stirring component 60 and the second stirring component 61 on the refrigerant, which is beneficial to avoid uneven heating of the refrigerant and improve the heat exchange efficiency of the full liquid evaporator 14.

[0048] The embodiments of the present invention are given for the purpose of illustration and description, and are not intended to be exhaustive or to limit the invention to the disclosed forms. Many modifications and variations will be apparent to those of ordinary skill in the art. The embodiments are selected and described in order to better illustrate the principles and practical applications of the present invention and to enable those of ordinary skill in the art to understand the present invention and thereby design various embodiments with various modifications suitable for specific uses.

Claims

1. A dual-evaporator non-isothermal chiller, characterized in that: The invention comprises a casing (10), wherein a compressor (11), an oil separator (12), a flooded evaporator (14), and a dry evaporator (15) are arranged on the lower side of the casing (10), a condenser (13) is arranged on the upper side of the casing (10), two condensing fans (72) are arranged at the upper end of the casing (10), two partitions (48) are symmetrically arranged inside the flooded evaporator (14), and the inside of the flooded evaporator (14) is divided into a liquid inlet chamber (49), a liquid outlet chamber (50), and a heat exchange chamber (51) by the two partitions (48), and a heat exchange component is arranged inside the heat exchange chamber (51); The heat exchange assembly comprises a first S-shaped heat exchange tube (52), a second S-shaped heat exchange tube (53), and a third S-shaped heat exchange tube (54); the first S-shaped heat exchange tube (52), the second S-shaped heat exchange tube (53), and the third S-shaped heat exchange tube (54) are vertically spaced and distributed inside the heat exchange chamber (51); a plurality of rotor tubes (58) are rotatably arranged at intervals in the middle of the second S-shaped heat exchange tube (53); an axial flow rotor (64) is arranged inside each of the rotor tubes (58); a plurality of first stirring assemblies (60) are arranged in a circumferential array at both ends of the outside of each of the rotor tubes (58); and a plurality of second stirring assemblies (60) are arranged in a circumferential array at both sides of the outside of each of the rotor tubes (58) near the middle. A hollow elastic member (62) is provided between each of the first stirring members (60) and the second stirring members (61), a first sliding block (65) is provided at one end of each of the second stirring members (61), and each of the first sliding blocks (65) slides inside the outer wall of the impeller tube (58), a plurality of pairs of baffles (55) are provided on both sides of the lower part of the heat exchange chamber (51), an elliptical plate (63) is fixedly provided in the middle of the outer part of each of the impeller tubes (58), two grooves (73) are provided on the side close to each other of each pair of the baffles (55), and the outer side of each of the elliptical plates (63) is in sliding contact with the inclined surface of one side of each pair of the grooves (73).

2. A dual-evaporator non-isothermal chiller according to claim 1, characterized in that: A plurality of pairs of baffles (55) are staggered and distributed on both sides of the lower part of the heat exchange chamber (51); the lower part of the heat exchange chamber (51) forms an S-shaped channel through the plurality of pairs of baffles (55); an exhaust pipe (23) is connected between the compressor (11) and the oil separator (12); an air pipe (16) is connected between the oil separator (12) and the condenser (13); a first liquid pipe (17) is connected between the condenser (13) and the flooded evaporator (14); a second liquid pipe (18) is connected between the flooded evaporator (14) and the dry evaporator (15); a first air intake pipe (19) is provided on one side of the dry evaporator (15); and the first air intake pipe (19) is connected to the condenser (13); and the second liquid pipe (18) is connected to the dry evaporator (15). An electric three-way valve (20) is provided at one end of the heat exchange chamber (19); a second air intake pipe (21) is connected between one end of the electric three-way valve (20) and the compressor (11); a third air intake pipe (22) is connected between the other end of the electric three-way valve (20) and the flooded evaporator (14); a water inlet pipe (44) is provided on one side of the liquid inlet chamber (49); a water outlet pipe (45) is provided on one side of the liquid outlet chamber (50); one end of the lower S-shaped channel of the heat exchange chamber (51) is connected to the first liquid pipe (17); the other end of the lower S-shaped channel of the heat exchange chamber (51) is connected to the second liquid pipe (18); and the upper part of the heat exchange chamber (51) is connected to the third air intake pipe (22).

