阅读说明：本技术 旋转压缩机和制冷循环系统 (Rotary compressor and refrigeration cycle system ) 是由 小津政雄 王玲 于 2020-07-30 设计创作，主要内容包括：本发明公开了一种旋转压缩机和制冷循环系统,所述旋转压缩机包括机壳、电机和压缩机构,电机设在机壳内且具有曲轴,曲轴包括第一偏心部、第二偏心部和中间轴；压缩机构设在机壳内且由曲轴驱动,压缩机构包括第一气缸、第二气缸、第一活塞和第二活塞,第一气缸具有第一缸室,第二气缸具有第二缸室,第一气缸和第二气缸之间设有隔板,隔板设有沿曲轴的轴向贯通隔板的中心腔,中间轴配合在中心腔内；第一偏心部配合在第一活塞内以带动第一活塞在第一缸室内偏心旋转,第二偏心部配合在第二活塞内以带动第二活塞在第二缸室内偏心旋转。本发明的旋转压缩机可以减少从活塞内周泄露到压缩腔的高压气体量,避免制冷量减少,提高压缩效率。(The invention discloses a rotary compressor and a refrigeration cycle system, wherein the rotary compressor comprises a shell, a motor and a compression mechanism, the motor is arranged in the shell and is provided with a crankshaft, and the crankshaft comprises a first eccentric part, a second eccentric part and an intermediate shaft; the compression mechanism is arranged in the shell and driven by the crankshaft, the compression mechanism comprises a first cylinder, a second cylinder, a first piston and a second piston, the first cylinder is provided with a first cylinder chamber, the second cylinder is provided with a second cylinder chamber, a partition plate is arranged between the first cylinder and the second cylinder, the partition plate is provided with a central cavity which penetrates through the partition plate along the axial direction of the crankshaft, and the intermediate shaft is matched in the central cavity; the first eccentric part is matched in the first piston to drive the first piston to eccentrically rotate in the first cylinder chamber, and the second eccentric part is matched in the second piston to drive the second piston to eccentrically rotate in the second cylinder chamber. The rotary compressor can reduce the amount of high-pressure gas leaked from the inner periphery of the piston to the compression cavity, avoid the reduction of refrigerating capacity and improve the compression efficiency.)

1. A rotary compressor, comprising:

a housing having a lubricant therein;

the motor is arranged in the shell and is provided with a crankshaft, and the crankshaft comprises a first eccentric part, a second eccentric part and an intermediate shaft connected between the first eccentric part and the second eccentric part; and

a compression mechanism disposed in the housing and driven by the crankshaft, the compression mechanism comprising:

the cylinder comprises a first cylinder and a second cylinder, the first cylinder is provided with a first cylinder chamber, the second cylinder is provided with a second cylinder chamber, a partition plate is arranged between the first cylinder and the second cylinder, the partition plate is provided with a central cavity which penetrates through the partition plate along the axial direction of the crankshaft, the intermediate shaft is matched in the central cavity, and the central line of the central cavity deviates from the central line of the intermediate shaft;

the piston comprises a first piston and a second piston, the first eccentric part is matched in the first piston to drive the first piston to eccentrically rotate in the first cylinder chamber, and the second eccentric part is matched in the second piston to drive the second piston to eccentrically rotate in the second cylinder chamber.

2. The rotary compressor according to claim 1, wherein the compression mechanism further includes a slide plate including a first slide plate and a second slide plate, the first cylinder having a first slide plate groove therein, the first slide plate being reciprocally movable in the first slide plate groove, a leading end portion of the first slide plate abutting against an outer peripheral surface of the first piston to divide the first cylinder chamber into a first low-pressure chamber and a first high-pressure chamber, the second cylinder having a second slide plate groove therein, the second slide plate being reciprocally movable in the second slide plate groove, a leading end portion of the second slide plate abutting against an outer peripheral surface of the second piston to divide the second cylinder chamber into a second low-pressure chamber and a second high-pressure chamber.

3. The rotary compressor of claim 2, wherein the pressure in the casing is equal to the discharge pressure of the first and second cylinders, and a center line of the central chamber is offset toward the first and second high pressure chambers with respect to a center line of the intermediate shaft.

4. The rotary compressor of claim 2, further comprising a suction pipe, a pressure inside the casing being equal to a suction pressure of the suction pipe, a center line of the central chamber being offset toward the first and second low pressure chambers with respect to a center line of the intermediate shaft.

5. The rotary compressor according to claim 2, wherein the compression mechanism further includes an elastic member including a first elastic member that presses the first vane toward the first piston to bring a leading end portion of the first vane into abutment with an outer peripheral surface of the first piston, and a second elastic member that presses the second vane toward the second piston to bring a leading end portion of the second vane into abutment with an outer peripheral surface of the second piston.

6. The rotary compressor of claim 1, wherein the compression mechanism further comprises a first bearing disposed at a top of the first cylinder and a second bearing disposed at a bottom of the second cylinder, the crankshaft being rotatably supported by the first and second bearings.

