Cam Stirling refrigerator

Abstract

The invention discloses a cam Stirling cryocooler which comprises a shell, a first piston, a second piston, a heat exchange pipeline, a first cam set and a second cam set. The shell is provided with a cold-hot cavity. The first piston is arranged in the cold and hot cavity; the second piston is arranged in the cold and hot cavity and is spaced from the first piston; the end, away from the second piston, of the first piston and the shell form a first cavity, and a second cavity is formed among the first piston, the second piston and the shell. The heat exchange pipeline is communicated with the first cavity and the second cavity; the first cam group is arranged on the side, away from the first piston, of the second piston and is in transmission connection with the first piston. The second cam set is arranged on the side, away from the first piston, of the second piston and is in transmission connection with the second piston, the cam Stirling cryocooler can improve the refrigeration efficiency, the structural size is reduced, the service life is prolonged, the maintenance cost is reduced, and the cam Stirling cryocooler is applied to the technical field of low-temperature refrigeration.

Description

Technical Field

[0001] The present invention relates to the technical field of low-temperature refrigeration, in particular to a cam Stirling refrigerator. Background Art

[0002] The Stirling cycle, proposed by Robert Stirling in 1816, was initially used as a heat engine and later developed for refrigeration through a reverse cycle (the reverse Stirling cycle). Its core principle is to convert heat energy through the processes of isothermal compression, isochoric heat release, isothermal expansion, and isochoric heat absorption of a gas. It is chemical-free, highly efficient, and environmentally friendly. Modern Stirling refrigerators are widely used in aerospace (such as cooling satellite infrared detectors), medicine (MRI equipment), and industry (cooling superconducting magnets).

[0003] A Stirling refrigerator is a closed-loop refrigeration device based on the reverse Stirling cycle. Its operating principle is based on the cyclic compression and expansion of a working fluid (such as helium or hydrogen). Core components include a heat exchanger, a cold exchanger, a regenerator, and a power transmission system. Because the working fluid circulates within a closed system, current refrigerators require a mechanical transmission mechanism to convert the rotational input into reciprocating motion of the piston. Traditional transmission methods (such as crankshafts) suffer from poor balance and high sealing requirements, prompting the exploration of novel structures such as cam transmissions.

[0004] In related technologies, the transmission system design of the Stirling refrigerator directly affects the power density and applicable scenarios. The early transmission mechanism was a crank-connecting rod mechanism: borrowing from the internal combustion engine technology, it needed to cooperate with the crosshead to maintain the vertical movement of the piston. The structure was simple but the balance was insufficient. And there are the following disadvantages: 1. Insufficient phase control: The phase difference between the compression piston and the expansion piston needs to be precisely adjusted to optimize efficiency, but traditional mechanical structures (such as crank-connecting rods) are difficult to dynamically adjust the phase. 2. Volume and vibration: The split structure driven by the linear motor is large in volume, and the free piston relies on a pneumatic spring, which is prone to vibration and reduced life due to gas leakage. 3. Friction loss: The contact friction of traditional transmission mechanisms (such as cams and connecting rods) will reduce energy efficiency and increase maintenance requirements. Summary of the Invention

[0005] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a cam Stirling refrigerator that can improve refrigeration efficiency, reduce structural volume, increase service life, and reduce maintenance costs.

[0006] A cam Stirling refrigerator according to an embodiment of the present invention includes: a housing having hot and cold cavities; a first piston disposed within the hot and cold chambers; a second piston, disposed in the hot and cold chambers and spaced apart from the first piston; Wherein, one end of the first piston away from the second piston forms a first cavity with the housing, and a second cavity is formed between the first piston, the second piston and the housing; a heat exchange pipeline, communicating with the first chamber and the second chamber; a first cam assembly, disposed on a side of the second piston away from the first piston and drivingly connected to the first piston; The second cam group is arranged on a side of the second piston away from the first piston and is transmission-connected to the second piston.

[0007] The cam Stirling refrigerator according to the embodiment of the present invention has at least the following beneficial effects: the first piston and the second piston are integrated into the same housing, thereby reducing the overall size of the structure and thus reducing the overall device volume; at the same time, the first cam group and the second cam group respectively drive the first piston and the second piston, so that the movement of the first piston and the second piston in the hot and cold chambers can complete the cooling, thereby improving the cooling efficiency; and the transmission method of the first cam group and the second cam group can also effectively increase the service life and reduce the maintenance cost.