3. A dual-evaporator non-isothermal chiller according to claim 1, characterized in that: The first stirring assembly (60) comprises a first stirring plate (66), a movable block (67) is slidably provided inside the first stirring plate (66), a second stirring plate (68) is fixedly provided at one end of the movable block (67), two elastic fins (70) are respectively connected to two ends of one end of the first stirring plate (66) and two ends of one end of the second stirring plate (68), a first spring (69) is provided at one end of the movable block (67) and is connected to the inside of the first stirring plate (66), the inside of the hollow elastic member (62) and the inside of the first stirring plate (66) are mutually connected and a connecting channel (71) is provided, the structure of the first stirring assembly (60) is the same as that of the second stirring assembly (61), the first stirring plate (66) in the first stirring assembly (60) is fixedly connected to the outer wall of the wheel tube (58), and the first stirring plate (66) in the second stirring assembly (61) is in sliding contact with the outer wall of the wheel tube (58).

4. A dual-evaporator non-isothermal chiller according to claim 1, characterized in that: Two second sliders (56) are fixedly provided on one side of each pair of baffles (55), each pair of the second sliders (56) slides in the side wall of the heat exchange chamber (51), and a second spring (57) is connected between each pair of the second sliders (56).

5. A dual-evaporator non-isothermal chiller according to claim 2, characterized in that: One end of the first S-shaped heat exchange tube (52) is connected to the liquid inlet chamber (49), the other end of the first S-shaped heat exchange tube (52) is connected to one end of the second S-shaped heat exchange tube (53), the other end of the second S-shaped heat exchange tube (53) is connected to one end of the third S-shaped heat exchange tube (54), and the other end of the third S-shaped heat exchange tube (54) is connected to the liquid outlet chamber (50).

6. The dual-evaporator non-isothermal chiller according to claim 1, characterized in that: Two annular components (59) are fixedly provided at both ends of each of the runner tubes (58), and each of the annular components (59) slides in an annular manner inside the tube wall of the second S-shaped heat exchange tube (53).

7. The dual-evaporator non-isothermal chiller according to claim 5, characterized in that: The first liquid pipe (17) is provided with a drying filter (24), a first throttling device (25), and a first solenoid valve (26), the first throttling device (25) and the first solenoid valve (26) being connected in parallel, the second liquid pipe (18) is provided with a second throttling device (27) and a second solenoid valve (28), the second throttling device (27) and the second solenoid valve (28) being connected in series, the first intake pipe (19) is provided with a first pressure sensor (29) and a first temperature sensor (30), the first pressure sensor (29) and the first temperature sensor (30) being connected in series, the flooded evaporator (14) is provided with a second pressure sensor (31) and a second temperature sensor (32), the condenser (13) is provided with a third pressure sensor (34), and the exhaust pipe (23) is provided with a third temperature sensor (33).

8. The dual-evaporator non-isothermal chiller according to claim 5, characterized in that: An injection oil return pipe (35) is provided on one side of the condenser (13), an injection pump (37) is provided at one end of the injection oil return pipe (35), a third solenoid valve (36) is provided on the injection oil return pipe (35), and the other two ends of the injection pump (37) are respectively connected to the flooded evaporator (14) and the second suction pipe (21).

9. The dual-evaporator non-isothermal chiller according to claim 5, characterized in that: A motor liquid spray pipe (38) is connected between the first liquid pipe (17) and the second air intake pipe (21), and a fourth solenoid valve (39) and an expansion valve (40) are provided on the motor liquid spray pipe (38). The fourth solenoid valve (39) and the expansion valve (40) are connected in series. An oil return pipe (41) is connected between the oil separator (12) and the second air intake pipe (21). An air supply pipe (42) is connected between the compressor (11) and the flooded evaporator (14), and a fifth solenoid valve (43) is provided on the air supply pipe (42).

10. A control method for a dual-evaporator non-isothermal chiller, characterized in that: The following steps are involved: S1: Mode selection: adjust the conventional cooling mode and ice storage mode of the air conditioner according to the peak and off-peak periods of power supply of the power grid, actively respond to energy-saving and carbon reduction policies, improve the cooling efficiency of the air-conditioning unit, and reduce the power supply load of the power grid; S2: Conventional cooling mode, using the flooded evaporator alone for air conditioning and cooling, giving full play to the high efficiency of the flooded evaporator; S3: Ice storage mode, using a combination of a flooded evaporator and a dry evaporator connected in series. At this time, the flooded evaporator acts as a liquid receiver and economizer to store abundant refrigerant, and compresses the compressor under ice storage and high compression ratio conditions, further improving the efficiency of the dry evaporator.

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