CN219754813U - Double-cylinder compressor and air conditioner - Google Patents

Abstract

The utility model discloses a double-cylinder compressor and an air conditioner, wherein a compression mechanism is arranged in an inner cavity of the compressor, the compression mechanism comprises an upper cylinder, a lower cylinder, an upper bearing, a lower bearing and an eccentric crankshaft, the eccentric crankshaft passes through the upper cylinder and the lower cylinder, the upper bearing is arranged on an upper eccentric shaft section of the eccentric crankshaft, the lower bearing is arranged on a lower eccentric shaft section of the eccentric crankshaft, an upper exhaust port communicated with a compression cavity of the upper cylinder is arranged on the upper bearing, a lower exhaust port communicated with a compression cavity of the lower cylinder is arranged on the lower bearing, an upper exhaust valve plate is fixed on the upper bearing and used for opening and closing the upper exhaust port, the lower exhaust valve plate is fixed on the lower bearing and used for opening and closing the lower exhaust port, the thicknesses of the upper exhaust valve plate and the lower exhaust valve plate are different, so that when the compressor operates at different frequencies, one exhaust valve plate can be effectively opened all the time, the phenomena of incapable of closing, chattering and the like are reduced, and the effective operation interval of the exhaust valve plate is increased.

Description

Double-cylinder compressor and air conditioner

Technical Field

The utility model relates to the technical field of air conditioners, in particular to a double-cylinder compressor and an air conditioner.

Background

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 refrigerating and heating cycle includes a series of processes involving compression, condensation, expansion and evaporation, and refrigerating or heating an indoor space.

The low-temperature low-pressure refrigerant enters the compressor, the compressor compresses the refrigerant gas into a high-temperature high-pressure state, and the compressed refrigerant gas is discharged. 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.

The rolling rotor compressor is widely applied to air conditioners nowadays, and the working principle of the existing rolling rotor compressor is as follows: the motor stator generates magnetic pulling force after being electrified, the motor rotor rotates under the action of the magnetic pulling force of the stator and drives the eccentric crankshaft of the compression mechanism to rotate together, the eccentric crankshaft rotates to drive the piston sleeved on the eccentric part of the eccentric crankshaft to do eccentric circular motion in the cylinder, the sliding vane is arranged in the sliding vane groove of the cylinder, the piston is always propped against the action of the compression spring in the spring hole to do reciprocating motion in the sliding vane groove, the sliding vane and the piston divide the cylinder into a high-pressure cavity and a low-pressure cavity, and the eccentric crankshaft drives the piston to rotate for one circle to suck air from the low-pressure cavity and exhaust air from the high-pressure cavity to complete one-time exhaust, so that the compression of the compressor to air is realized. An exhaust valve plate and a lift limiter are arranged at an exhaust port of the cylinder. When the cylinder is exhausted, the air flow pushes the exhaust valve plate open, and the lift limiter is used for limiting the opening angle of the exhaust valve plate. When the cylinder is not exhausted, the exhaust valve plate falls down to seal the exhaust port.

Under the trend of cost reduction and miniaturization of the existing compressor, the operation frequency range of the compressor is increased. Under the condition of no lift limiter, after the thickness, width and effective length of the exhaust valve plate are determined, the rigidity of the valve plate is increased along with the lift height, and the valve plate rigidity value is constant.

Therefore, in order to effectively increase the operation interval of the exhaust valve plate on the premise of not increasing the cost of the exhaust valve plate, on one hand, the low-frequency effective opening of the exhaust valve plate needs to be ensured, and the condition of continuously beating the lift limiter, the bearing surface or the flutter does not occur; on the other hand, the delay closing can be effectively reduced when the exhaust valve plate runs at high frequency.

The exhaust valve plate of the existing double-cylinder compressor cannot be effectively opened when low frequency exists, and the exhaust valve plate of the existing double-cylinder compressor is an industrial pain point which is closed by high frequency delay.

The above information disclosed in this background section is only for enhancement of understanding of the background section of the utility model and therefore it may not form the prior art that is already known to those of ordinary skill in the art.

Disclosure of Invention

Aiming at the problems pointed out in the background art, the utility model provides a double-cylinder compressor and an air conditioner, wherein the thicknesses of an upper exhaust valve plate and a lower exhaust valve plate are different, so that when the compressor operates at different frequencies, one exhaust valve plate can be effectively opened all the time, the phenomena of incapability of closing, flutter and the like are reduced, and the effective operation interval of the exhaust valve plates is increased.

