A rotary compressor includes a cylinder that is coupled to an inner space of a casing and that defines a compression space, a first bearing and a second bearing located at upper and lower sides of the cylinder, a roller disposed eccentrically with respect to an inner circumferential surface of the cylinder to vary a volume of the compression space based on rotation, and a vane inserted into the roller to rotate together with the roller, and drawn out toward the inner circumferential surface of the cylinder during the rotation of the roller to partition the compression space into a plurality of compression chambers. A suction passage communicating with the compression space is defined in the first bearing or the second bearing, and a suction port communicating between the suction passage and the compression space is defined on a side surface of the cylinder.
|
1. A rotary compressor, comprising:
a casing that defines an inner space;
a suction pipe that communicates with the inner space of the casing;
a cylinder located in the inner space of the casing and coupled to the casing, the cylinder defining at least a portion of a compression space by an inner circumferential surface of the cylinder;
a first bearing located at an upper side of the cylinder;
a second bearing located at a lower side of the cylinder, the first and second bearings defining the compression space together with the cylinder;
a roller that is located at an eccentric position in the compression space and that is offset toward the inner circumferential surface of the cylinder, the roller being configured to vary a volume of the compression space based on during rotation of the roller with respect to the cylinder; and
a vane that is located in the roller, that is configured to rotate with respect to the cylinder based on during rotation of the roller, and that is configured to, based on during rotation of the roller, protrude toward and retract from the inner circumferential surface of the cylinder, the vane partitioning the compression space into a plurality of compression chambers,
wherein the first bearing or the second bearing defines a suction passage that communicates with the compression space,
wherein the cylinder defines a suction port that is located at a side of the cylinder and that enables communication between the suction passage and the compression space,
wherein the rotary compressor further comprises a suction guide pipe located between the suction passage and the suction pipe, the suction guide pipe comprising a first end configured to connect to the suction pipe and a second end configured to correspond to the suction passage, and
wherein the second end of the suction guide pipe comprises:
an expansion portion having an inner diameter greater than an inner diameter of the suction passage, and
a sealing portion that has a flange-shape and extends from an outer circumferential surface of the expansion portion suction guide pipe.
2. The rotary compressor of
3. The rotary compressor of
4. The rotary compressor of
5. The rotary compressor of
6. The rotary compressor of
wherein the electric motor is coupled to the roller and connected to a rotation shaft that passes through the casing.
7. The rotary compressor of
a main passage portion; and
a sub-passage portion that extends from the main passage portion in a direction opposite to a rotational direction of the roller.
8. The rotary compressor of
wherein a circumferential length of the sub-passage portion is greater than the radial width of the sub-passage portion.
9. The rotary compressor of
0. 10. The rotary compressor of
wherein the sealing portion extends from an outer circumferential surface of the expansion portion.
0. 11. The rotary compressor of
wherein a radial width of the sealing portion is greater than or equal to the predetermined distance between the suction guide pipe and the suction passage.
0. 12. The rotary compressor of
wherein the sealing portion extends from an outer circumferential surface of the expansion portion.
0. 13. The rotary compressor of
wherein a radial width of the sealing portion is greater than or equal to the predetermined distance between the suction guide pipe and the suction passage.
0. 14. The rotary compressor of
|
|||||||||||||||||||
9 5.
On the other hand, a plurality of discharge ports 335a, 33b are formed along a compression path (compression advancing direction). For the sake of convenience, between the plurality of discharge ports 335a, 335b, a discharge port positioned on the upstream side with respect to the compression path is referred to as a sub-discharge port (or a first discharge port) 335a, and a discharge port positioned on the downstream side as a main discharge port (or a second discharge port) 335b.
However, the sub-discharge port is not necessarily required, but may be selectively formed as the need arises. For example, when the inner circumferential surface 331 of the cylinder 330 has a longer compression period as will be described later to appropriately reduce the over-compression of refrigerant as described in the present embodiment, the sub-discharge port may not be formed. However, in order to minimize the over-compression amount of the compressed refrigerant, the sub-discharge port 335a as in the related art may be formed on a front side of the main discharge port 335b, that is, on an upstream side, compared to the main discharge port 335b with respect to the compression advancing direction.
