CN115405524A - Double-cylinder rotor type compressor and air conditioner - Google Patents

Abstract

The invention discloses a double-cylinder rotor type compressor and an air conditioner.A compression mechanism comprises an upper compression cavity and a lower compression cavity, and a middle partition plate assembly is arranged between the upper compression cavity and the lower compression cavity; the middle clapboard component comprises a middle clapboard body, a disc and an elastic piece, wherein the middle clapboard body is arranged between the upper air cylinder and the lower air cylinder so as to separate the upper compression cavity from the lower compression cavity; the two disks are respectively arranged on the upper side and the lower side of the middle clapboard body; the elastic piece is arranged between the disk and the middle partition plate body and applies acting force to the disk so that the disk positioned above is always in contact with the upper piston and the disk positioned below is always in contact with the lower piston. When the piston is deformed due to expansion with heat and contraction with cold, the positions of the two discs are adjusted through the elastic piece, so that the discs can be in corresponding contact with the upper piston and the lower piston all the time, and the technical problems of cylinder clamping and low exhaust efficiency caused by the occurrence of gaps among the middle partition plate assembly, the upper piston and the lower piston are avoided.

Description

A double-cylinder rotor compressor and air conditioner

technical field

The invention relates to the technical field of refrigeration equipment, in particular to a double-cylinder rotor compressor and an air conditioner.

Background technique

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

The low-temperature and low-pressure refrigerant enters the compressor, and the compressor compresses it into a high-temperature and high-pressure refrigerant gas 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 the heat is released to the surrounding environment through the condensation process.

Rolling rotor compressors are now widely used in air conditioners. The working principle of the existing rolling rotor compressors is: the motor stator generates magnetic pulling force after being energized, and the motor rotor rotates under the magnetic pulling force of the stator, and drives the compression mechanism. The eccentric crankshaft rotates together, and the rotation of the eccentric crankshaft drives the piston sleeved on the eccentric part to perform eccentric circular motion in the cylinder. The sliding vane is installed in the sliding vane groove of the cylinder, under the action of the compression spring in the spring hole Always hold the piston to make it reciprocate in the sliding vane slot. The sliding vane and piston divide the cylinder into a high-pressure chamber and a low-pressure chamber. The eccentric crankshaft drives the piston to rotate one circle, sucking air from the low-pressure chamber and exhausting from the high-pressure chamber. Gas, so the compressor can compress the gas.

In a twin-cylinder rotor 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). The structure and function of the cavity and the lower compression cavity are the same. The interval between the upper compression chamber and the lower compression chamber is realized by a middle partition. The mass production of the piston is a cylinder, and the mass production of the cylinder is cast iron. Because the thermal expansion coefficient of steel is greater than that of cast iron, the piston must be deliberately set shorter and meet the gap requirements for thermal expansion and contraction at 120 °C. The existence of this gap will produce two Problems: ① When the compressor fails, such as reverse rotation, the cylinder will be stuck when the temperature is higher than 120 ℃; ② The gap reduces the exhaust efficiency.

The above information disclosed in this background technology is only for enhancement of understanding of the background technology of this application, and therefore it may include information that does not constitute the prior art that is already known to a person of ordinary skill in the art.

Contents of the invention

Aiming at the problems pointed out in the background technology, the present invention proposes a double-cylinder rotor compressor and an air conditioner. By improving the structure of the middle partition, the middle partition has a moving amount in the up and down direction, so that the middle partition can always be in line with the The contact between the upper piston and the lower piston eliminates the gap between the intermediate partition and the piston in the prior art, thereby avoiding the cylinder stuck, improving the exhaust efficiency and improving the energy efficiency of the compressor.

In order to achieve the above-mentioned purpose of the invention, the present invention adopts the following technical solutions to achieve:

Provided is a double-cylinder rotor compressor. The upper compression chamber and the lower compression chamber are separated by a middle partition assembly. The middle partition assembly includes a middle partition body, a disc and an elastic member. The middle partition body is designed Between the upper cylinder and the lower cylinder to separate the upper compression chamber and the lower compression chamber; there are two disks, which are respectively arranged on the upper side and the lower side of the middle partition body; the elastic member is arranged between the disk and the middle partition Between the plate bodies, the elastic member exerts force on the discs so that the upper disc is always in contact with the upper piston, and the lower disc is always in contact with the lower piston.

