A rotor-type Stirling refrigerator

Abstract

The present invention provides a rotor-type Stirling refrigerator, comprising a compression rotor and an expansion rotor, wherein the expansion rotor is located at the cold end and the compression rotor is located at the hot end; the phase angle of the rotor in the expansion rotor differs by 90° from the phase angle of the rotor in the compression rotor; the end covers of the compression rotor are respectively provided with air holes communicating with the hot chamber, and the end covers of the expansion rotor are respectively provided with air holes communicating with the cold chamber; the air holes communicating with the hot chamber are connected to the air holes communicating with the cold chamber via a heat exchange device. The compressor and expander of the present invention are arranged in opposing positions, one at the hot end and the other at the cold end. This design of separate cavities prevents heat conduction from the walls between the cavities, thereby affecting circulation, and reduces the temperature difference between different cavities within the refrigerator.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration, and in particular to a rotor-type Stirling refrigerator. Background Art

[0002] Stirling refrigerators are characterized by their light weight, small size, compact structure, and wide operating temperature range, and are widely used in the cryogenic industry and military fields. The working principle of a Stirling refrigerator is based on the reverse Stirling cycle, where the gas is compressed by a compressor, and a pressure difference is formed at both ends of the piston inside the regenerator, thereby performing a heat exchange process and realizing the circulation of the fluid in the circuit to achieve the purpose of cooling. Most existing Stirling refrigerators are piston-type reciprocating structures. However, piston-type refrigerators are large in size, have strong vibrations and make loud noises during operation. In addition, since the dynamic sealing components in the cylinder have a large sliding sealing area, the cylinder and the sealing components need to withstand high temperature and high pressure conditions, resulting in significant friction and wear between the two due to poor lubrication, which in turn reduces the operating stability and reliability of the refrigerator.

[0003] In addition, most refrigerator compressors compress and discharge high-temperature and high-pressure gases, and the discharged compressed gas is a constant value. Under some medium and low-load refrigeration conditions, there may be excess pressure entering the regenerator for heat exchange circulation. This situation will cause the piston load inside the regenerator to be too large, resulting in heat waste and an increase in the temperature difference between the two ends of the regenerator, which will have a negative impact on the overall thermal efficiency, affect the life of the regenerator, and even cause failure. Summary of the Invention

[0004] In response to the shortcomings of the existing technology, the present invention provides a rotor-type Stirling refrigerator, in which the compressor and expander are arranged in opposite directions, one is the hot end and the other is the cold end. The design of the separation cavity can avoid heat conduction between the walls of the cavities, thereby affecting the circulation, and reduce the temperature difference between different cavities in the rotor machine.

[0005] The present invention achieves the above technical objectives through the following technical means.

[0006] A rotor-type Stirling refrigerator comprises a compression rotor and an expansion rotor, wherein the expansion rotor is located at a cold end and the compression rotor is located at a hot end; the compression rotor has a hot chamber with a periodic volume change; the expansion rotor has a cold chamber with a periodic volume change; the phase angle of the rotor in the expansion rotor differs by 90° from the phase angle of the rotor in the compression rotor;

[0007] The end covers of the compression rotor machine are respectively provided with air holes connected to the hot chamber, and the end covers of the expansion rotor machine are respectively provided with air holes connected to the cold chamber; the air holes connected to the hot chamber are connected to the air holes connected to the cold chamber through a heat exchange device, wherein the hot chamber with a gradually decreasing volume in the compression rotor machine is connected to the cold chamber with a gradually increasing volume in the expansion rotor machine through a heat exchange device; the hot chamber with a gradually increasing volume in the compression rotor machine is connected to the cold chamber with a gradually decreasing volume in the expansion rotor machine through a heat exchange device, and when the hot chamber with a gradually increasing volume is in a state of starting to expand, the cold chamber with a gradually decreasing volume connected to it is in a state of starting to compress.

