CN114151339A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN114151339A CN114151339A CN202011475963.9A CN202011475963A CN114151339A CN 114151339 A CN114151339 A CN 114151339A CN 202011475963 A CN202011475963 A CN 202011475963A CN 114151339 A CN114151339 A CN 114151339A
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- China
- Prior art keywords
- refrigerant
- suction passage
- refrigerant suction
- opening
- compression chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 239000003507 refrigerant Substances 0.000 claims abstract description 104
- 230000006835 compression Effects 0.000 claims abstract description 84
- 238000007906 compression Methods 0.000 claims abstract description 84
- 230000004048 modification Effects 0.000 description 5
- 238000012986 modification Methods 0.000 description 5
- 229910000831 Steel Inorganic materials 0.000 description 3
- 230000003111 delayed effect Effects 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A rotary compressor is provided, which can not delay the starting timing of the compression of the refrigerant in the compression chamber and can not cause the interference of the refrigerant suction passage and other parts arranged near the refrigerant suction passage even if the maximum width of the refrigerant suction passage is widened for increasing the refrigerant flow. The rotary compressor comprises: an electric unit having a stator, a rotor, and a rotating shaft of the rotor; and a rotary compression mechanism part which is driven by the rotating shaft and comprises a cylinder having a compression chamber for compressing refrigerant and a refrigerant suction passage for sucking the refrigerant into the compression chamber, wherein the refrigerant suction passage comprises a widened part for allowing the refrigerant to flow in from the outside of the cylinder and an opening part which extends from the widened part toward the compression chamber and is connected with the compression chamber through an opening end facing the compression chamber, the opening end of the opening part has a width smaller than that of the widened part, and the opening end has an area larger than or equal to the vertical cross-sectional area of the widened part.
Description
Technical Field
The present invention relates to a rotary compressor.
Background
Conventionally, as a compressor used for an air conditioning apparatus, for example, rotary compressors as disclosed in patent document 1, patent document 2 have been provided. The rotary compressor includes an electric portion having a stator, a rotor, and a rotary shaft (crankshaft) of the rotor, and a rotary compression mechanism portion driven by the electric portion. The electric section and the rotary compression mechanism section are connected via a rotary shaft.
The rotary compression mechanism includes a cylinder including a compression chamber, an eccentric portion (crankshaft eccentric portion) integrally formed with the rotary shaft and housed in the compression chamber, a roller provided around an outer side surface of the eccentric portion, and a vane abutting against the outer side surface of the roller to divide the compression chamber into a low pressure chamber and a high pressure chamber. The cylinder is provided with a refrigerant suction passage connected to a suction pipe for sucking refrigerant into the rotary compressor and sucking the refrigerant into the compression chamber.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 61-25982
Patent document 2: japanese patent No. 4659427
Disclosure of Invention
Technical problem to be solved by the invention
However, as a method of improving the refrigerant compression efficiency of the rotary compressor, there is a method of increasing the width (diameter) of the refrigerant suction passage to increase the amount of refrigerant sucked into the compression chamber. However, the conventional refrigerant suction passage is a flow passage extending substantially straight in the radial direction of the cylinder and having substantially the same width from one end to the other end. Therefore, as the width of the refrigerant suction passage increases, the width of the opening end of the refrigerant suction passage facing the compression chamber also increases. As a result, the time until the opening end is closed by the eccentric portion (roller) that rotates increases, and the timing of starting refrigerant compression may be delayed.
Further, since the widened refrigerant suction passage extends inside the cylinder, there is a possibility that the refrigerant suction passage interferes with other portions (for example, a vertical groove into which the vane is slidably inserted, a bolt member for fixing a frame for closing the compression chamber in the cylinder, and the like) arranged in the vicinity of the refrigerant suction passage.
The present invention has been made in view of the above problems, and an object of the present invention is to provide a rotary compressor including a rotary compression mechanism unit configured as follows: even if the maximum width of the refrigerant suction passage is widened to increase the refrigerant flow rate, the start timing of the compression of the refrigerant in the compression chamber is not delayed, and even if the widened portion is provided in the refrigerant suction passage, interference between other portions disposed in the vicinity of the refrigerant suction passage and the refrigerant suction passage is not caused.