When the piston is deformed due to heat expansion and contraction, the position of the two discs is adjusted by the elastic member, so that the discs can always be in corresponding contact with the upper piston and the lower piston, thereby avoiding the gap between the middle partition plate assembly and the upper piston and the lower piston. The technical problems of cylinder sticking and low exhaust efficiency caused by gaps.

Other characteristics and advantages of the present invention will become clearer after reading the detailed description of the present invention in conjunction with the accompanying drawings.

Description of drawings

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 that need to be used in the description of the embodiments or the prior art. Obviously, the accompanying drawings in the following description These are some embodiments of the present invention. For those skilled in the art, other drawings can also be obtained according to these drawings without any creative effort.

Fig. 1 is a schematic structural view of a compressor according to an embodiment;

2 is a cross-sectional view of a compressor according to an embodiment;

Fig. 3 is a schematic diagram of the assembly structure of the rotor, the upper balance weight, the lower balance weight, and the oil retaining part according to the embodiment;

Fig. 4 is a sectional view of the structure shown in Fig. 3;

Fig. 5 is a structural schematic diagram of the structure shown in Fig. 3 omitting the oil deflector;

Fig. 6 is a schematic structural view of the structure shown in Fig. 3 observed from Q1 direction;

Fig. 7 is a top view of the structure shown in Fig. 3;

Fig. 8 is a schematic structural diagram of an upper balance weight according to an embodiment;

Fig. 9 is a second structural schematic diagram of the upper balance weight according to the embodiment;

Fig. 10 is a schematic diagram of the third structure of the upper balance weight according to the embodiment;

Fig. 11 is a schematic view 4 of the structure of the upper balance weight according to the embodiment;

Fig. 12 is a schematic structural diagram of an oil deflector according to an embodiment;

Fig. 13 is a schematic structural diagram of a compression mechanism according to an embodiment;

Figure 14 is a sectional view of the compression mechanism shown in Figure 13;

Figure 15 is a schematic view of the structure observed from Q2 as shown in Figure 13

Fig. 16 is a schematic structural diagram of a middle partition assembly according to an embodiment;

Fig. 17 is a schematic structural diagram of a middle partition body according to an embodiment;

18 is a cross-sectional view of a center bulkhead assembly according to an embodiment;

Figure 19 is an exploded view of a center bulkhead assembly according to an embodiment;

Fig. 20 is a schematic diagram of the assembly structure among the upper bearing, the lift limiter, and the exhaust valve plate according to the embodiment;

Fig. 21 is a sectional view along A-A in Fig. 20;

Reference signs:

100-housing;

200-motor, 210-stator, 220-rotor, 221-through hole;

300 - compression mechanism;

310-eccentric crankshaft, 311-main shaft section, 312-upper eccentric shaft section, 313-connecting shaft section, 314-lower eccentric shaft section, 315-minor shaft section;

321-upper cylinder, 322-lower cylinder;

331-upper bearing, 332-lower bearing, 333-lift limiter, 334-exhaust valve plate, 335-exhaust hole of upper bearing;

340-middle partition assembly, 341-middle partition body, 3411-upper groove, 3412-upper installation groove, 342-upper disk, 343-lower disk, 344-upper elastic member, 345-lower elastic member;

351-upper muffler, 352-lower muffler;

361-upper piston, 362-lower piston;

400-exhaust pipe;

500-intake pipe;

600-oil retaining part, 610-screw hole;

700-upper balance weight, 710-first half-ring structure, 711-protrusion, 7111-first protrusion, 7112-second protrusion, 712-air flow channel, 713-first mounting hole, 714- The second installation hole, 715-the second installation column, 716-the groove, 720-the second half-ring structure, 721-the first installation column, 722-the third installation hole;

800-lower balance weight;

910 - first rivet, 920 - second rivet.

Detailed ways

The following will clearly and completely describe the technical solutions in the embodiments of the application with reference to the drawings in the embodiments of the application. Apparently, the described embodiments are only some of the embodiments of the application, not all of them. Based on the embodiments in this application, all other embodiments obtained by persons of ordinary skill in the art without making creative efforts belong to the scope of protection of this application.

