Miniature refrigerant fluorine pump and air conditioning system

Abstract

The invention discloses a miniature refrigerant fluorine pump and an air conditioning system. The miniature refrigerant fluorine pump comprises an inner rotor and an outer rotor, and the inner rotor and the outer rotor are eccentrically arranged; the inner rotor comprises a rotor body and first worm claw parts which are uniformly distributed along the outer circumference of the rotor body, and every two adjacent first worm claw parts are matched to form a first cavity; the outer rotor comprises a rotor outer ring of a closed structure and second worm claw parts evenly distributed along the inner circumference of the rotor outer ring, and every two adjacent second worm claw parts are matched to form a second cavity. When the inner rotor drives the first worm claw part to do eccentric reciprocating motion along the second cavity, the second worm claw part of the outer rotor does the same eccentric reciprocating motion along the first cavity, and fluid flows between the first cavity and the second cavity. Frictional wear between the inner rotor and the outer rotor of the fluorine pump can be reduced, noise in the operation process is reduced, heat dissipation is facilitated, the influence of temperature on fluid is reduced, meanwhile, the conveying amount of the fluid is increased, and the utilization rate of the fluid is higher.

Description

Technical Field

[0001] The invention relates to a micro refrigerant fluorine pump and an air-conditioning system. Background Art

[0002] With the development of society, air conditioners are becoming more and more popular in our lives. Whether at home or on the road, air conditioners are an important device to provide a comfortable environment. Therefore, air conditioners are becoming more and more indispensable equipment in our lives.

[0003] The fluorine pump is an important component of the air-conditioning system, and its performance directly determines the operating status of the air-conditioning system.

[0004] The fluorine pump in the prior art needs to have two rotors in contact with each other, which will generate heat due to friction and wear. This not only reduces the service life, but is also not conducive to heat dissipation, resulting in low fluid utilization and small delivery volume. Summary of the Invention

[0005] The purpose of the present invention is to provide a technical solution for a micro refrigerant fluorine pump and an air-conditioning system to address the deficiencies in the prior art. The technical solution not only reduces the friction and wear between the inner rotor and the outer rotor of the micro refrigerant fluorine pump and reduces the noise during operation, but also facilitates heat dissipation and reduces the impact of temperature on the fluid. At the same time, it increases the fluid delivery rate and makes the fluid utilization rate higher.

[0006] In order to solve the above technical problems, the present invention adopts the following technical solutions: A micro refrigerant fluorine pump, comprising inner rotor; and an outer rotor, wherein the inner rotor and the outer rotor are eccentrically arranged; Its characteristics are: The inner rotor includes a rotor body and at least three first worm claws evenly distributed along the outer circumference of the rotor body, and two adjacent first worm claws cooperate to form a first chamber; The outer rotor includes a rotor outer ring with a closed structure and at least three second worm claws evenly distributed along the inner circumference of the rotor outer ring, wherein two adjacent second worm claws cooperate to form a second chamber, and the second chamber is communicated with the first chamber. When the inner rotor drives the first worm claw portion to perform eccentric reciprocating motion along the second chamber, the second worm claw portion of the outer rotor performs the same eccentric reciprocating motion along the first chamber, thereby achieving fluid flow between the first chamber and the second chamber.

[0007] Through the design of the above structure, not only can the friction and wear between the inner rotor and the outer rotor of the micro refrigerant fluorine pump be reduced, and the noise during operation be reduced, but it is also beneficial to heat dissipation, reducing the impact of temperature on the fluid, while increasing the fluid delivery volume and making the fluid utilization rate higher.

[0008] Furthermore, the first worm claw portion and the second worm claw portion both have a curved structure and are arranged in opposite directions. The curved structure can be arc-shaped or L-shaped. When the first worm claw portion bends in the clockwise direction, the second worm claw portion bends in the counterclockwise direction, or when the first worm claw portion bends in the counterclockwise direction, the second worm claw portion bends in the clockwise direction, ensuring that when the inner rotor rotates, the first worm claw portion and the second worm claw portion move synchronously, thereby achieving efficient fluid transportation.