7. The rotary compressor of claim 6, wherein the crankshaft further comprises a main shaft and a counter shaft, the first eccentric portion, the second eccentric portion and the intermediate shaft being disposed between the main shaft and the counter shaft, a lower end of the main shaft being fitted within the first bearing, the counter shaft being fitted within the second bearing.

8. The rotary compressor of claim 7, wherein the crankshaft has a longitudinal hole extending from a lower end surface of the auxiliary shaft in an axial direction of the auxiliary shaft and to the main shaft, and the compression mechanism further comprises a pump provided at a lower end of the auxiliary shaft opposite to the longitudinal hole for pumping the lubricating oil in the casing into the longitudinal hole.

9. The rotary compressor of claim 5, wherein oil supply holes are provided in the lower end of the main shaft, the first eccentric portion, the intermediate shaft, the second eccentric portion, and the auxiliary shaft, the oil supply holes communicating with the longitudinal hole and the central cavity.

10. The rotary compressor of any one of claims 1-9, wherein an inner diameter of the central bore is equal to or greater than an outer diameter of the first eccentric portion and an inner diameter of the central bore is equal to or greater than an outer diameter of the second eccentric portion.

11. A refrigeration cycle system comprising a compressor, a condenser, an expansion device, an evaporator and an accumulator, the compressor being a rotary compressor according to any one of claims 1 to 10.

Technical Field

The invention belongs to the technical field of compressors, and particularly relates to a rotary compressor and a refrigeration cycle system.

Background

Rotary compressors typically include a casing, a motor assembly and a compression mechanism, wherein the slide of the compression mechanism reciprocates in a slide groove of the cylinder, a spring is provided at the rear end of the slide, the spring presses the slide, whereby the front end of the slide abuts the outer peripheral surface of the piston in the compression chamber.

Disclosure of Invention

The present invention is based on the discovery and recognition by the inventors of the following facts and problems:

Drawings

Fig. 1 is a schematic view of a refrigeration cycle system according to an embodiment of the present invention.

Fig. 2 is a schematic structural view of a rotary compressor according to an embodiment of the present invention.

Fig. 3 is a sectional view of the rotary compressor X-X of fig. 2.

Fig. 4 is a cross-sectional view of the rotary compressor Y-Y of fig. 2.

Fig. 5 is another sectional view of the rotary compressor Y-Y of fig. 2.

Fig. 6 is still another sectional view of the rotary compressor Y-Y of fig. 2.

Fig. 7 is still another sectional view of the rotary compressor Y-Y section of fig. 2.

Fig. 8 is another further sectional view of the rotary compressor Y-Y section of fig. 2.

Fig. 9 is still another sectional view of the rotary compressor Y-Y section of fig. 2.

Reference numerals:

a rotary compressor 1, a casing 2, an exhaust pipe 3, a motor 4, a compression mechanism 5, an elastic member 6, a first elastic member 61, a second elastic member 62, a lubricating oil 8, a first cylinder 10, a first cylinder chamber 10A, a first low pressure chamber 10A, a first high pressure chamber 10B, a first vane groove 101, a first air suction hole 11a, a first piston 13, an assembly screw 14, a partition plate 15, a central chamber 15A, a center line 15C, a second cylinder 20, a second vane groove 201, a second cylinder chamber 20B, a second low pressure chamber 20A, a second high pressure chamber 20B, a second piston 23, a vane 24, a first vane 24A, a second vane 24B, an air suction pipe 25, a first air suction pipe 25A, a second air suction pipe 25B, a first bearing 26, a first air discharge hole 26a, a first muffler 27, a second bearing 28, a second air discharge hole 28a, a second muffler 29, a crankshaft 30, center line S, main shaft 30A, the auxiliary shaft 30B, the longitudinal hole 30a, the first eccentric portion 31B, the intermediate shaft 30c, the oil supply hole 30d, the pump 35, the accumulator 40, the condenser 50, the expansion device 51, and the evaporator 52.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

A rotary compressor 1 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

As shown in fig. 1 to 9, a rotary compressor 1 according to an embodiment of the present invention includes a casing 2, a motor 4, and a compression mechanism 5.

The casing 2 has a lubricating oil 8 therein, and as shown in fig. 1, the outer peripheral profile of the cross section of the casing 2 is approximately circular, and the inside of the casing 2 has a cavity, and the lubricating oil 8 is located at the bottom of the cavity.

The motor 4 is provided in the housing 2 and has a crankshaft 30, the crankshaft 30 including a first eccentric portion 31A, a second eccentric portion 31B, and an intermediate shaft 30C, the intermediate shaft 30C being connected between the first eccentric portion 31A and the second eccentric portion 31B. As shown in fig. 1 and 2, the motor 4 is disposed inside the casing 2 and adjacent to the top of the casing 2, the crankshaft 30 extends in the up-down direction, the upper end of the crankshaft 30 is connected to the motor 4, the lower end of the crankshaft 30 extends to the bottom of the casing 2 and is spaced apart from the bottom of the casing 2, the first eccentric portion 31A and the second eccentric portion 31B are both sleeved on the crankshaft 30, and the first eccentric portion 31A is located above the second eccentric portion 31B.