Technical scheme for solving technical problem
The present invention provides a rotary compressor including an electric portion and a rotary compression mechanism portion driven by the electric portion, wherein the rotary compression mechanism portion includes a cylinder including a refrigerant suction passage, an opening portion facing a compression chamber of the cylinder and having a widened portion is formed in the refrigerant suction passage, the opening portion has a width smaller than that of the widened portion, and a vertical cross-sectional area of the opening portion is equal to or larger than that of the widened portion.
According to this aspect of the present invention, the refrigerant flow rate of the refrigerant suction passage can be increased by providing the widened portion wider than the conventional refrigerant suction passage. In addition, the resistance to the refrigerant flowing through the widened portion is also reduced compared to the prior art. Further, in the present invention, an opening portion narrower than the widened portion is connected to the compression chamber and closed by the roller. Therefore, according to this aspect of the present invention, even if the maximum width of the refrigerant suction passage is increased as compared with the conventional structure, the closing time of the refrigerant suction passage by the roller is not increased. This makes it possible to compress the refrigerant introduced into the compression chamber at the same timing as in the conventional rotary compression mechanism. Further, a vertical sectional area of the opening portion facing the compression chamber is the same as or larger than a vertical sectional area of the widened portion. Therefore, according to this aspect of the present invention, the change in the flow velocity of the refrigerant flowing through the widened portion and the refrigerant flowing through the opening portion can be minimized. Thus, even if the refrigerant is caused to flow through the widened portions and the openings having different widths, the energy loss of the refrigerant flowing through the refrigerant suction passage can be reduced as much as possible, and the refrigerant compression efficiency can be improved.
In the rotary compressor according to the present invention, it is preferable that a longitudinal direction of the widened portion and a longitudinal direction of the opening form a predetermined angle in a plan view of the cylinder.
According to this aspect of the present invention, the refrigerant suction passage can be formed in a region that does not interfere with other portions by appropriately adjusting the angle formed between the longitudinal direction of the widened portion and the longitudinal direction of the opening portion. As a result, the resistance to the refrigerant flowing in the widened portion can be further reduced without limiting the maximum width of the widened portion.
In the rotary compressor according to the present invention, it is preferable that the rotary compressor further includes two or more of the cylinders provided in series in the height direction, and the refrigerant suction passage formed in one of the two or more cylinders and the refrigerant suction passage formed in the other cylinder are disposed apart from each other at a predetermined angle in a plan view of the cylinders.
According to this aspect of the present invention, since the plurality of refrigerant suction passages formed in each of the two or more cylinders are arranged at a predetermined angle in a plan view of the cylinder (i.e., arranged at a predetermined distance in the circumferential direction of the cylinder), they are not arranged side by side in the height direction. As a result, the strength of the container of the rotary compressor can be suppressed from being reduced.
Effects of the invention
According to the rotary compressor of the present invention, there can be provided a rotary compressor including a rotary compression mechanism part having a structure including: even if the maximum width of the refrigerant suction passage is widened in order to increase the refrigerant flow rate, the start timing of the compression of the refrigerant in the compression chamber is not delayed, and even if the widened portion is provided in the refrigerant suction passage, interference between other portions disposed in the vicinity of the refrigerant suction passage and the refrigerant suction passage is not caused.
Drawings
Fig. 1 is a vertical sectional view of a rotary compressor of a first embodiment.
Fig. 2 is a perspective view of the rotary compression mechanism of the first embodiment.
Fig. 3(a) is a horizontal sectional view of the rotary compression mechanism of the first embodiment taken along line a-a' of fig. 1, and fig. 3(B) is an upward view of the rotary compression mechanism having an opening with a rectangular cross section as viewed from arrow B of fig. 3 (a).
Fig. 4 is a horizontal cross-sectional view showing a modification of the rotary compression mechanism of the first embodiment.