Meanwhile, the foregoing roller 340 is rotatably provided in the compression space 332 of the cylinder 330. The outer circumferential surface of the roller 340 is formed in a circular shape, and the rotation shaft 250 is integrally coupled to the center of the roller 340. As a result, the roller 340 has a center corresponding to an axial center of the rotation shaft 250, and rotates together with the rotation shaft 250 about the center (Or) of the roller.
Moreover, the center (Or) of the roller 340 is eccentric with respect to the center (Oc) of the cylinder 33, that is, the center of the inner space of the cylinder 330 such that one side of the outer circumferential surface 341 of the roller 340 is substantially in contact with the inner circumferential surface 341 of the cylinder 330. Here, when a point of the cylinder 330 substantially in contact with the roller 340 is referred to as a contact point (P), the contact point (P) may be a position where the first center line (L1) passing through the center of the cylinder 330 corresponds to a short axis of an elliptic curve constituting the inner circumferential surface 331 of the cylinder 330.
Furthermore, the roller 340 has a vane slot 342 formed at appropriate positions along a circumferential direction on the outer circumferential surface 341 and a back pressure hole 343 configured to allow oil (or refrigerant) to flow thereinto to press each vane 351, 352, 353 in the direction of the inner circumferential surface of the cylinder 330 at an inner end of each vane slot 342.
Upper and lower back pressure chambers (C1, C2) may be respectively formed on upper and lower sides of the back pressure hole 343 to supply oil to the back pressure hole 343.
The back pressure chambers (C1, C2) are formed by the upper and lower sides of the roller 340 and the corresponding outer circumferential surfaces of the first and second bearings 310, 320 and the rotation shaft 250, respectively.
Furthermore, the back pressure chambers (C1, C2) may independently communicate with the second oil passage 252 of the rotation shaft 250, respectively, but a plurality of back pressure holes 343 may be formed together to communicate with the second oil passage 252 through one back pressure chamber (C1, C2).
When a vane closest to the contact point (P) with respect to the compression advancing direction is referred to as a first vane 351, and subsequently referred to as a second vane 352 and a third vane 353, respectively, the vanes 351, 352, 353 are spaced apart from each other by the same circumferential angle between the first vane 351 and the second vane 351, between the second vane 352 and the third vane 353, and between the third vane 353 and the first vane 351.
Therefore, when the compression chamber formed by the first vane 351 and the second vane 352 is referred to as a first compression chamber 333a, the compression chamber formed by the second vane 352 and the third vane 353 as a second compression chamber 333b, and the compression chamber formed by the third vane 353 and the first vane 351 as a third compression chamber 333c, all the compression chambers 333a, 333b, 333c have the same volume at the same crank angle.
The vanes 351, 352, 353 are formed in a substantially rectangular parallelepiped shape. Here, between both lengthwise ends of the vane, a surface of the vane facing the inner circumferential surface 331 of the cylinder 330 is referred to as a sealing surface 355a of the vane, and a surface opposite to the back pressure hole 343 is referred to as a back pressure surface 355b.
The sealing surface 355a of the vanes 351, 352, 353 may be formed in a curved shape to be in line contact with the inner circumferential surface 331 of the cylinder 330, and the back pressure surface 355b of the vanes 351, 352, 353 may be formed to be flat to be inserted into the back pressure hole 343 so as to receive a back pressure evenly.
In the transverse open type vane rotary compressor provided with a hybrid cylinder as described above, when power is applied to an electric motor unit (not shown) provided outside the casing 100 and the electric motor unit is driven, a rotational force of the electric motor unit is transmitted to the rotation shaft 250 by the magnetic clutch 400 coupled to the electric motor unit through a drive pulley, and the rotational force is transmitted to the roller 340 through the rotation shaft 250 to rotate the roller 340 together with the rotation shaft 250.