The compression mechanism 5 is disposed in the casing 2 and driven by the crankshaft 30, as shown in fig. 1, the compression mechanism 5 is disposed inside the casing 2 and adjacent to the bottom of the casing 2, the compression mechanism 5 is connected to the lower end of the crankshaft 30, and the compression mechanism 5 includes a cylinder and a piston.

The cylinders include a first cylinder 10 and a second cylinder 20, the first cylinder 10 having a first cylinder chamber 10A, the second cylinder 20 having a second cylinder chamber 20B, and a partition plate 15 provided between the first cylinder 10 and the second cylinder 20. As shown in fig. 1, the first cylinder 10, the partition 15, and the second cylinder 20 are sequentially disposed in the vertical direction, and the partition 15 connects the first cylinder 10 and the second cylinder 20. The partition plate 15 is provided with a center cavity 15A penetrating the partition plate 15 in the axial direction of the crankshaft 30, and the intermediate shaft 30C is fitted in the center cavity 15A with the center line of the center cavity 15A being offset from the center line of the intermediate shaft 30C. As shown in FIG. 2, the partition 15 is provided with a central cavity 15A along the up-down direction, the central cavity 15A is a circular through hole, the intermediate shaft 30C passes through the central cavity 15A, the diameter of the intermediate shaft 30C is smaller than that of the central cavity 15A, and the axis of the intermediate shaft 30C is not collinear with the axis of the central cavity 15A.

The pistons include a first piston 13 and a second piston 23, a first eccentric portion 31A is fitted in the first piston 13 to cause the first piston 13 to eccentrically rotate in the first cylinder chamber 10A, and a second eccentric portion 31B is fitted in the second piston 23 to cause the second piston 23 to eccentrically rotate in the second cylinder chamber 20A. As shown in fig. 2-9, the first piston 13 and the second piston 23 are annular, the first piston 13 is disposed on the first eccentric portion 31A, the second piston 23 is disposed on the second eccentric portion 31B, and when the crankshaft 30 rotates, the first eccentric portion 31A drives the first piston 13 to eccentrically rotate in the first cylinder chamber 10A, and the second eccentric portion 31B drives the second piston 23 to eccentrically rotate in the second cylinder chamber 20A.

The rotary compressor according to the embodiment of the present invention includes a motor having a crankshaft including a first eccentric portion, a second eccentric portion, and an intermediate shaft connected between the first eccentric portion and the second eccentric portion, and a compression mechanism driven by the crankshaft including a first cylinder, a second cylinder, a first piston, a second piston, and a partition plate provided between the first cylinder and the second cylinder, the intermediate shaft of the crankshaft passing through the partition plate, the first eccentric portion fitted in the first piston to drive the first piston to eccentrically rotate in the first cylinder, the second eccentric portion fitted in the second piston to drive the second piston to eccentrically rotate in the second cylinder, and by setting a center line of a central chamber to be eccentric from a center line of the intermediate shaft, so that a sliding gap between the first piston and the second piston eccentrically rotating on the partition plate is increased, an amount of high pressure gas leaking from sliding surfaces of the first piston and the second piston to the first cylinder and the second cylinder can be reduced, avoid the refrigerating output to reduce, improve compression efficiency and can reduce the high-pressure gas volume of revealing first cylinder and second cylinder from the glide plane of first piston and second piston, avoid the refrigerating output to reduce, improve compression efficiency.

In some embodiments, the compression mechanism 5 further includes a slide plate 24, the slide plate 24 includes a first slide plate 24A and a second slide plate 24B, the first cylinder 10 has a first slide plate groove 101 therein, the first slide plate 24A is reciprocally movable (e.g., reciprocally movable in a left-right direction in fig. 2) in the first slide plate groove 101, a front end portion of the first slide plate 24A (e.g., a left end of the first slide plate 24A in fig. 2) abuts against an outer peripheral surface of the first piston 13 to divide the first cylinder chamber 10A into a first low-pressure chamber 10A and a first high-pressure chamber 10B, the second cylinder 20 has a second slide plate groove 201 therein, the second slide plate 24B is reciprocally movable (e.g., in a left-right direction in fig. 2) in the second slide plate groove 201, and a front end portion of the second slide plate 24B (e.g., a left end of the second slide plate 24B in fig. 2) abuts against an outer peripheral surface of the second piston 23 to divide the second cylinder chamber 20A into a second low-pressure chamber 20A and a second high-pressure chamber 20B.

