Rotor type Stirling refrigerator

Abstract

The invention provides a rotor type Stirling cryocooler which comprises a compression rotor machine and an expansion rotor machine, the expansion rotor machine is located at the cold end, and the compression rotor machine is located at the hot end; the difference between the phase angle of a rotor in the expansion rotor machine and the phase angle of a rotor in the compression rotor machine is 90 degrees; the end cover of the compression rotor machine is provided with an air hole communicated with the hot chamber, and the end cover of the expansion rotor machine is provided with an air hole communicated with the cold chamber; and the air hole communicated with the hot chamber is communicated with the air hole communicated with the cold chamber through heat exchange equipment. The compressor and the expansion machine are oppositely distributed, one is a hot end, and the other is a cold end, so that the design of the separation cavity can prevent the wall surface heat conduction between the cavities from influencing the circulation, and the temperature difference between different cavities in the rotor machine is reduced.

Description

Technical Field

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

[0002] Stirling refrigerators have the characteristics of 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 the Stirling refrigerator is based on the reverse Stirling cycle. The gas is compressed by the compressor, and then a pressure difference is formed at both ends of the piston inside the regenerator to perform a heat exchange process, so that the fluid circulates in the loop to achieve the purpose of cooling. Most of the existing Stirling refrigerators are piston-type reciprocating structures. However, piston refrigerators are large in size, have strong vibrations and loud noises during operation. In addition, since the dynamic sealing components in the cylinder have a large sliding sealing area, the cylinder and each sealing component need to withstand high temperature and high pressure conditions, which makes the friction and wear between the two due to poor lubrication quite significant, which in turn leads to reduced 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 internal piston load of the regenerator to be too large, resulting in heat waste and increased temperature difference at both ends of the regenerator, which will have a negative impact on the overall thermal efficiency, affect the life of the regenerator, and even cause failures. Summary of the invention

[0004] In view of the shortcomings in the prior art, the present invention provides a rotor-type Stirling refrigerator, in which the compressor and the expander are oppositely distributed, one is the hot end and the other is the cold end. The design of the separation cavity can avoid heat conduction from the wall between the cavities and thus affect the circulation, thereby reducing 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, comprising 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 the 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 the heat exchange device, and when the hot chamber with a gradually increasing volume is in a starting expansion state, the cold chamber with a gradually decreasing volume connected thereto is in a starting compression state.

[0008] Further, 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 side 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 to control the connection and disconnection of the air inlet and the exhaust port; 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, so as to realize the connection and disconnection between the air inlet and the exhaust port.

[0011] Further, the actuator includes a T-shaped support rod and an outer support arc block; the T-shaped support rod is movably installed in a 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, on which three inner supporting arc blocks are installed. The inner supporting arc blocks are located inside the outer supporting arc blocks. The electric three-claw assembly is controlled to make the inner supporting arc blocks move linearly, thereby driving the outer supporting arc blocks to move radially, so that the outer supporting arc blocks push 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 bevels at both ends of the outer supporting arc block are chamfered outwards, and the bevels at 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 sealing 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 the expander are arranged opposite to each other, one is the hot end and the other is the cold end. Such a design of the separation cavity can avoid the heat conduction of the wall between the cavities and thus affect 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 reciprocating mechanism, it has a smaller size and lighter weight, and the friction and wear between the triangular rotor and the cylinder is smaller, so it works more smoothly and has better high-speed performance. 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 drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. 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 It 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 the expansion rotor machine described in the present invention.

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

[0025] Figure 5It is a schematic diagram of assembling the eccentric shaft described in the present invention.

[0026] Figure 6 This is an exploded view of the triangular rotor part 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 in the front part of the triangular rotor.

[0028] Figure 8 It is a schematic diagram of the triangular rotor described in the present invention.

[0029] Fig. 9 This is a layout diagram of the cam described in the present invention.

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

[0031] Fig.11 It is a schematic diagram of the sealing principle on the end cover of the present invention.

[0032] Fig.12 It is a front schematic diagram of the end cover described in the present invention.

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

[0034] Fig.14 The schematic diagram of the control system of the present invention is shown in FIG.