Then, the vanes 351, 352, 353 are drawn out from the roller 340 by a centrifugal force generated by the rotation of the roller 340 and a back pressure formed on the first back pressure surface 355b of the vanes 351, 352, 353 to allow the sealing surface 355b of the vanes 351, 352, 353 to be brought into contact with the inner circumferential surface 331 of the cylinder 330.
Then, the compression space 332 of the cylinder 330 forms the compression chambers 333a, 333b, 333c as many as the number of the vanes 351,352, 353 by the plurality of vanes 351,352, 353, and each of the compression chambers 333a, 333b, 333c varies in volume by the shape of the inner circumferential surface 331 of the cylinder 330 and the eccentricity of the roller 340 while moving along the rotation of the roller 340, and refrigerant filled into each of the compression chambers 333a, 333b, 333c repeats a series of processes of sucking, compressing and discharging the refrigerant while moving along the roller 340 and the vanes 351, 352, 353.
It will be described in more detail as follows.
In other words, when the compression unit 300 is operated by the electric motor unit, the refrigerant is sucked into the suction space 111 of the casing 100 through the suction pipe 115, and when based on the first compression chamber 333a, a volume of the first compression chamber 333a is continuously increased until the first vane 351 passes through the suction port 334 and the second vane 352 reaches the suction completion point to allow the refrigerant to continuously flow into the first compression chamber 333a through the suction passage 315 and the suction port 334.
Next, when the second vane 352 reaches the suction completion point (or compression start angle), the first compression chamber 333a will be in a sealing state to move together with the roller 340 in a discharge port direction. During the process, while the volume of the first compression chamber 333a is continuously reduced, the refrigerant in the first compression chamber 333a is gradually compressed.
Next, in a state where the first vane 351 passes through the first discharge port 335a and the second vane 352 does not reach the first discharge port 335a, the first discharge valve 336a is open by a pressure of the first compression chamber 333a while the first compression chamber 333a is communicated with the first discharge port 335a. Then, a part of the refrigerant in the first compression chamber 333a is discharged into the discharge space 112 of the casing 100 through the first discharge port 335a to reduce the pressure of the first compression chamber 333a to a predetermined pressure. Of course, in the absence of the first discharge port 335a, the refrigerant of the first compression chamber 333a is further moved toward the second discharge port 335b, which is a main discharge port, without being discharged.
Next, when the first vane 351 passes through the second discharge port 335b and the second vane 352 reaches the discharge start angle, the refrigerant of the first compression chamber 333a is discharged into the discharge space 112 of the casing 100 through the second discharge port 336b while the second discharge valve 336b is open by the pressure of the first compression chamber 333a.
The above-described series of processes are similarly repeated in the second compression chamber 333b between the second vane 352 and the third vane 353, and in the third compression chamber 333c between the third vane 353 and the first vane 351, and the vane rotary compressor according to the present embodiment performs three discharges per revolution (six discharges including discharge from the first discharge port) in the roller 340.
On the other hand, in case of a low pressure type in which the suction pipe communicates with the inner space of the casing as in the present embodiment, when the suction passage 315 is formed in the first bearing 310 and the suction port 334 is formed on the inner circumferential surface 331 of the cylinder 330, an area of the suction flow path through which the refrigerant is sucked into the compression chamber 332 may be maximized, thereby preventing suction loss.
In other words, in the related art, as the suction port is formed in the first bearing, an area of the suction port is greatly affected by a gap between an inner circumferential surface of the cylinder and an outer circumferential surface of the roller. As a result, as described above, there is a limit in increasing the area of the suction port, and there has been a limitation in the compression performance due to the suction loss.