[0008] Furthermore, the compression rotor machine and the expansion rotor machine each include a cylinder body, a triangular rotor, a valve assembly and an eccentric shaft;

[0009] The eccentric shaft drives the triangular rotor to rotate in the cylinder body, so that the cylinder body has three hot / cold chambers with periodic volume changes; the three arc surfaces of the triangular rotor are respectively provided with three air inlets corresponding to the three hot / cold chambers, and one end surface of the triangular rotor is provided with three exhaust ports corresponding to the three hot / cold chambers, each of the air inlets is connected to the corresponding exhaust port through an internal flow channel, and a valve assembly is provided on the internal flow channel for controlling the connection and disconnection of the air inlet and exhaust ports; an end cover is installed on one side of the cylinder body, and three sealed flow channels corresponding to the three exhaust ports are provided on the end cover, and the three sealed flow channels are not connected to each other; the end cover is provided with air holes respectively connected to the three sealed flow channels.

[0010] Furthermore, the valve assembly includes a pulley rod, a cam, a valve block, a push rod and an actuator; a retractable valve block is provided in the inner flow channel, one end of the valve block is connected to the pulley rod, the pulley rod is in contact with the cam, the push rod is movably installed in the first long groove inside the triangular rotor, one end of the push rod is in contact with the cam, and the other end of the push rod is connected to the actuator, and the push rod is driven by the actuator to move linearly, thereby driving the cam to make the valve block retract and retract in the inner flow channel, which is used to realize the connection and disconnection between the air inlet and the exhaust port.

[0011] Furthermore, the actuator includes a T-shaped support rod and an outer support arc block; the T-shaped support rod is movably installed in the T-shaped slot inside the triangular rotor, one end of the T-shaped support rod is connected to the outer support arc block; the outer support arc block is in contact with the other end of the push rod;

[0012] The eccentric shaft is provided with an electric three-claw assembly, and three inner support arc blocks are installed on the electric three-claw assembly. The inner support arc block is located on the inner side of the outer support arc block. By controlling the electric three-claw assembly, the inner support arc block moves linearly, driving the outer support arc block to move radially, so that the outer support arc block pushes the push rod to move linearly.

[0013] Furthermore, a contraction spring is provided between the T-shaped support rod and the T-shaped slot for resetting the outer support arc block.

[0014] Furthermore, the oblique sides of both ends of the outer supporting arc block are chamfered outwards, and the oblique sides of both ends of the inner supporting arc block are chamfered inwards, so that the outer arc length of the cross section of the outer supporting arc block is greater than the outer arc length of the cross section of the inner supporting arc block.

[0015] Furthermore, each sealed flow channel is provided with sealing grooves on both sides, and sealing sheets are installed inside.

[0016] Furthermore, a phase angle detection sensor is installed on the eccentric shaft to detect the phase angle of the rotor; and the action of the electric three-claw assembly is controlled according to the phase angle of the rotor.

[0017] The beneficial effects of the present invention are:

[0018] 1. In the rotor-type Stirling refrigerator described in the present invention, the compressor and expander are arranged in opposite directions, one as the hot end and the other as the cold end. This design of the separated cavities can prevent heat conduction from the walls between the cavities, thereby affecting the circulation, and reduce the temperature difference between different cavities in the rotor machine.

[0019] 2. The rotor-type Stirling refrigerator described in the present invention uses a new triangular rotor structure for the compressor and expander used for refrigeration. Compared with the Stirling refrigerator with a piston-type reciprocating mechanism, it is smaller in size and lighter in weight. In addition, the friction and wear between the triangular rotor and the cylinder are smaller, the operation is smoother, and the high-speed performance is better. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. The drawings described below are some embodiments of the present invention. For ordinary technicians in this field, it is obvious that other drawings can be obtained based on these drawings without paying any creative work.

[0021] Figure 1 This is an overall assembly diagram of the rotor-type Stirling refrigerator described in the present invention.

[0022] Figure 2 This is an exploded view of the assembly of the compression rotor machine and the expansion rotor machine described in the present invention.

[0023] Figure 3 This is a front overall schematic diagram of the compression rotor machine and expansion rotor machine described in the present invention.

[0024] Figure 4 This is an overall schematic diagram of the back of the compression rotor machine and the expansion rotor machine described in the present invention.