[0009] Furthermore, the first worm claw portion includes a first outer meshing section and a first inner meshing section and a first transition section formed by the rotor body extending and bending outward. The first outer meshing section is connected to the first inner meshing section through the first transition section. The first outer meshing section and the first inner meshing section are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0010] Furthermore, the first chamber is formed by the first outer meshing section of the previous first worm claw portion being recessed inward through the second transition section and connected to the first inner meshing section of the subsequent first worm claw portion. A first notch is formed between the two adjacent first worm claw portions for the second worm claw portion to extend into the first chamber, thereby improving the meshing efficiency between the inner rotor and the outer rotor and further improving the utilization rate of the fluid.

[0011] Furthermore, the sizes of the first notch and the first chamber are larger than those of the second worm claw portion, which facilitates the flow of fluid between the first chamber and the second chamber.

[0012] Furthermore, the second worm claw portion includes a second inner meshing section and a second outer meshing section and a fourth transition section formed by the outer ring of the rotor extending and bending inward. The second inner meshing section is connected to the second outer meshing section through the fourth transition section. The second inner meshing section and the second outer meshing section are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0013] Furthermore, the second chamber is formed by the second inner meshing section of the previous second worm claw portion protruding outward through the third transition section and connected to the second outer meshing section of the subsequent second worm claw portion. A second gap is formed between two adjacent second worm claw portions, which is used for the first worm claw portion to extend into the second chamber, thereby improving the meshing efficiency between the inner rotor and the outer rotor and further improving the utilization rate of the fluid. The size of the second gap and the second chamber is larger than that of the first worm claw portion, which is conducive to the circulation of fluid between the first chamber and the second chamber.

[0014] Furthermore, the first outer meshing section, the first inner meshing section, the first transition section, the second transition section, the second inner meshing section, the second outer meshing section, the third transition section and the fourth transition section all adopt an arc surface structure.

[0015] Furthermore, the inner rotor drives the outer rotor to rotate synchronously in the same direction, or the outer rotor is fixed and the inner rotor peristalses inside the outer rotor, so that the fluid flows between the first chamber and the second chamber, meeting the use requirements of different fluorine pumps and expanding the scope of application.

[0016] An air conditioning system includes a compressor, a condenser, an evaporator, a storage tank, a pressure gauge, an expansion valve, a first solenoid valve and a second solenoid valve. The compressor is connected to the condenser and the evaporator respectively. The first solenoid valve is provided between the inlet and outlet of the compressor. The second solenoid valve, the storage tank, the pressure gauge and the expansion valve are connected in series and are connected to the condenser and the evaporator. The system is characterized in that it also includes a micro refrigerant fluorine pump as described above, which is provided between the condenser and the evaporator and is connected in parallel with the second solenoid valve, the storage tank, the pressure gauge and the expansion valve. The air conditioning system has a simple structure and can not only reduce noise during operation but also extend its service life.

[0017] The present invention has the following beneficial effects due to the adoption of the above technical solution: 1. The present invention can not only reduce the friction and wear between the inner rotor and the outer rotor of the micro refrigerant fluorine pump and reduce the noise during operation, but also is conducive to heat dissipation, reduces the impact of temperature on the fluid, and at the same time increases the fluid delivery volume, making the fluid utilization rate higher.

[0018] 2. Both the first worm claw portion and the second worm claw portion have a curved structure and are arranged in opposite directions. The curved structure can be arc-shaped or L-shaped. When the first worm claw portion bends in the clockwise direction, the second worm claw portion bends in the counterclockwise direction, or when the first worm claw portion bends in the counterclockwise direction, the second worm claw portion bends in the clockwise direction. This ensures that when the inner rotor rotates, the first worm claw portion and the second worm claw portion move synchronously, thereby achieving efficient fluid transportation.