In the description of this application, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", The orientations or positional relationships indicated by "top", "bottom", "inner", "outer", etc. are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the application and simplifying the description, rather than indicating or implying References to devices or elements must have a particular orientation, be constructed, and operate in a particular orientation and therefore should not be construed as limiting the application.

The terms "first" and "second" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, a feature defined as "first" and "second" may explicitly or implicitly include one or more of these features. In the description of the present application, unless otherwise specified, "plurality" means two or more.

In the description of this application, it should be noted that unless otherwise specified and limited, the terms "installation", "connection", and "connection" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection. Connected, or integrally connected; it can be mechanically connected or electrically connected; it can be directly connected or indirectly connected through an intermediary, and it can be the internal communication of two components. Those of ordinary skill in the art can understand the specific meanings of the above terms in this application in specific situations.

In the present invention, unless otherwise clearly specified and limited, a first feature being "on" or "under" a second feature may include direct contact between the first and second features, and may also include the first and second features Not in direct contact but through another characteristic contact between them. Moreover, "above", "above" and "above" the first feature on the second feature include that the first feature is directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature. "Below", "beneath" and "under" the first feature to the second feature include that the first feature is directly below and obliquely below the second feature, or simply means that the first feature has a lower level than the second feature.

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, components and arrangements of specific examples are described below. Of course, they are only examples and are not intended to limit the invention. Furthermore, the present disclosure may repeat reference numerals and/or reference letters in different instances, such repetition is for simplicity and clarity and does not in itself indicate a relationship between the various embodiments and/or arrangements discussed. In addition, various specific process and material examples are provided herein, but one of ordinary skill in the art may recognize the use of other processes and/or the use of other materials.

[air conditioner]

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

The low-temperature and low-pressure refrigerant enters the compressor, and the compressor compresses it into a high-temperature and high-pressure refrigerant gas 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 the heat is released to the surrounding environment through the condensation process.

The expansion valve expands the high-temperature and high-pressure liquid-phase refrigerant condensed 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 realize the cooling 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 regulates the temperature of the interior space.

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

The indoor heat exchanger and the outdoor heat exchanger are used as condensers or evaporators. When the indoor heat exchanger is used as a condenser, the air conditioner performs a heating mode; when the indoor heat exchanger is used as an evaporator, the air conditioner performs a cooling mode.

Among them, the conversion of the indoor heat exchanger and the outdoor heat exchanger into a condenser or an evaporator generally adopts a four-way valve. For details, refer to the settings of a conventional air conditioner, and will not be repeated here.

The refrigeration working principle of the air conditioner is: the compressor works so that the indoor heat exchanger (in the indoor unit, 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, and the indoor fan blows out After being cooled by the indoor heat exchanger coil, the air becomes cold air and is blown indoors. After the vaporized refrigerant is pressurized by the compressor, the high pressure in the outdoor heat exchanger (in the outdoor unit, it is the condenser at this time) It condenses into a liquid state in the environment, releases heat, and dissipates the heat into the atmosphere through the outdoor fan, so that the cycle achieves the cooling effect.

The heating working principle of the air conditioner is: the gaseous refrigerant is pressurized by the compressor to become a high-temperature and high-pressure gas, enters the indoor heat exchanger (in this case, the condenser), condenses and liquefies, releases heat, and becomes a liquid, and at the same time heats the indoor air, thereby To achieve the purpose of increasing the indoor temperature. The liquid refrigerant is decompressed by the throttling device, enters the outdoor heat exchanger (the evaporator at this time), evaporates and gasifies, absorbs heat, and becomes a gas. At the same time, it absorbs the heat of the outdoor air (the outdoor air becomes colder), and becomes a gaseous refrigerant. Enter the compressor again to start the next cycle.

[compressor]

The compressor in this embodiment is a rolling rotor compressor, referring to Fig. 1 and Fig. 2, it includes a casing 100, and a closed inner cavity is formed in the casing 100, and a motor 200 and a compression mechanism 300 are arranged in the inner cavity, and the motor The motor 200 provides power for the compressor mechanism 300 , and the compression mechanism 300 is used for compressing refrigerant, and the motor 200 is arranged above the compression mechanism 300 .

The motor 200 includes a stator 210 and a rotor 220. The rotor 220 is disposed inside the stator 210. The stator 210 is fixedly connected to the inner wall of the casing 100, so as to realize the fixed installation of the motor 200 in the inner cavity of the compressor.

