A double-cylinder rotary compressor and an air conditioner

Abstract

The present invention discloses a double-cylinder rotary compressor and an air conditioner. The compression mechanism includes an upper compression chamber and a lower compression chamber, and a middle partition plate assembly is arranged between them; the middle partition plate assembly includes a middle partition plate body, a disc and an elastic member. The middle partition plate body is arranged between the upper cylinder and the lower cylinder to separate the upper compression chamber and the lower compression chamber; there are two discs, which are respectively arranged on the upper side and the lower side of the middle partition plate body; the elastic member is arranged between the disc and the middle partition plate body, and the elastic member applies a force to the disc so that the disc located above always contacts the upper piston, and the disc located below always contacts the lower piston. When the piston deforms due to thermal expansion and contraction, the positions of the two discs are adjusted through the elastic member, so that the discs can always contact the upper piston and the lower piston correspondingly, thereby avoiding the technical problems of cylinder jamming and low exhaust efficiency caused by the appearance of gaps between the middle partition plate assembly and the upper piston and the lower piston.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration equipment, and in particular to a twin-cylinder rotary compressor and an air conditioner. Background Art

[0002] An air conditioner performs a refrigeration and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration and heating cycle includes a series of processes involving compression, condensation, expansion, and evaporation to cool or heat an indoor space.

[0003] A low-temperature and low-pressure refrigerant enters the compressor, and the compressor compresses it into a refrigerant gas in a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.

[0004] The rolling rotor compressor is now widely used in air conditioners. The working principle of the existing rolling rotor compressor is as follows: After the motor stator is powered on, a magnetic pulling force is generated. The motor rotor makes a rotational movement under the action of the magnetic pulling force of the stator, and drives the eccentric crankshaft of the compression mechanism to make a rotational movement together. When the eccentric crankshaft rotates, it drives the piston sleeved on its eccentric part to make an eccentric circular movement in the cylinder. The sliding vane is installed in the sliding vane groove of the cylinder and always abuts against the piston under the action of the compression spring in the spring hole, so that it makes a reciprocating movement in the sliding vane groove. The sliding vane and the piston divide the cylinder into a high-pressure chamber and a low-pressure chamber. When the eccentric crankshaft drives the piston to rotate one week, it sucks air from the low-pressure chamber and discharges air from the high-pressure chamber to complete one exhaust, thus realizing the compression of the gas by the compressor.

[0005] In a twin-cylinder rotary compressor, the compression mechanism is composed of an upper compression chamber (including an upper bearing, an upper cylinder, and an upper piston) and a lower compression chamber (including a lower bearing, a lower cylinder, and a lower piston). They are fastened by bolts, and the structures and functions of the upper compression chamber and the lower compression chamber are the same. The upper compression chamber and the lower compression chamber are separated by a middle partition plate. The material of the piston is mass-produced as steel, and the material of the cylinder is mass-produced as cast iron. Because the thermal expansion coefficient of steel is greater than that of cast iron, the piston is deliberately set shorter to meet the clearance requirement of thermal expansion and contraction at 120 °C. The existence of this clearance causes two problems: ① When the compressor fails, such as running in reverse, jamming of the cylinder will occur when the temperature is higher than 120 °C; ② This clearance reduces the exhaust efficiency.

[0006] The above information disclosed in this background art is only used to increase the understanding of the background art of the present application. Therefore, it may include prior art that is not known to those of ordinary skill in the art. Summary of the Invention

[0007] In view of the problems pointed out in the background art, the present invention provides a double-cylinder rotary compressor and an air conditioner. By improving the structure of the middle partition plate, the middle partition plate has a displacement in the vertical direction, so that the middle partition plate can always be in contact with the upper piston and the lower piston, eliminating the gap between the middle partition plate and the piston in the prior art, thereby avoiding cylinder jamming, improving the exhaust efficiency, and enhancing the energy efficiency of the compressor.

[0008] To achieve the above-mentioned invention objectives, the present invention adopts the following technical solutions:

[0009] A double-cylinder rotary compressor is provided. The upper compression chamber and the lower compression chamber are separated by a middle partition plate assembly. The middle partition plate assembly includes a middle partition plate body, discs, and elastic members. The middle partition plate body is disposed between the upper cylinder and the lower cylinder to separate the upper compression chamber and the lower compression chamber. There are two discs, which are respectively disposed on the upper side and the lower side of the middle partition plate body. The elastic members are disposed between the discs and the middle partition plate body, and the elastic members apply forces to the discs so that the disc located above always contacts the upper piston and the disc located below always contacts the lower piston.

[0010] When the piston deforms due to thermal expansion and contraction, the positions of the two discs are adjusted by the elastic members, so that the discs can always contact the upper piston and the lower piston correspondingly, thereby avoiding the technical problems of cylinder jamming and low exhaust efficiency caused by the appearance of gaps between the middle partition plate assembly and the upper piston and the lower piston.