[0008] According to some embodiments of the present invention, the cam Stirling refrigerator has an isothermal compression stage, an isochoric heat release stage, an isothermal expansion stage, and an isochoric heat absorption stage, and the first cam group and the second cam group are configured as follows: During the isothermal compression stage, the first cam group drives the first piston to remain substantially stationary, and the second cam group drives the second piston to compress the second chamber; During the isochoric heat release stage, the first cam group drives the first piston to expand the first chamber and shrink the second chamber, and the second cam group drives the second piston to remain substantially stationary; During the isothermal expansion stage, the first cam group drives the first piston to expand the first chamber and compress the second chamber, and the second cam group drives the second piston to expand the second chamber, and the volume of the second chamber remains substantially unchanged; During the isochoric heat absorption stage, the first cam group drives the first piston to reduce the first chamber and expand the second chamber, and the second cam group drives the second piston to remain substantially stationary.

[0009] According to some embodiments of the present invention, the first cam group includes at least one first cam, and the stroke formula of the first cam is as follows: ; s: cam stroke; θ: The angle of cam rotation.

[0010] According to some embodiments of the present invention, the second cam group includes at least one second cam, and the stroke formula of the second cam is as follows: ; s: cam stroke; θ: The angle of cam rotation.

[0011] According to some embodiments of the present invention, further comprising a transmission assembly; The transmission assembly includes a first transmission rod and a second transmission rod. The first transmission rod is inserted into the second piston. One end of the first transmission rod is transmission-connected between the first piston and the first cam group. The second transmission rod is transmission-connected between the second piston and the second cam group.

[0012] According to some embodiments of the present invention, the transmission assembly further includes a first elastic member, a second elastic member, a first rolling abutment member, and a second rolling abutment member, the first elastic member being connected between the first piston and the second piston, the first rolling abutment member being rotatably arranged at one end of the first transmission rod, and the first rolling abutment member being rotatably abutted against the first cam group, the second elastic member being arranged between the first rolling abutment member and the second transmission rod, and the second rolling abutment member being rotatably abutted against the second cam group.

[0013] According to some embodiments of the present invention, a driving source is further included, wherein the driving source has an output shaft, and the output shaft is transmission-connected to the first cam group and the second cam group.

[0014] According to some embodiments of the present invention, the heat exchange pipeline includes a heat exchanger, a regenerator and a cold exchanger connected in sequence, the cold exchanger is connected to the first chamber, the heat exchanger is connected to the second chamber, and the regenerator is used to exchange heat with the heat medium.

[0015] According to some embodiments of the present invention, the heat exchanger includes a plurality of heat exchange cavities, and the plurality of heat exchange cavities are sequentially distributed around the circumference of the shell; And / or, the regenerator comprises a plurality of regenerating cavities, and the plurality of regenerating cavities are sequentially distributed around the circumference of the shell; And / or, the cold exchanger includes a plurality of cold exchange pipes, and the plurality of cold exchange pipes are sequentially distributed around the circumference of the shell.

[0016] According to some embodiments of the present invention, the heat exchange chamber includes a plurality of heat exchange pipes connecting the regenerator and the second chamber.

