CN111255807A - Bearing for rotary compressor and rotary compressor - Google Patents
Bearing for rotary compressor and rotary compressor Download PDFInfo
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- CN111255807A CN111255807A CN201811456791.3A CN201811456791A CN111255807A CN 111255807 A CN111255807 A CN 111255807A CN 201811456791 A CN201811456791 A CN 201811456791A CN 111255807 A CN111255807 A CN 111255807A
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- bearing
- rotary compressor
- hole
- point
- contour line
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
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- 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
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a bearing for a rotary compressor and the rotary compressor, wherein an exhaust valve seat of the bearing is internally provided with a mounting cavity and a flow guide cavity, the bottom wall of the flow guide cavity is constructed into a flow guide inclined plane, a connecting hole is formed on the bearing, the connecting hole which is closest to an exhaust hole and is positioned on one side of the exhaust hole far away from the mounting part is a target connecting hole, and the diameter of the target connecting hole on the outer surface of the bearing is d1The connecting line of the center of the target connecting hole and the center of the exhaust hole is a target connecting line, and the length of the target connecting line is L1. The point on the guide inclined plane farthest from the installation part is a far-end point of the guide cavity, the far-end point is located on one side, close to the central axis of the bearing, of the target connecting line, and the distance between the far-end point and the center of the exhaust hole is L2，L2And L1Satisfies the relationship: l is2≥L1‑d1. Bearing for rotary compressor according to the present inventionThe structure is simple, the impact of air flow on the inner wall of the silencer is reduced, and the performance and the sound quality of the rotary compressor are improved.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a bearing for a rotary compressor and the rotary compressor.
Background
The rotary compressor is a device for compressing low-temperature low-pressure gas into high-temperature high-pressure gas, and the gas flow discharged from a compression cavity sequentially needs to pass through an exhaust port, a lift limiter and a silencer and finally passes through a main gas accommodating cavity of the compressor. In the process, the air flow speed is very high, the local highest flow speed can reach about 30-50 m/s, local eddy loss is very serious due to narrow space, and the air flow impacting the wall surface is the main reason of eddy loss and air flow noise formed in the flowing process. In the related art, the rotary compressor has poor performance and large operation noise.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, the bearing for the rotary compressor is simple in structure, and is beneficial to reducing the impact of airflow on the inner wall of the silencer and improving the performance and sound quality of the rotary compressor.
The invention also provides a rotary compressor with the bearing.
According to the bearing for the rotary compressor in the embodiment of the first aspect of the present invention, the bearing is formed with a discharge valve seat, a mounting cavity and a diversion cavity are defined in the discharge valve seat, the mounting cavity is used for mounting a discharge valve and has a mounting portion and a discharge hole at two ends respectively, the diversion cavity is communicated with one side of the mounting cavity close to the discharge hole, and the bottom wall of the diversion cavity is configured as follows: a flow guide slope extending obliquely to an outer surface of the bearing in a direction away from the mounting portion; be formed with the connecting hole on the bearing, the connecting hole runs through the surface of bearing just is used for connecting the muffler, the connecting hole is a plurality of and follows the circumference interval distribution of bearing is a plurality of distance in the connecting hole exhaust hole is nearest, and is located keeping away from of exhaust hole one side of installation department the connecting hole is the target connecting hole, the target connecting hole is in aperture on the surface of bearing is d1The connecting line of the center of the target connecting hole and the center of the exhaust hole is a target connecting line, and the length of the target connecting line is L1(ii) a The point on the flow guide inclined plane, which is farthest away from the mounting part, is a far-end point of the flow guide cavity, and the far-end point is located in the middle of the target connecting line, which is close to the bearingOne side of the central axis, and the distance between the far end point and the center of the exhaust hole is L2Said L is2And said L1Satisfies the relationship: l is2≥L1-d1。
According to the bearing for the rotary compressor, the flow guide cavity communicated with the mounting cavity is defined in the exhaust valve seat of the bearing, the far end point of the flow guide cavity is positioned on one side of the target connecting line close to the central axis of the bearing, and the distance L between the far end point and the center of the exhaust hole is provided2Satisfies the following conditions: l is2≥L1-d1The flow guide cavity can directly guide the airflow to cross the part of the silencer corresponding to the target connecting hole in the process of guiding the airflow to flow, so that the impact of the airflow on the inner wall of the silencer is reduced, the flow loss of the airflow, such as the impact eddy loss and the friction loss of the airflow, is reduced, and the airflow noise is reduced; when the bearing is applied to the rotary compressor, the power consumption of the motor of the rotary compressor can be effectively reduced, the performance of the rotary compressor is improved, and meanwhile, the sound quality of the rotary compressor is improved.