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

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

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

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

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

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

[0041] In the figure:

[0042] 1-compression rotor machine; 2-expansion rotor machine; 3-end cover; 4-regenerator; 5-heat exchange tube; 6-eccentric shaft; 7-triangular rotor; 8-cylinder body; 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-air inlet; 16-exhaust port; 17-first through hole; 18-front part of eccentric shaft; 19-electric three-claw assembly; 20-rear part 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 electric control system; 39-rotating joint; 40-inner support arc block. DETAILED DESCRIPTION

[0043] Embodiments of the present invention are described in detail below, 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 should not 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", "upper", "lower", "axial", "radial", "vertical", "horizontal", "inner", "outer" and the like indicate positions or positional relationships based on the positions 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 only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, 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, the meaning of "multiple" is two or more, unless otherwise clearly and specifically defined.

[0045] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like 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 it can be an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to 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 covers of the compression rotor machine 1 are respectively provided with air holes connected to the hot chamber, and the end covers of the expansion rotor machine 2 are respectively provided with air holes connected to the hot chamber. There are 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 1 is connected to the cold chamber with a gradually increasing volume in the expansion rotor machine 2 through a heat exchange device; the hot chamber with a gradually increasing volume in the compression rotor machine 1 is connected to the cold chamber with a gradually decreasing volume in the expansion rotor machine 2 through a heat exchange device, and when the hot chamber with a gradually increasing volume is in the beginning expansion state, the cold chamber with a gradually decreasing volume connected to it is in the beginning compression state. The compression rotor machine 1 and the expansion rotor machine 2 are distributed separately, which is equivalent to separating the cold end from the hot end, so as to avoid the loss of cold caused by heat conduction of the cylinder body. At the same time, the temperature difference between different cavities in the same rotor machine is extremely small, avoiding the heat conduction of the cavity wall and affecting the circulation. Figure 1 The intermediate heat exchange device comprises a regenerator 4 and a heat exchange tube 5. Both ends of the regenerator 4 are connected to the air holes of the compression rotor machine 1 and the expansion rotor machine 2 through the heat exchange tube 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, and 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 (cold chambers in the expansion rotor machine 2) 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 chambers, and one side end surface of the triangular rotor 7 is provided with three exhaust ports 16 corresponding to the three hot chambers, and each of the air inlets 15 and the corresponding exhaust port 16 is connected through the inner flow channel 33, and a valve assembly is provided on the inner flow channel 3 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. Fig.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 inside the cylinder 8 to change the chamber volume and compress the gas. The compressed air flows through the flow channel 33 inside 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 the air flows through the flow channel inside the end cover 3, it enters the regenerator 4 through the air hole of the sealed flow channel through the heat exchange pipe 5, while the inside of the expansion 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 Fig. 9 As shown, in order to facilitate the installation of the valve assembly, the triangular rotor 7 is divided into a rotor front part 22 and a rotor rear part 21, which are assembled by bolts, and a seal is designed. 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 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 cam 26 is located in the first groove 32 inside the triangular rotor 7, 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, and the push rod 27 is driven by the actuator to move linearly, thereby driving the cam 26 to make the valve block 25 retract in the inner flow channel 33, which is used to realize the connection and disconnection 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 central hole of the triangular rotor 7 is provided with a concentric annular groove 31, and the annular groove 31 and the central hole form a step shape. The central hole and the eccentric shaft 6 realize transmission.

[0051] The T-shaped support rod 23 is movably installed 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 Fig.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 of the electric three-claws is 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 9 is provided with a first through hole 17, in which the wire for controlling the electric three-claw assembly 19 is fixed; 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 Fig.13 As shown, three inner support arc blocks 40 are installed on the electric three-claw assembly 19, and the inner support arc block 40 is located inside the outer support arc block 24. It can also be considered that the inner support arc block 40 is located at the annular groove 31. By controlling the electric three-claw assembly 19, the inner support arc block 40 is moved linearly, driving the outer support arc block 24 to move radially, so that the outer support arc block 24 pushes 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 for resetting the outer support arc block 24. The two ends of the outer support arc block 24 are chamfered outwards, and 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 outer support arc block 24 is greater than the outer arc length of the cross section of the inner support arc block 40.

