Multi-rotor compressor and refrigeration equipment

Abstract

The invention discloses a multi-rotor compressor and refrigeration equipment, and relates to the technical field of liquid variable-capacity compression pumps, the compressor comprises a shell, a crankshaft, rotors and a built-in motor, the crankshaft is mounted in the shell through a magnetic suspension bearing, each rotor is mounted on the crankshaft, and the built-in motor is arranged in the shell and is in transmission connection with the crankshaft; each rotor is of a three-arc structure, and the outer contour line of each rotor is composed of three identical protruding arc faces and three sealing vertexes. A sealed compression cavity is arranged in the shell, and each rotor is eccentrically arranged in the sealed compression cavity; the rotors are uniformly distributed on the circumference around the central axis of the crankshaft; the crankshaft rotates to drive all the sealing vertexes to be in dynamic contact with the inner wall of the sealing compression cavity all the time, and three independent working air cavities with the volume changing periodically are formed between the three protruding cambered surfaces and the inner wall of the sealing compression cavity. According to the compressor, pulsation noise can be greatly reduced, the compression efficiency is improved, and the efficient, energy-saving and ultra-silence effects are achieved.

Description

Technical Field

[0001] This invention relates to the field of liquid variable displacement compressor pump technology, and more particularly to a multi-rotor compressor and refrigeration equipment. Background Technology

[0002] Currently, the refrigeration industry, including refrigerators and air conditioners, widely uses rotary compressors as their core refrigeration components. The working principle of this type of compressor is as follows: an eccentric crankshaft drives rollers to move in a circular motion within a cylinder with an arc-shaped inner wall. Simultaneously, sliding vanes divide the cylinder into a high-pressure chamber and a low-pressure chamber. As the rollers rotate, the gas is compressed and discharged from the high-pressure chamber, thus achieving the compression process in the refrigeration cycle.

[0003] However, this traditional design faces a series of technical challenges in practical applications. For example, the compressor disclosed in Chinese Patent No. CN202310018814.7 is an improved version of the rolling rotor compressor. It achieves dual-cylinder, two-stage compression by setting a dual-chamber structure with piston and roller linkage in the compressor, which solves the compression efficiency problem to some extent. However, this structure still uses a single cylinder for compression, that is, the cylinder only completes one exhaust per revolution of the crankshaft. The violent pulsation will produce obvious vibration and "humming" airflow noise. In order to alleviate the violent pulsation of a single cylinder, the prior art arranges two cylinders side by side or staggered, such as the compressor disclosed in Chinese Patent No. CN202511268081.8, which arranges two cylinders vertically side by side, that is, each cylinder exhausts air once per revolution of the crankshaft.

[0004] It is evident that the compression process of the two aforementioned cylinder structures still exhibits significant intermittency, resulting in substantial flow pulsation in the compressor's exhaust, which in turn causes airflow pulsation noise in the system pipeline, and low power density per unit volume. Simultaneously, the eccentric mass of the crankshaft and the periodic radial gas force generated during compression are difficult to balance completely, leading to significant mechanical vibration and noise during operation, which not only affects the stable operation of the equipment but may also shorten its service life.

[0005] Meanwhile, based on the aforementioned compression structure, the crankshaft structure of existing compressors generally uses mechanical contact bearings (such as ball bearings or sliding bearings) for support. These mechanical bearings inevitably experience solid friction during operation, leading to significant energy consumption and wear, requiring a complex lubrication system to maintain operation. This not only increases the risk of failure but may also contaminate the refrigeration circuit.

[0006] Therefore, how to avoid or greatly reduce periodically changing flow pulsations in order to provide a continuous and smooth flow pulsation, thereby reducing airflow pulsation noise, improving compression efficiency, and achieving truly high efficiency, energy saving, and ultra-quiet operation in compression refrigeration technology has become an urgent problem to be solved. Summary of the Invention

[0007] In order to overcome the shortcomings of the prior art, one of the objectives of the present invention is to provide a multi-rotor compressor.

[0008] The second objective of this invention is to provide a refrigeration device that includes a multi-rotor compressor.

[0009] One of the objectives of this invention is achieved by the following technical solution: a multi-rotor compressor, comprising a housing, a crankshaft, at least one rotor, and a built-in motor, wherein the crankshaft is mounted in the housing via a magnetic levitation bearing, each rotor is mounted on the crankshaft, and the built-in motor is disposed inside the housing and is drively connected to the crankshaft;

[0010] The rotor has a three-arc structure, and its outer contour is composed of three identical convex arc surfaces and three sealing vertices located between adjacent convex arc surfaces. The three sealing vertices are located on the same circumference with the rotor center as the center, and adjacent sealing vertices are evenly distributed radially at a distance of 120°. The housing is provided with at least one sealed compression cavity, and the radial cross-sectional profile of the sealed compression cavity is a double-circle intersecting structure. Each rotor is eccentrically arranged in an independent sealed compression cavity. The rotors are evenly distributed on the circumference around the central axis of the crankshaft.

[0011] The rotation of the crankshaft causes the three sealing apexes of the rotor to maintain dynamic contact with the inner wall of the sealed compression cavity. The three protruding arc surfaces and the inner wall of the sealed compression cavity form three independent working air chambers with periodically changing volumes.

[0012] Furthermore, a rotor and a sealed compression chamber constitute a refrigerant compression structure. Each refrigerant compression structure is equipped with two sets of refrigerant circulation components. Each set of refrigerant circulation components includes two suction valves and two discharge valves.

[0013] Each refrigerant compression structure has a sealed compression chamber area divided into a first suction chamber, a first discharge chamber, a second suction chamber, and a second discharge chamber. The first suction chamber and the second discharge chamber share the same independent working chamber. The first discharge chamber corresponds to another independent working chamber, and the second suction chamber corresponds to the last independent working chamber. The first suction chamber is connected to one of the suction valves through a suction port, the first discharge chamber is connected to one of the discharge valves through a discharge port, the second suction chamber is connected to another suction valve through a suction port, and the second discharge chamber is connected to another discharge valve through a discharge port.