The compression mechanism 300 includes an eccentric crankshaft 310, a cylinder, a piston, and bearings.

The eccentric crankshaft 310 includes a main shaft section, an eccentric shaft section and a subshaft section, the main shaft section is fixedly connected to the rotor; referring to Fig. 2 , a piston is provided in the compression chamber of the cylinder, and the piston is sleeved on the eccentric shaft section; the bearing is fixedly connected to the cylinder, The bearing is equipped with a bearing exhaust hole, and the bearing exhaust hole is connected with the compression chamber; the cylinder is provided with a slide groove, and a slide plate is arranged in the slide groove, and the eccentric crankshaft drives the piston to make a circumferential movement in the compression chamber, and the slide plate Reciprocating along the sliding vane groove, the sliding vane always abuts against the piston, and the sliding vane and piston separate the compression chamber into a high-pressure chamber and a low-pressure chamber.

The working principle of the compressor is as follows: the stator 210 of the motor generates magnetic pulling force after being energized, the rotor 220 of the motor rotates under the magnetic pulling force of the stator, and drives the eccentric crankshaft 310 to rotate together, and the rotation of the eccentric crankshaft 310 drives the sleeve The piston on its eccentric shaft section performs eccentric circular motion in the compression chamber of the cylinder, and the sliding vane reciprocates in the sliding vane groove. The sliding vane and piston divide the compression chamber of the cylinder into a high-pressure chamber and a low-pressure chamber. The eccentric crankshaft 310 When the piston is driven to rotate once, air is sucked from the low-pressure chamber and exhausted from the high-pressure chamber to complete an exhaust, so as to realize the compression of the gas by the compressor, and the compressed gas is discharged through the bearing exhaust hole.

The exhaust pipe 400 is connected to the top of the casing 100 , the intake pipe 500 is connected to the circumferential side wall of the casing 100 , and the intake pipe 500 communicates with the air intake hole of the cylinder.

Figure 2 shows a double-cylinder rolling rotor compressor, and the compression mechanism 300 specifically includes an eccentric crankshaft 310, two cylinders (respectively upper cylinder 321 and lower cylinder 322), two bearings (respectively upper bearing 331 and lower bearing 332 ), two pistons (respectively upper piston 361 and lower piston 362 ), and a middle diaphragm assembly 340 .

13 and 14, the eccentric crankshaft 310 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 countershaft section 315 from top to bottom. There is an upper piston 361 capable of eccentric movement, and the upper piston 361 is sleeved on the upper eccentric shaft section 312; a lower piston 362 capable of eccentric movement is provided 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 assembly 340 is sleeved on the connecting shaft section 313, and the middle partition 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 simultaneously with the upper cylinder 321 connection; the lower bearing 332 is sleeved on the auxiliary shaft section 315 and is connected with the lower cylinder 322 at the same time.

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 rotate eccentrically at the same time, and the compressed gas in the compression chamber of the upper cylinder 321 is discharged through the exhaust hole on the upper bearing 331 , The compressed gas in the compression chamber of the lower cylinder 322 is discharged through the exhaust hole on the lower bearing 332 .

The upper bearing 331 is provided with an upper muffler 351, and the upper muffler 351 covers the exhaust hole of the upper bearing 331. The compressed gas in the upper cylinder 321 is first discharged to the upper muffler 351 and the upper bearing through the exhaust hole of the upper bearing 331. In the space surrounded by 331, it is discharged into the inner cavity of the compressor through the exhaust hole 3511 of the upper muffler.

The lower bearing 332 is provided with a lower muffler 352, and the lower muffler 352 covers the exhaust hole of the lower bearing 332, and the compressed gas in the lower cylinder 322 is first discharged to the lower muffler 352 and the lower bearing 332 through the exhaust hole. In the space enclosed by the lower bearing 332.

The difference is that there is no exhaust hole on the lower muffler 352, and 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 are provided with a plurality of through holes that penetrate up and down. 332 and the compressed gas in the lower muffler 352 are discharged upwards into the space surrounded by the upper bearing 331 and the upper muffler 351 through the through holes, and then discharged into the inner cavity of the compressor through the exhaust hole of the upper muffler.