[0017] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The present invention will be further described below with reference to the accompanying drawings and embodiments, in which: Figure 1 This is a structural diagram of a cam Stirling refrigerator according to an embodiment of the present invention; Figure 2 A schematic cross-sectional view of a cam Stirling refrigerator in an isothermal compression stage according to an embodiment of the present invention; Figure 3 A schematic cross-sectional view of a cam Stirling refrigerator in the isochoric heat release stage according to an embodiment of the present invention; Figure 4 A schematic cross-sectional view of a cam Stirling refrigerator in an isothermal expansion stage according to an embodiment of the present invention; Figure 5 A schematic cross-sectional view of a cam Stirling refrigerator in an isochoric endothermic stage according to an embodiment of the present invention; Figure 6 A cross-sectional schematic diagram of a cam Stirling refrigerator according to an embodiment of the present invention, after the first elastic member and the second elastic member are hidden in the isochoric endothermic stage; Figure 7 A coordinate diagram of temperature changes of a cam Stirling refrigerator at various stages according to an embodiment of the present invention; Figure 8 A simplified schematic diagram of a cam Stirling refrigerator in various stages according to an embodiment of the present invention is shown; Figure 9 A coordinate diagram of the stroke and rotation angle of the first cam group of a cam Stirling refrigerator according to an embodiment of the present invention; Figure 10 A coordinate diagram of the stroke and rotation angle of the second cam group of a cam Stirling refrigerator according to an embodiment of the present invention; Figure Number: Housing 100; hot and cold chamber 101; first chamber 102; second chamber 103; a first piston 200; Second piston 300; Heat exchange pipeline 400; heat exchanger 410; heat exchange pipe 411; regenerator 420; cold exchanger 430; hot fixing sleeve 440; cold fixing sleeve 450; First cam group 500; Second cam group 600; Transmission assembly 700 ; first transmission rod 710 ; second transmission rod 720 ; first elastic member 730 ; second elastic member 740 ; first rolling abutment member 750 ; second rolling abutment member 760 . DETAILED DESCRIPTION

[0019] The following describes embodiments of the present invention in detail. Examples of the embodiments 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 only to explain the present invention and are not to be construed as limiting the present invention.

[0020] In the description of the present invention, it should be understood that descriptions involving orientation, such as the orientation or positional relationship indicated by up, down, etc., are based on the orientation or positional relationship 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 a limitation on the present invention.

[0021] In the description of the present invention, "a number" refers to one or more, and "a plurality" refers to two or more. The terms "first" and "second" are used solely to distinguish technical features and are not to be construed as indicating or implying relative importance, or as implicitly indicating the number or order of the technical features.

[0022] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, and connecting should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0023] In related technologies, the transmission system design of the Stirling refrigerator directly affects the power density and applicable scenarios. The early transmission mechanism was a crank-connecting rod mechanism: borrowing from the internal combustion engine technology, it needed to cooperate with the crosshead to maintain the vertical movement of the piston. The structure was simple but the balance was insufficient. And there are the following disadvantages: 1. Insufficient phase control: The phase difference between the compression piston and the expansion piston needs to be precisely adjusted to optimize efficiency, but traditional mechanical structures (such as crank-connecting rods) are difficult to dynamically adjust the phase. 2. Volume and vibration: The split structure driven by the linear motor is large in volume, and the free piston relies on a pneumatic spring, which is prone to vibration and reduced life due to gas leakage. 3. Friction loss: The contact friction of traditional transmission mechanisms (such as cams and connecting rods) will reduce energy efficiency and increase maintenance requirements.

[0024] Reference Figures 1 to 10 As shown, an embodiment of the present invention provides a cam Stirling refrigerator, comprising: a housing 100 , a first piston 200 , a second piston 300 , a heat exchange pipeline 400 , a first cam group 500 and a second cam group 600 .

[0025] In this embodiment, a hot and cold cavity 101 is formed inside the shell 100. The shell 100 is cylindrical, one end of the shell 100 is provided with an opening, and the other end remains closed, and the end surface of the other end is spherical or flat or other shapes. The spherical end surface can increase the heat exchange area and improve the heat exchange efficiency.

[0026] The first piston 200 is disposed within the hot and cold chambers 101. The outer circumferential surface of the first piston 200 and the inner circumferential surface of the hot and cold chambers 101 formed by the housing 100 maintain a substantially sealed state, or are separated from the inner circumferential surface of the hot and cold chambers 101 by a small gap, so that the first piston 200 can slide smoothly relative to the housing 100 without generating friction with the housing 100, thereby reducing friction loss and frictional heat.

[0027] The second piston 300 is arranged in the hot and cold chamber 101 and is spaced apart from the first piston 200. The outer peripheral surface of the second piston 300 and the inner peripheral surface of the hot and cold chamber 101 formed by the shell 100 maintain a basically sealed state. At the same time, the second piston 300 seals the end of the shell 100 where the opening is located to achieve sealing of the shell 100, and a sealed chamber is formed in the shell 100, wherein the second piston 300 can move relative to the shell 100, and the second piston 300 can maintain a sealed state with the shell 100 during the movement, so that the second piston 300 achieves a sliding seal.

