CN107542661B - Single-cylinder rotary compressor - Google Patents
Single-cylinder rotary compressor Download PDFInfo
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- CN107542661B CN107542661B CN201710527693.3A CN201710527693A CN107542661B CN 107542661 B CN107542661 B CN 107542661B CN 201710527693 A CN201710527693 A CN 201710527693A CN 107542661 B CN107542661 B CN 107542661B
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Abstract
The invention discloses a single-cylinder rotary compressor, which comprises a motor part and a compression part, wherein the compression part comprises: the crankshaft comprises a shaft part and an eccentric part, the shaft part is connected with the motor part, one end of the eccentric part, far away from the motor part, is formed into a crankshaft thrust part, and the eccentric part of the crankshaft is provided with a flexible groove for reducing the axial rigidity of the crankshaft thrust part; the single-cylinder rotary compressor provided by the embodiment of the invention has the advantages that the friction loss of the thrust friction pair can be reduced, the service life of the compressor is prolonged, and the compression efficiency of the compressor is improved.
Description
Technical Field
The invention relates to the technical field of refrigeration, in particular to a single-cylinder rotary compressor.
Background
In the related art, the rolling rotor type rotary compressor generally uses the lower end surface of the eccentric portion of the crankshaft as a crankshaft thrust portion, and cooperates with the upper end surface of the auxiliary bearing to form a sliding thrust friction pair, so as to timely limit the axial movement of the crankshaft. Compared with the traditional structure that the lower end surface of the auxiliary shaft part of the crankshaft is used as the thrust part, the structure does not need parts such as a thrust plate, and the like, is simpler and more compact, has lower cost and is widely applied.
However, in practical use, the abrasion of the thrust friction pair with the structure is very serious, the performance of the compressor is seriously affected, and the defect is particularly obvious under severe operating conditions.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides a single-cylinder rotary compressor capable of reducing thrust friction loss.
The single cylinder rotary compressor according to an embodiment of the present invention includes a motor part and a compression part, the compression part including: the crankshaft comprises a shaft part and an eccentric part, the shaft part is connected with the motor part, one end of the eccentric part, far away from the motor part, is formed into a crankshaft thrust part, and the eccentric part of the crankshaft is provided with a flexible groove for reducing the axial rigidity of the crankshaft thrust part; the cylinder, inject air suction cavity and slide groove in the cylinder, the flexible groove sets up on the eccentric portion and be located at least when the eccentric portion rotates to the most far away from the slide groove on the one side that corresponds with the air suction cavity on the reference plane, the central axis of eccentric portion with the plane at the central axis place of vice axial region is the reference plane.
According to the single cylinder rotary compressor of the embodiment of the present invention, by disposing the flexible groove at the left side of the plane, so that the flexible groove is distributed on the side of the eccentric portion corresponding to the suction chamber when the discharge valve is opened, because the contact stress on the side of the crankshaft thrust part is larger, the rigidity of the crankshaft thrust part in the axial direction partially or wholly can be reduced by adopting the structure, so that under the action of external load (mainly gas force Fg), the partial or whole crankshaft thrust portion can produce larger deformation in axial direction, so that the contact stress applied on the thrust friction pair (or crankshaft thrust portion) can be more uniformly distributed, thereby effectively reducing the abrasion of the thrust friction pair, simultaneously reducing the area of rough contact, therefore, the friction loss is effectively reduced, the service life of the compressor is prolonged, and the compression efficiency of the compressor is improved.