[0014] The two intake valves maintain valve passage connection for intake under normal conditions, and close valve passage under high pressure; the two exhaust valves remain closed under normal conditions, and open valve passage for exhaust under high pressure.

[0015] Furthermore, each of the suction valves includes a suction valve housing, a suction sliding valve block, and a suction valve spring; the suction valve housing is provided with a first air inlet and a first air outlet, the suction sliding valve block is provided with an inner guide tube at the first air inlet, the suction sliding valve block is tubular and not connected in the middle, one end of the suction sliding valve block is slidably sleeved on the inner guide tube, and the other end is built into the suction valve spring, and the suction sliding valve block has a through hole near the opening of the inner guide tube; under normal conditions, the through hole is connected to the first air inlet and the first air outlet to realize suction, when the suction valve spring is squeezed and contracted, the suction sliding valve block slides, and the inner guide tube closes the through hole;

[0016] Each of the exhaust valves includes an exhaust valve housing, an exhaust sliding valve block, and an exhaust valve spring. The exhaust valve housing has a second air inlet and a second air outlet, and its interior has a hollow limiting chamber. The exhaust sliding valve block and the exhaust valve spring are sequentially installed in the hollow limiting chamber. The exhaust sliding valve block has a hollow channel inside. Under normal conditions, the hollow channel of the exhaust sliding valve block is not connected to the second air outlet. After being compressed, the refrigerant is in a high temperature and high pressure state and enters from the second air inlet, pushing the exhaust sliding valve block to slide in the hollow limiting chamber. The exhaust valve spring is squeezed and contracted, and the hollow channel on the exhaust sliding valve block is connected to the second air outlet to realize exhaust.

[0017] The first air inlet of the intake valve housing is provided with an intake valve sealing ring at the connection position of the housing, and the inner wall of the exhaust valve sliding valve block is provided with an intake valve sealing ring; the second air inlet of the exhaust valve housing is provided with an exhaust valve sealing ring at the connection position of the housing, and an exhaust valve sealing ring is provided between the exhaust valve sliding valve block and the hollow limiting chamber of the exhaust valve housing.

[0018] Furthermore, the housing includes a base and a top cover detachably mounted on the upper part of the base, and a housing sealing ring is provided between the base and the top cover; several air intake ports and exhaust ports are respectively provided on both sides of the base and the top cover; an air intake valve is installed on the air intake port and communicates with the sealed compression cavity, and an exhaust valve is installed on the exhaust port and communicates with the sealed compression cavity.

[0019] Furthermore, each of the three sealing apexes on the rotor is provided with a sealing connector, and each sealing connector includes a first sealing plate, a first spring plate, and a first fixing ring. The sealing apex of the rotor is recessed in the radial direction with a limiting groove for installing the first sealing plate. The first fixing ring is fixed at both ends of the groove opening of the limiting groove. The two ends of the first spring plate are respectively fixed on the first fixing ring. The two ends of the first sealing plate are provided with guide inclined surfaces. After one side of the first sealing plate is installed in the limiting groove, it abuts against the first spring plate, and the other side maintains dynamic sealing contact with the inner wall of the sealed compression cavity.

[0020] Furthermore, the rotor has two concentric annular grooves on its two side walls, and an annular sealing ring is installed in each inner annular groove.

[0021] Furthermore, each rotor has a rotating gear at its center, and a fixed gear corresponding to the number of rotating gears is fixed inside the housing. The fixed gears mesh with the rotating gears for transmission.

[0022] Furthermore, the built-in motor includes a motor rotor and a motor stator. The motor rotor is mounted on the stepped shaft of the crankshaft via a flange, and the motor stator is mounted inside the cavity of the housing.

[0023] Furthermore, the magnetic levitation bearing includes multiple radial magnetic levitation bearings installed in the middle of the crankshaft and axial magnetic levitation bearings installed at both ends of the crankshaft. The radial and axial magnetic levitation bearings are arranged in a Heilbeck array to enhance the rotor's support strength and rotational stability, and reduce rotor vibration and friction noise.

[0024] Each of the radial magnetic levitation bearings is installed in the housing by a corresponding number of bearing mounting seats, or a radial bearing limiting chamber for installing the radial magnetic levitation bearing is formed inside the housing. Each of the radial magnetic levitation bearings includes a radial magnetic levitation bearing rotating ring and a radial magnetic levitation bearing fixing ring sleeved on the outer ring of the radial magnetic levitation bearing rotating ring. The radial magnetic levitation bearing fixing ring is installed in the bearing mounting seat, and the radial magnetic levitation bearing rotating ring is fixed in the middle of the crankshaft.

[0025] Each of the axial magnetic levitation bearings is installed in the housing by a corresponding number of bearing mounting seats. The housing has axial bearing limiting chambers at both ends for installing the axial magnetic levitation bearings. Each of the axial magnetic levitation bearings includes an axial magnetic levitation bearing rotating ring and axial magnetic levitation bearing fixing rings arranged side by side on one side of the axial magnetic levitation bearing rotating ring. The axial magnetic levitation bearing fixing rings are installed in the axial bearing limiting chambers, and the axial magnetic levitation bearing rotating rings are fixed at both ends of the crankshaft.

[0026] The second objective of this invention is achieved by the following technical solution: a refrigeration device comprising a multi-rotor compressor as described above.

[0027] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0028] 1. This invention designs a triangular rotor compression structure as the refrigerant compression structure. It cleverly utilizes the triangular rotor and the inner wall of the sealed compression chamber to form three sub-circulation compression chambers, enabling continuous compression with smoother airflow and no intermittent pulses. Each rotor rotation completes the intake, compression, and exhaust cycle, resulting in a smooth and continuous compression process without reciprocating intermittent pulses. Furthermore, as the number of rotors increases, intermittent pulses decrease further, leading to increasingly stable and linear operation. Compared to existing industry product structures, this invention exhibits less refrigerant airflow pulsation, significantly reducing pipeline vibration and noise, making it more suitable for quiet environments such as silent refrigerators and air conditioners. Cooling capacity adjustment is also more linear and precise.