[0028] Among them, the end of the first piston 200 away from the second piston 300 forms a first chamber 102 with the shell 100, and a second chamber 103 is formed between the first piston 200, the second piston 300 and the shell 100; in this embodiment, the first chamber 102 is an expansion chamber, and the second chamber 103 is a compression chamber. The expansion chamber is used to expand the gas space and reduce the pressure, thereby achieving cooling, and the compression chamber is used to squeeze the gas space and increase the pressure, thereby achieving heating. In actual use, the first chamber 102 achieves cooling and the second chamber 103 is used for heat dissipation.

[0029] The heat exchange pipeline 400 is connected to the first chamber 102 and the second chamber 103, so that the gas in the first chamber 102 and the second chamber 103 is connected. The gas is the heat exchange medium, which can be air. In order to improve the heat exchange efficiency, the heat exchange medium can also be hydrogen or helium.

[0030] The first cam group 500 is arranged on the side of the second piston 300 away from the first piston 200 and is transmission-connected to the first piston 200. The first cam group 500 is transmission-connected to the first piston 200, thereby driving the first piston 200 to move relative to the second piston 300 along the axial direction of the shell 100 and realize the increase or decrease of the expansion chamber. Through the reciprocating movement of the first piston 200, the first chamber 102 can be continuously cooled to realize the cooling function.

[0031] The second cam group 600 is arranged on the side of the second piston 300 away from the first piston 200 and is transmission-connected to the second piston 300. The second cam group 600 is transmission-connected to the second piston 300, thereby driving the second piston 300 to move relative to the first piston 200 along the axial direction of the shell 100 and realize the increase or decrease of the compression chamber. Through the reciprocating movement of the second piston 300, the second chamber 103 can continuously dissipate heat, so that heat is discharged from the second chamber 103 of the shell 100, thereby meeting the cooling demand.

[0032] It is worth noting that the first piston 200 and the second piston 300 are integrated into the same housing 100, which reduces the overall size of the structure to reduce the overall device volume; at the same time, the first cam group 500 and the second cam group 600 respectively transmit the first piston 200 and the second piston 300. Compared with the pneumatic spring driving the first piston 200 and the second piston 300, the rotation of the first cam group 500 and the second cam group 600 is easier to control, so that the movement accuracy of the first piston 200 and the second piston 300 in the hot and cold chamber 101 is higher, thereby improving the cooling efficiency, and the service life of the first cam group 500 and the second cam group 600 is longer than that of the pneumatic spring.

[0033] Reference Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 、 Figure 6 、 Figure 7 and Figure 8 As shown, in some specific embodiments of the present invention, the cam Stirling refrigerator has an isothermal compression stage, an isochoric heat release stage, an isothermal expansion stage, and an isochoric heat absorption stage, and the first cam group 500 and the second cam group 600 are configured as follows: During the isothermal compression stage, the first cam group 500 drives the first piston 200 to remain substantially stationary, and the second cam group 600 drives the second piston 300 to compress the second chamber 103; During the isochoric heat release stage, the first cam assembly 500 drives the first piston 200 to expand the first chamber 102 and shrink the second chamber 103, and the second cam assembly 600 drives the second piston 300 to remain substantially stationary. During the isothermal expansion stage, the first cam assembly 500 drives the first piston 200 to expand the first chamber 102 and compress the second chamber 103. The second cam assembly 600 drives the second piston 300 to expand the second chamber 103. The volume of the second chamber 103 remains substantially unchanged. During the isochoric endothermic stage, the first cam group 500 drives the first piston 200 to reduce the first chamber 102 and expand the second chamber 103 , and the second cam group 600 drives the second piston 300 to remain substantially stationary.

[0034] In this embodiment, referring to Figure 2 、 Figure 7 and Figure 8 The isothermal compression stage means that: the first piston 200 is stationary, so that the first chamber 102 remains stationary; the second piston 300 moves toward the first piston 200 and compresses the second chamber 103. During the compression process, the heat exchange medium is squeezed, the pressure of the heat exchange medium increases, and the temperature increases at the same time. However, due to the existence of the heat exchange pipe 400, the heat of the heat exchange medium will be exchanged with the heat exchange pipe 400 in time and dissipated, so that the temperature of the heat exchange medium remains basically unchanged. Therefore, this stage is called isothermal compression, that is, the temperature of the heat exchange medium remains unchanged, but the pressure increases (the temperature change of the heat exchange medium is shown in the attached figure). Figure 6 The isothermal compression is shown by the dashed line. The temperature of the heat exchange medium remains unchanged, but the portion of the heat exchange pipe 400 connected to the second chamber 103 absorbs the heat of the heat exchange medium and dissipates the heat. Therefore, the temperature of the portion of the heat exchange pipe 411 directly connected to the second chamber 103 will increase. It should be noted that during actual operation, the temperature of the heat exchange medium rises together with the temperature of the heat exchange pipe 400 (the temperature change of the heat exchange medium is shown in the attached figure). Figure 6 isothermal compression shown by the solid line).