According to the single-cylinder rotary compressor provided by the embodiment of the invention, the flexible grooves are at least positioned in a preset distribution range; when the crankshaft rotates clockwise and the central axis of the eccentric part where the crankshaft thrust part is located between the central axis of the shaft part and the observer when the crankshaft rotates clockwise along the motor part and the central axis of the eccentric part where the crankshaft thrust part is located, the central axis of the eccentric part where the crankshaft thrust part is located and the plane where the central axis of the shaft part is located are defined as initial planes, and the preset distribution range is an area where an included angle in the clockwise direction with the initial planes falls within a range of (20 degrees and 120 degrees); follow the motor part to when compressing the part direction observation, the bent axle anticlockwise rotates, and the central axis of the eccentric portion at bent axle thrust portion place is located the central axis of axial region with during the observer, the definition the central axis of the eccentric portion at bent axle thrust portion place, the plane at the central axis place of axial region is initial plane, predetermine distribution range for with initial plane contained angle on the anticlockwise falls into (20, 120) the region of within range.
According to some embodiments of the invention, the flexible groove is radially disposed and spaced apart from the crankshaft thrust portion, wherein radially refers to a direction perpendicular to an axial direction, which is a central axis direction of the shaft portion of the crankshaft.
In some embodiments, a top portion of the flexible slot extends through an outer sidewall of the eccentric portion in the radial direction.
In some embodiments, a projection of the flexible groove in the axial direction is located outside a projection of the shaft portion in the axial direction.
In some embodiments, a bottom wall of the flexible groove is arc-shaped, a center of curvature of the bottom wall is collinear with a central axis of the shaft portion of the crankshaft, and both ends of the bottom wall extend to intersect with an outer peripheral surface of the eccentric portion; or the bottom wall of the flexible groove is a plane.
In some embodiments, a thickness between an inner wall of the flexible groove and the crankshaft thrust portion is a wall thickness of the flexible groove, the wall thickness of the flexible groove gradually decreases in a radial direction away from a central axis of the shaft portion or the wall thickness of the flexible groove is a constant value.
In some embodiments, the flexible slot has a constant width in the axial direction.
In some embodiments, the ratio of the maximum depth H of the flexible groove in the radial direction to the average wall thickness T of the flexible groove satisfies the following condition: H/T is more than or equal to 1 and less than or equal to 10.
In some embodiments, the maximum depth H ≧ 2mm in the radial direction of the flexible groove.
In some embodiments, the flexible groove has an average wall thickness T ≧ 1 mm.
In some embodiments, the minimum width W of the flexible slot in the axial direction is greater than or equal to 1 mm.
According to one embodiment of the single-cylinder rotary compressor, the single-cylinder rotary compressor is a vertical single-cylinder rotary compressor or a horizontal single-cylinder rotary compressor.
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 view of a conventional single cylinder rotary compressor.
Fig. 2 is a force-bearing schematic view of a thrust friction pair of a conventional single-cylinder rotary compressor.
Fig. 3 is a schematic view of a single cylinder rotary compressor according to one embodiment of the present invention.
FIG. 4 is a force diagram of a thrust friction pair of a single cylinder rotary compressor in accordance with one embodiment of the present invention.
FIG. 5 is a schematic top view of a crankshaft of a single cylinder rotary compressor in accordance with one embodiment of the present invention.
Fig. 6 is a schematic sectional view taken along line a-a of fig. 5.
Fig. 7 is a schematic bottom view of a crankshaft of a single cylinder rotary compressor in accordance with another embodiment of the present invention.
FIG. 8 is a graph illustrating maximum contact stress versus H/T for a single cylinder rotary compressor in accordance with one embodiment of the present invention.
Fig. 9 is a schematic sectional view of a crankshaft of a single-cylinder rotary compressor according to still another embodiment of the present invention (the width of the flexible groove is constant).
Fig. 10 is a schematic sectional view of a crankshaft of a single cylinder rotary compressor according to still another embodiment of the present invention (the wall thickness of the flexible groove is constant).
Reference numerals:
the traditional structure is as follows:
crankshaft 10 ', main shaft portion 11 ', auxiliary shaft portion 12 ', eccentric portion 13 ', crankshaft thrust portion 14 ', main bearing 30 ', auxiliary bearing 40 ', piston 50 ', cylinder 60 ',
the application:
a single cylinder rotary compressor 100, a crankshaft 10, a main shaft part 11, an auxiliary shaft part 12, an eccentric part 13, a crankshaft thrust part 14,
a flexible channel 20, a bottom wall 21 of the flexible channel,
the main bearing 30 is provided with a bearing,
the sub-bearing 40 is provided with a sub-bearing,
the piston (50) is provided with a piston,
and a cylinder 60.
