CN111720311A - Rotary compressors and refrigeration cycle systems - Google Patents

Abstract

The invention discloses a rotary compressor and a refrigeration cycle system. The rotary compressor includes a casing, a motor provided in the casing and having a crankshaft, and a compression mechanism disposed in the casing and driven by the crankshaft of the motor. The compression mechanism includes a cylinder with a cylinder chamber and a sliding vane groove, a piston eccentrically rotating in the cylinder chamber, a sliding vane and an elastic member. Then, the cylinder chamber is divided into a suction chamber and a compression chamber. The sliding vane includes at least three sliding vane plates stacked on the axial direction of the crankshaft. The adjacent sliding vane plates can move relatively in the reciprocating direction of the sliding vane, and the elastic The member presses the sliding piece toward the piston so that the front end portion of the sliding piece abuts on the outer peripheral surface of the piston. The rotary compressor of the present invention can reduce the gap between the sliding vane and the piston, reduce the amount of gas leaking from the high-pressure gas in the compression chamber to the low-pressure chamber, improve the performance of the compressor, and reduce the decrease in the cooling capacity of the refrigeration cycle system.

Description

Rotary compressors and refrigeration cycle systems

technical field

The invention belongs to the technical field of compressors, and in particular, relates to a sliding vane assembly, a rotary compressor and a refrigeration cycle system.

Background technique

The rotary compressor usually includes a casing, a motor assembly and a compression mechanism, wherein the sliding vane of the compression mechanism reciprocates in the sliding vane groove of the cylinder, and the rear end of the sliding vane is provided with a spring, which presses the sliding vane, so that the front end of the sliding vane is provided with a spring. The outer peripheral surface of the piston is abutted in the compression chamber.

SUMMARY OF THE INVENTION

The present invention is made based on the inventors' findings and understanding of the following facts and problems:

The inventor found through research that the deformation of the crankshaft when the compressor runs at a high speed will cause the piston to tilt, so the gap between the piston and the front end of the sliding vane increases, and the high-pressure gas in the compression chamber is easy to leak to the low-pressure chamber, which affects the performance of the compressor and refrigeration. The cooling capacity of the circulating system decreases. To this end, one aspect of the present invention proposes a rotary compressor, which can reduce the gap between the sliding vane and the piston, reduce the amount of gas leaking from the high-pressure gas in the compression chamber to the low-pressure chamber, and improve the performance of the compressor , reduce the drop in the cooling capacity of the refrigeration cycle system.

Another aspect of the present invention also provides a refrigeration cycle system.

A rotary compressor according to an embodiment of the first aspect of the present invention includes: a casing; a motor provided in the casing and having a crankshaft; and a compression mechanism provided in the casing And driven by the crankshaft of the motor, the compression mechanism has: a cylinder, which has a cylinder chamber and a sliding vane groove; a piston, which rotates eccentrically in the cylinder chamber; a sliding vane, which is in the The sliding vane can move back and forth in the groove, the front end of the sliding vane is in contact with the outer peripheral surface of the piston to divide the cylinder chamber into a suction chamber and a compression chamber, and the sliding vane is included in the crankshaft. At least three sliding vane plates stacked in the axial direction, and the adjacent sliding vane plates can move relatively in the reciprocating direction of the sliding vanes; an elastic piece, the elastic piece presses the sliding vanes toward the piston so that the front end portion of the slider is brought into contact with the outer peripheral surface of the piston.

According to the rotary compressor of the embodiment of the present invention, a sliding vane is provided in the sliding vane groove in the compression mechanism, and the sliding vane is formed by stacking at least three sliding vane plates, and the three sliding vane plates are relatively movable. The flexibility of the sliding vane is improved by the stacking of the three sliding vane plates, which can reduce the gap between the sliding vane and the piston, reduce the amount of gas leaking from the high-pressure gas in the compression chamber to the low-pressure chamber, improve the performance of the compressor, and reduce refrigeration. The drop in the cooling capacity of the circulating system.

In some embodiments, the number of the slide plates is n, and the number of the elastic pieces is n-1 pieces, where n is a natural number greater than or equal to 3, and each of the elastic pieces is connected to two adjacent slide pieces. The rear ends of the sheets are in contact with each other.