[0019] 3. The air conditioning system of the present invention has a simple structure, which can not only reduce noise during operation but also extend its service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The present invention will be further described below in conjunction with the accompanying drawings: Figure 1 This is a rendering of the effect of using six pairs of first and second volute claws in Example 1 of a micro refrigerant fluorine pump and air conditioning system of the present invention; Figure 2 for Figure 1 The main view; Figure 3 Schematic diagram of the structure of the inner rotor in Example 1 of the present invention; Figure 4 Schematic diagram of the structure of the outer rotor in Example 1 of the present invention; Figure 5This is a rendering of the effect of using five pairs of first and second worm claws in Example 2 of the present invention; Figure 6 for Figure 5 The main view; Figure 7 Schematic diagram of the structure of the inner rotor in Example 2 of the present invention; Figure 8 Schematic diagram of the structure of the outer rotor in Example 2 of the present invention; Figure 9 This is a rendering of the effect of using four pairs of first and second worm claws in Example 3 of the present invention; Figure 10 for Figure 9 The main view; Figure 11 Schematic diagram of the structure of the inner rotor in Example 3 of the present invention; Figure 12 Schematic diagram of the structure of the outer rotor in Example 3 of the present invention; Figure 13 This is a rendering of the effect of using three pairs of first worm claws and second worm claws in Example 4 of the present invention; Figure 14 for Figure 13 The main view; Figure 15 Schematic diagram of the structure of the inner rotor in Example 4 of the present invention; Figure 16 Schematic diagram of the structure of the outer rotor in Example 4 of the present invention; Figure 17 It is a structural block diagram of the air-conditioning system in the present invention.

[0021] In the figure: 1-inner rotor; 101-first worm portion; 102-first chamber; 103-first outer meshing section; 104-first transition section; 105-first inner meshing section; 106-second transition section; 107-rotor body; 2-outer rotor; 201-second worm claw portion; 202-second chamber; 203-rotor outer ring; 204-third transition section; 205-second inner meshing section; 206-fourth transition section; 207-second outer meshing section; 3-compressor; 4-condenser; 5-evaporator; 6-fluorine pump; 7-expansion valve; 8-storage tank; 9-second solenoid valve; 10-pressure gauge; 11-first solenoid valve. DETAILED DESCRIPTION

[0022] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0023] In order to enable those skilled in the art to better understand the solutions of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of the present invention.

[0024] It should be noted that the terms "first," "second," and so on in the description and claims of the present invention and the accompanying drawings are used to distinguish similar items and are not necessarily used to describe a specific order or precedence. Furthermore, the terms "including," "having," and any variations thereof are intended to cover non-exclusive inclusions.

[0025] Example 1 like Figures 1 to 4 Figure 6 shows a micro refrigerant fluorine pump 6 according to the present invention, comprising an inner rotor 1 and an outer rotor 2. The eccentric arrangement of the inner rotor 1 and the outer rotor 2 facilitates the formation of a continuously changing space between the first chamber 102 and the second chamber 202 during the meshing process of the inner rotor 1 and the outer rotor 2, thereby ensuring stable fluid delivery. The fluid can be gas or liquid.

[0026] The inner rotor 1 includes a rotor body 107 and six first worm claws 101 evenly distributed along the outer circumference of the rotor body 107 . Two adjacent first worm claws 101 cooperate to form a first chamber 102 .

[0027] The outer rotor 2 includes a closed rotor outer ring 203 and six second worm claws 201 evenly distributed along the inner circumference of the rotor outer ring 203. Two adjacent second worm claws 201 cooperate to form a second chamber 202, which is connected to the first chamber 102.

[0028] The first worm claw portion 101 and the second worm claw portion 201 both have a curved structure and are arranged in opposite directions. The curved structure can be arc-shaped or L-shaped. When the first worm claw portion 101 bends in the clockwise direction, the second worm claw portion 201 bends in the counterclockwise direction, or when the first worm claw portion 101 bends in the counterclockwise direction, the second worm claw portion 201 bends in the clockwise direction. This ensures that when the inner rotor 1 rotates, the first worm claw portion 101 and the second worm claw portion 201 move synchronously, thereby achieving efficient fluid transportation.