[0011] After reading the specific embodiments of the present invention in conjunction with the accompanying drawings, other features and advantages of the present invention will become clearer. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0013] Figure 1 It is a schematic structural diagram of the compressor according to the embodiment;

[0014] Figure 2 It is a cross-sectional view of the compressor according to the embodiment;

[0015] Figure 3 It is a schematic assembly structural diagram of the rotor, the upper balance weight, the lower balance weight, and the oil retaining portion according to the embodiment;

[0016] Figure 4 is Figure 3 a cross-sectional view of the structure shown;

[0017] Figure 5 The structural schematic diagram after omitting the oil retaining part for the structure shown; Figure 3

[0018] Figure 6 The structural schematic diagram observed from Q1 for the structure shown; Figure 3

[0019] Figure 7 The top view of the structure shown; Figure 3

[0020] Figure 8 The structural schematic of the upper balance weight according to the embodiment; Figure 1 ;

[0021] Figure 9 The structural schematic of the upper balance weight according to the embodiment; Figure 2 ;

[0022] Figure 10 The structural schematic of the upper balance weight according to the embodiment; Figure 3 ;

[0023] Figure 11 The structural schematic of the upper balance weight according to the embodiment; Figure 4 ;

[0024] Figure 12 The structural schematic diagram of the oil retaining part according to the embodiment;

[0025] Figure 13 The structural schematic diagram of the compression mechanism according to the embodiment;

[0026] Figure 14 The sectional view of the compression mechanism shown; Figure 13

[0027] Figure 15 The structural schematic diagram observed from Q2 for the structure shown; Figure 13

[0028] Figure 16 The structural schematic diagram of the middle partition plate assembly according to the embodiment;

[0029] Figure 17 The structural schematic diagram of the middle partition plate body according to the embodiment;

[0030] Figure 18 The sectional view of the middle partition plate assembly according to the embodiment;

[0031] Figure 19 The exploded view of the middle partition plate assembly according to the embodiment;

[0032] Figure 20 The structural schematic diagram of the assembly between the upper bearing, the lift limiter, and the exhaust valve plate according to the embodiment;​​​​​

[0033] Figure 21 For Figure 20 Cross-sectional view taken along the A-A direction in the middle;

[0034] Reference numerals:

[0035] 100 - Housing;

[0036] 200 - Motor, 210 - Stator, 220 - Rotor, 221 - Through hole;

[0037] 300 - Compression mechanism;

[0038] 310 - Eccentric crankshaft, 311 - Main shaft section, 312 - Upper eccentric shaft section, 313 - Connecting shaft section, 314 - Lower eccentric shaft section, 315 - Sub - shaft section;

[0039] 321 - Upper cylinder, 322 - Lower cylinder;

[0040] 331 - Upper bearing, 332 - Lower bearing, 333 - Lift limiter, 334 - Exhaust valve plate, 335 - Exhaust hole of the upper bearing;

[0041] 340 - Middle partition assembly, 341 - Middle partition body, 3411 - Upper groove, 3412 - Upper mounting groove, 342 - Upper disk, 343 - Lower disk, 344 - Upper elastic member, 345 - Lower elastic member;

[0042] 351 - Upper muffler, 352 - Lower muffler;

[0043] 361 - Upper piston, 362 - Lower piston;

[0044] 400 - Exhaust pipe;

[0045] 500 - Intake pipe;

[0046] 600 - Oil retaining part, 610 - Screw hole;

[0047] 700 - Upper balance weight, 710 - First half - ring structure, 711 - Protrusion part, 7111 - First protrusion part, 7112 - Second protrusion part, 712 - Air flow channel, 713 - First mounting hole, 714 - Second mounting hole, 715 - Second mounting post, 716 - Groove, 720 - Second half - ring structure, 721 - First mounting post, 722 - Third mounting hole;

[0048] 800 - Lower balance weight;

[0049] 910 - First rivet, 920 - Second rivet. Detailed implementation mode

[0050] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present application without creative efforts shall fall within the protection scope of the present application.

[0051] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application 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 should not be construed as a limitation of the present application.

[0052] The terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, unless otherwise stated, the meaning of "a plurality" is two or more.

[0053] In the description of the present application, it should be noted that unless otherwise clearly specified and defined, the terms "mounted", "connected" and "connected" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected, or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0054] In the present invention, unless otherwise clearly specified and defined, the first feature being "above" or "below" the second feature may include the direct contact between the first and second features, or may include the non-direct contact between the first and second features but through other features therebetween. Moreover, the first feature being "above", "over" and "on" the second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the horizontal height of the first feature is higher than that of the second feature. The first feature being "below", "under" and "beneath" the second feature includes the first feature being directly below and obliquely below the second feature, or merely indicating that the horizontal height of the first feature is lower than that of the second feature.