In order to achieve the aim of the utility model, the utility model is realized by adopting the following technical scheme:

in some embodiments of the present utility model, a dual-cylinder compressor is provided, wherein a compression mechanism for compressing refrigerant is arranged in an inner cavity of the dual-cylinder compressor, the compression mechanism comprises an upper cylinder, a lower cylinder, an upper bearing, a lower bearing and an eccentric crankshaft, the eccentric crankshaft passes through the upper cylinder and the lower cylinder, the upper bearing is arranged on an upper eccentric shaft section of the eccentric crankshaft, the lower bearing is arranged on a lower eccentric shaft section of the eccentric crankshaft, an upper exhaust port communicated with a compression cavity of the upper cylinder is arranged on the upper bearing, and a lower exhaust port communicated with a compression cavity of the lower cylinder is arranged on the lower bearing;

an upper exhaust valve plate fixedly mounted to the upper bearing for opening and closing the upper exhaust port;

a lower exhaust valve plate fixedly installed to the lower bearing for opening and closing the lower exhaust port;

the thickness of the upper exhaust valve plate is different from that of the lower exhaust valve plate.

The thicknesses of the upper exhaust valve plate and the lower exhaust valve plate are different, so that when the compressor operates at different frequencies, one exhaust valve plate can be effectively opened all the time, the phenomena of incapability of closing, flutter and the like are reduced, and the effective operation interval of the exhaust valve plate is increased.

In some embodiments of the present utility model, the thickness of the upper exhaust valve plate is d1, and the thickness of the lower exhaust valve plate is d2, d1=1.5d2, or d2=1.5d1.

In some embodiments of the present utility model, the lift limiter includes an upper lift limiter and a lower lift limiter, the upper lift limiter is disposed on the upper bearing and is used for limiting the lift of the upper exhaust valve plate, and the lower lift limiter is disposed on the lower bearing and is used for limiting the lift of the lower exhaust valve plate;

the lift limiter includes:

a straight section fixedly mounted to a first end of the upper or lower discharge valve plate;

a curved section connected to the straight section and extending obliquely toward a side away from the upper discharge valve plate or the lower discharge valve plate;

and the elastic reed is connected with the bending section and extends obliquely towards one side far away from the upper exhaust valve plate or the lower exhaust valve plate.

In some embodiments of the present utility model, the first end of the elastic reed is connected to one end of the curved section, the first end of the elastic reed is attached to a side surface of the curved section facing the upper exhaust port or the lower exhaust port, and the second end of the elastic reed extends obliquely in a direction away from the curved section and away from the upper exhaust port or the lower exhaust port.

In some embodiments of the present utility model, the curved section is provided with a groove on a side facing the upper exhaust valve plate or the lower exhaust valve plate, the first end of the elastic reed is disposed in the groove, and a portion of the elastic reed located in the groove is located on the same curved surface as the curved section.

In some embodiments of the present utility model, two opposite side walls of the curved section are respectively provided with a mounting groove, and the two mounting grooves are respectively arranged at two sides of the groove;

two connecting parts which are oppositely arranged are arranged at the first end of the elastic reed, and the connecting parts are arranged in the mounting groove.

In some embodiments of the present utility model, the lift limiter includes an upper lift limiter and a lower lift limiter, the upper lift limiter is disposed on the upper bearing and is used for limiting the lift of the upper exhaust valve plate, and the lower lift limiter is disposed on the lower bearing and is used for limiting the lift of the lower exhaust valve plate;

the lift limiter includes:

a straight section fixedly mounted to a first end of the upper or lower discharge valve plate;

a first curved section connected to the straight section and extending obliquely toward a side away from the upper discharge valve plate or the lower discharge valve plate;

the second bending section is connected with the first bending section and extends obliquely towards one side away from the upper exhaust valve plate or the lower exhaust valve plate;

the radius of curvature of the first curved section is greater than the radius of curvature of the second curved section.

In some embodiments of the present utility model, the first curved section has a radius of curvature R1, and the second curved section has a radius of curvature R2, r1= (1.3-1.5) R2.

In some embodiments of the utility model, the width of the straight section is greater than the width of the first curved section, and the width of the second curved section is greater than the width of the first curved section.

The utility model also provides an air conditioner comprising the double-cylinder compressor.

Other features and advantages of the present utility model will become apparent upon review of the detailed description of the utility model in conjunction with the drawings.

Drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions of the prior art, the drawings that are needed in the embodiments or the description of the prior art will be briefly described below, it will be obvious that the drawings in the following description are some embodiments of the present utility model, and that other drawings can be obtained according to these drawings without inventive effort to a person skilled in the art.