According to some embodiments of the invention, the L2And said L1Further satisfying the relationship: l is2≥L1-d1/2。
According to some embodiments of the invention, the distal point is L away from the center of the target connection hole3Said L is3And d is as described1Satisfies the relationship: l is3≥d1/2+2mm。
According to some embodiments of the invention, the contour of the flow guiding cavity on the outer surface of the bearing comprises an inner contour and an outer contour, the outer contour being provided on a side of the inner contour facing away from the central axis of the bearing, both the inner contour and the outer contour extending from the distal end point in a direction towards the mounting cavity, the radial distance between the outer contour and the inner contour gradually decreasing in a direction from the mounting cavity to the distal end point.
According to some embodiments of the invention, the outer contour line is constructed as an involute.
According to some embodiments of the invention, the outer contour line has a first point and a second point, the first point being a point where the outer contour line intersects the mounting cavity, the second point being a point where a connecting line between the mounting portion and the exhaust hole intersects the outer contour line, the first point being located at a distance R from a center of the exhaust hole1The second point is away from the center of the exhaust hole by R2Said R is1And said R2Satisfies the relationship: r1＜R2＜L2。
According to some embodiments of the invention, the flow guiding bevel is a smooth curved surface.
According to some embodiments of the invention, the smooth curved surface is a streamlined curved surface.
According to some embodiments of the invention, the streamline curved surface comprises a first flow guiding surface and a second flow guiding surface which are sequentially connected in a direction from the exhaust hole to the far end point, an included angle between the first flow guiding surface and a preset surface is α, an included angle between the second flow guiding surface and the preset surface is β, the α and the β satisfy the relation that β is more than or equal to α, and 0.3 is more than or equal to sin α is more than or equal to 0.8, wherein the preset surface is a plane perpendicular to a central axis of the bearing.
The rotary compressor according to the second aspect embodiment of the present invention includes the bearing for the rotary compressor according to the above-described first aspect embodiment of the present invention.
According to the rotary compressor provided by the embodiment of the invention, by adopting the bearing, the power consumption of the motor of the rotary compressor is effectively reduced, the extra power input by the compressor is avoided to offset the extra loss of airflow, the performance of the rotary compressor is improved, the running noise of the rotary compressor is reduced, and the sound quality of the rotary compressor is improved.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic structural view of a bearing for a rotary compressor according to an embodiment of the present invention;
FIG. 2 is a schematic view of another angular configuration of the bearing shown in FIG. 1;
FIG. 3 is a schematic view of a further angular configuration of the bearing shown in FIG. 1;
FIG. 4 is a schematic view of a further angular configuration of the bearing shown in FIG. 1;
fig. 5 is a partial structural view of the bearing shown in fig. 4.
Reference numerals:
bearing 100, outer surface 100a of bearing, inner surface 100b of bearing,
An exhaust valve seat 1, a target connecting line 10,
A mounting cavity 11, a first end 110a, a second end 110b,
A diversion cavity 12, a streamline curved surface 120, a first diversion surface 120a, a second diversion surface 120b,
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
A bearing 100 for a rotary compressor according to an embodiment of the present invention will be described with reference to fig. 1 to 5.
As shown in fig. 1 to 5, according to a bearing 100 for a rotary compressor according to an embodiment of the present invention, a discharge valve seat 1 and a coupling hole 2 are formed on the bearing 100.
An installation cavity 11 and a diversion cavity 12 are defined in the exhaust valve seat 1, the installation cavity 11 is used for installing an exhaust valve (not shown in the figure), both ends of the installation cavity 11 are respectively provided with an installation part 111 and an exhaust hole 112, the diversion cavity 12 is communicated with one side of the installation cavity 11 close to the exhaust hole 112, and the bottom wall of the diversion cavity 12 is configured as follows: a guide slope 121 extending obliquely to the outer surface 100a of the bearing in a direction away from the mounting portion 111.
The connection holes 2 penetrate through the outer surface 100a of the bearing and the connection holes 2 are used for connecting a silencer, the connection holes 2 are multiple and the connection holes 2 are distributed at intervals along the circumferential direction of the bearing 100, and the connection hole 2 which is closest to the exhaust hole 112 and located on one side of the exhaust hole 112 far away from the mounting portion 111 is a target connection hole 21.