[0055] The following disclosure provides many different embodiments or examples for implementing different structures of the present invention. To simplify the disclosure of the present invention, the components and settings of specific examples are described below. Of course, they are only examples and are not intended to limit the present invention. In addition, the present invention may repeat reference numerals and / or reference letters in different examples. Such repetition is for the purpose of simplification and clarity and does not itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the present invention provides examples of various specific processes and materials, but those of ordinary skill in the art can be aware of the application of other processes and / or the use of other materials.

[0056] [Air conditioner]

[0057] In this application, the air conditioner performs a refrigeration and heating cycle by using a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration and heating cycle includes a series of processes involving compression, condensation, expansion, and evaporation to cool or heat the indoor space.

[0058] The low-temperature and low-pressure refrigerant enters the compressor, and the compressor compresses it into a refrigerant gas in a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.

[0059] The expansion valve expands the high-temperature and high-pressure liquid-phase refrigerant formed by condensation in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a refrigeration effect by using the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. Throughout the cycle, the air conditioner can adjust the temperature of the indoor space.

[0060] The outdoor unit of the air conditioner refers to the part of the refrigeration cycle including the compressor and the outdoor heat exchanger. The indoor unit of the air conditioner includes an indoor heat exchanger, and the expansion valve can be provided in the indoor unit or the outdoor unit.

[0061] The indoor heat exchanger and the outdoor heat exchanger serve as condensers or evaporators. When the indoor heat exchanger serves as a condenser, the air conditioner executes the heating mode; when the indoor heat exchanger serves as an evaporator, the air conditioner executes the refrigeration mode.

[0062] Among them, the way in which the indoor heat exchanger and the outdoor heat exchanger are converted to serve as condensers or evaporators generally uses a four-way valve. For specific reference to the settings of a conventional air conditioner, it will not be elaborated here.

[0063] The refrigeration working principle of the air conditioner is as follows: When the compressor operates, the indoor heat exchanger (in the indoor unit, it is the evaporator at this time) is in an ultra-low pressure state. The liquid refrigerant in the indoor heat exchanger quickly evaporates and absorbs heat. The air blown by the indoor fan passes through the coils of the indoor heat exchanger, cools down, and then blows into the room as cold air. After the refrigerant evaporates and vaporizes, it is pressurized by the compressor and condenses into a liquid under the high-pressure environment in the outdoor heat exchanger (in the outdoor unit, it is the condenser at this time), releasing heat. Through the outdoor fan, the heat is dissipated into the atmosphere. Such a cycle achieves the refrigeration effect.

[0064] The heating working principle of the air conditioner is as follows: The gaseous refrigerant is pressurized by the compressor to become a high-temperature and high-pressure gas, enters the indoor heat exchanger (which is the condenser at this time), condenses and liquefies to release heat, and becomes a liquid. At the same time, the indoor air is heated, thus achieving the purpose of raising the indoor temperature. The liquid refrigerant passes through the throttling device to reduce pressure, enters the outdoor heat exchanger (which is the evaporator at this time), evaporates and vaporizes to absorb heat, becomes a gas, and at the same time absorbs the heat of the outdoor air (the outdoor air becomes colder), becomes a gaseous refrigerant, and then enters the compressor again to start the next cycle.

[0065] [Compressor]

[0066] The compressor in this embodiment is a rolling piston compressor. Referring to Figure 1 and Figure 2 , it includes a housing 100. A closed inner cavity is formed inside the housing 100. An electric motor 200 and a compression mechanism 300 are provided in the inner cavity. The electric motor 200 provides power for the compressor mechanism 300, and the compression mechanism 300 is used to compress the refrigerant. The electric motor 200 is arranged above the compression mechanism 300.

[0067] The electric motor 200 includes a stator 210 and a rotor 220. The rotor 220 is arranged inside the stator 210. The stator 210 is fixedly connected to the inner wall of the housing 100 to realize the fixed installation of the electric motor 200 in the inner cavity of the compressor.

[0068] The compression mechanism 300 includes an eccentric crankshaft 310, a cylinder, a piston, and a bearing.

[0069] The eccentric crankshaft 310 includes a main shaft section, an eccentric shaft section, and a secondary shaft section. The main shaft section is fixedly connected to the rotor; referring to Figure 2 , a piston is arranged in the compression cavity of the cylinder. The piston is sleeved on the eccentric shaft section; the bearing is fixedly connected to the cylinder. A bearing exhaust hole is provided on the bearing, and the bearing exhaust hole is communicated with the compression cavity; a sliding vane groove is provided on the cylinder, and a sliding vane is arranged in the sliding vane groove. The eccentric crankshaft drives the piston to perform a circumferential motion in the compression cavity, and the sliding vane reciprocates along the sliding vane groove. The sliding vane always abuts against the piston, and the sliding vane and the piston divide the compression cavity into a high-pressure cavity and a low-pressure cavity.