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

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

FIG. 3 is a schematic structural view of a compression mechanism according to an embodiment;

FIG. 4 is a cross-sectional view of a compression mechanism according to an embodiment;

FIG. 5 is a schematic view of a lift limiter according to a first embodiment;

FIG. 6 is a side view of a lift limiter according to a first embodiment;

FIG. 7 is an exploded view of a lift limiter according to a first embodiment;

FIG. 8 is a top view of the structure shown in FIG. 7;

FIG. 9 is a schematic view of a lift limiter according to a second embodiment;

FIG. 10 is a side view of a lift limiter according to a second embodiment;

FIG. 11 is a top view of a lift limiter according to a second embodiment;

FIG. 12 is a schematic structural view of an exhaust valve sheet according to an embodiment;

FIG. 13 is a top view of an exhaust valve sheet according to an embodiment;

reference numerals:

100-a housing;

200-motor, 210-stator, 220-rotor;

300-compression mechanism;

310-eccentric crankshafts, 311-main shaft sections, 312-upper eccentric shaft sections, 313-connecting shaft sections, 314-lower eccentric shaft sections, 315-auxiliary shaft sections;

320-cylinder, 321-upper cylinder and 322-lower cylinder;

330-bearing, 331-upper bearing, 332-lower bearing;

340-a septum assembly;

351-upper muffler, 352-lower muffler;

361-upper piston, 362-lower piston;

400-exhaust pipe;

500-air inlet pipe;

600-exhaust valve block, 610-first end of exhaust valve block, 620-second end of exhaust valve block, 630-first mounting hole, 641-first exhaust valve block section, 642-second exhaust valve block section, 643-third exhaust valve block section, 651-upper exhaust valve block, 652-lower exhaust valve block;

700-lift limiter, 710-straight section, 711-second mounting hole, 720-curved section, 721-groove, 722-mounting slot, 723-cambered surface, 724-inclined surface, 730-spring reed, 731-spring reed first section, 732-spring reed second section, 733-connecting portion, 734-spring reed first end, 735-spring reed second end, 740-second curved section, 750-second curved section, 761-first inclined surface, 762-second inclined surface;

w1-width of straight section;

w2-width of the curved section;

w3-width of one section of the elastic reed;

w4-width of the first curved section;

w5-the width of the second curved section;

d-the outer diameter of the second section of the elastic reed;

l1-length of straight section;

l2-length of the curved section;

l3-length of spring reed.

Description of the embodiments

The following description of the embodiments of the present utility model will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

In the description of the present utility model, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate describing the present utility model and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model.

The terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present utility model, unless otherwise indicated, the meaning of "a plurality" is two or more.

In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model will be understood in specific cases by those of ordinary skill in the art.

In the present utility model, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.

The following disclosure provides many different embodiments, or examples, for implementing different features of the utility model. In order to simplify the present disclosure, components and arrangements of specific examples are described below. They are, of course, merely examples and are not intended to limit the utility model. Furthermore, the present utility model may repeat reference numerals and/or letters in the various examples, which are for the purpose of brevity and clarity, and which do not themselves indicate the relationship between the various embodiments and/or arrangements discussed. In addition, the present utility model provides examples of various specific processes and materials, but one of ordinary skill in the art will recognize the application of other processes and/or the use of other materials.

The following is an illustration of an air conditioner.

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

The low-temperature low-pressure refrigerant enters the compressor, the compressor compresses the refrigerant gas into a high-temperature high-pressure state, and the compressed refrigerant gas is discharged. 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.

The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state 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 may achieve a cooling effect by exchanging heat with a material to be cooled using latent heat of evaporation of a refrigerant. The air conditioner may adjust the temperature of the indoor space throughout the cycle.

An outdoor unit of an air conditioner refers to a portion of a refrigeration cycle including a compressor and an outdoor heat exchanger, an 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 function as a condenser or an evaporator. 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.

The mode of converting the indoor heat exchanger and the outdoor heat exchanger into a condenser or an evaporator generally adopts a four-way valve, and the arrangement of a conventional air conditioner is specifically referred to and will not be described herein.

The refrigeration working principle of the air conditioner is as follows: the compressor works to enable the interior of an indoor heat exchanger (in an indoor unit, an evaporator at the moment) to be in an ultralow pressure state, liquid refrigerant in the indoor heat exchanger is rapidly evaporated to absorb heat, air blown out by an indoor fan is cooled by an indoor heat exchanger coil and then changed into cold air to be blown into the indoor, the evaporated refrigerant is pressurized by the compressor and then condensed into liquid state in a high-pressure environment in an outdoor heat exchanger (in an outdoor unit, a condenser at the moment), heat is released, the heat is emitted to the atmosphere by the outdoor fan, and the refrigerating effect is achieved through circulation.

The heating working principle of the air conditioner is as follows: the gaseous refrigerant is pressurized by the compressor to become high-temperature high-pressure gas, and enters the indoor heat exchanger (a condenser at the moment), so that the gaseous refrigerant is condensed, liquefied and released heat to become liquid, and meanwhile, the indoor air is heated, so that the aim of improving the indoor temperature is fulfilled. The liquid refrigerant is decompressed by the throttling device, enters the outdoor heat exchanger (an evaporator at the moment), evaporates, gasifies and absorbs heat to become gas, and simultaneously absorbs heat of outdoor air (the outdoor air becomes colder) to become gaseous refrigerant, and enters the compressor again to start the next cycle.