Wherein the target connection hole 21 has a hole diameter d on the outer surface 100a of the bearing1The connecting line between the center of the target connecting hole 21 and the center of the exhaust hole 112 is a target connecting line 10, and the length of the target connecting line 10 is L1The farthest point on the diversion inclined plane 121 from the mounting portion 111 is a distal end point P of the diversion cavity 12, the distal end point P is located on one side of the target connecting line 10 close to the central axis of the bearing 100, and the distance L between the distal end point P and the center of the exhaust hole 112 is equal to the distance L2，L2And L1Satisfies the relationship: l is2≥L1-d1。
For example, as shown in fig. 1 to 5, the exhaust valve seat 1 may be formed by a portion of an outer surface of the bearing 100 being recessed in an axial direction of the bearing 100, the mounting cavity 11 may have a first end 110a and a second end 110b that are oppositely disposed, the first end 110a and the second end 110b may be oppositely disposed in a length direction of the mounting cavity 11, the mounting portion 111 may be located at the first end 110a, the exhaust hole 112 may be located at the second end 110b, the guide cavity 12 communicates with the second end 110b of the mounting cavity 11, and the guide cavity 12 may communicate with the exhaust hole 112, and the air flow discharged from the exhaust hole 112 may flow under the guide of the guide slope 121; since the guide slope 121 extends obliquely to the outer surface 100a of the bearing in a direction away from the mounting portion 111, the guide slope 121 may guide the air flow to the upper side of the bearing 100. The distal end point P of the diversion inclined plane 121 may be a downstream end point of the diversion inclined plane 121 in the airflow flowing direction, and the distal end point P may be a point on the diversion inclined plane 121 farthest from the mounting portion 111 in the circumferential direction of the bearing 100.
The connecting holes 2 can be uniformly distributed along the circumferential direction of the bearing 100 at intervals, each connecting hole 2 penetrates through the outer surface 100a of the bearing, a silencer of the rotary compressor can be fixed on the bearing 100 by penetrating a fastener in the connecting hole 2, and a silencing cavity can be defined between the outer surface 100a of the bearing and the inner wall of the silencer; the closest distance between the target connection hole 21 and the exhaust hole 112 among the plurality of connection holes 2 may be the closest distance between the target connection hole 21 and the exhaust hole 112 in the circumferential direction of the bearing 100 among the plurality of connection holes 2, or the closest linear distance between the target connection hole 21 and the exhaust hole 112 among the plurality of connection holes 2.
Wherein d is1May be the diameter of the corresponding hole of the target connection hole 21 on the outer surface 100a of the bearing, and the target connection line 10 may be a projection of a line between the center of the target connection hole 21 and the center of the exhaust hole 112 on the cross-section of the bearing 100, L2May be the length of the projection of the line between the distal end point P and the center of the exhaust hole 112 on the cross section of the bearing 100, the length L of the target line 101And L2Satisfy L2≥L1-d1The distance between the far-end point P and the center of the exhaust hole 112 is larger, so that the far-end point P can conveniently cross the target connecting hole 21 in the direction far away from the exhaust hole 112, the flow guide cavity 12 can directly guide the airflow to cross the part of the silencer corresponding to the target connecting hole 21 in the process of guiding the airflow to flow, the impact of the airflow on the inner wall of the silencer is reduced, and thus the flow loss of the airflow, such as the impact eddy loss, the friction loss and the like of the airflow, and the airflow noise are reduced; when the bearing 100 is applied to the rotary compressor, the power consumption of the motor of the rotary compressor can be effectively reduced, the extra work input by the compressor is avoided to offset the extra flow loss of the air flow, the performance of the rotary compressor is improved, the running noise of the rotary compressor is reduced, and the sound quality of the rotary compressor is improved.
It will be appreciated that the distal point P is located near the central axis of the bearing 100 of the target line 10So that the distal end point P can be located at a side of the plurality of coupling holes 2 close to the central axis of the bearing 100 due to the length L of the target link 101And L2Satisfy L2≥L1-d1So that the position setting of the distal end point P has good flexibility, for example, the distal end point P may be located between the target connecting hole 21 and the connecting hole 21 adjacent thereto in the circumferential direction of the bearing 100, or the distal end point P may also be located between the connecting hole 21 adjacent to the target connecting hole 21 and the connecting hole 21 spaced one connecting hole 21 apart from the target connecting hole 21 in the circumferential direction of the bearing 100, but is not limited thereto.