Fig. 5 is a vertical sectional view of the rotary compressor of the second embodiment.
Fig. 6(a) is a horizontal sectional view of the rotary compression mechanism of the second embodiment taken along the line C-C' in fig. 5, and fig. 6(b) is a view of the rotary compression mechanism as viewed from the arrow D in fig. 6 (a).
Description of the reference numerals
1: a rotary compressor; 10: an electric section; 11: a stator; 12: a rotor; 13: a rotating shaft of the rotor; 20: a rotary compression mechanism part; 21: a cylinder; 211: a compression chamber; 22: a deflection core portion; 23: a roller; 24: a blade; 25: a coil spring; 27: a refrigerant suction passage; 271: a widening section; 272: an opening part; 273: an open end; 30: a container; 70: a reservoir.
Detailed Description
[ first embodiment ]
A rotary compressor according to an embodiment of the present invention will be described in detail below with reference to the accompanying drawings. First, the overall structure of a rotary compressor 1 according to a first embodiment of the present invention will be described with reference to fig. 1 and 2. Here, fig. 1 is a vertical sectional view of the rotary compressor 1. Fig. 2 is a perspective view of the rotary compression mechanism 20 provided in the rotary compressor 1.
As shown in fig. 1, the rotary compressor 1 of the present embodiment includes an electric motor unit 10 and a rotary compression mechanism unit 20 driven by the electric motor unit 10. The electric motor section 10 and the rotary compression mechanism section 20 are housed in a steel plate-made closed casing 30 provided with a casing body section 31 and a lid section 32. The rotary compressor 1 shown in the drawings is a vertical type, but is not limited thereto. The rotary compressor of the present invention may be applied to a horizontal type rotary compressor.
The electric motor unit 10 is a brushless DC motor including a stator 11, a rotor 12, and a rotating shaft (crankshaft) 13 of the rotor 12. Here, the stator 11 includes a laminated body 11a in which a plurality of electromagnetic steel plates having a substantially cylindrical airspace and a circular ring shape in a plan view are laminated in a height direction, and a stator coil 11b wound around a tooth portion provided in the laminated body 11a in a concentrated winding manner.
The rotor 12 includes a stacked body 12a formed by stacking a plurality of electromagnetic steel plates having a substantially circular shape in plan view in the height direction, and a permanent magnet provided in the stacked body 12 a. The laminated body 12a of the rotor 12 is disposed in a columnar space formed inside the stator 11. At this time, a slight gap is formed between the inner end of the tooth portion of the stator 11 and the outer surface of the rotor 12. A through hole 12b penetrating in the height direction is formed in the center of the rotor 12. The rotary shaft 13 is inserted into the through hole 12b to support the rotor 12.
Next, as shown in fig. 1 and 2, the rotary compression mechanism 20 includes a cylinder 21, an eccentric portion 22, a roller 23, a vane 24, and a coil spring 25. Here, as shown in fig. 1, the cylinder 21 includes a compression chamber 211 penetrating vertically therein. Further, frames 26a and 26b including bearing portions for the rotary shaft 13 are attached to the upper surface and the lower surface of the cylinder 21, respectively. The compression chamber 211 is closed by the frames 26a, 26 b.
As shown in fig. 2, the eccentric portion 22 is housed in the compression chamber 211 and is formed integrally with the rotary shaft 13. Further, a roller 23 is provided around the outer side surface of the eccentric portion 22. Further, the vane 24 is slidably disposed in a longitudinal groove 241 formed in the cylinder 21 and faces the compression chamber 211. At this time, the inner ends of the blades 24 abut against the outer surface of the rotor 23. Thereby, the compression chamber 211 is divided into a low pressure chamber and a high pressure chamber. The coil spring 25 is disposed outside the straight groove 241 and biases the outer end of the blade 24.