The following is an illustration of the compressor.

The compressor in this embodiment is a rolling rotor type double-cylinder compressor, referring to fig. 1 and 2, which includes a housing 100, a closed inner cavity is formed in the housing 100, a motor 200 and a compression mechanism 300 are disposed in the inner cavity, the motor 200 provides power for the compressor mechanism 300, the compression mechanism 300 is used for compressing refrigerant, and the motor 200 is disposed 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, and the stator 210 is fixedly connected with the inner wall of the housing 100, so as to realize the fixed installation of the motor 200 in the inner cavity of the compressor.

Compression mechanism 300 includes an eccentric crankshaft 310, cylinders, pistons, and bearings.

The eccentric crankshaft 310 comprises a main shaft section, an eccentric shaft section and a secondary shaft section, wherein the main shaft section is fixedly connected with the rotor; with reference to fig. 2, a piston is arranged in the compression cavity of the cylinder and sleeved on the eccentric shaft section; the bearing is fixedly connected with the air cylinder, a bearing exhaust hole is formed in the bearing, and the bearing exhaust hole is communicated with the compression cavity; the cylinder is provided with a sliding vane groove, a sliding vane is arranged in the sliding vane groove, the eccentric crankshaft drives the piston to do circumferential motion in the compression cavity, the sliding vane reciprocates along the sliding vane groove, the sliding vane is always abutted against the piston, and the sliding vane and the piston divide the compression cavity into a high-pressure cavity and a low-pressure cavity.

The working principle of the compressor is as follows: the stator 210 of the motor generates magnetic pulling force after being electrified, the rotor 220 of the motor rotates under the action of the magnetic pulling force of the stator and drives the eccentric crankshaft 310 to rotate together, the eccentric crankshaft 310 rotates to drive the piston sleeved on the eccentric shaft section of the eccentric crankshaft to do eccentric circular motion in the compression cavity of the cylinder, the sliding vane reciprocates in the sliding vane groove, the sliding vane and the piston divide the compression cavity of the cylinder into a high-pressure cavity and a low-pressure cavity, the eccentric crankshaft 310 drives the piston to rotate for one circle, then air is sucked from the low-pressure cavity to exhaust from the high-pressure cavity to complete one-time exhaust, the compression of the compressor to the air is realized, and the compressed air is exhausted through the bearing exhaust hole.

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

Referring to fig. 3 to 4, the compression mechanism 300 specifically includes an eccentric crankshaft 310, two cylinders (upper cylinder 321 and lower cylinder 322, respectively), two bearings (upper bearing 331 and lower bearing 332, respectively), two pistons (upper piston 361 and lower piston 362, respectively), and a middle spacer assembly 340.

The eccentric crankshaft 310 sequentially comprises 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, an upper piston 361 capable of eccentric movement is arranged in a compression cavity 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 performing eccentric motion is arranged in the compression cavity 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 positioned between the upper air cylinder 321 and the lower air cylinder 322; the upper bearing 331 is sleeved on the main shaft section 311 and is connected with the upper cylinder 321; the lower bearing 332 is sleeved on the auxiliary shaft section 315 and is simultaneously connected with the lower cylinder 322.

The upper eccentric shaft section 312 and the lower eccentric shaft section 314 are arranged at 180 ° relative angles, the upper piston 361 and the lower piston 362 simultaneously perform eccentric rotation, compressed air in the compression chamber of the upper cylinder 321 is discharged through the exhaust hole on the upper bearing 331, and compressed air 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 silencer 351, the upper silencer 351 covers the exhaust hole of the upper bearing 331, compressed air in the upper cylinder 321 is firstly discharged into a space surrounded by the upper silencer 351 and the upper bearing 331 through the exhaust hole of the upper bearing 331, and then is discharged into the inner cavity of the compressor through an upper silencer exhaust hole 3511.

The lower muffler 352 is arranged on the lower bearing 332, the lower muffler 352 covers the exhaust hole of the lower bearing 332, and the compressed air in the lower cylinder 322 is firstly discharged into the space surrounded by the lower muffler 352 and the lower bearing 332 through the exhaust hole on the lower bearing 332.

In contrast, the lower muffler 352 has no exhaust hole, 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 penetrating up and down, and the compressed air in the lower bearing 332 and the lower muffler 352 is 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 holes of the upper muffler.

The upper bearing 331 is provided with an upper exhaust port, which is communicated with the compression chamber of the upper cylinder 321. The upper bearing 331 is further provided with an upper exhaust valve plate and an upper lift limiter, the upper exhaust valve plate moves to open and close the upper exhaust port, and the upper lift limiter is used for limiting the lift of the upper exhaust valve plate.

The lower bearing 332 is provided with a lower exhaust port, which communicates with the compression chamber of the lower cylinder 322. The lower bearing 332 is further provided with a lower exhaust valve plate and a lower lift limiter, wherein the lower exhaust valve plate moves to open and close the lower exhaust port, and the lower lift limiter is used for limiting the lift of the lower exhaust valve plate.