However, when the suction port 334 corresponding to an outlet of the suction flow path is formed on the inner circumferential surface 331 of the cylinder 330 as in this embodiment, an area of the suction port 334 is not affected by a gap between the inner circumferential surface 331 of the cylinder 330 and the outer circumferential surface 341 of the roller 340 but affected by a height of the cylinder 330. Therefore, it may be possible to maximize the area of the suction port 334, namely, within a range that is smaller than the height of the cylinder 330 (of course, the sealing area should be taken into consideration). Accordingly, the area of the suction passage 315 corresponding to the inlet of the suction flow path and formed in the first bearing 310 may not be affected by a gap between the inner circumferential surface 331 of the cylinder 330 and the outer circumferential surface 341 of the roller 340, and thus enlarged as much as the area of the suction port 334. Therefore, the area of the suction flow path may be maximized to improve the performance of the compressor while reducing the suction loss.
Meanwhile, when the suction pipe 115 communicates with the inner space of the casing 100 as in the present embodiment, the refrigerant sucked into an inner space of the casing 100 through the suction pipe 115 circulates the inner space of the casing 100, (i.e., suction space) 111, and then is guided to the suction passage 315. Therefore, the flow path loss to the refrigerant is generated, which causes the performance of the compressor to deteriorate.
As a result, as shown in
This is because when the both ends of the suction guide pipe 130 are fixedly connected to the suction pipe 115 and the suction passage (or first or second bearing) 315, respectively, the suction guide pipe 130 may be damaged by the vibration of the compressor caused by the outside or inside of the compressor casing 100. Therefore, it may be preferably that at least one of the both ends of the suction guide pipe 130 is slightly spaced from the corresponding member in terms of reliability. For reference,
Furthermore, the suction guide pipe may be formed with an expansion portion 131 and a sealing portion 132 at an end spaced apart from the suction passage. For the expansion portion, when an inner diameter (or cross-sectional area) of the suction passage 315 is larger than that of the suction guide pipe (or suction pipe) 130, a diameter of the suction guide pipe 130 may be formed to correspond to that of the suction pipe 115 while the expansion portion 131 is formed at an end portion corresponding to the suction passage 315 to smoothly guide the refrigerant to the suction passage 315.
In addition, when an end portion of the suction guide pipe 130 is separated from the suction passage 315 as described above, a part of the refrigerant passing through the suction guide pipe 130 may leak through an open gap (t), and thus a flange-shaped sealing portion 132 may be formed to minimize the leakage of the refrigerant into the gap (t). For example, a radial width of the flange-shaped sealing portion 132 may be greater than or equal to the gap (t), as shown in FIG. 9A. As a result, the refrigerant may be smoothly guided to the suction passage.
Furthermore, the both ends of the suction guide pipe 130 may be spaced apart from either one of the suction pipe 115 or the suction passage 315 as described above. However, as shown in
Of course, in this case, the entire suction guide pipe 130 may be formed of a flexible material without having an additional elastic portion 123. In addition, in those cases, either one of the both ends of the suction guide pipe 130 may be spaced apart. Reference numeral 134 in the drawing is a fixed portion.
As described above, in the low-pressure vane rotary compressor in which the suction space 111 of the casing 100 is filled with a suction pressure, when the suction pipe 115 and the suction passage 315 are connected by the suction guide pipe 130, refrigerant sucked through the suction pipe 115 is guided directly to the suction passage 315 along the suction guide pipe 130.
Accordingly, since most of the refrigerant is directly supplied to the compression chamber without passing through the suction space 111 of the casing 100, flow loss may be minimized to further improve the performance of the compressor.
Meanwhile, another embodiment of the rotary compressor according to the present disclosure will be described as follows.
In other words, in the foregoing embodiment, an example is shown in which the electric motor unit is separately provided outside the casing and applied to an open type vane rotary compressor for transmitting electric power to the compression unit provided inside the casing, but the present disclosure may be similarly applicable to a closed type vane rotary compressor provided together with an electric motor unit and a compression unit.
For example, as shown in
In this case, the compression unit 300 may be configured in the same manner as the above-described embodiment. In particular, the suction passage 315 is formed in the first bearing 310 forming the main bearing, and the suction port 334 is formed in the cylinder 330, respectively, similarly to the foregoing embodiment. Accordingly, the detailed description thereof will be omitted.