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.
The present application was made by the applicant based on the following recognition:
the structure of the conventional single cylinder rotary compressor is briefly described as follows: referring to fig. 1, the conventional single cylinder rotary compressor includes a motor part and a compression part, and the compression part includes: a cylinder 60 ', a piston 50 ', a slide (not shown), a main bearing 30 ', a sub bearing 40 ', a crankshaft 10 ', etc. The cylinder 60 'is divided into a suction chamber and an exhaust chamber, and the motor unit drives the compression unit to move through the shaft of the crankshaft 10', so as to change the volumes of the suction chamber and the exhaust chamber, thereby completing the working process of continuously sucking, compressing and discharging the refrigerant.
The crankshaft 10 'includes a shaft portion including a main shaft portion 11' and an auxiliary shaft portion 12 ', and an eccentric portion 13', the main shaft portion 11 'being engaged with the main bearing 30' and connected with the motor part, and the auxiliary shaft portion 12 'being engaged with the auxiliary bearing 40'. The surface of the crankshaft 10 'on the side away from the motor part through the eccentric portion 13' is a crankshaft thrust portion 14 ', and the surface of the side of the auxiliary bearing 40' close to the motor part is an auxiliary bearing thrust portion, which is engaged with the crankshaft thrust portion 14 ', thereby restricting the axial movement of the crankshaft 10'. The crankshaft thrust part 14' and the auxiliary bearing thrust part together form a sliding thrust friction pair. The oil sump of the compressor supplies oil and lubricates the thrust friction pair through an oil supply passage (not shown) of the crankshaft 10'.
For the existing single-cylinder rotary compressor, the abrasion at the thrust friction pair is serious, and the phenomenon is particularly prominent under the severe operating condition. Therefore, the reliability of the operation of the compressor is poor, parts need to be replaced frequently, and meanwhile, the performance of the compressor is seriously affected due to large friction loss.
For the reasons of wear of the prior art designs of thrust friction pairs, the person skilled in the art has not been able to identify fundamentally the critical factors responsible for the wear. In view of the above, the applicant has conducted extensive, repeated and intensive studies to find and clarify the key factors causing the problem of wear of the thrust friction pair. Fig. 2 is an explanatory diagram of the principle of wear of the thrust friction pair discovered by the applicant. The deformation of the crankshaft 10' is exaggerated for ease of viewing.
The applicant has found that the crankshaft 10' is subjected to an axial force Fm mainly consisting of the gravitational force exerted on the rotating parts themselves and the axial magnetic pull of the motor. And the eccentric portion 13 'of the crankshaft 10' is largely deformed by the gas force Fg caused by the pressure difference between the suction chamber and the compression chamber, as shown in fig. 2.
After the crankshaft 10 'is deformed, the crankshaft thrust part 14' is inclined, and mainly inclined towards the side of the crankshaft thrust part 14 corresponding to the air suction cavity, and the outer side of the crankshaft thrust part 14 'is in line contact with the end surface of the auxiliary bearing 40', so that local contact stress concentration is caused, and the distribution of the thrust friction auxiliary contact stress P is illustrated in the figure. Thus, excessive local contact stress can cause severe wear and even scratching or sticking of the thrust portion, and in severe cases, failure of the thrust friction pair.
It follows that the deformation of the crankshaft 10' caused by the gas forces Fg is the key factor in causing wear of the thrust friction pair.