The following is an explanation of the upper and lower discharge valve plates.

The upper exhaust valve plate 651 is fixedly mounted to the upper bearing 331 for opening and closing the upper exhaust port. A lower exhaust valve plate 652 is fixedly installed to the lower bearing 332 for opening and closing the lower exhaust port.

The thickness of the upper and lower discharge valve plates 651 and 652 is different, and it may be that the thickness of the upper discharge valve plate 651 is greater than the thickness of the lower discharge valve plate 652 or that the thickness of the upper discharge valve plate 651 is less than the thickness of the lower discharge valve plate 652.

The thicknesses of the upper exhaust valve plate and the lower exhaust valve plate are different, so that when the compressor operates at different frequencies, one exhaust valve plate can be effectively opened all the time, the phenomena of incapability of closing, flutter and the like are reduced, and the effective operation interval of the exhaust valve plate is increased.

In some embodiments of the present utility model, the thickness of the upper exhaust valve plate 651 is d1, the thickness of the lower exhaust valve plate 652 is d2, d1=1.5d2, or d2=1.5d1, so that the upper and lower exhaust valve plates reach the optimal effective operation interval.

In some embodiments of the present utility model, the upper exhaust valve plate 651 and the lower exhaust valve plate 652 are both flat when closed, so as to achieve a more reliable sealing effect on the exhaust port.

The following is a description of the lift limiter.

For convenience of description, hereinafter, the upper lift limiter and the lower lift limiter are collectively referred to as lift limiter 700, the upper exhaust valve plate and the lower exhaust valve plate are collectively referred to as exhaust valve plate 600, the upper exhaust port and the lower exhaust port are collectively referred to as exhaust ports, the upper bearing 331 and the lower bearing 332 are collectively referred to as bearings 330, the upper cylinder 321 and the lower cylinder 322 are collectively referred to as cylinder 320, and the upper exhaust valve plate 651 and the lower exhaust valve plate 652 are collectively referred to as exhaust valve plate 600.

The structure of the discharge valve sheet 600 is shown in fig. 12 and 13, and the discharge valve sheet 600 has a first end 610 and a second end 620. The first end 610 of the air discharge valve plate is provided with a first mounting hole 630, and the first end 610 of the air discharge valve plate is fixedly mounted on the bearing 330 through a connecting piece such as a bolt. The second end 620 of the discharge valve plate moves in a direction away from the discharge port to open the discharge port, and the second end 620 of the discharge valve plate moves in a direction close to the discharge port to close the discharge port.

The lift limiter 700 is disposed at a side of the discharge valve plate 600 facing away from the exhaust port, for limiting the lift of the discharge valve plate 600.

The present utility model provides two embodiments of lift limiters.

A first embodiment of the lift limiter 700 is shown in fig. 5 to 8, the lift limiter 700 includes a straight section 710, a curved section 720, and a spring reed 730 connected in sequence.

The straight section 710 is fixedly mounted to the first end 610 of the exhaust valve plate, specifically, a second mounting hole 711 is formed in the straight section 710, the second mounting hole 711 is opposite to the first mounting hole 630 of the exhaust valve plate 600 from top to bottom, and the second mounting hole 711 and the first mounting hole 630 are fixedly mounted to the bearing 330 through a connecting piece such as a same bolt.

The curved section 720 is connected to the straight section 710 and extends obliquely toward a side away from the discharge valve plate 600.

The elastic reed 730 is connected to the bent section 720, and the elastic reed 730 is inclined to extend toward a side away from the discharge valve plate 600.

During exhaust, the second end 620 of the exhaust valve plate moves towards the direction away from the exhaust port, when the exhaust valve plate 600 lifts to the maximum height, the exhaust valve plate 600 contacts with the elastic reed 730, the exhaust valve plate 600 is acted by airflow thrust to push the elastic reed 700, so that the impact speed of the exhaust valve plate 600 is effectively reduced, the impact stress is reduced, meanwhile, the kinetic energy of the exhaust valve plate 600 is converted into the elastic potential energy of the elastic reed 700, and after the airflow thrust is reduced, the exhaust valve plate 600 can obtain a larger acceleration, and the exhaust valve plate 600 can quickly rebound to be closed.

According to the lift limiter 700, the elastic reed 730 is arranged, so that the pushing action of the elastic reed 730 on the exhaust valve plate 600 can be utilized, the operation interval of the exhaust valve plate 600 can be effectively increased on the premise of not increasing the cost of the exhaust valve plate, on one hand, the exhaust valve plate 600 can be effectively opened at low frequency, and the condition of continuously beating the lift limiter, the bearing surface or flutter does not occur; on the other hand, it is also possible to ensure that the discharge valve plate 600 can effectively reduce the delayed closing at the time of high frequency operation.