As shown in fig. 2 to 9, the first cylinder 10 has a first vane groove 101 therein, the first vane 24A is disposed in the first vane groove 101, and the first vane 24A is capable of reciprocating in the first vane groove 101 in the left-right direction, a left end of the first vane 24A abuts against an outer circumferential surface of the first piston 13 in the first cylinder 10 to divide the first cylinder chamber 10A into a first low pressure chamber 10A and a first high pressure chamber 10b, and a right end of the first vane 24A is connected to an inner circumferential wall of the casing 2.

The second cylinder 20 has a second slide groove 201 therein, the second slide 24B is provided in the second slide groove 201, and the second slide 24B is capable of reciprocating in the second slide groove 201 in the left-right direction, the left end of the second slide 24B abuts against the outer circumferential surface of the second piston 23 in the second cylinder 20 to divide the second cylinder chamber 20A into a second low-pressure chamber 20A and a second high-pressure chamber 20B, and the right end of the second slide 24B is connected to the inner circumferential wall of the casing 2.

In some embodiments, the pressure in the casing 2 is equal to the discharge pressure of the first and second cylinders 10 and 20, and the center line of the central chamber 15A is offset toward the first and second high-pressure chambers 10b and 20b with respect to the center line of the intermediate shaft 30C.

As shown in fig. 3-8, the central chamber 15A includes a center line 15C and the intermediate shaft 30C includes a center line S, the center line 15C of the central chamber 15A being offset toward the first and second high pressure chambers 10b and 20b with respect to the center line S of the intermediate shaft 30C.

In some embodiments, the rotary compressor 1 further includes a suction pipe 25, the pressure inside the casing 2 is equal to the suction pressure of the suction pipe 25, and the center line of the central chamber 15A is offset toward the first and second low pressure chambers 10a and 20a with respect to the center line of the intermediate shaft 30C.

As shown in fig. 9, the suction pipe 25 includes a first suction pipe 25A and a second suction pipe 25B, the first suction pipe 25A communicates with the first low pressure chamber 10a, and the second suction pipe 25B communicates with the second low pressure chamber 20 a. The center line 15C of the central chamber 15A is offset toward the first and second low pressure chambers 10a and 20a with respect to the center line S of the intermediate shaft 30C.

In some embodiments, the compression mechanism 5 further includes an elastic member 6, and the elastic member 6 includes a first elastic member 61 and a second elastic member 62, the first elastic member 61 presses the first vane 24A toward the first piston 13 to bring the leading end portion of the first vane 24A into abutment with the outer peripheral surface of the first piston 13, and the second elastic member 62 presses the second vane 24B toward the second piston 23 to bring the leading end portion of the second vane 24B into abutment with the outer peripheral surface of the second piston 23. Preferably, the elastic member is a spring.

As shown in fig. 2 to 9, a left end of the first elastic member 61 is connected to a right end of the first sliding vane 24A, a right end of the first elastic member 61 is connected to the casing 2, and the first elastic member 61 applies a thrust force to the first sliding vane 24A toward the first piston 13 so that the first sliding vane 24A abuts on an outer circumferential surface of the first piston 13. So as to ensure the relative independence of the first low-pressure chamber 10a and the first high-pressure chamber 10b and avoid the high-pressure gas and the low-pressure gas from being mixed.

The left end of the second elastic member 62 is connected to the right end of the second sliding vane 24B, the right end of the second elastic member 62 is connected to the casing 2, and the second elastic member 62 applies a thrust force to the second sliding vane 24B toward the second piston 23 so that the second sliding vane 24B abuts against the outer circumferential surface of the second piston 23. So as to ensure the relative independence of the second low pressure chamber 20a and the second high pressure chamber 20b and avoid the high pressure gas and the low pressure gas from being mixed.

In some embodiments, the compression mechanism 5 further includes a first bearing 26 and a second bearing 28, the first bearing 26 being disposed at a top portion of the first cylinder 10, the second bearing 28 being disposed at a bottom portion of the second cylinder 20, and a crankshaft 30 being rotatably supported by the first bearing 26 and the second bearing 28.

As shown in fig. 1 and 2, the lower end of the crankshaft 30 passes through the first bearing 26, the first cylinder 10, the second cylinder 20, and the second bearing 28 in this order. The lower end face of the first bearing 26 is connected to the upper end face of the first cylinder 10, the upper end face of the second bearing 28 is connected to the lower end face of the second cylinder 20, and the first bearing 26 and the second bearing 28 are slidably fitted to the crankshaft 30.

In some embodiments, crankshaft 30 further includes a primary shaft 30A and a secondary shaft 30B, with a first eccentric portion 31A, a second eccentric portion 31B, and an intermediate shaft 30C disposed between primary shaft 30A and secondary shaft 30B, with a lower end of primary shaft 30A fitted within first bearing 26 and secondary shaft 30B fitted within second bearing 28.