[0025] Figure 5This is a schematic diagram of the eccentric shaft assembly of the present invention.

[0026] Figure 6 This is an exploded view of the triangular rotor assembly described in the present invention.

[0027] Figure 7 This is a diagram showing the arrangement of the valve assembly described in the present invention within the front portion of the triangular rotor.

[0028] Figure 8 Schematic diagram of the triangular rotor described in the present invention.

[0029] Figure 9 This is a layout diagram of the cam according to the present invention.

[0030] Figure 10 This is a schematic diagram of the rotor-type Stirling refrigerator of the present invention.

[0031] Figure 11 Schematic diagram of the sealing principle on the end cover of the present invention.

[0032] Figure 12 This is a front view of the end cover of the present invention.

[0033] Figure 13 This is a matching diagram of the inner supporting arc block and the outer supporting arc block described in the present invention.

[0034] Figure 14 This is a schematic diagram of the control system described in the present invention.

[0035] Figure 15 This is a schematic diagram of the triangular rotor of the compressor of the present invention located at the top dead center.

[0036] Figure 16 This is a schematic diagram of the triangular rotor of the compressor of the present invention located 90° before the top dead center.

[0037] Figure 17 This is a schematic diagram of the triangular rotor of the compressor of the present invention located 120° before the top dead center.

[0038] Figure 18 This is a schematic diagram of the triangular rotor of the compressor of the present invention located 210° before the top dead center.

[0039] Figure 19 This is a schematic diagram of the triangular rotor of the compressor of the present invention located 240° before the top dead center.

[0040] Figure 20 This is a schematic diagram of the triangular rotor of the compressor of the present invention located 330° before the top dead center.

[0041] In the picture:

[0042] 1-Compression rotor; 2-Expansion rotor; 3-End cover; 4-Regenerator; 5-Heat exchange tube; 6-Eccentric shaft; 7-Triangular rotor; 8-Cylinder block; 9-First air hole; 10-Second air hole; 11-Third air hole; 12-First sealed flow channel; 13-Second sealed flow channel; 14-Third sealed flow channel; 15-Inlet; 16-Exhaust port; 17-First through hole; 18-Front of eccentric shaft; 19-Electric three-claw assembly; 20-Rear of eccentric shaft; 21-rear part of the rotor; 22-front part of the rotor; 23-T-shaped support rod; 24-outer support arc block; 25-valve block; 26-cam; 27-push rod; 28-first bolt; 29-pulley rod; 30-contraction spring; 31-annular groove; 32-first groove; 33-inner flow channel; 34-first long groove; 35-T-shaped groove; 36-sealing plate; 37-sealing groove; 38-three-claw electronic control system; 39-rotary joint; 40-inner support arc block. DETAILED DESCRIPTION

[0043] The following describes embodiments of the present invention in detail, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and are not to be construed as limiting the present invention.

[0044] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "axial", "radial", "vertical", "horizontal", "inside", "outside" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "multiple" means two or more, unless otherwise clearly and specifically defined.

[0045] In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," "connect," "fixed," etc. should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediary; or internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0046] like Figure 1 As shown, the rotor-type Stirling refrigerator of the present invention comprises a compression rotor machine 1 and an expansion rotor machine 2, wherein the expansion rotor machine 2 is located at the cold end and the compression rotor machine 1 is located at the hot end; the compression rotor machine 1 has a hot chamber with a periodic volume change; the expansion rotor machine 2 has a cold chamber with a periodic volume change; the phase angle of the rotor in the expansion rotor machine 2 differs by 90° from the phase angle of the rotor in the compression rotor machine 1; the end cover of the compression rotor machine 1 is respectively provided with an air hole connected to the hot chamber, and the end cover of the expansion rotor machine 2 is respectively provided with an air hole connected to the hot chamber. A pore is provided that communicates with the cold chamber; the pore that communicates with the hot chamber is connected to the pore that communicates with the cold chamber via a heat exchange device. The gradually decreasing hot chamber in the compression rotor 1 is connected to the gradually increasing cold chamber in the expansion rotor 2 via the heat exchange device; the gradually increasing hot chamber in the compression rotor 1 is connected to the gradually decreasing cold chamber in the expansion rotor 2 via the heat exchange device. When the gradually increasing hot chamber is in the initial expansion state, the gradually decreasing cold chamber connected to it is in the initial compression state. Separating the compression rotor 1 from the expansion rotor 2 is equivalent to separating the cold end from the hot end, thus avoiding cooling loss due to heat conduction from the cylinder. Furthermore, the temperature difference between different chambers within the same rotor is extremely small, preventing heat conduction from the cavity walls from affecting circulation. Figure 1 The intermediate heat exchange device includes a regenerator 4 and a heat exchange pipe 5. Both ends of the regenerator 4 are connected to the air holes of the compression rotor 1 and the expansion rotor 2 through the heat exchange pipe 5 respectively.