In some embodiments, the rear end of the sliding plate is provided with a concave portion, and the front end of each elastic member abuts in the concave portion of the adjacent sliding plate.

In some embodiments, the sliding vane plate includes a first sliding vane plate, a second sliding vane plate and a third sliding vane plate which are arranged adjacent to one another in an axial direction of the crankshaft, the first sliding vane plate and the rear end of the third slide plate are provided with at least one of the recesses, the rear end of the second slide plate is provided with at least two of the recesses, at least two of the second slide plate The recesses are arranged at intervals along the axial direction of the crankshaft, the elastic member includes a first elastic member and a second elastic member, and the front end of the first elastic member abuts against the recessed portion of the first sliding plate and the first elastic member. In one concave part of the second sliding plate, the front end of the second elastic member abuts in the other concave part of the second sliding plate and in the concave part of the third sliding plate.

In some embodiments, the elastic member is a spring.

In some embodiments, the slider plates are generally square plates, and a plurality of the slider plates are stacked along their widths.

In some embodiments, the widths of the plurality of said slide plates are substantially equal.

In some embodiments, in the reciprocating direction of the sliding plate, the relative moving distances between adjacent sliding plate plates are equal.

In some embodiments, the outer circumference of the piston abuts the lower side of the front end of the vane plate when the piston is at the maximum inclination angle.

A refrigeration cycle system according to an embodiment of the second aspect of the present invention includes a compressor, a condenser, an expansion valve, an evaporator, and a gas-liquid separator provided between the expansion valve and the evaporator, the compressor It is the rotary compressor described in any of the above embodiments.

Description of drawings

1 is a schematic structural diagram of a longitudinal section of a rotary compressor according to an embodiment of the present invention, and a schematic diagram of a refrigeration cycle system connected to the rotary compressor.

FIG. 2 is a schematic structural diagram of a compression mechanism of the rotary compressor in FIG. 1 .

FIG. 3 is a schematic structural diagram of an example of the sliding vane of the compression mechanism in FIG. 2 .

FIG. 4 is a schematic structural diagram of another example of the sliding vane of the compression mechanism in FIG. 2 .

FIG. 5 is a schematic structural diagram of a compression mechanism in the related art.

Reference number:

Rotary compressor 1, casing 2, exhaust pipe 3, suction pipe 4, compression mechanism 5, motor 6, evaporator 7, accumulator 8, expansion device 9, sliding vane 10, second sliding vane plate 11, The first sliding plate 12, the third sliding plate 13, the recess 14, the elastic member 15, the spring hole 16, the second sliding plate 17, the cylinder 18, the cylinder chamber 19, the suction chamber 191, the compression chamber 192, the first gap 20 , the second gap 21, the vane groove 22, the piston 23, the crankshaft 24, the eccentric shaft 25, the through hole 26, the main bearing 27, the auxiliary bearing 28, the main exhaust hole 29, the auxiliary exhaust hole 30, the main muffler 31, Auxiliary muffler 32, condenser 33.

Detailed ways

The following describes in detail the embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary, and are intended to explain the present invention and should not be construed as limiting the present invention.

A rotary compressor and a refrigeration cycle system and a vane assembly according to embodiments of the present invention will be described below with reference to the accompanying drawings.

As shown in FIGS. 1-4 , the rotary compressor 1 according to the embodiment of the present invention includes a casing 2 , a motor 6 and a compression mechanism 5 .

The electric motor 6 is provided in the casing 2 and has a crankshaft 24 . As shown in FIG. 1 , the motor 6 is fixed on the inner wall of the casing 2 , and one end of the crankshaft 24 (the upper end of the crankshaft 24 in FIG. 1 ) is inserted into the motor 6 to be fixedly connected to the motor 6 .

The compression mechanism 5 is provided in the casing 2 and is driven by the crankshaft 24 of the motor 6 . As shown in FIG. 1 , the compression mechanism 5 is fixed on the inner wall of the casing 2 and is located below the motor 6 , the other end of the crankshaft 24 (the lower end of the crankshaft 24 in FIG. 1 ) is fixedly connected to the compression mechanism 5 , and the motor 6 drives the crankshaft 24 Rotate, and then drive the compression mechanism 5 .