[0070] The working principle of the compressor is as follows: After the stator 210 of the motor is energized, a magnetic pulling force is generated. The rotor 220 of the motor makes a rotational movement under the action of the magnetic pulling force of the stator, and drives the eccentric crankshaft 310 to make a rotational movement together. When the eccentric crankshaft 310 rotates, it drives the piston sleeved on its eccentric shaft section to make an eccentric circular motion in the compression chamber of the cylinder. The sliding vane makes a reciprocating motion in the sliding vane groove. The sliding vane and the piston divide the compression chamber of the cylinder into a high-pressure chamber and a low-pressure chamber. When the eccentric crankshaft 310 drives the piston to rotate one week, it sucks air from the low-pressure chamber and discharges air from the high-pressure chamber to complete one exhaust, realizing the compression of the gas by the compressor. The compressed gas is discharged through the bearing exhaust hole.

[0071] The exhaust pipe 400 is connected to the top of the housing 100, and the intake pipe 500 is connected to the circumferential side wall of the housing 100. The intake pipe 500 is communicated with the cylinder intake hole.

[0072] Figure 2 As shown in the figure is a double-cylinder rolling rotor compressor. The compression mechanism 300 specifically includes an eccentric crankshaft 310, two cylinders (the upper cylinder 321 and the lower cylinder 322 respectively), two bearings (the upper bearing 331 and the lower bearing 332 respectively), two pistons (the upper piston 361 and the lower piston 362 respectively), and a middle partition plate assembly 340.

[0073] Refer to Figure 13 and Figure 14 As shown in FIGS. and, the eccentric crankshaft 310 successively includes a main shaft section 311, an upper eccentric shaft section 312, a connecting shaft section 313, a lower eccentric shaft section 314, and a secondary shaft section 315 from top to bottom. An upper piston 361 capable of making an eccentric motion is arranged in the compression chamber of the upper cylinder 321, and the upper piston 361 is sleeved on the upper eccentric shaft section 312; a lower piston 362 capable of making an eccentric motion is arranged in the compression chamber of the lower cylinder 322, and the lower piston 362 is sleeved on the lower eccentric shaft section 314; the middle partition plate assembly 340 is sleeved on the connecting shaft section 313, and the middle partition plate assembly 340 is located between the upper cylinder 321 and the lower cylinder 322; the upper bearing 331 is sleeved on the main shaft section 311 and is connected to the upper cylinder 321 at the same time; the lower bearing 332 is sleeved on the secondary shaft section 315 and is connected to the lower cylinder 322 at the same time.

[0074] The upper eccentric shaft section 312 and the lower eccentric shaft section 314 are arranged at a relative angle of 180°. The upper piston 361 and the lower piston 362 make eccentric rotations simultaneously. The compressed air in the compression chamber of the upper cylinder 321 is discharged through the exhaust hole on the upper bearing 331, and the compressed air in the compression chamber of the lower cylinder 322 is discharged through the exhaust hole on the lower bearing 332.

[0075] An upper muffler 351 is provided on the upper bearing 331. The upper muffler 351 covers the exhaust holes of the upper bearing 331. The compressed air in the upper cylinder 321 first discharges through the exhaust holes of the upper bearing 331 into the space enclosed by the upper muffler 351 and the upper bearing 331, and then discharges through the exhaust holes 3511 of the upper muffler into the inner cavity of the compressor.

[0076] A lower muffler 352 is provided on the lower bearing 332. The lower muffler 352 covers the exhaust holes of the lower bearing 332. The compressed air in the lower cylinder 322 first discharges through the exhaust holes on the lower bearing 332 into the space enclosed by the lower muffler 352 and the lower bearing 332.

[0077] Differently, there are no exhaust holes on the lower muffler 352. Multiple through holes penetrating up and down are provided on the walls of the upper bearing 331, the upper cylinder 321, the middle partition assembly 340, the lower cylinder 322, and the lower bearing 332. The compressed air in the lower bearing 332 and the lower muffler 352 discharges upward through the through holes into the space enclosed by the upper bearing 331 and the upper muffler 351, and then discharges through the exhaust holes of the upper muffler into the inner cavity of the compressor.

[0078] [Compression mechanism]

[0079] Figure 13 and Figure 14 The figure shows a schematic structural diagram of the compression mechanism in a twin-cylinder rotary compressor. The compression mechanism includes an upper compression chamber and a lower compression chamber. The upper compression chamber is composed of the upper cylinder 321, the upper piston 361, and the upper bearing 331. The lower compression chamber is composed of the lower cylinder 322, the lower piston 362, and the lower bearing 332. A middle partition assembly 340 is provided between the upper compression chamber and the lower compression chamber.