[0029] The first worm claw portion 101 includes a first outer meshing section 103 and a first inner meshing section 105 and a first transition section 104 formed by extending and bending the rotor body 107 outward. The first outer meshing section 103 is connected to the first inner meshing section 105 through the first transition section 104. The first outer meshing section 103 and the first inner meshing section 105 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0030] The first chamber 102 is formed by the first outer meshing section 103 of the preceding first worm portion 101 being recessed inwardly through the second transition section 106 and connected to the first inner meshing section 105 of the succeeding first worm portion 101. A first notch is formed between two adjacent first worm portions 101 for the second worm portion 201 to extend into the first chamber 102, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0031] The size of the first notch and the first chamber 102 is larger than that of the second worm claw portion 201 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0032] The second worm claw portion 201 includes a second inner meshing section 205 and a second outer meshing section 207 and a fourth transition section 206 formed by the rotor outer ring 203 extending and bending inward. The second inner meshing section 205 is connected to the second outer meshing section 207 through the fourth transition section 206. The second inner meshing section 205 and the second outer meshing section 207 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0033] The second chamber 202 is formed by the second inner meshing section 205 of the preceding second worm claw portion 201 protruding outward through the third transition section 204 and connected to the second outer meshing section 207 of the succeeding second worm claw portion 201. A second notch is formed between two adjacent second worm claw portions 201 to allow the first worm claw portion 101 to extend into the second chamber 202, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0034] The size of the second notch and the second chamber 202 is larger than that of the first worm claw portion 101 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0035] The first outer meshing section 103 , the first inner meshing section 105 , the first transition section 104 , the second transition section 106 , the second inner meshing section 205 , the second outer meshing section 207 , the third transition section 204 and the fourth transition section 206 all adopt arc surface structures.

[0036] When the inner rotor 1 drives the first worm portion 101 to perform eccentric reciprocating motion along the second chamber 202 , the second worm portion 201 of the outer rotor 2 performs the same eccentric reciprocating motion along the first chamber 102 , thereby enabling fluid to flow between the first chamber 102 and the second chamber 202 .

[0037] Through the design of the above structure, not only can the friction and wear between the inner rotor 1 and the outer rotor 2 of the micro refrigerant fluorine pump 6 be reduced, and the noise during operation be reduced, but it is also beneficial to heat dissipation, reducing the impact of temperature on the fluid, and at the same time increasing the fluid delivery volume, making the fluid utilization rate higher.

[0038] The inner rotor 1 drives the outer rotor 2 to rotate synchronously in the same direction, or the outer rotor 2 is fixed and the inner rotor 1 peristalses inside the outer rotor 2, so as to realize the flow of fluid between the first chamber 102 and the second chamber 202, thereby meeting the use requirements of different fluorine pumps 6 and expanding the scope of application.

[0039] Example 2 like Figures 5 to 8 Figure 6 shows a micro refrigerant fluorine pump 6 according to the present invention, comprising an inner rotor 1 and an outer rotor 2. The eccentric arrangement of the inner rotor 1 and the outer rotor 2 facilitates the formation of a continuously changing space between the first chamber 102 and the second chamber 202 during the meshing process of the inner rotor 1 and the outer rotor 2, thereby ensuring stable fluid delivery. The fluid can be gas or liquid.

[0040] The inner rotor 1 includes a rotor body 107 and five first worm claws 101 evenly distributed along the outer circumference of the rotor body 107 . Two adjacent first worm claws 101 cooperate to form a first chamber 102 .

[0041] The outer rotor 2 includes a closed rotor outer ring 203 and five second worm claws 201 evenly distributed along the inner circumference of the rotor outer ring 203. Two adjacent second worm claws 201 cooperate to form a second chamber 202, which is connected to the first chamber 102.

[0042] The first worm claw portion 101 and the second worm claw portion 201 both have a curved structure and are arranged in opposite directions. The curved structure can be arc-shaped or L-shaped. When the first worm claw portion 101 bends in the clockwise direction, the second worm claw portion 201 bends in the counterclockwise direction, or when the first worm claw portion 101 bends in the counterclockwise direction, the second worm claw portion 201 bends in the clockwise direction. This ensures that when the inner rotor 1 rotates, the first worm claw portion 101 and the second worm claw portion 201 move synchronously, thereby achieving efficient fluid transportation.