In some embodiments of the present utility model, the straight section 710 and the curved section 720 are integrally formed, the first end 734 of the elastic reed 730 is connected to one end of the curved section 720, the first end 734 of the elastic reed is attached to a side of the curved section 720 facing the exhaust port, and the second end 735 of the elastic reed extends obliquely in a direction away from the curved section 720 and away from the exhaust port.

Taking the orientation shown in fig. 6 as an example, during exhausting, the exhaust valve plate 600 is opened upwards at the bottom side of the lift limiter 700, and the elastic reed 730 is arranged at the bottom side of the bending section 720, so that the exhaust valve plate 600 can well contact with the bending section 720 and the elastic reed 730, and kinetic energy of the exhaust valve plate 600 is more efficiently converted into elastic potential energy of the elastic reed 720.

In some embodiments of the present utility model, referring to fig. 7, the curved section 720 is provided with a groove 721 on the side facing the exhaust valve plate 600, the first end 734 of the elastic reed is disposed in the groove 721, and the portion of the elastic reed 730 located in the groove 721 is located on the same curved surface as the curved section 720, so that the elastic reed 730 and the curved section 720 can smoothly transition and be better attached to the exhaust valve plate 600.

In some embodiments of the present utility model, referring to fig. 7, mounting grooves 722 are respectively formed on two opposite sidewalls of the curved section 720, and the two mounting grooves 722 are respectively formed on two sides of the groove 721.

The first end 734 of the elastic reed is provided with two connecting parts 733 which are oppositely arranged, and the connecting parts 733 are fixedly arranged in the mounting groove 722.

The elastic reed 730 is securely mounted and fixed by the recess 721 and the two mounting grooves 722.

The elastic spring 730 is pushed into the groove 721 from one end of the bending section 720, one end 734 of the elastic spring abuts against the side wall of the groove 721, and the connecting portion 733 is clamped into the corresponding mounting groove 722, so that the elastic spring 730 can be fixedly mounted and is convenient to mount.

In some embodiments of the present utility model, referring to fig. 7, the lateral end surface of the curved section 720 and the bottom surface of the groove 721 are transited by an arc 723.

During exhaust, the exhaust valve plate 600 moves towards the direction away from the exhaust port until contacting the bending section 720 and the elastic reed 730, the movement trend of the elastic reed 730 towards the direction away from the exhaust port is larger under the thrust action of the exhaust valve plate 600, and the upwarp movement of the elastic reed 730 can not be influenced through the cambered surface 723.

If the lateral end surface of the curved section 720 and the bottom surface of the groove 721 do not pass through the arc surface transition, for example, still have a sharp corner structure, the sharp corner structure herein obviously affects the upwarp motion of the elastic reed 730, so that the elastic reed 730 cannot play a role in making the exhaust valve plate 600 rebound and close in time.

In some embodiments of the present utility model, referring to FIG. 8, straight section 710 has a width W1 and curved section 720 has a width W2, W1 > W2. The straight section 710 has a length L1 and the curved section 720 has a length L2, L1 < L2. The straight section 710 and the curved section 720 are in transitional connection through a bevel 724.

The flat section 710 is mainly used for fixedly mounting the lift limiter 700 on the bearing 330, so that the length L1 of the flat section 710 is not required to be too long, which can affect the opening angle of the exhaust valve plate 600, and the width W1 of the flat section 710 is larger, so that the flat section has a better pressing effect on the exhaust valve plate 600, and is beneficial to improving the mounting reliability of the exhaust valve plate 600.

In some embodiments of the present utility model, referring to fig. 8, the elastic reed 730 includes an elastic reed first section 731 and an elastic reed second section 732 which are integrally formed, one end of the elastic reed first section 731 is connected to the curved section 720, the elastic reed first section 731 has a rectangular structure, the width W3 of the elastic reed first section 731 is the same as the width W2 of the curved section 720, and the outer diameter D of the elastic reed second section 732 is larger than the width W3 of the elastic reed first section 731.

The first elastic reed section 731 is in a flat, long strip structure, and the second elastic reed section 732 is in a flat, round or oval structure, so that the elastic reed section 731 can be well attached to the exhaust valve plate 600.

In some embodiments of the present utility model, the thickness of the air release valve 600 is t1, the thickness of the elastic spring 730 is t2, and t2= (1.3-1.7) t1.

The elastic reed 730 has moderate thickness, and can be elastically deformed under the thrust action of the exhaust valve plate 600 more reliably so as to convert the kinetic energy of the exhaust valve plate 600 into the elastic potential energy of the elastic reed 730, so that the exhaust valve plate 600 obtains a larger acceleration to realize quick rebound closing.

In some embodiments of the utility model, the lift limiter 700 has a length L and the spring reed 730 has a length L3, L/3.ltoreq.L3.ltoreq.L/2.