[0035] Reference Figure 3 、 Figure 7 and Figure 8 The isochoric heat release stage refers to the following: the first piston 200 moves toward the second piston 300, thereby expanding the first chamber 102 and compressing the second chamber 103; the second piston 300 stops moving. During the isochoric heat release process, the compressed heat exchange medium in the second chamber 103 moves through the heat exchange pipe 400 into the first chamber 102, so that the overall capacity of the heat exchange medium remains basically unchanged. During the movement, the heat exchange medium exchanges heat with the heat exchange pipe 400, so that the heat of the heat exchange medium is transferred to the heat exchange pipe 400, thereby cooling the heat exchange medium. As shown in the attached figure Figure X The isochoric exotherm is shown by the solid line.

[0036] Reference Figure 4 、 Figure 7 and Figure 8The isothermal expansion stage refers to the following: the first piston 200 moves toward the second piston 300, thereby expanding the first chamber 102. At the same time, the second piston 300 moves in a direction away from the first piston 200. The movement of the first piston 200 and the second piston 300 will keep the second chamber 103 basically unchanged. During the isothermal expansion process, the volume of the first chamber 102 increases, the pressure of the heat exchange medium decreases, and the gas temperature drops. However, due to the presence of the heat exchange pipe 411, the heat of the heat exchange medium will be exchanged with the heat exchange pipe 400 in a timely manner, causing the temperature of the heat exchange pipe 400 to drop, while the temperature of the heat exchange medium remains basically unchanged. Therefore, this stage is called isothermal compression, that is, the temperature of the heat exchange medium remains unchanged, but the pressure decreases (the temperature change of the heat exchange medium is shown in the attached figure). Figure 6 The isothermal expansion is shown by the dashed line. The temperature of the heat exchange medium remains unchanged, but the portion of the heat exchange pipe 400 connected to the first chamber 102 absorbs the heat of the heat exchange medium and its temperature decreases, thus achieving refrigeration. Therefore, the temperature of the portion of the heat exchange pipe 411 directly connected to the second chamber 103 will continue to decrease. It should be noted that, during actual operation, the temperature of the heat exchange medium will also rise (the temperature change of the heat exchange medium is shown in the attached figure). Figure 6 isothermal expansion shown by the solid line).

[0037] Reference Figure 5 、 Figure 6 、 Figure 7 and Figure 8 The isochoric heat absorption stage occurs when the first piston 200 moves away from the second piston 300 while the second piston 300 remains stationary, thereby reducing the first chamber 102 and expanding the second chamber 103. The total volume of the first and second chambers 102 and 103 remains essentially unchanged. During the isochoric heat absorption process, the heat exchange medium passes through the heat exchange pipe 400 again, exchanging heat with the heat exchange pipe 400 and absorbing heat. This causes the volume of the heat exchange medium to remain unchanged, but the temperature to increase.

[0038] It should be noted that during the above stages, the first chamber 102, the heat exchange pipeline 400, and the second chamber 103 all remain connected. Specifically, during the isothermal expansion process, the first piston 200 and the second piston 300 together drive the second chamber 103 away from the first chamber 102. During this distance, the second chamber 103 remains connected to the heat exchange pipeline 400. In this embodiment, the first piston 200 includes a main body sealing portion and a spacer communication portion. The main body sealing portion is connected to the end of the spacer communication portion away from the second piston 300. The outer circumference of the main body sealing portion is sealed against the inner circumference of the hot and cold chambers 101 formed by the housing 100, or a slight gap is formed between the outer circumference of the main body sealing portion and the inner circumference of the hot and cold chambers 101 formed by the housing 100; and a larger gap is formed between the spacer communication portion and the inner circumference of the hot and cold chambers 101 formed by the housing 100, thereby ensuring communication between the second chamber 103 and the heat exchange pipeline 400.