Each connecting hole 2 can be a blind hole or a through hole, so that the target connecting hole 21 can be a blind hole or a through hole; when the coupling hole 2 is formed as a blind hole, the blind hole may be formed by recessing a portion of the outer surface of the bearing 100, and when the coupling hole 2 is formed as a through hole, the through hole may penetrate the outer surface 100a of the bearing and the inner surface 100b of the bearing. Of course, the attachment hole 2 may also be formed as a screw hole, the bearing 100 and the muffler may be fixedly attached by a screw-type attachment member such as a screw, and when the target attachment hole 21 is formed as a screw hole, d1May be the nominal diameter of the target attachment hole 21 on the outer surface 100a of the bearing.
Here, it should be noted that "the outer surface 100a of the bearing" may refer to a surface of the side of the bearing 100 far from the cylinder, that is, a surface of the side of the bearing 100 near the muffler, when the bearing 100 is used in the rotary compressor, and "the inner surface 100b of the bearing" may refer to a surface of the side of the bearing 100 near the cylinder, when the bearing 100 is used in the rotary compressor. The "bottom wall of the guide chamber 12" may refer to a side wall surface of the flow chamber 12 in the axial direction of the bearing 100, in other words, in the concave direction of the guide chamber 12, the top side of the guide chamber 12 is open and the bottom side of the guide chamber 12 is closed. "cross-section of the bearing 100" refers to a plane perpendicular to the axial direction of the bearing 100. In the description of the present invention, "a plurality" means two or more.
In addition, the diversion inclined plane 121 extends obliquely, and can direct the extending direction of the diversion inclined plane 121 to be oblique to the central axis of the bearing 100, that is, the included angle between the extending direction of the diversion inclined plane 121 and the central axis of the bearing 100 is not equal to 0 °. It can be understood that the extending direction of the diversion inclined plane 121 may be changed during the extending process of the diversion inclined plane 121, and it is only necessary to ensure that the extending direction of the diversion inclined plane 121 is inclined with respect to the central axis of the bearing 100.
According to the bearing 100 for the rotary compressor of the embodiment of the present invention, the guide chamber 12 communicating with the installation chamber 11 is defined in the discharge valve seat 1 of the bearing 100, and the distal end point P of the guide chamber 12 is located on one side of the target connecting line 10 close to the central axis of the bearing 100 and is spaced from the center of the discharge hole 112 by a distance L2Satisfies the following conditions: l is2≥L1-d1The flow guide cavity 12 can directly guide the airflow to cross the part of the silencer corresponding to the target connecting hole 21 in the process of guiding the airflow to flow, so that the impact of the airflow on the inner wall of the silencer is reduced, and the flow loss of the airflow, such as the impact vortex loss of the airflow, and the airflow noise are reduced; when the bearing 100 is applied to the rotary compressor, the power consumption of the motor of the rotary compressor can be effectively reduced, the performance of the rotary compressor is improved, and the sound quality of the rotary compressor is improved.
Further, L2And L1Further satisfying the relationship: l is2≥L1-d1And/2, thereby further facilitating the far end point P to cross the target connecting hole 21 in the direction far away from the exhaust hole 112, so that the diversion cavity 12 guides the air flow to cross the part of the silencer corresponding to the target connecting hole 21 and flow to the part of the silencing cavity corresponding to the position between the target connecting hole 21 and the adjacent connecting hole 2.
In a further embodiment of the invention, the distal point P is located at a distance L from the center of the target connection hole 213，L3And d1Satisfies the relationship: l is3≥d 12+2 mm. For example, as shown in FIGS. 1-5, L3May be on axis as a line connecting the distal point P and the center of the target exhaust aperture 112Length of projection, L, on cross section of bearing 1003The difference between the radii of the holes on the outer surface of the bearing 100 from the target connection hole 21 exceeds 2mm, thereby ensuring that the distance between the distal end point P and the target connection hole 21 is large when the bearing 100 is applied to the rotary compressor, so that there is a sufficient distance between the distal end point P and the inner wall of the muffler on the cross section of the bearing 100, further reducing the impact of the gas flow guided by the baffle chamber 12 on the inner wall of the muffler.
In some embodiments of the present invention, the contour line 122 of the flow guiding cavity 12 on the outer surface 100a of the bearing includes an inner contour line 1221 and an outer contour line 1222, the outer contour line 1222 is disposed on a side of the inner contour line 1221 away from the central axis of the bearing 100, the inner contour line 1221 and the outer contour line 1222 each extend from the distal end point P toward the mounting cavity 11, and the radial distance between the outer contour line 1222 and the inner contour line 1221 decreases gradually in a direction from the mounting cavity 11 to the distal end point P.