[compression mechanism]

Fig. 13 and Fig. 14 are schematic diagrams showing the structure of the compression mechanism in the twin-cylinder rotary compressor. The compression mechanism includes an upper compression chamber and a lower compression chamber. The upper compression chamber is composed of an upper cylinder 321, an upper piston 361, and an upper bearing 331. , the lower compression chamber is composed of a lower cylinder 322, a lower piston 362, and a lower bearing 332, and a middle partition assembly 340 is arranged between the upper compression chamber and the lower compression chamber.

Referring again to FIG. 18 and FIG. 19 , the middle partition assembly 340 includes a middle partition body 341 , a disk, and an elastic member.

The middle partition body 341 is in the shape of a disc as a whole, and is arranged between the upper cylinder 321 and the lower cylinder 322 to separate the upper compression chamber from the lower compression chamber.

There are two disks, which are respectively arranged on the upper side and the lower side of the middle partition body 341, that is, one disk is respectively arranged on the upper side and the lower side of the middle partition body 341, and the whole disk is also in a circular sheet structure. .

The elastic member is disposed between the disk and the middle partition body 341 , and the elastic member exerts force on the disk so that the upper disk is always in contact with the upper piston 361 , and the lower disk is always in contact with the lower piston 362 . The elastic member can be a linear spring.

Since the mass production of the piston is a cylinder, and the mass production of the cylinder is cast iron, because the thermal expansion coefficient of steel is greater than that of cast iron, the piston must be deliberately set shorter and meet the gap requirements for thermal expansion and contraction at 120 °C. The existence of this gap will cause two There are two problems: ① When the compressor fails, such as when it is reversed, the cylinder will be stuck if the temperature is higher than 120 °C; ② The gap reduces the exhaust efficiency.

Two disks that can move up and down can solve the above problems. When the piston (including the upper piston 361 and the lower piston 362) is deformed due to thermal expansion and contraction, the two disks move correspondingly under the action of the elastic member. Elastic parts are used to adjust the positions of the two disks, so that the disks can always be in corresponding contact with the upper piston 361 and the lower piston 362, thereby avoiding gaps between the middle partition assembly 340 and the upper piston 361 and the lower piston 362. Cylinder stuck, low exhaust efficiency technical problems, improve compressor energy efficiency.

Regarding the specific installation structure of the two disks, in some embodiments, referring to Figures 16 to 19, an upper groove 3411 is provided on the upper side of the middle partition body 341, and the upper groove 3411 is a circular sinker structure, An upper disc 342 is arranged in the upper groove 3411, and an upper elastic member 344 is arranged between the upper disc 342 and the bottom wall of the upper groove 3411. The upper elastic member 344 exerts an upward movement force on the upper disc 342, so that The upper disc 342 is always in contact with the upper piston 361 .

Similarly, the lower side of the middle partition body 341 is provided with a lower groove, the lower groove is a circular sinker structure, the lower groove is provided with a lower disc 343, and the lower disc 343 is connected to the top wall of the lower groove. A lower elastic member 345 is disposed therebetween, and the lower elastic member 345 exerts a downward movement force on the lower disc 343 so that the lower disc 343 is always in contact with the lower piston 362 .

In some embodiments, the diameter of the upper disc 342 is not larger than the inner diameter of the upper cylinder 321, and when the upper disc 342 moves upward, it can enter the inner cavity of the upper cylinder 321 and contact the upper piston 361, avoiding the bottom wall of the upper cylinder 321. Interfering with the movement of the upper platter 342 .

The diameter of the lower disc 343 is not greater than the inner diameter of the lower cylinder 322. When the lower disc 343 moves downward, it can enter the inner cavity of the lower cylinder 322 and contact the lower piston 362, so as to prevent the bottom wall of the lower cylinder 322 from interfering with the lower disc 343. exercise.

In some embodiments, the bottom wall of the upper groove 3411 is provided with a plurality of upper installation grooves 3412 arranged at intervals along its circumference, and the upper elastic member 344 is arranged in the upper installation groove 3412 to improve the installation reliability of the upper elastic member 344 sex.

Similarly, the bottom wall of the lower groove is provided with a plurality of lower installation grooves arranged at intervals along its circumference, and the lower elastic member 345 is arranged in the lower installation groove to improve the installation reliability of the lower elastic member 345 .