[0047] The structures of the compression rotor machine 1 and the expansion rotor machine 2 in the present invention are exactly the same. The only difference is that the phase angle of the rotor in the expansion rotor machine 2 is 90° different from the phase angle of the rotor in the compression rotor machine 1. Generally, the compression rotor machine 1 is 90° ahead of the expansion rotor machine 2. The compression rotor machine 1 is taken as an example below. Figure 2 、 Figure 3 and Figure 4As shown, the compression rotor machine 1 includes a cylinder body 8, a triangular rotor 7, a valve assembly and an eccentric shaft 6; the eccentric shaft 6 drives the triangular rotor 7 to rotate in the cylinder body 8, so that the cylinder body 8 has three hot chambers with periodic volume changes (cold chambers in the expansion rotor machine 2); the three arc surfaces of the triangular rotor 7 are respectively provided with three air inlets 15 corresponding to the three hot chambers, and one side end surface of the triangular rotor 7 is provided with three exhaust ports 16 corresponding to the three hot chambers, each of the air inlets 15 and its corresponding exhaust port 16 are connected to each other. 6 is connected through an inner flow channel 33, and a valve assembly is provided on the inner flow channel 33 to control the opening and closing of the air inlet 15 and the exhaust port 16; an end cover 3 is installed on one side of the cylinder body, and three sealed flow channels corresponding to the three exhaust ports 16 are provided on the end cover 3, namely the first sealed flow channel 12, the second sealed flow channel 13 and the third sealed flow channel 14; the first sealed flow channel 12, the second sealed flow channel 13 and the third sealed flow channel 14 are not connected to each other; the end cover 3 is provided with three air holes connected to the three sealed flow channels respectively. Figure 11 and 12 As described above, each sealed flow channel is provided with sealing grooves on both sides, and a sealing sheet 36 is installed inside for sealing.

[0048] Working Principle: The eccentric shaft 6 drives the triangular rotor 7 inside the cylinder 8 to rotate. The triangular rotor 7 rotates within the cylinder 8, changing the chamber volume and compressing the gas. The compressed air flows through the flow channel 33 of the triangular rotor 7 through the air inlet 15, and enters one of the sealed flow channels of the end cover 3 from the exhaust port 16. After flowing through the flow channel in the end cover 3, the air flows through the air holes in the sealed flow channel through the heat exchange pipe 5 and enters the regenerator 4. The inside of the expander rotor machine 2 performs a process opposite to the working cycle of the compressor, thereby realizing the heat exchange cycle function.

[0049] like Figure 6 、 Figure 7 、 Figure 8 and Figure 9 As shown, to facilitate installation of the valve assembly, the triangular rotor 7 is divided into a rotor front portion 22 and a rotor rear portion 21. The rotor front portion 22 and rotor rear portion 21 are assembled using bolts and a seal is provided. The valve assembly includes a pulley rod 29, a cam 26, a valve block 25, a push rod 27, and an actuator. A retractable valve block 25 is provided within the internal flow channel 33. One end of the valve block 25 is connected to the pulley rod 29, which contacts the cam 26. The cam 26 is located within a first groove 32 within the triangular rotor 7. The push rod 27 is movably mounted within a first elongated groove 34 within the triangular rotor 7. One end of the push rod 27 contacts the cam 26, and the other end is connected to the actuator. The actuator drives the push rod 27 to move linearly, thereby driving the cam 26 to cause the valve block 25 to retract and retract within the internal flow channel 33, thereby achieving open / close communication between the air inlet 15 and the exhaust port 16.