Here, it should be noted that "the contour line 122 of the guide cavity 12 on the outer surface 100a of the bearing" may guide the outer contour line 1222 of the projection of the guide cavity 12 on the cross section of the bearing 100.
In some alternative embodiments of the present invention, the outer contour line 1222 is formed as an involute curve, thereby facilitating the machining of the diversion cavity 12, and at the same time, the diversion cavity 12 can better guide the airflow to the distal point P, thereby ensuring the diversion effect of the diversion cavity 12.
Alternatively, in the example of fig. 1 to 5, the outer contour line 1222 has a first point a and a second point B, the first point a is a point where the outer contour line 1222 intersects the mounting cavity 11, the second point B is a point where a connecting line between the mounting portion 111 and the exhaust hole 112 intersects the outer contour line 1222, that is, the second point B is a point where a plane parallel to the axial direction of the bearing 100, where the connecting line between the center of the mounting portion 111 and the center of the exhaust hole 112 is located, intersects the outer contour line 1222, and the first point a is located at a distance R from the center of the exhaust hole 1121The second point B is spaced from the center of the exhaust hole 112 by a distance R2，R1And R2Satisfies the relationship: r1＜R2＜L2That is, the first point a, the second point B and the distal point P are all points on the outer contour line 1222And the first point a and the far end point P are end points of both ends of the outer contour line 1222, respectively, and the second point B is located between the first point a and the far end point P. Thus, by setting R1＜R2＜L2The forming of the diversion cavity 12 is facilitated, and meanwhile, the diversion cavity 12 can effectively and rapidly guide the airflow to the far-end point P, so that the impact of the airflow and the diversion inclined plane 121 is reduced.
It is understood that the outer contour line 1222 may be formed in a diverging curve in the flow direction of the air flow such that the distance between each point on the outer contour line 1222 and the center of the air discharge hole 112 gradually increases with the flow direction of the air flow.
Further, as shown in fig. 1 to 5, the contour line 122 may be formed substantially in a C shape, or a U shape, or a part of a C shape, or a part of a U shape, the inner contour line 1221 may be formed in a curved line, and an end of the inner contour line 1221 away from the mounting portion 111 extends to the distal end point P, and a distance between the inner contour line 1221 and the outer contour line 1222 in a radial direction of the bearing 100 is gradually reduced along a flow direction of the air flow in the baffle cavity 12, so that the contour line 122 is in a tapered state along a circumferential direction of the bearing 100, and a baffle effect of the baffle cavity 12 is ensured.
In some embodiments of the present invention, the diversion inclined plane 121 is a smooth curved surface, that is, the diversion inclined plane 121 may be formed as a smooth curved surface, so that the diversion cavity 12 may smoothly guide the airflow at the exhaust hole 112 to the distal end point P, further reducing the flow resistance of the airflow in the diversion cavity 12 to reduce the flow loss of the airflow.
Here, it should be noted that "curved surface" is referred to as "plane surface", that is, a single plane surface does not belong to a curved surface, but plane surfaces may be combined to form a curved surface, for example, two plane surfaces of different surfaces may be formed as a curved surface, or a plane surface may be formed as one curved surface together with a certain curved surface.
In some embodiments of the present invention, the smooth curved surface is a streamline curved surface 120, and at this time, the diversion cavity 12 may be formed with a streamline diversion cavity 12, so that resistance of the airflow flowing in the diversion cavity 12 is further effectively reduced, and flow loss of the airflow is further reduced.
Specifically, the streamline curved surface 120 includes a first flow guiding surface 120a and a second flow guiding surface 120b connected in sequence along a direction from the air discharge hole 112 to the distal end point P, an included angle between the first flow guiding surface 120a and a preset plane is α, an included angle between the second flow guiding surface 120b and the preset plane is β and β, which satisfy the relationship that β is greater than or equal to α, and 0.3 is greater than or equal to sin α and less than or equal to 0.8, wherein the preset plane is a plane perpendicular to a central axis of the bearing 100, for example, as shown in fig. 1-5, the first flow guiding surface 120a may be located upstream of the second flow guiding surface 120b in the direction of the flow of the air, that is, the air is discharged through the air discharge hole 112 and first guided to flow by the first flow guiding surface 120a, then the second flow guiding surface 120b guides the air to the distal end point P, the first flow guiding surface 120a and the second flow guiding surface 120b may be smoothly transitioned before the first flow guiding surface 120a second flow guiding surface 120a and the second air discharge hole 120b, wherein the preset plane is a cross-sectional plane of the bearing 100, an end point between the first flow guiding surface 120a and the second flow guiding surface 120a, and a second flow guiding surface is defined as an included angle between a line parallel to the second flow guiding surface, and a line, and a second flow guiding surface, and a second guide surface is defined by a reference line, and a predetermined line, and a reference line, a reference line is defined as an included angle between the second line, a predetermined axis, a line parallel to a line, a reference line, a line is defined by which is parallel to a line.