In the rotary compression mechanism 20 having the above-described configuration, when the rotary shaft 13 rotates, the eccentric portion 22 and the rotor 23 eccentrically rotate in the compression chamber 211. At this time, the rotor 23 eccentrically rotates along the inner surface of the compression chamber 211. Further, the vane 24 abutting against the outer surface of the rotor 23 is inserted outside the cylinder 21 in accordance with the eccentric rotation of the rotor 23. If the rotor 23 continues to rotate eccentrically, the vane 24 slides in the opposite direction to the previous direction, returning to the original position.
However, as shown in fig. 1, the cylinder 21 includes a refrigerant suction passage 27 connected to the accumulator 70. The refrigerant sucked from the accumulator 70 and flowing through the refrigerant suction pipe 27 is discharged to the low pressure chamber of the compression chamber 211. The refrigerant discharged into the low-pressure chamber of the compression chamber 211 is moved to the high-pressure chamber side and compressed by the above-described operation of the rotor 23 and the vane 24. Subsequently, the refrigerant compressed in the high-pressure chamber of the compression chamber 211 is discharged from the discharge port 261 toward the container 30 through a flow path (not shown) in the housing 26 a.
Next, the refrigerant suction passage 27 will be described in detail with reference to fig. 3. Here, fig. 3(a) is a horizontal sectional view of the rotary compression mechanism 20 (a sectional view of the rotary compression mechanism 20 taken along the line a-a' in fig. 1). Fig. 3B is a view of the refrigerant suction passage 27 as viewed from the compression chamber 211 side (a view shown by arrow B in fig. 3 a). Here, the refrigerant suction passage 27 shown in fig. 3(b) has an opening 272 having a rectangular cross section, but the cross-sectional shape of the opening 272 (the opening end 273) is not limited thereto.
As shown in fig. 3(a), the refrigerant suction passage 27 includes a widened portion 271 disposed radially outside the cylinder 21, and an opening 272 extending from the widened portion 271 toward the compression chamber 211. The widened portion 271 is a portion connected to the refrigerant discharge tube of the accumulator 70. The refrigerant supplied from the accumulator 70 is introduced into the widened portion 271 of the cylinder 21. The widening 271 of the present embodiment is a flow path having a circular cross section as shown in fig. 3 (b). However, it is not limited thereto.
The opening 272 is connected to the compression chamber 211 via an open end 273 facing the compression chamber 211. As shown in the drawing, the opening 272 of the present embodiment is directly joined to the widened portion 271, but is not limited thereto. That is, another pipeline portion may be interposed between the widened portion 271 and the opening portion 272.
As shown in fig. 3(a), the widened portion 271 of the present embodiment does not communicate with the compression chamber 211, but terminates at a predetermined position in the cylinder 21 (although this is not particularly limited, the termination position of the widened portion 271 includes a position communicating with the opening 272, a position before the compression chamber, and the like). Therefore, the refrigerant flowing from the accumulator 70 (outside the cylinder 21) into the widened portion 271 reaches the opening portion 272. The refrigerant that has reached the opening 272 passes through the opening end 273 of the opening 272 and is discharged into the compression chamber 211 (see fig. 2 for an example of the path of the refrigerant in the refrigerant suction passage 27).
As shown in fig. 3b, the width W2 of the opening 272 (the width of the opening end 273 in the present embodiment) is smaller than the width of the widened portion 271 (for example, the maximum width W1 of the widened portion 271). The vertical cross-sectional area of the opening 272 (the opening area S2 shown in fig. 3 (b); the area of the opening end 273 in the present embodiment) is equal to or greater than the vertical cross-sectional area S1 of the widened portion 271. The vertical cross-sectional area S1 of the widened portion 271 of the present embodiment is, for example, a cross-sectional area obtained by vertically cutting the widened portion 271 so as to include a portion having the maximum width W1.