[0050] The actuator includes a T-shaped support rod 23 and an outer support arc block 24. The center hole of the triangular rotor 7 is provided with a concentric annular groove 31, which forms a step shape with the center hole. The center hole and the eccentric shaft 6 realize transmission.

[0051] The T-shaped support rod 23 is movably mounted in the T-shaped slot 35 inside the triangular rotor 7, and one end of the T-shaped support rod 23 is connected to the outer support arc block 24; the outer support arc block 24 is located at the annular slot 31, and the outer support arc block 24 is in contact with the other end of the push rod 27; Figure 5 and Figure 14 As shown, the eccentric shaft 6 includes an eccentric shaft front portion 18, an electric three-claw assembly 19 and an eccentric shaft rear portion 20; the eccentric shaft front portion 18 and the eccentric shaft rear portion 20 are installed at both ends of the electric three-claw assembly 19, and the electric three-claw assembly 19 has three retractable electric three-claws, and the retraction and extension of the electric three-claws are controlled by a control system. Each of the electric three-claws is equipped with an internal support arc block 22; the eccentric shaft front portion 18 is provided with a first through hole 17, inside which is fixed the wire that controls the electric three-claw assembly 19; the eccentric shaft front portion 18, the electric three-claw assembly 19 and the eccentric shaft rear portion 20 are fixedly connected so that the eccentric cone of the eccentric shaft front portion 18 is coaxial with the eccentric cone of the electric three-claw assembly 19 and the eccentric cone of the eccentric shaft rear portion 20; as shown Figure 13 As shown, three inner support arc blocks 40 are mounted on the electric three-claw assembly 19. The inner support arc blocks 40 are located inside the outer support arc blocks 24. Alternatively, the inner support arc blocks 40 can be considered to be located in the annular groove 31. By controlling the electric three-claw assembly 19 to cause the inner support arc blocks 40 to move linearly, the outer support arc blocks 24 are driven to move radially, thereby causing the outer support arc blocks 24 to push the push rod 27 to move linearly. A contraction spring 30 is provided between the T-shaped support rod 23 and the T-shaped groove 35 to reset the outer support arc blocks 24. The outer support arc blocks 24 have their beveled edges chamfered outward, while the inner support arc blocks 40 have their beveled edges chamfered inward, so that the outer arc length of the cross-section of the outer support arc blocks 24 is greater than the outer arc length of the cross-section of the inner support arc blocks 40.

[0052] like Figure 10As shown, for the convenience of explanation, the three hot chambers are respectively recorded as hot chamber A, hot chamber B and hot chamber C, and the three cold chambers are respectively recorded as cold chamber D, cold chamber E and cold chamber F. Since the state of the rotor at the top dead center is very short, it is considered in the principle introduction that one compressor pore / expander pore is only connected to one chamber. The hot chamber A is connected to the first pore 9 of the compressor through the inner flow channel 33 of the triangular rotor 7 and the first sealed flow channel 12 in the end cover 3. The hot chamber B is connected to the second pore 10 of the compressor through the inner flow channel 33 of the triangular rotor 7 and the second sealed flow channel 13 in the end cover 3. The hot chamber C is connected to the third pore 11 of the compressor through the inner flow channel 33 of the triangular rotor 7 and the third sealed flow channel 14 in the end cover 3. The first pore 9, the second pore 10 and the third pore 11 of the compressor are connected to the regenerator 4 through the heat exchange pipe 5; similarly, The cold chamber D is connected to the first air hole 9 of the expander through the inner flow channel 33 of the triangular rotor 7 and the first sealed flow channel 12 in the end cover 3. The cold chamber E is connected to the second air hole 10 of the expander through the inner flow channel 33 of the triangular rotor 7 and the second sealed flow channel 13 in the end cover 3. The cold chamber F is connected to the third air hole 11 of the expander through the inner flow channel 33 of the triangular rotor 7 and the third sealed flow channel 14 in the three-channel end cover 3. Similarly, the first air hole 9, the second air hole 10, and the third air hole 11 of the expander are connected to the regenerator 4 through the heat exchange pipe 5.