[0039] It is worth understanding that in the isochoric heat release or isochoric heat absorption stage, only the first piston 200 needs to move axially along the housing 100, and the second piston 300 remains stationary. The second piston 300 has less movement, less friction loss, and longer service life.

[0040] Reference Figure 9 As shown, in some specific embodiments of the present invention, the first cam group 500 includes at least one first cam, and the stroke formula of the first cam is as follows: ; s: cam stroke; θ: The angle of cam rotation.

[0041] In this embodiment, the relationship between the stroke and the rotation angle of the first cam is shown in the attached figure. Figure 9 shown.

[0042] The relationship between the specific stroke data and angle of the first cam is shown in Table 1: Table 1. Rotation angle and lift data of the first cam

[0043] Reference Figure 10 As shown, in some specific embodiments of the present invention, the second cam group 600 includes at least one second cam, and the stroke formula of the second cam is as follows: ; s: cam stroke; θ: The angle of cam rotation.

[0044] In this embodiment, the curve relationship between the stroke of the second cam and the rotation angle is shown in the attached figure. Figure 10 shown.

[0045] The relationship between the specific stroke data and angle of the second cam is shown in Table 2: Table 2. Rotation angle and lift data of the second cam

[0046] Reference Figure 2 、 Figure 3 、 Figure 4 and Figure 5 As shown, in some specific embodiments of the present invention, a transmission assembly 700 is further included; the transmission assembly 700 includes a first transmission rod 710 and a second transmission rod 720, the first transmission rod 710 is passed through the second piston 300, one end of the first transmission rod 710 is transmission-connected between the first piston 200 and the first cam group 500, and the second transmission rod 720 is transmission-connected between the second piston 300 and the second cam group 600.

[0047] In this embodiment, the second piston 300 and the second transmission rod 720 are integrally formed, and the first transmission rod 710 is passed through both the second transmission rod 720 and the second piston 300. As another embodiment, the second transmission rod 720 can also be arranged in parallel with the first transmission rod 710, the first transmission rod 710 is passed through the second piston 300, and the second transmission rod 720 is connected to the second piston 300.

[0048] Reference Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 and Figure 6 As shown, in some specific embodiments of the present invention, the transmission assembly 700 also includes a first elastic member 730, a second elastic member 740, a first rolling abutment member 750 and a second rolling abutment member 760, the first elastic member 730 is connected between the first piston 200 and the second piston 300, the first rolling abutment member 750 is rotatably arranged at one end of the first transmission rod 710, and the first rolling abutment member 750 is rotatably abutted against the first cam group 500, the second elastic member 740 is arranged between the first rolling abutment member 750 and the second transmission rod 720, and the second rolling abutment member 760 is rotatably abutted against the second cam group 600.

[0049] In this embodiment, the first transmission rod 710 abuts against the outer circumferential surface of the cam in the first cam group 500 via the first rolling abutment 750. When the cam in the first cam group 500 rotates, the first rolling abutment 750 also rotates accordingly. At the same time, the first transmission rod 710 rises and falls accordingly as the radius of the cam in the first cam group 500 changes, thereby achieving transmission of the first transmission rod 710. The second transmission rod 720 drives and raises the cam in the second cam group 600 via the second rolling abutment 760. The first cam group 500 includes one cam, and the second cam group 600 includes two cams. The two cams of the second cam group 600 are respectively arranged on either side of the first cam group 500 to ensure overall force balance.

[0050] In this embodiment, the first transmission rod 710 is arranged in the middle of the second piston 300, and the outer peripheral surface of the second piston 300 is basically flush with the outer peripheral surface of the second transmission rod 720, so that the second piston 300 can seal the hot and cold chambers 101 in the shell 100 together with the second transmission rod 720, thereby achieving sealing of the shell 100.