As shown in fig. 1 and 2, the upper end of the main shaft 30A is connected to the motor 4, the lower end of the main shaft 30A is connected to the upper end of the intermediate shaft 30C after passing through the first bearing 26, the lower end of the intermediate shaft 30C is connected to the upper end of the auxiliary shaft 30B after passing through the second bearing 28, the lower end of the auxiliary shaft 30B extends toward the bottom of the casing 2, and the lower end of the auxiliary shaft 30B is located in the lubricant oil 8.

In some embodiments, the crankshaft 30 has a longitudinal hole 30A, the longitudinal hole 30A extending from a lower end surface of the auxiliary shaft 30B in the axial direction of the auxiliary shaft 30B and to the main shaft 30A, and the compression mechanism 5 further includes a pump 35 provided at a lower end of the auxiliary shaft 30B and opposed to the longitudinal hole 30A for pumping the lubricating oil 8 in the casing 2 into the longitudinal hole 30A.

As shown in fig. 1 and 2, a longitudinal hole 30A extends upward from a lower end surface of the sub shaft 30B into the main shaft 30A in the axial direction of the sub shaft 30B, and an upper end of the longitudinal hole 30A is located above the first eccentric portion 31A, and a lower end of the longitudinal hole 30A is provided with a pump 35, and both the lower end of the longitudinal hole 30A and the pump 35 are located in the lubricating oil 8, and the pump 35 is used to draw the lubricating oil 8 and transport the lubricating oil 8 upward through the longitudinal hole 30A to the first eccentric portion 31A and the second eccentric portion 31B.

In some embodiments, oil supply holes 30d are provided in the lower end of the main shaft 30A, the first eccentric portion 31A, the intermediate shaft 30C, the second eccentric portion 31B, and the auxiliary shaft 30B, and the oil supply holes 30d communicate with the longitudinal hole 30A and the central cavity 15A.

As shown in fig. 2, the number of the oil supply holes 30d is at least 5, and 5 oil supply holes 30d are provided in the lower end of the main shaft 30A, the first eccentric portion 31A, the intermediate shaft 30C, the second eccentric portion 31B, and the auxiliary shaft 30B, respectively, and the oil supply holes 30d communicate with the longitudinal hole 30A and the central cavity 15A. The lubricating oil 8 can flow from the longitudinal hole 30a to the outside of the longitudinal hole 30a through the oil supply hole 30 d. Therefore, lubricating oil 8 falls from oil supply hole 30d in partition plate 15 onto the sliding surfaces of first piston 13 and second piston 23 that eccentrically rotate on partition plate 15, and the problem of leakage of high-pressure gas in the inner peripheries of first piston 13 and second piston 23 into first cylinder chamber 10A and second cylinder chamber 20B is improved, and compression efficiency is improved.

In some embodiments, as shown in FIG. 1, the inner diameter of the central bore 15A is equal to or greater than the outer diameter of the first eccentric portion 31A, and the inner diameter of the central bore 15A is equal to or greater than the outer diameter of the second eccentric portion 31B.

The inventor finds that in order to enable the crankshaft to penetrate through the central cavity, the inner diameter of the central cavity needs to be larger than or equal to the outer diameter of any one of the first eccentric part and the second eccentric part so as to ensure that the first eccentric part and the second eccentric part can penetrate through the central cavity, but under the assembly condition, the difference between the outer diameter of the piston and the inner diameter of the central cavity is reduced, when the crankshaft drives the piston to eccentrically revolve, a sliding gap exists between the piston and the edge of the central cavity in the radial direction of the piston, high-pressure gas in the central cavity leaks, and the refrigerating capacity of the compression mechanism is reduced.

Therefore, according to the rotary compressor provided by the embodiment of the invention, the lubricating oil can be guided into the central cavity by arranging the oil supply hole which is communicated with the inner space of the shell and the central cavity, so that the high-pressure gas in the central cavity is discharged, the high-pressure gas is prevented from leaking through the sliding gap between the piston and the central cavity, and the refrigerating capacity of the rotary compressor is improved.

In some implementations, as shown in fig. 2-9, the center line S bisects the first cylinder chamber 10A into a first low pressure chamber 10A having the first suction holes 11a and a first high pressure chamber 10b having the first discharge holes 26a, and the center chamber 15A is eccentric to the first high pressure chamber 10b side with respect to the rotational axis 33 of the crankshaft 30 by an eccentric dimension e. Accordingly, the outer peripheral clearances C1 and C2 of the center chamber 15A and the first piston 13 increase on the first low pressure chamber 10a side and decrease on the first high pressure chamber 10b side, respectively, so that the inner peripheral high pressure gas of the first piston 13 is less likely to leak on the first low pressure chamber 10a side where the pressure difference is large and less likely to leak on the first high pressure chamber 10b side where the pressure difference is small.

A rotary compressor according to a specific example of the present invention will be described with reference to fig. 1 to 9.

As shown in fig. 1 to 9, a rotary compressor 1 according to an embodiment of the present invention includes a casing 2, a motor 4, a compression mechanism 5, and a suction pipe 25.