The compression mechanism 5 includes a cylinder 18 , a piston 23 , a sliding vane 10 and an elastic member 15 .

The cylinder 18 has a cylinder chamber 19 and a vane groove 22 , and the piston 23 rotates eccentrically in the cylinder chamber 19 .

The sliding vane 10 can move back and forth in the sliding vane groove 22 (reciprocating movement along the left and right directions shown in FIG. 1 ), and the front end of the sliding vane 10 (the left end of the sliding vane 10 in FIG. 1 ) is in contact with the outer peripheral surface of the piston 22 . Next, the cylinder chamber 19 is divided into a suction chamber 191 and a compression chamber 192 . The sliding vane 10 includes at least three sliding vane plates stacked in the axial direction of the crankshaft 24 (up and down in FIG. 1 ), and adjacent sliding vane plates are relatively movable in the reciprocating direction of the sliding vane 10 .

The elastic member 15 presses the slider 10 toward the piston 23 so that the front end portion of the slider 10 abuts on the outer peripheral surface of the piston 23 .

According to the rotary compressor of the embodiment of the present invention, a sliding vane is provided in the sliding vane groove in the compression mechanism, and the sliding vane is formed by stacking at least three sliding vane plates, and the three sliding vane plates are relatively movable. The flexibility of the sliding vane is improved by the stacking of the three sliding vane plates, which can reduce the gap between the sliding vane and the piston, reduce the amount of gas leaking from the high-pressure gas in the compression chamber to the low-pressure chamber, improve the performance of the compressor, and reduce refrigeration. The drop in the cooling capacity of the circulating system.

In some embodiments, the number of sliding plates is n, and the number of elastic members 15 is n−1, where n is a natural number greater than or equal to 3, and each elastic member 15 is connected to the rear end ( The right end of the slider plate as shown in Figures 1 and 3) abuts.

As shown in FIG. 3 and FIG. 4 , n sliding plates are stacked along the axial direction of the crankshaft 24 to form the sliding plate 10 , and n-1 elastic members 15 are arranged on the rear end of the n sliding plates and the inner wall of the casing 2 superior. The left end of the elastic member 15 is connected with the right end of the sliding plate, and the left end of the elastic member 15 is provided with an upper joint and a lower joint arranged oppositely along the up-down direction, and the upper joint and the lower joint are respectively connected to two adjacent sliding plates. the back end. The right end of the elastic member 15 is connected to the inner wall of the casing 2 , and the elastic member 15 presses the n sliding vane plates toward the piston 23 so that the left ends of the n sliding vane plates contact the outer peripheral surface of the piston 23 .

In some embodiments, as shown in FIGS. 3 and 4 , the rear end of the sliding plate is provided with a concave portion 14 , and the front end of each elastic piece 15 abuts in the concave portion 14 of the adjacent sliding plate.

As shown in FIG. 3 and FIG. 4 , the left end of the elastic member 15 is provided with an upper joint and a lower joint opposite to each other along the up-down direction, and the upper joint and the lower joint are matched with the concave portion 14 .

In some embodiments, the vane plates include a first vane plate 12 , a second vane plate 11 and a third vane plate 13 which are arranged adjacent to one another in the axial direction of the crankshaft 24 , the first vane plate 12 and the third vane plate 13 The rear end of the third sliding plate 13 is provided with at least one concave portion 14 , the rear end of the second sliding plate 12 is provided with at least two concave portions 14 , and the at least two concave portions 14 of the second sliding plate 12 are along the crankshaft 24 . Axially spaced, the elastic member 15 includes a first elastic member and a second elastic member, the front end of the first elastic member abuts in the concave portion 14 of the first sliding plate 12 and a concave portion 14 of the second sliding plate 11, The front end of the second elastic member abuts in the other concave portion 14 of the second sliding plate 11 and in the concave portion 14 of the third sliding plate 13 .