[Lift limiter, exhaust valve plate]

Referring to Figure 15, Figure 20 and Figure 21, the upper bearing 331 is provided with an exhaust hole 335, the compressed gas in the upper compression chamber flows into the upper bearing exhaust hole 335 through the exhaust hole of the upper cylinder 321, and then is discharged. The upper bearing 331 is provided with a lift limiter 333 and an exhaust valve plate 334, the exhaust valve plate 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 exhaust valve plate 334 displacement.

The upper bearing 331 is provided with a mounting groove, the lift limiter 333 is a sheet structure, and one end of the lift limiter 333 and the exhaust valve plate 334 is fixed in the mounting groove by bolts. When exhausting, the exhaust valve plate 334 is opened under the momentum of the compressed gas, and the compressed gas is discharged. After exhausting, the exhaust valve plate 334 automatically resets.

In the application process of the compressor, it often happens that the circuit is reversed and the compressor is reversed. The entire pump body is in a vacuum state. The pump body will quickly generate high temperature under the vacuum state, which will cause wear. If the parts are severely worn, the compression will occur. Chances of jamming and failure will occur, and continuous high temperature will also demagnetize the motor and melt some plastic parts.

In some embodiments, the present application makes the lift limiter 333 and the exhaust valve plate 334 made of magnetic materials. When the temperature in the compression chamber reaches the upper limit, the lift limiter 333 and the exhaust valve plate 334 respectively generate magnetism to attract each other, the exhaust valve plate 334 is adsorbed by the lift limiter 333, and the exhaust valve plate 334 is far away from the exhaust hole 335 to open the exhaust hole 335. At this time, the exhaust channel of the compression chamber Connected, the compressor is no longer in a vacuum state, the temperature will not continue to rise, avoiding damage to the compressor, and improving the operating reliability of the compressor.

The magnetic material has the characteristic of being magnetic as the temperature rises. When the temperature rises to a certain temperature, the lift limiter 333 and the exhaust valve plate 334 generate magnetism, and the two attract each other to open the exhaust hole 335. the goal of. When the temperature drops to a certain temperature, the lift limiter 333 and the magnetism on the exhaust valve plate 334 disappear, and the exhaust valve plate 334 resets and returns to a normal working state.

The magnetic material is a well-known material in the prior art, and the specific principles can be referred to the existing literature, which will not be elaborated herein.

In some embodiments, a temperature sensor (not shown) is provided on the air inlet pipe 500 of the compressor, and the temperature sensor is arranged close to the casing 100 of the compressor. The temperature sensor is used to detect the air inlet temperature of the compressor. Stop working when the difference between the temperature measured by the temperature sensor and the ambient temperature is greater than the set value, so as to avoid aggravating the wear of the compression mechanism due to high temperature and improve the operation reliability of the compressor.

The purpose of reverse rotation protection is achieved by detecting the temperature at the air inlet.

The distance between the temperature sensor and the casing 100 of the compressor is 5-10 mm, so as to improve the reliability of temperature detection.

In some embodiments, a thermal protector (not shown) is provided on the air inlet pipe 500 of the compressor, and the heat sensitive protector is arranged close to the casing 100 of the compressor, and the air inlet pipe 500 is made of metal with thermal conductivity, Such as copper.

When the compressor is reversed, the exhaust valve is closed and no high-pressure gas is discharged. Therefore, the temperature near the upper shell of the casing is relatively high, and the temperature sensor on it cannot sense abnormal temperature, which cannot protect in time. damage to the compressor. By setting the thermal protector, when the temperature of the cylinder rises, the heat is transferred to the thermal protector through the copper intake pipe 500, and the thermal protector cuts off the power supply to play a protective role and improve the reliability of the compressor. sex.

[rotor, balance weight]

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

The top of the rotor 220 is provided with an upper balance weight 700 , and the bottom is provided with a lower balance weight 800 .

Figures 8 to 11 show the upper balance weight 700 with different structural deformations. The upper balance weight 700 is a ring structure, and the upper surface of the ring structure has a plurality of protrusions 711 arranged at intervals, and two adjacent protrusions 711 An air flow channel 712 for refrigerant circulation is formed therebetween.

The top of the upper balance weight 700 is provided with an oil deflector 600, and the oil deflector 600 is located directly above the through hole 221, that is, referring to FIG. At the same time, the top opening of the airflow channel 712 is covered.