On the one hand, theoretically, when the exhaust valve plate 600 is opened to the slap lift limiter 700, the longer the elastic reed 730 is, the more impact force of the exhaust valve plate 600 can be effectively reduced, and elastic potential energy can be provided when the exhaust valve plate 600 rebounds; however, as the elastic reed 730 is lengthened, the lift height of the exhaust valve plate 600 may be too large due to the excessive thinness, and fatigue, impact fracture, and the like may occur. Therefore, in summary, the length of the spring reed 730 is set to a value in the range of L/3.ltoreq.L3.ltoreq.L/2.

A second embodiment of a lift limiter is shown in fig. 9-11. The lift limiter 700 includes a straight segment 710, a first curved segment 740, and a second curved segment 750 of unitary construction.

The straight section 710 is fixedly mounted to the first end 610 of the exhaust valve plate, specifically, a second mounting hole 711 is formed in the straight section 710, the second mounting hole 711 is opposite to the first mounting hole 630 of the exhaust valve plate 600 from top to bottom, and the second mounting hole 711 and the first mounting hole 630 are fixedly mounted to the bearing 330 through a connecting piece such as a same bolt.

The first curved section 740 is connected to the straight section 710 and extends obliquely toward a side away from the discharge valve plate 600. The second curved section 750 is connected to the first curved section 740 and extends obliquely toward a side away from the discharge valve plate 600.

The first curved section 740 has a radius of curvature R1, and the second curved section 750 has a radius of curvature R2, R1 > R2.

The exhaust valve plate is linearly changed before being attached to the lift limiter along with the increase of the lift height of the exhaust valve plate, namely the rigidity is constant, but the rigidity is obviously nonlinear after being attached to the lift limiter, and the rigidity is greatly improved. However, when the compressor operates at a high rotation speed, the existing lift limiter has a single curvature radius, and cannot effectively provide enough deformation, namely valve plate elasticity, for the exhaust valve plate.

Therefore, the lift limiter 700 in the present utility model is composed of two curved sections with different curvature radii, and the curvature radius R1 of the first curved section 740 is larger than the curvature radius R2 of the second curved section 750, so as to achieve low starting effective rigidity of the exhaust valve plate 600 at low frequency, reduce chatter and increase winding, and significantly increase effective rigidity when the exhaust valve plate 600 lifts to winding with the second curved section 750 at high frequency, so that the exhaust valve plate 600 has a larger elastic force, and effectively reduce delayed closing when the exhaust valve plate 600 operates at high frequency.

In some embodiments of the present utility model, r1= (1.3-1.5) R2 is set, so that the exhaust valve plate 600 can obtain the optimal technical effects of effective opening at low frequency and timely closing at high frequency.

In this embodiment, on the premise of the radius of curvature R1 of the existing lift limiter 700, on one hand, in order to effectively increase the resilience of the exhaust valve plate 600; on the other hand, considering the possibility of breakage after too much bending of the exhaust valve sheet due to too small a machining process and a radius of curvature, the relationship between the radius of curvature R of the first bending section 740 and the radius of curvature R2 of the second bending section 750 is set as follows: r1= (1.3-1.5) R2.

In some embodiments of the present utility model, the width of straight section 710 is W1, the width of first curved section 740 is W4, and the width of second curved section 750 is W5, W1 > W4, W5 > W4.

The flat section 710 is mainly used for fixedly mounting the lift limiter 700 to the bearing 330, and the wider flat section 710 can perform a better pressing action on the exhaust valve plate 600, so as to improve the mounting reliability of the exhaust valve plate 600.

The first bending section 740 is located at the middle position of the lift limiter 700, and the width of the first bending section 740 is set narrower, so that the elastic performance of the lift limiter 700 is improved, and a better elastic resetting effect on the exhaust valve plate 600 is achieved.

In some embodiments of the present utility model, the straight section 710 is transitionally connected to the first curved section 740 by the first inclined surface 761, and the first curved section 740 is transitionally connected to the second curved section 750 by the second inclined surface 762, so as to avoid the problem that the right angle connection is easy to break.

In some embodiments of the utility model, the thickness of the straight section 710, the first curved section 740, and the second curved section 750 are the same.

The constant thickness structure of each part of the lift limiter 700 facilitates the processing and production of the lift limiter 700.

In some embodiments of the present utility model, referring to fig. 12 and 13, the exhaust valve plate 600 includes a first exhaust valve plate 641, a second exhaust valve plate 642, and a third exhaust valve plate 643 connected in sequence, where the first exhaust valve plate 641 and the straight section 710 are fixedly mounted to the bearing 330 together by a connector. When the discharge vane 600 is opened, the discharge vane second section 642 is opened to contact the first curved section 740, and the discharge vane third section 643 is opened to contact the second curved section 750.