[0080] Combined with Figure 18 and Figure 19 , the middle partition assembly 340 includes a middle partition body 341, a disk, and an elastic member.

[0081] The middle partition body 341 is integrally in a disk-shaped structure. It is provided between the upper cylinder 321 and the lower cylinder 322 to separate the upper compression chamber and the lower compression chamber.

[0082] There are two disks, which are respectively arranged on the upper side and the lower side of the middle partition body 341. That is, there is one disk on each of the upper side and the lower side of the middle partition body 341. The disks are also integrally in a circular sheet structure.

[0083] The elastic member is provided between the disk and the middle partition body 341. The elastic member applies a force to the disk so that the disk located above always contacts the upper piston 361, and the disk located below always contacts the lower piston 362. The elastic member can be a linear spring.

[0084] Since the material of the piston is mass-produced into the cylinder, and the cylinder is mass-produced into cast iron, because the thermal expansion coefficient of steel is greater than that of cast iron, the piston is deliberately set shorter to meet the clearance requirements for thermal expansion and contraction at 120 °C. The existence of this clearance causes two problems: ① When the compressor fails, such as running in reverse, the cylinder will jam when the temperature is higher than 120 °C; ② This clearance reduces the exhaust efficiency.

[0085] Two movable disks up and down can solve the above problems. When the piston (including the upper piston 361 and the lower piston 362) deforms due to thermal expansion and contraction, the two disks move correspondingly under the action of the elastic members, and the positions of the two disks are adjusted by the elastic members so that the disks can always be in contact with the upper piston 361 and the lower piston 362 correspondingly, thereby avoiding the technical problems of cylinder jamming and low exhaust efficiency caused by the appearance of gaps between the middle partition plate assembly 340 and the upper piston 361 and the lower piston 362, and improving the energy efficiency of the compressor.

[0086] For the specific installation structure of the two disks, in some embodiments, referring to Figures 16 to 19 , on the upper side of the middle partition plate body 341, there is an upper groove 3411. The upper groove 3411 is a circular sunk groove structure. An upper disk 342 is arranged in the upper groove 3411. An upper elastic member 344 is arranged between the upper disk 342 and the bottom wall of the upper groove 3411. The upper elastic member 344 applies an upward acting force to the upper disk 342 so that the upper disk 342 can always be in contact with the upper piston 361.

[0087] Similarly, on the lower side of the middle partition plate body 341, there is a lower groove. The lower groove is a circular sunk groove structure. A lower disk 343 is arranged in the lower groove. A lower elastic member 345 is arranged between the lower disk 343 and the top wall of the lower groove. The lower elastic member 345 applies a downward acting force to the lower disk 343 so that the lower disk 343 can always be in contact with the lower piston 362.

[0088] In some embodiments, the diameter of the upper disk 342 is not greater than the inner diameter of the upper cylinder 321. When the upper disk 342 moves upward, it can enter the inner cavity of the upper cylinder 321 and be in contact with the upper piston 361, avoiding the interference of the bottom wall of the upper cylinder 321 with the movement of the upper disk 342.

[0089] The diameter of the lower disk 343 is not greater than the inner diameter of the lower cylinder 322. When the lower disk 343 moves downward, it can enter the inner cavity of the lower cylinder 322 and be in contact with the lower piston 362, avoiding the interference of the bottom wall of the lower cylinder 322 with the movement of the lower disk 343.

[0090] In some embodiments, a plurality of upper mounting grooves 3412 are arranged at intervals along the circumferential direction on the bottom wall of the upper groove 3411. The upper elastic member 344 is arranged in the upper mounting grooves 3412 to improve the installation reliability of the upper elastic member 344.

[0091] Similarly, a plurality of lower mounting grooves are provided on the bottom wall of the lower groove and are arranged at intervals along its circumferential direction. The lower elastic member 345 is arranged in the lower mounting groove, improving the mounting reliability of the lower elastic member 345.

[0092] [Lift limiter, exhaust valve disc]

[0093] Refer to Figure 15 、 Figure 20 and Figure 21 , an exhaust hole 335 is provided on the upper bearing 331. The compressed air in the upper compression chamber flows into the exhaust hole 335 of the upper bearing through the exhaust hole of the upper cylinder 321 and then is discharged. An lift limiter 333 and an exhaust valve disc 334 are provided on the upper bearing 331. The exhaust valve disc 334 is used to open and close the exhaust hole 335 of the upper bearing, and the lift limiter 333 is used to limit the displacement of the exhaust valve disc 334.

[0094] An installation groove is provided on the upper bearing 331. The lift limiter 333 is a sheet-like structure. One ends of the lift limiter 333 and the exhaust valve disc 334 are fixedly arranged in the installation groove through bolts. During exhaust, the exhaust valve disc 334 is opened under the impact of the compressed air, and the compressed air is discharged. After the exhaust is completed, the exhaust valve disc 334 automatically resets.