The outer peripheral profile of the casing 2 is approximately cylindrical, and a cavity is formed inside the casing 2, and the lubricating oil 8 is located at the bottom of the cavity.

The motor 4 comprises a crankshaft 30, the motor 4 is arranged in the casing 2 and is adjacent to the top of the casing 2, the upper end of the crankshaft 30 is connected with the motor 4, and the lower end of the crankshaft 30 extends to the bottom of the casing 2 along the up-down direction.

The crankshaft 30 includes a first eccentric portion 31A, a second eccentric portion 31B, an intermediate shaft 30C, a main shaft 30A, and a sub shaft 30B.

The first eccentric portion 31A and the second eccentric portion 31B are both sleeved on the crankshaft 30, and the first eccentric portion 31A is located above the second eccentric portion 31B. The upper end of the main shaft 30A is connected with the motor 4, the lower end of the main shaft 30A is connected with the upper end of the intermediate shaft 30C after passing through the first bearing 26, the lower end of the intermediate shaft 30C is connected with the upper end of the auxiliary shaft 30B after passing through the second bearing 28, the lower end of the auxiliary shaft 30B extends towards the bottom of the machine shell 2, and the lower end of the auxiliary shaft 30B is positioned in the lubricating oil 8.

The crankshaft 30 has a longitudinal hole 30A, the longitudinal hole 30A extends upward into the main shaft 30A from the lower end surface of the sub shaft 30B in the axial direction of the sub shaft 30B, and the upper end of the longitudinal hole 30A is located above the first eccentric portion 31A, the lower end of the longitudinal hole 30A is provided with a pump 35, the lower end of the longitudinal hole 30A and the pump 35 are both located in the lubricating oil 8, and the pump 35 is used to draw the lubricating oil 8 and transport the lubricating oil 8 upward through the longitudinal hole 30A to the first eccentric portion 31A and the second eccentric portion 31B.

The crankshaft 30 has 5 oil supply holes 30d, the 5 oil supply holes 30d are provided in the lower end of the main shaft 30A, the first eccentric portion 31A, the intermediate shaft 30C, the second eccentric portion 31B, and the sub shaft 30B, respectively, and the oil supply holes 30d communicate with the longitudinal hole 30A and the central cavity 15A. The lubricating oil 8 can flow from the longitudinal hole 30a to the outside of the longitudinal hole 30a through the oil supply hole 30 d.

The compression mechanism 5 is disposed inside the casing 2 and adjacent to the bottom of the casing 2, the compression mechanism 5 is connected to the lower end of the crankshaft 30, and the compression mechanism 5 includes a cylinder, a piston, a sliding vane 24, a first bearing 26, a second bearing 28, and an elastic member 6.

The cylinders include a first cylinder 10 and a second cylinder 20, the first cylinder 10 having a first cylinder chamber 10A, the second cylinder 20 having a second cylinder chamber 20B, and a partition plate 15 provided between the first cylinder 10 and the second cylinder 20. The partition plate 15 is provided with a center cavity 15A penetrating the partition plate 15 in the axial direction of the crankshaft 30, and the intermediate shaft 30C is fitted in the center cavity 15A with the center line of the center cavity 15A being offset from the center line of the intermediate shaft 30C.

The pistons comprise a first piston 13 and a second piston 23, the peripheral profiles of the first piston 13 and the second piston 23 are approximate to a circular tube type, the first piston 13 is sleeved on the first eccentric portion 31A, the second piston 23 is sleeved on the second eccentric portion 31B, when the crankshaft 30 rotates, the first eccentric portion 31A drives the first piston 13 to eccentrically rotate in the first cylinder chamber 10A, and the second eccentric portion 31B drives the second piston 23 to eccentrically rotate in the second cylinder chamber 20A.

The slide sheet 24 includes a first slide sheet 24A and a second slide sheet 24B, a first slide sheet groove 101 is formed in the first cylinder 10, the first slide sheet 24A is disposed in the first slide sheet groove 101, the first slide sheet 24A can reciprocate in the first slide sheet groove 101 in the left-right direction, the left end of the first slide sheet 24A and the outer peripheral surface of the first piston 13 in the first cylinder 10 are abutted to divide the first cylinder chamber 10A into a first low-pressure chamber 10A and a first high-pressure chamber 10B, and the right end of the first slide sheet 24A is connected to the inner peripheral wall of the casing 2.

The second cylinder 20 has a second slide groove 201 therein, the second slide 24B is provided in the second slide groove 201, and the second slide 24B is capable of reciprocating in the second slide groove 201 in the left-right direction, the left end of the second slide 24B abuts against the outer circumferential surface of the second piston 23 in the second cylinder 20 to divide the second cylinder chamber 20A into a second low-pressure chamber 20A and a second high-pressure chamber 20B, and the right end of the second slide 24B is connected to the inner circumferential wall of the casing 2.