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 retaining part 600 and cannot continue to flow upward. On the one hand, the air flow channel 712 helps to improve the sufficient separation of the refrigerant and the oil, and reduces the oil discharge rate of the compressor; The backflow speed is high, and the oil in the oil pool at the bottom of the compressor is kept sufficient, thereby ensuring the lubrication effect and operation reliability of the compressor.

In some embodiments, the extending direction of the airflow channel 712 is the same as the rotation direction of the rotor 220. At this time, the airflow 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.

In some embodiments, referring to FIG. 8 , the ring structure includes two oppositely arranged first half-ring structures 710 and second half-ring structures 720, the two half-ring structures form a ring structure, the first half-ring structure 710 and the second half-ring structure The second half-ring structure 720 is an integral structure, and a plurality of protrusions 711 are disposed on the upper surface of the first half-ring structure 710 , and the offset arrangement of the plurality of protrusions 711 acts as a top balance weight.

At least one protrusion 711 is provided with a first installation hole 713, and the second half-ring structure 720 is provided with a first installation column 721, and the oil deflector 600 is fixedly installed to the first installation hole 713 through a connecting piece (such as a screw). , The first installation column 721 realizes the fixed installation of the oil deflector 600 on the top of the upper balance weight 700 .

Referring to FIG. 12 for the structure of the oil deflector 600 , it is a disc-shaped structure. The outer diameter of the oil deflector 600 is the same as that of the rotor 220 . The oil deflector 600 is provided with a screw hole 610 through which the above-mentioned connectors pass.

The lower balance weight 800 faces the second half-ring structure 720 , and the upper balance structure formed by a plurality of protrusions 711 is staggered with the lower balance weight 800 to realize the balance effect on the rotor 220 .

For the fixed installation structure between the upper balance weight 700, the lower balance weight 800, and the rotor 220, in some embodiments, referring to FIG. The installation hole 714 is located in the airflow channel 712, the second half-ring structure 720 is provided with a third installation hole 722, the first rivet 910 passes through the second installation hole 714 and the rotor 220, and the second rivet 920 passes through the third installation hole 722 , the rotor 220, and the lower balance weight 800, thereby realizing the fixed installation between the upper balance weight 700, the lower balance weight 800, and the rotor 220.

The height h1 of the first half-ring structure 10 is greater than the height h2 of the second half-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 a material number and facilitate assembly .

For the fixed installation structure between the upper balance weight 700, the lower balance weight 800, and the rotor 220, in other embodiments, referring to FIG. The structure 720 is provided with a third mounting hole 722, the first rivet 910 passes through the second mounting column 715, the first half-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, so as to realize the fixed installation between the upper balance weight 700, the lower balance weight 800, and the rotor 220.

The setting of the second mounting column 715 is also to make the length of the first rivet 910 equal to the length of the second rivet 920, so that multiple rivets can be unified into a material number, which is convenient for assembly.

There is a gap for refrigerant circulation between the second mounting column 715 and the vertical side wall of the protruding portion 711 so as not to affect the normal circulation of the refrigerant.

Corresponding to the arrangement of the protrusions, in a specific embodiment, referring to FIG. 8, there are four protrusions 711, including two symmetrically arranged first protrusions 7111 and two symmetrically arranged second protrusions 7112. , the two second raised parts 7112 are arranged between the two first raised parts 7111, three air flow passages 712 are formed between the four raised parts 711, the two second raised parts 7112 are provided with first The mounting holes 713 and the second semi-ring structure 720 are provided with two first mounting columns 721 . Correspondingly, referring to FIG. 12 , the oil retaining part 600 is provided with four screw holes 610 to realize reliable installation of the oil retaining part 600 .

In some embodiments, a groove 716 is provided on the upper surface of the protruding portion 711 without the first installation hole 713 , and a channel for refrigerant circulation is defined between the groove 716 and the oil retaining portion 600 .

For example, referring to FIG. 9, the two second protrusions 7112 in the middle are provided with first installation holes 713, and the top surfaces of the two second protrusions 7112 are in contact with the oil deflector 600. The upper surface of the raised part 7111 is provided with a groove 716, and a channel for refrigerant circulation is defined between the groove 716 and the oil retaining part 600, which increases the circulation path of the refrigerant, further improves the oil return efficiency, and improves the interaction between the refrigerant and the oil. seperate effect.