[0095] During the application of the compressor, it often occurs that the wiring is reversed, resulting in the reverse rotation of the compressor. The entire pump body is in a vacuum state. The pump body will quickly generate high temperature in the vacuum state, and then wear will occur. If the parts are severely worn, the compressor will be stuck and fail, etc. The continuous high temperature will also demagnetize the motor and melt some plastic parts.

[0096] In some embodiments, in the present application, the lift limiter 333 and the exhaust valve disc 334 are made of a magnetic material. When the temperature in the compression chamber reaches the upper limit value, the lift limiter 333 and the exhaust valve disc 334 respectively generate magnetism to attract each other. The exhaust valve disc 334 is adsorbed by the lift limiter 333, and the exhaust valve disc 334 moves away from the exhaust hole 335 to open the exhaust hole 335. At this time, the exhaust passage of the compression chamber is connected, and the compressor is no longer in a vacuum state, so the temperature will not continue to rise, avoiding damage to the compressor and improving the operation reliability of the compressor.

[0097] The magnetic material has the characteristic of generating magnetism as the temperature rises. When the temperature rises to a certain temperature, the lift limiter 333 and the exhaust valve disc 334 generate magnetism and attract each other to achieve the purpose of opening the exhaust hole 335. When the temperature drops to a certain temperature, the magnetism on the lift limiter 333 and the exhaust valve disc 334 disappears, and the exhaust valve disc 334 resets to return to the normal working state.

[0098] The magnetic material is a well-known material in the prior art. For the specific principle, reference can be made to the existing literature, and no specific elaboration will be made in this article.

[0099] In some embodiments, a temperature sensor (not shown) is provided on the intake pipe 500 of the compressor. The temperature sensor is disposed close to the housing 100 of the compressor. The temperature sensor is used to detect the temperature at the intake port of the compressor. The compressor stops operating when the difference between the temperature measured by the temperature sensor and the ambient temperature is greater than a set value, so as to avoid aggravating the wear of the compression mechanism due to high temperature and improve the operating reliability of the compressor.

[0100] By detecting the temperature at the intake port, the purpose of reverse rotation protection is achieved.

[0101] The distance between the temperature sensor and the housing 100 of the compressor is 5 - 10 mm to improve the reliability of temperature detection.

[0102] In some embodiments, a thermal protector (not shown) is provided on the intake pipe 500 of the compressor. The thermal protector is disposed close to the housing 100 of the compressor. The intake pipe 500 is made of a metal with heat conduction performance, such as copper.

[0103] When the compressor rotates in reverse, the exhaust valve plate is in a closed state and no high-pressure gas is discharged. Therefore, the temperature near the upper shell of the housing is relatively high, and the temperature sensor thereon cannot sense the abnormal temperature and cannot play a role in timely protection, ultimately causing damage to the compressor. By providing the thermal protector, when the temperature of the cylinder increases, heat is transferred to the thermal protector through the copper intake pipe 500, and the thermal protector disconnects the power supply to play a protective role and improve the operating reliability of the compressor.

[0104] [Rotor, balance weight]

[0105] Refer to Figures 3 to 6 , a shaft hole for connecting with the eccentric crankshaft 310 is provided in the middle of the rotor 220. A plurality of through holes 221 arranged at intervals are provided along the outer periphery of the shaft hole. The refrigerant compressed by the bottom compression mechanism 300 flows upward through the through holes 221 and finally discharges from the exhaust pipe 400.

[0106] An upper balance weight 700 is provided at the top of the rotor 220, and a lower balance weight 800 is provided at the bottom.

[0107] Figures 8 to 11 The upper balance weight 700 shown is of different structural deformations. The upper balance weight 700 is of an annular structure, and a plurality of protruding portions 711 arranged at intervals are provided on the upper surface of the annular structure. An air flow channel 712 for the refrigerant to flow through is formed between two adjacent protruding portions 711.

[0108] An oil blocking portion 600 is provided at the top of the upper balance weight 700. The oil blocking portion 600 is located directly above the through hole 221, that is, refer to Figure 7When viewed from above, the through-hole 221 is completely blocked by the oil baffle 600, and the oil baffle 600 simultaneously covers the top opening of the air flow channel 712.

[0109] After the refrigerant compressed by the compression mechanism 300 flows upward through the through-hole 221 on the rotor 220, it is blocked by the oil baffle 600 and cannot continue to flow upward. Under the centrifugal force of the rotor 220, the refrigerant with oil is radially thrown out along the air flow channel 712. On the one hand, the air flow channel 712 helps to improve the full separation of the refrigerant and the oil, reducing the oil spitting rate of the compressor. On the other hand, the air flow channel 712 is equivalent to increasing the oil return channel, which helps to accelerate the oil return speed, keep the oil volume in the oil sump at the bottom of the compressor sufficient, and thus ensure the lubrication effect and operation reliability of the compressor.