Because the included angle α between the first flow guiding surface 120a and the preset surface satisfies 0.3-sin α -0.8, in the process of guiding the airflow, on the premise that the first flow guiding surface 120a can effectively guide the high-speed airflow flowing out from the air outlet 112, the impact of the high-speed airflow on the flow guiding inclined surface 121 can be reduced, so as to further reduce the power consumption of the motor of the rotary compressor, further improve the performance of the rotary compressor, and further improve the sound quality of the rotary compressor, and when sin α is less than 0.3, the high-speed airflow cannot be tightly attached to the first flow guiding surface 120a, so that a low-pressure backflow vortex can be formed between the main flow airflow of the high-speed airflow and the first flow guiding surface 120a, the backflow vortex can cause additional vortex loss of the airflow, at this time, the input work of the rotary compressor can be increased, so that the COP performance of the rotary compressor is reduced, and when sin α is greater than 0.8, the high-speed airflow can directly impact the first flow guiding surface 120a, so that the COP performance of the rotary compressor can not be increased, and the COP of the rotary compressor can be reduced.
The included angle β between the second guiding surface 120b and the preset surface is greater than or equal to the included angle α between the first guiding surface 120a and the preset surface, so that the impact of the airflow on the inner wall of the silencer is further reduced under the guidance of the second guiding surface 120b, and meanwhile, the second guiding surface 120b can better guide the airflow to the far-end point P.
Certainly, the smooth curved surface may also be formed into other types of curved surfaces, at this time, the smooth curved surface may also include the first flow guiding surface 120a and the second flow guiding surface 120b, in the airflow flowing direction, the first flow guiding surface 120a may be located at the upstream of the second flow guiding surface 120b, an included angle α between the first flow guiding surface 120a and the preset surface and an included angle β between the second flow guiding surface 120b and the preset surface respectively satisfy β is greater than or equal to α, and sin α is greater than or equal to 0.3 and less than or equal to 0.8, and the impact of the airflow on the flow guiding inclined surface 121, the impact of the airflow on the inner wall of the muffler may also be reduced, and the performance and sound quality of the rotary compressor may be.
At this time, the first flow guiding surface 120a may be formed as a plane or a smooth curved surface, and the second flow guiding surface 120b may be formed as a plane or a smooth curved surface, that is, the first flow guiding surface 120a is formed as a plane, and the second flow guiding surface 120b is formed as a plane, at this time, an included angle between the first flow guiding surface 120a and the preset surface is an included angle between the two planes, and an included angle between the second flow guiding surface 120b and the preset surface is an included angle between the two planes, or the first flow guiding surface 120a is formed as a plane, and the second flow guiding surface 120b is formed as a smooth curved surface, at this time, an included angle between the first flow guiding surface 120a and the preset surface is an included angle between the two planes, and an included angle between the second flow guiding surface 120b and the preset surface is an included angle between the second flow guiding line and the preset surface, or the first flow guiding surface 120a is formed as a smooth curved surface, and the second flow guiding surface 120b is formed as a plane, and at this time, and an included angle between the The included angle and the included angle between the second guiding surface 120b and the preset surface are the included angle between the two planes, or the first guiding surface 120a is formed into a smooth curved surface and the second guiding surface 120b is formed into a smooth curved surface, at this time, the included angle between the first guiding surface 120a and the preset surface may be the included angle between the first guiding line and the preset surface, and the included angle between the second guiding surface 120b and the preset surface may be the included angle between the second guiding line and the preset surface.