The applicant further researches and discovers that the gas force is mainly determined by the operation condition and main structural parameters such as the diameter and the height of the cylinder 60 ', the shaft diameter of the crankshaft 10 ' is generally designed in a small diameter mode in order to improve the performance of the compressor, so that the rigidity of the crankshaft 10 ' is poor, and finally the abrasion of the thrust friction pair becomes a common problem in the industry. Since the gas force Fg and the rigidity of the crankshaft 10' are restricted by other factors and are difficult to change, the improvement of the wear of the thrust friction pair is greatly restricted and difficult.
Based on the research findings, the invention creatively provides a solution for arranging the flexible structure near the thrust part, and the solution has the advantages of simple structure, convenient implementation and extremely obvious improvement effect.
The single cylinder rotary compressor 100 according to the embodiment of the present invention will be described in detail with reference to fig. 3 to 10.
As shown in fig. 3, the single cylinder rotary compressor 100 according to the embodiment of the present invention includes a motor part and a compression part, the compression part including: crankshaft 10 and cylinder 60, crankshaft 10 include the axial part and eccentric portion 13, the axial part is connected with the motor part, the one end far away from the motor part of eccentric portion 13 forms crankshaft thrust portion 14, eccentric portion 13 of crankshaft 10 is equipped with flexible groove 20 used for reducing the axial rigidity of said crankshaft thrust portion 14. The cylinder 60 defines a suction cavity and a slide sheet groove therein, the flexible groove 20 is disposed on the eccentric portion 13 and at least located on one side of the reference plane corresponding to the suction cavity when the eccentric portion 13 rotates to a position farthest from the slide sheet groove, and a plane where the central axis of the eccentric portion 13 and the central axis of the auxiliary shaft portion 12 are located is the reference plane.
The applicant has found through intensive research that, during the operation of the compressor, the gas force Fg applied to the crankshaft 10 changes continuously, the gas force applied to the crankshaft is the greatest at the exhaust angle (i.e. the position of the crankshaft 10 when the exhaust valve of the compressor is just opened), the contact stress distributed on the thrust portion 14 of the crankshaft is the greatest at this time, and the designed position of the flexible groove 20 should correspond to the side of the thrust friction pair where the maximum contact stress is distributed in the axial direction.
The single cylinder rotary compressor 100 according to the embodiment of the present invention, by disposing the flexible groove 20 at the left side of the reference plane, so that the flexible slots 20 are distributed on the side of the eccentric 13 opposite to the suction chamber when the discharge valve is open, since the contact stress to which the crankshaft thrust portion 14 is subjected on that side is large, employing the above-described structure can reduce the rigidity of the crankshaft thrust portion 14 partially or entirely in the axial direction, so that under the action of external load (mainly gas force Fg) of crankshaft 10, the crankshaft thrust portion 14 can be locally or wholly deformed greatly in axial direction, so that the contact stress applied on the thrust friction pair (or crankshaft thrust portion 14) can be more uniformly distributed, thereby effectively reducing the abrasion of the thrust friction pair, simultaneously reducing the area of rough contact, therefore, the friction loss is effectively reduced, the service life of the compressor is prolonged, and the compression efficiency of the compressor is improved.
Specifically, a side of the eccentric portion corresponding to the suction chamber on the reference plane at least when the eccentric portion is rotated to a position farthest from the vane slot may be a left side of the reference plane.
By providing the flexible groove 20 at the above position, the stress concentration distribution on the crankshaft thrust portion 14 can be avoided, and the friction loss of the thrust friction pair can be effectively reduced.
Specifically, when the crankshaft 10 rotates clockwise, the side of the reference plane corresponding to the suction chamber is the right side of the reference plane; when the crankshaft 10 rotates counterclockwise, the side of the reference plane corresponding to the suction chamber is the left side of the reference plane.
Wherein the left-right direction is defined in the following way: when viewed along the motor member in the direction of the compression member (in plan view), the center axis of the eccentric portion 13 is located between the center axis of the shaft portion and the observer, with reference to the left-right direction assumed by the observer at this time.