As shown in FIG. 3 and FIG. 4 , the first sliding plate 12 , the second sliding plate 11 and the third sliding plate 13 are stacked in the up-down direction to form the sliding plate 10 , and the second sliding plate 11 is located in the first sliding plate 10 . Between the plate 12 and the third sliding plate plate 13, the elastic member 15 includes a first elastic member and a second elastic member. The left end of the elastic member 15 is provided with an upper joint and a lower joint arranged oppositely. The concave part 14 of the first sliding plate 12 is matched, the lower joint of the first elastic piece is matched with the concave part 14 above the second sliding plate 11, the upper joint of the second elastic piece is matched with the lower part of the second sliding plate 11, the first The lower joints of the two elastic members are matched with the concave portion 14 of the third sliding plate 13 .

In some embodiments, the elastic member 15 is a spring.

In some embodiments, as shown in FIGS. 3 and 4 , the slider plates are generally square plates, and a plurality of slider plates are stacked along their width direction (up-down direction in FIG. 1 ).

In some embodiments, as shown in FIGS. 3 and 4 , the widths of the plurality of slide plates are substantially equal.

In some embodiments, as shown in FIG. 4 , the dimensions of the first sliding plate 12 , the second sliding plate 11 and the third sliding plate 13 are the same, and in the reciprocating direction of the sliding plate 10 , adjacent sliding plates The relative movement distances between the plates are equal.

In some embodiments, when the piston 23 is at the maximum tilt angle, the outer circumference of the piston 23 abuts the lower side of the front end of the sliding plate.

As shown in FIG. 4 , the dimensions of the first sliding plate 12 , the second sliding plate 11 and the third sliding plate 13 are the same. When the piston 23 is at the maximum inclination angle, the first sliding plate 12 , the second sliding plate 13 and the second sliding plate 13 have the same size. The plate 11 and the third sliding plate 13 move under the action of the elastic member 15, so that the lower side of the left end of the first sliding plate 12, the lower side of the left end of the second sliding plate 11 and the lower side of the third sliding plate 13. The lower side of the left end abuts on the outer circumference of the piston 23 . Therefore, through the design of the first sliding vane plate, the second sliding vane plate and the third sliding vane plate, the total gap between the outer periphery of the piston and the sliding vanes is reduced, reducing the leakage of the high pressure gas in the compression chamber to the low pressure chamber. Gas volume, improve compressor performance, and reduce the drop in cooling capacity of the refrigeration cycle system.

In some specific embodiments, as shown in FIG. 1 , the rotary compressor 1 is composed of a motor 6 accommodated in a sealed casing 2 with an opening in the exhaust pipe 3 , and a compression mechanism 5 driven by a crankshaft 24 connected to the motor 6 , The bottom of the casing 2 has lubricating oil (not shown).

The compression mechanism 5 is fixed on the inner wall of the casing 2 , and the compression mechanism 5 includes a cylinder 18 , a main bearing 27 , an auxiliary bearing 28 , a crankshaft 24 , a piston 23 and a sliding vane 10 .

The cylinder 18 has a cylinder chamber 19 and a sliding vane groove 22. The upper end surface of the cylinder chamber 19 has an upper opening hole, and the lower end surface of the cylinder chamber 19 has a lower opening hole.

The main bearing 27 is provided on the upper end surface of the cylinder chamber 19 for sealing the upper opening of the cylinder chamber 19 , and the auxiliary bearing 28 is provided on the lower end surface of the cylinder chamber 19 for sealing the lower opening of the cylinder chamber 19 .

The upper end of the crankshaft 24 is fixedly connected with the motor 6 , and the lower end of the crankshaft 24 penetrates the main bearing 27 , the cylinder chamber 19 and the auxiliary bearing 28 in sequence, the main bearing 27 and the auxiliary bearing 28 are slidingly matched with the crankshaft 24 , and the lower end of the crankshaft 24 is provided with an eccentric shaft 25 , the eccentric shaft 25 is arranged in the cylinder chamber 19 .

The piston 23 is arranged in the cylinder chamber 19 , the piston 23 is sleeved on the outer peripheral contour of the eccentric shaft 25 , and the piston 23 is driven to revolve in the cylinder chamber 19 by the eccentric shaft 25 .