The suction pipe 25 includes a first suction pipe 25A and a second suction pipe 25B, the first suction pipe 25A communicating with the first low pressure chamber 10a, and the second suction pipe 25B communicating with the second low pressure chamber 20 a.

The elastic member 6 includes a first elastic member 61 and a second elastic member 62, a left end of the first elastic member 61 is connected to a right end of the first sliding piece 24A, a right end of the first elastic member 61 is connected to the casing 2, and the first elastic member 61 applies a thrust force toward the first piston 13 to the first sliding piece 24A so that the first sliding piece 24A abuts on an outer circumferential surface of the first piston 13.

The left end of the second elastic member 62 is connected to the right end of the second sliding vane 24B, the right end of the second elastic member 62 is connected to the casing 2, and the second elastic member 62 applies a thrust force to the second sliding vane 24B toward the second piston 23 so that the second sliding vane 24B abuts against the outer circumferential surface of the second piston 23.

The first bearing 26 is arranged at the top of the first cylinder 10, the second bearing 28 is arranged at the bottom of the second cylinder 20, the lower end of the crankshaft 30 sequentially passes through the first bearing 26, the first cylinder 10, the second cylinder 20 and the second bearing 28, and the first bearing 26 and the second bearing 28 are in sliding fit with the crankshaft 30.

It will be appreciated that the present application is not limited to a two-cylinder rotary compressor comprising only a first cylinder and a second cylinder, but is also applicable to a multi-cylinder rotary compressor having more than two cylinders, the center line of the central chamber of the partition plate between each adjacent cylinder being offset from the center line of the intermediate shaft fitted in the central chamber.

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

As shown in fig. 1, a refrigeration cycle system according to an embodiment of the present invention includes a rotary compressor 1 according to any one of the embodiments described above. The refrigeration cycle system further includes a condenser 50, an expansion device 51, an evaporator 52, and an accumulator 40 located outside the cabinet 2.

A motor 4 and a compression mechanism 5 driven by the motor 4 are housed in a casing 2 having an opening of an exhaust pipe 3, and a lubricant oil 8 is stored in the bottom of the casing 2.

The compression mechanism 5 fixed to the inner periphery of the casing 2 is constituted by a first cylinder 10, a second cylinder 20, a partition plate 15, a first bearing 26, a second bearing 28, and a crankshaft 30. A first bearing 26 is connected to an upper surface of the first cylinder 10, and a second bearing 28 is connected to a lower surface of the second cylinder 20.

As the crankshaft 30 rotates, high-pressure gas compressed in the first and second cylinders 10 and 20 is discharged to the first and second mufflers 27 and 29, respectively. The high-pressure gas of the second muffler 29 and the high-pressure gas of the first muffler 27 are merged and discharged to the inside of the casing 2. Therefore, the pressure inside the casing 2 is high pressure.

The high-pressure gas discharged from the gas discharge pipe 3 is condensed in the condenser 50, the condensed high-pressure gas passes through the expansion device 51, and the condensed high-pressure gas is evaporated in the evaporator 52 into low-pressure gas, which flows into the first cylinder 10 and the second cylinder 20 through the accumulator 40 and the first and second gas suction pipes 25A and 25B, respectively. Thereby, a sealed refrigerant cycle is established.

The partition 15 connects the first cylinder 10 and the second cylinder 20, the first bearing 26 is connected to an upper surface of the first cylinder 10, and the second bearing 28 is connected to a lower surface of the second cylinder 20 to close the first chamber 10A and the second chamber 20B.

The first bearing 26 is provided with a first exhaust hole 26a, the first exhaust hole 26a communicates with the first cylinder chamber 10A, the second bearing 28 is provided with a second exhaust hole 28a, and the second exhaust hole 28a communicates with the second cylinder chamber 20B.

The crankshaft 30 includes a main shaft 30A slidably engaged with the first bearing 26, a first eccentric portion 31A eccentrically rotating the first piston 13 in the first cylinder chamber 10A, an intermediate shaft 30C rotating inside the central cavity 15A of the partition plate 15, a second eccentric portion 31B eccentrically rotating the second piston 23 in the second cylinder chamber 20B, and a sub shaft 30B slidably engaged with the second bearing 28. The first vane 24A and the second vane 24B abut against the outer periphery of the first piston 13 and the outer periphery of the second piston 23, respectively.

In the assembly work of the crankshaft 30 having the first and second eccentric portions 31A and 31B having the same shape, the inner diameter of the central bore 15A is slightly larger than the outer diameters of the first and second eccentric portions 31A and 31B, and the inner diameter of the central bore 15A is equal to the inner diameters of the first and second pistons 13 and 23, wherein the assembly screw 14 is precisely assembled to constitute a fixed part of the compression mechanism 5.

A pump 35 is provided at the lower end of a vertical hole 30A formed from the sub shaft 30B to the main shaft 30A, and when the crankshaft 30 rotates, the lubricating oil 8 in the casing 2 rises upward from the lower end of the vertical hole 30A by the pump 35.