[0053] Figure 14 The rotor in the middle compression rotor machine 1 is about to rotate counterclockwise past the top dead center. At this time, the volume of the hot chamber A gradually increases, and at the same time, the volume of the cold chamber D in the expansion rotor machine 2 gradually decreases, and the hot chamber A is connected to the cold chamber D through a heat exchange device; the volume of the hot chamber B gradually decreases, and at the same time, the volume of the cold chamber E in the expander gradually increases, and the hot chamber B is connected to the cold chamber E through a heat exchange device; the volume of the hot chamber C gradually increases, and at the same time, the volume of the cold chamber F in the expander gradually decreases, and the hot chamber C is connected to the cold chamber F through a heat exchange device; it can be seen from the figure that when the hot chamber C is in the initial expansion state, it is in the initial compression state with the cold chamber F.

[0054] The following takes the cycle of hot chamber B and cold chamber E as an example to illustrate:

[0055] Figure 15The triangular rotor 7 of the middle compressor is initially located at the top dead center position, and the eccentric shaft 6 of the compressor drives the triangular rotor 7 of the compressor to rotate counterclockwise. At this time, the hot chamber B of the compressor is connected to the second air hole 10 of the compressor, and the second air hole 10 of the compressor is connected to the regenerator 4 through the heat exchange pipe 5. When the hot chamber B is at the top dead center position, the internal gas begins to be compressed. Due to the heat dissipation of the cylinder wall, the gas temperature cannot be increased synchronously, and an isothermal compression process is performed to release heat. Subsequently, the gas enters the regenerator 4 through the heat exchange pipe 5, and the gas absorbs heat and performs an isochoric heat release process; at this time, the second air hole 10 of the expander is connected to the regenerator 4 through the heat exchange pipe 5, and the gas flow enters the cold chamber E through the second air hole 10 of the expander. The gas expands, and the temperature and pressure are reduced. It absorbs heat from the surrounding environment, so that its own temperature remains unchanged, and an isothermal expansion process is performed.

[0056] like Figure 16 and Figure 17 As shown in the figure, the compressor triangular rotor 7 is located at 90° before the top dead center and rotates counterclockwise to 120° before the top dead center. At this time, the volume of the compressor hot chamber B gradually increases during the counterclockwise rotation of the compressor triangular rotor 7, while the volume of the corresponding cold chamber E gradually decreases. At this time, when the expander cold chamber E starts to compress, the gas is pushed through the regenerator 4 to absorb heat and return to the compressor hot chamber B.

[0057] Figure 18 and Figure 19 As shown in the figure, when the triangular rotor 7 of the compressor is located at 210° before the top dead center and rotates counterclockwise to 240° before the top dead center, the volume of the compressor hot chamber B gradually decreases, while the volume of the corresponding cold chamber E gradually increases. The gas in the compressor hot chamber B is pushed through the regenerator 4 to absorb heat and return to the expander cold chamber E.

[0058] Figure 19 and Figure 20 As shown in the figure, when the triangular rotor 7 of the compressor is located at 240° before the top dead center and rotates counterclockwise to 330° before the top dead center, the volume of the compressor hot chamber B gradually increases, and the volume of the corresponding cold chamber E gradually decreases. At this time, when the expander cold chamber E begins to compress, the gas is pushed through the regenerator 4 to absorb heat and return to the compressor hot chamber B.

[0059] Figure 20 and Figure 15 As shown in the figure, the triangular rotor 7 of the compressor continues to rotate counterclockwise from 330° before the top dead center to the top dead center position. During this process, the volume of the compressor hot chamber B gradually decreases, while the volume of the corresponding cold chamber E gradually increases. The gas in the compressor hot chamber B is pushed through the regenerator 4 to absorb heat and enter the expander cold chamber E.