The sliding vane 10 is arranged in the sliding vane groove 22, the left end of the sliding vane 10 abuts on the outer circumference of the piston 23, and the right end of the sliding vane 10 is connected to the inner wall of the casing 2 through the elastic member 15, and the sliding vane 10 can be placed on the sliding vane 10. Reciprocating sliding in the groove 22 .

The slider 10 is composed of a second slider plate 11 located in the center, a first slider plate 12 and a third slider plate 13 connected to the upper and lower sides thereof, the second slider plate 11, the first slider plate 12 and the third slider plate 13. The sliding plate 13 abuts the outer circumference of the piston 23 and reciprocates, and the two elastic members 15 located at the right end of the sliding plate 10 press the second sliding plate 11 and the right end of the first sliding plate 12, and the second sliding plate 12 respectively. The right end of the blade plate 11 and the third sliding blade plate 13 .

Preferably, by enlarging the upper and lower dimension H of the cylinder chamber 19, the displacement of the cylinder chamber 19 is increased, so that the outer peripheral height dimension of the piston 23 is also increased. Thereby, the number of the slider plates constituting the slider 10 can be increased, for example, an n-th slider plate can be added, and the slider 10 can be constituted by n slider plates.

Preferably, the low-pressure gas sucked in by the suction pipe 4 connected to the accumulator 8 is compressed into a high-pressure gas in the compression chamber 192 of the cylinder chamber 19, and the high-pressure gas flows from the main exhaust holes 29 and 29 located in the main bearing 27, respectively. The auxiliary exhaust hole 30 on the auxiliary bearing 28 is discharged into the main muffler 31 and the auxiliary muffler 32 , and the high-pressure gas in the auxiliary muffler 32 joins the high-pressure gas in the main muffler 31 through the through hole 26 .

Preferably, the high-pressure gas in the main muffler 31 after the confluence is discharged to the lower space of the motor 6 and gradually moves to the upper space of the motor 6 , the high-pressure gas is finally discharged from the exhaust pipe 3 , and the high-pressure gas passes through the condenser 33 After that, it becomes a liquid refrigerant, and the liquid refrigerant passes through the expansion device 9 and evaporates in the evaporator 7 to become a low-pressure gas. Refrigeration cycle system.

In some specific embodiments, as shown in FIG. 2 , the eccentric shaft 25 at the lower end of the crankshaft 24 that rotates counterclockwise rotates, so that the piston 23 revolves in the cylinder chamber 19 , the left end of the sliding vane 10 abuts on the outer circumference of the piston 23 , and the sliding The sheet 10 slides back and forth in the slide groove 22 .

Preferably, when the rotational speed of the crankshaft 24 driven by the motor 6 is, for example, 60 rps (60 revolutions per second), the number of revolutions of the piston 23 is 60 times per second, and the number of reciprocating sliding movements of the sliding vane 10 is also 60 times per second. The high-pressure gas and the elastic member 15 acting on the compression chamber 192 at the right end of the sliding vane 10 press the left end of the sliding vane 10 against the outer peripheral surface of the piston 23, so the number of rotations of the piston 23 (dotted arrow in FIG. 2) is the number of revolutions (solid arrow in Figure 2) 10% (6 times/sec). Since the pressure of the left end of the sliding vane 10 on the piston 23 limits the number of rotations of the piston 23 , the wear between the left end of the sliding vane 10 and the outer circumference of the piston 23 is reduced.

In some specific embodiments, as shown in FIG. 3 , the sliding plate 10 includes a first sliding plate plate 12 , a second sliding plate plate 11 and a third sliding plate plate 13 which are arranged adjacent to one another in the up-down direction. The rear ends of the blade plate 12 and the third sliding blade plate 13 are each provided with a recessed portion 14 , and the rear end of the second sliding blade plate 12 is provided with two recessed portions 14 .

The elastic member 15 is a spring, and the number of elastic members 15 is two. The left end of the spring is embedded in the two recesses 14 of the second sliding plate 11 , the first sliding plate 12 and the third sliding plate 13 , and By pressing the rear end of the sliding piece 10 , the right ends of the springs are respectively embedded in the spring holes 16 on the outer circumference of the cylinder 18 .