[0110] In some embodiments, the extending direction of the air flow channel 712 is the same as the rotation direction of the rotor 220. At this time, the air flow channel 712 is similar to the centrifugal line of the refrigerant flow, which helps to further improve the gas-liquid separation effect and the oil return speed.

[0111] In some embodiments, referring to Figure 8 The annular structure includes two relatively arranged first half-ring structures 710 and second half-ring structures 720. The two half-ring structures enclose the annular structure. The first half-ring structure 710 and the second half-ring structure 720 are an integral structure. A plurality of convex portions 711 are arranged on the upper surface of the first half-ring structure 710, and the offset arrangement of the plurality of convex portions 711 serves as the function of the top balance weight.

[0112] At least one convex portion 711 is provided with a first mounting hole 713, and the second half-ring structure 720 is provided with a first mounting post 721. The oil baffle 600 is fixedly mounted to the first mounting hole 713 and the first mounting post 721 through a connecting member (such as a screw), so as to realize the fixed mounting of the oil baffle 600 on the top of the upper balance weight 700.

[0113] The structure of the oil baffle 600 refers to Figure 12 It is a disc-shaped structure. The outer diameter of the oil baffle 600 is the same as the outer diameter of the rotor 220. The oil baffle 600 is provided with screw holes 610 for the above-mentioned connecting members to pass through.

[0114] The lower balance weight 800 is opposite to the second half-ring structure 720, and the upper balance structure formed by the plurality of convex portions 711 is staggered from the lower balance weight 800 to realize the balancing effect on the rotor 220.

[0115] For the fixed mounting structure among the upper balance weight 700, the lower balance weight 800, and the rotor 220, in some embodiments, referring to Figure 8, a second mounting hole 714 is provided on the first semi-ring structure 710. The second mounting hole 714 is located within the air flow passage 712. A third mounting hole 722 is provided on the second semi-ring structure 720. The first rivet 910 passes through the second mounting hole 714 and the rotor 220, and the second rivet 920 passes through the third mounting hole 722, the rotor 220, and the lower balance weight 800, thereby realizing the fixed installation among the upper balance weight 700, the lower balance weight 800, and the rotor 220.

[0116] The height h1 of the first semi-ring structure 10 is greater than the height h2 of the second semi-ring structure 720. The purpose is to make the length of the first rivet 910 equal to the length of the second rivet 920, so as to unify multiple rivets into one part number for convenient assembly.

[0117] Regarding the fixed installation structure among the upper balance weight 700, the lower balance weight 800, and the rotor 220, in some other embodiments, refer to Figure 10 , a second mounting post 715 is provided within the air flow passage 712. A third mounting hole 722 is provided on the second semi-ring structure 720. The first rivet 910 passes through the second mounting post 715, the first semi-ring structure 710, and the rotor 220, and the second rivet 920 passes through the third mounting hole 722, the rotor 220, and the lower balance weight 800, thereby realizing the fixed installation among the upper balance weight 700, the lower balance weight 800, and the rotor 220.

[0118] The provision of the second mounting post 715 is also to make the length of the first rivet 910 equal to the length of the second rivet 920, so as to unify multiple rivets into one part number for convenient assembly.

[0119] There is a gap for refrigerant flow between the second mounting post 715 and the vertical side wall of the convex portion 711, so as not to affect the normal flow of the refrigerant.

[0120] Corresponding to the setting of the convex portion, in a specific embodiment, refer to Figure 8 , there are four convex portions 711, including two symmetrically arranged first convex portions 7111 and two symmetrically arranged second convex portions 7112. The two second convex portions 7112 are provided between the two first convex portions 7111. Three air flow passages 712 are formed among the four convex portions 711. First mounting holes 713 are provided on the two second convex portions 7112. Two first mounting posts 721 are provided on the second semi-ring structure 720. Correspondingly, refer to Figure 12 , four screw holes 610 are provided on the oil baffle portion 600 to realize the reliable installation of the oil baffle portion 600.

[0121] In some embodiments, a groove 716 is provided on the upper surface of the convex portion 711 without the first mounting hole 713. A passage for refrigerant flow is defined between the groove 716 and the oil baffle portion 600.

[0122] For example, with reference to Figure 9 , on the two second protrusions 7112 located in the middle, there are first mounting holes 713. The top surfaces of the two second protrusions 7112 are in contact with the oil baffle 600. Then, grooves 716 are provided on the upper surfaces of the two first protrusions 7111. A channel for refrigerant flow is defined between the grooves 716 and the oil baffle 600, increasing the refrigerant flow path, further improving the oil return efficiency, and enhancing the separation effect of the refrigerant and the oil.

[0123] Similarly, on the upper balance weight 700 shown in Figure 11 , grooves 716 are provided on the two first protrusions 7111.