[0029] In addition, the refrigerant compression structure of this invention is more suitable for high-speed and high-power-density application scenarios. The rotor structure is suitable for high-speed operation, without reciprocating inertia limitations, and has a higher power density per unit volume. Under the same cooling capacity, the whole machine is smaller and lighter, which can significantly improve the utilization rate of internal space in the refrigeration industry such as refrigerators and air conditioners.

[0030] 2. This invention incorporates magnetic levitation bearings, designing a combination of radial and axial magnetic levitation bearings, particularly employing a specific Halebeck array arrangement. This arrangement significantly enhances the magnetic field strength within the required range. Specifically, the position and arrangement of the fixed and rotating rings greatly increase the axial end face magnetic field strength between the crankshaft ends and the housing, as well as the magnetic field strength between the middle of the crankshaft and the housing, especially on the inner and outer sides of the rings. This strengthens the support strength and rotational stability of the triangular rotor, while reducing its vibration and friction noise.

[0031] More specifically, the advantages of this combination of radial and axial magnetic levitation bearings in this compressor are as follows: (1) The array structure enhances and makes the magnetic field distribution more uniform and symmetrical, which can automatically correct the rotor eccentricity deviation and provide high rigidity support. The vibration and displacement of the compressor are small when it is running, reducing noise and pipeline resonance problems under high-speed operation. (2) Non-contact operation with almost zero frictional power consumption improves the compressor's energy efficiency ratio. The compact size and high magnetic density of the Heilbeck array can reduce the space of the bearing and the overall structure, simplify the crankshaft structure, and make the refrigerator compressor design lighter. (3) This bearing combination enables the rotor to achieve frictionless high-speed and stable operation. Combined with the frequency conversion adjustment in application scenarios such as refrigerator compressors, it can quickly respond to load changes, resulting in higher cooling efficiency and smaller temperature fluctuations.

[0032] 3. The aforementioned multi-triangular rotor compression structure and the axially and radially supported Heilbeck array permanent magnet levitation bearings work in synergy. Multiple triangular rotors are directly fixed on a common suspension drive shaft. Driven by the same built-in motor, these rotors rotate synchronously in the circumferential direction. Each rotor has two independent refrigerant circulation chambers for refrigerant compression, significantly improving compression efficiency and power density. Simultaneously, the axially and radially supported Heilbeck array permanent magnet levitation bearings enhance the supporting force of the magnetic levitation bearings, concentrating the compressor rotors within the working air gap. This provides a stable, rigid, non-contact levitation force for the triangular rotors without external power or active control, achieving low friction, low wear, high speed, high power density, and ultra-quiet cooling performance. Attached Figure Description

[0033] Figure 1 This is a three-dimensional structural diagram of a multi-rotor compressor according to a preferred embodiment of the present invention;

[0034] Figure 2 for Figure 1 Schematic diagram of the cross-sectional structure of line AA in the middle;

[0035] Figure 3 for Figure 2 Enlarged view of point B in the middle;

[0036] Figure 4 for Figure 2 Enlarged view of point C in the middle;

[0037] Figure 5 This is a side view of the multi-rotor compressor according to a preferred embodiment of the present invention;

[0038] Figure 6 for Figure 5 Schematic diagram of the cross-sectional structure of the DD line;

[0039] Figure 7 This is a three-dimensional structural diagram of the rotor of the preferred embodiment 1 of the present invention;

[0040] Figure 8 This is a side view of the rotor structure of a preferred embodiment 1 of the present invention;

[0041] Figure 9 for Figure 8 Enlarged view of point E in the middle;

[0042] Figure 10 This is a schematic diagram of the crankshaft structure according to a preferred embodiment of the present invention;

[0043] Figure 11This is a schematic diagram of the assembly structure of the fixed gear and the rotating gear in a preferred embodiment of the present invention;

[0044] Figure 12 This is a schematic diagram of the cross-sectional structure of the rotor in the preferred embodiment 1 of the present invention;

[0045] Figure 13 This is a schematic diagram of the intake valve structure and its FF line in a preferred embodiment of the present invention;

[0046] Figure 14 This is a schematic diagram of the exhaust valve structure and its GG line according to a preferred embodiment of the present invention;

[0047] Figure 15 This is a schematic diagram of the radial magnetic levitation bearing structure and magnetization direction in a preferred embodiment of the present invention;

[0048] Figure 16 This is a schematic diagram of the axial magnetic levitation bearing structure and magnetization direction in a preferred embodiment of the present invention.

[0049] In the picture:

[0050] 100. Multi-rotor compressor;

[0051] 1. Housing; 11. Sealed compression chamber; 111. First intake chamber; 112. First exhaust chamber; 113. Second intake chamber; 114. Second exhaust chamber; 11a. First working air chamber; 11b. Second working air chamber; 11c. Third working air chamber; 12. Base; 13. Top cover; 14. Housing sealing ring; 15. Intake port; 16. Exhaust port; 17. Limiting guide rod;

[0052] 2. Crankshaft; 21. Central shaft; 22. Eccentric part;

[0053] 3. Rotor; 3a. First rotor; 3b. Second rotor; 3c. Third rotor; 31. Protruding arc surface; 32. Sealing apex; 33. Sealing connector; 331. First sealing plate; 3311. Guide inclined surface; 332. First spring plate; 333. First fixing ring; 34. Limiting groove; 35. Annular groove; 36. Annular sealing ring;

[0054] 4. Built-in motor; 41. Motor rotor; 42. Motor stator;