In general, a compressor of an air conditioner is rotated counterclockwise in a plan view, and a flexible groove should be provided at the left side of a reference plane in the plan view, and fig. 5 is a plan view, so that the flexible groove is seen at the left side of the reference plane.
As a preferred embodiment, as shown in fig. 5, a plane where the central axis of the eccentric portion 13 and the central axis of the shaft portion where the crankshaft thrust portion 14 is located is defined as an initial plane, the preset distribution range is a region where an included angle in a clockwise direction from the initial plane falls within a range of (20 ° and 120 °), and the flexible groove 20 is located at least within the preset distribution range. In other words, as shown in fig. 6, the preset distribution range is a region in which an angle in the counterclockwise direction from the initial plane falls within a range of (20 °, 120 °) as viewed in the direction of the mechanical part with respect to the motor part (from the bottom).
Therefore, the crankshaft thrust part 14 is not damaged, and the crankshaft thrust part 14 is fully contacted with the corresponding thrust part, so that better fluid dynamic pressure lubrication is formed at the thrust friction pair, the abrasion is reduced, and the stability and the reliability of the operation of the compressor are enhanced.
It will be appreciated that the compression member comprises: a cylinder 60, a piston 50, a sliding vane (not shown), a main bearing 30, an auxiliary bearing 40, a crankshaft 10, and the like. The cylinder 60 is divided into a suction chamber and an exhaust chamber, and the motor unit drives the compression unit to move through the shaft of the crankshaft 10, so as to change the volumes of the suction chamber and the exhaust chamber, thereby completing the working process of continuously sucking, compressing and discharging the refrigerant.
The shaft portion of the crankshaft 10 includes a main shaft portion 11 and a sub shaft portion 12, the main shaft portion 11 is engaged with the main bearing 30 and connected to the motor part, and the sub shaft portion 12 is engaged with the sub bearing 40. When the crankshaft thrust part 14 is matched with the auxiliary bearing 40, the crankshaft thrust part 14 of the eccentric part 13 of the crankshaft 10 and the auxiliary bearing thrust part of the auxiliary bearing 40 form a thrust friction pair, and when the crankshaft 10 is in thrust matching with the thrust plate, the crankshaft thrust part 14 of the eccentric part 13 of the crankshaft 10 and the thrust plate thrust part of the thrust plate form a thrust friction pair.
As shown in fig. 4, according to the single cylinder rotary compressor 100 of one embodiment of the present invention, the flexible structure is the flexible groove 20. Thus, by providing the flexible slot 20 in the eccentric portion 13 of the crankshaft 10, the stiffness of the crankshaft thrust portion 14 in the axial direction is significantly reduced, such that when the crankshaft 10 is subjected to the gas force FgWhen deformation occurs under the action, the crankshaft thrust part 14 can still well keep surface contact with the thrust part of the auxiliary bearing or the thrust plate thrust part, so that the contact stress acting on the thrust friction pair is uniform, the maximum contact stress and the rough contact degree are effectively reduced, and the abrasion and the friction loss of the thrust friction pair are improved.
Of course, the flexible structure is not limited to the flexible groove 20, and the axial rigidity of the crankshaft thrust portion 14 may be reduced by embedding a material with a smaller elastic modulus on the crankshaft thrust portion 14, that is, other structures provided on the eccentric portion 13 of the crankshaft 10, which can reduce the rigidity of the crankshaft thrust portion 14 in the axial direction partially or entirely, as will be understood by those skilled in the art, are also covered in the protection scope of the present application, and are not listed here.
According to some embodiments of the present invention, the flexible groove 20 is radially disposed and spaced apart from the crankshaft thrust portion 14, wherein radially refers to a direction perpendicular to an axial direction, which is a central axis direction of the shaft portion of the crankshaft 10. Therefore, the crankshaft thrust part 14 cannot be damaged, the crankshaft thrust part 14 can move towards the direction far away from the motor component under the action of gas force, and the crankshaft thrust part 14 is in full contact with the corresponding thrust part, so that better fluid dynamic pressure lubrication is formed at a thrust friction pair, the abrasion is reduced, and the stability and the reliability of the operation of the compressor are enhanced.