[0043] The first worm claw portion 101 includes a first outer meshing section 103 and a first inner meshing section 105 and a first transition section 104 formed by extending and bending the rotor body 107 outward. The first outer meshing section 103 is connected to the first inner meshing section 105 through the first transition section 104. The first outer meshing section 103 and the first inner meshing section 105 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0044] The first chamber 102 is formed by the first outer meshing section 103 of the preceding first worm portion 101 being recessed inwardly through the second transition section 106 and connected to the first inner meshing section 105 of the succeeding first worm portion 101. A first notch is formed between two adjacent first worm portions 101 for the second worm portion 201 to extend into the first chamber 102, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0045] The size of the first notch and the first chamber 102 is larger than that of the second worm claw portion 201 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0046] The second worm claw portion 201 includes a second inner meshing section 205 and a second outer meshing section 207 and a fourth transition section 206 formed by the rotor outer ring 203 extending and bending inward. The second inner meshing section 205 is connected to the second outer meshing section 207 through the fourth transition section 206. The second inner meshing section 205 and the second outer meshing section 207 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0047] The second chamber 202 is formed by the second inner meshing section 205 of the preceding second worm claw portion 201 protruding outward through the third transition section 204 and connected to the second outer meshing section 207 of the succeeding second worm claw portion 201. A second notch is formed between two adjacent second worm claw portions 201 to allow the first worm claw portion 101 to extend into the second chamber 202, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0048] The size of the second notch and the second chamber 202 is larger than that of the first worm claw portion 101 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0049] The first outer meshing section 103 , the first inner meshing section 105 , the first transition section 104 , the second transition section 106 , the second inner meshing section 205 , the second outer meshing section 207 , the third transition section 204 and the fourth transition section 206 all adopt arc surface structures.

[0050] When the inner rotor 1 drives the first worm portion 101 to perform eccentric reciprocating motion along the second chamber 202 , the second worm portion 201 of the outer rotor 2 performs the same eccentric reciprocating motion along the first chamber 102 , thereby enabling fluid to flow between the first chamber 102 and the second chamber 202 .

[0051] Through the design of the above structure, not only can the friction and wear between the inner rotor 1 and the outer rotor 2 of the micro refrigerant fluorine pump 6 be reduced, and the noise during operation be reduced, but it is also beneficial to heat dissipation, reducing the impact of temperature on the fluid, and at the same time increasing the fluid delivery volume, making the fluid utilization rate higher.

[0052] The inner rotor 1 drives the outer rotor 2 to rotate synchronously in the same direction, or the outer rotor 2 is fixed and the inner rotor 1 peristalses inside the outer rotor 2, so as to realize the flow of fluid between the first chamber 102 and the second chamber 202, thereby meeting the use requirements of different fluorine pumps 6 and expanding the scope of application.

[0053] Example 3 like Figures 9 to 12 Figure 6 shows a micro refrigerant fluorine pump 6 according to the present invention, comprising an inner rotor 1 and an outer rotor 2. The eccentric arrangement of the inner rotor 1 and the outer rotor 2 facilitates the formation of a continuously changing space between the first chamber 102 and the second chamber 202 during the meshing process of the inner rotor 1 and the outer rotor 2, thereby ensuring stable fluid delivery. The fluid can be gas or liquid.

[0054] The inner rotor 1 includes a rotor body 107 and four first worm claws 101 evenly distributed along the outer circumference of the rotor body 107 . Two adjacent first worm claws 101 cooperate to form a first chamber 102 .

[0055] The outer rotor 2 includes a closed rotor outer ring 203 and four second worm claws 201 evenly distributed along the inner circumference of the rotor outer ring 203. Two adjacent second worm claws 201 cooperate to form a second chamber 202, which is connected to the first chamber 102.

[0056] The first worm claw portion 101 and the second worm claw portion 201 both have a curved structure and are arranged in opposite directions. The curved structure can be arc-shaped or L-shaped. When the first worm claw portion 101 bends in the clockwise direction, the second worm claw portion 201 bends in the counterclockwise direction, or when the first worm claw portion 101 bends in the counterclockwise direction, the second worm claw portion 201 bends in the clockwise direction. This ensures that when the inner rotor 1 rotates, the first worm claw portion 101 and the second worm claw portion 201 move synchronously, thereby achieving efficient fluid transportation.