The lubricating oil 8 is discharged from the 5 oil supply holes 30d, and the lubricating oil 8 is used to lubricate the crankshaft 30, the first bearing 26, the second bearing 28, the first piston 13, and the second piston 23.

After the assembly of the compression mechanism 5 is completed, a part of the sliding surfaces having the first piston 13 and the second piston 23 protrudes into the central cavity 15A. The inner diameter of the central chamber 15A is equal to the inner diameters of the first piston 13 and the second piston 23. The protruding lengths C1 and C2 vary according to the eccentric rotation of the first piston 13 and the second piston 23.

The center of the central chamber 15A is eccentric toward the first high-pressure chamber 10b with respect to the rotation shaft 33 of the crankshaft 30. However, the second piston 23 which eccentrically rotates concentrically and at a phase angle of 180 ° is identical in rotation locus to the first piston 13. Therefore, the role of the center chamber 15A in the first cylinder chamber 10A coincides with the role of the center chamber 15A in the second cylinder chamber 20B.

The first cylinder chamber 10A is divided uniformly by a center line S connecting the rotation shaft 33 and the center of the first vane 24A into a first high pressure chamber 10b having the first exhaust port 26a and a first low pressure chamber 10A having the first intake port 11 a. The center line 15C of the center chamber 15A (indicated by a dotted line) of the partition 15 is eccentric from the rotation shaft 33 of the crankshaft 30 to the first high pressure chamber 10b, and the eccentric dimension is e. Since the center line 15C is eccentric, the gap between the central chamber 15A and the inner periphery of the first piston 13 varies. Assuming that the eccentric amount of the center line 15C is e, the eccentric angle with respect to the center of the first vane 24A is 270 °. The rotation angle θ of the first piston 13 with respect to the center of the first vane 24A is 90 °, and when θ is 90 °, the maximum effective clearance between the inner periphery and the outer periphery of the first piston 13 is C1, and when θ is 270 °, the maximum effective clearance is C2.

Due to the eccentricity of the center line 15C, the effective clearance of the first piston 13 in the first low-pressure chamber 10a increases and the effective clearance in the first high-pressure chamber 10b decreases. Here, the effective clearance refers to a clearance in which high-pressure gas on the inner periphery of the first piston 13 leaks into the low first pressure chamber 10A or the first high pressure chamber 10b of the first cylinder chamber 10A.

As shown in fig. 4 to 8, the minimum clearance C2 is shown when the rotational position of the first piston 13 is 90 °, 120 °, 180 °, 230 °, and 360 °, respectively. It can be confirmed that the maximum effective clearance C1 is more in the first low pressure chamber 10a and the minimum effective clearance is more in the first high pressure chamber 10 b.

When the refrigerant is R410A or R32, the pressure difference between the high-pressure gas pressure and the low-pressure gas pressure is about 3.1MpaG and about 0.9MpaG, respectively, is 2.2 MpaG.

On the other hand, when the pressure of the first cylinder chamber 10A reaches the exhaust pressure (Pd) equal to the internal pressure of the housing 2 under the steady operation condition, the rotation angle of the first piston 13, that is, the rotation angle θ at which the first exhaust hole 26a opens, is in the range of 180 ° to 250 ° under the steady operation condition in which the variation in the exhaust pressure is small. When the first exhaust port 26a is opened within the range of the rotation angle, the pressure of the first cylinder chamber 10A does not change until the first piston 13 rotates to θ equal to 360 °.

On the other hand, the inner peripheral pressure of the first piston 13 is always equal to the pressure of the housing 2, and is the above-mentioned high pressure of 3.1 Mp. Therefore, when the angle θ of the first piston 13 is in the range of 180 ° to 360 °, the difference between the inside and outside pressures of the first piston 13 is zero or less than 0.1Mp, and a small amount of high-pressure gas in the inner periphery of the first piston 13 leaks to the high-pressure side of the compression chamber. In order to minimize the total amount of gas that leaks from the inner peripheries to the outer peripheries of the first piston 13 and the second piston 23 in the first cylinder chamber 10A and the second cylinder chamber 20B, the center chamber 15A of the diaphragm 15 is made eccentric to the first high pressure chamber 10B or the second high pressure chamber 20B. And, the eccentricity e and the left-right direction are fine-tuned and optimized.

As shown in fig. 9, the internal pressure of the housing 2 is a high pressure (Pd) equal to the gas pressure discharged from the first cylinder chamber 10A and the second cylinder chamber 20B, but the internal pressure of the housing 2 is a low pressure (Ps) equal to the suction pressure of the first suction pipe 25A, and the position of the eccentricity e of the center cavity 15A of the partition 15 needs to be in the first low pressure cavity 10A of the first cylinder chamber 10A.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.

Furthermore, the terms "first", "second" and "first" 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 defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the present disclosure, the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples" and the like mean that a specific feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the terms used above are not necessarily intended to refer 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, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.