When the compression mechanism 5 operates, the compressive load acting on the piston 23 revolving in the cylinder chamber 19 greatly changes, and the crankshaft 24 is deformed toward the low pressure chamber side of the cylinder chamber 19 due to the load change, so that the eccentric shaft 25 in the piston 23 slightly changes tilt.

When the vertical dimension of the cylinder chamber 19 is H and the vertical dimension of the piston 23 revolving in the cylinder chamber 19 is R, H-R=C, and C is the sliding clearance of the piston 23 . When the eccentric shaft 25 in the piston 23 is inclined due to the inclination of the crankshaft 24, the piston 23 inclines within the range of the sliding gap C, so that a gap is created between the outer periphery of the piston 23 and the left end of the vane plate.

In some specific embodiments, as shown in FIG. 4 , the inclination angle of the piston 23 during the operation of the compression mechanism 5 is increased, and the gap between the piston 23 and the left end of the sliding vane plate constituting the sliding vane 10 is W. The upper and lower dimensions h of the vane plates are the same, so the three gaps W between the second vane plate 11 , the first vane plate 12 , and the third vane plate 13 and the piston 23 are the same.

The right end of the vane plate is pressed by the high-pressure gas and the elastic member 15 , and the left end of the vane plate abuts on the outer periphery of the piston 23 . At this time, three first gaps 20 are generated, and the first gaps 20 become the leakage paths through which the high-pressure gas from the cylinder chamber 19 leaks to the low-pressure chamber. The area of the first gaps 20 is A, A=0.5W*h. The total gap between the outer peripheries of the piston 23 is 3A.

In the related art, as shown in FIG. 5 , the outer dimension of the second sliding vane 17 is the same as that of the sliding vane 10 , and the area of the second gap 21 generated between the outer circumference of the piston 23 and the left end of the second sliding vane 17 is B, B is 0.5*3h*3W=0.5*h*W*9.

Compared with the second sliding vane 17 in the related art, the sliding vane 10 in the specific embodiment of the present invention has a total clearance of the sliding vane 10 composed of three sliding vane plates, which is 1/3 of the total clearance of the second sliding vane 17 . . In addition, even if the total gap is the same, the smaller the gap area, the smaller the amount of leaked gas. Therefore, the sliding vane 10 in the embodiment of the present invention has the effect of greatly reducing the amount of leaked gas.

Although the rotary compressor of the embodiment of the present invention has been described based on a single-cylinder rotary compressor, it can be easily applied to a multi-cylinder rotary compressor such as a two-cylinder.

A refrigeration cycle system according to an embodiment of the present invention will be described below with reference to FIG. 1 .

A refrigeration cycle system according to an embodiment of the present invention includes the rotary compressor 1 of any of the above-described embodiments. The refrigeration cycle system further includes an exhaust pipe 3 , a suction pipe 4 , a condenser 33 , a liquid accumulator 8 , an expansion device 9 and an evaporator 7 all located outside the casing 2 .

The top of the casing 2 is connected with the exhaust pipe 3, and the low-pressure gas sucked by the suction pipe 4 connected to the accumulator 8 is compressed into high-pressure gas in the cylinder chamber 19. The exhaust hole 29 and the auxiliary exhaust hole 30 on the auxiliary bearing 28 are discharged to the main muffler 31 and the sub muffler 32 .

The combined high-pressure gas of the main muffler 31 is discharged to the lower space of the motor 6 and moved to the upper space of the motor 6. The high-pressure gas discharged from the exhaust pipe 3 becomes a liquid refrigerant in the condenser 33, and passes through the expansion device 9. The low-pressure refrigerant is evaporated in the evaporator 7 to become low-pressure gas, and the low-pressure gas flows from the accumulator 8 through the suction pipe 4 into the cylinder chamber 19 , and a refrigeration cycle including the rotary compressor 1 is established.

In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", " Rear, Left, Right, Vertical, Horizontal, Top, Bottom, Inner, Outer, Clockwise, Counterclockwise, Axial, The orientations or positional relationships indicated by "radial direction", "circumferential direction", etc. are based on the orientations or positional relationships shown in the accompanying drawings, which are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying the indicated devices or elements. It must have a specific orientation, be constructed and operate in a specific orientation, and therefore should not be construed as a limitation of the present invention.