[0051] Among them, the first elastic member 730 is arranged between the first piston 200 and the second piston 300, and is used to limit the relative movement between the first piston 200 and the second piston 300. By limiting the relative movement of the first piston 200 and the second piston 300, the first rolling abutment member 750 can be continuously abutted against the outer peripheral surface of the cam in the first cam group 500, and the first piston 200 will also drive the first transmission rod 710 under the action of its own weight, so that the first rolling abutment member 750 can be continuously abutted against the outer peripheral surface of the cam in the first cam group 500; similarly, the second piston 300 will also drive the second transmission rod 720 under the action of its own weight, so that the first elastic member 730 can also enable the second rolling abutment member 760 to be continuously abutted against the outer peripheral surface of the cam in the second cam group 600. In this embodiment, the first elastic member 730 is arranged on the first piston 200 and surrounds the first transmission rod 710, and is located between the end face of the first piston 200 and the end face of the second piston 300. The end face of the first piston 200 and / or the end face of the second piston 300 has a groove for accommodating the first elastic member 730, so that the first elastic member 730 can have a sufficient stretching length through the groove, or a portion of the first elastic member 730 is arranged on the outer periphery of the spacer connecting portion, one end of which is in contact with the main body sealing portion, and the other end of which is in contact with the second piston 300.

[0052] The second elastic member 740 is provided between the first rolling abutment member 750 and the second transmission rod 720 . The function of the second elastic member 740 is the same as that of the first elastic member 730 , and will not be described in detail here.

[0053] In some specific embodiments of the present invention, a driving source is further included. The driving source has an output shaft, and the output shaft is drivingly connected to the first cam group 500 and the second cam group 600 .

[0054] In this embodiment, the driving source includes a motor, the motor has an output shaft, the output shaft includes a shaft body and a transmission key arranged on the outer periphery of the shaft body, and the output shaft sequentially transmits the first cam group 500 and the second cam group 600, so that the first cam group 500 and the second cam group 600 rotate synchronously, that is, the ratio of the angular velocity of the first cam group 500 and the second cam group 600 is 1:1.

[0055] Reference Figure 2 、 Figure 3 、 Figure 4 and Figure 5 As shown, in some specific embodiments of the present invention, the heat exchange pipeline 400 includes a heat exchanger 410, a regenerator 420 and a cold exchanger 430 connected in sequence, the cold exchanger 430 is connected to the first chamber 102, the heat exchanger 410 is connected to the second chamber 103, and the regenerator 420 is used to exchange heat with the heat medium.

[0056] In this embodiment, the heat exchanger 410 is used to dissipate heat, the regenerator 420 is used to improve the heat exchange efficiency with the heat exchange medium, so that the heat dissipation efficiency of the heat exchanger 410 is higher, and the cold exchanger 430 is used to exchange heat with the heat exchange medium and for cooling.

[0057] Reference Figure 2 、 Figure 3 、 Figure 4 and Figure 5 As shown, in some specific embodiments of the present invention, the heat exchanger 410 includes a plurality of heat exchange cavities, which are distributed in sequence around the circumference of the shell 100; and / or, the regenerator 420 includes a plurality of heat recovery cavities, which are distributed in sequence around the circumference of the shell 100; and / or, the cold exchanger 430 includes a plurality of cold exchange pipes, which are distributed in sequence around the circumference of the shell 100.

[0058] It is worth understanding that multiple heat exchange cavities, multiple heat recovery cavities, and multiple cold exchange pipes can improve the heat exchange efficiency and improve the uniformity of heat exchange along the circumference of the shell 100.

[0059] In this embodiment, the heat exchange piping 400 further includes a heat fixing sleeve 440 and a cold fixing sleeve 450. The heat fixing sleeve 440 surrounds and is fixed to the housing 100, and is used to fix each heat exchange cavity, so that each heat exchange cavity can be evenly spaced along the circumference of the housing 100, which is more conducive to heat dissipation. The cold fixing sleeve 450 surrounds the cold exchanger 430 and fixes each cold exchange pipe, so that each cold exchange pipe can be evenly spaced along the circumference of the housing 100, which is more conducive to uniform cooling. Furthermore, the evenly arranged heat exchange cavities and cold exchange pipes further facilitate the uniform distribution of the heat exchange medium along the circumference of the housing 100, avoiding excessive local pressure.

[0060] Reference Figure 2 、 Figure 3 、 Figure 4 and Figure 5 As shown, in some specific embodiments of the present invention, the heat exchange chamber includes multiple heat exchange pipes 411 connecting the regenerator 420 and the second chamber 103. It is worth noting that each heat exchange pipe 411 can increase the heat exchange area, thereby improving the heat exchange efficiency and achieving better heat dissipation effect of the heat exchange chamber.