[0060] As can be seen in the flow chart, when hot chamber B begins compression, the gas is compressed. Due to heat dissipation from the cylinder wall, the gas temperature cannot rise simultaneously, resulting in an isothermal compression process, releasing heat. The gas then passes through heat exchange tube 5 and enters regenerator 4, where it absorbs heat, undergoing an isochoric heat release process. The gas then enters cold chamber E, where it expands, causing both its temperature and pressure to decrease. It absorbs heat from the surrounding environment, maintaining its own temperature constant, undergoing an isothermal expansion process. When cold chamber E begins compression, the gas is pushed through regenerator 4, absorbing heat, and returns to hot chamber B. This completes a Stirling reverse cycle. During this cycle, the gas continuously absorbs heat in the expander chamber, while the compressor chamber continuously absorbs heat from the gas, continuously lowering the temperature of the cold-end chamber and achieving a cooling effect. The three compressor chambers correspond one-to-one with the three expander chambers, allowing three Stirling reverse cycles to occur simultaneously. This Stirling refrigerator leverages the advantages of a rotor compressor's compact size and high power density, and by separating the cold and hot ends, it significantly improves cooling efficiency.

[0061] like Figure 11 and Figure 12 Since the triangular rotor 7 rotates on one side of the end cover 3, sealing measures need to be taken in the process of the airflow entering the flow channel of the end cover 3 through the exhaust port 16. Figure 14 According to the length and width dimensions of the exhaust port 16 on the end face of the triangular rotor 7 and the movement trajectory of the triangular rotor 7 along the cylinder body 8, three sealing flow channels in the end cover 3 are designed, and sealing grooves 37 are provided on both sides, and a sealing sheet 36 is installed inside to prevent the gas discharged from the exhaust port 16 of the triangular rotor 7 from leaking into the chamber.

[0062] Combine Figure 13 When the compression rotor machine 1 and the expansion rotor machine 2 are working, the rotational speeds of the eccentric shaft 6 and the triangular rotor 7 are different. Therefore, although the inner support arc block 40 and the outer support arc block 24 are always attached to each other, there is relative rotation. In order to ensure that there is no interference during operation, the two ends of the outer support arc block 24 are chamfered outwards, so that the outer arc length of the cross-section of the outer support arc block 24 is greater than the inner arc length. The two ends of the inner support arc block 40 are chamfered inwards, so that the outer arc length of the cross-section of the inner support arc block 40 is less than the outer arc length. A phase angle detection sensor is installed on the eccentric shaft 6 to detect the phase angle of the rotor; the action of the electric three-claw assembly 19 is controlled according to the phase angle of the rotor.

[0063] It should be understood that although this specification is described according to various embodiments, not every embodiment contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

[0064] The series of detailed descriptions listed above are only specific descriptions of feasible embodiments of the present invention. They are not intended to limit the scope of protection of the present invention. Any equivalent embodiments or changes that do not deviate from the technical spirit of the present invention should be included in the scope of protection of the present invention.

Claims

1. A rotor-type Stirling refrigerator, characterized in that: The invention comprises a compression rotor machine (1) and an expansion rotor machine (2), wherein the expansion rotor machine (2) is located at a cold end and the compression rotor machine (1) is located at a hot end; the compression rotor machine (1) has a hot chamber with a periodic volume change; the expansion rotor machine (2) has a cold chamber with a periodic volume change; the phase angle of the rotor in the expansion rotor machine (2) differs by 90° from the phase angle of the rotor in the compression rotor machine (1); The end cover of the compression rotor machine (1) is respectively provided with an air hole communicating with the hot chamber, and the end cover of the expansion rotor machine (2) is respectively provided with an air hole communicating with the cold chamber; the air hole communicating with the hot chamber is communicated with the air hole communicating with the cold chamber via a heat exchange device, wherein the hot chamber with a gradually decreasing volume in the compression rotor machine (1) is communicated with the cold chamber with a gradually increasing volume in the expansion rotor machine (2) via the heat exchange device; the hot chamber with a gradually increasing volume in the compression rotor machine (1) is communicated with the cold chamber with a gradually decreasing volume in the expansion rotor machine (2) via the heat exchange device, and when the hot chamber with a gradually increasing volume is in a state of starting to expand, the cold chamber with a gradually decreasing volume connected thereto is in a state of starting to compress.