[0055] 5. Magnetic levitation bearing; 51. Radial magnetic levitation bearing; 511. Radial magnetic levitation bearing rotating ring; 512. Radial magnetic levitation bearing retaining ring; 52. Axial magnetic levitation bearing; 521. Axial magnetic levitation bearing rotating ring; 522. Axial magnetic levitation bearing retaining ring; 53. Bearing mounting base;

[0056] 6. Refrigerant circulation assembly; 61. Suction valve; 61a. First suction valve; 61b. Second suction valve; 611. Suction valve housing; 6111. First inlet; 6112. First outlet; 6113. Inner guide tube; 612. Suction sliding valve block; 6121. Through hole; 613. Suction valve spring; 614. Suction valve sealing ring; 62. Exhaust valve; 62a. First exhaust valve; 62b. Second exhaust valve; 621. Exhaust valve housing; 6211. Second inlet; 6212. Second outlet; 6213. Hollow limiting chamber; 622. Exhaust sliding valve block; 623. Exhaust valve spring; 624. Exhaust valve sealing ring;

[0057] 7. Fixed gear; 71. Gear fixing plate; 72. Gear limiting plate;

[0058] 8. Rotating gear;

[0059] 9. Flange;

[0060] O, rotor center; W, spindle rotation direction. Detailed Implementation

[0061] The present invention will now be further described in conjunction with the accompanying drawings and specific embodiments. It should be noted that, without conflict, the various embodiments or technical features described below can be arbitrarily combined to form new embodiments.

[0062] Example 1

[0063] like Figures 1-16 As shown, a multi-rotor compressor 100 includes a housing 1, a crankshaft 2, three rotors 3, and a built-in motor 4. The crankshaft is mounted inside the housing via a magnetic levitation bearing 5. All three rotors are mounted on the crankshaft. The built-in motor is disposed inside the housing and is drivenly connected to the crankshaft.

[0064] Each rotor 3 has a tri-arc structure, and its outer contour consists of three identical convex arc surfaces 31 and three sealing vertices 32 located between adjacent convex arc surfaces. The three sealing vertices are located on the same circumference with the rotor center O as the center, and adjacent sealing vertices are evenly distributed radially at intervals of 120°. Figure 8 As shown; the housing is provided with three sealed compression cavities, the radial cross-sectional profile of the sealed compression cavities is a double-circle intersecting structure, and each rotor is eccentrically arranged in each independent sealed compression cavity; each rotor is evenly distributed on the circumference around the central axis of the crankshaft;

[0065] The crankshaft rotation synchronously drives the three sealing apexes of the rotor to maintain dynamic contact with the inner wall of the sealed compression chamber. Between the three convex arc surfaces and the inner wall of the sealed compression chamber, three independent working gas chambers with periodically changing volumes are formed. Figure 6 As shown.

[0066] Currently, most rotary compressors in the industry use a single cylinder with a circular arc surface for gas compression. This invention uses a rotor (triangular rotor) with a three-arc surface structure. Each arc surface corresponds to one of three independent compression chambers. Each rotor completes two intake, compression, and exhaust cycles simultaneously in one rotation. Furthermore, each rotor is evenly distributed around the central axis of the crankshaft. The multiple independent compression chambers simultaneously complete multiple intake, compression, and exhaust cycles. The uniform symmetry on the geometric circumference minimizes, or even eliminates, the sum of the centrifugal forces generated by the multiple rotors, resulting in self-balancing and dynamic equilibrium. This effectively reduces periodic flow pulsations, providing a continuous, smooth flow pulsation, significantly reducing pulsation noise and improving compression efficiency. In addition, this invention employs magnetic levitation bearings to provide stable, rigid, non-contact suspension for the rotor, achieving true high efficiency, energy saving, and ultra-quiet operation—a problem that urgently needs to be solved.

[0067] In this preferred embodiment, the present invention preferably designs three rotors 3, namely a first rotor 3a, a second rotor 3b, and a third rotor 3c, as follows: Figure 2 As shown; wherein, the crankshaft is levitably and rotatably mounted in the housing via a magnetic levitation bearing 5, the first rotor 3a, the second rotor 3b, and the third rotor 3c are mounted on the crankshaft 2 and respectively placed in each of the preset sealed compression cavities of the compressor. In this example, one rotor 3 and one sealed compression cavity constitute a refrigerant compression structure. Each refrigerant compression structure is provided with two sets of refrigerant circulation components 6. Each set of refrigerant circulation components 6 includes two suction valves 61 and two exhaust valves 62, namely the first suction valve 61a, the first exhaust valve 62a, the second suction valve 61b, and the second exhaust valve 62b.

[0068] like Figure 6As shown, the sealed compression chamber 11 area on each refrigerant compression structure is divided into a first suction chamber 111, a first exhaust chamber 112, a second suction chamber 113, and a second exhaust chamber 114. The first suction chamber and the second exhaust chamber share the same independent first working gas chamber 11a. The first exhaust chamber corresponds to another independent second working gas chamber 11b, and the second suction chamber corresponds to the last independent third working gas chamber 11c. The first suction chamber 111 is connected to the first suction valve through a suction port, the first exhaust chamber is connected to the first exhaust valve through an exhaust port, the second suction chamber is connected to the second suction valve through a suction port, and the second exhaust chamber is connected to the second exhaust valve through an exhaust port.

[0069] The first and second intake valves maintain valve passage connection for intake under normal conditions, and valve passage is closed under high pressure; the first and second exhaust valves remain closed under normal conditions, and valve passage is opened for exhaust under high pressure.