However, in this embodiment, the electric motor unit 200 serves to provide power for compressing refrigerant, and ncludes a stator 210 and a rotor 220.
The stator 210 is fixedly provided inside the casing 100 and may be mounted on an inner circumferential surface of the casing 100 by a method such as shrink-fitting.
The rotor 220 is spaced apart from the stator 210 and located inside the stator 210. The rotation shaft 250 is pressed into the center of the rotor 220, and the roller 340 constituting the compression unit 300 is integrally formed or assembled at an end portion of the rotation shaft 250. Accordingly, when power is applied to the stator 210, a force generated by a magnetic field formed between the stator 210 and the rotor 220 causes the rotor 220 to rotate.
As the rotor 220 rotates, a rotational force of the electric motor unit is transmitted to the compression unit 300 by the rotation shaft 250 coupled to the center of the rotor 220.
As described above, when both the electric motor unit 200 and the compression unit 300 are provided inside the casing 100, the suction passage 315 is formed in the first bearing 310, and the suction port 334 in a side surface of the cylinder 330, respectively. Accordingly, it may be possible to secure a large area of the suction passage 315, thereby reducing suction loss to the minimum
Moreover, even in this case, a suction guide pipe (not shown) (refer to
On the other hand, as shown in
When the suction pipe 115 is installed on the opposite side of the compression unit 300 with the electric motor unit 200 therebetween, the suction passage 315 and the suction ports 334a, 334b may be formed in the same manner as the above-described embodiment. Accordingly, the detailed description thereof will be omitted.
However, as the suction pipe 115 is provided on the opposite side of the compression unit 300 with the electric motor unit 200 therebetween, cold suction refrigerant being sucked through the suction pipe 115 may cool the electronic motor unit 200, thereby enhancing the efficiency of the electric motor unit.
On the other hand, though the present disclosure has been described with reference to an example applied to a transverse type compressor, the same may be applicable to the case of a longitudinal type.
Shin, Jinung, Noh, Kiyoul, Moon, Seokhwan
| Patent | Priority | Assignee | Title |
| Patent | Priority | Assignee | Title |
| 3744942, | |||
| 4619595, | Apr 15 1983 | Hitachi, Ltd.; Hitachi Automotive Engineering Co., Ltd. | Capacity control device for compressor |
| 4702684, | Oct 07 1981 | Hitachi, Ltd. | Slide vane type compressor with increased suction part-cross-sectional area |
| 20130101412, | |||
| 20140069139, | |||
| 20160153452, | |||
| 20160241092, | |||
| 20180187680, | |||
| EP2520803, | |||
| EP2784325, | |||
| KR1020060048898, | |||
| KR20000001097, | |||
| KR20060048898, |
| Executed on | Assignor | Assignee | Conveyance | Frame | Reel | Doc |
| Apr 14 2022 | LG Electronics Inc. | (assignment on the face of the patent) | / |
| Date | Maintenance Fee Events |
| Apr 14 2022 | BIG: Entity status set to Undiscounted (note the period is included in the code). |
| Sep 11 2024 | M1551: Payment of Maintenance Fee, 4th Year, Large Entity. |
| Date | Maintenance Schedule |
| Jun 25 2027 | 4 years fee payment window open |
| Dec 25 2027 | 6 months grace period start (w surcharge) |
| Jun 25 2028 | patent expiry (for year 4) |
| Jun 25 2030 | 2 years to revive unintentionally abandoned end. (for year 4) |
| Jun 25 2031 | 8 years fee payment window open |
| Dec 25 2031 | 6 months grace period start (w surcharge) |
| Jun 25 2032 | patent expiry (for year 8) |
| Jun 25 2034 | 2 years to revive unintentionally abandoned end. (for year 8) |
| Jun 25 2035 | 12 years fee payment window open |
| Dec 25 2035 | 6 months grace period start (w surcharge) |
| Jun 25 2036 | patent expiry (for year 12) |
| Jun 25 2038 | 2 years to revive unintentionally abandoned end. (for year 12) |