By configuring the refrigerant suction passage 27 as described above, the refrigerant flows into the widened portion 271 which is wider than the refrigerant suction passage of the conventional configuration, and therefore, the resistance of the refrigerant flowing through the widened portion 271 can be reduced as compared with the conventional configuration. Further, an opening 272 narrower than the widened portion 271 is connected to the compression chamber 211. That is, in the present embodiment, the portion closed by the contact of the roller 23 is the opening 272 (open end 273). Therefore, even if the maximum width of the refrigerant suction passage 27 is increased by the amount of the widening 271, the time for which the refrigerant suction pipe 27 is closed by the roller 23 does not increase as compared with the conventional structure. As a result, the refrigerant compression in the compression chamber 211 can be started at the same timing as in the conventional rotary compression mechanism.
The cross-sectional area of the opening 272 is equal to or larger than the vertical cross-sectional area of the widened portion 271. Therefore, the flow velocity changes of the refrigerant flowing through the widened portion 271 and the refrigerant flowing through the opening 272 can be minimized. Thus, even if the refrigerant is caused to flow through the widened portion 271 and the opening 272 having different widths, the energy loss of the refrigerant flowing through the refrigerant suction passage 27 can be reduced as much as possible, and the refrigerant compression efficiency can be improved.
[ modified example of the first embodiment ]
Next, a modification of the first embodiment will be described with reference to fig. 4. Here, fig. 4 is a horizontal cross-sectional view of the rotary compression mechanism 20 according to the modification of the first embodiment taken along the line a-a' of fig. 1. The difference between the first embodiment and the present modification is the joint between the widened portion 271 and the opening 272 of the refrigerant suction passage 27.
More specifically, in the case of the modification shown in fig. 4, in a plan view of the cylinder 21, both (the widened portion 271 and the opening 272) are joined so that the longitudinal direction L1 of the widened portion 271 and the longitudinal direction L2 of the opening 272 form an angle θ 1. Therefore, by appropriately adjusting the angle θ 1 formed between the longitudinal direction L1 of the widened portion 271 and the longitudinal direction L2 of the opening 272, even if the widened portion 271 is provided in the refrigerant suction passage 27, the refrigerant suction passage 27 can be formed in a region that does not interfere with other portions. This can further reduce the resistance to the refrigerant flowing through the widened portion 271 without limiting the maximum width of the widened portion 271.
[ second embodiment ]
Next, a rotary compressor 1' according to a second embodiment of the present invention will be described with reference to fig. 5 and 6. Here, fig. 5 is a vertical sectional view of the rotary compressor 1' of the second embodiment. Fig. 6(a) is a horizontal cross-sectional view of the rotary compression mechanism 20 ' of the second embodiment taken along the line C-C ' in fig. 5, and fig. 6(b) is a view of the rotary compression mechanism 20 ' as viewed from the arrow D in fig. 6 (a).
As shown in fig. 5, the rotary compressor 1' according to the second embodiment is a so-called double-cylinder type rotary compressor, and includes a first cylinder 21a and a second cylinder 21b which are provided in series in the height direction. As in the first embodiment, the first cylinder 21a is provided with a first refrigerant suction passage 27a having a first widening 271a and a first opening 272 a.
As shown in fig. 5 and 6(a), the first opening 272a extends from the first widened portion 271a toward the first compression chamber 211 a. Further, the first opening portion 272a is connected to the first compression chamber 211a in the first cylinder 21a via a first opening end 273a facing the first compression chamber 211 a. However, another pipe portion may be interposed between the first widening portion 271a and the first opening portion 272 a.
In addition, similarly to the first cylinder 21a, the second cylinder 21b is provided with a second refrigerant suction passage 27b having a second widening portion 271b and a second opening portion 272 b. As shown in fig. 5 and 6(a), the second opening 272b extends from the second widened portion 271b toward the second compression chamber 211 b. Further, the second opening portion 272b is connected to the second compression chamber 211b in the second cylinder 21b via a second opening end 273b facing the second compression chamber 211 b. However, another pipe portion may be interposed between the second widening portion 271b and the second opening portion 272 b.