[0057] The first worm claw portion 101 includes a first outer meshing section 103 and a first inner meshing section 105 and a first transition section 104 formed by extending and bending the rotor body 107 outward. The first outer meshing section 103 is connected to the first inner meshing section 105 through the first transition section 104. The first outer meshing section 103 and the first inner meshing section 105 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0058] The first chamber 102 is formed by the first outer meshing section 103 of the preceding first worm portion 101 being recessed inwardly through the second transition section 106 and connected to the first inner meshing section 105 of the succeeding first worm portion 101. A first notch is formed between two adjacent first worm portions 101 for the second worm portion 201 to extend into the first chamber 102, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0059] The size of the first notch and the first chamber 102 is larger than that of the second worm claw portion 201 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0060] The second worm claw portion 201 includes a second inner meshing section 205 and a second outer meshing section 207 and a fourth transition section 206 formed by the rotor outer ring 203 extending and bending inward. The second inner meshing section 205 is connected to the second outer meshing section 207 through the fourth transition section 206. The second inner meshing section 205 and the second outer meshing section 207 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0061] The second chamber 202 is formed by the second inner meshing section 205 of the preceding second worm claw portion 201 protruding outward through the third transition section 204 and connected to the second outer meshing section 207 of the succeeding second worm claw portion 201. A second notch is formed between two adjacent second worm claw portions 201 to allow the first worm claw portion 101 to extend into the second chamber 202, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0062] The size of the second notch and the second chamber 202 is larger than that of the first worm claw portion 101 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0063] The first outer meshing section 103 , the first inner meshing section 105 , the first transition section 104 , the second transition section 106 , the second inner meshing section 205 , the second outer meshing section 207 , the third transition section 204 and the fourth transition section 206 all adopt arc surface structures.

[0064] When the inner rotor 1 drives the first worm portion 101 to perform eccentric reciprocating motion along the second chamber 202 , the second worm portion 201 of the outer rotor 2 performs the same eccentric reciprocating motion along the first chamber 102 , thereby enabling fluid to flow between the first chamber 102 and the second chamber 202 .

[0065] Through the design of the above structure, not only can the friction and wear between the inner rotor 1 and the outer rotor 2 of the micro refrigerant fluorine pump 6 be reduced, and the noise during operation be reduced, but it is also beneficial to heat dissipation, reducing the impact of temperature on the fluid, and at the same time increasing the fluid delivery volume, making the fluid utilization rate higher.

[0066] The inner rotor 1 drives the outer rotor 2 to rotate synchronously in the same direction, or the outer rotor 2 is fixed and the inner rotor 1 peristalses inside the outer rotor 2, so as to realize the flow of fluid between the first chamber 102 and the second chamber 202, thereby meeting the use requirements of different fluorine pumps 6 and expanding the scope of application.

[0067] Example 4 like Figures 13 to 16 Figure 6 shows a micro refrigerant fluorine pump 6 according to the present invention, comprising an inner rotor 1 and an outer rotor 2. The eccentric arrangement of the inner rotor 1 and the outer rotor 2 facilitates the formation of a continuously changing space between the first chamber 102 and the second chamber 202 during the meshing process of the inner rotor 1 and the outer rotor 2, thereby ensuring stable fluid delivery. The fluid can be gas or liquid.

[0068] The inner rotor 1 includes a rotor body 107 and three first worm claws 101 evenly distributed along the outer circumference of the rotor body 107 . Two adjacent first worm claws 101 cooperate to form a first chamber 102 .

[0069] The outer rotor 2 includes a closed rotor outer ring 203 and three second worm claws 201 evenly distributed along the inner circumference of the rotor outer ring 203. Two adjacent second worm claws 201 cooperate to form a second chamber 202, which is connected to the first chamber 102.