[0070] As a further preferred embodiment, the intake valve 61 can be an existing intake valve, or it can adopt the following structure, such as... Figure 13 As shown, the intake valve 61 includes an intake valve housing 611, an intake sliding valve block 612, and an intake valve spring 613;

[0071] The intake valve housing 611 is detachably and fixedly installed on both sides of the housing. The intake valve housing 611 is provided with a first air inlet 6111 and a first air outlet 6112. An inner guide tube 6113 is provided at the first air inlet 6111 of the intake sliding valve block. The intake sliding valve block 612 is tubular and not connected in the middle. One end of the intake sliding valve block is slidably sleeved on the inner guide tube 6113, and the other end is built into the intake valve spring. A through hole 61 is opened on the intake sliding valve block near the opening of the inner guide tube. 21. The housing 1 is provided with a limiting guide rod 17. The left and right ends of the air sliding valve block are respectively slidably sleeved on the inner guide tube 6113 and the limiting guide rod 17. An air intake valve sealing ring 614 is connected between the limiting guide rod 17 and the air intake sliding valve block 612. Under normal conditions, the through hole is connected to the first air inlet 6111 and the first air outlet 6112 to realize air intake. When the air intake valve spring is squeezed and contracted, the air intake sliding valve block slides, closing the through hole of the inner guide tube. In this example, the flow direction of liquid or gas in the air intake valve is as follows: Figure 13 As indicated by the arrow, the air flows from the first air inlet 6111 through the through hole 6121 inside the valve body to the first air outlet 6112.

[0072] The exhaust valve 62 can be an existing exhaust valve, or it can adopt the following structure, such as... Figure 14As shown, the exhaust valve 62 includes an exhaust valve housing 621, an exhaust sliding valve block 622, and an exhaust valve spring 623. The exhaust valve housing has a second inlet 6211 and a second outlet 6212, and its interior has a hollow limiting chamber 6213. The exhaust sliding valve block and the exhaust valve spring are sequentially installed within the hollow limiting chamber. The exhaust sliding valve block has a hollow channel; under normal conditions, the hollow channel of the exhaust sliding valve block is not connected to the second outlet 6212. After compression, the refrigerant is in a high-temperature, high-pressure state and enters through the second inlet 6211, pushing the exhaust sliding valve block to slide within the hollow limiting chamber. The exhaust valve spring is compressed and contracts, and the hollow channel on the exhaust sliding valve block connects to the second outlet 6212, thus achieving exhaust. In this example, the flow direction of the liquid or gas within the exhaust valve is as follows: Figure 14 As indicated by the arrow, the air flows from the second air inlet 6211 through the hollow channel inside the exhaust sliding valve block 622 to the second air outlet 6212.

[0073] To further improve the airtightness between the intake valve or exhaust valve and the internal cavity of the housing, an intake valve sealing ring 614 is provided at the first air inlet 6111 of the intake valve housing 611 at the housing connection position, and an intake valve sealing ring 614 is provided on the inner wall of the exhaust valve sliding valve block. An exhaust valve sealing ring 624 is provided at the second air inlet 6211 of the exhaust valve housing 621 at the housing connection position, and an exhaust valve sealing ring 624 is provided between the exhaust valve sliding valve block and the hollow limiting cavity of the exhaust valve housing.

[0074] This invention relates to a refrigerant compression structure, specifically a triangular rotor compression structure. It cleverly utilizes three working chambers as two sets of refrigerant circulation compression structures. Combined with two sets of fully automatic refrigerant replenishment or discharge based on gas pressure, it achieves continuous compression with smoother airflow and no intermittent pulses. Each rotor rotation completes the intake, compression, and exhaust cycle, resulting in a smooth and continuous compression process without reciprocating intermittent pulses. Furthermore, as the number of rotors increases, intermittent pulses decrease further, leading to increasingly stable and linear operation. Compared to existing industry product structures, it exhibits less refrigerant airflow pulsation, significantly reducing pipeline vibration and noise, making it more suitable for quiet refrigerator applications, and providing more linear and precise cooling capacity adjustment.

[0075] In addition, the refrigerant compression structure of this invention is more suitable for high-speed and high-power-density application scenarios. The rotor structure is suitable for high-speed operation, without reciprocating inertia limitations, and has a higher power density per unit volume. Under the same cooling capacity, the whole machine is smaller and lighter, which can significantly improve the utilization rate of internal space in the refrigeration industry such as refrigerators and air conditioners.

[0076] To facilitate rapid assembly of the rotors and motor, and to ensure or improve the sealing of the compression chamber, this housing is designed as a detachable structure, as detailed below: Figure 6 As shown, the housing 1 includes a base 12 and a top cover 13 detachably mounted on the upper part of the base. A housing sealing ring 14 is provided between the base and the top cover. Several air intake ports 15 and exhaust ports 16 are respectively provided on both sides of the base and the top cover. An air intake valve is installed on the air intake port and communicates with the sealed compression chamber. An exhaust valve is installed on the exhaust port and communicates with the sealed compression chamber.

[0077] As a further preferred embodiment, such as Figures 7-10 As shown, each of the three sealing vertices on the rotor is provided with a sealing connector 33. Each sealing connector 33 includes a first sealing plate 331, a first spring plate 332, and a first fixing ring 333. The sealing vertices of the rotor are recessed in the radial direction with a limiting groove 34 for installing the first sealing plate. The first fixing ring is fixed at both ends of the groove opening of the limiting groove. The two ends of the first spring plate are respectively fixed on the first fixing ring. The two ends of the first sealing plate are provided with guide inclined surfaces 3311. After one side of the first sealing plate is installed in the limiting groove, it abuts against the first spring plate, and the other side maintains dynamic sealing contact with the inner wall of the sealed compression cavity.

[0078] The rotor has two concentric annular grooves 35 on its two side walls, and an annular sealing ring 36 is installed in each inner annular groove.

[0079] To ensure the airtightness of the three independent working chambers on each rotor, radially oriented limiting grooves are provided at the contact positions between the three sealing apexes of the rotor and the chamber, and radial sealing spring plates are installed. The pre-tightening force generated by the cooperation between the sealing spring plates and the inner wall of the sealed compression chamber achieves reliable sealing at the three sealing apexes of the rotor. In addition, at least one, preferably two or more, annular sealing rings are provided on the side walls of the rotor to ensure reliable sealing at the side wall positions of the rotor. The two work together to achieve reliable sealing between the rotor and the cylinder, ensuring compression quality and efficiency.