[0052] like Fig.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 being at the top dead center is very short, it is assumed 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 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 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 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 tube 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 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 29 of the triangular rotor 7 and the second 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 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] Fig.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 with 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 with 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 with 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] Fig.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 tube 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 tube 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 tube 5, and the gas flow enters the cold chamber E through the second air hole 10 of the expander, and the gas expands, and the temperature and pressure are reduced, absorbing the heat of the surrounding environment, so that its own temperature remains unchanged, and an isothermal expansion process is performed.

[0056] like Fig.16 and Fig.17 As shown in the figure, the triangular rotor 7 of the compressor 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 hot chamber B of the compressor gradually increases during the counterclockwise rotation of the triangular rotor 7 of the compressor, while the volume of the corresponding cold chamber E gradually decreases. At this time, when the cold chamber E of the expander begins to compress, the gas is pushed through the regenerator 4 to absorb heat and return to the hot chamber B of the compressor.

[0057] Fig.18 and Fig.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, and 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] Fig.19 and Fig. 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 cold chamber E of the expander begins to compress, the gas is pushed through the regenerator 4 to absorb heat and return to the hot chamber B of the compressor.

[0059] Fig. 20 and Fig.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 hot chamber B of the compressor gradually decreases, while the volume of the corresponding cold chamber E gradually increases. The gas in the hot chamber B of the compressor is pushed through the regenerator 4 to absorb heat and enter the cold chamber E of the expander.

[0060] It can be seen from the flow chart that when the hot chamber B starts to compress, the gas is 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. Then the gas enters the regenerator 4 through the heat exchange tube 5, and the gas absorbs heat and performs an isochoric heat release process. Then the gas enters the cold chamber E, the gas expands, the temperature and pressure are reduced, and the surrounding environment heat is absorbed, so that its own temperature remains unchanged, and an isothermal expansion process is performed. When the cold chamber E starts to compress, the gas is pushed through the regenerator 4 to absorb heat and return to the hot chamber B. At this point, a Stirling reverse cycle is completed. In this cycle, the gas continuously absorbs heat in the expander chamber, while the compressor chamber continuously absorbs gas heat, and the temperature of the cold end chamber continues to decrease, achieving a refrigeration effect. The three chambers of the compressor correspond one to one with the three chambers of the expander, and three Stirling reverse cycles are performed at the same time. The Stirling refrigerator takes advantage of the small size and high power density of the rotor machine, and separates the cold end from the hot end, which greatly improves the refrigeration efficiency.

[0061] like Fig.11 and Fig.12 Since the triangular rotor 7 rotates on one side of the end surface 3, sealing measures need to be taken in the process of the airflow entering the flow channel of the end surface 3 through the exhaust port 16. Fig.14 According to the length and width of the exhaust port 19 on the end face of the triangular rotor 7 and the movement trajectory of the triangular rotor 7 with 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] Combination Fig.13 When the compression rotor machine 1 and the expansion rotor machine 2 are working, the rotation 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 beveled edges 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 beveled edges 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 may 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. All 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 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 from the phase angle of the rotor in the compression rotor machine (1) by 90°; The end cover of the compression rotor machine (1) is respectively provided with air holes connected to the hot chamber, and the end cover of the expansion rotor machine (2) is 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 via a heat exchange device, wherein the hot chamber with a gradually decreasing volume in the compression rotor machine (1) is connected to 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 connected to 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 starting expansion state, the cold chamber with a gradually decreasing volume connected to it is in a starting compression state.

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 comprise 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; 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 side 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 (3) 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 three sealed flow channels corresponding to the three exhaust ports (16) are provided on the end cover (3), 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 arranged 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 mounted in a 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 installed 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 supporting arc blocks (40) are installed on the electric three-claw assembly (19). The inner supporting arc blocks (40) are located inside the outer supporting arc blocks (24). By controlling the electric three-claw assembly (19), the inner supporting arc blocks (40) are moved linearly, driving the outer supporting arc blocks (24) to move radially, so that the outer supporting arc blocks (24) 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 groove (35) for resetting the outer support arc block (24).

6. The rotor-type Stirling refrigerator according to claim 4, characterized in that: The bevels at both ends of the outer support arc block (24) are chamfered outwards, and the bevels 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 has sealing grooves on both sides and sealing sheets 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) 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.

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