[0070] The first worm claw portion 101 and the second worm claw portion 201 both have a curved structure and are arranged in opposite directions. The curved structure can be arc-shaped or L-shaped. When the first worm claw portion 101 bends in the clockwise direction, the second worm claw portion 201 bends in the counterclockwise direction, or when the first worm claw portion 101 bends in the counterclockwise direction, the second worm claw portion 201 bends in the clockwise direction. This ensures that when the inner rotor 1 rotates, the first worm claw portion 101 and the second worm claw portion 201 move synchronously, thereby achieving efficient fluid transportation.

[0071] The first worm claw portion 101 includes a first outer meshing section 103 and a first inner meshing section 105 and a first transition section 104 formed by extending and bending the rotor body 107 outward. The first outer meshing section 103 is connected to the first inner meshing section 105 through the first transition section 104. The first outer meshing section 103 and the first inner meshing section 105 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0072] The first chamber 102 is formed by the first outer meshing section 103 of the preceding first worm portion 101 being recessed inwardly through the second transition section 106 and connected to the first inner meshing section 105 of the succeeding first worm portion 101. A first notch is formed between two adjacent first worm portions 101 for the second worm portion 201 to extend into the first chamber 102, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0073] The size of the first notch and the first chamber 102 is larger than that of the second worm claw portion 201 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0074] The second worm claw portion 201 includes a second inner meshing section 205 and a second outer meshing section 207 and a fourth transition section 206 formed by the rotor outer ring 203 extending and bending inward. The second inner meshing section 205 is connected to the second outer meshing section 207 through the fourth transition section 206. The second inner meshing section 205 and the second outer meshing section 207 are bent in the same direction to ensure stability during the meshing process and reduce friction and wear.

[0075] The second chamber 202 is formed by the second inner meshing section 205 of the preceding second worm claw portion 201 protruding outward through the third transition section 204 and connected to the second outer meshing section 207 of the succeeding second worm claw portion 201. A second notch is formed between two adjacent second worm claw portions 201 to allow the first worm claw portion 101 to extend into the second chamber 202, thereby improving the meshing efficiency between the inner rotor 1 and the outer rotor 2 and further enhancing the utilization rate of the fluid.

[0076] The size of the second notch and the second chamber 202 is larger than that of the first worm claw portion 101 , which facilitates the flow of fluid between the first chamber 102 and the second chamber 202 .

[0077] The first outer meshing section 103 , the first inner meshing section 105 , the first transition section 104 , the second transition section 106 , the second inner meshing section 205 , the second outer meshing section 207 , the third transition section 204 and the fourth transition section 206 all adopt arc surface structures.

[0078] When the inner rotor 1 drives the first worm portion 101 to perform eccentric reciprocating motion along the second chamber 202 , the second worm portion 201 of the outer rotor 2 performs the same eccentric reciprocating motion along the first chamber 102 , thereby enabling fluid to flow between the first chamber 102 and the second chamber 202 .

[0079] Through the design of the above structure, not only can the friction and wear between the inner rotor 1 and the outer rotor 2 of the micro refrigerant fluorine pump 6 be reduced, and the noise during operation be reduced, but it is also beneficial to heat dissipation, reducing the impact of temperature on the fluid, and at the same time increasing the fluid delivery volume, making the fluid utilization rate higher.

[0080] The inner rotor 1 drives the outer rotor 2 to rotate synchronously in the same direction, or the outer rotor 2 is fixed and the inner rotor 1 peristalses inside the outer rotor 2, so as to realize the flow of fluid between the first chamber 102 and the second chamber 202, thereby meeting the use requirements of different fluorine pumps 6 and expanding the scope of application.

[0081] Figure 17 As shown, an air-conditioning system of the present invention includes a compressor 3, a condenser 4, an evaporator 5, a storage tank 8, a pressure gauge 10, an expansion valve 7, a first solenoid valve 11 and a second solenoid valve 9. The compressor 3 is connected to the condenser 4 and the evaporator 5 respectively. A first solenoid valve 11 is provided between the inlet and outlet of the compressor 3. The second solenoid valve 9, the storage tank 8, the pressure gauge 10 and the expansion valve 7 are connected in series and connected to the condenser 4 and the evaporator 5. The system also includes the micro refrigerant fluorine pump 6 as described above. The fluorine pump 6 is provided between the condenser 4 and the evaporator 5 and is connected in parallel with the second solenoid valve 9, the storage tank 8, the pressure gauge 10 and the expansion valve 7. The air-conditioning system has a simple structure, which can not only reduce noise during operation, but also extend service life.