As a preferred embodiment, as shown in fig. 5 and 6, the top of the flexible slot 20 radially penetrates the outer side wall of the eccentric portion 13. In other words, the notch of the flexible groove 20 is formed on the outer side wall of the eccentric portion 13. Thus, not only is the influence of the flexible groove 20 on the strength of the eccentric portion 13 reduced, but also the processing is facilitated.
It will be appreciated that the top of the flexible slot 20 may not extend through the outer side wall of the eccentric portion 13 or a portion of the top of the flexible slot 20 may extend through the outer side wall of the eccentric portion 13.
In some embodiments, as shown in fig. 5, the projection of the flexible groove 20 in the axial direction is located outside the projection of the shaft portion in the axial direction. Alternatively, the bottom wall 21 of the flexible groove 20 may have a circular arc shape, the center of curvature of the bottom wall 21 being collinear with the central axis of the shaft portion of the crankshaft 10, and both ends of the bottom wall extending to intersect the outer peripheral surface of the eccentric portion 13. In this way, the weakening of the stiffness of the crankshaft 10 itself by the flexible slots 20 is reduced, while the wear of the thrust friction pairs is improved, and at the same time the stress concentration on the crankshaft 10 is reduced.
Further studies have found that the dimensioning of the flexible groove 20 has a great influence on the improvement. As shown in FIGS. 7 and 8, the ratio of the radial maximum depth H of the flex groove 20 to the average wall thickness T affectsMost importantly, as H/T increases, the rigidity of the crankshaft thrust portion 14 gradually decreases and the maximum contact stress PmaxRapidly decreases; however, as H/T is further increased, the stiffness of the crankshaft thrust portion 14 becomes too low, which leads to a concentrated distribution of contact stress, and the maximum contact stress P is setmaxAnd is increased.
According to the above theory and the related experimental research, it is found that the ratio of the maximum depth H of the flexible groove 20 in the radial direction to the average wall thickness T of the flexible groove 20 satisfies the following condition: the improvement effect is better when H/T is more than or equal to 1 and less than or equal to 10. The thickness between the inner wall of the flexible groove 20 and the crankshaft thrust part 14 is the wall thickness of the flexible groove 20, and the average wall thickness T is the volume V of the inner wall between the inner wall of the flexible groove 20 and the crankshaft thrust part 14/the projection area S of the flexible groove 20 in the axial direction.
Advantageously, the maximum depth H of the flexible groove 20 in the radial direction is ≧ 2 mm. That is, the maximum depth H of the flexible groove 20 in the radial direction around the center axis of the shaft portion is 2mm or more.
When the size of the flexible groove 20 is too small, the flexible groove is not beneficial to processing and manufacturing, and in order to improve the processing manufacturability, the following design can be adopted: the average wall thickness T of the flexible groove 20 is more than or equal to 1mm, and the minimum width W of the flexible groove 20 in the axial direction is more than or equal to 1 mm. In the embodiment shown in fig. 6, W is the minimum width value when it is gradually reduced in the radial direction away from the axis of the shaft portion of the crankshaft 10.
In the embodiment shown in fig. 9, the width of the flexible groove 20 in the axial direction may be a constant value, and the minimum width W is the fixed groove width of the flexible groove 20. In this way, equal-width turning tool machining is possible, and the flexible groove 20 has little effect on the outer peripheral area of the eccentric portion 13, and does not affect lubrication between the eccentric portion 13 of the crankshaft 10 and the piston 50.
In the particular embodiment shown in FIG. 6, the thickness between the inner wall of the flex groove 20 and the crankshaft thrust portion 14 is the wall thickness of the flex groove 20, with the wall thickness of the flex groove 20 gradually decreasing in a radial direction away from the central axis of the shaft portion.