In addition, the terms "first" and "second" are only used for descriptive purposes, and should not be construed as indicating or implying relative importance or implying the number of indicated technical features. Thus, a feature delimited with "first", "second" may expressly or implicitly include at least one of that feature. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise expressly and specifically defined.

In the present invention, unless otherwise expressly specified and limited, the terms "installed", "connected", "connected", "fixed" and other terms should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection , or integrated; it can be a mechanical connection or an electrical connection or can communicate with each other; it can be directly connected or indirectly connected through an intermediate medium, it can be the internal connection of two components or the interaction relationship between the two components, unless otherwise expressly qualified. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

In the present invention, unless otherwise expressly specified and limited, a first feature "on" or "under" a second feature may be in direct contact between the first and second features, or the first and second features indirectly through an intermediary touch. Also, the first feature being "above", "over" and "above" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is level higher than the second feature. The first feature being "below", "below" and "below" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature has a lower level than the second feature.

In this disclosure, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples" and the like mean a specific feature, structure, material, or description described in connection with the embodiment or example. Features are included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, those skilled in the art may combine and combine the different embodiments or examples described in this specification, as well as the features of the different embodiments or examples, without conflicting each other.

Although the embodiments of the present invention have been shown and described above, it should be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Embodiments are subject to variations, modifications, substitutions and variations.

Claims (10)

1. A rotary compressor, comprising:

a housing;

a motor disposed within the housing and having a crankshaft; and

a compression mechanism disposed within the housing and driven by the crankshaft of the motor, the compression mechanism having:

the air cylinder is internally provided with a cylinder chamber and a slide sheet groove;

a piston eccentrically rotating within the cylinder chamber;

a slide plate, which is reciprocatingly movable in the slide plate groove, a front end portion of which abuts against an outer circumferential surface of the piston to divide the cylinder chamber into a suction chamber and a compression chamber, the slide plate including at least three slide plate plates stacked in an axial direction of the crankshaft, adjacent slide plate plates being relatively movable in a reciprocating direction of the slide plate;

and the elastic piece presses the sliding piece towards the piston so that the front end part of the sliding piece is abutted against the outer peripheral surface of the piston.

2. The rotary compressor according to claim 1, wherein the number of the vane plates is n, the number of the elastic members is n-1, wherein n is a natural number of 3 or more, and each of the elastic members abuts against rear ends of adjacent two of the vane plates.

3. The rotary compressor of claim 2, wherein the rear end of the vane plate is provided with a recess, and the front end of each of the elastic members abuts in the recess of the adjacent vane plate.

4. The rotary compressor of claim 3, wherein the vane plates include a first vane plate, a second vane plate, and a third vane plate that are arranged adjacent to each other in the axial direction of the crankshaft, rear ends of the first vane plate and the third vane plate are each provided with at least one of the recesses, a rear end of the second vane plate is provided with at least two of the recesses, the at least two recesses of the second vane plate are arranged at intervals in the axial direction of the crankshaft,

the elastic member comprises a first elastic member and a second elastic member, the front end of the first elastic member abuts against the concave part of the first slide plate and one concave part of the second slide plate, and the front end of the second elastic member abuts against the other concave part of the second slide plate and the concave part of the third slide plate.

5. The rotary compressor of any one of claims 1 to 4, wherein the elastic member is a spring.

6. The rotary compressor of any one of claims 1 to 4, wherein the vane plates are substantially square plates, and a plurality of the vane plates are stacked in their width direction.

7. The rotary compressor of claim 6, wherein a plurality of the vane plates are substantially equal in width.

8. The rotary compressor of any one of claims 1 to 4, wherein a relative moving distance between adjacent vane plates is equal in a reciprocating moving direction of the vane.

9. The rotary compressor of claim 1, wherein an outer periphery of the piston abuts against a lower side of a front end of the vane plate when the piston is at a maximum inclination angle.

10. A refrigeration cycle system comprising a compressor, a condenser, an expansion valve, an evaporator, and a gas-liquid separator provided between the expansion valve and the evaporator, wherein the compressor is a rotary compressor according to any one of claims 1 to 8.

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