[0080] As a further preferred option, such as Figure 2 , Figure 12 As shown, each rotor has a rotating gear 8 at its center, and a fixed gear 7, corresponding to the number of rotating gears, is fixed inside the housing. The fixed gears mesh with the rotating gears for transmission. The fixed gears 7 are mounted on the concentric main shaft of the crankshaft and are fixedly connected to the housing 1 via a gear fixing disc 71 or a gear limiting disc 72 integrally formed with the housing. Meanwhile, the rotor is mounted on the eccentric portion of the crankshaft. When the rotor rotates, it rotates on its own axis around the center of the concentric main shaft and revolves around the eccentric portion of the crankshaft.

[0081] In the refrigeration industry, rotary compressors are the first to introduce a triangular rotor structure as the compression structure. Utilizing the planetary motion principle of the triangular rotor, only the rotor and the central shaft are retained as the core moving parts, eliminating reciprocating inertial impact. The overall structure is simple, with more than 40% fewer parts than traditional reciprocating compressors of the same power. The entire assembly eliminates reciprocating structures such as rollers, vanes, and spring connecting rods, and also eliminates the need for shock-absorbing counterweights located inside the casing. Manufacturing and maintenance costs are lower. At the same time, since all moving parts are rotary, the oscillation space is small, the compression space is large, friction is lower, the friction mode is more stable and controllable, there are fewer wear points, and the service life is longer.

[0082] As a further preferred embodiment, the built-in motor 4 includes a motor rotor 41 and a motor stator 42. The motor rotor is mounted on the stepped shaft of the crankshaft via a flange 9, and the motor stator is mounted in the cavity of the housing.

[0083] As a further preferred option, such as Figures 2-3 As shown, the magnetic levitation bearing 5 includes a plurality of radial magnetic levitation bearings 51 installed in the middle of the crankshaft and axial magnetic levitation bearings 52 installed at both ends of the crankshaft, so as to enhance the support strength and rotational stability of the rotor and reduce rotor vibration and friction noise.

[0084] Each of the radial magnetic levitation bearings is installed in the housing by a matching number of bearing mounting seats 53, or a radial bearing limiting chamber for installing the radial magnetic levitation bearing is formed inside the housing. Each of the radial magnetic levitation bearings 51 includes a radial magnetic levitation bearing rotating ring 511 and a radial magnetic levitation bearing fixing ring 512 sleeved on the outer ring of the radial magnetic levitation bearing rotating ring. The radial magnetic levitation bearing fixing ring is installed in the bearing mounting seat, and the radial magnetic levitation bearing rotating ring is fixed in the middle of the crankshaft.

[0085] Each of the axial magnetic levitation bearings is installed in the housing by a corresponding number of bearing mounting seats 53. The housing has axial bearing limiting chambers at both ends for installing the axial magnetic levitation bearings. Each of the axial magnetic levitation bearings 52 includes an axial magnetic levitation bearing rotating ring 521 and an axial magnetic levitation bearing fixing ring 522 arranged side by side on one side of the axial magnetic levitation bearing rotating ring. The axial magnetic levitation bearing fixing ring is installed in the axial bearing limiting chamber, and the axial magnetic levitation bearing rotating ring is fixed at both ends of the crankshaft.

[0086] In this embodiment, the radial magnetic levitation bearing rotating ring 511, the radial magnetic levitation bearing fixed ring 512, the axial magnetic levitation bearing rotating ring 521, and the axial magnetic levitation bearing fixed ring 522 are all Halbach arrays composed of multiple annular permanent magnets with different magnetization directions, specifically arranged as follows: Figures 15-16As shown in the diagram, the side indicated by the arrow is the N pole of the magnetic field, and the other side is the S pole. This represents the direction of the magnetic field of the N pole pointing inwards along the bearing axial direction. The direction of the magnetic field, representing the N pole pointing outward along the bearing axial direction, is indicated by the magnetic field direction. Both the radial magnetic levitation bearing rotating ring 511 and the radial magnetic levitation bearing fixed ring 512 of this invention are composed of 12 permanent magnet rings; multiple Halbach arrays can be used in practical applications. The magnetization directions of the radial magnetic levitation bearing rotating ring 511, in clockwise order, are: outward, opposite to the main shaft rotation direction W, outward, main shaft rotation direction W, outward, opposite to the main shaft rotation direction W, outward, main shaft rotation direction W, outward, opposite to the main shaft rotation direction W, outward, main shaft rotation direction W; the magnetization directions of the radial magnetic levitation bearing fixed ring 512 are: inward, opposite to the main shaft rotation direction W, outward, main shaft rotation direction W, inward, opposite to the main shaft rotation direction W, outward, main shaft rotation direction W, inward, opposite to the main shaft rotation direction W, outward, main shaft rotation direction W.

[0087] Both the axial magnetic levitation bearing rotating ring 521 and the axial magnetic levitation bearing fixed ring 522 of this invention are composed of 12 permanent magnet rings. In practical applications, multiple Halbach arrays can be used. The magnetization directions of the axial magnetic levitation bearing rotating ring 521 and the axial magnetic levitation bearing rotating ring 521, in clockwise order, are as follows: N pole pointing inward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing outward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing inward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing outward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing outward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing outward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing outward along the bearing axial direction, opposite to the main shaft rotation direction W; N pole pointing outward along the bearing axial direction, opposite to the main shaft rotation direction W.

[0088] The Hellbeck array is a specific arrangement that can greatly enhance the magnetic field strength within a required range by designing a specific arrangement. In this invention, the position and arrangement of each fixed ring and rotating ring greatly increase the axial end face magnetic field strength between the two ends of the crankshaft and the housing, as well as greatly increase the magnetic field strength between the middle of the crankshaft and the housing, especially the inner and outer sides of the rings. This enhances the rotor's support strength and rotational stability, reduces eccentric vibration friction, and decreases rotor vibration and friction noise.