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

In some embodiments, the groove 716 is configured as an arc-shaped groove structure, and the arc-shaped 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 further Improve the gas-liquid separation effect and oil return speed.

In the description of the above embodiments, specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in an appropriate manner.

The above is only a 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 imagined by those skilled in the art within the technical scope disclosed in the present invention shall be covered. Within the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims (10)

1. A twin-cylinder rotary compressor, comprising: Compression mechanism, which is used to compress 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, and the lower compression chamber is composed of a lower cylinder, a lower Composed of a piston and a lower bearing, a middle baffle assembly is arranged between the upper compression chamber and the lower compression chamber; It is characterized in that the middle partition assembly includes: a middle partition body, which is arranged between the upper cylinder and the lower cylinder to separate the upper compression chamber from the lower compression chamber; There are two disks, which are respectively arranged on the upper side and the lower side of the middle partition body; The elastic member is arranged between the disc and the middle partition body, and the elastic member applies force to the disc so that the upper disc is always in contact with the upper piston. The lower disc is always in contact with the lower piston. 2. The twin-cylinder rotary compressor according to claim 1, characterized in that, The upper side of the middle partition body is provided with an upper groove, and an upper disk is arranged in the upper groove, and an upper elastic member is arranged between the upper disk and the bottom wall of the upper groove, so that The upper elastic member exerts an upward movement force on the upper disc, so that the upper disc is always in contact with the upper piston; The lower side of the middle partition body is provided with a lower groove, and a lower disk is arranged in the lower groove, and a lower elastic member is arranged between the lower disk and the top wall of the lower groove, so that The lower elastic member exerts a downward movement force on the lower disk, so that the lower disk is always in contact with the lower piston. 3. The twin-cylinder rotary compressor according to claim 2, characterized in that, The diameter of the upper disk is not larger than the inner diameter of the upper cylinder, and the diameter of the lower disk is not larger than the inner diameter of the lower cylinder. 4. The twin-cylinder rotary compressor according to claim 2, characterized in that, The bottom wall of the upper groove is provided with a plurality of upper installation grooves arranged at intervals along its circumference, and the upper elastic member is arranged in the upper installation groove; The bottom wall of the lower groove is provided with a plurality of lower installation grooves arranged at intervals along its circumferential direction, and the lower elastic member is arranged in the lower installation grooves. 5. The two-cylinder rotary compressor according to any one of claims 1 to 4, characterized in that, The compressor also includes a motor, the motor includes a stator and a rotor arranged inside the stator, the rotor is connected to the eccentric crankshaft in the compression mechanism, the motor is arranged above the compression mechanism, the The rotor is provided with a through hole extending along its axial direction, and the refrigerant compressed by the compression mechanism flows upward through the through hole; The top of the rotor is provided with an upper balance weight, the upper balance weight is a ring structure, and the upper surface of the ring structure has a plurality of protrusions arranged at intervals, and a gap is formed between two adjacent protrusions. Airflow channels for refrigerant circulation; The top of the upper balance weight is provided with an oil deflector, and the oil deflector is located directly above the through hole and covers the top opening of the airflow channel. 6. The twin-cylinder rotary compressor according to claim 5, characterized in that, The annular structure includes two oppositely arranged first half-ring structures and second half-ring structures, and a plurality of protrusions are arranged on the upper surface of the first half-ring structure; At least one of the protrusions is provided with a first installation hole, the second half-ring structure is provided with a first installation column, and the oil deflector is fixedly installed to the first installation hole and the first installation hole through a connecting piece. Describe the first mounting column. 7. The twin-cylinder rotary compressor according to claim 6, characterized in that, The bottom of the rotor is provided with a lower balance weight, and the lower balance weight is facing the second half-ring structure; A first rivet is passed between the first half-ring structure and the rotor, and a second rivet is passed between the second half-ring structure, the rotor, and the lower balance weight. 8. The twin-cylinder rotary compressor according to claim 5, characterized in that, A groove is provided on the upper surface of the raised portion, and a channel for refrigerant circulation is defined between the groove and the oil retaining portion. 9. The twin-cylinder rotary compressor according to claim 5, characterized in that, The extending direction of the airflow channel is the same as the rotating direction of the rotor. 10. An air conditioner, characterized by comprising the twin-cylinder rotary compressor according to any one of claims 1-9.

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