The profile of the first section 641 of the discharge vane is adapted to the profile of the straight section 710, the profile of the second section 642 of the discharge vane is adapted to the profile of the first curved section 740, and the profile of the third section 643 of the discharge vane is adapted to the profile of the second curved section 750.

When the exhaust valve plate 600 is opened, the exhaust valve plate 600 can better abut against the lift limiter 700 to obtain limiting and resilience force.

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

The foregoing is merely illustrative of the present utility model, and the present utility model is not limited thereto, and any changes or substitutions easily contemplated by those skilled in the art within the scope of the present utility model should be included in the scope of the present utility model. Therefore, the protection scope of the utility model is subject to the protection scope of the claims.

Claims (10)

1. The double-cylinder compressor is characterized in that a compression mechanism for compressing refrigerant is arranged in an inner cavity of the double-cylinder compressor, the compression mechanism comprises an upper cylinder, a lower cylinder, an upper bearing, a lower bearing and an eccentric crankshaft, the eccentric crankshaft penetrates through the upper cylinder and the lower cylinder, the upper bearing is arranged on an upper eccentric shaft section of the eccentric crankshaft, the lower bearing is arranged on a lower eccentric shaft section of the eccentric crankshaft, an upper exhaust port communicated with a compression cavity of the upper cylinder is arranged on the upper bearing, and a lower exhaust port communicated with a compression cavity of the lower cylinder is arranged on the lower bearing;

the double-cylinder compressor is characterized by further comprising:

an upper exhaust valve plate fixedly mounted to the upper bearing for opening and closing the upper exhaust port;

a lower exhaust valve plate fixedly installed to the lower bearing for opening and closing the lower exhaust port;

the thickness of the upper exhaust valve plate is different from that of the lower exhaust valve plate.

2. The twin-tub compressor as defined in claim 1, wherein,

the thickness of the upper exhaust valve plate is d1, and the thickness of the lower exhaust valve plate is d2, d1=1.5d2, or d2=1.5d1.

3. The twin-cylinder compressor as defined in claim 1 or 2, further comprising:

the lift limiter comprises an upper lift limiter and a lower lift limiter, the upper lift limiter is arranged on the upper bearing and used for limiting the lift of the upper exhaust valve plate, and the lower lift limiter is arranged on the lower bearing and used for limiting the lift of the lower exhaust valve plate;

the lift limiter includes:

a straight section fixedly mounted to a first end of the upper or lower discharge valve plate;

a curved section connected to the straight section and extending obliquely toward a side away from the upper discharge valve plate or the lower discharge valve plate;

and the elastic reed is connected with the bending section and extends obliquely towards one side far away from the upper exhaust valve plate or the lower exhaust valve plate.

4. The twin-tub compressor as defined in claim 3, wherein,

the first end of the elastic reed is connected with one end of the bending section, the first end of the elastic reed is attached to one side surface of the bending section, which faces the upper exhaust port or the lower exhaust port, and the second end of the elastic reed obliquely extends in a direction away from the bending section and away from the upper exhaust port or the lower exhaust port.

5. The twin-tub compressor as defined in claim 4, wherein,

the side face of the bending section, which faces the upper exhaust valve plate or the lower exhaust valve plate, is provided with a groove, the first end of the elastic reed is arranged in the groove, and the part of the elastic reed in the groove is positioned on the same curved surface with the bending section.

6. The twin-tub compressor as defined in claim 5, wherein,

mounting grooves are respectively formed in two opposite side walls of the bending section, and the two mounting grooves are respectively formed in two sides of the groove;

two connecting parts which are oppositely arranged are arranged at the first end of the elastic reed, and the connecting parts are arranged in the mounting groove.

7. The twin-cylinder compressor as defined in claim 1 or 2, further comprising:

the lift limiter comprises an upper lift limiter and a lower lift limiter, the upper lift limiter is arranged on the upper bearing and used for limiting the lift of the upper exhaust valve plate, and the lower lift limiter is arranged on the lower bearing and used for limiting the lift of the lower exhaust valve plate;

the lift limiter includes:

a straight section fixedly mounted to a first end of the upper or lower discharge valve plate;

a first curved section connected to the straight section and extending obliquely toward a side away from the upper discharge valve plate or the lower discharge valve plate;

the second bending section is connected with the first bending section and extends obliquely towards one side away from the upper exhaust valve plate or the lower exhaust valve plate;

the radius of curvature of the first curved section is greater than the radius of curvature of the second curved section.

8. The twin-tub compressor as defined in claim 7, wherein,

the curvature radius of the first bending section is R1, and the curvature radius of the second bending section is R2, R1= (1.3-1.5) R2.

9. The twin-tub compressor as defined in claim 7, wherein,

the width of the straight section is larger than the width of the first bending section, and the width of the second bending section is larger than the width of the first bending section.

10. An air conditioner comprising the twin-cylinder compressor according to any one of claims 1 to 9.