Here, as shown in fig. 6(a), the first refrigerant suction passage 27a and the second refrigerant suction passage 27b are arranged apart from each other at an angle θ 2 in the cylinder circumferential direction in a plan view of the first cylinder 21a (the second cylinder 21 b). At this time, as shown in fig. 6(b), the first widened portion 271a and the first opening portion 272a of the first refrigerant suction passage 27a, and the second widened portion 271b and the second opening portion 272b of the second refrigerant suction passage 27b are arranged at a predetermined distance in the circumferential direction of the rotary compression mechanism 20'. As a result, the strength of the container 30 (container body 31) in the rotary compressor 1' can be suppressed from being reduced.
The first opening 272a (first opening end 273a) and the second opening 272b (second opening end 273b) shown in fig. 6(b) are channels having a rectangular cross section, but may have other cross-sectional shapes.
The first refrigerant suction passage 27a shown in fig. 6(a) is a straight passage, but the form of the first refrigerant suction passage 27a is not limited to this. As another example of the first refrigerant suction passage 27a, there is a modified example of the first embodiment in which the longitudinal direction of the first widened portion 271a and the longitudinal direction of the first opening 272a form a predetermined angle and are curved at the boundary between the first widened portion 271a and the first opening 272 a. However, it is not limited thereto.
The second refrigerant suction passage 27b shown in fig. 6(a) is a straight passage, but the form of the second refrigerant suction passage 27b is not limited to this. As another example of the second refrigerant suction passage 27b, there is a modified example of the first embodiment in which the longitudinal direction of the second widening 271b and the longitudinal direction of the second opening 272b form a predetermined angle and the joint between the second widening 271b and the second opening 272b is curved at the boundary. However, it is not limited thereto.
The embodiments of the present invention are explained in detail. However, the above description is for the purpose of facilitating understanding of the present invention, and is not intended to limit the present invention. The present invention may include embodiments modified or improved from the above-described embodiments without departing from the gist thereof. Further, equivalents thereof are included in the present invention.
Industrial applicability
The rotary compressor of the present invention is used for, for example, household and commercial air conditioners. However, the use thereof is not limited thereto.
Claims (3)
1. A rotary compressor comprising an electric portion and a rotary compression mechanism portion driven by the electric portion,
the rotary compression mechanism includes a cylinder having a refrigerant suction passage,
a widened portion and an opening portion facing a compression chamber of the cylinder are formed in the refrigerant suction passage,
the width of the opening portion is narrower than the width of the widened portion,
the vertical cross-sectional area of the opening is the same as or larger than the vertical cross-sectional area of the widened portion.
2. The rotary compressor of claim 1,
in a plan view of the cylinder, a longitudinal direction of the widened portion and a longitudinal direction of the opening portion form a predetermined angle.
3. The rotary compressor of claim 1 or 2,
two or more of the cylinders are provided in succession in the height direction,
the refrigerant suction passage formed in one cylinder and the refrigerant suction passage formed in the other cylinder of the two or more cylinders are arranged apart from each other at a predetermined angle in a plan view of the cylinders.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020149872A JP2022044311A (en) | 2020-09-07 | 2020-09-07 | Rotary compressor |
| JP2020-149872 | 2020-09-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114151339A true CN114151339A (en) | 2022-03-08 |
Family
ID=80462179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011475963.9A Pending CN114151339A (en) | 2020-09-07 | 2020-12-14 | Rotary compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2022044311A (en) |
| CN (1) | CN114151339A (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109642576A (en) * | 2016-11-09 | 2019-04-16 | 富士通将军股份有限公司 | Rotary compressor |
| CN110418892A (en) * | 2017-03-17 | 2019-11-05 | 大金工业株式会社 | Rotary compressor |
-
2020
- 2020-09-07 JP JP2020149872A patent/JP2022044311A/en active Pending
- 2020-12-14 CN CN202011475963.9A patent/CN114151339A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109642576A (en) * | 2016-11-09 | 2019-04-16 | 富士通将军股份有限公司 | Rotary compressor |
| CN110418892A (en) * | 2017-03-17 | 2019-11-05 | 大金工业株式会社 | Rotary compressor |
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| Publication number | Publication date |
|---|---|
| JP2022044311A (en) | 2022-03-17 |
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