For example, in the example of fig. 1 to 5, the second guide surface 120b may extend from the downstream end of the first guide surface 120a in the circumferential direction of the bearing 100, in other words, the second guide surface 120b may extend from the downstream end of the first guide surface 120a in the direction toward the airflow outlet of the muffler, and the first guide surface 120a and the second guide surface 120b may be integrally provided, so that the guide slope 121 may be smoothly formed gradually in the exhaust direction, facilitating the machining of the guide slope 121; when the bearing 100 is applied to the rotary compressor, the second guide surface 120b may extend from the downstream end of the first guide surface 120a along the rotation direction of the driving of the rotary compressor, so that the design between the bearing 100 and the cylinder of the rotary compressor is more reasonable, the high pressure side and the low pressure side of the cylinder may correspond to the reasonable positions of the bearing 100, the matching between the bearing 100 and the cylinder is improved, and the use reliability of the rotary compressor is ensured.
Alternatively, the outer circumferential side of the discharge hole 112 may be formed with a protrusion 112a, and the protrusion 112a may be formed in a ring shape to be disposed around the discharge hole 112, so that the discharge valve may be in direct contact with the protrusion 112a when the discharge valve closes the discharge hole 112, and line contact may be made between the discharge valve and the protrusion 112a, ensuring that the discharge valve effectively closes the discharge hole 112.
The rotary compressor according to the second aspect embodiment of the present invention includes the bearing 100 for the rotary compressor according to the above-described first aspect embodiment of the present invention.
For example, an exhaust valve and a lift stopper of the rotary compressor may be installed in the installation cavity 11 through the installation part 111, and both the exhaust valve and the lift stopper may be fixedly connected to the bearing 100, an end of the exhaust valve corresponding to the exhaust hole 112 is adapted to cooperate with the exhaust hole 112 to open or close the exhaust hole 112, and an end of the lift stopper corresponding to the exhaust hole 112 is adapted to cooperate with the exhaust valve to limit a maximum displacement of the end of the exhaust valve; when the exhaust valve opens the exhaust hole 112, the compressed air flow (for example, refrigerant air flow) in the rotary compressor is exhausted through the exhaust hole 112 and flows into the silencing cavity under the guiding action of the diversion inclined plane 121 to perform silencing and rectification.
The rotary compressor can comprise a shell, a compression mechanism part and a driving device, wherein the driving device and the compression mechanism part are arranged in the shell, the compression mechanism part comprises an upper bearing, a lower bearing and an air cylinder assembly, the upper bearing and the lower bearing are respectively arranged at two axial ends of the air cylinder assembly to define a compression cavity, an exhaust hole is communicated with the compression cavity, and a crankshaft is arranged on the compression mechanism part in a penetrating manner; at least one of the upper and lower bearings may be provided with a silencer thereon, and at least one of the upper and lower bearings may be the bearing 100 for the rotary compressor according to the embodiment of the first aspect of the present invention. Wherein the driving device can be selected as a motor.
According to the rotary compressor provided by the embodiment of the invention, by adopting the bearing 100, the power consumption of the motor of the rotary compressor is effectively reduced, the extra power input by the compressor is avoided to offset the extra loss of airflow, the performance of the rotary compressor is improved, the running noise of the rotary compressor is reduced, and the sound quality of the rotary compressor is improved.
Other constructions and operations of the rotary compressor according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail herein.
In the description of the present invention, it is to be understood that the terms "central," "lateral," "length," "upper," "lower," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," "circumferential," and the like are used in the indicated orientations and positional relationships based on the figures, merely to facilitate the description of the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily 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.
While embodiments of the invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (10)
1. A bearing for a rotary compressor, characterized in that,
be formed with the exhaust valve seat on the bearing, inject installation cavity and water conservancy diversion chamber in the exhaust valve seat, the installation cavity is used for installing discharge valve and both ends to have installation department and exhaust hole respectively, the water conservancy diversion chamber intercommunication is in being close to of installation cavity one side in exhaust hole, just the diapire in water conservancy diversion chamber constructs to be: a flow guide slope extending obliquely to an outer surface of the bearing in a direction away from the mounting portion;
be formed with the connecting hole on the bearing, the connecting hole runs through the surface of bearing just is used for connecting the muffler, the connecting hole is a plurality of and follows the circumference interval distribution of bearing is a plurality of distance in the connecting hole exhaust hole is nearest, and is located keeping away from of exhaust hole one side of installation department the connecting hole is the target connecting hole, the target connecting hole is in aperture on the surface of bearing is d1The connecting line of the center of the target connecting hole and the center of the exhaust hole is a target connecting line, and the length of the target connecting line is L1；
The point on the diversion inclined plane, which is farthest from the mounting part, is a far-end point of the diversion cavity, the far-end point is positioned on one side, close to the central axis of the bearing, of the target connecting line, and the far-end point is L away from the center of the exhaust hole2Said L is2And said L1Satisfies the relationship: l is2≥L1-d1。
2. The bearing for the rotary compressor of claim 1, wherein the L is2And said L1Further satisfying the relationship: l is2≥L1-d1/2。
3. The bearing for the rotary compressor of claim 1, wherein the distal end point is spaced apart from a center of the target connection hole by a distance of L3Said L is3And d is as described1Satisfies the relationship: l is3≥d1/2+2mm。
4. The bearing for the rotary compressor of claim 1, wherein the contour line of the baffle cavity on the outer surface of the bearing includes an inner contour line and an outer contour line, the outer contour line being disposed on a side of the inner contour line away from the central axis of the bearing, both the inner contour line and the outer contour line extending from the distal end point in a direction toward the mounting cavity, a radial distance between the outer contour line and the inner contour line gradually decreasing in a direction from the mounting cavity to the distal end point.