[0089] More specifically, the advantages of this combination of radial and axial magnetic levitation bearings in this compressor are as follows: (1) The array structure enhances and makes the magnetic field distribution more uniform and symmetrical, which can automatically correct the rotor eccentricity deviation and provide high rigidity support. The vibration and displacement of the compressor are small when it is running, reducing noise and pipeline resonance problems under high-speed operation. (2) Non-contact operation with almost zero frictional power consumption improves the compressor's energy efficiency ratio. The compact size and high magnetic density of the Heilbeck array can reduce the space of the bearing and the overall structure, simplify the crankshaft structure, and make the refrigerator compressor design lighter. (3) This bearing combination enables the rotor to achieve frictionless high-speed and stable operation. Combined with the frequency conversion adjustment in application scenarios such as refrigerator compressors, it can quickly respond to load changes, resulting in higher cooling efficiency and smaller temperature fluctuations.

[0090] The working process of the multi-rotor compressor in this embodiment is as follows:

[0091] like Figure 6 As shown, during operation, the built-in motor drives the crankshaft to rotate, and the crankshaft drives multiple rotors to rotate synchronously in their respective sealed compression chambers, and the volume of the three independent working gas chambers changes periodically.

[0092] When the volume of the first working air chamber is at its minimum after compression and negative pressure is generated, the second exhaust valve 62b connected to the first working air chamber is closed, while the first intake valve 61a is automatically opened. Low-temperature and low-pressure coolant enters from the first intake valve 61a. As the rotor continues to rotate, the volume of the first working air chamber gradually increases and then gradually decreases. The coolant is compressed to a high-temperature and high-pressure state and finally discharged from the first exhaust valve 62a, completing the first intake, compression, and exhaust cycle.

[0093] In addition, while the low-temperature and low-pressure coolant enters from the first intake valve 61a, the low-temperature and low-pressure coolant simultaneously enters the third working air chamber from the second intake valve 61b. As the volume of the third working air chamber gradually increases and then gradually decreases, the coolant is compressed to a high-temperature and high-pressure state and finally discharged from the second exhaust valve 62b, completing the second intake, compression, and exhaust cycle.

[0094] The rotor of this invention completes two intake, compression, and exhaust cycles simultaneously with each revolution. Multiple rotors evenly distributed on the circumference rotate around the central axis of the crankshaft, and multiple independent compression chambers simultaneously complete multiple intake, compression, and exhaust cycles. The uniform symmetry on the superimposed geometric circumference makes the sum of the centrifugal force vectors generated by each rotor extremely small, or even zero, effectively reducing the periodic flow pulsation. The entire compression process is smooth and continuous, without reciprocating intermittent pulses. During the above process, the refrigerant airflow pulsation is small, which can significantly reduce pipeline vibration and noise, making it more suitable for quiet scenarios, and the cooling capacity adjustment is also more linear and precise.

[0095] The overall benefits of this solution are remarkable. First, the Heilbeck array magnetic levitation bearing completely eliminates the need for mechanical friction and lubrication, significantly improving energy efficiency and reliability, and achieving near-silent operation. Second, the symmetrical arrangement of the three triangular rotors combined with magnetic levitation support results in a more balanced distribution of compression force, greatly suppressing vibration. Simultaneously, the three-way parallel compression significantly increases the refrigerant displacement per unit volume, improving compression efficiency and response speed. Finally, this highly integrated design makes the compressor structure more compact, with fewer parts and a longer lifespan, providing a feasible and effective solution for next-generation high-efficiency, energy-saving, and ultra-quiet home refrigeration solutions.

[0096] Example 2

[0097] A refrigeration device includes a multi-rotor compressor as described in Embodiment 1. The refrigeration device includes, but is not limited to, refrigerators and air conditioning units. The structure and operation of the multi-rotor compressor are specifically described using the multi-rotor compressor 100 of Embodiment 1. The advantages of the multi-rotor compressor also give the refrigeration device its advantages, which will not be elaborated here.

[0098] The above embodiments are merely preferred embodiments of the present invention and should not be construed as limiting the scope of protection of the present invention. Any non-substantial changes and substitutions made by those skilled in the art based on the present invention shall fall within the scope of protection claimed by the present invention.

Claims

1. A multi-rotor compressor, characterized in that, The device includes a housing, a crankshaft, at least one rotor, and a built-in motor. The crankshaft is mounted inside the housing via a magnetic levitation bearing. Each rotor is mounted on the crankshaft. The built-in motor is disposed inside the housing and is drively connected to the crankshaft. Each rotor has a three-arc structure, and its outer contour consists of three identical convex arc surfaces and three sealing vertices located between adjacent convex arc surfaces. The three sealing vertices are located on the same circumference with the rotor center as the center, and adjacent sealing vertices are evenly distributed radially at a distance of 120°. The housing is provided with at least one sealed compression cavity, and the radial cross-sectional profile of the sealed compression cavity is a double-circle intersecting structure. Each rotor is eccentrically arranged in an independent sealed compression cavity. Each rotor is evenly distributed on the circumference around the central axis of the crankshaft. The rotation of the crankshaft causes the three sealing apexes of the rotor to maintain dynamic contact with the inner wall of the sealed compression cavity. The three protruding arc surfaces and the inner wall of the sealed compression cavity form three independent working air chambers with periodically changing volumes.