[0061] The embodiments of the present invention are described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Various changes can be made within the scope of knowledge possessed by ordinary technicians in the relevant technical field without departing from the scope of the present invention.

Claims

1. A cam Stirling refrigerator, characterized in that: include: a housing having hot and cold cavities; a first piston disposed within the hot and cold chambers; a second piston, disposed in the hot and cold chambers and spaced apart from the first piston; Wherein, one end of the first piston away from the second piston forms a first cavity with the housing, and a second cavity is formed between the first piston, the second piston and the housing; a heat exchange pipeline, communicating with the first chamber and the second chamber; a first cam assembly, disposed on a side of the second piston away from the first piston and drivingly connected to the first piston; The second cam group is arranged on a side of the second piston away from the first piston and is transmission-connected to the second piston.

2. The cam Stirling refrigerator according to claim 1, characterized in that: The cam Stirling refrigerator has an isothermal compression stage, an isochoric heat release stage, an isothermal expansion stage, and an isochoric heat absorption stage. The first cam group and the second cam group are configured as follows: During the isothermal compression stage, the first cam group drives the first piston to remain substantially stationary, and the second cam group drives the second piston to compress the second chamber; During the isochoric heat release stage, the first cam group drives the first piston to expand the first chamber and shrink the second chamber, and the second cam group drives the second piston to remain substantially stationary; During the isothermal expansion stage, the first cam group drives the first piston to expand the first chamber and compress the second chamber, and the second cam group drives the second piston to expand the second chamber, and the volume of the second chamber remains substantially unchanged; During the isochoric heat absorption stage, the first cam group drives the first piston to reduce the first chamber and expand the second chamber, and the second cam group drives the second piston to remain substantially stationary.

3. The cam Stirling refrigerator according to claim 1, characterized in that: The first cam group includes at least one first cam, and the stroke formula of the first cam is as follows: ； s: cam stroke; θ: Angle of cam rotation.

4. The cam Stirling refrigerator according to claim 1, characterized in that: The second cam group includes at least one second cam, and the stroke formula of the second cam is as follows: ； s: cam stroke; θ: The angle of cam rotation.

5. The cam Stirling refrigerator according to claim 1, characterized in that: Also included are transmission components; The transmission assembly includes a first transmission rod and a second transmission rod. The first transmission rod is inserted into the second piston. One end of the first transmission rod is transmission-connected between the first piston and the first cam group. The second transmission rod is transmission-connected between the second piston and the second cam group.

6. The cam Stirling refrigerator according to claim 5, characterized in that: The transmission assembly also includes a first elastic member, a second elastic member, a first rolling abutment member, and a second rolling abutment member. The first elastic member is connected between the first piston and the second piston. The first rolling abutment member is rotatably arranged at one end of the first transmission rod, and the first rolling abutment member is rotatably abutted against the first cam group. The second elastic member is arranged between the first rolling abutment member and the second transmission rod, and the second rolling abutment member is rotatably abutted against the second cam group.

7. The cam Stirling refrigerator according to claim 1, characterized in that: It also includes a driving source, which has an output shaft, and the output shaft is transmission-connected to the first cam group and the second cam group.

8. The cam Stirling refrigerator according to claim 1, characterized in that: The heat exchange pipeline includes a heat exchanger, a regenerator and a cold exchanger which are connected in sequence. The cold exchanger is connected to the first chamber, the heat exchanger is connected to the second chamber, and the regenerator is used to exchange heat with the heat medium.

9. The cam Stirling refrigerator according to claim 8, characterized in that: The heat exchanger comprises a plurality of heat exchange cavities, and the plurality of heat exchange cavities are sequentially distributed around the circumference of the shell; And / or, the regenerator comprises a plurality of regenerating cavities, and the plurality of regenerating cavities are sequentially distributed around the circumference of the shell; And / or, the cold exchanger includes a plurality of cold exchange pipes, and the plurality of cold exchange pipes are sequentially distributed around the circumference of the shell.

10. The cam Stirling refrigerator according to claim 8, characterized in that: The heat exchange chamber includes a plurality of heat exchange pipes communicating with the regenerator and the second chamber.

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