5. The bearing for the rotary compressor of claim 4, wherein the outer contour line is constructed as an involute curve.
6. The bearing for the rotary compressor of claim 4, wherein the outer contour line has a first point and a second point, the first point being a point where the outer contour line intersects the mounting cavity, the second point being a point where a connecting line of the mounting portion and the discharge hole intersects the outer contour line, the first point being spaced apart from a center of the discharge hole by a distance of R1The second point is away from the center of the exhaust hole by R2Said R is1And said R2Satisfies the relationship: r1＜R2＜L2。
7. The bearing for the rotary compressor of any one of claims 1 to 6, wherein the guide slope is a smooth curved surface.
8. The bearing for the rotary compressor of claim 7, wherein the smooth curved surface is a streamline curved surface.
9. The bearing for the rotary compressor of claim 8, wherein the streamlined curved surface comprises a first guide surface and a second guide surface sequentially connected in a direction from the discharge hole to the distal end point, an included angle between the first guide surface and a preset surface is α, an included angle between the second guide surface and the preset surface is β, and the α and the β satisfy the relationship of β ≥ α and 0.3 ≤ sin α ≤ 0.8, wherein the preset surface is a plane perpendicular to a central axis of the bearing.
10. A rotary compressor characterized by comprising the bearing for a rotary compressor according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811456791.3A CN111255807B (en) | 2018-11-30 | 2018-11-30 | Bearing for rotary compressor and rotary compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811456791.3A CN111255807B (en) | 2018-11-30 | 2018-11-30 | Bearing for rotary compressor and rotary compressor |
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| CN111255807A true CN111255807A (en) | 2020-06-09 |
| CN111255807B CN111255807B (en) | 2021-10-19 |
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| KR20110015852A (en) * | 2009-08-10 | 2011-02-17 | 엘지전자 주식회사 | Compressor |
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| CN106089656A (en) * | 2016-08-16 | 2016-11-09 | 珠海凌达压缩机有限公司 | Compressor and cylinder assembly thereof |
| CN205744466U (en) * | 2016-05-17 | 2016-11-30 | 广东美芝制冷设备有限公司 | Delivery valve seat and there is its rotary compressor |
| CN106246558A (en) * | 2016-09-18 | 2016-12-21 | 珠海凌达压缩机有限公司 | The deafener of compressor and there is its compressor |
| CN107120279A (en) * | 2017-06-30 | 2017-09-01 | 广东美芝制冷设备有限公司 | Compressor and the refrigerating plant with it |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JPS6111493A (en) * | 1984-06-27 | 1986-01-18 | Hitachi Ltd | Horizontal rotary compressor |
| CN2913668Y (en) * | 2006-06-05 | 2007-06-20 | 松下·万宝(广州)压缩机有限公司 | Compressor |
| KR20110015852A (en) * | 2009-08-10 | 2011-02-17 | 엘지전자 주식회사 | Compressor |
| CN204877872U (en) * | 2015-08-18 | 2015-12-16 | 珠海凌达压缩机有限公司 | Pump body structure and compressor |
| CN205744466U (en) * | 2016-05-17 | 2016-11-30 | 广东美芝制冷设备有限公司 | Delivery valve seat and there is its rotary compressor |
| CN106089656A (en) * | 2016-08-16 | 2016-11-09 | 珠海凌达压缩机有限公司 | Compressor and cylinder assembly thereof |
| CN106246558A (en) * | 2016-09-18 | 2016-12-21 | 珠海凌达压缩机有限公司 | The deafener of compressor and there is its compressor |
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| Publication number | Publication date |
|---|---|
| CN111255807B (en) | 2021-10-19 |
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