[0082] The above are only specific embodiments of the present invention, but the technical features of the present invention are not limited thereto. Any simple changes, equivalent replacements, or modifications based on the present invention to achieve substantially the same technical effects are all within the scope of protection of the present invention.

Claims

1. A micro refrigerant fluorine pump, comprising inner rotor; and an outer rotor, the inner rotor and the outer rotor being eccentrically arranged; Its characteristics are: The inner rotor includes a rotor body and at least three first worm claws evenly distributed along the outer circumference of the rotor body, and two adjacent first worm claws cooperate to form a first chamber; The outer rotor includes a rotor outer ring with a closed structure and at least three second worm claws evenly distributed along the inner circumference of the rotor outer ring, wherein two adjacent second worm claws cooperate to form a second chamber, and the second chamber is communicated with the first chamber. When the inner rotor drives the first worm claw portion to perform eccentric reciprocating motion along the second chamber, the second worm claw portion of the outer rotor performs the same eccentric reciprocating motion along the first chamber, thereby achieving fluid flow between the first chamber and the second chamber.

2. A micro refrigerant fluorine pump according to claim 1, characterized in that: The first worm claw portion and the second worm claw portion both have a curved structure and are arranged in opposite directions.

3. A micro refrigerant fluorine pump according to claim 1, characterized in that: The first worm claw portion includes a first outer meshing section, a first inner meshing section, and a first transition section formed by the rotor body extending and bending outward. The first outer meshing section is connected to the first inner meshing section through the first transition section.

4. A micro refrigerant fluorine pump according to claim 3, characterized in that: The first chamber is formed by the first outer meshing section of the previous first worm claw portion being recessed inward through the second transition section and connected to the first inner meshing section of the next first worm claw portion. A first notch is formed between two adjacent first worm claw portions for the second worm claw portion to extend into the first chamber.

5. A micro refrigerant fluorine pump according to claim 4, characterized in that: The first notch and the first chamber have sizes larger than the second worm portion.

6. A micro refrigerant fluorine pump according to claim 4, characterized in that: The second worm claw portion includes a second inner meshing segment, a second outer meshing segment, and a fourth transition segment formed by inwardly extending and bending the rotor outer ring. The second inner meshing segment is connected to the second outer meshing segment through the fourth transition segment.

7. A micro refrigerant fluorine pump according to claim 6, characterized in that: The second chamber is formed by the second inner meshing section of the preceding second worm claw portion protruding outward through the third transition section and connected to the second outer meshing section of the succeeding second worm claw portion. A second notch is formed between two adjacent second worm claw portions for the first worm claw portion to extend into the second chamber. The size of the second notch and the second chamber is larger than that of the first worm claw portion.

8. A micro refrigerant fluorine pump according to claim 7, characterized in that: The first outer meshing section, the first inner meshing section, the first transition section, the second transition section, the second inner meshing section, the second outer meshing section, the third transition section and the fourth transition section all adopt an arc surface structure.

9. The micro refrigerant fluorine pump according to claim 1, characterized in that: The inner rotor drives the outer rotor to perform synchronous rotational motion in the same direction, or the outer rotor is fixed and the inner rotor creeps inside the outer rotor, thereby achieving fluid flow between the first chamber and the second chamber.

10. An air conditioning system comprising a compressor, a condenser, an evaporator, a storage tank, a pressure gauge, an expansion valve, a first solenoid valve, and a second solenoid valve, wherein the compressor is connected to the condenser and the evaporator, respectively; the first solenoid valve is provided between the inlet and outlet of the compressor; the second solenoid valve, the storage tank, the pressure gauge, and the expansion valve are connected in series and to the condenser and the evaporator, characterized in that: It also includes a micro refrigerant fluorine pump according to any one of claims 1 to 9, wherein the fluorine pump is arranged between the condenser and the evaporator and is connected in parallel with the second solenoid valve, the storage tank, the pressure gauge and the expansion valve.

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