Of course, the present invention is not so limited and the wall thickness of the flexible channel 20 may be selected in a variety of ways, and in the particular embodiment shown in FIG. 10, the wall thickness of the flexible channel 20 is constant. The design of the flexible groove 20 with the same wall thickness is adopted, the influence of the increase of the flexible groove 20 on the processing of the crankshaft 10 is reduced to the maximum extent, the processing manufacturability is better, and the influence on the contact area between the eccentric part 13 of the crankshaft 10 and the piston 50 is smaller.
In addition, the above definition of the size (e.g., H, T, W) of the flexible slot 20 is also applicable to the specific embodiment shown in fig. 9 to 10, and is not repeated herein. In the particular embodiment shown in fig. 9-10, the wall thickness of the flexible groove 20 is a constant value, and thus the average wall thickness T, the thickness between the inner wall of the flexible groove 20 and the crankshaft thrust portion 14, is the wall thickness of the flexible groove 20.
The single-cylinder rotary compressor 100 shown in fig. 3 to 10 is a vertical single-cylinder rotary compressor. It will be appreciated that the above embodiments are equally applicable to horizontal single cylinder rotary compressors.
The crankshaft thrust portion 14, the auxiliary bearing thrust portion, and the like may be thrust surfaces formed on the respective components.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present invention and to simplify the description, but are not intended to indicate or imply that the structures or elements so referred to must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered as limiting. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
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 (13)
1. A single cylinder rotary compressor comprising a motor part and a compression part, said compression part comprising:
the crankshaft comprises a shaft part and an eccentric part, the shaft part is connected with the motor part, the shaft part comprises a main shaft part and an auxiliary shaft part, one end of the eccentric part, which is far away from the motor part, is formed into a crankshaft thrust part, and the eccentric part of the crankshaft is provided with a flexible groove for reducing the axial rigidity of the crankshaft thrust part; and
the cylinder, inject air suction cavity and slide groove in the cylinder, the flexible groove sets up on the eccentric portion and be located at least when the eccentric portion rotates to the most far away from the slide groove on the one side that corresponds with the air suction cavity on the reference plane, the central axis of eccentric portion with the plane at the central axis place of vice axial region is the reference plane.
2. The single cylinder rotary compressor of claim 1, wherein the flexible slots are located at least within a predetermined distribution;
when the crankshaft rotates clockwise and the central axis of the eccentric part where the crankshaft thrust part is located between the central axis of the shaft part and an observer when the crankshaft rotates clockwise along the motor part and the central axis of the eccentric part where the crankshaft thrust part is located, the central axis of the eccentric part where the crankshaft thrust part is located and the plane where the central axis of the shaft part is located are defined as initial planes, and the preset distribution range is an area where an included angle in the clockwise direction with the initial planes falls within a range of (20 degrees and 120 degrees);
the edge the motor part to when compressing the part direction observation, during bent axle anticlockwise rotation, and the central axis of the eccentric portion at bent axle thrust portion place is located the central axis of axial region with when the observer between, the definition the central axis of the eccentric portion at bent axle thrust portion place, the plane at the central axis place of axial region be initial plane, predetermine distribution range for with initial plane contained angle on the anticlockwise falls into (20, 120) the region within range.
3. The single cylinder rotary compressor of claim 1 or 2, wherein the flexible groove is radially disposed and spaced apart from the crankshaft thrust portion, wherein radially refers to a direction perpendicular to an axial direction, which is a central axis direction of the shaft portion of the crankshaft.
4. The single cylinder rotary compressor of claim 1 or 2, wherein a top of the flexible slot radially penetrates an outer sidewall of the eccentric portion.
5. The single cylinder rotary compressor of claim 1 or 2, wherein a projection of the flexible groove in the axial direction is located outside a projection of the shaft portion in the axial direction.