2. The rotor-type Stirling refrigerator according to claim 1, characterized in that: The compression rotor machine (1) and the expansion rotor machine (2) both include a cylinder body (8), a triangular rotor (7), a valve assembly and an eccentric shaft (6); The eccentric shaft (6) drives the triangular rotor (7) to rotate in the cylinder body (8), so that the cylinder body (8) has three hot / cold chambers with periodic volume changes; the three arc surfaces of the triangular rotor (7) are respectively provided with three air inlets (15) corresponding to the three hot / cold chambers, and one end surface of the triangular rotor (7) is provided with three exhaust ports (16) corresponding to the three hot / cold chambers, each of the air inlets (15) is connected to its corresponding exhaust port (16) through an internal flow channel (33), and a valve assembly is provided on the internal flow channel (33) for controlling the opening and closing of the air inlet (15) and the exhaust port (16); an end cover (3) is installed on one side of the cylinder body, and the end cover (3) is provided with three sealed flow channels corresponding to the three exhaust ports (16), and the three sealed flow channels are not connected to each other; the end cover (3) is provided with air holes respectively connected to the three sealed flow channels.

3. The rotor-type Stirling refrigerator according to claim 2, characterized in that: The valve assembly comprises a pulley rod (29), a cam (26), a valve block (25), a push rod (27) and an actuator; a retractable valve block (25) is provided in the inner flow channel (33); one end of the valve block (25) is connected to the pulley rod (29), the pulley rod (29) contacts the cam (26), the push rod (27) is movably installed in the first long groove (34) inside the triangular rotor (7), one end of the push rod (27) contacts the cam (26), and the other end of the push rod (27) is connected to the actuator; the push rod (27) is driven by the actuator to move linearly, thereby driving the cam (26) to make the valve block (25) retract and retract in the inner flow channel (33), so as to realize the on-off between the air inlet (15) and the exhaust port (16).

4. The rotor-type Stirling refrigerator according to claim 3, characterized in that: The actuator comprises a T-shaped support rod (23) and an outer support arc block (24); the T-shaped support rod (23) is movably mounted in a T-shaped slot (35) inside the triangular rotor (7); one end of the T-shaped support rod (23) is connected to the outer support arc block (24); the outer support arc block (24) is in contact with the other end of the push rod (27); The eccentric shaft (6) is provided with an electric three-claw assembly (19), and three inner support arc blocks (40) are installed on the electric three-claw assembly (19). The inner support arc blocks (40) are located inside the outer support arc blocks (24). By controlling the electric three-claw assembly (19), the inner support arc blocks (40) are moved linearly, driving the outer support arc blocks (24) to move radially, thereby causing the outer support arc blocks (24) to push the push rod (27) to move linearly.

5. The rotor-type Stirling refrigerator according to claim 4, characterized in that: A contraction spring (30) is provided between the T-shaped support rod (23) and the T-shaped slot (35) for resetting the outer support arc block (24).

6. The rotor-type Stirling refrigerator according to claim 4, characterized in that: The oblique edges at both ends of the outer support arc block (24) are chamfered outwards, and the oblique edges at both ends of the inner support arc block (40) are chamfered inwards, so that the outer arc length of the cross section of the outer support arc block (24) is greater than the outer arc length of the cross section of the inner support arc block (40).

7. The rotor-type Stirling refrigerator according to claim 2, characterized in that: Each sealing flow channel is provided with sealing grooves on both sides and sealing sheets are installed inside.

8. The rotor-type Stirling refrigerator according to claim 4, characterized in that: A phase angle detection sensor is installed on the eccentric shaft (6) for detecting the phase angle of the rotor; and the action of the electric three-claw assembly (19) is controlled according to the phase angle of the rotor.

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