2. The multi-rotor compressor as described in claim 1, characterized in that, A rotor and a sealed compression chamber constitute a refrigerant compression structure. Each refrigerant compression structure is equipped with two sets of refrigerant circulation components. Each set of refrigerant circulation components includes two suction valves and two discharge valves. Each refrigerant compression structure has a sealed compression chamber area divided into a first suction chamber, a first discharge chamber, a second suction chamber, and a second discharge chamber. The first suction chamber and the second discharge chamber share the same independent working chamber. The first discharge chamber corresponds to another independent working chamber, and the second suction chamber corresponds to the last independent working chamber. The first suction chamber is connected to one of the suction valves through a suction port, the first discharge chamber is connected to one of the discharge valves through a discharge port, the second suction chamber is connected to another suction valve through a suction port, and the second discharge chamber is connected to another discharge valve through a discharge port. The two intake valves maintain valve passage connection for intake under normal conditions, and close valve passage under high pressure; the two exhaust valves remain closed under normal conditions, and open valve passage for exhaust under high pressure.

3. The multi-rotor compressor as described in claim 2, characterized in that, Each of the aforementioned suction valves includes a suction valve housing, a suction sliding valve block, and a suction valve spring. The suction valve housing has a first air inlet and a first air outlet. The suction sliding valve block has an inner guide tube at the first air inlet. The suction sliding valve block is tubular and not connected in the middle. One end of the suction sliding valve block is slidably sleeved on the inner guide tube, and the other end is fitted with the suction valve spring. The suction sliding valve block has a through hole near the opening of the inner guide tube. Under normal conditions, the through hole is connected to the first air inlet and the first air outlet to achieve suction. When the suction valve spring is squeezed and contracted, the suction sliding valve block slides, closing the through hole with the inner guide tube. Each of the exhaust valves includes an exhaust valve housing, an exhaust sliding valve block, and an exhaust valve spring. The exhaust valve housing has a second air inlet and a second air outlet, and its interior has a hollow limiting chamber. The exhaust sliding valve block and the exhaust valve spring are sequentially installed in the hollow limiting chamber. The exhaust sliding valve block has a hollow channel inside. Under normal conditions, the hollow channel of the exhaust sliding valve block is not connected to the second air outlet. After being compressed, the refrigerant is in a high temperature and high pressure state and enters from the second air inlet, pushing the exhaust sliding valve block to slide in the hollow limiting chamber. The exhaust valve spring is squeezed and contracted, and the hollow channel on the exhaust sliding valve block is connected to the second air outlet to realize exhaust. The first air inlet of the intake valve housing is provided with an intake valve sealing ring at the connection position of the housing, and the inner wall of the exhaust valve sliding valve block is provided with an intake valve sealing ring; the second air inlet of the exhaust valve housing is provided with an exhaust valve sealing ring at the connection position of the housing, and an exhaust valve sealing ring is provided between the exhaust valve sliding valve block and the hollow limiting chamber of the exhaust valve housing.

4. The multi-rotor compressor as described in claim 1, characterized in that, The housing includes a base and a top cover that is detachably mounted on the upper part of the base. A housing sealing ring is provided between the base and the top cover. Several air intake ports and exhaust ports are respectively provided on both sides of the base and the top cover. An air intake valve is installed on the air intake port and communicates with the sealed compression chamber, and an exhaust valve is installed on the exhaust port and communicates with the sealed compression chamber.

5. The multi-rotor compressor as described in claim 1, characterized in that, Each of the three sealing apexes on the rotor is provided with a sealing connector. Each sealing connector includes a first sealing plate, a first spring plate, and a first fixing ring. The sealing apex of the rotor is recessed in the radial direction with a limiting groove for installing the first sealing plate. The first fixing ring is fixed at both ends of the groove opening. The two ends of the first spring plate are respectively fixed on the first fixing ring. The two ends of the first sealing plate are provided with guide inclined surfaces. After one side of the first sealing plate is installed in the limiting groove, it abuts against the first spring plate, and the other side maintains dynamic sealing contact with the inner wall of the sealed compression cavity.

6. The multi-rotor compressor as described in claim 5, characterized in that, The rotor has two concentric annular grooves on its two side walls, and an annular sealing ring is installed in each inner annular groove.

7. The multi-rotor compressor as described in claim 1, characterized in that, Each rotor has a rotating gear at its center, and a fixed gear corresponding to the number of rotating gears is fixed inside the housing. The fixed gears mesh with the rotating gears to drive each other.

8. The multi-rotor compressor as described in claim 1, characterized in that, The built-in motor includes a motor rotor and a motor stator. The motor rotor is mounted on the stepped shaft of the crankshaft via a flange, and the motor stator is installed inside the cavity of the housing.

9. The multi-rotor compressor according to any one of claims 1-7, characterized in that, The magnetic levitation bearing includes multiple radial magnetic levitation bearings installed in the middle of the crankshaft and axial magnetic levitation bearings installed at both ends of the crankshaft. The radial and axial magnetic levitation bearings are arranged in a Heilbeck array to enhance the rotor's support strength and rotational stability, and reduce rotor vibration and friction noise. Each of the radial magnetic levitation bearings is installed in the housing by a corresponding number of bearing mounting seats, or a radial bearing limiting chamber for installing the radial magnetic levitation bearing is formed inside the housing. Each of the radial magnetic levitation bearings includes a radial magnetic levitation bearing rotating ring and a radial magnetic levitation bearing fixing ring sleeved on the outer ring of the radial magnetic levitation bearing rotating ring. The radial magnetic levitation bearing fixing ring is installed in the bearing mounting seat, and the radial magnetic levitation bearing rotating ring is fixed in the middle of the crankshaft. Each of the axial magnetic levitation bearings is installed in the housing by a corresponding number of bearing mounting seats. The housing has axial bearing limiting chambers at both ends for installing the axial magnetic levitation bearings. Each of the axial magnetic levitation bearings includes an axial magnetic levitation bearing rotating ring and axial magnetic levitation bearing fixing rings arranged side by side on one side of the axial magnetic levitation bearing rotating ring. The axial magnetic levitation bearing fixing rings are installed in the axial bearing limiting chambers, and the axial magnetic levitation bearing rotating rings are fixed at both ends of the crankshaft.

10. A refrigeration device, characterized in that, It includes a multi-rotor compressor as described in any one of claims 1-9.

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