[0124] In some embodiments, the groove 716 is set as an arc-shaped groove structure, and the arc extension direction of the groove 716 is the same as the rotation direction of the rotor 220. At this time, the groove 716 is similar to the centrifugal line of the refrigerant flow, which helps to further improve the gas-liquid separation effect and the oil return speed.

[0125] In the description of the above embodiments, specific features, structures, materials, or characteristics can be combined in a suitable manner in any one or more embodiments or examples.

[0126] The above is only the specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by those skilled in the art within the technical scope disclosed by the present invention should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention should be subject to the protection scope of the claims.

Claims

1. A twin-cylinder rotary compressor, comprising: A compression mechanism for compressing a refrigerant. The compression mechanism includes an upper compression chamber and a lower compression chamber. The upper compression chamber is composed of an upper cylinder, an upper piston, and an upper bearing. The lower compression chamber is composed of a lower cylinder, a lower piston, and a lower bearing. A middle partition plate assembly is provided between the upper compression chamber and the lower compression chamber; Characterized in that the middle partition plate assembly includes: A middle partition plate body provided between the upper cylinder and the lower cylinder to separate the upper compression chamber and the lower compression chamber; Two discs respectively provided on the upper side and the lower side of the middle partition plate body; An elastic member provided between the disc and the middle partition plate body. The elastic member applies a force to the disc so that the disc located above always contacts the upper piston, and the disc located below always contacts the lower piston; An upper groove is provided on the upper side of the middle partition plate body. An upper disc is provided in the upper groove. An upper elastic member is provided between the upper disc and the bottom wall of the upper groove. The upper elastic member applies an upward movement force to the upper disc so that the upper disc always contacts the upper piston; A lower groove is provided on the lower side of the middle partition plate body. A lower disc is provided in the lower groove. A lower elastic member is provided between the lower disc and the top wall of the lower groove. The lower elastic member applies a downward movement force to the lower disc so that the lower disc always contacts the lower piston; A lift limiter and an exhaust valve plate are provided on the upper bearing; The lift limiter and the exhaust valve plate are made of a magnetic material. When the temperature in the compression chamber reaches the upper limit value, the lift limiter and the exhaust valve plate respectively generate magnetism to attract each other, and the exhaust valve plate is adsorbed by the lift limiter.

2. The twin-cylinder rotary compressor according to claim 1, characterized in that The diameter of the upper disc is not greater than the inner diameter of the upper cylinder, and the diameter of the lower disc is not greater than the inner diameter of the lower cylinder.

3. The twin-cylinder rotary compressor according to claim 1, characterized in that A plurality of upper mounting grooves are provided on the bottom wall of the upper groove and are arranged at intervals along its circumference. The upper elastic member is provided in the upper mounting groove; A plurality of lower mounting grooves are provided on the bottom wall of the lower groove and are arranged at intervals along its circumference. The lower elastic member is provided in the lower mounting groove.

4. The twin-cylinder rotary compressor according to any one of claims 1 to 3, characterized in that The compressor further includes a motor. The motor includes a stator and a rotor provided inside the stator. The rotor is connected to an eccentric crankshaft in the compression mechanism. The motor is provided above the compression mechanism. A through hole extending along its axial direction is provided on the rotor. The refrigerant compressed by the compression mechanism flows upward through the through hole; An upper balance weight is provided at the top of the rotor. The upper balance weight is of an annular structure. A plurality of spaced protrusions are provided on the upper surface of the annular structure. An air flow channel for refrigerant flow is formed between adjacent two of the protrusions; The top of the upper balance weight is provided with an oil baffle portion, and the oil baffle portion is located directly above the through hole and covers the top opening of the air flow passage.

5. The twin-cylinder rotary compressor according to claim 4, wherein the annular structure includes two relatively arranged first half-ring structures and second half-ring structures, and a plurality of the convex portions are provided on the upper surface of the first half-ring structure; at least one of the convex portions is provided with a first mounting hole, the second half-ring structure is provided with a first mounting post, and the oil baffle portion is fixedly mounted to the first mounting hole and the first mounting post through a connecting member.

6. The twin-cylinder rotary compressor according to claim 5, wherein the bottom of the rotor is provided with a lower balance weight, and the lower balance weight faces the second half-ring structure; a first rivet is passed through between the first half-ring structure and the rotor, and a second rivet is passed through between the second half-ring structure, the rotor, and the lower balance weight.

7. The twin-cylinder rotary compressor according to claim 4, wherein a groove is provided on the upper surface of the convex portion, and a passage for refrigerant to flow is defined between the groove and the oil baffle portion.

8. The twin-cylinder rotary compressor according to claim 4, wherein the extending direction of the air flow passage is the same as the rotation direction of the rotor.

9. An air conditioner, characterized in that, including the twin-cylinder rotary compressor according to any one of claims 1 to 8.

Images