6. The single cylinder rotary compressor of claim 1 or 2, wherein the bottom wall of the flexible groove is circular arc-shaped, the center of curvature of the bottom wall is collinear with the central axis of the shaft portion, and both ends of the bottom wall extend to intersect with the outer peripheral surface of the eccentric portion; or the bottom wall of the flexible groove is a plane.
7. The single cylinder rotary compressor of claim 1 or 2, wherein a thickness between the inner wall of the flexible groove and the crankshaft thrust portion is a wall thickness of the flexible groove, the wall thickness of the flexible groove gradually decreases in a direction away from the central axis of the shaft portion in a radial direction or the wall thickness of the flexible groove is a constant value.
8. The single cylinder rotary compressor of claim 1 or 2, wherein the width of the flexible groove in the axial direction is constant.
9. The single cylinder rotary compressor of claim 1 or 2, wherein the ratio of the maximum depth H of the flexible groove in the radial direction to the average wall thickness T of the flexible groove satisfies the following condition: H/T is more than or equal to 1 and less than or equal to 10.
10. The single cylinder rotary compressor of claim 1 or 2, wherein the maximum depth H of the flexible groove in the radial direction is 2mm or more.
11. Single cylinder rotary compressor according to claim 1 or 2, characterized in that the flexible groove has an average wall thickness T ≧ 1 mm.
12. The single cylinder rotary compressor of claim 1 or 2, wherein the minimum width W of the flexible groove in the axial direction is not less than 1 mm.
13. The single cylinder rotary compressor of claim 1, wherein the single cylinder rotary compressor is a vertical single cylinder rotary compressor or a horizontal single cylinder rotary compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710527693.3A CN107542661B (en) | 2017-06-30 | 2017-06-30 | Single-cylinder rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710527693.3A CN107542661B (en) | 2017-06-30 | 2017-06-30 | Single-cylinder rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107542661A CN107542661A (en) | 2018-01-05 |
| CN107542661B true CN107542661B (en) | 2020-01-10 |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02277995A (en) * | 1989-04-20 | 1990-11-14 | Sanyo Electric Co Ltd | Rotary compressor |
| CN2103672U (en) * | 1991-07-30 | 1992-05-06 | 国营八四四厂 | Rotary compressor lubricating system |
| CN1601126A (en) * | 2003-09-27 | 2005-03-30 | 乐金电子(天津)电器有限公司 | Crankshaft of rotary compressor |
| CN201953659U (en) * | 2011-03-09 | 2011-08-31 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN203500015U (en) * | 2013-09-09 | 2014-03-26 | 广东美芝制冷设备有限公司 | Crankshaft for rotary compressor and rotary compressor with crankshaft |
| CN105889069A (en) * | 2016-05-30 | 2016-08-24 | 广西大学 | Rotating compressor low in exhaust oil content |
| CN207297354U (en) * | 2017-06-30 | 2018-05-01 | 广东美芝制冷设备有限公司 | Single cylinder rotary compressor |
-
2017
- 2017-06-30 CN CN201710527693.3A patent/CN107542661B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02277995A (en) * | 1989-04-20 | 1990-11-14 | Sanyo Electric Co Ltd | Rotary compressor |
| CN2103672U (en) * | 1991-07-30 | 1992-05-06 | 国营八四四厂 | Rotary compressor lubricating system |
| CN1601126A (en) * | 2003-09-27 | 2005-03-30 | 乐金电子(天津)电器有限公司 | Crankshaft of rotary compressor |
| CN201953659U (en) * | 2011-03-09 | 2011-08-31 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN203500015U (en) * | 2013-09-09 | 2014-03-26 | 广东美芝制冷设备有限公司 | Crankshaft for rotary compressor and rotary compressor with crankshaft |
| CN105889069A (en) * | 2016-05-30 | 2016-08-24 | 广西大学 | Rotating compressor low in exhaust oil content |
| CN207297354U (en) * | 2017-06-30 | 2018-05-01 | 广东美芝制冷设备有限公司 | Single cylinder rotary compressor |
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| CN107542661A (en) | 2018-01-05 |
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